Differential gear for a vehicle

Abstract

Differential gear (1; 201; 301) for a vehicle, the differential gear (1; 201; 301) comprising - a housing (2; 202; 302) with at least one slideway (20, 21; 212), - a first axle shaft gear (4; 203) with a first axle shaft gear toothing (5; 204), - a second axle shaft gear (6) with a second axle shaft gear toothing (7) and - at least one differential gear (8, 9; 108; 205) with a differential gear toothing (11, 16; 206), - at least one sliding block (13, 17; 113), where - the at least one sliding block (13, 17; 113) rotatably receives the at least one compensating gear (8, 9; 108), - the differential gear (8, 9; 108, 205) is arranged between the first axle shaft gear (4; 203) and the second axle shaft gear (6), - the differential gear toothing (11, 16; 206) is in engagement with the first axle shaft gear toothing (5; 204), - the differential gear toothing (11, 16; 206) is in engagement with the second axle shaft gear toothing (7), - the first axle shaft gear toothing (5; 204) exerts a first displacement force (F1) on the differential gear toothing (11, 16; 206), - the second axle shaft gear toothing (7) exerts a second displacement force (F2) on the differential gear toothing (11, 16; 206), - the at least one sliding block (13, 17; 113) is displaceably mounted together with the at least one compensating gear (8, 9; 108; 205) in the slideway (20, 21; 212), so that the sliding block (13, 17; 113) and the compensating gear (8, 9; 205) can move together between the first axle shaft gear (4; 203) and the second axle shaft gear (6), and - the differential gear (8, 9; 108; 205) is displaced by the first displacement force (F1) and the second displacement force (F2) into an equilibrium position between the first axle shaft gear (4; 203) and the second axle shaft gear (6), where - the compensating gear (8, 9) has a pin (12), - the sliding block (13, 17) has a receptacle (18, 19) matching the pin (12), or - the sliding block (113) has a pin (112), - the compensating gear (108) has a receptacle (118) matching the pin (112), and - the pin (112) is rotatably mounted within the receptacle (118), and the differential gear (1) further comprising at least one friction disc (22), wherein - the compensating gear (8) has a back surface (14) which is supported on the housing (2) and / or on the sliding block (13), - the friction disc (22) is arranged between the back surface (14) and the housing (2) and / or between the back surface (14) and the sliding block (13).

Description

Technical area

[0001] The present invention relates to a differential gear for a vehicle. A further independent claim is directed to a vehicle with such a differential gear. State of the art

[0002] The rapid advance of civilization and the shift in consumer behavior toward e-commerce are creating a growing need for freight transport, particularly in limited urban spaces. Traditional delivery vehicles such as trucks and cars struggle in many urban areas with the lack of infrastructure necessary for proper functioning, such as a lack of parking spaces for loading and unloading. Furthermore, the increasing densification of cities is also driving the need for smaller and more maneuverable vehicles, particularly cargo bikes. Cargo bikes come in various designs. For example, cargo bikes can be multi-wheeled, particularly two-wheeled or three-wheeled. The drive axle is usually located on the rear axle, which can be powered by a chain drive or an electric motor.A container, bin or box designed for transporting goods or small children is located either in front of the handlebars at the level of the front axle or behind the saddle at the level of the rear axle and is connected to the bicycle frame.

[0003] In order to improve the maneuverability of the vehicles, especially cargo bikes, or to reduce the turning radius and increase stability when cornering, cargo bikes are known to be equipped with differentials that make it possible to compensate for different rotational speeds of two wheels on one axle, especially when cornering.

[0004] In these differentials, a differential pinion typically contacts a differential housing, resulting in friction, particularly between a pinion pin and the housing. Furthermore, the individual components within the differential typically have very tight tolerances, which are partly due to different machine setups. This can result in the pinions not being optimally positioned within the differential if different forces act between the side gears and the differential pinions, and specified tolerances may not be met.

[0005] DE 10 2018 211 812 A1 describes a differential gear for a motor vehicle, comprising a first axle shaft bevel gear mounted rotatably about a first axle shaft rotation axis, a second axle shaft bevel gear mounted rotatably about a second axle shaft rotation axis, and at least one differential bevel gear rotatably mounted on a planetary gear carrier and meshing with both the first axle shaft bevel gear and the second axle shaft bevel gear. Each of the axle shaft bevel gears is fixed in the axial direction with respect to the first axle shaft rotation axis and / or the second axle shaft rotation axis in a direction facing away from the other of the axle shaft bevel gears. Provision is made for the mounting of the differential bevel gear on the planetary gear carrier to have a play in the axial direction, within which the differential bevel gear is freely movable relative to the planetary gear carrier. A similar disclosure is also made in US Pat. No. 4,959,043 A.

[0006] US Patent No. 5,980,416 A describes a differential for smaller vehicles that achieves higher efficiency, lower wear, and reduced heat generation by directly mounting a ring gear on the axle shafts. The ring gear contains a web with openings to accommodate planetary gears that mesh with bevel gears on the axle shafts. This design improves component alignment and enables a compact construction. Various designs of the planetary shafts and the use of powder-metallurgical materials contribute to cost efficiency and dimensional stability.

[0007] It is known to use toy differentials with planetary gears that can slide and rotate within a housing. One design known from WO 2021 / 074282 A1 uses a bell-shaped housing that supports the mounting and movement of the gears and is intended for toys with realistic movement. Such arrangements are intended to enable smooth and dynamic gear interaction to improve functionality in a play context. Description of the invention

[0008] An object of the invention is to provide a differential gear which takes into account the problems described above.

[0009] The problem is solved by a differential gear having the features of claim 1 and a vehicle having the features of claim 12. Advantageous further developments emerge from the subclaims, the description, and the figures.

[0010] The invention provides a differential gear for a vehicle, which in particular comprises a housing, a cover, two axle shaft gears, and one or more (usually two to four) differential gears. The housing can be designed as a closed or open one.

[0011] According to the present invention, the differential gear has a floating support for at least one differential gear. The at least one differential gear is floatingly mounted in at least one sliding block. The at least one sliding block is, in turn, slidably mounted in a slideway of a housing of the differential gear. A central feature is therefore the slideways in which the differential gears and the sliding blocks are supported. These slideways, with corresponding sliding seats of the sliding blocks, enable the differential gears to center themselves, thereby simultaneously reducing the friction between the differential gears and the housing of the differential gear.

[0012] In this sense, according to a first aspect of the invention, a differential gear for a vehicle is provided. The differential gear comprises a housing with at least one sliding track, a first axle gear with first axle gear teeth, a second axle gear with second axle gear teeth, and at least one differential gear with differential gear teeth. The axle gears are designed to establish the connection to an axle and the wheels of the vehicle. The at least one differential gear can compensate for speed differences between the wheels. The at least one differential gear is arranged between the first axle gear and the second axle gear, with the differential gear teeth engaging with the first axle gear teeth and the second axle gear teeth. The first axle gear teeth of the first axle gear mesh with the differential gear teeth of the at least one differential gear.The second axle shaft gear toothing of the second axle shaft gear also meshes with the differential gear toothing of at least one differential gear.

[0013] Forces arise in the meshing of the gears described above. On the one hand, these forces push the at least one differential gear towards the housing, i.e. in the direction of the differential gear's longitudinal axis. On the other hand, these forces push the side shaft gears towards the housing and cause rotation. If the side shaft gears are pressed against the housing but cannot move, then the same force acts in the opposite direction on the at least one differential gear. The differential gear therefore tends to move away from the side shaft gears. The tooth mesh therefore acts like a spring, trying to displace the at least one differential gear. Only when both forces are in balance is the at least one differential gear in a stable position. The closer the differential gear comes to one of the side shaft gears, the greater the force.In particular, only when the balance wheel is in the middle (central position) between both wheels has it reached its stable position.

[0014] In this sense, according to the invention, the first axle shaft gear toothing exerts a first displacement force on the differential gear toothing, wherein the second axle shaft gear toothing exerts a second displacement force on the differential gear toothing. This is particularly the case during operation of the differential gear, i.e., when the axle shaft gears rotate. According to the present invention, the differential gear is displaceably mounted in the slideway via the sliding block, such that the differential gear can move between the first axle shaft gear and the second axle shaft gear. The differential gear is displaced by the first displacement force and the second displacement force into an equilibrium position between the first axle shaft gear and the second axle shaft gear.Contrary to prior art solutions, the at least one differential gear is not rigidly mounted, but rather movably mounted between the axle shaft gears by means of the at least one sliding track and the at least one sliding block. This allows a kind of self-centering of the gearing due to the shape of the housing with its sliding seats and sliding tracks, which also reduces friction in the differential gear.

[0015] In other words, the special feature of this differential design is that the differential gears center themselves due to the tooth forces and can therefore move to a central position. This allows for better running characteristics of the gearing, even with larger manufacturing and assembly tolerances. In this context, to achieve good running characteristics in a differential gear, the gears should have the theoretically correct distance from each other. This is not entirely easy, since, for example, the planes for the side gear cannot be manufactured in the same setup. The position of the center axis for the differential gears must be manufactured with equal precision, with reference to the planes of the side gears.With the differential gear according to the present invention, care should still be taken to ensure that the distance between the axle shaft gears is approximately correct (deviations can be easily compensated within a certain range). However, the components then adjust themselves to the correct position. This represents an advantage over a conventional design, in which the differential gears are attached to the housing via a bolt so that they are only rotatable but not movable.

[0016] The differential gear further comprises at least one sliding block, which rotatably supports the differential gear. Furthermore, the sliding block is slidably mounted along the slideway with the differential gear, allowing the sliding block and differential gear to move together between the first axle shaft gear and the second axle shaft gear. The floating mounting of the differential gear via a sliding block in the slideway represents a particularly simple and reliable mounting arrangement. If the differential gear comprises multiple differential gears, each of the differential gears can move independently of the other differential gears between the axle shaft gears and into the optimal position. This particularly effectively counteracts the occurrence of stresses within the gear. Furthermore, the sliding block can advantageously fulfill a force-supporting function.

[0017] The differential gear is rotatably mounted in the sliding blocks, in particular by means of a plain bearing. Mounting the differential gear in the sliding block enables optimization of the plain bearing. Thus, the sliding block can provide a significantly larger plain bearing surface for the pin of the differential gear than is the case with conventional bearings, according to which the shaft of the differential gear is mounted directly in the housing of the differential gear. In this sense, in one embodiment, the differential gear has a pin, wherein the sliding block has a receptacle that fits the pin, and wherein the pin is rotatably mounted within the receptacle. The bearing can, in particular, be a plain bearing.Alternatively, the sliding block can have a pin, and the differential gear comprises a receptacle that fits the pin, wherein the pin is rotatably mounted within the receptacle, in particular by means of a plain bearing. The pin can be integrally connected to the rest of the sliding block. Alternatively, the sliding block can have a bore into which a cylindrical pin is inserted, in particular in a rotationally fixed manner. The cylindrical pin protrudes from the bore of the sliding block, wherein the differential gear is rotatably mounted on the cylindrical pin with a receptacle that fits the cylindrical pin.

[0018] The housing of the differential gear is usually made of a non-hardened material to save costs. The same can apply to the sliding block. The differential gear, on the other hand, is usually made of a hardened material. With such a material combination (hard metal on soft metal), possible relative movement and the associated friction between the differential gear and the sliding block and / or the housing can lead to increased wear, particularly on the sliding block and / or the housing. A friction disc, which could also be referred to as a support disc or sliding disc, on the corresponding contact and friction surfaces of the aforementioned elements can significantly reduce wear. As far as the material of the friction disc is concerned, unalloyed steels can be used, for example C15, low-alloy steels or even higher-alloy steels such as nitrided steels.The friction disc allows for the prevention or at least reduction of wear. The friction disc can be designed such that it is not a wear part itself and therefore does not need to be replaced. In this sense, in a further embodiment, the differential gear further comprises at least one friction disc, wherein the differential gear has a back surface that is supported on the housing and / or on the sliding block, and wherein the friction disc is arranged between the back surface and the housing and / or between the back surface and the sliding block.

[0019] The sliding blocks can be designed in different ways. For example, rectangular profiles with a hole in the longitudinal section can be used (i.e. tubular sliding blocks) or, for example, sliding blocks that have a T-profile in the longitudinal section. A sliding block that has a rectangular section profile in the longitudinal section with a hole (e.g. a bore that matches the diameter of the pin to accommodate the pin of the differential gear) is particularly simple and cost-effective to manufacture. The differential gear can be supported with its back surface on the sliding block or on the housing. A support surface of the sliding block can be particularly large if the sliding block has a T-profile in the longitudinal section. As described above, a friction disc can also be arranged between the sliding block and the back surface of the differential gear.In this sense, in one embodiment, the sliding block is designed in a T-shaped longitudinal section and has a first leg and a second leg which runs perpendicular to the first leg, wherein the first leg of the T-shaped sliding block is displaceably mounted in the slideway, whereas the back surface of the differential gear is supported on the second leg of the T-shaped sliding block.

[0020] In a preferred embodiment, the differential gear has at least two differential gears (preferably three or four differential gears) which are rotatably mounted in at least two sliding blocks (preferably three or four sliding blocks), wherein the sliding blocks are slidably mounted in at least two slideways (preferably three or four slideways) of the transmission housing between the two axle shaft gears. The first sliding block (of the at least two sliding blocks) supports the first differential gear, wherein the first sliding block is slidably mounted in the first slideway of the at least two slideways. The second sliding block (of the at least two sliding blocks) supports the second differential gear, wherein the second sliding block is slidably mounted in the second slideway of the at least two slideways.In this sense, in one embodiment, the differential gear comprises a first differential gear with a first differential gear toothing, a second differential gear with a second differential gear toothing, a first sliding block and a second sliding block, wherein the first sliding block rotatably receives the first differential gear and the second sliding block rotatably receives the second differential gear, and wherein the two differential gears are arranged between the first axle shaft gear and the second axle shaft gear.The first pinion gear toothing and the second pinion gear toothing are in engagement (in other words: mesh) with the first side gear toothing and with the second side gear toothing, wherein the first side gear toothing exerts a first displacement force on the first pinion gear toothing and on the second pinion gear toothing, and wherein the second side gear toothing exerts a second displacement force on the first pinion gear toothing and on the second pinion gear toothing.The housing has a first slideway and a second slideway, wherein the first sliding block is displaceably mounted together with the first differential gear in the first slideway such that the first sliding block and the first differential gear can move between the first axle gear and the second axle gear, and wherein the second sliding block is displaceably mounted together with the second differential gear in the second slideway such that the second sliding block and the second differential gear can move between the first axle gear and the second axle gear. The first differential gear and the second differential gear are each displaced by the first displacement force and the second displacement force into an equilibrium position between the first axle gear and the second axle gear.

[0021] The pinion gears can move into a "central position," which describes the position of the pinion gears relative to the axle shaft gears. Bevel gears have what is known as the axis intersection point, meaning the longitudinal axes of the pinion gears intersect at a point that is ideally the center of the differential. This is the theoretical position in which the pinion gears should be for optimal operation and best performance. When the pinion gears are in equilibrium, they are preferably located at or at least close to this theoretical point (axis intersection point). In this sense, the first pinion gear is a bevel gear with a first longitudinal axis, and the second pinion gear is a bevel gear with a second longitudinal axis.The first differential gear and the second differential gear are displaced into the equilibrium position by the first displacement force and the second displacement force in such a way that an intersection point of the extensions of the first longitudinal axis and the second longitudinal axis moves in the direction of an axle intersection point which lies in the center point of the differential gear. Particularly preferably, the first differential gear and the second differential gear are displaced into the equilibrium position by the first displacement force and the second displacement force in such a way that the intersection point of the first longitudinal axis and the second longitudinal axis moves into the axle intersection point. In particular, the longitudinal axes of the differential gears and the longitudinal axes of the axle shaft gears meet at the center point of the differential gear when the axle shaft gears and differential gears are in their designed position. the center point The longitudinal axes orThe rotational axes of the side gears are collinear, meaning they form the same axis. The longitudinal axes and rotational axes of the differential gears are also collinear, meaning they form the same axis. The axes of all gears in the differential should intersect at one point, the axle intersection point.

[0022] Furthermore, the use of spring washers allows for backlash-free operation without the need to adjust the gears during assembly. This allows for very simple and quick installation. The spring washers can be arranged either in the area of ​​the axle shaft gears or in the area of ​​at least one differential gear.

[0023] In this sense, in a further embodiment, the differential gear comprises at least one axle gear spring washer, wherein the axle gear spring washer is arranged between one of the axle gears and the housing in such a way that the axle gear spring washer exerts an axle gear spring force on the respective axle gear, so that the axle gear spring force presses the axle gear toothing of the respective axle gear into engagement with the differential gear toothing of the at least one differential gear.Alternatively or additionally, the differential gear may further comprise at least one differential gear spring washer, wherein the differential gear spring washer is arranged between the at least one differential gear and the housing or between the at least one differential gear and the at least one sliding block such that the differential gear spring washer exerts a differential gear spring force on the differential gear, so that the differential gear spring force presses the differential gear toothing of the differential gear into engagement with the axle shaft gear toothings of the axle shaft gears.

[0024] In a classic differential gear, particularly in the passenger car sector, a drive gear is normally screwed or welded to the housing of the differential gear. Due to a special external geometry of the housing of the differential gear according to the invention, the housing can be connected particularly efficiently to a drive element (e.g. to a drive gear or part of an axle shaft) which drives the housing of the differential gear, e.g. by means of a positive connection or by adhesive bonding. The housing can therefore have a tripod geometry, which can be used for a positive connection, for example, with the drive gear. Instead of designing the housing to be round on the outside, the housing can have material and weight-saving pockets (bulges) which are directed inwards and into which corresponding inward-facing mating elements of the drive gear can engage in a positive-fitting manner.Alternatively, a drive element can also be connected to the housing by a material fit. In other words, the idea is that the "tripod" outer shape of the housing creates "grooves" that are particularly suitable for a positive fit with the drive gear. In this sense, an outer surface of the housing has a tripod geometry, so that an inner surface of a drive element, shaped complementarily to the tripod geometry of the outer surface of the housing, can be positively connected to the housing.

[0025] According to a second aspect of the invention, a vehicle is provided. The vehicle comprises a differential gear according to a first aspect of the invention. The vehicle can be a multi-track vehicle, in particular with two wheels arranged on a common (in particular driven) axle. The vehicle can be, in particular, a passenger car (car), a light motor vehicle, or a cargo bike (e-bike, pedelec, S-pedelec, etc.). The vehicle can also be a non-electric, i.e., purely muscle-powered, bicycle or cargo bike, in particular a multi-track one.

[0026] Furthermore, the differential gear according to the invention is particularly suitable for installation and operation in 3- or 4-wheel vehicles, in a quad or in a truck.

[0027] Further advantages and features of the present invention will become apparent from the following description of preferred embodiments. The features described therein can be implemented alone or in combination with one or more of the features presented above, provided the features do not contradict each other. The following description of preferred embodiments is made with reference to the accompanying drawings. Short description of the characters

[0028] Preferred further embodiments of the invention are explained in more detail by the following description of the schematic figures. Fig. 1 a perspective sectional view of an embodiment of a part of a differential gear according to a first embodiment of the invention with a T-shaped sliding block, Fig. 2 an alternative perspective sectional view of the differential gear according to Fig. 1, Fig. 3 a longitudinal section of a friction disc or a spring disc which is arranged between a sliding block and a differential gear of the differential gear according to Fig. 1 is arranged, Fig. 4 a longitudinal section of a friction disc or a spring disc arranged between an alternative tubular sliding block and a differential gear of the differential gear according to Fig. 1 is arranged, Fig. 5 a perspective sectional view of the differential gear according to Fig. 1 with a thrust washer and an axle shaft spring washer, Fig. 6 a perspective sectional view of the differential gear according to Fig. 1 with an axle shaft spring washer but without a thrust washer, Fig. 7 a perspective sectional view of the differential gear according to Fig. 1 with a thrust washer but without an axle shaft spring washer, Fig. 8 a perspective view of an alternative sliding block with tenons, Fig. 9 an alternative perspective view of the sliding block according to Fig. 8, Fig. 10 an alternative perspective view of the sliding block according to Fig. 8, with a compensating gear with a holder mounted on the pin, Fig. 11 an alternative perspective view of the sliding block and the compensating wheel according to Fig. 10, Fig. 12 a perspective view of the differential gear according to Fig. 10, Fig. 13 an alternative perspective view of the balance wheel according to Fig. 10, Fig. 14 is a cross-sectional view of an embodiment of a part of a differential gear according to a second embodiment of the invention with a pin arrangement and Fig. 15 is a perspective view of an embodiment of a differential gear according to a third embodiment of the invention with a housing having a tripod geometry. Detailed description of preferred embodiments

[0029] Preferred embodiments are described below with reference to the figures. Identical, similar, or equivalent elements in the different figures are provided with identical reference numerals, and a repeated description of these elements is partially omitted to avoid redundancies. Where applicable, all individual features illustrated in the embodiments can be combined and / or interchanged without departing from the scope of the invention.

[0030] Fig. 1 and Fig. 2 show a differential gear 1 for a motor vehicle (not shown). The motor vehicle may, in particular, be a cargo bike, with the differential gear being arranged in the area of ​​a front axle or in the area of ​​a rear axle of the cargo bike to compensate for speed differences between wheels mounted at opposite ends of the front axle or rear axle, respectively.

[0031] In the illustrated embodiment, the differential gear 1 comprises a housing 2, one end of which is closed with a cover 3. The differential gear 1 further comprises a first axle gear 4 with a first axle gear toothing 5 and a second axle gear 6 with a second axle gear toothing 7. Both the first axle gear 4 and the second axle gear 6 are bevel gears in the illustrated embodiment. Thus, the first axle gear toothing 5 and the second axle gear toothing 7 are also bevel gears.

[0032] Furthermore, the differential gear 1 comprises a total of three differential gears, of which Fig. 1 due to the cutting direction only a first differential gear 8 and a second differential gear 9 are shown and of which in Fig. 2, only the first differential gear 8 is shown. In the illustrated embodiment, the differential gears 8, 9 are arranged equidistantly in a circumferential direction, spaced 120° apart from one another. The differential gears 8, 9 are identical in the illustrated embodiment, ie, the differential gears 8, 9 are identical parts. In the illustrated embodiment, all three differential gears are bevel gears.

[0033] The first differential gear 8 has a first plate 10, which forms a first differential gear toothing 11 on its radially outer surface, which is a bevel gear toothing. Oriented perpendicularly to the first plate 10, the first differential gear 8 further has a first pin 12, which serves for rotatable mounting within a first sliding block 13. A first back surface 14 of the first differential gear 8 faces the first sliding block 13. The first differential gear 8 is supported with its first back surface 14 on the first sliding block 13. The second differential gear 9 has a second plate 15, which forms a second differential gear toothing 16 on its radially outer surface, which is a bevel gear toothing. Oriented perpendicularly to the second plate 15, the second differential gear 9 further has a second pin (not visible in Fig. 1, Fig. 2; cf. the identically designed first compensating gear 8), which serves for the rotatable mounting within a second sliding block 17 ( Fig. 2). A second back surface (not visible in Fig. 1, Fig. 2; cf. the identically designed first differential gear 8) of the second differential gear 9 faces the second sliding block 17. The second differential gear 9 rests with its second back surface on the second sliding block 17. The third differential gear (not visible in Fig. 1, Fig. 2; compare the identically designed differential gears 8, 9) is rotatable in the same way as the first differential gear 8 and the second differential gear 9 in a third sliding block (not visible a Fig. 1, Fig. 2; compare the identically designed sliding blocks 13, 17).

[0034] The first sliding block 13 has a first receptacle 18 that matches the first pin 12 of the first differential gear 8. The first pin 12 of the first differential gear 8 is rotatably mounted in this first receptacle 18. In particular, a plain bearing exists between the first receptacle 18 and the first pin 12. In the same way, the second sliding block 17 has a second receptacle 19 that matches the second pin of the second differential gear 9. The second pin of the second differential gear 9 is rotatably mounted in this second receptacle 19. In particular, a plain bearing exists between the second receptacle 19 and the second pin of the second differential gear 9. The third sliding block (not shown) has a third receptacle that is designed identically to the first sliding block 13 and the second sliding block 17.The third pin of the third differential gear, not shown, is also rotatably mounted within the third receptacle, in particular by means of a plain bearing.

[0035] In the following, the example is described according to Fig. 1 and Fig. 2 predominantly in connection with the first differential gear 8 and the second differential gear 9 as well as with the first sliding block 13 and the second sliding block 17, which can be moved in a first slideway 20 (first sliding block 13) of the housing 2 or in a second slideway 21 (second sliding block 17) of the housing 2 between the first axle shaft gear 4 and the second axle shaft gear 6. However, these explanations also apply analogously to the third differential gear (not shown), to the third sliding block (not shown) and to the third slideway (not shown).

[0036] The two differential gears 8, 9 are arranged between the first axle shaft gear 4 and the second axle shaft gear 6. The first differential gear toothing 11 and the second differential gear toothing 16 are in engagement with the first axle shaft gear toothing 5 and with the second axle shaft gear toothing 7. The first axle shaft gear toothing 5 exerts a first displacement force F1 on the first conical differential gear toothing 11 and on the second conical differential gear toothing 16. In the exemplary embodiment shown, the first displacement force F1 runs parallel to a longitudinal axis of the first axle shaft gear 4. Analogously, the second axle shaft gear toothing 7 exerts a second displacement force F2 on the first differential gear toothing 11 and on the second differential gear toothing 16. The second displacement force F2 is opposite to the first displacement force F1.

[0037] The first sliding block 13, together with the first differential gear 8, is slidably mounted in the first slideway 20, so that the first sliding block 13 and the first differential gear 8 can move between the first axle shaft gear 4 and the second axle shaft gear 6. The first slideway 20 is formed in the circumferential direction and in the radial direction by a recess adapted to the shape and size of the first sliding block 13, which extends in the axial direction (in which the axles of the motor vehicle, which are connected to the axle shaft gears 4, 6, also run) between the first axle shaft gear 4 and the second axle shaft gear 6. Analogously, the second sliding block 17, together with the second differential gear 9, is slidably mounted in the second slideway 21, so that the second sliding block 17 and the second differential gear 9 can move between the first axle shaft gear 4 and the second axle shaft gear 6.The second slideway 21 is formed in the circumferential direction and in the radial direction by a recess adapted to the shape and size of the second sliding block 17, which extends in the axial direction between the first axle shaft gear 4 and the second axle shaft gear 6. The first differential gear 8 and the second differential gear 9 are each displaced independently of one another by the first displacement force F1 and the second displacement force F2 into an equilibrium position between the first axle shaft gear 4 and the second axle shaft gear 6.

[0038] In the tooth engagement described above, the displacement forces F1, F2 occur. Due to the conicity of the side gears 4, 6 and the differential gears 8, 9, these displacement forces F1, F2 press the differential gears 8, 9 towards the housing 2, i.e. in the direction of a longitudinal axis of the journal 12 of the respective differential gear 8, 9. On the other hand, the displacement forces F1, F2 press the side gears 4, 6 towards the housing 2 or towards the cover 3, respectively, and cause rotation. If the side gears 4, 6 are pressed against the housing 2 or against the cover 3, but cannot move, then the same displacement forces F1, F2 also act in the opposite direction on the two differential gears 8, 9. The differential gears 8, 9 therefore tend to move away from the side gears 4, 6 towards the housing 2. The tooth engagement acts like a spring, which tries to displace the differential gears 8, 9.Only when both forces F1 and F2 are in equilibrium do the differential gears 8 and 9 reach a stable position. The closer the differential gears 8 and 9 get to one of the two axle shaft gears 4 and 6, the greater the displacement force F1 / F2. In particular, only when the differential gears 8 and 9 are in the middle (central position) between the two axle shaft gears 4 and 6 have they reached their stable position.

[0039] The aforementioned central position or central location describes a position of the differential gears 8, 9 relative to the axle shaft gears 4, 6. With bevel gears, there is the so-called axis intersection point, i.e. the extensions of the collinear longitudinal axes L1, L2 of the differential gears 8, 9 and the extensions of the collinear longitudinal axes L3, L4 of the axle shaft gears 4, 6 intersect at a point 23, which can be regarded as the center point of the differential gear 1. This is the theoretical central position in which the differential gears 8, 9 should be located in order to run optimally and exhibit the best properties. When the differential gears 8, 9 are in the equilibrium position, they are preferably located at or at least close to this theoretical point (axis intersection point 23).

[0040] The scenery stones 13, 17 after Fig. 1 and Fig. 2 have, in longitudinal section, T-shaped profiles with a hole or a receptacle 18, 19. Fig. 3 shows schematically that an intermediate element 22, e.g. a friction disk and / or a spring disk, can be arranged between the sliding blocks, which are T-shaped in longitudinal section (in the embodiment shown between the first sliding block 13), and the back surfaces 14 of the three identical differential gears 8. The sliding block 13 has a first leg 26 and a second leg 27 which runs perpendicular to the first leg 26. The first leg 26 runs coaxially around a longitudinal axis L1 of the pin 12 of the differential gear 8. The first leg 26 of the sliding block 13 has the receptacle 18 matching the pin 12, wherein the pin 12 is rotatably mounted within the receptacle 18, in the embodiment shown by means of a plain bearing. The first leg 26 is slidably mounted in the first slideway 20 of the housing 2 of the differential gear 1.The back surface 14 of the compensating gear 8 is supported on the second leg 27 of the T-shaped sliding block 13, in particular via the intermediate element 22.

[0041] If the intermediate element 22 is a friction disc, the friction disc can reduce wear on the sliding block 13 and on the housing 2, which can be made of a softer metal than the sliding block 13, which can be made of a hardened metal, for example. The intermediate element 22 can also be a differential spring washer, which exerts a differential spring force on the differential gear 8, so that the differential spring force presses the differential gear toothing 11 of the differential gear 8 into engagement with the two side gear toothings 5, 7 of the two side gears 4, 6. A friction disc can also be combined with a differential spring washer, for example by placing the two on top of each other, or by placing a differential spring washer between two friction discs.Friction discs and / or differential wheel spring discs can also be arranged between the other two differential wheels and sliding blocks, as described above in connection with the first sliding block 13 and the first differential wheel 8.

[0042] Fig. 4 shows that the sliding blocks, in the example shown the first sliding block13, can alternatively be tubular (only a first leg and no second leg according to Fig. 3). In this case, an intermediate element 22 can be arranged between the back surface 14 of the compensating gear 8 on the one hand and the sliding block 13 and the housing 2 on the other hand, similar to what is described in connection with Fig. 3 has been described.

[0043] Fig. 5 shows the differential gear 1 after Fig. 1, wherein a thrust washer 24 is arranged between the cover 3 and the first side gear 4. On the other side, a side gear spring washer 25 is arranged between the second side gear 6 and the housing 2. The side gear spring washer 25 exerts a side gear spring force on the second side gear 6, so that the side gear spring force presses the second side gear toothing 7 of the second side gear 6 into engagement with the differential gear toothings 11, 16 of the differential gears 8, 9. The thrust washer 24 is optional and can be omitted, which is achieved by Fig. 6. Alternatively, the thrust washer 24 can be provided, whereby the axle shaft gear spring washer 25 is omitted, which is achieved by Fig. 7 is shown.

[0044] Fig. 8 to 13 show an alternative sliding block 113 and / or an alternative differential gear 108 for the differential gear 1 according to Fig. 1. In the embodiment shown, the sliding block 113 has a pin 112 and the compensating gear 108 comprises a receptacle 118 that fits to the pin 112. The pin 112 of the sliding block 113 can be inserted into the receptacle 118, so that the compensating gear 108 is rotatably mounted on the sliding block 113, as shown in Fig. 10 and Fig. 11 is shown.

[0045] The pin 112 is in the Fig. 8 to 13, the sliding block 113 is connected in one piece with the rest of the sliding block 113. Alternatively, the sliding block 113 can have a bore 119 which is Fig. 11 is indicated by dashed lines. In this variant, the pin 112 is a separate component from the sliding block 113 and can be referred to as a cylindrical pin. The cylindrical pin 112 is inserted or mounted in the bore 119 of the sliding block 113, in particular in a rotationally fixed manner. The cylindrical pin 112 protrudes from the bore 119 of the sliding block 113, with the compensating gear 108, with its receptacle 118 matching the cylindrical pin 112, being rotatably mounted on the cylindrical pin 112.

[0046] Fig. Figure 14 shows an alternative spider or pinion type differential 201. The differential 201 comprises a housing 202, two axle gears 203 (one of which is Fig. 14) each having a single axle gear toothing 204. Both axle gears 203 are bevel gears. Thus, the axle gear toothings 204 are also bevel gears. Furthermore, the differential gear 201 comprises a total of three identical differential gears 205, which are arranged equidistantly in a circumferential direction, spaced 120° apart from each other. In the illustrated embodiment, all three differential gears 205 are bevel gears. The differential gears 205 each have a single differential gear toothing 206 on their radially outer surface, which is a bevel gear toothing.

[0047] The differential gear 201 further comprises a pin arrangement 207 with three pins 208. Starting from a common center point 209 of the pin arrangement 207, the three pins 208 are arranged equidistantly in a circumferential direction, each spaced 120° apart from one another. The three pins 208 are rigidly connected to one another, in the illustrated embodiment as a single piece. The three differential gears 205 are each rotatably mounted on a central portion 210 of one of the three pins 208, in the illustrated embodiment by means of a plain bearing. Each of the pins 208 further has a freely extending (distal) end 211, which is displaceably mounted in one of three slideways 212 formed by the housing 202.The slideways 212 extend between the two axle shaft gears 203 in such a way that the journal arrangement 207 with all three journals 208 and the differential gears 205 rotatably mounted thereon can move back and forth together between the two axle shaft gears 203. This displaceability allows the axle shaft gears—caused by displacement forces of the meshing between the axle shaft gears and differential gears—to move into a central position, as is the case with the differential gear 1 according to FIG. Fig. 1 and Fig. 2 has been described.

[0048] Fig. 15 shows another differential gear 301 from the outside, which in its interior, for example, like the differential gear according to Fig. 1 or how the differential gear 201 according to Fig. 14. The differential gear has a housing 302 and a cover 303, which closes the housing 302 on one of its end faces. The housing 302 has a tripod geometry. A tripod geometry can be understood in connection with Fig.15 in particular, it should be understood that the housing 302 has on its outer side three material and weight-saving pockets 304 (indentations) which are directed inwards. In the exemplary embodiment shown, the three pockets 304 are arranged at a distance of 120° from one another in the circumferential direction. An element for driving the differential gear 301, e.g. a drive gear or part of an axle shaft, can have inward-facing bulges designed to be complementary to the three pockets 304 and which are also arranged at a distance of 120° from one another in the circumferential direction. The bulges of the element for driving the differential gear 301 can be brought into engagement with the three pockets 304 of the housing 302, so that a positive connection is produced and so that torque can be transmitted. List of reference symbols: F1 first displacement force F2 second displacement force L1 Longitudinal axis first differential gear L2 Longitudinal axis second differential gear L3 Longitudinal axis first axle shaft gear L4 Longitudinal axis second axle gear 1 differential gear 2 housings 3 lids 4 first axle shaft gear 5 first axle shaft gear teeth 6 second axle shaft gear 7 second axle shaft gear teeth 8 first balance wheel 9 second balance wheel 10 first plates 11 first differential gear teeth 12 first cone 13 first sliding block 14 first back surface 15 second plate 16 second differential gear teeth 17 second sliding block 18 first recording 19 second shot 20 first slideway 21 second slideway 22 Friction disc, balance wheel spring disc 23 Axis crossing point 24 Thrust washer 26 first leg of the sliding block 27 second leg sliding block 108 balance wheel 112 cones 113 sliding block 118 recording 201 differential gear 202 housings 203 axle shaft gear 204 axle shaft gear teeth 205 balance wheel 206 differential gear teeth 207 Pin arrangement 208 cones 209 Center of the tenon arrangement 210 middle section tenon 211 distal end of the cone 212 Slideway 301 differential gear 302 housing 303 lid 304 Tripod geometry

Claims

[1] Differential gear (1; 201; 301) for a vehicle having differential gear (1; 201; 301) - a housing (2; 202; 302) with at least one sliding track (20, 21; 212), - a first axle shaft gear (4; 203) with a first axle shaft gear toothing (5; 204), - a second axle shaft gear (6) with a second axle shaft gear toothing (7) and - at least one compensating gear (8, 9; 108; 205) with a compensating gear toothing (11, 16; 206), - at least one scenery stone (13, 17; 113), where - which at least one cam block (13, 17; 113) rotatably receives at least one compensating wheel (8, 9; 108), - the compensating gear (8, 9; 108, 205) is arranged between the first axle shaft gear (4; 203) and the second axle shaft gear (6), - the compensating gear teeth (11, 16; 206) are in engagement with the first axle shaft gear teeth (5; 204), - the compensating gear teeth (11, 16; 206) are in engagement with the second axle shaft gear teeth (7), - the first axle shaft gear toothing (5; 204) exerts a first displacement force (F1) on the compensating gear toothing (11, 16; 206), - the second axle shaft gear toothing (7) exerts a second displacement force (F2) on the compensating gear toothing (11, 16; 206), - the at least one cam block (13, 17; 113) together with the at least one compensating wheel (8, 9; 108; 205) is slidably mounted in the slide (20, 21; 212), so that the cam block (13, 17; 113) and the compensating wheel (8, 9; 205) can move together between the first axle shaft wheel (4; 203) and the second axle shaft wheel (6), and - the compensating gear (8, 9; 108; 205) is moved by the first displacement force (F1) and the second displacement force (F2) into an equilibrium position between the first axle shaft gear (4; 203) and the second axle shaft gear (6), where - the compensating wheel (8, 9) has a pin (12), - the stage set stone (13, 17) has a receptacle (18, 19) that matches the cone (12), or - the scenery stone (113) has a pin (112), - the compensating wheel (108) has a receptacle (118) that fits the pin (112), and - the pin (112) is rotatably mounted within the receptacle (118), and the differential gear (1) further comprising at least one friction disc (22), wherein - the compensating wheel (8) has a back surface (14) which is supported on the housing (2) and / or on the cam block (13), - the friction disc (22) is arranged between the back surface (14) and the housing (2) and / or between the back surface (14) and the cam block (13). [2] Differential gear (1) according to claim 1, wherein - the scenery stone (13) is T-shaped in longitudinal section and has a first leg (26) and a second leg (27) that runs perpendicular to the first leg (26), - the first leg (26) of the T-shaped cam block (13) is slidably mounted in the slide track (20), and - the back surface (14) of the compensating wheel (8) is supported on the second leg (27) of the T-shaped cam block (13). [3] Differential gear (1) according to one of the preceding claims, comprising the differential gear (1) - a first compensating gear (8) with a first compensating gear toothing (11), - a second compensating gear (9) with a second compensating gear toothing (16), - a first backdrop stone (13) and - a second backdrop stone (17), where - the first cam block (13) rotatably receives the first compensating wheel (8) and the second cam block (17) rotatably receives the second compensating wheel (9), - the two compensating gears (8, 9) are arranged between the first axle shaft gear (4) and the second axle shaft gear (6), - the first compensating gear toothing (11) and the second compensating gear toothing (16) are in engagement with the first axle shaft gear toothing (5) and with the second axle shaft gear toothing (7), - the first axle shaft gear toothing (5) exerts a first displacement force (F1) on the first differential gear toothing (11) and on the second differential gear toothing (16), and the second axle shaft gear toothing (7) exerts a second displacement force (F2) on the first differential gear toothing (11) and on the second differential gear toothing (16), - the housing (2) has a first sliding track (20) and a second sliding track (21), - the first cam block (13) together with the first compensating wheel (8) is slidably mounted in the first slide track (20), so that the first cam block (13) and the first compensating wheel (8) can move between the first axle shaft wheel (4) and the second axle shaft wheel (6), - the second cam block (17) together with the second compensating wheel (9) is slidably mounted in the second slide track (21), so that the second cam block (17) and the second compensating wheel (9) can move between the first axle shaft wheel (4) and the second axle shaft wheel (6), and - the first compensating gear (8) and the second compensating gear (9) are each moved into an equilibrium position between the first axle shaft gear (4) and the second axle shaft gear (6) by the first displacement force (F1) and the second displacement force (F2). [4] Differential gear (1) according to claim 3, wherein - the first compensating gear (8) is a bevel gear with a first longitudinal axis (L1), - the second compensating gear (9) is a bevel gear with a second longitudinal axis (L2), - the first compensating gear (8) and the second compensating gear (9) are moved into the equilibrium position by the first displacement force (F1) and by the second displacement force (F2) such that an intersection point of the extensions of the first longitudinal axis (L1) and the second longitudinal axis (L2) moves in the direction of an axis crossing point (23) which lies in the center of the differential gear (1). [5] Differential gear (1) according to claim 4, wherein the first compensating gear (8) and the second compensating gear (9) can be displaced into the equilibrium position by the first displacement force (F1) and by the second displacement force (F2) such that the intersection point of the first longitudinal axis (L1) and the second longitudinal axis (L2) moves to the axis intersection point (23). [6] Differential gear (1) according to one of the preceding claims, the differential gear (1; 101) further comprising at least one axle shaft spring washer (25), wherein the axle shaft spring washer (25) is arranged between one of the axle shaft wheels (6) and the housing (2) such that the axle shaft spring washer (22) exerts an axle shaft spring force on the axle shaft wheel (6) in question, such that the axle shaft spring force presses the axle shaft gear teeth (7) of the axle shaft wheel (6) in engagement with the differential gear teeth (11, 16) of the at least one differential gear (8, 9). [7] Differential gear (1) according to one of the preceding claims, the differential gear (1) further comprising at least one differential gear spring washer (22), wherein the differential gear spring washer (22) is arranged between the at least one differential gear (8, 9) and the housing (2) or between the at least one differential gear (8, 9) and the at least one cam block (13) such that the differential gear spring washer (22) exerts a differential gear spring force on the differential gear (8, 9) such that the differential gear spring force presses the differential gear teeth (11, 16) of the differential gear (8, 9) into engagement with the axle shaft gear teeth (5, 7) of the axle shaft gears (4, 6). [8] Differential gear (301) according to one of the preceding claims, wherein an outer surface of the housing (302) has a tripod geometry (304) such that an inner surface of a drive element shaped complementary to the tripod geometry (302) of the outer surface of the housing (301) can be positively connected to the housing (301). [9] Vehicle comprising a differential gear (1; 101; 201; 301) according to any of the preceding claims.

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