Transmission mechanism with isolation shell and motor vehicle with transmission mechanism

Abstract

The invention provides a transmission mechanism with an isolation shell and a motor vehicle with the transmission mechanism. The transmission mechanism is provided with a transmission device housing; the spur gear transmission device is arranged in the transmission device shell and is provided with a driving wheel and an output wheel which are connected with each other in a transmission technology; the differential mechanism is arranged in the transmission device shell and is provided with a differential mechanism shell which is connected with the output wheel in a relative rotation resisting manner, and a plurality of compensation wheels which are rotatably supported in the differential mechanism shell; the oil sump limits the oil level in the transmission device shell in the static loading state of the transmission mechanism; and an isolating housing arranged in the transmission housing, the isolating housing surrounding the output wheel and the differential housing at least below the oil level in order to isolate them from the oil sump, the isolating housing having a first oil guide contour along which oil in the isolating housing (19) can be conveyed from the isolating housing (19) to at least one oil filling point of the transmission (3).

Description

Technical Field

[0001] The invention relates to a transmission for a motor vehicle having the features of the preamble of claim 1. The invention also relates to a motor vehicle having such a transmission. Background Art

[0002] Electric drive trains are increasingly used for driving vehicles, which are used for electric and / or hybrid drives of vehicles. Typically, such drive trains have an electric machine, in particular an electric motor, and a reduction gear located downstream, which reduces the rotational movement generated by the electric motor. The reduction gear can be connected to one or more wheels of the vehicle in terms of drive technology via a differential in order to transmit the rotational movement to the wheels. In order to reduce the drag losses of the reduction gear and the differential, isolating devices are known that isolate the transmission components from the lubricating medium sump.

[0003] The printed document EP 1 635 090 A2, for example, discloses an oil drainage structure, which includes a transmission housing that surrounds a rotating body in a rotating body chamber, an oil storage container for storing oil discharged from the rotating body chamber, an oil drainage channel from the rotating body chamber to the oil storage container, and a deflection plate, wherein the deflection plate is arranged in the rotating body chamber between the transmission housing and the rotating body so as to surround the lower part of the rotating body, so that the oil around the rotating body is divided into the rotating body side and the transmission housing side in the rotating body chamber, wherein the deflection plate contains an oil drainage hole, which is opposite to the side surface of the rotating body and opposite to the opening of the oil drainage channel on one side of the rotating body chamber, so that the oil separated by the deflection plate is discharged to the oil drainage track through the oil drainage hole in the rotating body side. Summary of the invention

[0004] The object of the present invention is to provide a transmission which is distinguished by an improved lubrication concept.

[0005] This object is achieved by a transmission having the features of claim 1 and by a motor vehicle having the features of claim 15. Preferred or advantageous embodiments of the invention are apparent from the dependent claims, the following description and / or the drawings.

[0006] The subject of the present invention is a transmission mechanism, which is constructed and / or suitable for use in a motor vehicle. In particular, the transmission mechanism is used to transmit and distribute a drive torque or drive power provided by a drive unit, in particular an electric motor, to at least one wheel of the motor vehicle.

[0007] The transmission mechanism has a transmission housing. In particular, the transmission housing is used to accommodate all transmission mechanism components. Preferably, the transmission housing is configured as a wet chamber, which is sealed in a fluid-tight manner relative to the surrounding environment. The transmission mechanism can be connected to the drive unit via the transmission housing.

[0008] The transmission has a spur gear transmission arranged in a transmission housing, which is designed and / or suitable for transmitting a drive torque. Preferably, the spur gear transmission is designed to convert a high drive speed and a low drive torque into a lower drive speed and a higher drive torque. Preferably, the spur gear transmission has a transmission ratio i>1 for this purpose. In other words, the spur gear transmission is used for a reduction transmission.

[0009] The spur gear transmission has a drive wheel and an output wheel, which are connected to each other in terms of transmission technology within the transmission housing. In principle, the drive wheel and the output wheel can be directly meshed with each other. Alternatively, the drive wheel and the output wheel are connected to each other in terms of transmission technology via at least one or exactly one intermediate wheel, preferably a stepped intermediate wheel. In particular, the drive wheel is constructed and / or suitable for being driven by a drive machine. For this purpose, the drive wheel can be connected to the drive unit in terms of drive technology via a drive shaft. Particularly preferably, the drive wheel, the output wheel and any intermediate wheels are each constructed as a spur gear.

[0010] The transmission has a differential arranged in the transmission housing, which is designed and / or suitable for distributing the drive torque. Preferably, the differential is designed to distribute the drive torque between at least two or exactly two wheels of the motor vehicle, in particular between the left wheel and the right wheel. Such a differential is also called an axle differential. Alternatively, the differential can be designed to distribute the drive torque between at least two or exactly two axles, in particular between the front axle and the rear axle. Such a differential is also called a central differential or a longitudinal differential.

[0011] The differential has a differential case connected to the output wheel in a rotationally fixed manner, a plurality of compensating wheels rotatably supported in the differential case, and a first and a second driven shaft connected in terms of transmission technology via the compensating wheels. Preferably, the drive power can be transmitted from the output wheel to the differential case and output from the differential case to the driven shaft via the compensating wheels. In principle, the differential can be constructed as a cylindrical gear differential, wherein the compensating wheel is constructed as a cylindrical gear. However, preferably, the differential is constructed as a bevel gear differential, wherein the compensating wheel is constructed as a bevel gear. Preferably, the differential is rotatably supported in the differential case via a bearing pin, respectively. In particular, the output wheel is arranged eccentrically offset on the outside of the differential case.

[0012] The transmission has an oil sump which defines the oil level in the transmission housing in the static installed state of the transmission. In particular, the oil sump is formed within the transmission housing in the bottom region. Preferably, the oil sump is designed as a dry sump. The oil sump is preferably formed by the transmission oil located in the transmission housing. The transmission oil is preferably used to cool and / or lubricate transmission components during operation of the transmission.

[0013] The transmission also has an isolating shell arranged in the transmission housing, which surrounds the output gear and the differential housing at least below the oil level in order to isolate them from the oil sump. In particular, the isolating shell is used to isolate the transmission chamber of the spur gear transmission and the differential from the oil sump. For this purpose, the isolating shell is designed to be closed all around and / or oil-tight at least below the oil level.

[0014] It is proposed within the scope of the invention that the separating housing has a first oil-conducting contour, wherein the oil located in the separating housing can be conveyed from the separating housing along the first oil-conducting contour to at least one or exactly one oil filling point of the transmission by the rotation of the output wheel. Preferably, the conveying effect of the output wheel is utilized in such a way that the output wheel, during rotation, carries with it the oil located in the separating housing or in the transmission chamber via the toothing. Preferably, the first oil-conducting contour is arranged in the oil flow generated by the output wheel, so that the majority of the oil picked up by the output wheel is discharged to the oil filling point via the first oil-conducting contour. In particular, the oil flow path extends from the bottom area of ​​the separating housing via the output wheel and the first oil-conducting contour to at least one oil filling point. In particular, an oil-conducting contour is understood to be a contour that causes shearing or separation and / or redirection of the oil flow. The oil filling point can be a lubrication point or a supply point. For example, a lubrication point is understood to be a bearing point or a tooth region of one or more transmission components of a spur gear transmission and / or a differential. A supply point is understood, for example, to be a suction area of ​​an oil pump.

[0015] The invention is based on the recognition that in dynamic driving situations, such as when driving on a slope, accelerating, braking, cornering, etc., and when actively filling transmission components with oil, oil can enter the separating housing or the transmission chamber from the oil sump. In order to avoid additional drag losses and ensure an adequate oil supply, the oil must be drained from the separating housing and fed back to the oil sump. In addition, the transmission components must also be lubricated in a targeted manner.

[0016] The advantage of the present invention is that the oil carried by the output wheel can be delivered to the individual transmission components in a targeted manner by means of the first oil guide contour, and at the same time the transmission chamber can be deoiled in a simple manner. Thus, a transmission with an improved lubrication concept is proposed, wherein the first oil guide contour can be used to passively supply oil to the individual transmission components. In addition, drag losses and oil foam formation within the transmission chamber are significantly reduced, whereby the efficiency of the transmission can be significantly improved.

[0017] In a specific design of the present invention, the first oil guide profile is constructed as a multi-stage oil guide profile. For this purpose, the first oil guide profile has at least two or exactly two oil guide stages arranged one after another in terms of flow technology, through which a partial amount of oil transported by the output wheel can be transported to different oil injection locations. In particular, at least two oil guide stages are arranged one after another in the oil flow generated by the output wheel, so that a partial amount of oil transported by the output wheel can be transported to the first oil injection location via the first oil guide stage, and another partial amount of oil or residual oil can be transported to the second oil injection location via the second oil guide stage, etc. Preferably, the oil flow path is divided into a plurality of partial flow paths by the oil guide stages. In other words, the partial oil volume transported therein is derived via these oil guide stages. For example, most of the oil volume transported therein, especially more than 50%, can be derived via the first oil guide stage. Simply put, the oil guide stage at least partially absorbs the excess oil carried in the circumferential direction. In particular, the first oil guide contour has at least two or exactly two oil guide stages, preferably exactly three oil guide stages, in the circumferential direction relative to the rotation axis of the output gear and / or the differential case. Thus, multiple oiling locations can be passively supplied with oil via the multi-stage oil guide contour. Depending on the priorities, multiple oiling locations can also be supplied with different amounts of oil via the arrangement of the respective oil guide stages.

[0018] In a specific embodiment, it is provided that at least one or exactly one oil guide stage is formed by a first oil planer, which is arranged adjacent to the drive wheel. In particular, the oil planer directly cooperates with the driven wheel when the driven wheel is moved, entraining the oil. The first oil planer is preferably provided to separate at least a part, in particular a major part, of the oil flow generated by the driven wheel and to convey it to one of the oiling points, in particular the first oiling point. The first oil planer can be arranged at the upper side of the driven wheel in a prescribed installation position, in particular between the 9 o'clock position and the 12 o'clock position. In particular, the first oil planer is arranged substantially or exactly at the 11 o'clock position.

[0019] According to this embodiment, the first oil planing section has a shearing edge facing the output wheel for separating a part of the oil volume and an oil guide section for conveying the part of the oil volume to one of the oil filling locations, in particular the first oil filling location. In particular, the oil volume conveyed by the output wheel is at least partially separated from the output wheel by means of the first oil planing section under the action of the shearing edge, wherein the separated oil is discharged to the first oil filling location via the oil guide section. Preferably, the shearing edge extends substantially or exactly transversely to the direction of rotation and / or in the axial direction relative to the axis of rotation. Particularly preferably, the shearing edge extends in the axial direction over the entire width of the output wheel. The oil guide section can be formed by a partially open or closed channel, through which the separated oil is guided and / or redirected at least once. Thus, the first oil planing section ensures that at least a part of the oil volume conveyed in the circumferential direction is separated by the shearing edge and conveyed to the first oil filling location. By using the oil planing section, the amount of oil discharged can be selectively influenced in a simple manner depending on the arrangement relative to the output wheel.

[0020] In one embodiment, it is provided that the first oil filling point is assigned to the differential case, wherein the oil guide connects the shearing edge in terms of flow technology to a drip edge arranged above the differential case. In particular, a portion of the oil volume conducted away via the first oil plane can drip onto the differential case via the drip edge radially from above relative to the axis of rotation. Preferably, the drip edge is arranged at the end of the oil guide so that the separated oil can be conducted away from the oil plane in a defined manner. In particular, the drip edge is arranged in the center of the differential case and / or the bearing pin in the axial direction relative to the axis of rotation. Alternatively or optionally supplementarily, the drip edge is arranged at the upper side of the differential case in a prescribed installation position and / or substantially or exactly at the 12 o'clock position. Thus, an insulating shell is proposed, which enables a targeted supply of oil to the differential case, thereby ensuring sufficient oil filling of the differential case, preferably the compensating wheel.

[0021] In a further development, it is provided that the second oil planing section forms at least one or exactly one further oil discharge stage, which is arranged fluidically downstream of the first oil planing section adjacent to the output wheel. In particular, the first oil planing section and the second oil planing section are arranged offset or spaced apart from one another in the circumferential direction relative to the axis of rotation of the output wheel. The second oil planing section is preferably provided to separate at least a portion of the residual oil flow downstream of the first oil planing section and to convey it to one of the oiling points, in particular the second oiling point. The second oil planing section can be arranged in a prescribed installation position on the upper side of the output wheel, in particular between the 12 o'clock position and the 3 o'clock position. In particular, the second oil planing section is arranged substantially or exactly at the 1 o'clock position.

[0022] According to this improved solution, the second oil planing section has a shearing edge facing the output wheel for separating out a further partial oil volume or residual oil volume and an oil guide for conveying the partial oil volume or residual oil volume to one of the oiling locations, in particular the second oiling location. In particular, the residual oil volume conveyed by the output wheel is at least partially separated from the output wheel by means of the second oil planing section under the action of the shearing edge, wherein the separated oil is discharged to the second oiling location via the oil guide. Preferably, the shearing edge of the second oil planing section extends parallel to and / or in the same direction as the shearing edge of the first oil planing section. Particularly preferably, the shearing edge of the second oil planing section extends in the axial direction over the entire width of the output wheel. The oil guide of the second oil planing section can be formed by a partially open or closed channel, through which the separated oil is guided and / or redirected at least once. Thus, at least a part of the residual oil volume can be used for a further oiling location in a simple manner by means of the second oil planing section.

[0023] In another specific embodiment, it is provided that the differential case is rotatably supported in the transmission housing via at least one or exactly one, preferably exactly two differential case bearings. In principle, the differential case bearings can be constructed as sliding bearings, but are preferably constructed as rolling bearings. Preferably, the differential case bearings are supported on the differential case in the radial direction on the one hand and on the transmission housing, in particular on the housing section, on the other hand. In particular, the two differential case bearings are spaced apart from each other in the axial direction relative to the axis of rotation. Preferably, the output wheel is arranged between the two differential case bearings on the differential case. The second oil filling point is assigned to at least one of the differential case bearings, wherein the oil guide connects the shear edge to the drip edge arranged above the differential case bearing in terms of flow technology. Preferably, one of the differential case bearings is arranged inside the isolation shell, and the other differential case bearing is arranged outside the isolation shell, wherein at least the differential case bearing arranged outside the isolation shell can be supplied with oil via the second oil guide stage. In principle, the oil can drip directly from the drip edge onto the differential carrier bearing. Alternatively, the oil dripping from the drip edge can be supplied to the differential carrier bearing via a housing segment. For example, the transmission housing or the housing segment can have one or more lubrication openings in the region of the differential carrier bearing, preferably in the region of the bearing seat, via which the oil can be supplied to the differential carrier bearing. Thus, an insulating housing is proposed, in which excess oil or a further partial amount of oil can be used for lubrication and / or cooling of the differential carrier bearing. As a result, the service life of at least one differential carrier bearing can be improved or extended.

[0024] In a further embodiment, at least one or exactly one oil guide stage is formed by a throw-off contour, which is arranged adjacent to the output wheel. In principle, the throw-off contour can be located upstream of the first and / or second oil planing section, so that a partial amount of oil is firstly thrown off via the throw-off contour and then a further partial amount of oil or a residual amount of oil is separated off via the first and / or second oil planing section. Alternatively, the throw-off contour is located downstream of the first and / or second oil planing section, so that a partial amount of oil is firstly separated off via the first and / or second oil planing section and then a further partial amount of oil or a residual amount of oil is thrown off via the throw-off contour. In particular, the throw-off contour is arranged at one side of the output wheel in a prescribed installation position, preferably between the 8 o'clock position and the 10 o'clock position, preferably substantially or exactly in the 9 o'clock position.

[0025] According to the present design, the throwing-off profile has a throwing-off edge away from the output wheel, which is constructed and / or suitable for throwing off a part of the oil quantity to at least one or exactly one oiling point. In particular, the throwing-off profile is used to convey or throw off the residual oil quantity in the isolation shell after the first and / or second oiling section in the circumferential direction to one or more transmission components in a targeted manner. Preferably, the throwing-off edge ensures that the oil volume carried by the output wheel is thrown off substantially radially and / or tangentially relative to the direction of rotation. Preferably, the throwing-off edge extends substantially or exactly transversely to the direction of rotation and / or in the axial direction relative to the axis of rotation. Particularly preferably, the throwing-off edge extends in the axial direction over the entire width of the output wheel. In particular, the isolation shell is interrupted in the circumferential direction to form the throwing-off edge. Therefore, the excess oil in the isolation shell can be conveyed in a simple manner in a targeted manner to one or more transmission components, in particular a cylindrical gear transmission, by means of the throwing-off profile.

[0026] In another specific embodiment, the third oil filling point is assigned to the meshing area of ​​the drive element and / or the output wheel, wherein the casting edge is arranged below the meshing area. In particular, due to the acting casting force, the oil is cast away in the direction of the meshing area via the casting edge. In particular, the casting edge is arranged below the meshing area of ​​the output wheel and the intermediate wheel. Due to the casting force caused by the rotation of the output wheel, the oil can preferably be separated or cast away at the casting edge in the direction of the meshing area. In this way, passive meshing cooling of the spur gear transmission can also be achieved. In particular, the flow path is thus divided into a plurality of partial flow paths, wherein a first partial flow path extends via a first oiling section to a first oiling point, a second partial flow path extends via a second oiling section to a second oiling point, and a third partial flow path extends via a casting contour to a third oiling point.

[0027] In a further embodiment, it is provided that the separating housing has a further oil-conducting contour, wherein the oil located in the separating housing can be conveyed directly from the separating housing along the further oil-conducting contour into the oil sump by the rotation of the differential case. In particular, the further oil-conducting contour is used to return the oil supplied to the differential gear via the oil-conducting contour to the oil sump after filling and / or to return excess oil to the oil sump in a targeted manner. Preferably, the conveying effect of the differential case is utilized in such a way that the differential case, during rotation, entrains at least part of the oil located in the separating housing or the gear chamber via the outer contour. Preferably, the further oil-conducting contour is arranged in the oil flow generated by the differential in such a way that a large part of the oil picked up by the differential case is discharged into the oil sump via the further oil-conducting contour. Preferably, the further oil-conducting contour is designed as a single-stage oil-conducting contour. In particular, the further flow path extends parallel to the flow path from the differential case via the further oil-conducting contour into the oil sump. The efficiency in the region of the differential can thus be further optimized by means of the further oil-conducting contour, since drag losses due to excess oil are prevented.

[0028] In a specific embodiment, it can be provided that the further oil guide contour is formed by at least one or precisely one further oil plane, which is arranged adjacent to the differential case. In particular, the further oil plane directly cooperates with the oil carried by the differential case during its movement. The further oil plane is preferably provided to separate at least a part, in particular a major part, of the oil flow generated by the differential case and to convey it directly to the oil sump. The further oil plane can be arranged at the upper side of the differential case in a prescribed installation position, in particular between the 9 o'clock position and the 3 o'clock position, preferably in the 12 o'clock position. The further oil plane can have a shearing edge facing the differential case for separating the oil and an oil guide for conveying the oil to the oil sump. In particular, the oil volume conveyed by the differential case is at least partially separated from the differential case by means of the further oil plane under the action of the shearing edge, wherein the separated oil is discharged directly into the oil sump via the oil guide. Preferably, the shearing edge extends substantially or exactly transversely to the direction of rotation and / or in the axial direction relative to the axis of rotation. The oil guide can be formed by a partially open or closed channel, through which the separated oil is guided and / or redirected at least once. For example, the amount of oil conducted via the further oil-shaving section can drip into the oil sump radially relative to the axis of rotation after the oil guide. Thus, the further oil-shaving section ensures that at least a portion of the oil volume conveyed in the circumferential direction through the differential case is separated by the shearing edge and supplied to the oil sump.

[0029] Alternatively or optionally in addition, it is provided that the transmission housing has a second oil-conducting contour, wherein the oil located in the separating housing can be conveyed along the second oil-conducting contour directly into the oil sump and / or into at least one or exactly one of the oil filling points by the rotation of the transmission wheel of the spur gear transmission. In particular, the second oil-conducting contour is used to convey the oil supplied to the spur gear transmission via the first oil-conducting contour to at least one further oil filling point after the oil filling, and / or to return excess oil in a targeted manner to the oil sump. Preferably, the conveying effect of one or more transmission wheels of the spur gear transmission is utilized in such a way that during the rotation, these transmission wheels carry away at least a portion of the oil located in the separating housing or the transmission chamber via the outer contour. Preferably, the second oil-conducting contour is arranged in the oil flow generated by the spur gear transmission in such a way that a large portion of the oil picked up by at least one transmission wheel is discharged into the oil sump or into the further oil filling point via the second oil-conducting contour. The second oil-conducting contour can be designed as a single-stage or multi-stage oil-conducting contour. In particular, the second flow path extends parallel to the first flow path and / or the further flow path from the at least one transmission wheel via the second oil-conducting contour directly to the oil sump and / or the at least one further oil filling point. Thus, the second oil-conducting contour makes it possible to further optimize the efficiency in the region of the spur gear transmission, since drag losses due to excess oil are prevented.

[0030] In a specific embodiment, it is provided that the second oil guide profile is constructed as a multi-stage oil guide profile. For this purpose, the second oil guide profile has at least two or exactly two oil guide stages arranged one after the other in terms of flow technology, through which a partial amount of oil and / or a residual amount of oil at at least one or exactly one oil filling point can be directly conveyed to the oil pool, in particular, at least two oil guide stages are arranged one after the other in the oil flow generated by the intermediate wheel, so that the partial amount of oil conveyed by the intermediate wheel is conveyed to another oil filling point via the first oil guide stage, while the residual amount of oil is conveyed directly to the oil pool via the second oil guide stage. However, optionally, the second oil guide profile can also have another oil guide profile in order to drain the partial amount of oil conveyed by the intermediate wheel to another oil filling point. In particular, the second oil guide profile has at least two or exactly two oil guide stages in the circumferential direction relative to the rotation axis of the output wheel and / or the differential case. Therefore, oil can be passively supplied to another oil filling point via the multi-stage second oil guide profile.

[0031] In a specific embodiment, it is provided that at least one or exactly one oil conducting step of the second oil conducting contour is formed by an oil shaving section, which is arranged adjacent to the intermediate wheel. In particular, the oil shaving section cooperates with the oil carried by the intermediate wheel during its movement. The oil shaving section is preferably provided to separate at least a part, in particular a major part, of the oil flow generated by the intermediate wheel and to convey it directly to an oil sump or another oiling point. The oil shaving section can be arranged at the bottom side of the intermediate wheel in a prescribed installation position, in particular between the 3 o'clock position and the 9 o'clock position, preferably in the 6 o'clock position. The oil shaving section can have a shearing edge facing the intermediate wheel for separating the oil and an oil guide for conveying the oil to an oil sump or another oiling point. In particular, the oil volume conveyed by the intermediate wheel is at least partially separated from the intermediate wheel by means of the oil shaving section under the action of the shearing edge, wherein the separated oil is discharged directly to the oil sump or another oiling point via the oil guide. Preferably, the shearing edge extends substantially or exactly transversely to the direction of rotation and / or in an axial direction relative to the axis of rotation.

[0032] Alternatively or optionally in addition, it is provided that at least one or exactly one oil guide stage of the second oil guide profile is formed by a throw-off profile, which is arranged adjacent to the intermediate wheel. In particular, the throw-off profile is used to throw away a partial oil amount or a residual oil amount in a targeted manner into the oil collection area. In principle, the throw-off profile can be located upstream of the oil-shaving section, so that a partial oil amount is firstly thrown away via the throw-off profile, and then a further partial oil amount or a residual oil amount is separated via the oil-shaving section. Alternatively, the throw-off profile is located downstream of the oil-shaving section, so that a partial oil amount is firstly separated via the oil-shaving section, and then a further partial oil amount or a residual oil amount is thrown away via the throw-off profile. In particular, the throw-off profile is arranged in a prescribed installation position on one side of the output wheel, preferably between the 8 o'clock position and the 10 o'clock position, preferably substantially or exactly in the 9 o'clock position. In particular, the oil collecting area is used to collect at least a portion of the oil separated in the transmission housing and then to deliver it in a targeted manner, for example via one or more housing holes to an oil filling point or directly to an oil sump. The throw-off profile can have a throw-off edge remote from the intermediate wheel, which is constructed and / or suitable for throwing a part of the oil quantity directly into at least one or exactly one oil filling point and / or into the oil collecting area. Preferably, the throw-off edge ensures that the oil volume carried by the output wheel is thrown out substantially radially and / or tangentially relative to the direction of rotation. In particular, the throw-off edge is formed directly on the transmission housing, preferably in an integral manner.

[0033] In another embodiment, the separating shell has at least one or exactly one oil delivery opening, which is constructed and / or suitable for active oil delivery by means of an oil pump. In particular, the oil delivery opening is connected and / or can be connected to the oil pump in terms of flow technology. Preferably, the oil pump is connected to the oil pool in terms of flow technology on the suction side, and / or is connected to the oil delivery opening in terms of flow technology on the pressure side, so that oil is transported from the oil pool to the oil delivery opening via the oil pump. At least one oil delivery opening leads to the meshing area of ​​the drive member and / or the output wheel. Preferably, at least one first oil delivery opening leads to the first meshing area between the drive wheel and the intermediate wheel, and / or at least one second oil delivery opening leads to the second meshing area between the output wheel and the intermediate wheel. In particular, active oil delivery to the meshing area between the spur gears of the spur gear transmission can be achieved via the oil delivery opening, wherein the delivered oil is collected in the separating shell and delivered to one or more oil injection locations via the output wheel and at least the first oil guide contour. Therefore, particularly effective and reliable lubrication of the transmission components is ensured.

[0034] In a specific embodiment, it is provided that the isolation shell has a first shell section surrounding the output wheel and a second shell section surrounding the differential. The shell section is preferably used on the one hand to isolate the spur gear transmission and the differential from the oil pool, and on the other hand to guide the oil flow generated by the spur gear transmission and the differential during operation. In particular, the first and second shell sections are made in one piece, preferably made of a common material section. For example, the isolation shell can be constructed as a sheet metal forming component or as a plastic injection molding component. Preferably, the first shell section has a contour that matches the output wheel, preferably the external toothing, at least in sections. Alternatively or optionally supplemented, the second shell section has a contour that matches the differential, preferably the differential case, at least in sections.

[0035] According to this embodiment, it is provided that at least the second shell segment completely surrounds the differential. This means that the second shell segment is designed to be closed in the circumferential direction. Preferably, the first shell segment is designed to be interrupted in the circumferential direction at least in the meshing area and / or to form the casting profile. For example, the second shell segment extends in the circumferential direction over an angle range of more than 180 degrees, preferably more than 270 degrees. Particularly preferably, the first oil-shaving portion and / or the second oil-shaving portion and / or the casting profile are constructed on the inner circumference of the first shell segment. Alternatively or optionally supplemented, a further oil-shaving portion is constructed on the inner circumference of the second shell segment. Optionally supplemented, the insulating shell has at least one or exactly one further shell segment, which surrounds the drive wheel and / or the intermediate wheel at least in sections. For example, the further shell segment extends in the circumferential direction over an angle range of more than 45 degrees, preferably more than 90 degrees, in particular more than 180 degrees. Preferably, at least one oil delivery opening is introduced into the further shell segment. The spur gear and the differential can be completely isolated from the oil sump at least in static driving situations by the surrounding housing section, wherein the housing section also enables the oil flow to be controlled during operation.

[0036] In another embodiment, it is provided that the insulating shell is fixed in a form-locking manner between the first and second housing sections of the transmission housing at least in the axial direction relative to the axis of rotation of the differential. In particular, in the axial direction and optionally in the radial direction, the insulating shell is supported in a form-locking manner on the first housing section with the first housing section and in a form-locking manner on the second housing section with the second housing section. Particularly preferably, the insulating shell, preferably the second housing section, has a radial shoulder around the axis of rotation, via which the insulating shell is supported on the second housing section at least at the second housing section in the axial and radial direction and / or is coaxially centered relative to the axis of rotation. The two housing sections can be constructed as two independent housing parts, which are preferably connected to each other in the axial direction relative to the axis of rotation, for example via a screw connection. Thus, a particularly simple and inexpensive solution for fastening the insulating shell in the transmission housing is proposed, which can be realized without the need for additional fastening means.

[0037] According to the implementation scheme, it is provided that the first shell section is supported on the first housing section in an oil-tight manner at least below the oil level, and the second shell section is supported on the second housing section in an oil-tight manner at least below the oil level. In particular, the isolation shell is supported on both sides of the transmission housing in an axial and / or radial direction in a sealed manner relative to the rotation axis, preferably on two housing sections. Preferably, the first shell section is sealed on the first housing section at least in sections in the axial direction via a first sealing device. Preferably, the second shell section is sealed on the second housing section in an axial and / or radial direction relative to the rotation axis. For example, the first and / or second sealing device can be constructed as an elastomeric seal. Particularly preferably, the spur gear transmission and / or the differential is completely surrounded between the two housing halves and / or isolated relative to the oil pool by the isolation shell. Therefore, an isolation shell is proposed, which prevents leakage flow between the isolation shell and the transmission housing from the oil pool to the transmission cavity in a simple manner, especially in static driving conditions. Furthermore, the insulating shell can be used in a simple manner as a sealing component for sealing the transmission chamber.

[0038] Another subject of the invention relates to a motor vehicle with a transmission as described above. In particular, the vehicle is designed as a motor vehicle, a commercial vehicle or a rail vehicle. Particularly preferably, the vehicle is designed as an electric vehicle. In particular, the transmission is arranged in the power path in the drive train of the vehicle between the drive unit, in particular the electric motor, and at least one wheel. Particularly preferably, the transmission is integrated into an electric axle of the vehicle, in particular an electric front axle or a rear axle. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Other features, advantages and effects of the present invention are derived from the following description of preferred embodiments of the present invention.

[0040] Figure 1 A schematic diagram of a vehicle having a transmission mechanism as an embodiment of the present invention is shown;

[0041] Figure 2 A perspective view of a spur gear transmission of the transmission mechanism is shown;

[0042] Figure 3 A schematic cross-sectional view of the transmission mechanism along the rotation axis is shown;

[0043] Figure 4 shows another schematic cross-sectional view of the transmission mechanism along the axis of rotation;

[0044] Figure 5 A detailed perspective view of the insulating housing in the transmission mechanism in the installed state is shown;

[0045] Figure 6A three-dimensional diagram of the isolation shell is shown;

[0046] Figure 7 A further detailed view of the insulation shell in the installed state is shown;

[0047] Figure 8 A detailed view of the transmission housing of the transmission mechanism in the installed state is shown;

[0048] Fig. 9 A further detailed view of the transmission housing is shown in the installed state. DETAILED DESCRIPTION

[0049] Figure 1 A highly schematic illustration of a vehicle 1 is shown as an embodiment of the invention. The vehicle 1 is designed as an electrically operated motor vehicle, for example.

[0050] The vehicle 1 has an electric axle, which is formed by a drive unit 2 and a transmission 3. The drive unit 2 is designed, for example, as an electric machine which generates an electric drive torque during operation. The transmission 3 has a spur gear 4 and a differential 5, wherein the drive torque is transmitted via the spur gear 4 to the differential 5 and then distributed via the differential 5 to two wheels 6a, 6b.

[0051] The transmission 3 has a drive shaft 7 as a transmission input and two driven shafts 8a, 8b as transmission outputs. The drive shaft 7 is connected to the drive unit 2 in terms of drive technology, and the two driven shafts 8a, 8b are connected to one of the wheels 6a, 6b respectively. Via the two driven shafts 8a, 8b, the drive torque or drive power can be at least partially transmitted from the differential 5 in the direction of the driven wheels 6a, 6b. Therefore, the differential 5 is designed as an axle differential.

[0052] The spur gear transmission 4 is configured as a reduction gear transmission, for example, which has a transmission ratio of i>1. In other words, the spur gear transmission 4 is used for reduction transmission. For this purpose, the spur gear transmission 4 can be configured as a two-stage spur gear transmission, for example. Therefore, the spur gear transmission 4 is suitable for increasing the torque generated by the drive unit 2 or reducing the rotational speed.

[0053] like Figure 2 As shown in FIG, the transmission 3 has a transmission housing 9 for accommodating the spur gear transmission 4 and the differential 5. The transmission housing 9 delimits a wet chamber that is sealed in an oil-tight manner relative to the environment. For example, the transmission housing 9 can be mounted on the drive unit 2 via a flange connection.

[0054] The spur gear transmission 4 has a drive wheel 10 and an output wheel 11 which are connected to the drive shaft 7 in a rotationally fixed manner, wherein the drive wheel 10 and the output wheel 11 are connected to each other in terms of drive technology via an intermediate wheel 12. In this case, the drive shaft 7 is guided into the transmission housing 9 on the drive side and thus forms the transmission input of the transmission 3. The drive wheel 10, the output wheel 11 and the intermediate wheel 12 are each designed as a spur gear which carries a spur gear toothing on their circumference.

[0055] For example, the intermediate wheel 12 is designed as a stepped wheel, wherein the intermediate wheel 12 has two different tip circle diameters for this purpose. To form a first transmission stage, the drive wheel 10 is meshed with a first intermediate wheel section of the intermediate wheel 12, wherein for a reduced transmission, the first intermediate wheel section has a larger tip circle diameter than the drive wheel 10. To form a second transmission stage, the output wheel 11 is meshed with a second intermediate wheel section of the intermediate wheel 12, wherein for a further reduced transmission, the second intermediate wheel section has a smaller tip circle diameter than the output wheel 11.

[0056] like Figure 3 As shown in the figure, the differential 5 has a differential case 13 connected to the output wheel 11 in a rotationally fixed manner and a plurality of compensating wheels 14a, 14b rotatably supported in the differential case 13, which are rotatably supported in the differential case 12 via support pins 15a, 15b and are connected to the two driven shafts 8a, 8b in terms of transmission technology. Here, the two driven shafts 8a, 8b are guided out of the transmission housing 9 on the driven side and thus form the transmission output end of the transmission mechanism 3. The output wheel 11, the differential case 13 and the two driven shafts 8a, 8b are rotatably supported in the transmission housing 9 around the rotation axis 100.

[0057] For this purpose, the differential 5 has a first and a second differential case bearing 16a, 16b, via which the differential case 13 is rotatably supported in the transmission housing 8. For this purpose, the two differential case bearings 16a, 16b are each designed as rolling bearings, for example, via which the differential case 13 is supported on the transmission housing 9 in the radial direction with respect to the rotation axis 100. The two differential case bearings 16a, 16b are spaced apart from each other in the axial direction with respect to the rotation axis 100, wherein the driven gear 13 and the compensating gears 14a, 14b are axially arranged between the two differential case bearings 16a, 16b.

[0058] The transmission housing 9 is partially filled with transmission oil, wherein, in the static installed state of the transmission 3, a lubricating medium sump 17 with a lubricating medium level 18 is formed in the bottom region of the transmission housing 9. The transmission oil serves, for example, to lubricate and / or cool the transmission 3 and optionally the drive unit 2.

[0059] The transmission 3 has an isolating case 19 which is arranged in the transmission housing 8 and surrounds the spur gear 4 and the differential 5 at least below the oil level 18 in order to isolate them from the oil sump 17. This prevents the driven gear 11 and the differential case 13 from being directly immersed in the oil sump 17, thereby reducing the drag losses of the transmission 3.

[0060] The insulating housing 19 has a first and a second housing section 20a, 20b, wherein the first housing section 20a surrounds the spur gear and the second housing section 20b surrounds the differential case 13. Here, the first housing section 20a has a circumferential geometry that matches the output gear 11, and the second housing section 20b has a circumferential geometry that matches the differential case 13. As a result, the amount of play between the output gear 11 and the first housing section 20a or between the differential case 13 and the second housing section 20b can be minimized.

[0061] The transmission housing 9 has a first and a second housing section 21a, 21b, which are connected to one another, for example screwed, in an axial direction relative to the rotation axis 100, for example in a radial plane of the rotation axis 100. The insulating shell 19 is arranged between the first and second housing sections 21a, 21b in an axially positively locking manner relative to the rotation axis 100, wherein the first housing section 20a is supported in an axially positively and / or non-positively locking manner on the first housing section 21a, and the second housing section 20b is supported in an axially opposite direction in an axially positively and / or non-positively locking manner on the second housing section 21b.

[0062] The second shell section 20b has a radial shoulder 22 at the end side about the rotation axis 100, via which the second shell section 20b additionally rests on the second housing section 21b in the radial direction relative to the rotation axis 100. For example, the separating shell 19 can be centered on the second housing section 21b coaxially with respect to the rotation axis 100 via the radial shoulder 22. Furthermore, the separating shell 19 is supported in a fluid-tight manner on the respective housing section 21a, 21b, for example in an oil-tight manner via an elastomeric seal, at least in the region of the oil sump 19 or below the oil level 18.

[0063] In dynamic driving operation, oil enters the separating housing from the oil sump 17, thereby increasing the drag losses of the transmission 3. The first housing section 20a has a larger outer diameter than the second housing section 20b, wherein the second housing section 20b has an inner circumferential side that is inclined in the direction of the first housing section 20a and is preferably conical, so that the oil that enters the separating housing 19 is collected in the bottom area of ​​the first housing section 20a and can be carried along in the circumferential direction by the driven gear 11. This is achieved in that the driven gear 11 picks up the oil with its spur gear meshing when rotating about the rotation axis 100 and then carries it along in the circumferential direction.

[0064] In order to guide the oil collected in the isolation shell 19 out again, the isolation shell 19 has a multi-stage first oil guide contour 23a on the inner circumference of the first shell section 20a. By the rotation of the drive wheel 11, the oil collected in the first shell section 20a can be transported from the isolation shell 19 to multiple oil injection positions 25a, 25b, 25c of the transmission mechanism 3 along the first oil guide contour through multiple oil guide stages 24a, 24b, 24c. The first oil flow path 101a of the oil flow generated by the output wheel 11 is divided into multiple partial flow paths 102a, 102b, 102c by the first oil guide contour 23a. Figures 3 to 7 As schematically indicated by arrows in FIG. 1 , when the driven wheel 11 rotates, a partial amount of the oil volume transported by the driven wheel 11 is respectively directed to the respectively associated oil filling point 25 a , 25 b , 25 c .

[0065] like Figure 3 As shown in FIG, the first oil guide contour 23a has a first oil guide stage 24a, via which a first partial oil quantity is separated along a first partial flow path 102a to a first oil filling point 25a. The first oil filling point 25a is assigned to the differential case 13, wherein the first partial flow path 102a therefore extends from the driven gear 11 via the first oil guide contour 23a to the differential case 13, preferably to the bearing pins 15a, 15b, in order to cool and / or lubricate the compensating gears 14a, 14b.

[0066] like Figure 4 As shown in FIG. 1 , the first oil guide contour 23a has a second oil guide stage 24b, via which the second partial oil quantity is separated along the second partial flow path 102b to the second oil injection point 25b. The second oil injection point 25b is assigned to the second differential case bearing 16b, wherein the second partial flow path 102b therefore extends from the driven gear 11 via the first oil guide contour 23a to the second differential case bearing 16b in order to cool and / or lubricate the second differential case bearing 16b.

[0067] like Figure 5As shown in FIG. 1 , the first oil guide stage 24a is formed by a first oil planing section 26a, and the second oil guide stage 24b is formed by a second oil planing section 26b, wherein the second oil planing section 26b is arranged spaced apart after the first oil planing section 26a in the rotation direction 103 of the output wheel 11 or in the first oil flow path 101a. The two oil planing sections 26a, 26b each have a shearing edge 27 facing the output wheel 11 and an oil guide section 28 connected to the shearing edge 27, along which the respective partial flow paths 102a, 102b extend to the respectively assigned oil filling points 25a, 25b. Here, the oil volume transported by the output wheel 11 is at least partially separated from the output wheel 11 by means of the oil planing sections 26a, 26b under the action of the shearing edge 27, wherein the separated oil is guided to the respective oil filling points 25a, 25b along the respective partial flow paths 102a, 102b via the oil guide section 28.

[0068] like Figure 3 As shown in FIG. 1 , the oil guide 28 of the first oil guide stage 24a connects the drip edge 29 with the shear edge 27, wherein the separated oil is guided along the oil guide 28 to the drip edge 29. The drip edge 29 is arranged above the differential case 13 in the radial direction relative to the rotation axis 100, preferably in the 12 o'clock position, so that the partial amount of oil separated along the first partial flow path 102a can drip from above onto the differential case 13 or the bearing pins 15a, 15b. The first partial flow path 102a is redirected several times by the oil guide 28 in order to divert the oil in the direction of the differential case 13.

[0069] The oil guide 28 of the first lubrication stage 24a has a first oil guide section 30a and a second oil guide section 30b, wherein the first oil guide section 30a redirects the first partial flow path 102a axially at the first housing section 20a in the direction of the differential case 13, and the second oil guide section 30b redirects the first partial flow path 102a radially at the first housing section 20a in the direction of the differential case 13. For this purpose, the shearing edge 27 is arranged at the beginning of the first oil guide section 30a, and the dripping edge 29 is arranged at the end of the second oil guide section 30b.

[0070] like Figure 4As shown in FIG. 1 , the oil guide 28 of the second oil guide stage 24b connects the drip edge 29 with the shear edge 27, wherein the separated oil is guided along the oil guide 28 to the drip edge 29. The drip edge 29 is arranged above the second housing section 21b in the radial direction relative to the rotation axis 100 at the location of the second differential carrier bearing 16b, so that the partial amount of oil separated along the second partial flow path 102b can be supplied to the second differential carrier bearing 16b from above via the second housing section 21b. For this purpose, the second housing section 21b has at least one or exactly one lubrication opening 31, via which the oil guided along the second partial flow path 102b is guided directly to the second oil filling point 25b, in particular to the bearing seat of the second differential carrier bearing 16b. The second partial flow path 102b is redirected multiple times by the oil guide 28 in order to redirect the oil in the direction of the second differential carrier bearing 16b or to the at least one lubrication opening 31.

[0071] The oil guide 28 of the second lubrication stage 24b has a first oil guide section 30a, a second oil guide section 30b and a third oil guide section 30c, wherein the first oil guide section 30a redirects the second partial flow path 102b axially at the first housing section 20a in the direction of the second differential housing bearing 16b, the second oil guide section 30b redirects the second partial flow path 102b radially at the first housing section 20a in the direction of the second differential housing bearing 16b, and the third oil guide section 30c redirects the second partial flow path 102b axially at the second housing section 20b in the direction of the second differential housing bearing 16b. For this purpose, the shearing edge 27 is arranged at the beginning of the first oil guide section 30a, and the dripping edge 29 is arranged at the end of the third oil guide section 30c.

[0072] like Figure 6 As shown in FIG. 1 , at least the second housing section 20b is designed to be closed around the differential 5, so that the differential 5 is completely surrounded by the isolation housing 19 or the second housing section 20b between the two housing sections 21a, 21b. In order to guide the excess oil supplied to the differential 5 via the oil filling points 25a, 25b from the isolation housing 19, the second housing section 20b has another oil guide contour 32, and the residual oil is directly separated into the oil flow path 104 via the other oil guide contour. Figure 3 The oil sump 17 is described. This is achieved in that the differential carrier 14 picks up the oil with its outer contour when rotating about the axis of rotation 100 and then carries it along in the circumferential direction. Thus, a further oil flow path 104 extends from the differential carrier 14 via a further oil guide contour 32 to the oil sump 17.

[0073] The further oil guide contour 32 is formed by a further oil plane 26c, which is formed on the inner circumference of the second housing section 20b. Like the two oil planes 26a, 26b, the further oil plane 26c also has a shearing edge 27 facing the differential case 13 and an oil guide 28 connected to the shearing edge 27, along which the further oil flow path 104 extends into the oil sump 17. In this case, the oil volume conveyed by the differential case 13 is at least partially separated from the differential case 13 by means of the further oil plane 26c under the action of the shearing edge 27, wherein the separated oil is guided along the further oil flow path 104 via the oil guide 28 into the oil sump 17.

[0074] like Figure 7 As shown in FIG. 1 , the multi-stage first oil guide profile 23 a has a third oil guide stage 24 c, via which a further partial oil quantity is separated along a third partial flow path 102 b to be given as follows. Figure 5 The third oil injection point 25c is assigned to the meshing region between the driven gear 11 and the intermediate gear 12, wherein the third partial flow path 102c extends from the driven gear 11 via the first oil guide contour 23a to the meshing region in order to cool and / or lubricate the driven gear 11 and the intermediate gear 12 in the meshing region.

[0075] For this purpose, the third oil guide stage 24c is formed by a throw-off profile 33, which is arranged at a distance before or after the first and second oil planing sections 26a, 26b in the direction of rotation 103 of the driven wheel 11. The throw-off profile 33 has a throw-off edge 34 facing away from the driven wheel 11, via which a partial amount of oil is thrown along the third partial flow path 102c to the third oiling location 25c. In this case, the oil volume conveyed from the driven wheel 11 is at least partially separated from the driven wheel 11 by means of the throw-off profile 33 under the action of the throw-off edge 34, wherein the separated oil is thrown radially and / or tangentially along the third partial flow path 102c with respect to the direction of rotation 103. For this purpose, the throw-off edge 34 is arranged in the radial direction below the meshing region with respect to the rotation axis 100, preferably at the 9 o'clock position, so that the partial amount of oil separated along the third partial flow path 102c can be thrown from below into the meshing region.

[0076] like Figure 7 As shown in , the insulating shell 19 also has further shell segments 20c, 20d, wherein the third shell segment 20c surrounds the intermediate wheel 12 in a segmented manner, and the fourth shell segment 20c surrounds the drive wheel 10 in a segmented manner. Here, the third shell segment 20c has a circumferential geometry that matches the intermediate wheel 12, in particular the two intermediate wheel segments, and the fourth shell segment 20c has a circumferential geometry that matches the drive wheel 10.

[0077] In order to supply oil to the meshing regions between the drive wheel 10 and the intermediate wheel 12 and between the output wheel 11 and the intermediate wheel 12, the two further housing sections 20c, 20d can each have an oil delivery opening 35, which opens into the respective meshing region. For example, the oil delivery openings 35 are fluidically connected to an oil pump, which delivers oil, preferably oil from the oil sump 17, into the meshing regions via the two oil delivery openings 35. As described above, excess oil can then be entrained by the output wheel 10 and distributed in the transmission housing 9 via the first oil guide contour 23a or the further oil guide contour 23b.

[0078] like Figure 8 and Fig. 9 As shown in FIG. 1 , the transmission housing 9, in particular the first housing section 21a, has a second oil guide contour 23b, via which the excess oil quantity conveyed together by the intermediate wheel 12 can be conveyed along the second oil flow path 101b from the separating housing 19 to the fourth oil filling position 25d and / or directly to the oil pool 17. This is achieved in the following manner, that is, the intermediate wheel 12 picks up the oil with its outer contour during rotation and then drives it in the circumferential direction. The second oil guide contour 23b can be constructed in multiple stages, wherein the second oil flow path 101b is schematically divided into a plurality of, preferably exactly two, partial flow paths 105a, 105b as indicated by arrows.

[0079] like Figure 8 As shown in FIG, the second oil guide contour 23b has a first oil guide stage 24a, via which a first partial oil quantity is separated along a first partial flow path 105a to a fourth oil filling point 25d. The fourth oil filling point 25d is assigned to the first differential case bearing 16a, wherein the first partial flow path 105a therefore extends from the intermediate gear 12 via the first oil guide stage 24a of the second oil guide contour 23b to the first differential case bearing 16a, in order to cool and / or lubricate the first differential case bearing 16a.

[0080] The first oil guiding stage 24a of the second oil guiding profile 23b is formed by a further throwing-off profile 33b having a throwing-off edge 34 facing away from the intermediate wheel 12, via which a partial amount of oil is thrown along a first partial flow path 105a into an oil collecting area 36. In this case, the oil volume conveyed by the intermediate wheel 12 is at least partially separated from the intermediate wheel 12 by means of the further throwing-off profile 33b under the action of the throwing-off edge 34, wherein the separated oil is thrown away along the first partial flow path 105a radially and / or tangentially to the direction of rotation 106.

[0081] The oil collecting area 36 is arranged adjacent to the throw-off contour 33 b so that part of the oil quantity thrown off via the throw-off edge 34 is guided via one or more oil guide surfaces 37 formed on the transmission housing 9 into the oil collecting area 36 and collected there. For example, the oil guide surface 37 can be formed as an inclined surface inclined in the direction of the oil collecting area 37, onto which the oil can be thrown and then flows into the oil collecting area 37 as schematically indicated by arrows.

[0082] The oil collecting area 36 is arranged offset from the throw-off edge 34 or is bounded by the throw-off contour 33b so that the oil collected in the oil collecting area 36 is simultaneously blocked by the throw-off contour 33b. At least one or exactly one housing hole 38 is arranged in the oil collecting area 36, ​​through which the oil in the oil collecting area 36 can flow to the fourth oil filling point 25d. Thus, the first partial flow path 105a extends from the intermediate wheel 12 via the further throw-off contour 33b and the oil collecting area 36 to the fourth oil filling point 25d.

[0083] like Fig. 9 As shown in FIG, the second oil guide profile 23b has a second oil guide stage 24b, via which the residual oil volume is separated along the second partial flow path 105b directly into the oil pool 17. Thus, the second partial flow path 105b extends from the intermediate wheel 12 via the second oil guide stage 24b of the second oil guide profile 23b into the oil pool 17.

[0084] The second oil-conducting step 24b of the second oil-conducting profile 23b is formed by a further oil-shaving section 26d, which is formed on the inner side of the first housing section 21a behind the further throw-off profile 33b in the direction of rotation 107 of the intermediate wheel 12. The further oil-shaving section 26d is a cast profile formed integrally on the first housing section 21a, which has a shearing edge 27 facing the intermediate wheel 12 and an oil guide 28 connected to the shearing edge 27, along which the second partial flow path 105b extends into the oil sump 17. In this case, the oil volume conveyed by the intermediate wheel 12 is at least partially separated from the intermediate wheel 12 by means of the further oil-shaving section 26d under the action of the shearing edge 27, wherein the separated oil is guided along the second partial flow path 105b via the oil guide 28 into the oil sump 17. For example, the shearing edge 27 is formed by a rib geometry extending tangentially to the intermediate wheel 12, and the oil guide 28 is formed by an outlet geometry connected to the rib geometry.

[0085] Reference numerals list

[0086] 1 Vehicle

[0087] 2 drive units

[0088] 3 Transmission mechanism

[0089] 4 cylindrical gear transmission

[0090] 5 Differential

[0091] 6a, 6b wheels

[0092] 7 Drive shaft

[0093] 8a, 8b driven shaft

[0094] 9 Transmission housing

[0095] 10 driving wheels

[0096] 11 Output wheel

[0097] 12 intermediate wheels

[0098] 13 Differential case

[0099] 14a, 14b compensation wheel

[0100] 15a, 15b support pin

[0101] 16a, 16b differential case bearing

[0102] 17 Oil Pool

[0103] 18 Oil level

[0104] 19 Isolation Shell

[0105] 20a-20c Shell segments

[0106] 21a, 21b Shell sections

[0107] 22 Radial shoulder

[0108] 23a, 23b Oil guide profile

[0109] 24a-24c oil guide grade

[0110] 25a-25d Oil filling area

[0111] 26a-26d Oil Planing Department

[0112] 27 Shear Edge

[0113] 28 Oil guide

[0114] 29 Dripping Edge

[0115] 30a-30c Oil guide section

[0116] 31 Lubrication opening

[0117] 32 Additional oil guide profiles

[0118] 33a, 33b Throwing profile

[0119] 34 Throwing Edge

[0120] 35 Oil delivery opening

[0121] 36 Oil Collection Area

[0122] 37 Oil guide surface

[0123] 38 Shell holes

[0124] 100 Rotation axis

[0125] 101a, 101b Oil flow path

[0126] 102a-102c Partial flow path

[0127] 103 Rotation direction

[0128] 104 Additional oil flow path

[0129] 105a, 105b Additional partial flow paths

[0130] 106 Rotation direction

Claims

1. A transmission mechanism (3) for a motor vehicle (1), the transmission mechanism having - Transmission housing (9), - a spur gear transmission (4) arranged in the transmission housing (9), wherein: The spur gear transmission (4) has a drive wheel (10) and an output wheel (11) which are connected to each other in terms of transmission technology. - a differential (5) arranged in the transmission housing (9), wherein the differential (5) comprises a differential case (13) connected to the output gear (11) in a rotationally fixed manner, and a plurality of compensating gears (14a, 14b) rotatably mounted in the differential case (13), - an oil sump (17) which defines the oil level (18) in the transmission housing (9) when the transmission (3) is in the static installed state, and - an isolating housing (19) arranged in the transmission housing (9), which surrounds the output wheel (11) and the differential housing (13) at least below the oil level (18) in order to isolate them from the oil sump (17), It is characterized in that The separating shell (19) has a first oil guide contour (23a), wherein oil in the separating shell (19) can be conveyed from the separating shell (19) along the first oil guide contour (23a) to at least one oil filling point (25a, 25b, 25c, 25d) of the transmission (3).

2. The transmission mechanism (3) according to claim 1, characterized in that: The first oil guiding profile (23a) is designed as a multi-stage oil guiding profile, wherein the first oil guiding profile (23a) has at least two oil guiding stages (24a, 24b, 24c) arranged one behind the other in terms of flow technology, via which partial quantities of oil can be conveyed to different oil filling locations (25a, 25b, 25c, 25d).

3. The transmission mechanism (3) according to claim 2, characterized in that: At least one oil guide stage (24a, 24b, 24c) is formed by a first oil planer (26a), which is arranged adjacent to the output wheel (11), wherein the first oil planer (26a) has a shearing edge (27) facing the output wheel for separating a partial amount of oil and an oil guide (28) for conveying the separated partial amount of oil to one of the oil filling locations (25a, 25b, 25c, 25d).

4. The transmission mechanism (3) according to claim 3, characterized in that: A first oil filling point (25a) is associated with the differential carrier (13), wherein the oil guide (28) connects the shearing edge (27) in terms of flow to a drip edge (29) arranged above the differential carrier (13).

5. The transmission mechanism (3) according to claim 3 or 4, characterized in that: At least one further oil-conducting stage (24a, 24b, 24c) is formed by a second oil-cutting section (26b), which is arranged flow-wise downstream of the first oil-cutting section (26a) and adjacent to the output wheel (11), wherein the second oil-cutting section (26b) has a shearing edge (27) facing the output wheel (11) for separating off a further partial amount of oil and an oil guide (28) for conveying the further partial amount of oil to one of the oiling locations (25a, 25b, 25c, 25d).

6. The transmission mechanism (3) according to claim 5, characterized in that: The differential case (13) is rotatably supported in the transmission housing (9) via at least one differential case bearing (16a, 16b), wherein a second oil filling point (25b) is associated with the differential case bearing (16a, 16b), wherein the oil guide (28) connects the shearing edge (27) in terms of flow to a drip edge (29) arranged above the differential case bearing (16a, 16b).

7. The transmission mechanism (3) according to any one of claims 2 to 6, characterized in that: At least one oil guide stage (24a, 24b, 24c) is formed by a throw-off contour (33), which is arranged adjacent to the output wheel (11), wherein the throw-off contour (33) has a throw-off edge (34) facing away from the output wheel (11) for throwing off a partial amount of oil to at least one of the oil filling points (25a, 25b, 25c, 25d).

8. The transmission mechanism (3) according to claim 7, characterized in that: The third oil filling point (24c) is assigned to a meshing region of the drive wheel (10) and / or the output wheel (11), wherein the throw-off edge (34) is arranged below the meshing region.

9. The transmission mechanism (3) according to any one of the preceding claims, characterized in that The insulating shell (19) has a further oil-conducting contour (32), wherein the oil in the insulating shell (19) can be conveyed directly from the insulating shell (19) along the further oil-conducting contour (32) into the oil sump (17) by the rotation of the differential carrier (13).

10. The transmission mechanism (3) according to any one of the preceding claims, characterized in that The transmission housing (9) has a second oil guide contour (23b), wherein the oil in the separating housing (19) can be transported directly from the separating housing (19) along the further oil guide contour (23b) into the oil sump (17) and / or at least one oil filling point (25a, 25b, 25c, 25d) by the rotation of the drive wheels (10, 11, 12) of the spur gear transmission (4).

11. The transmission mechanism (3) according to claim 10, characterized in that: The second oil guiding profile (23b) is designed as a multi-stage oil guiding profile, wherein the second oil guiding profile (23b) has at least two oil guiding stages (24a, 24b) arranged one behind the other in terms of flow technology, via which partial quantities of oil can be conveyed to oil filling points (25a, 25b, 25c, 25d) and / or directly into the oil sump (17).

12. The transmission mechanism (3) according to any one of the preceding claims, characterized in that The separating housing (19) has at least one oil delivery opening (35) for active oil delivery by means of an oil pump, wherein the oil delivery opening (35) opens into a meshing region of the drive wheel (10) and / or the output wheel (11).

13. The transmission mechanism (3) according to any one of the preceding claims, characterized in that The insulating housing (19) has a first housing section (20a) surrounding the driven gear (11) and a second housing section (20b) surrounding the differential housing (13), wherein at least the second housing section (20b) is designed to be closed all around.

14. The transmission mechanism (3) according to any one of the preceding claims, characterized in that The insulating shell (19) is fixed in a form-fitting manner between a first and a second housing section (21a, 21b) of the transmission housing (9) at least in the axial direction relative to the rotation axis (100) of the differential (5), wherein the first housing section (20a) is supported on the first housing section (21a) in an oil-tight manner at least below the oil level (18), and the second housing section (20b) is supported on the second housing section (21b) in an oil-tight manner at least below the oil level (18).

15. A motor vehicle (1) having a transmission (3) according to any one of the preceding claims.

Images