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Home Features AGMA/ANSI/ISO Standards on Bevel and Hypoid Gears
AGMA/ANSI/ISO Standards on Bevel and Hypoid Gears
Vishnu Irigireddy
Dr. Stephen P. Radzevich Ph.D., Dr. (Eng) Sci.
An examination of how standards for bevel and hypoid gearing benefit from the latest achievements in gearing theory.
This paper deals with gearings that operate (a) on intersected shafts and (b) on crossed shafts. The gearings that operate on intersected shafts are referred to as "intersected-axes gearings," or just "Ia−gearings" for simplicity. Similarly, the gearings that operate on crossed shafts are referred to as "crossed-axes gearings," also referred to as "Ca−gearings1." Hypoid, spiroid, and a few other gear systems are covered by the terms "crossed-axes gearings."
The main goal of the paper is to show how the ANSI/AGMA/ISO standards for bevel and hypoid gearing; that is, [1], [2], [3], [4], and others can be benefited by the latest achievements in the theory of gearing2 [5]. All the standards, including but not limited to ANSI/AGMA/ISO standards, must provide a user with a complete and consistent information on the subject. Often, unfortunately, this is not observed.
As an example, the principal features of the determination and inspection of the design parameters of a gear and a mating pinion that directly affect the gear mesh efficiency are considered in this paper. In particular: (a) the geometrical dimensioning and tolerancing; (b) the contact pattern; (c) the mounting distance, and (d) the backlash in Ia−gearing, as well as in Ca−gearing, are discussed as examples.
As is well known, the "kinematics" and the "geometry" of a gear and a mating pinion tooth flanks are investigated in the theory of gearing. Therefore, only the kinematics of a gear pair and the geometry of the gear and the mating pinion tooth flanks are covered in this paper. However, it should be noted that use of the approach developed in the theory of gearing enables one to solve numerous problems in the field of gear dynamics, transmitted power density, noise excitation and vibration generation in a gear pair, calculating of the tolerances for the design parameters of a gear pair, and so forth.
It is shown that the theory of gearing could be a powerful tool to improve ANSI/AGMA/ISO standards [1], [2], [3], [4], and others. Some inconsistencies in ANSI/AGMA/ISO standards are discussed as the examples. The geometrical dimensioning and tolerancing, the contact pattern, the mounting distance, and the backlash are among them. A more detailed discussion of these issues would take a far lengthier paper. It makes sense to begin the discussion on bevel and hypoid gearing with an analysis of the recommended [1], [2], [3], [4], geometrical dimensioning.
Geometrical dimensioning
The set of the geometrical dimensions recommended for bevel gearing by ANSI/AGMA/ISO standards ([1] in particular), is shown in Figure 1. All the geometrical dimensions shown in Figure 1, and those not shown here, can be subdivided into two groups; that is, the geometrical dimensions that directly affect the conditions of the gear teeth engagement, and those indirectly affected by the conditions of the gear teeth engagement. Let's take a brief look at the terminology and geometrical dimensioning recommended by ANSI/AGMA/ISO standards ([1] in particular).
Figure 1: A set of the geometrical dimensions for bevel and hypoid gearings recommended by ANSI/AGMA 2005-D03 standard [1].
The set of the recommended geometrical dimensions3 illustrated in Figure 1 is far from being aligned with the best practice for national and international standards on design dimensioning. An excessive plurality of datum surfaces (and sometimes the physical absence of the datum surfaces) is the main reason for that.
For example, the back cone and the back face are used as the datum surfaces for the specification of the back angle, A. The back cone angle, B, is specified as the apex angle of the back cone. The back cone distance, C, is specified as a distance between the back cone apex (the back cone apex physically does not exist) and the pitch cone that physically also does not exist, and so forth.
Importance (and usefulness) of the items such as the crown point, E, is at least doubtful, as this datum element of poor quality. The geometrical dimension shown in Figure 1 and labeled as M is not a mounting distance at all, as the mounting distance cannot be specified in terms of the location of point M outside of the gear tooth flank (see following section on Contact Patterning).
Figure 2: An alternative set of the geometrical dimensions for bevel and hypoid gearings.
An alternative set of the geometrical dimensions is illustrated in Figure 2. This set of geometrical dimensions is sufficient for both the gear production as well as for the gear inspection. The gear common reference surface and the gear bore are used as the main set of datum surfaces for the gear. Similarly, the pinion common reference surface and the pinion bore are used as the main set of datum surfaces for the pinion4. All the geometrical dimensions that directly affect the condition of meshing are required to be specified with respect to the corresponding set of the main datum. The rest of the design parameters are also to be associated with the corresponding set of the main datum. Because of this, the geometrical dimensioning of a bevel gear pair in Figure 2 are advantageous over those in Figure 1.
Again, an excessive plurality of datum surfaces (and sometimes the physical absence of the datum surfaces) have to be eliminated in all possible ways. In the best-case scenario, only main sets of the datum surfaces of a gear and a mating pinion are used to specify all the geometrical dimensions of a gear, of a pinion, and of the gear pair.
Figure 3: Bevel gear nomenclature in the mean section of Figure 1.
Next, ANSI/AGMA/ISO standards ([1] in particular) refers to the so-called "mean section" as illustrated in Figure 3. Bevel and hypoid gearings only of poor quality can be analyzed in the mean section. Moreover, many of the design parameters — such as the (a) addendum, (b) dedendum, (c) circular pitch, (d) circular thickness, (e) clearance, (f) whole depth, (g) backlash, and (h) working depth — are considered as linear dimensions [1]. All of these design parameters are angular values in nature [5]. The common vertex of all of these angles coincides with the base cone apex of the gear (of the mating pinion) [5]. The angular design parameters (a), (b), (e), (f), and (h) are specified in a section of a gear or a pinion by a plane through the centerline. The angular design parameters (c) and (d) are specified in the pitch plane, PP, of a gear pair. Finally, the angular design parameter (g) — that is, the backlash — is specified within the pitch plane, PP, of a gear pair.
Other design parameters of a bevel/hypoid gear, such as (i) chordal addendum and (ii) chordal thickness, also need to be construed as the corresponding "angular" design parameters having the gear/pinion vertex as the common vertex [5]. It is wrong practice to try to express the design parameters of a bevel/hypoid gear in terms of "pitch circle" and "equivalent radius." All correctly engineered bevel and hypoid gearings need being considered only in 3D space, and not in equivalent plane sections as in [5].
Figure 4: Hypoid nomenclature as recommended by ANSI/AGMA 2005-D03 standards [1].
Finally, not the "pitch point" but the "pitch line" (or the "axis of instant rotation, Pln" — preferred), instead has to be considered in all Ia−gearings, as well as in all Ca−gearings [5]. In Ca−gearings (Figure 4), the design parameters of a gear, of a mating pinion, and of a gear pair fall in three groups.
The design parameters of a gear pair that directly affect the conditions of meshing of the interacting tooth flanks of a gear and of a pinion. They are as follows: the shaft angle, H; the pinion offset, M; the mounting distance, N; and the pitch angle, P [5]. The actual values of the tolerances for all of these design parameters of a gear pair must be very tight. All of them have to be calculated (and not just set) in terms of permissible variation in shape, size, and configuration of the desirable contact pattern. It should be stressed here that the pitch cone angle, P, can be expressed in terms of shaft angle, H ; pinion offset, M; and gear ratio of the gear pair.
The design parameters of a gear pair that directly do not affect the conditions of meshing of the interacting tooth flanks of a gear and of a pinion. They are as follows: the face apex beyond crossing point, A; the root apex beyond crossing point, B; the crown to crossing point, D; the front crown to crossing point, E; the outside diameter, F; the pitch diameter, G; the root angle, J; the face angle of blank, K; the face width, L; and the outer cone distance, R. The tolerances for all of these design parameters of a gear pair are not as tight as for the first group of design parameters of a gear pair.
The incorrect design parameters of a gear pair. This is the "pitch apex beyond crossing point, C." In correctly engineered Ca−gearings this distance must be of a zero value [5].
The set of the design parameters of a Ca gear pair shown in Figure 4 also can be "cleaned up" similar to that in Figure 1 and Figure 2. No numerical values for geometrical tolerances are recommended by ANSI/AGMA/ISO standards for the design parameters of a gear, a pinion, and the entire gear pair; those directly affect conditions of meshing of the gear and the pinion. The discussion on geometrical dimensioning and tolerancing of bevel and hypoid gearings is briefly summarized here:
The geometrical dimensioning of a bevel gear pair shown in Figure 1 is inconsistent as the principle of common datum surfaces is violated; that is, too many datum surfaces are used in Figure 1.
The geometrical dimensioning of that same gear pair proposed in Figure 2 strictly follows the principle of common datum surfaces — the bore and the common reference surface in a gear (as well as in a pinion) are used for the purposes of geometrical dimensioning of the gear pair.
The geometrical dimension labeled as M shown in Figure 1 is not a mounting distance at all.
It is of critical importance to stress here that the base pitch, which is a design parameter No. 1 in gearings of all types, is missed in ANSI/AGMA/ISO standards for bevel and hypoid gearing. Neither base pitch of a bevel/hypoid gear, ϕ  b.g, nor base pitch of its mating pinion, ϕ b.p, nor the operating base pitch, ϕb.op, of a gear pair are specified by ANSI/AGMA/ISO standards. Equality of the angular base pitches ϕb.g = ϕb.op and ϕb.p = ϕb.op is vital for: (a) the reduction of noise excitation; (b) the reduction of vibration generation; (c) an increase of power density, and so forth [7], [8], [9], [10], [11], [12], [13]. This considerable mistake in ANSI/AGMA/ISO standards for bevel and hypoid gearing needs to be fixed (the sooner, the better).
A more detailed discussion on geometrical dimensioning and tolerancing of bevel and hypoid gearings is desirable, aiming at the elimination of all possible inconsistencies. Correct dimensioning and tolerancing is a "must" in the design and production of high quality bevel and hypoid gears.
Conclusion: In intersected-axes, as well as in crossed-axes gearings, drawings for a gear, for a mating pinion, and for a gear pair must be properly dimensioned. The principle of common reference surfaces is a must to follow when dimensioning the components of a gear pair. Out-of-date terms and corresponding dimensions must be eliminated from the drawings.
Contact pattern
Bevel and hypoid gears have to be assembled in a specific way to ensure smooth running and a favorable load distribution between gears. To attain this goal, a contact pattern between the interacting tooth flanks of a gear and a mating pinion is commonly used.
The contact pattern is a critical attribute of any and all bevel/hypoid gear design (Figure 5). Simply stated, the contact pattern is the area in which the gear teeth come in contact as they engage and disengage during their rotation. When a gear is installed in a gearbox and is powering the designated application, there are varying degrees of pressure, or load, on the gear teeth. These pressures are influenced by box deflections, bearing movement and temperature changes. When the gear teeth are subjected to these variables, the contact pattern will change. There is a general rule of thumb stating that the heavier the load, the larger the contact pattern and vice versa. For a gear to perform properly under operating load, the contact pattern must be of a certain shape and at a certain location. Typically, an ideal tooth contact pattern under load should encompass the bulk of the tooth surface while avoiding any contact with the edges of the tooth flank. So far, the contact pattern is more a "qualitative" than a "quantitative" indicator of gear pair quality.
Figure 5: An example of acceptable shape and configuration of contact pattern under a low load.
The permissible variation in contact pattern location, orientation, and shape, can be used to calculate the tolerances for design parameters of a gear pair5. Unfortunately, in contemporary gear practice, contact pattern is a qualitative, and not quantitative, measure of the gear pair quality.
The discussion on contact pattern in bevel and hypoid gearings is briefly summarized as follows:
The contact pattern cannot be measured similar to that (and with a corresponding accuracy) as other design parameters of a gear are measured, for example, as a bore diameter, a face width, a face angle, and so forth.
The measurements of the contact pattern are not reliable.
The actual misalignment in bevel/hypoid gearing cannot be expressed in terms of the actual geometry and configuration of the contact pattern.
Efforts of the gear experts must be focused toward searching possible ways to express the bevel/hypoid gears misalignment in terms of geometry, size, and configuration of the contact pattern.
Instead of the contact pattern analysis, the teeth flank geometry along with the actual value of the mounting distance should be measured. No contact pattern analysis is necessary if a bevel/hypoid gear is machined and assembled according to the properly designed blueprint. A more detailed discussion of the contact pattern in bevel and hypoid gearings is desirable.
Conclusion: This is an out-of-date practice to use contact pattern as a tool to improve the accuracy of gears for intersected-axes, and crossed-axes gear pairs. Instead, the teeth flanks geometry, and the mounting distance have to be properly specified and inspected. These can be done on the basis of a broader application of the results the theory of gearing returns. Use of the lapping process, pairing of bevel and hypoid gears, nowadays practice for the calculation of mounting distance, and tolerance for the mounting distance, reveal the lack of knowledge in the scientific theory of gearing.
Mounting distance
Mounting distance is a vital design parameter for intersected-axes gearings (that is, for bevel gearings), as well as for crossed-axes gearings (that is, hypoid, spiroid, double-enveloping worm gearings, and so forth). The specification, inspection, and tolerancing of the mounting distance is challenging to understand by practical gear engineers as this issue is insufficiently outlined in ANSI/AGMA/ISO standards. Numerous publications on the topic [14], [15], [16], [17], and many others reveal this. At the beginning, let's clarify what the term "mounting distance" stands for.
First, and the most critical, by means of mounting distances the location of tooth flanks in axial direction of a gear and a mating pinion are specified in relation to the centerlines in the gear housing. Apex point of a tooth flank of both, of the gear, A fg, and the pinion, Afp, must coincide either with the point of intersection of the centerlines in the gear housing (for Ia−gearings), or with the "pitch plane"/"plane of action" apex (for Ca−gearings) [5]. The pitch plane apex is commonly designated as App, and the plane of action apex is commonly designated as Apa. These two conditions can be expressed as follows: Afg ≡ App ≡ Apa and Afp ≡ App ≡ Apa
Second, the pitch cone apex of a gear, Ag, (and of a mating pinion, Ap) must coincide with the apex point of a tooth flank of both, of the gear, Afg, and the pinion, Afp. These two conditions can be expressed as follows: A g ≡ A fg and Ap ≡ A fp
Third, the base cone apex of a gear, Abg, (and of a mating pinion, A bp) must coincide with the apex point of a tooth flank of both, of the gear, Afg, and the pinion, Afp. These two conditions can be expressed as follows: Abg ≡ A fg and Abp ≡ A fp.
Fourth, there are two outer cones. One of them is for the gear and another one is for the mating pinion. There are also two root cones. Again, one of them is for the gear and another one is for the mating pinion. Neither outer cones nor root cones directly affect the actual value of the mounting distance. However, these cones need to be mentioned here as in current practice outer cones are commonly used when determining the mounting distance.
In a precision gear pair, it is recommended to inspect the mounting distance at nominal operating load and the preloaded bearings.
The plurality of the apexes is confusing and results in misunderstanding of the terms "mounting distance" in acting ANSI/AGMA/ISO standards. To make things clear, it is necessary to outline to the best possible extent what the term "mounting distance" stands for. As an example, consider tooth flank of a straight bevel gear6 as illustrated in Figure 6. The tooth flank of the gear, G, can be construed as a family of straight lines through each point of the gear tooth profile and the gear tooth flank apex, Afg (the gear tooth flank apex, Afg, is an equivalent to the gear base cone apex, A bg). Only the gear tooth flank apex, Afg, should be used for the specification and inspection of the mounting distance, M. Commonly, the outer cone apex of the gear, Aog.1, is inward in relation to the gear tooth flank apex, Afg, as shown for the straight generating line 1 in Figure 6. However, this is not a must as the gear outer cone apex, Aog.2, can be located either outward, or the gear outer cone apex, Aog.3, can be located inward in relation to the apex Aog.1, as it is illustrated in Figure 6 for the straight generating lines 2 and 3 of the outer cone of the gear. The actual location of the gear outer cone apex (either Aog.1, or Aog.2, or Aog.3) does not affect the conditions of meshing of the gear, G, and the pinion, P, tooth flanks. The conditions of meshing of the gear, G, and the pinion, P, tooth flanks depend only of the actual location of the gear/pinion tooth flanks apex, Afg. Therefore, the tolerance for the mounting distance (the mounting distance is measured in relation to the gear tooth flank apex, Afg) is tight, while the configuration of the apex of the outer cone of the gear, Aog, is a free dimension with no specified tolerance.
Figure 6: On the definition of the "tooth flank apex," A fg, in intersected-axes and crossed-axes gearings.
Depending on the accuracy of the set up parameters when cutting straight bevel gears, the axial position of the tooth flank, G, can be changed. After being assembled, the gear tooth flank apex, A fg, must be coincident with the centerlines in the gearbox housing. Therefore, the mounting distance of a gear is the distance from the gear tooth flank apex, A fg, to the common reference surface of the gear. A similar definition is valid with respect to the mounting distance of a pinion. In reality, as it is recommended by ANSI/AGMA/ISO standards, the mounting distance is specified differently from the preceding.
As it is shown in Figure 2, two dimensions — that is, the crown to back, F, and the pitch cone apex to crown, R — are used to specify the mounting distance, M. The crown is used to specify both the dimensions. It is right to point out here that a crown is not a reliable datum for the inspection of the mounting distance. Taking into account that tolerance for the mounting distance is very tight, it is nonsense to use the crown for precision measurements. This is the first issue that makes the crown inappropriate datum for such an inspection.
Then, the crown is not geometrically associated with the gear tooth flank, G. An analysis of Figure 7 reveals that, depending on the accuracy of the set up parameters when machining straight bevel gears, the axial position of the tooth flank, G, and the gear tooth flank apex, Afg, can be variable.
Figure 7: "Crown" in intersected-axes and crossed-axes gearings. Note on rough surface of the outer cone of the gear; this rough surface is used to specify the crown, E; that is, it is used to specify the crown to back, F, and ultimately the mounting distance, M.
A bevel/hypoid gear tooth flank must be correctly specified in relation to the common reference surface. For this purpose an arbitrary point, m, either within the tooth flank or within extension of this surface can be used. The tooth flank apex, A fg (Figure 6), is convenient to be used for this purpose. It is incorrect practice to use the wedge, E, and the dimension, F (Figure 7), to specify the mounting distance in bevel/hypoid gearing as shown in Figure 1.
With that said, it is the right point to proceed with a discussion of a nowadays practice to specify and inspect the mounting distance in intersected-axes, and in crossed-axes gearing. The current practice is outlined in [15] and is illustrated in Figure 8. The procedure for assembling the bevel gears in this gearbox by the measurement method is as follows [15]:
Figure 8: Measurements recommended in [15] for mounting both overhung and straddle-mounted bevel gears in a typical gearbox.
On the housing, measure the distance from locating surface to bore centerline in both horizontal and vertical directions (HMD and VMD).
Record the gear and pinion mounting distances (MDG and MDP);
Measure the gear and pinion thicknesses (WG and WP).
Assemble the gears into their subassemblies.
Measure the length that controls gear position in each subassembly (MAG and MAP).
Calculate the distance from shim mounting surface to crossing point for each subassembly (MDV and MDH): MDV = MD G − MG + MAG and MDH = MDP − MP + MAP correspondingly (Figure 8) [15].
Calculate the required shim thicknesses and assemble the gearbox with shims in place.
Items No. 1 through No. 5 are correct. In the item #6, when calculating the dimension MDV, the actual, MDG  actual, and not the nominal, MDG, value of the mounting distance must be entered into the equation for the calculating of MDV. Similarly, when calculating the dimension MDH, the actual, M DP  actual, and not the nominal,
M D  P, value of the mounting distance must be entered into the equation for the calculating of MDH.
Neither the dimension M DG, nor the dimension M D  P can be measured as the gear tooth flank apex, Afg, (as well as the pinion tooth flank apex, Ap) does not physically exist. The pitch cone apexes Ag, Ap , and base cone apexes Abg, Abp, also do not exist physically. Therefore, the use of the gear tooth flank, G, (and the pinion tooth flank, P) is the only possibility to measure the dimensions M DG  actual and M DP  actual. For this purpose, a method for inspection of the mounting distance in bevel and hypoid gearing is proposed by the author7. The proposed method of inspection is based on use of a ball of a pre-specified diameter in a space between two neighboring teeth of a gear to be inspected. A prescribed point of contact, m, (see Figure 3) is located reasonably close to the mid of the face-width gear, and to the line of intersection of the gear tooth flank by the pitch cone. It is assumed that the rest of the gear tooth flank deviations either are zero, or are known and can be incorporated in the procedure of the calculations.
For a specified point m within a gear tooth flank the dimension M *actual is measured. The measured distance M *actual is compared with its nominal value, M *. In this way a decision can be made on whether or not the actual dimension M *actual is within the tolerance.
Item No. 7 is useless. No shimming is necessary if the gears are machined to properly calculated tolerances. It is no longer required to machine gears and pinions in sets, and gears and pinions can be assembled with no regards of the sets, that is, no gear pairing is required if the gears are machined to the correctly calculated tolerances. Therefore, if engineered properly, it is possible to manufacture all gears to the nominal mounting distance specified on the drawing with no additional cost. Under such a scenario, no pairing in bevel/hypoid gearing is required, and the gears can be engaged in a correct mesh with any bevel/hypoid pinion if both of them are correctly engineered and manufactured. Moreover, if one gear in a set fails, the entire set should not be replaced, but only the failed gear is required to be replaced.
Because of dimensional variations between parts, each gear will have a unique value for the mounting distance [16]. For the mounting distance, it is common to set a tolerance of ± 0.05 mm up to ± 0.1 mm [16]. For correctly engineered bevel and hypoid gears, the tolerance for mounting distance must not be set but, instead, it must be calculated and must be expressed in terms of the permissible variation in contact pattern location, orientation, and shape. No methods to calculate the tolerances for the mounting distance are available in the public domain. No methods to verify whether or not the actual errors for the mounting distance are within the corresponding tolerance are available in the public domain.
The discussion on mounting distance in Ia− and Ca−gearings in bevel and hypoid gearings is briefly summarized as follows:
In the current practice of bevel/hypoid gear production and application, there are no means to ensure whether or not the actual value of the mounting distance is within a specified tolerance for this dimension.
An actual geometry and configuration of the contact pattern is an evidence that the mounting distance is of a reasonable value, but no one can guarantee that the actual value of the mounting distance is not out the specified tolerance.
An incorrect mounting distance is not the only reason for a shift of the contact pattern. Even if the mounting distance is within the tolerance, an unfavorable contact pattern can be observed because of: (a) the deviations of the actual tooth flank geometry from it desirable geometry; (b) the gears are designed and cut as approximate gears (even ground bevel and hypoid gears are not perfect, that is, they are not geometrically accurate), and; (c) distortions after heat treatment (especially for a gear).
Direct measurements of the mounting distance8 are necessary. This can be done, for example, by means of laser scanning of the machined tooth flank, and creating on premise of that a CAD model of the actual tooth flanks. Comparison of two CAD models, that is, of the desirable and of the actual tooth flanks returns an exact number of the mounting distance in a machined bevel/hypoid gear. Simpler methods and means for the direct inspection of the actual mounting distance in bevel/hypoid gearings can be proposed.
No reliable methods for the calculation of the tolerances for the mounting distance in bevel/hypoid gearings are known. This particular problem needs to be addressed. A more detailed discussion on mounting distance in Ia− and Ca−gearings in bevel and hypoid gearings follows:
Conclusion: Reliable methods to inspect the mounting distance can be developed on the premise of the results derived from the theory of gearing. A correct alignment (snapping of the base/pitch cone apexes in cases of Ia−gearings, and correct configuration of the base/pitch cone apexes in cases of Ca−gearings) depends on the mounting distance of both; that is, of a gear and its mating pinion. Therefore, shimming in/out of the gear/pinion is an obsolete practice. Tolerances for the mounting distance neither of a gear, nor of its mating pinion cannot be properly calculated/inspected in the contemporary production of gears.
Bevel and hypoid gears are designed and manufactured to provide a specific amount of backlash. That is, the space between mating gear teeth or the difference in width of the gear tooth and pinion tooth of the mating gear to let the gears mesh without binding and to provide space for a film of lubricating oil between the teeth. This prevents overheating and tooth damage. The backlash is necessary for proper operation of the gear pair.
To optimize the performance of any two bevel gears, the gears must be positioned together so that they run smoothly without binding and/or excessive backlash. In the current practice of gear production, unless otherwise specified, the minimum amount of total backlash of a pair of bevel/hypoid gears is measured at the tightest point of mesh with a dial indicator on a bevel gear testing machine. Unless otherwise specified, backlash is assumed to be normal backlash9 and cannot be measured in the plane of rotation. Backlash is necessary to achieve correct operation of the gears and varies with the size of the tooth and operating conditions. Bevel gears are cut to have a definite amount of backlash when correctly assembled together. But excessive backlash or play, if great enough, can cause a sudden impulse or shock load in starting or reversing that may cause serious tooth damage. Excessive or insufficient backlash can also result in noise, excessive wear, and damage.
Numerous inconsistencies are observed in the definition and interpretation of backlash in bevel and hypoid gearings. To avoid the above discussed inconsistencies in the definition of backlash in bevel and hypoid gearings, the backlash in bevel/hypoid gearing can be defined in the following manner.
Consider a phantom crown gear that is engaged in correct mesh with the gear. This crown gear can be referred to as a "crown gear/gear," or simply as C Gg. The outer diameter of the crown gear is labeled as r  o.pp, the inner diameter is labeled as r  l.pp, and the pitch diameter is labeled as r pp. Face width, Fpp, of the crown gear is equal to Fpp = r  o.pp − r  l.pp. The central angle Ψ pp spans over the active portion of the crown gear, CGg. The axis of rotation of the crown gear, CGg, is labeled as Opp. Here, the subscript "pp" indicates that the parameters relate to the pitch plane, PP.
Figure 9: On definition of the: (a) "angular tooth thickness, ϕ t," (b) "angular space width, ϕ w," and (c) "angular backlash, ϕ B," in intersected-axes gearing by means of C G g-to- C G p mesh. [Note: The interaction of the tooth flank of the gear, G, (not shown) and the tooth flank of the pinion, P, (not shown) occurs within the plane of action, PA, and not within the pitch plane, PP]. A similar schematic is valid for crossed-axes gearing as well.
The angular tooth thickness, ϕ  t.g, and the angular space width, ϕ  w.g, in a gear is measured within the pitch plane, PP, of the crown gear/gear, CG g, as shown in Figure 9 (a similar schematic is valid for crossed-axes gearing, as well). The angular pitch of the gear teeth in Figure 9 is labeled as ϕ  x.g.
Similarly, consider a phantom crown gear that is engaged in correct mesh with the pinion. This crown gear can be referred to as a "crown gear/pinion," or simply as CG p. The angular tooth thickness, ϕ  t.p, and the angular space width, ϕ  w.p, of a gear is measured within the pitch plane, PP, of the "crown gear/pinion, CGp" (not shown in Figure 9). The angular pitch of the pinion teeth is labeled as ϕ  x.p(not shown in Figure 9).
The angular pitches of the gear, ϕ  x.g, and the pinion, ϕ  x.p, are equal; that is, the equality ϕ  x.g = ϕ  x.p = ϕ  x. Therefore, the further designations for these angular pitches are replaced with ϕ  x.
When the crown gear, CGg, and the crown gear, CGp, are engaged in mesh, they are free to turn about the O pp−axis in relation to one another through a certain angle, ϕ B. The angle, ϕ B, is referred to as the "angular backlash." The "angular backlash, ϕ B," can be calculated as:
ϕ B = ϕ  w.g − ϕ  t.p Equation 1
or as:
ϕ B = ϕ  w.p − ϕ  t.g Equation 2
Novel instrumentation can be developed for the direct measurement of the design parameters in a gear (ϕ  t.g,ϕ  w.g, and ϕ  x.g) and in a pinion (ϕ  t.p,ϕ  w.p, and ϕ  x.p). Then either Equation 1 or Equation 2 can be used for the calculation of the angular backlash, ϕ B.
In a bevel/hypoid gear pair the backlash is measured at a configuration of a gear and a pinion when "two pairs of teeth are engaged in mesh."
The discussion on backlash in I a− and C a−gearings in bevel and hypoid gearings is briefly summarized below:
The existing practice to set and to inspect backlash in a bevel/hypoid gear pair is inconsistent.
The angular backlash is a reliable design parameter of a bevel/hypoid gear pair.
The angular backlash is measured within the plane of action in a gear pair (and not perpendicular to the gear teeth as it is recommended by ANSI/AGMA/ISO standards). It makes sense to specify the angular backlash as an angle within the pitch plane at a corresponding configuration of the gear and the pinion in relation to one another, and not as an angle through which the gear (the pinion) turns about its axis as values of these two angles are different: the angle for the gear is smaller compared to that for the pinion (gear ratio).
If the backlash does not fall within the recommended limits, no corrections to the mounting distance are allowed to adjust the backlash. If possible, the tooth thickness can be corrected (reduced) by additional machining. For strength calculations, the normal backlash can be expressed in terms of the backlash in the plane of rotation.
There is a trade-off when setting an actual value of backlash: The backlash must be large enough for operating of the gear pair, and it must be small enough when reversing the rotation. With the discussed approach, the contact ratio in bevel and hypoid gearing can be accurately calculated (spiral bevel, and others).
More details on the kinematics and the geometry of intersected-axis, and in crossed-axis gearing can be found in numerous recently published papers [7], [8], [9], [10], [11], [12], [13], and others.
Conclusion: Backlash in intersected-axes, and in crossed-axes gearing is an "angular" parameter, and not a "linear" parameter. Backlash is measured within the pitch plane of the gear pair. Appropriate methods of and means for inspection of the angular backlash can be developed on the premise of the developed theory of gearing [5].
In a brief overview on the acting ANSI/AGMA/ISO standards for bevel and hypoid gearings, it is shown that the geometrical dimensioning in ANSI/AGMA/ISO standards differs from the best practice of part dimensioning and in most cases can be significantly improved. Violation of the principle of common datum surfaces is the root cause for that. An alternative geometrical dimensioning for a bevel gear pair is discussed. Base pitches of a gear, of a mating pinion, and the operating base pitches of a gear pair must be incorporated into the set of the design parameters for bevel and hypoid gearings.
Use of the contact pattern for the purpose of evaluation of bevel/hypoid gear performance is briefly discussed. It is illustrated that (a) the measurements of the contact pattern are not reliable and (b) the actual misalignment in bevel/hypoid gearing cannot be expressed in terms of the actual geometry and configuration of the contact pattern. Therefore, the efforts of gear experts must be focused toward searching possible ways to express the bevel/hypoid gears misalignment in terms of geometry, size, and configuration of the contact pattern.
It is shown that in current practice of bevel/hypoid gear production and application, there are no reliable means to ensure whether the actual value of the mounting distance is within a specified tolerance for this dimension. The commonly used design parameter referred to as the "mounting distance" is not the mounting distance at all. A method for the inspection of mounting distance in intersected-axes, and in crossed-axes gearings is necessary to be developed. Once the actual value of the mounting distance is known, and the gears are cut to the correctly calculated tolerances, then: (a) the gears no longer need to be produced in sets; (b) there is no necessity to replace the entire gear pair when one of the components of a gear pair is brakes; only the broken component can be replaced instead if the gears are correctly designed and properly manufactured; (c) no pairing is necessary, and (d) potentially, lapping process in manufacturing of precision bevel and hypoid gearings can be eliminated at all.
No reliable methods for the calculation of the tolerances for the mounting distance in bevel/hypoid gearings are known (in the public domain). This particular problem needs to be addressed.
It is demonstrated that the existing practice to set and to inspect backlash in a bevel/hypoid gear pair is inconsistent. It is proposed to use the "angular backlash" when designing bevel/hypoid gear pairs.
Ultimately, the discussed examples of inconsistencies in the acting ANSI/AGMA/ISO standards for bevel and hypoid gearings show that the latest accomplishments in the scientific theory of gearing need to be taken into account when revising the acting ANSI/AGMA/ISO standards for bevel and hypoid gearings.
C a−gearings also include "worm gearings." However, worm gearings could be a subject of a separate article.
Per the author's observation, the current gear industry, both, the gear practitioners, as well as the gear researchers, do not value properly the accomplishments attained in the theory of gearing. The ignorance of the output from the theory of gearing is one of the root causes of insufficient gear quality, problems with the gear inspection, too-high costs of produced precision gearings, and so forth. No one has a chance to succeed with bevel, hypoid, and worm gearing having no correct knowledge of the gear kinematics and the gear geometry. Knowledge of the theory of gearing is a must for all gear experts involved in precision gear design and manufacture.
The similar recommendation are provided in Figure 2.7 on page 22, and in Figure 2.8 on page 23 in the recently published book by J. Klingelnberg [6].
It is worthy to stress here that the fewer the overall number of the datum surfaces, the higher the accuracy of the part machining can be attained, and vice versa.
In much, the contact pattern is a subjective (and not objective) parameter. Neither the dimensions and orientation, nor the tolerances for the dimensions and orientation of the contact pattern can be assigned (and be directly measured on the shop floor). The contact pattern is an insufficiently engineered parameter of quality of a gear pair. The contact pattern is not measurable; that is, it cannot be reliably measured by means that are commonly available on the shop floor. It is desired to substitute the contact pattern with another reliably measurable design parameter of a gear pair. The mounting distance is a promising candidate for that.
This concept can be easily extended to bevel gears of any and all other types [5].
A method for inspection of the mounting distance in bevel and hypoid gearing is a subject of a separate article.
Important: In addition to the mounting distance, in C a−gearings, one more design parameter must be inspected. This is an angle that a gear/pinion axis of rotation forms with the centerline, ℄. A tolerance for this angle needs to be specified, and the actual deviation of the angle from required value of it needs to be inspected. An appropriate tolerance for the center distance.
A straight line along which the so-called "normal backlash" is measured cannot be perpendicular to both, to the gear tooth flank, G, and the pinion tooth flank, P, at the same time.
ANSI/AGMA 2005-D03. Design Manual for Bevel Gears, Approved November 2001, 36 pages.
ANSI/AGMA ISO 23509-A08. Bevel and Hypoid Gear Geometry, Approved May 20, 2008, 145 pages.
ANSI/AGMA 2008-C01. Assembling Bevel Gears, Approved November 2001, 36 pages.
ISO 23509: 2016, Bevel and Hypoid Gear Geometry, 140 pages.
Radzevich, S.P., Theory of Gearing: Kinematics, Geometry, and Synthesis, CRC Press, Boca Raton, Florida, 2012, 743 pages.
Bevel Gear: Fundamentals and Applications, by Klingelnberg, J., (Editor), 1st ed., Springer Vieweg, 2016 edition (December 24, 2015), 325 pages.
Radzevich, S.P., et al, "Preliminary Results of Testing of Low-Tooth-Count Bevel Gears of a Novel Design. Part 1," Gear Solutions, October 2014, pp. 25-26.
Radzevich, S.P., et al, "Preliminary Results of Testing of Low-Tooth-Count Bevel Gears of a Novel Design. Part 2," Gear Solutions, December 2014, pp. 20-21.
Radzevich, S.P., et al, "Preliminary Results of Testing of Low-Tooth-Count Bevel Gears of a Novel Design. Part 3," Gear Solutions, January 2015, pp. 20-23.
[Radzevich, S.P., "Precision Bevel Gears with Low Tooth Count," Gear Solutions, September, 2015, pp. 33-41.
Radzevich, S.P., Irigireddy, V.V., Precision Bevel Gears with Low Tooth Count, AGMA Technical Paper 14FTM18, American Gear Manufacturers Association, 2014, 12 pages.
Radzevich, S.P., "Principal Design Parameters of Gearing with Non-Parallel Axes of Rotations," Gear Solutions, August, 2014, pp. 65-73.
Radzevich, S.P., V.V., Precision Bevel Gears with Low Tooth Count, Gear Solutions, September, 2014, pp. 33-41.
Arvin, J.L., Mifflin, T.C., (with contribution from Cervinka, J.J.), "Spiral Bevel Gear Development: Eliminating Trial and Error with Computer Technology," Gear Technology, January/February, 2003, pp. 34-39.
Wasilewski, R.F., "How to Install Bevel Gears for Peak Performance," Power Transmission Design, March 1994, pp. 51-53.
Marsh, S., "How to Design and Install Bevel Gears for Optimum Performance: Lessons Learned," Gear Technology, June/July 2013, pp. 60-69.
"Bevel Gear Mounting – Ask the Expert," Gear Technology, www.geartechnology.com/questions/bevel_gear_mounting.php, 8/13/2015.
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, MS holds a MS in Mechanical Engineering and an MBA, and is currently director of global R&D, mechanical engineering, with Apex Tool Group, LLC.
can be reached at 586-292-7209 or radzevich@usa.com.
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This is my good friend, Lucy, who as you can see, dressed up as me for her school Book Week parade. Did you dress up too? Would you like to have your photo on the Alice-Miranda blog site? if you would, please email it to jacqueline@jacquelineharvey.com.au and I'm sure that she will post it here too.
I hope you had a wonderful Book Week!
I really wish I could meet you Alice-Miranda. So I need some help with a costume idea for Alice-Miranda for Book Week it is coming up, and I have no idea what book in the Alice-Miranda series I should dress up as. I have the whole series by the way and they are AMAZING books!
I sometimes feel like Alice-Miranda is real, too! It's as if this tiny gorgeous girl stands over my shoulder and tells me what to write. Alice-Miranda is a mixture of the best attributes of so many gorgeous children I've known over my years of teaching and writing, so in some ways I suppose she is real. Perhaps you have met someone just like her?
When it comes to Book Week dress ups, why not look at some of the things that you have at home that you might be able to adapt to fit with a Alice-Miranda book? The key is to use your imagination- but please send in a photo as an entry to the August Newsletter competition. I would love to see what you can create!
Hi I'm Sarah l really love ALICE Miranda and want to go as her for book week but don't have a costume. What do I do?
Well – I'd look at all the covers and choose one that you might have an outfit similar to. Then once you're dressed up take some photos and make sure that you have the newsletter and you can email them through on the competition. Have fun – I look forward to your pictures!


PROGRAMME FOR # RAM19 IN PROGRESS!
What can you expect during the Rotterdam Architecture Month?
Discover it here! We will give you a small taste: spend the night at great height during the Dakendagen. Take a spectacular look behind the scenes in the Schiecentrale or the Markthal. Or get carried away during in-depth debates in POST – the month promises to be interesting.
We will add more special events to the programme in the coming period.


I cannot say this is the right way to deal with the plugs, but this is what I do.
Sometimes the plugs fall out, sometimes they can be pried out, but otherwise they must be drilled out. Use a smaller size drill than the plug and carefully remove the remainder to leave a hole the proper size for the replacement.
Most plugs are tapered, so the small end goes in first. I make a mark across the top of the plug parallel to the grain, so the plug grain can be set parallel to the grain of the wood. Push the plug in, and tap it with a hammer to get it seated well. For plugs in the interior, you may not need any glue, but exterior ones usually do, particularly if the hole is shallow. I use two-part epoxy glue which comes in ½ pint cans.
When the glue dries (if any) trim the plug flush with the surrounding wood. I usually use a sharp chisel and hammer. Make the first cut of the plug at least 1/16" above the surface of the wood, cutting with the grain. Then you can see which way the grain runs, that is, which way to trim further so as not to chisel too deep. When it is flush, finish off with sandpaper. Some advise using a block plane. Some may use a sander.
There may be other or better advice from our group.
I "glue" exterior and interior plugs with varnish, the same kind I'm using on the woodwork. They're easier to remove next time, and no more likely to fall out since it's almost always due to wet/dry cycles. Obviously this wouldn't work on untreated teak decks, etc.
Varnish is a good idea, but I never touch the stuff.
I put it in the same class as mowing glass and washing cars.
I remove them with a sharp small steel dentists tool without damageing any surrounding wood. Then cut my own from teak scrap, insert with sealant, wait a few days, then remove excess cutting with the grain using a very sharp chisel and cutting small amounts until almost level, finishing with sandpaper.
Just to add my two cents on installing plugs. Regardless of what is used to glue the plug I do my trimming with a sharp chisel used bevel side up while the glue is still wet. So if the plug shears off wrong I can remove it and start again.


much love, illy: sponsor love + giveaway with Yellow Heart Art.
meet leonora of Yellow Heart Art.
first off, i know this girl in REAL life and has become one of my best friends! she is beautiful, creative, sweet - and if you all follow her blog or twitter at all, she is freaking hilarious! and her shop is exploding with awesomeness - from the witty, hilarious prints to the gorgeous jewelry to her squishable artwork. talk about OBSESSION. and don't say i didn't warn you, people.
and today one of your incredibly luuuuucky Much Love, illy readers get the chance to win your very own naturally wooden necklace from the Yellow Heart Art shop! these are three of my top faves but be sure sure to check out the other gorgeous options HERE. i have one and i can tell you from personal experience, you WANT this!
Like the Yellow Heart Art Facebook page!
use coupon code MuchLove15 for 15% off of your entire order!
Giveaway is open to US Much Love, illy readers thru August 21st.
Winner will be announced on August 22nd.
the happy whale pillow... totally my favorite from her shop. second favorite, every single bow necklace. they ALL tie for second.
the second Leonora said she was selling on Fab.com, I signed up for an account :) I'm hooked.
I follow her too through GFC.
i like yellow heart art on facebook.
I love the Happy Whale Pillow! SO cute!!
I like Yellow Heart Art on FB!
Loooove the "Life Is Short, Jump on the Bed" print!
I liked Yellow Heart fb page!
I LOVE the sewing machine necklace!
like the page as Petunia Blooms!
I liked the Yellow Heart Art Facebook page!
My favorite item in the Yellow Heart Art shop is the diamond wood necklace. Love!
I (@mylatestexcuse) followed @muchloveilly and @yellowheartart on Twitter!
I tweeted about this giveaway using the suggested tweet text at around 12:50 PM CST.
The neon arrow necklace! Oh my gosh...i'm in love.
I follow her with GFC!
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I signed up for Fab.com.
I'm torn between the neon yellow holga camera necklace and the toy vintage camera necklace. They're both so cute! Thanks for introducing me to this great shop!
I just liked yellow heart art on facebook!
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I signed up at fab.com!
I love the whale pillow or necklaces... so cute.
I really like the flower bib wood necklace, but I also like the one with the sewing machine! Both are sooooo cute!
I love the camera wooden necklaces. Can't decide if I like just plain wood or neon! All so lovely!
liked yellow heart art on facebook!


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Data-driven Finance
Finance Leadership
FOAM inspiration
CFOAX Round tables
This is what organizations expect from Finance as a business partner
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Written by Hette Mollema, Vice President Benelux Workday
What do other teams in the business expect from Finance? If the finance team wants to be a full partner of the business, what should it bring to the meeting table? To add strategic value, other departments expect Finance to look more ahead and not just report on what has been. In other words, looking more through the windshield and less in the mirrors.
Of course, the arithmetical and accounting basis must still be in order. Finance remains responsible for the numbers. Modern (cloud) technology ensures that the entry of transactions and the pure arithmetical and control work can be automated – and much faster and more accurately. Good finance systems make relevant data available throughout the organization in a bite-sized format. Thanks to technological solutions, Finance could (and should) now have its hands largely free to deliver the right information to the business in a timely manner.
More than turnover and profit
And there is a great need for this. This year, the ongoing study on the transformation of Finance – 'Finance in the digital era' – conducted annually by the University of Amsterdam, Workday, Agium and Finance on a Mission, revealed, among other things, that the other teams expect Finance to add more value to strategic decisions in the here and now. Not so much the reporting and accountability after the fact (although that remains important too), but precisely the numerical substantiation and insights to take steps forward. A sales director said in the survey that he hoped and expected that Finance could provide the business with an "outside-in" perspective, similar to the report that analysts prepare on the performance of the organization. A marketing director indicated that it would also be good, for example, if Finance included relevant social developments in the analyses.
Solid basis for strategic plans
Finance as a business partner: what is needed for this? Managers and directors of other departments expect Finance to be able to lay a solid foundation for strategic plans. Where are the risks, where is the room, and if that room is not there, where do we make it anyway? Especially in uncertain times, the value of Finance to the strategy and success of an organization cannot be overstated. The CFO and his team can bring a broader perspective to the table and immediately provide directors with up-to-date and relevant numbers to properly weigh decisions and plans. This doesn't just apply to short-term decisions. The long-term perspective can also be well underpinned with Finance's insights.
The report 'Finance in the digital era' also provides concrete tools to better fulfill the role of business partner. The financial professionals surveyed indicated that they still consider themselves to be strongest in the 'traditional' tasks: reporting, compliance and risk management. Where can we do better? Finance itself feels that technology and data skills need to be further developed (53%), collaboration with others could be at a higher level (64%), its own contribution to the transformation of the organization could be stronger (63%), and leadership competencies are lagging behind (62%). The teams from the other disciplines also surveyed in the study also find Finance strong in the traditional tasks. They feel the areas for improvement are mainly in leadership skills (35%) and in the skills to collaborate and inspire other teams (18%). So, in addition to making sure Finance has the right technology solutions, building true partnership within the organization is also a challenge. After all, Finance wants to be seen as a full business partner.
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ESG reporting still in its infancy, developments in Self-Service BI promising
Digital transformation in Finance: your EPM tech refresh
Return on data assets: A new way for leaders to think about data and the balance sheet
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Unique Benefits
Why choose Blossoms Montessori School?
Nido & Toddler Program
Primary Program (3-6 yrs)
Prospective Family
Montessori Students
Benefits of Montessori
Montessori Philosophy
Approach of Education
Montessori Approach of Education
"Discipline must come through liberty...We do not consider an individual disciplined only when he has been rendered as artificially silent as a mute and as immovable as a paralytic. He is an individual annihilated, not disciplined."
— Maria Montessori
Dr. Maria Montessori was a leading thinker in education whose ideas were, in many ways, ahead of her time. She was a visionary and Italy's first female physician. Dr. Montessori was born in Chiaravalle, Italy in 1870, and became one of that country's first female physicians in 1886. Through her profound interest in child development and scientific observation of children from various backgrounds and cultures, she developed a unique method of education. She acutely studied and observed how children learn, and concluded that children teach themselves based on what they find in their environment. She gave up her medical practice and university professorship to found the first Montessori school, Casa dei Bambini, or Children's House, in the San Lorenzo neighborhood of Rome. In teaching those sixty children, she developed the philosophy, methods, and materials that has eventually became known as the Montessori approach.
Dr. Montessori wrote, "The most important period of life is not the age of university studies, but the first one, the period from birth to age six, for that is the time when man's intelligence itself is being formed." Recent scientific research has confirmed that children develop 50% of their mature intelligence from conception to age 6.
Dr. Montessori observed that children went through sensitive periods during which they showed special aptitude for certain kinds of developmental activity. These periods are especially pronounced in the development of movement, order, language, music, fascination with small objects, and bonding or attachment. Modern neuroscience has validated these discoveries, which calls them "Windows of Opportunity."
Montessori education develops the child in all of its holistic dimensions. The Montessori curriculum encourages self-discipline, self-knowledge, independence, academic skills, problem-solving ability, social development, and an enthusiasm for learning through a combination of a self-regulated and multi-sensory approach. One of the most essential, stimulating, and supportive elements in children's learning is the prepared environment. Working within a classroom, well-equipped with a wide range of carefully designed, hands-on materials, children are encouraged to explore, understand, and experience the joy of discovering the world around them.
In a typical Montessori classroom, the teacher or guide blends in with the children. The children independently choose their own activities, which are designed to teach daily living skills, from cooking to sensorial acuity, numeration and arithmetic, as well as writing skills and reading. The guide gives individual or group presentations of the material to those who need them.
Children become self-regulated through concentrating on stimulating self-chosen tasks that they can pursue individually or in groups; Montessori called this process "normalization." There is a progression of activities which require focused movement, balanced body coordination and high levels of concentration. Among these are "walking on the line" and "the silence game" where children are invited and encouraged to be physically still and focus on the objects in the classroom environment, taking these children to the highest level of discipline and self-control.
For more than 100 years, the scientific method of Montessori pedagogy has provided strong foundation to students. These Montessori alumni have shown great contribution towards education and have transformed the world through their imagination and creativity. A few among them are:
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Plugins these days make music kreation a breeze with all the kool tricks done in one click. But sometimes you do have the funds to purchase the easy way out. In this video we demonstrate how to kreate the common technique done in orchestral ensembles. If you're making a beat for commercial or film, string octave run ups is a pretty kool addition to give your music that polish finish.


Beginning on April 16, Starbucks Rewards members can earn an extra shot of espresso, among other perks, after spending as little as $13 in store. Customers earn two "stars" for every dollar spent, redeemable for beverages, food, or even packaged coffee. Accrued points will no longer expire if they're earned via purchase on a Starbucks Visa or prepaid card, according to the company.
Starbucks has teased changes to its rewards program since early last year. The platform, launched in 2009, is often regarded as the gold standard in the restaurant industry for its ability to turn online engagement into in-store sales. Starbucks Rewards currently has 16 million members as of the end of 2018, a 25 percent increase over the past two years. Roughly 40 percent of Starbucks' U.S. sales come from rewards members.
Domestic rival Dunkin' has also run into early troubles in rolling out its cold beverage lineup, it said last month. The company reported flat fourth quarter sales after it shelled out $65 million on new espresso equipment. Yet Starbucks Rewards could give the company an advantage in generating the sales spike it is looking for over its rival, with customers now more incentivized to earn points quickly. Starbucks has also recently announced plans to expand its U.S. delivery partnership with Uber Eats to one quarter of its U.S. stores by the summer to boost overall sales.


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By: Akshita
How Has Drupal Revamped The Media Experience?
The internet is arguably one of the most effective tools in media for communication and has helped improve a number of things such as timeliness factor, reaching a larger audience, building connection between politics, culture and economic life and the society, engagement with a larger community is also possible and much more.
With the advent of the Internet, there has been a surge in online activities. Thousands and thousands of websites are created on a daily basis. However not everything is greener on the other side, media websites are equally combating the regular problems of views, security, and management.
Why Are Websites Important for Media?
Increasing use of Smartphones: A fine majority of individuals use smartphones instead of a laptop/PC as their daily driver. The smartphone has become an irreplaceable invention with new users storming in every single day. The generic use of smartphones is quite understood a tale by all of us, news, websites, social media, and connectivity. Drupal, the CMS has been powering heavy, content-laden websites for long and it has transformed user experiences all across the globe. Media channels do need to provide a flawless experience to its visitors for better visitor retention in this jam-packed market.
Popularity Tracker: Through online views, media houses can assess their popularity and know what sort of news is popular among which demographics, which again helps them identify and deliver a personalized experience to their target audience. This was not the case with newspapers and TV channels.
User's feedback adding a new dimension to mass communication: Even though user feedback is no new feature but with online media it is instant and leads to identifying the issue. This helps promote and maintain healthy user-media house relationship.
How Suitable is Drupal For Media Platforms?
It is flexible and scalable
Drupal publishes a single website or shares content in multiple languages across many devices. Technology and business leaders transform content management into powerful digital solutions with Drupal backed by one of the world's most innovative open source communities.
All the news websites consist of many news articles, comments and discussions and related News. Which means the database is huge but needs no compromise on fluency and user experience. Also, it has top-tier customizability in terms of content management and visuals.
Quick Websites with Drupal Distributions
Distributions provide site features and functions for a specific type of site as a single download containing Drupal core, contributed modules, themes, and pre-defined configuration. They make it possible to quickly set up a complex, use-specific site in a fewer step than if installing and configuring elements individually.
Some of the related distributions are:
OpenPublish: OpenPublish is a Drupal 7 packaged distribution designed for the online news industry. It is deployed in a variety of media outlets sites including magazines, newspapers, journals, trade publications, broadcasts, wire services, multimedia sites and membership publications.
Lightning: The intent of Lightning is to enable developers to create a great authoring experience and empower editorial teams. We do this by providing a lightweight framework, documentation and best practice examples for building working solutions in Drupal.
Thunder: Thunder is a Drupal 8 distribution for professional publishers. It is in lines with the current version functionalities. It has (hand-picked) publisher-centric modules with custom enhancements and an environment which makes it easy to install, deploy and add new functionality.
Modules: Drupal has more than 10,000 actively maintained modules which can be downloaded for free from its website. They add features to the website and reduce effort in website development. Some of the useful modules for this sector are:
Quick Page Loading with AMP: The AMP module is designed to convert Drupal pages into pages that comply with the AMP standard. Initially, only node pages will be converted. Any other kinds of pages will be enabled late in time. All the news related 4 articles pages can be converted to AMP Page for quick loading on Smartphones and Tablets.
Manage related news with views: With views, media houses can entirely redesign their website as per reader persona preferences.
Reduced Cost of Website
Drupal is an Open Source Content Management System. It can be downloaded and customized very easily according to website demand.
Drupal website has many actively maintained distributions, which can be used to set up a website very quickly.
Now since most of the SME's face funding issues, creating a website with Drupal can save cost as most of the elements for building the website are available for free on Drupal.
Excellent design with Drupal Themes
It is very important for a website to have a nice and responsive design to showcase every possible content in a meaningful and appealing way.
Drupal has 20k+ themes available which can be customized accordingly.
It has around 2500 actively maintained themes available for free on its website, which can be easily downloaded and customized accordingly.
Media technology has made communication increasingly easier as time has passed. Today, as technology is available to more and more people, mediums of communication have increased and so has the effectiveness and reach of the new media.
But with the various benefit/s also comes the ill. But Drupal helps solve these various shortcomings and issues such as of security, designing and theme, page loading time, high cost, SEO, and various others.
Akshita
Akshita is a Senior Content & Marketing Associate at OpenSense Labs. A Hubspot certified Content Marketer, she likes to devour content related to SEO, open source technologies, and politics besides Drupal, of course. As a hobby, she trains young girls with TaeKwondo. She is also a big Game of Thrones fan and quotes Tyrion atleast 5 times a day.


With the rise in popularity of vintage trailers, the Terry Classic by Heartland has become one of the standout trailers in recent years. Their retro styling makes them makes them highly desirable and extremely visually appealing. They aren't all about outer appearance though, the Terry Classic may have a retro look, but it comes with completely modern technology. Featuring spacious interiors, lightweight construction, and environmentally friendly building materials you can get the vintage feel while enjoying all of the benefits of modern technology.


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Warner Bros. Entertainment Inc. Sexual Harassment Attorney in California
Warner Bros is a highly sought after company with many individuals working there for some time. There are also other workers like interns and guest producers who are present for a short time. No matter what kind of employee you are at Warner bros, you should be fairly treated and not subjected to sexual harassment. Unfortunately, the Hollywood industry is not particularly caring, and you could be targeted in the workplace. Whether an individual at Warner Bros. Entertainment Inc. harasses you and retaliates against you or you were sexually harassed by Warner Bros. Entertainment Inc. or someone working at Warner Bros. Entertainment Inc., you should be aware that there are legal options for you to take and the chance to earn necessary compensation. A lawyer who has experience in Warner Bros. Entertainment Inc. sexual harassment cases can assist you with your lawsuit if you contact the California Labor Law Employment Attorneys Group.
What laws prevent sexual harassment?
Sexual harassment in the workplace is prohibited by way of the Civil Rights Act of 1964 and the Fair Employment and Housing Act in California. These Acts include prohibition of sexual advances, visual or verbal conducts, physical actions, and more that create a hostile workplace or an intimidating atmosphere. The actions do not have to be based on sexual desire or on sex itself; they can include gender identity, gender expression, sexual orientation, perceived sex, pregnancy, childbirth, and more.
To get the most accurate information regarding sexual harassment, contact our Warner Bros. Entertainment Inc. sexual harassment lawyers in Los Angeles.
What are forms of sexual harassment?
Sexual harassment in the workplace can take on two forms. The first can be carried out by anyone, whether a coworker or customer. You may not even be a victim in some situations; it is enough that you witnessed some sexual assault or harassment occur, and you could have been severely affected by it. Perhaps you were a victim yourself at one point in time or you were unable to stop the incident and someone was seriously injured. You could sue Warner Bros. Entertainment Inc. for sexual harassment in either case. This hostile workplace environment sexual harassment can occur in various ways. If a supervisor or coworker at Warner Bros. Entertainment Inc. creates a hostile work environment, you should sue.
The second form of sexual harassment is quid pro quo harassment, which is Latin for "something for something" or "this for that."It can only take place between a manager, supervisor, boss, or other authority figure and a subordinate or underling. There must be some implicit or overt threat of negative consequence, or there must be a request for a favor or positive gift in exchange for sexual actions. Bosses who participate in proposing employment or promotions in exchange for sexual favors are guilty of quid pro quo harassment.
If a manager or supervisor at Warner Bros. Entertainment Inc. sexually harassed you, you could have been faced with negative consequences. Some of the consequences include bad performance reviews, demotion, denial of promotion, rejection of benefits and insurance coverage, retaliation, forced overtime with no compensation, illegal termination, docked wages and reduced salary, reassignment to another store or location, blacklisting in the company or field, and much more.
You could be sexually harassed in the following ways:
You were given sexually explicit objects as gifts or there were such objects on display in someone's cubicle or desk
You were a victim of inappropriate touching, such as when a coworker groped you, fondled you, held on too long during a hug, touched your butt, caressed you, massaged your neck, and much more
You were a victim of sexual molestation, whether as an adult or a minor
A coworker sent you inappropriate pictures of themselves masturbating, in suggestive poses or areas, or engaging in other acts, or simply sent you pornographic material with lewd statements
Someone at work tried to have sexual relations with you, whether by soliciting sex, repeatedly asking you on dates, trying to goad you into an affair, and more
You were a victim of rape or you were sexually assaulted, in which case, you should do more than file an employment claim – you should hire a Warner Bros. Entertainment Inc. sexual assault lawyer to assist you
Sexual harassment should never go unpunished. It is important that you find a lawyer who can help sue Warner Bros. Entertainment Inc. for sexual harassment. If there is no action taken against the perpetrators, they will continue to harass other people, and the company will protect them. A workplace sexual harassment lawyer can be of great assistance to you and your claim.
How to File a Sexual Harassment Lawsuit Against Warner Bros. Entertainment Inc.
To file a Warner Bros. Entertainment Inc. sexual harassment lawsuit, you will need to provide enough evidence showing that you were victimized. We recommend procuring and putting together evidence from the first instance of harassment. This is because many individuals routinely participate in it; these are seldom isolated incidents. If you have a long list of proof of repeated occurrences, your claim will have a higher chance of success. Of course, this comes at the risk of suffering through more harassment. You can speak with a Warner Bros. Entertainment Inc. harassment lawyer to learn the proper course of action.
You should do the following:
Read everything you can about the harassment policy at your company, including what the punishments are, what the training methods are, and more
Acquire statements and testimonies from any coworkers who saw the incident happen or who were similarly affected by the harassment
Take photos of the harassment, record videos or acquire security footage of the harassment, or get audio recordings of conversations about it
Keep a journal of the incidents and make sure to meticulously detail them, including the dates, times, involved parties, and more
Inform your boss and Human Resources representative about the harassment, and keep all emails and such so that you can show that they were aware; they may try to deny that they were told about the harassment in an attempt to discredit you
File a complaint with the Department of Fair Employment and Housing or the Equal Employment Opportunity Commission (this can be undertaken by a lawyer with experience in Warner Bros. Entertainment Inc. sexual harassment cases)
Report sexual assault to police
Acquire medical attention, keep copies of any hospital receipts, and make copies of doctor's notes and prescriptions
It is highly recommended that you reach out to a Warner Bros. Entertainment Inc. sexual harassment lawyer to help with your case. You may not have any legal experience at all, and if you try to proceed with a claim, you run the risk of losing completely.
You also risk being fired if you report sexual harassment. If Warner Bros. Entertainment Inc. wrongfully and illegally fired you after you reported sexual harassment, you should get help from a Warner Bros. Entertainment Inc. wrongful termination lawyer. Don't leave the company without filing a Warner Bros. Entertainment Inc. wrongful termination and sexual harassment lawsuit.
What can I win in a lawsuit against Warner Bros. for sexual harassment?
Warner Bros. Entertainment Inc. sexual harassment lawsuits can be worth hundreds of thousands of dollars. Warner Bros. Entertainment Inc. sexual harassment cases can have an average value of more than $1,000,000 if there are numerous parties involved or if there were physical violence. You may also be able to file a class action lawsuit against Warner Bros. Entertainment Inc. for sexual harassment. This is viable if there are numerous individuals who were harassed. The benefit is that there will be a lot of evidence to pull from; the downside is that the compensation would be distributed among a group, so each party would receive a smaller amount.
We will fight to win you the following damages:
Lost income
Job reinstatement
Reimbursement of benefits, promotions, commissions, bonuses, and more
Punitive damages if there was gross negligence or an intention to cause harm
If you wish to file a Warner Bros. Entertainment Inc. sexual harassment class action lawsuit or other kind of claim, contact a Warner Bros. Entertainment Inc. workplace sexual harassment attorney today.
Los Angeles Warner Bros. Entertainment Inc. Sexual Harassment Lawyer
If you are seeking a law firm representing victims of sexual harassment against Warner Bros. Entertainment Inc., you have come to the right place. The California Labor Law Employment Attorneys Group can provide you with Warner Bros. Entertainment Inc. discrimination attorneys to handle your claim. We are aggressive and renowned for our highly skilled lawyers and large rate of success.
Call us today to set up a free legal consultation to discuss your claim. We'll talk you through the legal process and help you understand the viability of your case. We will also tell you more about our zero fee guarantee, which says that we won't get paid anything unless and until we win your claim. If we lose, we take no payment whatsoever.
To get help from a California sexual harassment attorney for Warner Bros. Entertainment Inc. employees, contact the California Labor Law Employment Attorneys Group today.


:: Peanut Press Creative ::: Sorry I've been M.I.A!
My goodness...it's been some time since I've last blogged! What have I been up to?! Well, Invitation & Paper Element design for 3 weddings and attending a few weddings at that! Wedding season has been in full effect and while things are calming down here for just about a month, November will be one for the books with back-to-back travel to San Francisco for my best friend's wedding and then to Costa Rica for yet another wedding! I promise I'll be back with some great photos of some of the work I've been doing recently and hopefully some great photos from my travels!


Makeup and beauty !!!: My January Vellvette Box !
My January Vellvette Box !
And here are the stuffs !
And a little detail pictures of every products !
And another parcel is Anna andre one.
You remember my broken lipstick story in December box that was replace by the company itself.Here is the picture of it .
Have you got your vellvette box? What you got?
Time to go ,see you in my next Post !
Hi! Thanks for stopping by my blog! I love Opi's 'Kiss me on my tulips', it's such a pretty colour!


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Justia › US Law › Case Law › Alabama Case Law › Alabama Court of Civil Appeals Decisions › 1976 › Young v. City of Huntsville
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Young v. City of Huntsville
342 So. 2d 918 (1976)
In re Barbara YOUNG v. CITY OF HUNTSVILLE, Alabama, d/b/a Huntsville Hospital. Ex parte Barbara Young.
Civ. 852.
Court of Civil Appeals of Alabama.
December 8, 1976.
Rehearing Denied January 12, 1977.
*920 M. U. Griffin, Huntsville, for petitioner.
Ford, Caldwell, Ford & Payne and Robert L. Hodges, Huntsville, for respondent.
BRADLEY, Judge.
Barbara Young initiated this workmen's compensation case by alleging in the Circuit Court of Madison County that she is totally and permanently disabled as a result of contracting bilateral thrombophlebitis during the course of her employment as a licensed practical nurse at the Huntsville Hospital, Huntsville, Alabama. She sought both compensation and medical expenses under Title 26, Section 313(34), Code of Alabama 1940 (Recomp.1958) (Supp.1973), and Title 26, Section 262 et seq., Code of Alabama 1940 (Recomp.1958). After a hearing the trial court denied petitioner all relief. This is the decision to be reviewed here.
Petitioner is a fifty-three year old woman who has worked most of her adult life at jobs requiring a great deal of standing or sitting. From sometime in 1965 until March 1972, she worked on the night shift at the Athens-Limestone Hospital as a practical nurse. In order to work on a day shift, petitioner left the Athens-Limestone Hospital on March 13, 1972. Her duties at Huntsville Hospital were the same as they had been before, primarily giving medication to patients and making beds. However, due to increased activity during the day, there was more medicine to administer and more beds to make; thus the work was more strenuous and required more standing and walking.
In June 1974, while engaged in her routine duties, petitioner noticed some redness in one of her ankles. She was not able to relate the condition to any particular activity or incident. Petitioner was treated for this condition by a resident at the hospital until October 23, 1974, when she was referred to Dr. John Howard Lary, Jr., who diagnosed her as having superficial phlebitis of the right lower leg. She continued to work and to receive treatment from Dr. Lary until November 11, 1974, at which time she ceased working upon the instruction of Dr. Lary.
Petitioner's condition has steadily worsened since she has been unemployed. In March 1975 she was taken to the emergency room and admitted to the hospital for treatment for both superficial thrombophlebitis and deep vein thrombophlebitis in both legs. In April 1975 Dr. Lary determined that petitioner is permanently and totally disabled from gainful employment, due to bilateral thrombophlebitis. He said the external cause of petitioner's thrombophlebitis was her duties as a nurse, and that the condition could not have existed for more than three or four months prior to his examination of her in October 1974.
At the trial medical evidence was furnished by two doctors, Dr. Lary and Dr. James H. Rogers. Both testified that thrombophlebitis is a condition in which blood adheres to the wall of a vein, forming a clot, accompanied by inflammation of the surrounding area. Superficial thrombophlebitis refers to the condition in the veins just beneath the surface of the skin; deep vein thrombophlebitis refers to the condition when the veins affected are deeper. A blood clot may form when the wall of a vein has been irritated, or when the flow of blood from the heart through the venous *921 system is sufficiently slowed. Prolonged sitting or standing can cause the flow of blood to slow so that the condition develops. Some people are more susceptible than others to thrombophlebitis; thus, one person could contract the disease where another under the same circumstances would not.
Petitioner presents six issues for us to decide. The first three question whether there is any legal evidence to support the trial court's finding: (1) that petitioner's thrombophlebitis is not an occupational disease as defined in Title 26, Section 313(34), Code of Alabama 1940 (Recomp.1958); (2) that petitioner did not suffer an aggravation of a preexisting condition as envisioned by Title 26, Section 313(34), Code of Alabama 1940 (Recomp.1958); and (3) that petitioner's disability does not result from a compensable accident as contemplated by Title 26, Chapter 5, Article 2, Code of Alabama 1940. The fourth question is whether the trial court's findings of fact and conclusions of law comply with Title 26, Section 304. The fifth issue raises the validity of the trial court's allowing into evidence statistics on the incidence of thrombophlebitis as revealed by admissions to the Huntsville Hospital for several years prior to trial. The final issue is whether the trial court erred in overruling petitioner's motion for summary judgment.
The standard of review in workmen's compensation cases is whether there is any legal evidence to sustain the trial court's finding or conclusion or judgment. Mobile Paint Manufacturing Co. v. Crowley, 56 Ala.App. 673, 325 So. 2d 182 (1975); Glover v. Howell Plywood Co., 50 Ala.App. 22, 276 So. 2d 608 (1973); Edwards v. City of Huntsville, 49 Ala.App. 498, 273 So. 2d 475 (1973). Thus, the first issue to be decided by this court is whether there was any legal evidence to support the trial court's finding that petitioner's condition of thrombophlebitis is not an "occupational disease" within the meaning of Title 26, Section 313(34), and that she did not suffer disablement caused by the contraction of an occupational disease as defined in that statute.
"Occupational disease" is defined in the cited statute as being:
"[A] disease arising out of and in the course of employment, . . . which is due to hazards in excess of those ordinarily incident to employment in general and is peculiar to the occupation in which the employee is engaged, but without regard to negligence or fault, if any, of the employer. A disease . . . shall be deemed an occupational disease only if caused by a hazard recognized as peculiar to a particular trade, process, occupation or employment as a direct result of exposure over a period of time to the normal working conditions of such trade, process, occupation or employment. The term `contraction of an occupational disease' as used herein shall include any aggravation of such disease without regard to the employment in which the disease was contracted. . ."
Thus, to be occupational the disease must be (1) due to hazards in excess of those ordinarily incident to employment in general, and (2) peculiar to the occupation in which the employee is engaged.
In City of Tuscaloosa v. Howard, 55 Ala.App. 701, 318 So. 2d 729 (1975), we stated what evidence an employee-plaintiff must show in order to establish that he or she has an occupational disease within the meaning of the statute. The disease must be directly caused by or result from exposure over a period of time to a hazard recognized as peculiar to the normal working conditions of the employee's particular occupation. The disease must in fact be contracted from or aggravated by the nature of the employment, and the contraction or aggravation must arise out of and in the course of the employment. Finally, the disability claimed must result from the disease.
Neither of the two doctors who testified at trial stated that thrombophlebitis is prevalent in or peculiar to the nursing profession. Dr. Lary said in his opinion nurses have an increased risk of contracting the disease because of their prolonged standing or sitting, but that the risk is no greater *922 than in any other job which requires the same amount of sitting or standing. Dr. Rogers said that thrombophlebitis does not seem to be more prevalent in one occupation than in another, as there is nothing about a nurse's duties which make a nurse more susceptible to the disease than a truck driver, a store clerk, a secretary, or an assembly line worker. He personally had treated a person who held a Ph.D in education, several housewives, several persons in a postoperative stage, several persons taking oral contraceptive pills, and a nurse for thrombophlebitis. Petitioner maintains that thrombophlebitis does not have to be peculiar to the nursing profession in order for her to recover under the occupational disease statute.
The appellate courts of this state have not construed the term "peculiar to the occupation" contained in the statute. Dicta in the Howard case, supra, could be mistaken to establish a definition requiring that the hazard giving rise to the disease be found only within the employee's occupation and in no other. This court did not intend such a restrictive definition. It is a well established policy of this state that the workmen's compensation act is to be liberally construed to accomplish its beneficent purposes; Gilmore v. Rust Engineering Co., 289 Ala. 46, 265 So. 2d 591 (1972) and cases cited. To require that the disease originate exclusively from the particular kind of employment in which the employee-plaintiff is engaged would severely limit recovery under the occupational disease statute and contravene the remedial legislative purpose.
Courts in other jurisdictions have rejected such a restrictive interpretation of the term "peculiar to the occupation." The Connecticut court defined the phrase, as used in its statute, to mean that:
". . . the conditions of [the] employment must result in a hazard which distinguishes it in character from the general run of occupations." Glodenis v. American Brass Co., 118 Conn. 29, 40, 170 A. 146, 150 (1934).
This definition has been adopted by the courts of Michigan, Underwood v. National Motor Castings Division, 329 Mich. 273, 45 N.W.2d 286 (1951), and Minnesota, Gray v. City of St. Paul, 250 Minn. 220, 84 N.W.2d 606 (1957).
Applying the construction to the definition in our statute, we think that in order for a disease to be occupational it must be due to hazards which are (1) in excess of those ordinarily incident to employment in general and (2) different in character from those found in the general run of occupations. To state the matter succinctly, the plaintiff must be exposed by his or her employment to the risk causing the disease in a measurably greater degree and in a substantially different manner than are persons in employment generally.
In the case at bar there was sufficient evidence before the trial court for it to find that persons in employment generally, and even unemployed persons, are exposed to the risk of contracting thrombophlebitis, and therefore that thrombophlebitis is not caused by hazards in excess of those ordinarily incident to employment in general and peculiar to the nursing profession. In addition to the doctors' testimony, Dr. Benjamin C. Johnston, a rehabilitative psychologist who works as a consultant for the Social Security Administration at its disability hearings, testified that in the past two years he had had contact with sixty cases involving thrombophlebitis. In none of those cases were the petitioners nurses.
Petitioner's lawyer even stated at trial:
"We don't contend that phlebitis is a disease which is exclusively contracted by nurses nor that it is unique to nurses. Of course, we are well aware that there are many people, of many occupations in life who contract thrombophlebitis or phlebitis and we are also well aware that there are many unemployed people who contract it, too. . . ."
Consequently we conclude that there was legal evidence to support the trial court's finding that petitioner's thrombophlebitis is not an occupational disease.
Title 26, Section 313(34) also provides:
*923 "The term `contraction of an occupational disease' as used herein shall include any aggravation of such disease without regard to the employment in which the disease was contracted."
Petitioner claims she falls within this provision of the statute in that she had a preexisting susceptibility to thrombophlebitis, due to a proven long history of varicose veins. She claims that aggravation of the varicose veins caused the thrombophlebitis.
Again, there is legal evidence in the record to support the trial court's finding that petitioner's disease of thrombophlebitis was not due to aggravation of a preexisting condition. Petitioner's own doctor testified that there is no established causal connection between thrombophlebitis and varicose veins. Although a person with varicose veins might have a slightly increased incidence of superficial thrombophlebitis, most people with varicose veins do not have the latter disease. Furthermore, there was testimony that walking, one activity required by petitioner's job and of which she complains, aids in the treatment of early stages of thrombophlebitis because it tends to speed the flow of blood through the circulatory system, thereby preventing stagnation in the lower extremities.
Petitioner's third contention, that there is no legal evidence to support the trial court's finding that petitioner did not suffer a compensable accident as contemplated by Title 26, Chapter 5, Article 2, supra, is equally without foundation. This court in the Howard case, supra, traced the history of the term "accident" as used in Article 2, supra, and pointed out that in the early existence of the statute the courts required that the injury be traceable to an event which happened suddenly and violently and was of unusual nature and foreign to the usual occurrences on that job. Howard then noted that more recently the term "accident" has been construed in the context of the effect rather than the event; there is an accident if the result was unexpected and unforeseen and it was caused by the job. The test is:
"If in the performance of the duties for which he is employed an employee is exposed to a danger or risk materially in excess of that to which people not so employed are exposed, and an injury occurs, such injury may legally be determined to have arisen from his employment and be an accident under the statute.. . ." 55 Ala.App. at 705, 318 So. 2d at 732.
It was Dr. Lary's opinion that nurses face an increased risk of incurring thrombophlebitis. However, as already discussed, there was other evidence before the court that the hazard of incurring the disease in the nursing profession is not materially in excess of that to which people not so employed are exposed. Where testimony in workmen's compensation proceedings is conflicting, and there is testimony supporting the trial court's finding, such finding is conclusive. Davis-Day Timber Co. v. Gentry, 54 Ala.App. 385, 309 So. 2d 97 (1975). Consequently, we conclude that the trial court's finding on this aspect of the case is supported by legal evidence.
Petitioner's fourth contention is that the trial court failed to make sufficient "findings of fact and conclusions of law" as required by Title 26, Section 304, Code of Alabama 1940 (Recomp.1958), and that such failure requires reversal. It appears that petitioner is saying that the trial court failed to make findings on issues raised at trial, specifically her susceptibility to the disease, the aggravation of an occupational disease, and the aggravation of a nonoccupational preexisting disease. Petitioner maintains that Pinkney v. James B. Clow & Sons, Inc., 277 Ala. 648, 173 So. 2d 811 (1965), compels reversal where the trial court fails to determine an issue raised by the pleadings.
Although petitioner correctly states the Pinkney decision, there is no merit to her complaint. The pleadings filed by petitioner raised the issue of disability due to an occupational disease and an accident. The trial court made specific findings of fact and conclusions of law as to these issues. The five distinctions made by petitioner *924 in brief of these issues are not, so far as we can determine, supported by the record before us. We find no error here.
The fifth issue raised by petitioner is that the trial court erred in admitting testimony of Paul B. Miller, medical records director for the Huntsville Hospital, relating to statistics extracted from the business records of the hospital and compiled by the hospital for trial. The evidence was taken from a computer printout showing the number of patients treated at the Huntsville Hospital for thrombophlebitis categorized by occupation.
In a workmen's compensation case the appellate court reviews the judgment of the trial court by writ of certiorari, i.e., the reviewing court will look to see if there are errors of law apparent from the face of the record and will only be concerned with whether or not there is legal evidence to support the findings of fact. Boatwright v. Dothan Aviation Corp., 278 Ala. 142, 176 So. 2d 500 (1965). The appellate court will not review technical questions regarding the trial court's rulings on objections to the admission of evidence. Houser v. Young, 247 Ala. 562, 25 So. 2d 421 (1946); Sloss-Sheffield Steel & Iron Co. v. House, 217 Ala. 422, 116 So. 167 (1928). The reason for appellate restraint, given in Woodward Iron Co. v. Bradford, 206 Ala. 447, 90 So. 803 (1921), is that there is no statutory provision for setting out the trial court's rulings on admissibility in the findings of the trial judge and therefore these rulings are not part of the record. Thus, we do not reach the question raised by petitioner.
Finally, petitioner claims that the trial court erred in overruling her motion for summary judgment.
A motion for summary judgment may be granted only when there is no genuine issue as to any material fact, and the moving party is entitled to judgment as a matter of law. Rule 56, ARCP; Birmingham Television Corp. v. Water Works, 292 Ala. 147, 290 So. 2d 636 (1974). In the case at bar the pleadings and evidence on file at the time the summary judgment motion was filed shows that a genuine issue of material fact was presented for resolution by the trial court; therefore, the motion was properly overruled.
No reversible error having been argued, the trial court's judgment is affirmed.
WRIGHT, P. J., and HOLMES, J., concur.


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