Differential bevel gear and bevel gear differential for vehicle

Abstract

The utility model relates to a differential bevel gear (100), teeth of the differential bevel gear have a tooth crest height coefficient within the range of at least 1.15 and the maximum of 1.25 or have a tooth crest height coefficient within the range of at least 0.6 and the maximum of 0.85, and the differential bevel gear (100) has a pressure angle within the range of 21 degrees and 26 degrees. In addition, the utility model further relates to a corresponding bevel gear differential mechanism used for the vehicle, the bevel gear differential mechanism comprises the differential bevel gear which is provided with an outer tooth part and forms a first differential bevel gear and a second differential bevel gear meshed with the first differential bevel gear, teeth of the first differential bevel gear have the tooth top height coefficient within the range of 1.18-1.25, and the tooth top height coefficient of the second differential bevel gear is larger than the tooth top height coefficient of the first differential bevel gear. The teeth of the second differential bevel gear have an addendum height coefficient in the range of 0.6 to 0.85, and the total overlap ratio of the first differential bevel gear and the second differential bevel gear is in the range of 1.25 to 1.45.

Description

Field of the Invention

[0001] The utility model relates to a differential bevel gear, a bevel gear differential with at least two differential bevel gears, and a method for manufacturing a differential bevel gear. In particular, the tooth geometry is optimized to improve the load-carrying capacity and performance of the differential bevel gear. Background Art

[0002] There are a large number of gear transmission mechanisms in mechanical engineering. In particular, cylindrical gear transmission mechanisms and bevel gear transmission mechanisms. The common point of gear transmission mechanisms is that two gears rotate around their respective rotation axes, and the gears are in contact with each other through teeth on the tooth surfaces, and the gears act on each other through the tooth surfaces. Each tooth of a gear is effectively in contact with the teeth of another gear only during a part of the rotation of the corresponding gear. Compared with cylindrical gear transmission mechanisms, the rolling geometry design of bevel gear transmission mechanisms is much more complex. The characteristics of bevel gear transmission mechanisms usually include two intersecting rotation axes (different from hypoid bevel gears, etc.). In a bevel gear transmission mechanism, two contact points in a pair of contact points describe a circle, just like in a cylindrical gear transmission mechanism, but in a bevel gear transmission mechanism, these two contact points are not located in a common plane. However, the constant (and equal) distance between the two contact points and the intersection point of the two rotation axes causes these two circles to be located on a common spherical surface. Therefore, similar to cylindrical gear transmission mechanisms, the rolling on this spherical surface can be regarded as independent of the tooth width.

[0003] Differential bevel gears are important components in many applications such as the automotive and aerospace industries. The efficiency and reliability of differential bevel gears depend on many factors, including tooth geometry, addendum coefficient, and contact ratio.

[0004] The addendum coefficient is an important parameter when calculating the tooth profile of a gear. Its definition is the ratio of the addendum height to the pitch of the gear. The greater the addendum height, the stronger the load-carrying capacity of the gear, but at the same time, it will also increase the load and tooth surface wear. The typical addendum height of a differential bevel gear is about 0.3 to 0.5 times the pitch. The addendum coefficient is also used for this purpose. Here, the addendum height is set according to the module. The typical value is about 0.9 to 1.0 times. Another important parameter in the design of differential bevel gears is the contact ratio. It describes the degree of spatial overlap between the tooth surfaces of the two gears used in differential transmission. The higher the contact ratio, the more evenly the load is distributed and the stronger the load-carrying capacity, but at the same time, it will also lead to an increase in friction losses and noise. The latter is indirectly related. In order to make the gear transmission mechanism more robust and durable and suppress noise generation, it is usually attempted to increase the contact ratio. The optimal contact ratio depends on various factors, including tooth geometry and operating conditions.

[0005] EP 2 484 474 A1 discloses a method for determining the geometric data of a first bevel gear in a bevel gear drive, and a bevel gear drive including a first and a second bevel gear. EP 2 580 493 B1 discloses a bevel gear tooth part with optimized load capacity. Summary of the Invention

[0006] The technical problem to be solved by the present utility model is to provide a creative tooth geometry according to the present utility model, which is improved or at least represents an alternative embodiment to improve the performance and reliability of differential bevel gears. The technology proposed by the present utility model can be used in various applications of differential bevel gears. In particular, it is necessary to solve the additional challenges brought by electric vehicles, such as through recovery ability.

[0007] According to the present utility model, the differential bevel gear has a conical tooth part. An external tooth part with a plurality of teeth is formed on the tooth part. The addendum height coefficient of these teeth is in the range of at least 1.15 to a maximum of 1.25, or in the range of at least 0.6 to a maximum of 0.85. The differential bevel gear is particularly suitable for a bevel gear differential in a vehicle.

[0008] The differential bevel gear can generally be called a bevel gear. The axes of the differential bevel gears are not parallel but intersecting. The intersection angle can be 90°. Its basic shape is a truncated cone with teeth on its side surface. In other words, a large number of teeth are formed on the side surface, and the range can be called the tooth part. The tooth part is arranged on the side surface. If two differential bevel gears are paired with each other, their tips (i.e., the tips of the imaginary cones) will coincide. The teeth can extend linearly along the side surface line. The differential bevel gear can be a straight tooth part, that is, the tooth surface line of the spur gear tooth part is a straight line passing through the center of the spur gear. Therefore, the differential bevel gear can also be called a straight bevel gear. The differential bevel gear can have an octoid tooth part (Oktoidenverzahnung). Different from the involute that describes the tooth height profile of a cylindrical gear, the octoid is not the tooth height profile of a bevel gear, but its meshing line represents a section of an octoid (displayed as an octoid curve on the entire length of the imaginary sphere). The tooth height profile of the differential bevel gear is based on a first-order or second-order octoid or spherical involute. The term "octoid" comes from the shape of the meshing line E on the spherical shell of the bevel gear pair, which is represented as an octoid curve (octoid).

[0009] Due to the use of previously uncommon tooth part parameters, the side safety and profile coincidence degree have been improved targeted. Therefore, longer service life, improved recovery ability and longer service life can be achieved at higher torques, especially for electric vehicles.

[0010] The addendum height coefficient is at least 1.19.

[0011] The pressure angle of the differential bevel gear can be in the range between 24° and 25°.

[0012] The profile modification coefficient of the differential bevel gear can be between ±0.24 and ±0.28. In particular, the magnitude of the profile modification coefficient of the differential bevel gear can be between 0.24 and 0.28.

[0013] The dedendum height coefficient of the differential bevel gear can be between 0.9 and 1.55. In particular, the dedendum height coefficient can be in the range between 0.9 and 1.0 or in the range between 1.3 and 1.55.

[0014] The differential bevel gear can have a tooth thickness in the range between 4.7 mm and 7.5 mm. Alternatively, the differential bevel gear has a module in the range between 3.9 and 4.1.

[0015] The value of the number of teeth can be between 9 and 16.

[0016] The differential bevel gear can be manufactured by a forming process, in particular without subsequent machining of the teeth. As will be explained in detail below, the differential bevel gear can be manufactured by a hot forming process and / or a warm forming process and / or a cold forming process.

[0017] The spherical involute of the tooth height profile can be changed in the tooth height direction and / or the width direction (Profil-und / oder Breitenrichtung).

[0018] According to the present utility model, a bevel gear differential for a vehicle includes a differential bevel gear formed as a balance bevel gear and a differential bevel gear formed as a shaft gear that meshes with the balance bevel gear, wherein the total contact ratio of the balance bevel gear and the shaft gear is between 1.25 and 1.45. According to a variant of the above differential bevel gear, both the balance bevel gear and the shaft gear are differential bevel gears.

[0019] Therefore, the bevel gear differential includes a first differential bevel gear according to the above-described embodiment having an external tooth portion, wherein the teeth of the first differential bevel gear have a addendum height coefficient in the range of at least 1.18 and at most 1.25; and a second differential bevel gear according to the above-described embodiment that meshes with the first differential bevel gear, wherein the teeth of the second differential bevel gear have an addendum height coefficient in the range of at least 0.6 and at most 0.85, wherein the total contact ratio of the first differential bevel gear and the second differential bevel gear is in the range of 1.25 to 1.45.

[0020] A bevel gear differential can be understood as a bevel gear differential drive, a differential gear drive mechanism, a balancing gear drive mechanism or simply a differential, or a bevel gear rolling gear drive mechanism, i.e., gear rolling and sliding. The balancing bevel gear can also be called a balancing gear. The shaft gear can also be called a bevel gear. The bevel gear differential can be coupled to one input and two outputs (a power divider, Verteilergetriebe). The bevel gear differential can have a differential housing, and two, three or four balancing bevel gears can be installed inside the housing. The shaft gear of the driven shaft can bear against these gears.

[0021] The first differential bevel gear can have a plurality of first teeth and rotate about a first axis of rotation at a first speed during operation, wherein the second differential bevel gear has a plurality of second teeth and rotates about a second axis of rotation at a second speed during operation. The two axes of rotation intersect and form an intersection angle at the axis intersection, wherein the two differential bevel gears act on each other through the first tooth surface of the first teeth and the second tooth surface of the second teeth.

[0022] The bevel gear differential can have at least four differential bevel gears. The bevel gear differential can be symmetrically installed inside a planetary gear carrier (also called a cage or basket): the differential bevel gears connected to the driven shaft can be arranged oppositely. The cage can have a plurality (usually two) of differential bevel gears meshing with the driven differential bevel gears on the circumference.

[0023] The first differential bevel gear of the bevel gear differential can have a profile modification coefficient between 0.24 and 0.28, and the profile modification coefficient of the first differential bevel gear of the bevel gear differential can especially be 0.24 or 0.28. The second differential bevel gear of the bevel gear differential can have a profile modification coefficient between -0.24 and -0.28, and the profile modification coefficient of the second differential bevel gear of the bevel gear differential can especially be -0.24 or -0.28.

[0024] If the bevel gear differential is used for the driven shaft of a motor vehicle, it can be called an axle differential. It can be used to balance the rotational speeds between two wheels. When driving straight, at the axle gap, the two pinions do not rotate but rotate together with the large gear, so their function is neutral. On the other hand, when turning, the two gears rotate around the axis in opposite directions, so the wheel on the outer radius is driven at a slightly higher speed, while the other wheel is driven at a slightly lower speed. In vehicles where all wheels are driven (all-wheel drive), an additional power divider is required: first, each other driven shaft needs an axle differential, and a center differential or a longitudinal differential is also needed to distribute the engine driving force to multiple axles. Four-wheel drive vehicles have two axle differentials and a center differential.

[0025] The first differential bevel gear may have a dedendum height coefficient in the range between 0.9 and 0.98, while the second differential bevel gear may have a dedendum height coefficient in the range between 1.30 and 1.55.

[0026] The first differential bevel gear may have a tooth thickness in the range between 6.3 mm and 7.5 mm, while the second differential bevel gear may have a tooth thickness in the range between 4.7 mm and 5.4 mm.

[0027] A method for manufacturing a differential bevel gear, in particular for a motor vehicle bevel gear differential, by forming, may have at least one preparation step, a heating step, a volume forming step, and a cooling step. In the preparation step, a blank is provided. In particular, the blank may be a section of round material. In the heating step, the blank is heated to a temperature between 650 °C and 1250 °C, in particular by induction heating. In the volume forming step, the heated blank is formed into a differential bevel gear according to the above variants. The volume formed differential bevel gear, in particular for a bevel gear differential in a motor vehicle, has a conical tooth part, on which an external tooth part with a plurality of teeth is formed, and the teeth of the differential bevel gear have a tip height coefficient of at least 1.1. In the cooling step, the differential bevel gear is cooled.

[0028] Volume forming is a forming process in which the material undergoes three-dimensional flow and different wall thicknesses can be achieved in the part. Specifically, volume forming can be understood as die forging. Specifically, volume forming can be hot forming, or as a supplement or alternative, warm forming (700 °C - 980 °C, in particular 750 °C - 950 °C), or as a supplement or alternative, cold forming. For example, hot forming can be combined with warm forming or cold forming. Additionally, in one embodiment, the volume forming step may only include hot forming. The volume forming step can be carried out on a multi-stage press. Volume forming can be understood as extrusion forming, and thus is a special flashless volume forming. Cold extrusion is an extrusion forming process in which the workpiece is approximately at room temperature before the start of forming, i.e., it is not heated before forming.

[0029] In the heating step, the blank can be heated to below 1000 °C, in particular below 980 °C, especially below 950 °C. The volume forming step can be carried out below recrystallization. In particular, for steel, the volume forming step can be carried out below the austenite transformation temperature.

[0030] In the cooling step, the differential bevel gear can be cooled in a controlled manner, in particular in an air stream. Alternatively, the differential bevel gear can be left to forge harden.

[0031] The differential bevel gears can be sandblasted after the solid forming step, in particular with steel grit, and as an addition or alternative, another forming step can be carried out after the volume forming step (or the sandblasting step), in which the differential bevel gears are corrected. The further forming step can be a cold forming step. Description of the Drawings

[0032] The concept of the present invention will be described in more detail below with reference to the drawings. However, the following description should be regarded as purely exemplary. The present invention is only defined by the subject matter in the claims. Advantageous embodiments of the present invention will be explained below with reference to the drawings. Elements having the same or similar functions are denoted by the same reference numerals. In addition, for the sake of easy reading and correspondence, reference numerals will also be used for features that are not shown in the described figures. Additionally, if these features have been clearly marked in the previous figures, not all reference numerals are always shown in similar figures. In the drawings:

[0033] Figure 1 is a perspective view of a bevel gear differential with two differential bevel gears according to an embodiment of the present invention;

[0034] Figure 2 is a side view of a bevel gear differential according to an embodiment of the present invention;

[0035] Figure 3 is a schematic cross-sectional view of a differential bevel gear according to an embodiment of the present invention;

[0036] Figure 4 is a partial cross-sectional schematic view of two meshing differential bevel gears according to an embodiment of the present invention;

[0037] Figure 5 is a perspective view of a bevel gear differential according to an embodiment of the present invention;

[0038] Figure 6 is a perspective view of a differential bevel gear according to an embodiment of the present invention;

[0039] Figure 7 is a spherical section (Kugelschnitt) of a bevel gear differential according to an embodiment of the present invention;

[0040] Figure 8 is a schematic view of a vehicle with a bevel gear differential according to an embodiment of the present invention;

[0041] Figure 9 is a flow chart of a method according to the present invention according to an embodiment of the present invention;

[0042] Figures 10 to 14Schematic illustration of meshing differential bevel gears according to an embodiment of the present invention (under no load and under load); and

[0043] Figures 15 to 16 is the backside geometry according to an embodiment of the present invention. Detailed Description

[0044] Figure 1 Shows a perspective view of a bevel gear differential 100 with two differential bevel gears 102. The differential bevel gears 102 of the bevel gear differential 100 are equivalent in all respects. To distinguish between the two differential bevel gears 102, the first differential bevel gear 102 will hereinafter be referred to as the balance bevel gear 104 and the second differential bevel gear 102 will be referred to as the shaft gear 106. Thus, the first differential bevel gear 102 is the balance bevel gear 104 and the second differential bevel gear is the shaft gear 106. The bevel gear differential 100 is a bevel gear drive in which the differential bevel gears 102 can rotate about their respective axes of rotation R 104 and R 106 respectively. The two axes of rotation R 104 、R 106 intersect at a common intersection point 112. In the Figure 1 illustrated embodiment, the angle α at which the two axes of rotation R 104 、R 106 intersect is 90°. Both differential bevel gears 102 have a plurality of teeth 108 with tooth surfaces 110. The differential bevel gears 102 interact via the tooth surfaces 110, or in other words, the differential bevel gears 102 transmit the provided torque. Each tooth 108 of the two differential bevel gears 102 is only effectively in contact with the tooth 108 of the other differential bevel gear 102 via its respective tooth surface 110 during a partial rotation of the respective differential bevel gear 102. This is also clearly shown again in the Figure 5 and Figure 7 schematic illustrations. The movements of the two contact points of the contact point pair of the two meshing differential bevel gears 102 each describe a circle, where these two circles are not in a plane but on a sphere, because the distances of the two contact points to the intersection point 112 are equal and constant. Thus, it can be observed that the two differential bevel gears 102 roll on this sphere. This is sometimes referred to as the spherical section (Kugelschnitt).

[0045] The basic shape of the differential bevel gear 102 is a truncated cone. The truncated cone is a solid of revolution based on a cone, where the cone is cut off in a manner parallel to the bottom surface 116. Thus, the truncated cone has two circular surfaces and a side surface 114. The larger circular surface is hereinafter referred to as the bottom surface 116, and the smaller of the two circular surfaces is called the top surface 118. A tooth portion 120 is formed on the side surface 114. Thus, the differential bevel gear 102 has an external tooth portion 122.

[0046] In Figure 1 the illustrated embodiment, the balance bevel gear 104 has 10 teeth, while in Figure 1 the illustrated embodiment, the shaft gear 106 has 14 teeth. In embodiments not specifically shown, it can be envisioned that the number of teeth of the differential bevel gear 104 is greater than or equal to 9, and the number of teeth of the shaft gear 106 is greater than or equal to 13.

[0047] Figure 2 Shows Figure 1 a side view of the bevel gear differential shown.

[0048] Figure 3 Shows a schematic cross-sectional view of the differential bevel gear 102 according to an embodiment of the present invention. The most important dimensions and their positions are shown in the figure. The figure shows a root circle 130 having a root circle diameter d f , a pitch circle 132 having a pitch circle diameter d, and an addendum circle 134 having an addendum circle diameter d a , where only half of the diameter, i.e., the radius, is shown as an arrow from the center to the corresponding circle. The pitch circle is also called the rolling circle, and its rolling circle diameter is d w . The tooth height h extends from the root circle to the addendum circle, and the addendum height h a extends from the pitch circle to the addendum circle, and the root height h f extends from the root circle to the pitch circle.

[0049] The pitch p is defined as the arc length of the pitch circle 132 between two identical points on two adjacent teeth 108. The pitch p is also called the tooth pitch or the circumferential pitch. Thus, the pitch p is the arc length dimension from the tooth center to the tooth center of consecutive teeth on the gear. The pitch p is calculated by the product of pi π and the diameter d of the pitch circle 132. The module m characterizes similar differential bevel gears and is usually in millimeters. The module m represents the ratio of the pitch circle diameter d to the number of teeth z. The product of the module m and π is called the pitch p. The pitch p is also the sum of the clearance width e between two teeth 108 and the tooth thickness s, both measured on the pitch circle 132.

[0050] The addendum height coefficient h a * is defined as the ratio of the addendum height h a of the tooth 108 to the pitch p of the gear 102. In the illustrated embodiment, the addendum height coefficient ha * At least 0.6. As mentioned above, the addendum height coefficient can be at least 0.6 or at least 1.15. Additionally, the addendum height coefficient can be at most 0.85 or at most 1.25. In a particular embodiment, the addendum height coefficient can be between 1.15 and 1.25, or between 0.6 and 0.85.

[0051] The profile shift V of a gear is usually given by the profile shift coefficient x related to the module m. A positive coefficient (x > 0) indicates that the tool profile moves outward, and a negative coefficient (x < 0) indicates that the tool profile moves inward (for external gears). For example, a profile shift coefficient x = +0.25 means that the tool profile moves outward by 0.25 times the module. Generally, the root circle radius and the addendum circle radius will increase by the amount of the profile shift accordingly.

[0052] Figure 4 A partial view of a schematic cross - sectional view showing two meshing differential bevel gears 102 is presented, where it can be clearly seen that the addendum clearance c is the distance between the addendum circle 134 of one differential bevel gear 102 and the root circle 130 of the other differential bevel gear 102.

[0053] Figure 5 The view in Figure 1 and Figure 2 shows the bevel gear differential 100 as shown, where compared with Figure 2 this differential rotates about the axis of rotation R of the shaft gear 106 106 rotates. Figure 6 Shows a balancing bevel gear 104 as an example of the differential bevel gear 102. Figure 7 Shows a spherical cross - section of the bevel gear differential 100.

[0054] Figure 8 Shows a schematic view of a vehicle 800 with an engine 802, where the rotational movement of the engine is transmitted through the bevel gear differential 100 to the axle 804 and then to the wheels 806.

[0055] Figure 9 Shows a flow chart of a method for manufacturing the differential bevel gear 102 of the bevel gear differential 100, especially for use in a vehicle 800, by a forming technique. The step S1 of the method is to provide a blank. For example, the blank can be a section of round material. In the heating step S2, the blank is heated to a temperature between 650 °C and 1250 °C. The heating step S2 can be inductive. In one embodiment, the steps S1 and S2 can also be combined. For example, heat the round material and first cut off a section of the heated round material to produce the blank to be provided.

[0056] In a subsequent volume forming step S3, the blank is formed into a differential bevel gear 102, and the addendum height coefficient of the teeth 108 of the differential bevel gear 102 is at least 1.1.

[0057] In a final step S4, the differential bevel gear 102 is cooled.

[0058] Figures 10 to 12 A schematic view showing the differential bevel gear in a plane is presented, where the meshing and load diagrams of the teeth are visible. Figure 11 A view showing two differential bevel gears in contact without load is presented. Figure 12 A view showing the case with load is presented. Figure 13 and Figure 14 A view showing the contact without load and with load, as can be determined in the simulation. Finally, in Figure 15 and Figure 16 the possible backside geometries are presented.

[0059] List of Reference Numerals

[0060] 100 Bevel Gear Differential

[0061] 102 Differential Bevel Gear

[0062] 104 Balancing Bevel Gear

[0063] 106 Axial Gear

[0064] 108 Tooth

[0065] 110 Tooth Surface

[0066] 112 Intersection Point

[0067] 114 Side Surface

[0068] 116 Bottom Surface

[0069] 118 Top Surface

[0070] 120 Tooth Portion

[0071] 122 External Tooth Portion

[0072] 130 Root Circle

[0073] 132 Pitch Circle

[0074] 134 Addendum Circle

[0075] 800 Vehicle

[0076] 802 Engine

[0077] 804 Axle

[0078] 806 Wheel

[0079] R 104 ,R 106 Rotation axis

[0080] α included angle

[0081] c clearance at the tooth tip

[0082] d pitch diameter

[0083] d a Tip diameter

[0084] d b Base circle diameter

[0085] d f Root circle diameter

[0086] d w Rolling circle diameter

[0087] h tooth height

[0088] h a Tip height

[0089] h f Root height

[0090] m module (mm)

[0091] p pitch (on the pitch circle)

[0092] z number of teeth

[0093] x profile shift coefficient

[0094] V = x * m profile shift

[0095] h * a Tip height coefficient

[0096] S1 - S4 Method steps

Claims

1. A differential bevel gear (100), the differential bevel gear having a conical tooth portion, on which an external tooth portion with a plurality of teeth is formed, It is characterized in that the teeth of the differential bevel gear having a addendum height coefficient in the range of at least 1.15 and at most 1.25 or having an addendum height coefficient in the range of at least 0.6 and at most 0.85, and the differential bevel gear (100) having a pressure angle in the range between 21° and 26°.

2. The differential bevel gear (100) according to claim 1, wherein, The differential bevel gear (100) is a differential bevel gear for a bevel gear differential in a vehicle.

3. The differential bevel gear (100) according to claim 1, wherein, The differential bevel gear (100) has a pressure angle of at least 24°.

4. The differential bevel gear (100) according to claim 1, wherein, The differential bevel gear (100) has a maximum pressure angle of 25°.

5. The differential bevel gear (100) according to claim 1, wherein, The addendum height coefficient is at least 1.

19.

6. The differential bevel gear (100) according to any one of claims 1 to 5, wherein, The differential bevel gear - has a profile modification coefficient between ±0.24 and ±0.28, and / or - has a dedendum height coefficient in the range of 0.9 to 1.55, and / or - has a tooth thickness in the range of 4.7 mm to 7.5 mm, and / or - has a module between 3.9 and 4.

1.

7. The differential bevel gear (100) according to claim 6, wherein, The differential bevel gear has a profile modification coefficient between 0.24 and 0.

28.

8. The differential bevel gear (100) according to any one of claims 1 to 5, wherein, The value of the number of teeth is between 9 and 16.

9. The differential bevel gear (100) according to any one of claims 1 to 5, wherein, The differential bevel gear is manufactured by a forming process.

10. The differential bevel gear (100) according to claim 9, wherein, The differential bevel gear is manufactured in such a way that no post-cutting process is performed on the tooth portion.

11. A bevel gear differential for a vehicle, the bevel gear differential comprising The first differential bevel gear, the first differential bevel gear being a differential bevel gear according to any one of claims 1 to 10 and having an external tooth portion, wherein, the teeth of the first differential bevel gear having an addendum height coefficient in the range of at least 1.18 and at most 1.25, and a second differential bevel gear, the second differential bevel gear being the differential bevel gear according to any one of claims 1 to 10 and meshing with the first differential bevel gear, wherein the teeth of the second differential bevel gear have an addendum height coefficient in the range of at least 0.6 and at most 0.85, wherein the total contact ratio of the first differential bevel gear and the second differential bevel gear is in the range of 1.25 to 1.

45.

12. The bevel gear differential for a vehicle according to claim 11, wherein, The first differential bevel gear has a dedendum height coefficient in the range of 0.9 to 0.98, while the second differential bevel gear has a dedendum height coefficient between 1.30 and 1.

55.

13. The bevel gear differential for a vehicle according to claim 11 or 12, wherein, The first differential bevel gear has a tooth thickness in the range of 6.3 mm to 7.5 mm, while the second differential bevel gear has a tooth thickness in the range of 4.7 mm and 5.4 mm.

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