WO2020157004A1 - Ensemble d'engrenage - Google Patents

Ensemble d'engrenage Download PDF

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Publication number
WO2020157004A1
WO2020157004A1 PCT/EP2020/051925 EP2020051925W WO2020157004A1 WO 2020157004 A1 WO2020157004 A1 WO 2020157004A1 EP 2020051925 W EP2020051925 W EP 2020051925W WO 2020157004 A1 WO2020157004 A1 WO 2020157004A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricating oil
wheel
gear
arrangement
gear arrangement
Prior art date
Application number
PCT/EP2020/051925
Other languages
German (de)
English (en)
Inventor
Mark Schmidt
Jürgen Haber
Frank BERNREUTHER
Torsten Tietgen
Damian DUDEK
Original Assignee
Gkn Automotive Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gkn Automotive Limited filed Critical Gkn Automotive Limited
Priority to CN202080011257.0A priority Critical patent/CN113316694A/zh
Publication of WO2020157004A1 publication Critical patent/WO2020157004A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0409—Features relating to lubrication or cooling or heating characterised by the problem to increase efficiency, e.g. by reducing splash losses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0426—Means for guiding lubricant into an axial channel of a shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0476—Electric machines and gearing, i.e. joint lubrication or cooling or heating thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears
    • F16H57/0494—Gearings with spur or bevel gears with variable gear ratio or for reversing rotary motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/003—Arrangement or mounting of electrical propulsion units with means for cooling the electrical propulsion units
    • B60K2001/006—Arrangement or mounting of electrical propulsion units with means for cooling the electrical propulsion units the electric motors

Definitions

  • the present invention relates to a gear arrangement for a motor vehicle, in particular for an electric drive.
  • gear arrangements for motor vehicles have been subject to ever increasing demands with regard to their efficiency, for example due to legal regulation.
  • gear arrangements must be usable in increasingly small installation spaces of motor vehicles, so that they have increasingly compact architectures. Both aspects make adequate lubrication of the components in the gear arrangement difficult.
  • a gear arrangement for a motor vehicle comprising: a first gear and a second gear, which are connected to each other at the drive; a lubricant filling, which stood in a static Installation to the gear arrangement defines a lubricant level; a first reservoir, which is arranged above the level of lubricant and can be filled with lubricant when driving the gear arrangement by rotating the first gear, a second reservoir, which is arranged above the level of lubricant and when driving the gear arrangement by rotating the second gear with lubricant is fillable.
  • the reservoirs are limited by a housing part and a cover element.
  • a gear arrangement with a lower lubricant reservoir and two upper lubricant reservoirs is known.
  • the upper lubricating Medium 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.
  • a lubricating oil structure for a speed reducer is known from DE 10 2015 013 973 A1.
  • the lubricating oil assembly includes a housing with a side wall, a reduction gear that is connected to an output shaft, and a collecting container for receiving a portion of a lubricating oil that is entrained 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.
  • 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 object of the present invention is to propose a gear arrangement which has an improved thermal operating behavior.
  • a gear arrangement in particular for an electric drive, comprising: a housing arrangement; a first gear stage with a first wheel which can be driven by a pinion of the first gear stage to rotate about a first axis of rotation 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 to the second wheel has an opposite direction of rotation; 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 resting level in the calm state, wherein a lubricating oil guide geometry is arranged in axial overlap with the second wheel and is designed such that when the transmission arrangement is in operation from second wheel thrown lub
  • the gear arrangement according to the invention has the advantage that the lubricating oil of the second wheel flung off is guided via the lubricating oil guide geometry in the axial direction to the first central plane or into an effective area of the first wheel.
  • the effective area can, for example, be a collecting section for the lubricant, in which the first wheel comes into contact with the lubricant and takes it with it when it rotates, so that the lubricant is conveyed further upward from the effective area by the first wheel.
  • the two counter-rotating first and second wheels thus effect a multi-stage delivery of lubricant.
  • a delivery stage is formed by the second wheel which, when rotating, delivers lubricant to the lubricating oil guide geometry.
  • the lubricant is guided from an axial overlap area of the second wheel in the direction of the first center plane or the effective area of the first wheel.
  • the lubricant is carried along by the counter-rotating first wheel, which forms a further delivery stage.
  • the separating element arranged axially between the first central plane and the second central plane reduces or prevents the splash oil of the second wheel from striking the wheel body of the first wheel against the direction of rotation of the first wheel.
  • the lubricating oil guide geometry which redirects or directs the lubricant from the spray area of the second wheel to the effective area of the first wheel, forms a targeted fluidic connection between the two wheels.
  • the lubricating oil conveyed by the second wheel in the second direction of rotation and supplied to the first wheel via the lubricating oil guide geometry and further conveyed by the latter in the first direction of rotation is conveyed in a continuous flow movement. It therefore does not have to be braked by the first wheel in order to then be accelerated in the opposite circumferential direction. In this way, the splashing losses of the first wheel are reduced.
  • this two-stage guidance 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 both be supplied with lubricating oil in a targeted, permanent and efficient manner.
  • the center plane should be understood to mean the planes perpendicular to the axis of rotation of the respective wheel, which are defined by the center of the axial overlap of the elements of the respective gear stage.
  • the center plane 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 center plane E2 is accordingly defined by the center of the axial overlap of the second wheel and the pinion of the second gear stage and extends perpendicular to the second axis of rotation.
  • the transmission arrangement can, for example, be used in a drive train of a motor vehicle to transmit a drive force from a drive source to a vehicle axle.
  • the drive source can be, for example, an electrical machine, other drive sources such as an internal combustion engine also being possible.
  • Operation of the gear arrangement should be understood to mean 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.
  • the direction of travel corresponds to a backward travel of a vehicle.
  • the lubricating oil guide geometry in the installed position of the transmission arrangement, can be arranged below a plane that is spanned by the first axis of rotation and the second axis of rotation.
  • the lubricating oil guide geometry can also 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.
  • the Mün extension of the lubricating oil guide geometry and the opening of the separating element can be arranged in a radial overlap.
  • the lubricating oil guidance geometry is configured such that the lubricating oil thrown off the second Rades past the separating element to the first center plane.
  • 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.
  • the first wheel can be immersed in an oil sump that can form in the first lubricating oil collecting section and the second wheel 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 limited by the separating element.
  • the first lubricating oil collecting section is in the installed position of the transmission, in particular above half of the second lubricating oil collecting section.
  • the second wheel can deliver lubricating oil from the second collection section up to the lubricating oil guide geometry that directs the lubricating oil to the first lubricating oil collecting section. From here, the first wheel can further advance the lubricant in the opposite direction of rotation. Insofar, the first and the second lubricating oil collecting section are fluidly connected to one another via the lubricating oil guide geometry. In the installed position of the gearbox arrangement, the first lubricating oil collecting section can be arranged above the lubricating oil resting level.
  • the gear 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 comprises in particular at least one outlet which stores lubricating oil captured in the lubricating oil distribution arrangement and / or toothing interventions of the transmission arrangement directs.
  • the lubricating oil distribution assembly may include a distributor element that divides the flow of the collected lubricating oil such that outlets that are connected to elements of the transmission assembly to be lubricated are supplied with lubricating oil in a predetermined ratio.
  • the gear arrangement can comprise a lubricating oil reservoir, which is arranged above the first lubricating oil collecting section in the installed position of the gear 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 reservoir.
  • 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 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.
  • 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 area 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 at least partially arranged in a lower section of the housing arrangement.
  • a lubricating oil calming chamber each chamber should be understood in the housing arrangement, in which spray oil can be collected and calmed down before it is supplied to the second lubricating oil collecting section.
  • the lubricating oil calming chamber can be connected via an opening to the second lubricating oil collecting section, which is designed in particular as a throttle, so that in a reference operating point, lubricating oil is supplied to the second lubricating oil collecting section or the second wheel in a constant, defined amount 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. Preferred embodiments are explained below with reference to the drawing figures. It shows
  • Figure 1 a shows a first perspective view of a drive arrangement with an inventive transmission arrangement
  • FIG. 1b shows a second perspective view of the drive arrangement from FIG. 1a;
  • FIG. 2 shows an exploded view of the drive arrangement from FIG. 1;
  • FIG. 3 shows a perspective view of the gear arrangement of the drive arrangement from FIG. 1 in a first partial section;
  • FIG. 4 shows a perspective view of the gear arrangement of the drive arrangement from FIG. 1 in a second partial section
  • FIG. 5 shows a perspective view of the motor housing of the gear arrangement of the drive arrangement from FIG. 1 with the lubricating oil spike shown;
  • FIG. 6 is a perspective view of the gear housing of the gear arrangement of the drive arrangement from FIG. 1;
  • Figure 7 is a perspective view of the drive assembly of Figure 1 in a
  • FIG. 8 shows a perspective view of the drive arrangement from FIG. 1 in a sectional plane along the dividing line of the housing arrangement with a view from the engine side towards the transmission side, lubricating oil levels being shown which form at a reference operating point of the drive arrangement;
  • FIG. 9 shows a first perspective detailed view of the insert element of the drive arrangement from FIG. 1;
  • FIG. 10 shows a second perspective detailed view of the insert element of the drive arrangement from FIG. 1;
  • Figure 1 1 is a perspective view analogous to Figure 9 with the elements of the first and second gear stage of the gear arrangement of the drive arrangement from Figure 1, the wheel of the first gear stage being shown axially offset for the sake of clarity;
  • FIG. 12 shows the gear arrangement of the drive arrangement from FIG. 1 in a sectional illustration along the axis of rotation of the intermediate shaft;
  • FIG. 13 shows the sectional illustration from FIG. 12 in a perspective view
  • FIG. 14 shows a partial section of the gear arrangement of the drive arrangement from FIG. 1 along the axis of rotation of the input shaft.
  • FIGS. 1 to 14 show an electric drive arrangement 1 with a transmission arrangement 2 according to the invention for a motor vehicle.
  • the gear arrangement comprises a housing arrangement 3, in which a first gear stage 6 and a second gear stage 13 connected to the drive are arranged.
  • the first gear stage 6 comprises a pinion 8 and a first wheel 9 in a first gear plane.
  • the second gear stage 13 comprises a second pinion 14 and a second gear 15 in a second gear plane.
  • the first gear 9 rotates about a first axis of rotation B.
  • a lubricating oil guide geometry 21 is provided which, when the wheels rotate, directs lubricating oil thrown off the second wheel 15 in the direction of the first wheel 9 or the first wheel plane.
  • the housing arrangement 3 includes in particular a first housing part 4 and a second housing part 5.
  • the first housing part 4 receives an electric motor 36 from one side and can therefore also be referred to as a motor housing.
  • the electric motor 36 is connected via a wire harness 39 to a control unit 38 which serves to control the electric drive arrangement 1.
  • the motor housing 4 is connected to the second housing part 5 by means of connecting elements, so that a gear space is formed in which the gear arrangement 2, a differential 16 and an insert element 25 are accommodated.
  • the second Ge housing part 5 can thus also be referred to as a gear housing.
  • 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, no further gear stage is arranged between the first gear stage 6 and the second gear stage 13.
  • the pinion 8 of the first gear stage 6 is connected to an input shaft 7, in particular integrated in one piece, which is supported by a bearing 10 in the gear housing 5 and a bearing 10 'in the motor housing 4 about an axis of rotation A.
  • the input shaft 7 is rotatably connected to a motor shaft 37 of the electric motor 36.
  • the pinion 8 meshes with the first wheel 9 of the first Gear stage 6, which sits on an intermediate shaft 1 1.
  • the intermediate shaft 11 is mounted with a bearing 12 in the gear housing 5 and with a bearing 12 'in the motor housing 4 about an axis of rotation B.
  • the intermediate shaft 1 1 also has a pinion 14 of the second gear stage 13, which with a second wheel 15 of the second Ge gear stage 13 in the form of a ring gear is engaged.
  • the second wheel 15 is connected to an annular housing section of the differential 16, for example welded or screwed.
  • the differential 16 is mounted with a bearing 17 in the Ge gear housing 5 and with a bearing 17 'in the motor housing 4 about an axis of rotation C. Through the differential 16, the power transmitted by the second wheel 15 can be distributed to two output shafts 40, 40 'in a well-known manner.
  • the axes of rotation A, B and C are arranged parallel to each other in the present case and thus jointly define an axial extent of the drive arrangement 1 or the transmission arrangement 2.
  • the plane which is defined by the connection of the axis of rotation A with the axis of rotation C divides the housing arrangement 3 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 has a second center plane E2.
  • the center plane the planes are to be understood as perpendicular to the axial extent of the gear arrangement 2, which are defined by the center of the axial overlap of the elements of the respective gear stage.
  • the center planes E1 and E2 are determined by the center point of the axial overlap of the first wheel 9 and the pinion 8 of the first gear stage 6 or the second wheel 15 and the pinion 14 of the second gear stage 13.
  • the middle planes can also be called wheel planes.
  • Lubricating oil is taken up in a predefined amount in the housing arrangement 2, so that a lubricating oil resting level L1 is formed.
  • the lubricating oil idle level L1 is set in an installed position of the drive arrangement 1 in a calm state when the entire lubricating oil accumulates in the bottom area of the housing arrangement 3, as shown in FIG. 5.
  • the lubricating oil idle level L1 can be chosen that at least a part of the elements of the gear arrangement 2, in particular the bearings 10, 10 'of the input shaft 7, the pinion 8 of the first gear stage 6, the second wheel 15 of the second gear stage 13 and the bearings 17, 17' of the Diffe renzials 16, immerse in the lubricating oil sump formed in this way with the lubricating oil resting level L1.
  • the lubricating oil level L2 of the lubricating oil calming chamber 34 described below is identical to the lubricating oil resting level L1.
  • the insert element 25 is arranged with position elements 41, which engage in corresponding receiving areas of the housing arrangement 3, in the upper housing section.
  • the insert element 25 has a distribution section 26 and an overflow section 27 which, when the transmission arrangement 2 is in operation, can collect and store splash oil of the transmission unit Ge, which can also be referred to as centrifuged oil.
  • the overflow section 27 can also be referred to as a lubricating oil reservoir.
  • the distribution section 26 and the overflow section 27 have a common catch area 45 which, when the gear arrangement 2 is operated in the preferred direction of rotation, i. H. as a rule, when the vehicle is moving forward, 6 oil collects from the first wheel 9 of the first gear stage 6. In special cases, the preferred direction of rotation can also be defined when the vehicle is reversing.
  • the catch area 45 is arranged in axial overlap with the first wheel 9.
  • the lubricating oil fed into the distribution section 26 is directed to a transmission-side outlet 31 and an engine-side outlet 31 ′.
  • the outlets 31, 31 " can be connected to suitable oil guide elements, which guide the lubricating oil in a known manner to locations to be lubricated in the gear arrangement 2, such as bearings and toothing engagements, for example oil guide plates or oil guide holes in the housing arrangement 3
  • Distributor element 43 in the distribution section 26 the lubricating oil flow can be divided according to the need for the outlets 31, 31 ".
  • a lubricating oil level L3 can form in the distribution section 26 before lubricating oil overflows from the distribution section 26. This defines the maximum amount of lubricating oil that can be taken up by the distribution section 26.
  • the lubricating oil level L3 is arranged above the lubricating oil resting level L1.
  • the distribution section 26 also has a wiper 42.
  • lubricating oil which has been taken up by the second wheel 15 of the second gear stage 13 is stripped off and thus reaches the distribution section 26.
  • the distributor element 43 can be designed in this way that the stripped lubricating oil is distributed and directed to the outlets 31, 31 'according to the respective requirement.
  • the overflow section 27 is formed bowl-shaped and has an overflow area in the form of an overflow edge 32.
  • the vertically upward edge region of the overflow section 27, which is arranged vertically at the lowest level, is defined as the overflow edge 32.
  • a lubricating oil level L4 can form in the overflow section 27 until the collected lubricating oil flows over the overflow edge 32. This defines the maximum amount of lubricating oil that can be absorbed by the overflow section 27.
  • the lubricating oil level L4 is arranged vertically above the lubricating oil resting level L1.
  • the overflow area can be configured as an opening in the overflow section 27.
  • the lubricating oil level L4 is then defined by the vertically lowest point of the opening.
  • the insert element 25 encloses a partial area of the circumference of the second Ra of the 15 with the distribution section 26. With the catch area 45 and a part of the overflow section 27, the insert element 25 comprises the first wheel 9.
  • the overflow section 27 also includes an outlet 31 ", via which lubricating oil is conducted to the bearings 10, 10" of the input shaft 7, as shown in FIG. 14.
  • the insert element 25 also includes a separating element 28 which is arranged in the axial direction between the center plane E1 of the first gear stage 6 and the center plane E2 of the second gear stage 13.
  • the separating element 28 is designed as a separate component.
  • the separating element 28 has an annular section with a central opening 29 through which the intermediate shaft 11 is passed.
  • the annular section is arranged in axial overlap with the first wheel 9 of the first gear stage 6.
  • the outer diameter of the annular section is larger than the tip circle diameter of the first wheel 9.
  • the separating element 28 has in the region of the circular annular section a connecting opening 30 which connects a first lubricating oil collecting section 18 of the gear arrangement 2 with a second lubricating oil collecting section 23 gear arrangement 2. It is also conceivable that instead of the connection opening 30, the separating element 28 has an opening which corresponds in particular to a circular ring segment. In the present case, the separating element 28 also forms a wall of the collecting section 26 and a wall of the overflow section 27 of the insert element 25.
  • the first wheel 9 of the first gear stage 6 is arranged in the first lubricating oil section 18 of the gear compartment.
  • the first lubricating oil collection section 18 is limited on the side facing away from the engine by a pot-shaped limita tion section 19 of the transmission housing 5.
  • the first lubricating oil collecting section 18 is delimited by the separating element 28 of the insert element 25.
  • the outer contour of the separating element 28 follows in a partial area the limiting section 19 of the gear housing 5. It is also conceivable that sealing elements are arranged between the separating element 28 and the intermediate shaft 11 on the one hand and between the separating element 28 and the limiting section 19 of the gear housing 5 on the other hand .
  • the second wheel 15 of the second gear stage 13 is arranged in the second lubricating oil section 23 of the gear chamber.
  • the second wheel 15 rotates in the opposite direction of rotation to the first wheel 9 of the first gear stage 6.
  • the second lubricating oil collecting section 23 is delimited on the side facing away from the motor 36 by a wall section 24 of the gear housing 5.
  • the second is on the engine side Lubricating oil collecting section 23 through a wall 46 of the motor housing 4 be limited.
  • the motor housing 4 has an oil guide rib 20 which surrounds the second wheel 15 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 20 forms together with the outer contour and the Wan extension 46 of the motor housing 4 a cup-shaped section which surrounds the second wheel 15 approximately three-quarters.
  • the oil guide rib 20 also fixes, together with a fixing rib 44, the insert element 25 in the area of the separating element 28 in the axial direction between the motor housing 4 and the transmission housing 5.
  • the gear arrangement 2 has a lubricating oil guide geometry which is arranged in axial overlap with the second wheel 15 and is designed such that when the gear arrangement 2 is in operation, lubricating oil thrown off the second wheel 15 is directed in the direction of the first center plane E1.
  • the lubricating oil guide geometry in the present case comprises a catch groove 21 which is formed by an oil guide rib 20 together with a catch rib 22 of the motor housing 4 and is arranged in axial overlap with the second wheel 15 of the second gear stage 13.
  • the catch groove 21 can be arranged in the housing space below a plane which is spanned by the axis of rotation B of the intermediate shaft 11 and the axis of rotation C of the differential 16.
  • the catch groove 21 is axially oriented and widens in the radial direction, starting from the motor side, along the width of the second wheel 15 in the direction of the separating element 28.
  • the catch groove 21 and the connecting opening 30 of the separating element 28 are arranged in radial overlap with one another and border directly to each other.
  • the lubricating oil guide geometry is at least partially formed 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 3.
  • the lubricating oil is passed from the first lubricating oil collecting section 18 via the catch groove 21 into the effective area of the first wheel 9 of the first gear stage 6, so that when the gear arrangement 2 is in operation, the filled lubricating oil from the lower housing section of the transmission is quick and easy arrangement 2, in particular from the floor area, is promoted into the insert element 25. In this way, the splashing losses caused by the second wheel 15 can be significantly reduced.
  • this two-stage guidance of the lubricating oil can ensure that the gear meshes of the first gear stage 6 and the gear stage 13 are both supplied with lubricating oil in a targeted, permanent and efficient manner.
  • the spray oil of the two-th gear stage 13 is axially fed to the first wheel 9 of the first gear stage 6.
  • a gear arrangement 2 without such a separating element 28 between the first lubricating oil collecting section 18 and the second lubricating oil collecting section 23 an impact of the spray oil of the second gear stage 13 on the first wheel 9 of the first gear stage 6 is thus counter to the direction of rotation of the first wheel
  • the spray oil therefore does not have to be braked by the first wheel 9 to accelerate the spray oil in the opposite direction according to the direction of rotation of the first wheel 9.
  • the spray oil is deflected by the lubricating oil guide geometry 21 to such an extent that the spray oil is supplied to the first wheel 9 of the first gear stage 6 in the circumferential direction with the direction of rotation.
  • the overflow edge 32 of the overflow section 27 of the insert element 25 is arranged above a heat-receiving surface 33 of the housing arrangement 3 oriented in the transmission space.
  • the heat absorption surface 33 in the present case includes partial surfaces of the motor housing 4 and the transmission housing 5.
  • the heat absorption surface 33 has a first section 33 ', which is arranged obliquely below the overflow edge 32.
  • a second section 33 "extends from the first section 33 'with a slight inclination towards the bottom of the housing arrangement 3.
  • a third section 33" connects the second section 33" to the bottom of the housing arrangement 3.
  • Exceeds the level of the collected lubricating oil in the overflow section 27 the level L4 of the overflow edge 32 lubricating oil flows from the overflow section 27 to the first section 33 'of the heat-receiving surface 33.
  • the lubricating oil continues to flow along the second section 33 "and the third section 33""by gravity.
  • the lubricating oil to deliver its thermal energy to the wall of the housing arrangement 3, so that high cooling of the lubricating oil can be achieved.
  • the outer wall of the housing arrangement 3 in the area of the heat absorption surface 33 can be designed in such a way that the thermal energy is efficiently released to the surroundings.
  • the heat receiving surface 33 limits in particular together with the oil line 20 a lubricating oil calming chamber 34, in which the overflowing portion of the overflow section 27 of the insert element 25 is collected after it has flowed along the heat receiving surface 33.
  • the lubricating oil calming chamber 34 is connected via an opening 35 in the oil guide rib 20 to the second lubricating oil collecting section 23.
  • the opening 35 can be designed as a throttle, via which the second wheel 15 of the second gear stage 13 is supplied with lubricating oil in a defined amount and in a slightly turbulent state. This in turn can reduce the churning losses of the second wheel 15.
  • the size of the opening 35 can be used to set how much lubricating oil is accumulated in the lubricating oil calming chamber 34, so that at a reference operating point, in particular during nominal operation of the drive arrangement 1, in which second lubricating oil collecting section 23 forms a lubricating oil level L1 'and in the lubricating oil calming chamber 34 forms a lubricating oil level L2'. It is particularly taken into account here that at the reference operating point a portion of the lubricating oil filled into the housing arrangement 3 is stored in the insert element 25, the lubricating oil level L3 being formed in the distribution section 26 and the lubricating oil level L4 being formed in the overflow section 27.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne un ensemble d'engrenage comprenant : un ensemble de boîtier (3), un premier étage d'engrenage (6) comprenant une première roue (9), qui peut être entraînée en rotation autour d'un axe de rotation (B) et qui présente un premier plan médian (E1), et un deuxième étage d'engrenage (13) comprenant une deuxième roue (15), qui peut être entraînée en rotation autour d'un deuxième axe de rotation (C) et qui présente un deuxième plan médian (E2), les premier et deuxième étages d'engrenage (6, 13) étant reliés entre eux en entraînement, et la première et la deuxième roue (9, 15) présentant un sens de rotation opposé ; un élément de séparation (28), qui est disposé axialement entre le premier et le deuxième plan médian (E1, E2), et de l'huile lubrifiante, qui définit, à l'état de repos, un niveau de repos d'huile lubrifiante (L1), une géométrie d'amenée d'huile lubrifiante (21) étant disposée chevauchant axialement la deuxième roue (15) et étant conçue de telle façon que, lors du fonctionnement de l'ensemble d'engrenage, de l'huile lubrifiante éjectée de la deuxième roue (15) est guidée dans la direction du premier plan médian (E1).
PCT/EP2020/051925 2019-01-28 2020-01-27 Ensemble d'engrenage WO2020157004A1 (fr)

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DE102019102078.6A DE102019102078B3 (de) 2019-01-28 2019-01-28 Getriebeanordnung

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