• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a torque transmission device, in particular for a motor vehicle, comprising first and second series gear trains (1, 2) arranged in series, each comprising an internal sun gear (1a, 2a), an external sun gear (1b, 2b), and a connecting member (1c, 2c, 16) cooperating with the internal (1a, 2a) and external (1b, 2b) planetary, the external planetary (1b, 2b) of the first and second planetary gear (1, 2) being connected to a fixed member (8), a torque input member (5) for being rotatably coupled to a crankshaft, the inner sun gear (2a) of the second sun gear (2) forming a torque output and being adapted to be coupled in rotation to an input shaft of a gearbox.
    公开号:FR3020427A1
    申请号:FR1453758
    申请日:2014-04-25
    公开日:2015-10-30
    发明作者:Herve Maurel；Christophe Mollier
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The invention relates to a torque transmission device, particularly for a motor vehicle, such as for example a double damping flywheel. Document US Pat. No. 7,341,524 discloses a double damping flywheel comprising a primary flywheel intended to be coupled in rotation to a crankshaft of an internal combustion engine, and a secondary flywheel intended to be coupled to a input shaft of a gearbox. Both flywheels are rotatable relative to each other. First damping elastic members extend circumferentially between the two flywheels, so as to oppose the rotation of a flywheel relative to the other. In operation, the angular position of the first flywheel relative to the second flywheel varies cyclically around an average angular position. The average angular position is dependent on the torque transmitted by the double damping flywheel to the gearbox. The variations around the average position are due to vibrations and rotational acyclisms of the motor. In addition, second elastic damping members are mounted between the two flywheels, the second damping members comprising at least one spring washer adapted to exert a positive or negative torque depending on the angular position of the secondary flywheel by compared to the primary flywheel. Positioning means make it possible to vary the position of the second damping means as a function of the average torque to be transmitted. These positioning means comprise a movable slide connected to the spring washer, and friction means arranged between a drawer and the secondary flywheel.
    [0002] Thus, around the average angular position, the action of the second damping members comes to oppose, at least partially, the action of the first damping members, so that the device has a global stiffness zero or almost zero in a limited angular range. This improves the quality of the damping and filtration performed by the device. The abovementioned friction means can cause shocks during a change in the torque to be transmitted by the device. Furthermore, the friction means must exert a force greater than the force exerted by the first resilient damping members, the force exerted by the friction means being otherwise difficult to manage. Finally, the amplitude of said angular range (on which the second damping means make it possible to reduce the overall stiffness of the device) is limited, in particular less than 100. These various drawbacks affect the quality of damping and filtration. . The invention is particularly intended to provide a simple, effective and economical solution to the aforementioned problems. For this purpose, it proposes a torque transmission device, in particular for a motor vehicle, characterized in that it comprises a first and a second series of planetary gear trains arranged in series, each comprising an internal sun gear, an external sun gear, and a connecting member cooperating with the inner and outer planetaries, said connecting member being movable relative to said inner and outer planetaries, the outer planetaries of the first and second planetary gears being connected to a fixed member, a torque input member, movable in rotation relative to the inner sun gear of the second sun gear, the torque input member being adapted to be coupled in rotation to a crankshaft, the inner sun gear of the second sun gear forming a torque output and being intended to be coupled in rotation to an input shaft of a gearbox, positioning means able to move and position the gearbox outer louvre of the first sun gear with respect to the fixed member, at least one first circumferentially extending damping member mounted between the torque input member and the inner sun gear of the second sun gear, and at least one second damping member extending generally radially, prestressed in its radial position, and connecting the torque input member and the inner sun gear of the first sun gear, the damping system formed by the first damping member and the second damping member being designed to form an overall stiffness, exerted between the input and the torque output, of reduced value with respect to the stiffness of the first damping member, for example a global stiffness of zero value, on a determined angular range of the torque input relative to the torque output. Thus, according to the invention, the second damping member is adapted to generate a torque on the inner sun gear of the first sun gear. The torque generated by the second damping member varies between a maximum value and a minimum value. The angular range located between the angular position corresponding to the maximum torque and the angular position corresponding to the minimum torque can be divided into a first half where the torque generated by the second damping member is positive, followed by a second half where the torque generated by the second damping member is negative. Throughout said aforementioned angular range, the slope of the curve representing the torque as a function of the angular position of the torque input relative to the torque output, that is to say the stiffness equivalent or brought back between the input and torque output) of the second damping member is negative. Thus, on said angular range, the second damping member generates a negative stiffness opposing the positive stiffness, for example constant, of the first damping member. The overall stiffness exerted between the input and the torque output therefore has a reduced value, which can be zero or almost zero depending on the sizing of the first and second damping members. The invention thus proposes a damping device having a reduced or zero stiffness over a given angular range. In operation, when the average torque transmitted by the transmission device is modified, that is to say when the operating point of the device is changed, the positioning means actuate the displacement of the outer sun gear of the first sun gear so as to recentering the aforementioned angular range around the operating point. In other words, when the average torque transmitted is changed, the average angular position of the torque input member is changed relative to the inner sun gear of the second epicyclic gear. Indeed, the first damping member is more or less compressed, depending on the average torque to be transmitted. The positioning means then allow to bring the second damping member into its radial position, through the external sun gear, the connecting member and the inner sun gear of the first sun gear. Of course, the position of the torque input member relative to the inner sun gear of the second sun gear varies around the average position, in order to damp vibrations and motor rotation acyclisms. Furthermore, the use of two planetary gear sets the total gear ratio of the device, that is to say the ratio of the speed of rotation of the inner sun gear of the second planetary gear on the speed of rotation of the sun gear. internal of the first planetary gear (or the speed of rotation of the torque input member), depending on the characteristics of the internal and external planetary and the connecting members. It will be noted that, in operation, most of the torque transmitted by the device passes successively through the torque input member, the first damping member and the internal sun gear of the second damping member, only a small portion of the torque transmitted by the device passing through all the elements of the planetary gear. The efficiency of such a device is thus improved, in particular in the case where planetary gears are planetary gear trains with a large number of gears generating friction and significant losses. According to one characteristic of the invention, the positioning means comprise calculation and control means able to control the position of the external sun gear of the first epicyclic gear train, so as to maintain the second damping member in the radial direction, for example to from a mean torque setpoint transmitted by said device. Preferably, the first damping member comprises at least one curved or straight helical spring. In addition, the positioning means may comprise a worm meshing with a toothed portion of the outer sun gear of the first epicyclic gear. In addition, the first and second planetary gear can be designed so that the total gear ratio, that is to say the ratio of the speed of rotation of the inner sun gear of the second planetary gear on the speed of rotation of the planetary gear of the first planetary gear, equal to 1. Such a feature facilitates the integration of the device to existing gearboxes. The outer sun gear of the second sun gear can be fixed relative to the fixed member. According to one embodiment of the invention, each planetary gear train is an epicyclic gear train comprising an internal sun gear formed by a toothed wheel, an external sun gear formed by a ring gear, and at least one connecting member formed by a satellite meshing with the inner sun gear and with the external sun gear of the corresponding epicyclic gear train, the satellites of the two planetary gear trains being pivotally mounted about an axis of a planet carrier common to the two planetary gear trains. According to another embodiment of the invention, each planetary gear train is a magnetic planetary gear train, the inner and outer planetary gears being formed by an alternation of permanent magnet poles, the connecting members of the two planetary gears being formed by a ring common to both planetary gear and having ferromagnetic polar elements distributed over the entire circumference of the ring. A magnetic planetary gear train does not generate wear, shock or noise, does not require lubrication, and has a long service life. According to an alternative embodiment, the device may comprise friction means located between the inner sun gear of the first sun gear and the torque input member, said friction means being able to generate a hysteresis outside said determined angular range. e such variant allows to have a high hysteresis, if the operating conditions require it, for example when starting the engine, around the operating point. Finally, the torque input member can be rotatably coupled to a primary flywheel, the inner sun gear of the second sun gear being rotatably coupled to a secondary flywheel. The device thus forms a double damping flywheel (D.V.A.). The invention will be better understood and other details, characteristics and advantages of the invention will appear on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which: FIG. Schematic sectional view of a torque transmission device according to a first embodiment of the invention, Figure 2 is a side view of a portion of the device of Figure 1, in a first angular position of the torque input member relative to the inner sun gear of the first epicyclic gear, FIG. 3 is a view corresponding to FIG. 2, illustrating a second angular position of the torque input member with respect to the internal sun gear of the first gear train. 4 is a diagram showing the torque transmitted by the first elastic damping members, as a function of the angular position of the internal sun gear of the second tread. 1 is an epicyclic diagram with respect to the torque input member, FIG. 5 is a diagram showing the torque transmitted by the second elastic damping members, as a function of the angular position of the internal sun gear of the second epicyclic gear with respect to the torque input member, FIG. 6 is a diagram representing the torque transmitted by the device according to the invention, as a function of the angular position of the internal sun gear of the second epicyclic gear with respect to the torque input member, Figure 7 is a view corresponding to Figure 1, illustrating a second embodiment of the invention, Figures 8 and 9 are views respectively corresponding to Figures 2 and 3, illustrating an alternative embodiment of the invention. Figures 1 to 6 illustrate a torque transmission device according to a first embodiment of the invention. The device comprises first and second epicyclic gear trains 1, 2, arranged in series. Each epicyclic gear train 1, 2 comprises an internal sun gear 1 a, 2 a formed by a toothed wheel, an external sun gear b, 2 b formed by a ring gear, and satellites 1 c, 2 c formed by toothed wheels meshing with the internal sun wheels. la, 2a and external lb, 2b corresponding. The device further comprises a torque input member 5, rotatable about an axis A, rotatably coupled to a primary flywheel 3. The inner sun gear 2a of the second epicyclic gear 2 is rotatably coupled to a secondary flywheel 4. The device thus forms a double damping flywheel (DVA). The satellites 1c, 2c of the two planetary gear trains 1, 2 are pivotally mounted about axes 6 of a planet carrier 7 common to the two epicyclic gear trains 1, 2. The internal planes 1a, 2a and the external sun gear 1b, 2b pivot about a common axis, namely around the axis A. The outer sun gear 2b of the second epicyclic gear 2 is fixed relative to a fixed member 8.
    [0003] First damping members 9, such as for example curved or straight helical compression springs, are mounted circumferentially between the torque input member 5 and the inner sun gear 2a of the second epicyclic gear train 2. The external sun gear lb of first epicyclic gear 1 comprises a toothed portion 10 meshing with a worm 11. The worm 11 is rotated by an electric motor, for example, so as to drive in rotation and angularly position the external sun gear lb of the first train epicyclic 1 relative to the fixed member 8. The worm 11 and the outer sun gear lb of the first epicyclic gear train 1 form an irreversible system: the transmission of movement can be done only worm 11 to the external sun gear. lb of the first epicyclic gear 1, so as to be able to stop the electric motor when it is not necessary to move the external sun gear lb of the first epicyclic gear train 1.
    [0004] Second elastic damping members 12, such as for example radial springs, extend radially generally between the torque input member 5 and the inner sun gear 1a of the first sun gear 1. The second damping members 12 are prestressed in their radial position, illustrated in Figure 2, and articulated on the torque input member 5 and on the inner sun gear 1 a.
    [0005] In operation, a mean torque is transmitted from the torque input member 5 to the inner sun gear 2a of the second epicyclic gear train 1. As indicated above, for the same average torque to be transmitted, the angular position of the primary flywheel 3 by ratio to the secondary flywheel 4 may vary around a mean angular position a0 representing the operating point of the device, in order to damp vibrations and rotational acyclisms. The diagram of FIG. 4 is the characteristic curve of the first damping means 9, representing the torque that can be transmitted by the first damping members 9 as a function of the angular position a of the primary flywheel 3 with respect to the secondary flywheel 4 It is noted that the characteristic curve of the first damping means 9 has a constant slope, whatever the value of the angular position a. In other words, the stiffness K1 of the first damping means 9 is substantially constant. The diagram of FIG. 5 is the characteristic curve of the second damping means 12, representing the torque that can be transmitted by the second damping members 12 as a function of the angular position a of the primary flywheel 3 with respect to the secondary flywheel 4 It can be seen that the second damping members 12 are able to generate a torque on the inner sun gear 1a of the first sun gear 1. The torque generated by the second damping members 12 varies between a maximum value and a minimum value.
    [0006] The angular range Aa situated between the angular position corresponding to the maximum torque and the angular position corresponding to the minimum torque can be divided into a first half where the torque generated by the second damping members 12 is positive, followed by a second half where the torque generated by the second damping members 12 is negative. Throughout said aforementioned angular range Aa, the slope of the curve of FIG. 5, that is to say the equivalent stiffness K2 of the second damping members 12, is negative, said stiffness K2 being brought back between the inlet and the couple release.
    [0007] Thus, on said angular range Aa, the second damping members 12 generate a negative stiffness K2 opposing the positive stiffness K1 of the first damping member 9. The overall stiffness K exerted between the primary flywheel 3 and the secondary flywheel 4 therefore has a reduced value, which can be zero or almost zero depending on the dimensioning of the first and second damping members 9, 12. This is illustrated in the diagram of FIG. 6, which represents the characteristic curve of the device damping, namely the torque adapted to be transmitted by the device according to the angular position of the primary flywheel 3 relative to the secondary flywheel 4. It can be seen that this curve comprises a zone 13 forming a substantially horizontal plateau , that is to say a slope or global stiffness K zero or almost zero. This zone 13 of zero stiffness is centered around a value a0 of angular position. In order to guarantee the proper functioning of the device, it is necessary to ensure that this value a0 corresponds to the operating point of the device, that is to say to the angular position of the primary flywheel 3 with respect to the secondary flywheel 4 corresponding to the average torque to be transmitted. For this purpose, the angular position of the inner sun gear 30 of the first epicyclic gear train 1 is regulated by means of the calculation and control means, the worm gear 11, as well as the external sun gear lb and the satellite lc of the first gear 1. When the average torque to be transmitted is changed, the angular position of the primary flywheel 3 relative to the secondary flywheel 4 is modified as well as the angular position of the torque input member 5 relative to the internal sun gear of the first This has the effect of inclining the second damping members 12 with respect to the radial direction (FIG. 3). In the position illustrated in FIG. 3, the second damping members 12 thus tend to exert a positive or negative torque on the internal sun gear 1a of the first epicyclic gear train 1. As indicated above, the calculation and control means reposition then the outer sun gear lb and, indirectly, the inner sun gear 1 a, so that the second damping members 12 find their radial position, illustrated in Figure 2, in which they exert no torque on the internal sun gear. 1 a. Of course, in operation, the angular position a of the primary flywheel 3 relative to the secondary flywheel 4 may vary, around the position a0, that is to say around the operating point, in a limited angular range, preferably in the aforementioned Aa beach.
    [0008] Note also that, in operation, the majority of the torque transmitted by the device passes successively through the torque input member 5, the first damping members 9 and the inner sun gear 2a, while a small portion of the torque is intended to successively pass through the torque input member 5, the second damping members 12 and then the different elements of the two planetary gear trains 1, 2. This prevents significant losses through the various gears of the planetary gear trains 1, 2, which improves the performance of such a device. FIG. 7 illustrates a torque transmission device according to a second embodiment of the invention, which differs from that described with reference to FIGS. 1 to 6 in that the epicyclic gear trains 1, 2 have been replaced by magnetic planetary gear trains. 1, 2. Thus, the inner planetary la, 2a and the outer planetary 1b, 2b each comprise alternating poles of permanent magnets 14, 15 distributed over the entire circumference. A common ring 16 to the two planetary gear 1, 2 is mounted radially between the inner planetary 1a, 2a and external 1b, 2b, said ring 16 having ferromagnetic polar elements 17 distributed over the entire circumference of the ring 16. L ring 16 is mounted on a bearing 18 so as to pivot relative to the axis A. The operation of such a device is identical to that described above. As previously indicated, magnetic planetary gear trains 1, 2 do not generate wear, shock or noise, do not require lubrication, and have a long service life.
    [0009] Figures 8 and 9 illustrate an alternative embodiment of the invention, which differs from the embodiment described with reference to Figures 1 to 6 in that the torque transmission device comprises friction means or hysteresis 19 mounted between the torque input member 5 and the inner sun gear la, for example. These friction means 19 are active only in an angular operating range located outside the negative stiffness zone Aa. The objective of such a variant is to have a high hysteresis, if the operating conditions require it, for example when starting the engine, around the point of operation.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. Torque transmission device, in particular for a motor vehicle, characterized in that it comprises a first and a second planetary gear set (1,
    [0002]
    2) arranged in series, each comprising an internal sun gear (la, 2a), an external sun gear (lb, 2b), and a connecting member (1c, 2c, 16) cooperating with the internal (1a, 2a) and external planetaries. (lb, 2b), said connecting member (1c, 2c, 16) being movable with respect to said internal (1a, and external (1b, 2b) planetary, the external planetary (1b, 2b) of the first and second planetary gear ( 1, 2) being connected to a fixed member (8), a torque input member (5) rotatable relative to the inner sun gear (2a) of the second sun gear (2), the input member having a torque (5) being rotatably coupled to a crankshaft, the inner sun gear (2a) of the second sun gear (2) forming a torque output and being adapted to be rotatably coupled to an input shaft of a gearbox, positioning means (11) able to move and position the outer sun gear (lb) of the first sun gear (1) by port to the fixed member (8), at least a first damping member (9) extending circumferentially and mounted between the torque input member (5) and the inner sun gear (2a) of the second sun gear (2), and at least one second generally radially extending second damping member (12) prestressed in its radial position, and connecting the torque input member (5) and the internal sun gear (1a) of the first planetary gear (1), the damping system formed by the first damping member (9) and the second damping member (12) being designed to form an overall stiffness, exerted between the inlet (5) and the output (2a) of torque, of reduced value with respect to the stiffness of the first damping member (9), for example a global stiffness of zero value, over a determined angular range (ta) of the torque input ( 5) with respect to the torque output (2a). 2. Device according to claim 1, characterized in that the positioning means comprise calculation and control means adapted to control the position of the outer sun gear (lb) of the first epicyclic gear (1), so as to maintain the second gear member. damping (12) in the radial direction, for example from a mean torque setpoint transmitted by said device.
    [0003]
    3. Device according to claim 1 or 2, characterized in that the first damping member (9) comprises at least one curved or straight helical spring.
    [0004]
    4. Device according to one of claims 1 to 3, characterized in that the positioning means comprising a worm (11) meshing with a toothed portion (10) of the outer sun gear (Ib) of the first epicyclic gear (1). ).
    [0005]
    5. Device according to one of claims 1 to 4, characterized in that the first and second planetary gear (1, 2) are designed so that the total gear ratio, that is to say the ratio the rotational speed of the inner sun gear (2a) of the second sun gear (2) on the rotational speed of the inner sun gear (1a) of the first sun gear (1) is equal to 1.
    [0006]
    6. Device according to one of claims 1 to 5, characterized in that the outer sun gear (2b) of the second sun gear (2) is fixed relative to the fixed member (8). 25
    [0007]
    7. Device according to one of claims 1 to 6, characterized in that each planetary gear (1, 2) is an epicyclic gear comprising an internal sun gear (la, 2a) formed by a gear wheel, an external sun gear (lb, 2b) formed by a ring gear, and at least one connecting member (1c, 2c) formed by a satellite meshing with the inner sun gear (1a, 2a) and with the external sun gear (1b, 2b) of the corresponding epicyclic gear ( 1, 2), the satellites (1c 2c) of the two planetary gear trains (1, 2) being mounted pivoting about an axis (6) of a planet carrier (7) common to the two planetary gear trains (1, 2).
    [0008]
    8. Device according to one of claims 1 to 7, characterized in that each planetary gear (1, 2) is a magnetic planetary gear, the inner planetary (la, 2a) and the external planetary (lb, 2b) being formed by an alternation of permanent magnet poles (14, 15), the connecting members of the two planetary gears being formed by a ring (16) common to the two planetary gears and comprising ferromagnetic polar elements (17) distributed over the entire circumference of the ring (16).
    [0009]
    9. Device according to one of claims 1 to 8, characterized in that it comprises friction means (19) between the inner sun gear (la) of the first sun gear (1) and the input member of torque (5), said friction means (19) being able to generate a hysteresis outside the determined angular range (da).
    [0010]
    10. Device according to one of claims 1 to 9, characterized in that the torque input member (5) is rotatably coupled to a primary flywheel (3), the inner sun gear (2a) of second sun gear (2) being rotatably coupled to a secondary flywheel (4).
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    同族专利:
    公开号 | 公开日
    FR3020427B1|2016-04-29|
    DE102015106117A1|2015-10-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1120832B|1954-01-01|1961-12-28|Thomas Hindmarch|Epicyclic gear with a friction brake operated by pressure medium|
    FR2916504A1|2007-05-22|2008-11-28|Valeo Embrayages|DUAL SHOCK ABSORBER WITH EPICYCLOIDAL TRAIN.|
    DE102012212961A1|2012-07-19|2014-01-23|Zf Friedrichshafen Ag|Torque transmission device for use as preassembled unit in clutch housing for transmission of torque of motor of motor car on gear box, has rotating element coacted with gear wheel, and coupling device coacted with stationary housing|
    EP1566566B1|2004-02-18|2008-04-16|LuK Lamellen und Kupplungsbau Beteiligungs KG|Torsional vibration damper|DE102015221893A1|2015-11-06|2017-05-11|Zf Friedrichshafen Ag|Torsional vibration damping arrangement for the drive train of a vehicle|
    DE102015221894A1|2015-11-06|2017-05-11|Zf Friedrichshafen Ag|Torsional vibration damping arrangement for the drive train of a vehicle|
    US10247292B2|2016-08-10|2019-04-02|GM Global Technology Operations LLC|Vehicle starting clutch-damper assembly|
    US10119604B2|2016-11-15|2018-11-06|GM Global Technology Operations LLC|Damper architectures|
    法律状态:
    2015-04-30| PLFP| Fee payment|Year of fee payment: 2 |
    2015-10-30| PLSC| Search report ready|Effective date: 20151030 |
    2016-04-28| PLFP| Fee payment|Year of fee payment: 3 |
    2017-04-28| PLFP| Fee payment|Year of fee payment: 4 |
    2018-04-26| PLFP| Fee payment|Year of fee payment: 5 |
    2019-04-29| PLFP| Fee payment|Year of fee payment: 6 |
    2020-04-30| PLFP| Fee payment|Year of fee payment: 7 |
    2021-04-29| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1453758A|FR3020427B1|2014-04-25|2014-04-25|TORQUE TRANSMISSION DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|FR1453758A| FR3020427B1|2014-04-25|2014-04-25|TORQUE TRANSMISSION DEVICE, IN PARTICULAR FOR A MOTOR VEHICLE|
    DE102015106117.1A| DE102015106117A1|2014-04-25|2015-04-21|Device for transmitting a torque, in particular for a motor vehicle|
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