DE102019102078B3 - Gear arrangement - Google Patents

Abstract

Gear arrangement comprising: a housing arrangement (3), a first gear stage (6) with a first wheel (9) which can be driven to rotate about a first axis of rotation (B) and has a first center plane (E1), and a second gear stage (13) with a second wheel (15) which can be driven in rotation about a second axis of rotation (C) parallel to the first axis of rotation (B) and has a second center plane (E2), the first gear stage (6) and the second gear stage (13) with one another are connected to the drive and the first wheel (9) has an opposite direction of rotation to the second wheel (15), a separating element (28) which is arranged axially between the first center plane (E1) and the second center plane (E2), and lubricating oil which in the Calms down a lubricating oil idle level (L1), wherein a lubricating oil guide geometry (21) is arranged in axial overlap with the second wheel (15) and is designed in such a way that when the gear arrangement is in operation it is thrown off the second wheel (15) The lubricating oil is directed towards the first center level (E1).

Description

The present invention relates to a transmission arrangement for a motor vehicle, in particular for an electric drive.

In recent years, transmission arrangements for motor vehicles have been subject to ever increasing demands with regard to their efficiency, for example due to legal regulation. In addition, the gear arrangements must be usable in ever smaller installation space areas of the motor vehicles, so that they have increasingly compact architectures. Both aspects make adequate lubrication of the components in the gear arrangement difficult.

From the DE 11 2013 007 520 T5 A transmission arrangement for a motor vehicle is known, comprising: a first gearwheel and a second gearwheel which are drive-connected to one another; a lubricant fill that defines a lubricant level in a static installed state of the gear arrangement; a first reservoir which is arranged above the level of lubricant and can be filled with lubricant when the gear arrangement is driven by rotation of the first gear, a second reservoir which is arranged above the level of lubricant and can be filled with lubricant when the gear arrangement is driven by rotation of the second gear. The reservoirs are limited by a housing part and a cover element.

From the WO 2007/013642 A1 a transmission arrangement with a lower lubricant reservoir and two upper lubricant reservoirs is known. The upper lubricant stores are supplied with lubricant by the spray oil from two counter-rotating wheels of a gear arrangement, which are immersed in a common oil sump of the lower lubricant store. Due to the force of gravity, the lubricant flows from the upper lubricant stores to various bearing points of the gear arrangement.

From the DE 10 2015 013 973 A1 a lubricating oil assembly for a speed reducer is known. The lubricating oil assembly includes a housing with a sidewall, a reduction gear connected to an output shaft, and a collection container for receiving a part of a lubricating oil carried by the reduction gear. An oil passage for guiding the lubricating oil entrained by the reduction wheel to the collecting container is formed in the side wall. Furthermore, a rib extending in the radial direction is provided on the side wall for guiding the entrained lubricating oil. A groove is provided on an end edge of the rib, which is connected to a lubricating oil supply object.

The present invention is based on the object of proposing a gear arrangement which has an improved thermal operating behavior.

To achieve the object, a gear arrangement, in particular for an electric drive, is proposed, comprising: a housing arrangement; a first gear stage with a first wheel which can be driven to rotate about a first axis of rotation by a pinion of the first gear stage and has a first center plane; and a second gear stage with a second wheel which can be driven by a pinion of the second gear stage to rotate about a second axis of rotation parallel to the first axis of rotation and has a second center plane, the first gear stage and the second gear stage being accommodated in the housing arrangement and being drive-connected to one another and the first wheel has an opposite direction of rotation to the second wheel; a separator disposed axially between the first center plane and the second center plane; and lubricating oil, which is provided in the housing arrangement and defines a lubricating oil idle level in the calm state, wherein a lubricating oil guide geometry is arranged in axial overlap with the second wheel and is configured such that, when the transmission arrangement is in operation, lubricating oil thrown off the second wheel is directed towards the first center plane, wherein the lubricating oil guide geometry in the installed position of the gear arrangement is arranged below the plane that is spanned by the first axis of rotation and the second axis of rotation.

The gear arrangement according to the invention has the advantage that the thrown off lubricating oil of the second wheel is guided in the axial direction into the effective area of the first wheel via the lubricating oil guide geometry. Impingement of the spray oil of the second wheel on the wheel body of the first wheel against the direction of rotation of the first wheel is thus reduced or prevented. The lubricating oil thus supplied to the first wheel does not therefore have to be braked by the first wheel in order to then be accelerated in the opposite circumferential direction. This reduces the churning losses of the first wheel. In addition, this two-stage routing of the lubricating oil, from the second wheel to the first wheel, can ensure that the tooth engagements of the first gear stage and the second gear stage are both supplied with lubricating oil in a targeted, permanent and efficient manner.

The center plane is understood to mean the planes perpendicular to the axis of rotation of the respective wheel are defined by the center of the axial overlap of the elements of the respective gear stage. The middle level E1 is thus defined by the center point of the axial overlap of the first wheel and the pinion of the first gear stage and is perpendicular to the first axis of rotation. The middle level E2 is accordingly defined by the center point of the axial overlap of the second wheel and the pinion of the second gear stage and is perpendicular to the second axis of rotation.

The operation of the gear arrangement is to be understood as the rotation of the elements of the gear arrangement in a preferred direction of rotation. The preferred direction of rotation usually corresponds to a forward drive of a vehicle. Depending on the configuration of the lubrication system of the transmission arrangement, however, it is also conceivable that the preferred direction corresponds to a backward travel of a vehicle.

In one possible embodiment, the lubricating oil guide geometry can be such

be configured such that the lubricating oil thrown off the second wheel is guided through an opening of the separating element in the direction of the first center plane. In particular, the mouth of the lubricating oil guide geometry and the opening of the separating element can be arranged in a radial overlap. Alternatively, it is conceivable that the lubricating oil guide geometry is designed in such a way that the thrown off lubricating oil of the second wheel is guided past the separating element to the first center plane.

In a further possible embodiment, the first wheel can be arranged at least partially in a first lubricating oil collecting section of the housing arrangement and the second wheel can be arranged at least partially in a second lubricating oil collecting section of the housing arrangement. In particular, the first wheel can be immersed in an oil sump that can form in the first lubricating oil collecting section and the second wheel can be immersed in an oil sump that can form in the second lubricating oil collecting section. The first lubricating oil collecting section and the second lubricating oil collecting section can be at least partially delimited by the separating element. The first lubricating oil collecting section and the second lubricating oil collecting section can be connected to one another via the lubricating oil guide geometry. In the installed position of the gear arrangement, the first lubricating oil collecting section can be arranged above the lubricating oil resting level.

The transmission arrangement can comprise a lubricating oil distribution arrangement, wherein when the transmission arrangement is operating, the first wheel conveys lubricating oil from the first lubricating oil collecting section into the lubricating oil distribution arrangement, and the lubricating oil distribution arrangement in particular comprises at least one outlet that directs lubricating oil collected in the lubricating oil distribution arrangement to bearings and / or gear engagements of the transmission arrangement. The lubricating oil distribution arrangement may include a distributor element that divides the flow of the collected lubricating oil in such a way that outlets that are connected to elements of the transmission arrangement to be lubricated are supplied with lubricating oil in a predetermined ratio.

The gear arrangement can comprise a lubricating oil reservoir which is arranged in the installed position of the gear arrangement above the first lubricating oil collecting section, the first wheel conveying lubricating oil from the first lubricating oil collecting section into the lubricating oil reservoir when the transmission arrangement is in operation. For this purpose, the lubricating oil reservoir can be arranged at least partially in axial overlap with the lubricating oil reservoir.

The lubricating oil reservoir can store the thrown off lubricating oil up to a defined volume. When the defined volume is exceeded, lubricating oil can be returned to the oil sump via overflow areas and / or can flow from the lubricating oil reservoir via outlets to elements of the gear arrangement which have to be lubricated.

The lubricating oil reservoir can have an overflow area which, in the installed position of the gear arrangement, is arranged above, in particular vertically above, an internal convection surface of the housing arrangement. In the context of this invention, a convection surface is to be understood as an inward surface of an outer wall of the housing arrangement, via which lubricating oil can flow into the bottom region of the gear arrangement, in particular into an oil sump. The convection surface can therefore also be referred to as the heat absorption surface. The convection surface can be arranged at least partially above the lubricating oil resting level.

The housing arrangement can comprise a lubricating oil calming chamber, which is arranged at least partially in a lower section of the housing arrangement. A lubricating oil calming chamber is to be understood as any chamber in the housing arrangement in which spray oil can be collected and calmed down before it is fed to the second lubricating oil collecting section. For this purpose, the lubricating oil settling chamber can be connected to the second lubricating oil collecting section via an opening, which is designed in particular as a throttle, so that the second lubricating oil collecting section or Lubricating oil is supplied to the second wheel in a constant, defined quantity and in a defined direction. The lubricating oil calming chamber can be at least partially limited by the convection surface of the housing arrangement.

The gear arrangement can have an insert element connected to the housing arrangement, which comprises at least one of the lubricating oil reservoir, the lubricating oil distribution arrangement and the separating element.

• 1a eine erste perspektivische Ansicht einer Antriebsanordnung mit einer erfindungsgemäßen Getriebeanordnung;
• 1b eine zweite perspektivische Ansicht der Antriebsanordnung aus 1a;
• 2 eine Explosionsdarstellung der Antriebsanordnung aus 1;
• 3 eine perspektivische Ansicht der Getriebeanordnung der Antriebsanordnung aus 1 in einem ersten Teilschnitt;
• 4 eine perspektivische Ansicht der Getriebeanordnung der Antriebsanordnung aus 1 in einem zweiten Teilschnitt;
• 5 eine perspektivische Ansicht des Motorgehäuses der Getriebeanordnung der Antriebsanordnung aus 1 mit eingezeichnetem Schmierölruhepegel;
• 6 eine perspektivische Ansicht des Getriebegehäuses der Getriebeanordnung der Antriebsanordnung aus 1;
• 7 eine perspektivische Ansicht der Antriebsanordnung aus 1 in einer Schnittebene entlang der Trennlinie der Gehäuseanordnung mit einer Blickrichtung von der Getriebeseite in Richtung der Motorseite, wobei Schmierölniveaus eingezeichnet sind, die sich in einem Referenzbetriebspunkt der Antriebsanordnung ausbilden;
• 8 eine perspektivische Ansicht der Antriebsanordnung aus 1 in einer Schnittebene entlang der Trennlinie der Gehäuseanordnung mit einer Blickrichtung von der Motorseite in Richtung der Getriebeseite, wobei Schmierölniveaus eingezeichnet sind, die sich in einem Referenzbetriebspunkt der Antriebsanordnung ausbilden;
• 9 eine erste perspektivische Detailansicht des Einsatzelementes der Antriebsanordnung aus 1;
• 10 eine zweite perspektivische Detailansicht des Einsatzelementes der Antriebsanordnung aus 1;
• 11 eine perspektivische Ansicht analog zu 9 mit den Elementen der ersten und zweiten Getriebestufe der Getriebeanordnung der Antriebsanordnung aus 1, wobei das Rad der ersten Getriebestufe der Übersichtlichkeit halber axial versetzt dargestellt ist;
• 12 die Getriebeanordnung der Antriebsanordnung aus 1 in einer Schnittdarstellung entlang der Drehachse der Zwischenwelle;
• 13 die Schnittdarstellung aus 12 in perspektivischer Ansicht; und
• 14 einen Teilschnitt der Getriebeanordnung der Antriebsanordnung aus 1 entlang der Drehachse der Eingangswelle.

Preferred embodiments are explained below with reference to the drawing figures. It shows

• 1a a first perspective view of a drive arrangement with a transmission arrangement according to the invention;
• 1b a second perspective view of the drive assembly 1a ;
• 2nd an exploded view of the drive assembly 1 ;
• 3rd a perspective view of the gear assembly of the drive assembly 1 in a first partial section;
• 4th a perspective view of the gear assembly of the drive assembly 1 in a second partial section;
• 5 a perspective view of the motor housing of the gear arrangement of the drive arrangement 1 with indicated lubricating oil level;
• 6 a perspective view of the gear housing of the gear arrangement of the drive arrangement 1 ;
• 7 a perspective view of the drive assembly 1 in a sectional plane along the dividing line of the housing arrangement with a viewing direction from the transmission side towards the motor side, lubricating oil levels being shown which form at a reference operating point of the drive arrangement;
• 8th a perspective view of the drive assembly 1 in a sectional plane along the dividing line of the housing arrangement with a viewing direction from the motor side in the direction of the transmission side, lubricating oil levels being shown which form at a reference operating point of the drive arrangement;
• 9 a first perspective detail view of the insert element of the drive assembly 1 ;
• 10th a second perspective detail view of the insert element of the drive assembly 1 ;
• 11 a perspective view analogous to 9 with the elements of the first and second gear stage of the gear arrangement of the drive arrangement 1 , the wheel of the first gear stage being shown axially offset for the sake of clarity;
• 12 the gear arrangement of the drive arrangement 1 in a sectional view along the axis of rotation of the intermediate shaft;
• 13 the sectional view 12 in perspective view; and
• 14 a partial section of the gear arrangement of the drive arrangement 1 along the axis of rotation of the input shaft.

The 1 to 14 , which are jointly described below, show an electric drive arrangement 1 with a gear arrangement according to the invention 2nd for a motor vehicle. The gear arrangement 2nd comprises a housing arrangement 3rd with a first housing part 4th and a second housing part 5 . The first housing part 4th takes an electric motor from one side 36 and can therefore also be called a motor housing. The electric motor 36 is about a wire harness 39 with a control unit 38 that control the electric drive assembly 1 serves, connected. The motor housing is on the opposite side 4th with the second housing part 5 connected by means of connecting elements so that a gear space is formed in which a gear unit, a differential 16 as well as an insert element 25th are included. The second housing part 5 can therefore also be called a gear housing.

The gear unit comprises a first gear stage 6 and a second gear stage 13 . The second gear stage 13 follows in the power path from the electric motor 36 to the differential 16 immediately after the first gear stage 6 . In other words, is between the first gear stage 6 and the second gear stage 13 no further gear stage arranged. A pinion 8th the first gear stage 6 is in an input shaft 7 incorporated by a warehouse 10th in the gearbox 5 and a warehouse 10 ' in the motor housing 4th about an axis of rotation A is stored. The input shaft 7 is with a motor shaft 37 of the electric motor 36 non-rotatably connected. The pinion 8th combs with a first wheel 9 the first gear stage 6 that on an intermediate shaft 11 sits. The intermediate shaft 11 is with a camp 12 in the gearbox 5 and with a camp 12 ' in the motor housing 4th about an axis of rotation B stored. The intermediate shaft 11 also has a pinion 14 the second gear stage 13 on that with a second wheel 15 the second gear stage 13 is in the form of a ring gear. The second wheel 15 is with an annular housing portion of the differential 16 connected, for example welded or screwed. The differential 16 is with a camp 17th in the gearbox 5 and with a camp 17 ' in the motor housing 4th about an axis of rotation C. stored. Through the differential 16 can that of the second wheel 15 transmitted power in a well known manner on two output shafts 40 , 40 ' be distributed.

The axes of rotation A , B and C. are arranged parallel to each other in the present case and thus together define an axial extension of the drive arrangement 1 or the gear arrangement 2nd . The plane created by connecting the axis of rotation A with the axis of rotation C. is defined, divides the housing arrangement 3rd into a lower housing section and an upper housing section.

The first gear stage 6 has a first center plane E1 and the second gear stage 13 a second center level E2 on. The planes should be perpendicular to the axial extent of the gear arrangement as the center plane 2nd are understood, which are defined by the center of the axial overlap of the elements of the respective gear stage. In the present case, the middle levels E1 and E2 through the center of the axial overlap of the first wheel 9 and the pinion 8th the first gear stage 6 or the second wheel 15 and the pinion 14 the second gear stage 13 certainly.

In the housing arrangement 2nd lubricating oil is absorbed in a predefined amount, so that a lubricating oil resting level L1 trains. The lubrication level L1 turns itself into an installed position of the drive arrangement 1 in a calm state when all the lubricating oil is in the bottom area of the housing arrangement 3rd accumulates as in 5 shown. The lubrication level L1 can be chosen so that at least some of the elements of the gear arrangement 2nd , especially the bearings 10th , 10 ' the input shaft 7 , the pinion 8th the first gear stage 6 , the second wheel 15 the second gear stage 13 as well as the bearings 17th , 17 ' of the differential 16 , in the lubricating oil sump formed in this way with the lubricating oil resting level L1 immerse. The lubricating oil level is in the calm state described above L2 the lubricating oil calming chamber described below 34 with the lube oil resting level L1 identical.

The insert element 25th is with position elements 41 which in corresponding receiving areas of the housing arrangement 3rd intervene, arranged in the upper housing section. The insert element 25th has a distribution section 26 and an overflow section 27 on the operation of the gear assembly 2nd each capture and store splash oil from the gear unit, which can also be referred to as spun-off oil. The overflow section 27 can also be called a lubricating oil reservoir. The distribution section 26 and the overflow section 27 have a common catch area 45 on the operation of the gear assembly 2nd in the preferred direction of rotation, that is to say as a rule when the vehicle is moving forward, from the first wheel 9 the first gear stage 6 Spray oil catches. In special cases, the preferred direction of rotation can also be defined when the vehicle is reversing. The catch area 45 is in axial overlap with the first wheel 9 arranged.

Starting from the catch area 45 this will be in the distribution section 26 led lubricating oil to a transmission-side outlet 31 and an engine-side outlet 31 ' headed. The outlets 31 , 31 ' can be connected to suitable oil guiding elements, which carry the lubricating oil in a known manner at points to be lubricated in the gear arrangement 2nd , such as bearings and gear engagements, lead, for example, oil guide plates or oil guide holes in the housing arrangement 3rd . Via a distributor element 43 in the distribution section 26 the lubricating oil flow can be adjusted according to the needs of the outlets 31 , 31 ' be divided. In addition, the distribution section 26 a lubricating oil level L3 train before lubricating oil from the distribution section 26 overflows. This is the maximum amount of lubricating oil that can flow through the distribution section 26 can be included. The lubricating oil level L3 is above the lubricating oil resting level L1 arranged.

The distribution section 26 also has a scraper 42 on. When operating the gear arrangement 2nd contrary to the preferred direction of rotation, ie usually when reversing, lubricating oil from the second wheel 15 the second gear stage 13 was picked up, stripped and thus reaches the distribution section 26 . The distribution element 43 can be designed so that the stripped lubricating oil according to the respective need for the outlets 31 , 31 ' divided and managed.

Part of the in the catchment area 45 trapped lubricating oil is also in the overflow section 27 directed and collected there. The overflow section 27 is bowl-shaped and has an overflow area in the form of an overflow edge 32 on. As an overflow edge 32 becomes the vertically upward edge region of the overflow section 27 defined, which is arranged vertically at the lowest level. Thus, in the overflow section 27 a lubricating oil level L4 train until the collected lubricating oil over the overflow edge 32 flows over. This is the maximum amount of lubricating oil that can flow through the overflow section 27 can be included. The lubricating oil level L4 is vertically above the lubricating oil resting level L1 arranged. Alternatively, the overflow area can be an opening in the overflow section 27 be designed. Then the lubricating oil level L4 defined by the vertically lowest point of the opening.

The insert element 25th encloses a portion of the circumference of the second wheel 15 with the distribution section 26 . With the catch area 45 and part of the overflow section 27 includes the insert element 25th the first wheel 9 . As a result, the intermediate shaft in particular 11 as well as the motor side, the input shaft 7 receiving bearings 10 ' compared to the spray oil of the first gear stage 6 and the second gear stage 13 shadowed. To ensure an adequate supply to the warehouse 10 ' to secure with lubricating oil includes the overflow section 27 also an outlet 31 " , over the lubricating oil to the bearings 10th , 10 'of the input shaft 7 is conducted as in 14 shown.

The insert element 25th also includes a separator 28 that in the axial direction between the center plane E1 the first gear stage 6 and the middle level E2 the second gear stage 13 is arranged. However, it is also conceivable that the separating element 28 is designed as a separate component. The separator 28 in the present case has an annular section with a central opening 29 on, through which the intermediate shaft 11 is passed through. The annular section is in axial overlap with the first wheel 9 the first gear stage 6 arranged. The outer diameter of the annular section is larger than the tip diameter of the first wheel 9 . The separator 28 has a connection opening in the region of the annular section 30th on that a first oil collection section 18th the gear arrangement 2nd with a second lubricating oil collecting section 23 Gear arrangement 2nd connects. It is also conceivable that instead of the connection opening 30th the separator 28 has an opening which corresponds in particular to a circular ring segment. In the present case, the separating element forms 28 also a wall of the collecting section 26 and a wall of the overflow section 27 of the insert element 25th .

The first wheel 9 the first gear stage 6 is in the first lubricating oil collecting section 18th arranged in the gearbox. The first oil collection section 18th is on the side facing away from the motor through a pot-shaped limiting section 19th of the gearbox 5 limited. The first lubricating oil collecting section is on the engine side 18th through the separating element 28 of the insert element 25th limited. The outer contour of the separating element 28 follows the boundary section in a partial area 19th of the gearbox 5 . It is also conceivable that between the separating element 28 and the intermediate shaft 11 on the one hand and between the separating element 28 and the limiting section 19th of the gearbox 5 on the other hand, sealing elements are arranged.

The second wheel 15 the second gear stage 13 is in the second lubricating oil collecting section 23 arranged in the gearbox. The second wheel 15 turns in the opposite direction to the first wheel 9 the first gear stage 6 . The second oil collection section 23 will on the the engine 36 opposite side through a wall section 24th of the gearbox 5 limited. The second lubricating oil collecting section is on the engine side 23 through a wall 46 of the motor housing 4th limited. The engine case 4th has an oil guide rib 20th on who the second wheel 15 surrounds in a partial area in the circumferential direction. The partial area extends in the installed position of the drive arrangement 1 starting from a vertically lowest point of the second wheel 15 by up to 120 °, in particular up to 90 °, in the direction of the preferred direction of rotation. The oil guide rib 20th forms together with the outer contour and the wall 46 of the motor housing 4th a cup-shaped section that holds the second wheel 15 surrounds approximately three-quarters. The oil guide rib is fixed in the assembled state 20th also together with a fixing rib 44 the insert element 25th in the area of the separating element 28 in the axial direction between the motor housing 4th and the gearbox 5 .

The gear arrangement 2nd has a lubricating oil guide geometry that is in axial overlap with the second wheel 15 is arranged and configured such that when the gear arrangement is in operation 2nd from the second wheel 15 thrown off lubricating oil in the direction of the first center plane E1 is directed.

In the present case, the lubricating oil guide geometry includes a catch groove 21st by an oil guide fin 20th along with a catch rib 22 of the motor housing 4th is formed and in axial overlap with the second wheel 15 the second gear stage 13 is arranged. The catch groove 21st can be arranged in the housing space below a plane through the axis of rotation B the intermediate shaft 11 and the axis of rotation C. of the differential 16 is spanned. The catch groove 21st is axially oriented and widens in the radial direction from the motor side along the width of the second wheel 15 in the direction of the separating element 28 . The catch groove 21st and the connection opening 30th of the separating element 28 are arranged in radial overlap with one another and directly adjoin one another. When the second wheel rotates 15 in the preferred direction of rotation, as indicated by the arrow X1 in shown the in the present case corresponds to a forward drive, is by the second wheel 15 Lube oil from the bottom of the second lube oil collecting section 23 taken and against the catch groove 21st pressed. Due to the shape of the catch groove 21st the lubricating oil is deflected axially away from the engine side and through the connection opening 30th of the separating element 28 in the first lubricating oil collecting section 18th towards the first center plane E1 promoted. The corresponding lubricating oil movement is in the 7 and 8th represented by arrows.

It is also conceivable that the lubricating oil guide geometry, at least in part, by a separate component, by the separating element 28 or by any combination of a separate component, the separating element 28 and the housing arrangement 3rd is formed.

As previously described, from the first lubricating oil collecting section 18th the lubricating oil over the catch groove 21st in the effective range of the first wheel 9 the first gear stage 6 passed so that when operating the gear arrangement 2nd the filled lubricating oil from the lower housing section of the gear arrangement in a quick and simple manner 2nd , in particular from the floor area, into the insert element 25th is promoted. This can cause the splashing losses caused by the second wheel 15 caused to be significantly reduced. At the same time, this two-stage guidance of the lubricating oil can ensure that the meshing of the first gear stage 6 and the gear stage 13 both are supplied with lubricating oil in a targeted, permanent and efficient manner.

In addition, due to the geometry of the lubricating oil 21st the spray oil of the second gear stage 13 the first wheel 9 the first gear stage 6 axially fed. Opposite a gear arrangement 2nd without such a separator 28 between the first lubricating oil collecting section 18th and the second lubricating oil collecting section 23 is thus an impact of the spray oil of the second gear stage 13 on the first wheel 9 the first gear stage 6 against the direction of rotation of the first wheel 9 reduced or prevented. The spray oil therefore does not have to come from the first wheel 9 are first braked to the spray oil then according to the direction of rotation of the first wheel 9 accelerate in the opposite direction. This reduces splashing losses caused by the first wheel 9 caused. It is particularly conceivable that the spray oil through the lubricating oil guide geometry 21st is deflected so far that the spray oil is the first wheel 9 the first gear stage 6 is fed in the circumferential direction with the direction of rotation.

The overflow edge 32 of the overflow section 27 of the insert element 25th is above a heat absorption surface oriented in the gearbox 33 the housing arrangement 3rd arranged. The heat absorption surface 33 in the present case includes partial areas of the motor housing 4th and the gearbox 5 . The heat absorption surface 33 has a first section 33 ' that runs obliquely below the overflow edge 32 is arranged. A second section 33 " runs from the first section 33 ' with a slight inclination towards the bottom of the housing arrangement 3rd . A third section 33 '" connects the second section 33 " with the bottom of the housing assembly 3rd . Exceeds the level of the collected lubricating oil in the overflow section 27 the level L4 the overflow edge 32 , lubricating oil flows from the overflow section 27 on the first section 33 ' the heat absorption surface 33 . The lubricating oil continues to flow along the second section due to gravity 33 " and the third section 33 '" . This enables the lubricating oil to apply its thermal energy to the wall of the housing arrangement 3rd dispense so that a high cooling of the lubricating oil can be achieved. For this purpose, the outer wall of the housing arrangement 3rd in the area of the heat absorption surface 33 be designed in such a way that the thermal energy is efficiently released into the environment.

The heat absorption surface 33 limited in particular together with the oil guide rib 20th a lube oil chamber 34 in which that from the overflow section 27 of the insert element 25th overflowing lubricating oil is collected after it reaches the heat absorbing surface 33 has flowed along. The lubrication chamber 34 is about a breakthrough 35 in the oil guiding rib 20th with the second lubricating oil collecting section 23 connected. The breakthrough 35 can be designed as a throttle, via the second wheel 15 the second gear stage 13 Lubricating oil is supplied in a defined amount and in a little turbulent state. This in turn can cause the splashing losses of the second wheel 15 be reduced.

About the size of the breakthrough 35 can be set how much lubricating oil in the lubricating oil calming chamber 34 is accumulated, so that at a reference operating point, in particular during nominal operation of the drive arrangement 1 , in the second lubricating oil collecting section 23 a lubricating oil level L1 ' and in the lubrication chamber 34 a lubricating oil level L2 ' trains. In this context, particular attention is paid to the fact that at the reference operating point a part of the into the housing arrangement 3rd filled lubricating oil in the insert element 25th is stored, being in the distribution section 26 the lubricating oil level L3 and in the overflow section 27 the lubricating oil level L4 trains. In the present case, around 30% of the originally filled amount of lubricating oil collects in the second lubricating oil collecting section at the reference operating point 23 , while up to 70% of the originally filled amount of lubricating oil in the insert element 25th and the lubrication chamber 34 be accumulated.

Reference symbol list

1

Drive arrangement

2nd

Gear arrangement

3rd

Housing arrangement

4th

Engine housing

5

Gear housing

6

First gear stage

7

Input shaft

8th

pinion

9

wheel

10, 10 '

warehouse

11

Intermediate shaft

12, 12 '

warehouse

13

Second gear stage

14

pinion

15

Sprocket

16

differential

17, 17 '

warehouse

18th

First oil collection section

19th

Boundary section

20th

Oil guiding rib

21st

Catch groove, oil guide geometry

22

Rib

23

Second oil collection section

24th

Wall section

25th

Insert element

26

Distribution section

27th

Overflow section, lubricating oil reservoir

28

Separating element

29

opening

30th

Connection opening

31, 31 ', 31 "

Outlet

32

Overflow edge

33, 33 ', 33 ", 33'"

Heat absorption surface

34

Calming chamber

35

breakthrough

36

engine

37

Motor shaft

38

Control unit

39

Wiring harness

40.40 '

Output shaft

41

Position element

42

Wipers

43

Distributor

44

Fixing rib

45

Catch area

46

Wall

A, B, C

Axis of rotation

E

level

L

level

X

Preferred direction of rotation

Claims (15)

Gear arrangement, in particular for an electric drive, comprising: a housing arrangement (3); a first gear stage (6) with a first wheel (9) which can be driven by a pinion (8) of the first gear stage (6) to rotate about a first axis of rotation (B) and has a first center plane (E1); and a second gear stage (13) with a second wheel (15) which can be driven by a pinion (14) of the second gear stage (13) to rotate about a second axis of rotation (C) parallel to the first axis of rotation (B) and a second center plane ( E2); wherein the first gear stage (6) and the second gear stage (13) are accommodated in the housing arrangement (3) and are drive-connected to one another, and wherein the first wheel (9) has an opposite direction of rotation to the second wheel (15); a separating element (28) which is arranged axially between the first center plane (E1) and the second center plane (E2); Lubricating oil, which is provided in the housing arrangement (3) and defines a lubricating oil resting level (L1) in the calm state; and a lubricating oil guide geometry (21) which is arranged in axial overlap with the second wheel (15) and is designed such that when the transmission arrangement is in operation, lubricating oil thrown off the second wheel (15) is directed in the direction of the first center plane (E1), wherein in the installed position of the gear arrangement the lubricating oil guide geometry (21) is arranged below a plane which is spanned by the first axis of rotation (B) and the second axis of rotation (C). Gear arrangement according to Claim 1 , characterized in that the lubricating oil guide geometry (21) is designed such that the lubricating oil thrown off the second wheel (15) is guided through an opening (30) of the separating element (28) in the direction of the first center plane (E1). Gear arrangement according to one of the Claims 1 or 2nd , characterized in that the first wheel (9) in a first lubricating oil collecting section (18) of the housing arrangement (3) and the second wheel (15) in a second lubricating oil collecting section (23) of the housing arrangement (3) is arranged. Gear arrangement according to Claim 3 , characterized in that the first lubricating oil collecting section (18) and the second lubricating oil collecting section (23) are at least partially delimited by the separating element (28). Gear arrangement according to one of the Claims 3 or 4th , characterized in that the first lubricating oil collecting section (18) and the second lubricating oil collecting section (23) are connected to one another via the lubricating oil guide geometry (21). Gear arrangement according to one of the Claims 3 to 5 , characterized in that in the installed position of the gear arrangement, the first lubricating oil collecting section (18) is arranged above the lubricating oil resting level (L1). Gear arrangement according to one of the Claims 3 to 6 , characterized by - a lubricating oil reservoir (27) which is arranged in the installed position of the gear arrangement above the first lubricating oil collecting section (18), the first wheel (9) lubricating oil from the first lubricating oil collecting section (18) into the lubricating oil reservoir (27) during operation of the transmission arrangement promotes. Gear arrangement according to one of the Claims 3 to 7 , characterized by a lubricating oil distribution arrangement (26), the first wheel (9) conveying lubricating oil from the first lubricating oil collecting section (18) into the lubricating oil distribution arrangement (26) during operation of the transmission arrangement. Gear arrangement according to Claim 8 , characterized in that the lubricating oil distribution arrangement (26) comprises at least one outlet (31, 31 ') which directs the lubricating oil collected in the lubricating oil distribution arrangement (26) to bearings and / or toothing engagements of the gear arrangement. Gear arrangement according to Claim 8 or 9 , characterized in that the gear arrangement has an insert element (25) connected to the housing arrangement (3), which comprises at least one of the lubricating oil reservoir (27), the lubricating oil distribution arrangement (26) and the separating element (28). Gear arrangement according to one of the Claims 8 to 10th , characterized in that the lubricating oil reservoir (27) has an overflow area (32) which is arranged in the installed position of the gear arrangement above an internal convection surface (33) of the housing arrangement (3). Gear arrangement according to Claim 11 , characterized in that the convection surface (33) is at least partially arranged above the lubricating oil resting level (L1). Gear arrangement according to one of the Claims 1 to 12 , characterized by a lubricating oil calming chamber (34) of the housing arrangement (3), which is arranged at least partially in a lower section of the housing arrangement (3). Gear arrangement according to Claim 13 , characterized in that the lubricating oil calming chamber (34) is connected via an opening (35) to the second lubricating oil collecting section (23). Gear arrangement according to Claim 13 or 14 , characterized in that the lubricating oil calming chamber (34) is at least partially delimited by the convection surface (33) of the housing arrangement (3).

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