JP2017110742A - Power transmission device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure capable of suppressing rattling noise generated by fitting parts formed in a rotational shaft constituting a power transmission device.SOLUTION: Even in a case where since a rubber elastic body 54 is interposed between an output side rotational shaft 32 and a rotor shaft 34, looseness formed at a spline fitting part 52 between the output side rotational shaft 32 and the rotor shaft 34 cannot be eliminated, the output side rotational shaft 32 and a rotational shaft of the rotor shaft can be held without looseness by the rubber elastic body 54 to suppress rattling noise generated by the spline fitting part 52. Since in the rubber elastic body 54, formed is a pressure receiving unit 68 configured to receive oil pressure of working fluid supplied from the output side rotational shaft 32, the rubber elastic body 54 can be pushed against the rotor shaft 34 by the oil pressure to obtain high holding torque.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a power transmission device provided in a vehicle, and particularly relates to suppression of rattling noise generated at a fitting portion formed on a power transmission path.

  It is known that a rattling noise is generated in a fitting portion formed between rotating shafts constituting a power transmission device provided in a vehicle due to a collision of teeth between backlashes formed in the fitting portion. Measures for suppressing this rattling noise have been proposed. For example, in the power transmission device of Patent Document 1, the rotor shaft of the second electric motor constitutes a part of the power transmission path from the engine to the drive wheels. Therefore, since the direct torque of the engine is transmitted to the rotor shaft, the spline teeth of the rotor shaft are pressed against the spline teeth of the other rotating shaft while the engine is driven even if the torque of the second motor is near zero. It will be in the state. Therefore, the play between the spline teeth of the rotor shaft and the spline teeth of the other rotating shaft is packed, and the occurrence of rattling noise is suppressed.

International Publication No. 2013/080311 JP-A-4-362346 JP 2012-52638 A

  By the way, in the power transmission device of Patent Document 1, the backlash of the rotor shaft of the second electric motor is packed on the power transmission path between the engine and the second electric motor, but the torque input to the transmission is reduced. When near zero, the play formed between the input shaft of the transmission disposed on the downstream side (drive wheel side) of the second electric motor and the rotor shaft of the second electric motor is not clogged. Therefore, if the torque input to the transmission is close to zero, rattling noise may occur due to rattling of the fitting portion formed between the rotor shaft of the second motor and the input shaft of the transmission. It was. In addition, although patent document 1 was a hybrid type power transmission device, the problem similar to patent document 1 will generate | occur | produce if it is a structure in which a fitting part is formed between rotating shafts.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is a structure capable of suppressing rattling noise generated at a fitting portion formed between rotating shafts constituting a power transmission device. Is to provide.

  The gist of the first invention is that: (a) a fitting portion that is connected so that power can be transmitted by fitting the first rotating shaft and the second rotating shaft arranged around a common axis line; (B) An elastic body is interposed between the first rotating shaft and the second rotating shaft in the vicinity of the fitting portion in the direction of the axis. (C) an oil passage for supplying hydraulic oil is formed inside one of the first rotating shaft and the second rotating shaft, and (d) the elastic body has Is characterized in that a pressure receiving portion that receives the hydraulic pressure of the hydraulic oil supplied from the oil passage directly or indirectly in the direction toward the other rotating shaft is formed.

  According to the vehicle power transmission device of the first aspect of the present invention, since the elastic body is interposed between the first rotating shaft and the second rotating shaft, the fitting portion between the first rotating shaft and the second rotating shaft. Even if the backlash formed is not clogged, the rotation shafts of both the first rotation shaft and the second rotation shaft are held by the elastic body without rattling. Therefore, the rattling noise generated at the fitting portion can be suppressed.

  Further, since the elastic body is formed with a pressure receiving portion that receives the hydraulic pressure of the hydraulic oil supplied from one rotating shaft, the pressure receiving portion is pressed by the hydraulic pressure of the hydraulic oil supplied to the oil passage, and the elastic body Pressed against the other rotating shaft. Thus, since the pressing force with which the elastic body presses the other rotating shaft increases, the holding torque for holding the first rotating shaft and the second rotating shaft generated by this pressing force increases. That is, in addition to the holding torque due to the compression when the elastic body is assembled, the holding torque due to the oil pressure of the oil passage is generated, so that a higher holding torque can be obtained.

1 is a skeleton diagram illustrating a power transmission device of a hybrid vehicle to which the present invention is applied. It is sectional drawing which shows a part of power transmission device of FIG. FIG. 3 is a cross-sectional view of the first inlay portion of FIG. 2 cut along a cutting line A. It is sectional drawing which shows a part of power transmission device which is another Example of this invention. It is sectional drawing of the 1st spigot part which is further another Example of this invention.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a skeleton diagram illustrating a power transmission device 10 for a hybrid vehicle to which the present invention is applied. In FIG. 1, a power transmission device 10 includes an input shaft 14 as an input rotation member disposed on a common axis C in a transmission case 12 (hereinafter referred to as case 12) as a non-rotation member attached to a vehicle body. The differential unit 11 (electrical differential unit) as a continuously variable transmission unit directly connected to the input shaft 14 or indirectly through a pulsation absorbing damper (vibration damping device) (not shown), and the differential An automatic transmission 20 connected in series via a transmission member 18 on a power transmission path from the section 11 to a drive wheel (not shown), and an output shaft 22 as an output rotating member connected to the automatic transmission 20 Are provided in series. The power transmission device 10 is preferably used for, for example, an FR (front engine / rear drive) type vehicle vertically installed in a vehicle, and directly to the input shaft 14 or directly via a pulsation absorbing damper (not shown). As a driving power source connected to the engine 8, for example, an engine 8 which is an internal combustion engine such as a gasoline engine or a diesel engine and a drive wheel are provided. Then, the power from the engine 8 is transmitted to the drive wheels sequentially through a differential gear device (final reduction gear) (not shown) that constitutes a part of the power transmission path and the axle.

  Thus, in the power transmission device 10 of the present embodiment, the engine 8 and the differential unit 11 are directly connected. This direct connection means that the connection is made without passing through a hydraulic power transmission device such as a torque converter or a fluid coupling. For example, the connection via the pulsation absorbing damper is included in this direct connection.

  The differential unit 11 is connected to a power transmission path between the engine 8 and the drive wheels, and functions as a differential motor that controls the differential state of the input shaft 14 and the transmission member 18 (output shaft). 1 is a mechanical mechanism that mechanically distributes the output of the engine 8 input to the electric motor MG1 and the input shaft 14 and that is a differential mechanism that distributes the output of the engine 8 to the first electric motor MG1 and the transmission member 18. A moving planetary gear unit 24, a second electric motor MG2 operatively connected to rotate integrally with a transmission member 18 functioning as an output shaft, and a fixed brake B0 for stopping the rotation of the input shaft 14. Have. The first motor MG1 and the second motor MG2 of the present embodiment are so-called motor generators that also have a power generation function, but the first motor MG1 has at least a generator (power generation) function for generating a reaction force, and the second motor Since MG2 functions as a traveling motor that outputs driving force as a driving force source for traveling, it has at least a motor (motor) function.

  The differential planetary gear unit 24 functioning as a differential mechanism is mainly configured by a single pinion type differential planetary gear unit 24 having a predetermined gear ratio. This differential planetary gear unit 24 is differentially provided via a differential sun gear S0, a differential planetary gear P0, a differential carrier CA0 that supports the differential planetary gear P0 so as to rotate and revolve, and a differential planetary gear P0. A differential ring gear R0 meshing with the sun gear S0 is provided as a rotating element.

  In the differential planetary gear unit 24, the differential carrier CA0 is connected to the input shaft 14, that is, the engine 8 to form the first rotating element RE1, and the differential sun gear S0 is connected to the first electric motor MG1 to perform the second rotation. The element RE2 is configured, and the differential ring gear R0 is connected to the transmission member 18 to configure a third rotating element RE3. The differential planetary gear unit 24 configured in this way is configured such that the differential sun gear S0, the differential carrier CA0, and the differential ring gear R0, which are the three elements of the differential planetary gear unit 24, can rotate relative to each other. The differential action can be activated, that is, the differential state is activated. As a result, the output of the engine 8 is distributed to the first electric motor MG1 and the transmission member 18, and a part of the distributed output of the engine 8 is stored with the electric energy generated from the first electric motor MG1. Electric motor MG2 is rotationally driven. Therefore, the differential unit 11 is caused to function as an electrical differential device. For example, the differential unit 11 is in a so-called continuously variable transmission state, and the rotation of the transmission member 18 is continuously changed regardless of the predetermined rotation of the engine 8. That is, the differential unit 11 is an electric continuously variable transmission whose speed ratio (the rotational speed Nin of the input shaft 14 / the rotational speed N18 of the transmission member 18) is continuously changed from the minimum value γ0min to the maximum value γ0max. Function.

  The automatic transmission 20 constitutes a part of a power transmission path between the engine 8 and driving wheels, and includes a single pinion type first planetary gear device 26 and a single pinion type second planetary gear device 28. It is a planetary gear type multi-stage transmission that functions as a stepped automatic transmission. The first planetary gear unit 26 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear S1 via the first planetary gear P1. The first ring gear R1 that meshes with the first gear R1 and has a predetermined gear ratio. The second planetary gear device 28 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. And a second ring gear R2 that meshes with each other, and has a predetermined gear ratio.

  In the automatic transmission 20, the first sun gear S1 is selectively coupled to the case 12 via the first brake B1. Further, the first carrier CA1 and the second ring gear R2 are integrally connected and connected to the transmission member 18 via the second clutch C2, and selectively connected to the case 12 via the second brake B2. ing. Further, the first ring gear R1 and the second carrier CA2 are integrally connected and connected to the output shaft 22. Further, the second sun gear S2 is selectively coupled to the transmission member 18 via the first clutch C1. Further, the first carrier CA1 and the second ring gear R2 are connected to the case 12 which is a non-rotating member via the one-way clutch F1, so that the rotation in the same direction as the engine 8 is allowed, while the rotation in the reverse direction is allowed. Is prohibited. Thus, the first carrier CA1 and the second ring gear R2 function as rotating members that cannot be rotated in reverse.

  The automatic transmission 20 is configured so that a clutch-to-clutch shift is executed by releasing the disengagement-side engagement device and engaging the engagement-side engagement device, so that a plurality of shift speeds are selectively established. A gear ratio γ (= rotational speed N18 of the transmission member 18 / rotational speed Nout of the output shaft 22) that changes with time is obtained for each gear position.

  FIG. 2 is a cross-sectional view showing a part of the power transmission device 10. In the power transmission device 10 of FIG. 2, a cross-sectional view of a transmission member 18 mainly functioning as an output shaft of the differential section 11 and a second electric motor MG <b> 2 connected to the transmission member 18 is illustrated. The transmission member 18 includes an input side rotary shaft 30 connected to the differential ring gear R0 of the differential planetary gear device 24, an output side rotary shaft 32 that also functions as an input shaft of the automatic transmission 22, and a second electric motor MG2. The rotor shaft 34 is configured. The input side rotation shaft 30, the output side rotation shaft 32, and the rotor shaft 34 are all arranged around the same axis C. The output side rotating shaft 32 corresponds to the first rotating shaft and one rotating shaft of the present invention, and the rotor shaft 34 corresponds to the second rotating shaft and the other rotating shaft of the present invention.

  The input side rotary shaft 30 and the output side rotary shaft 32 are arranged at positions separated in the direction of the axis C when viewed from the outside in the radial direction, and between the input side rotary shaft 30 and the output side rotary shaft 32, The rotor shaft 34 of the second electric motor MG2 is connected.

  The rotor shaft 34 of the second electric motor MG2 is formed in a cylindrical shape, and is disposed so as to cover the outer peripheral ends (tips) of the input-side rotating shaft 30 and the output-side rotating shaft 32 that face each other in the axis C direction. The rotor shaft 34 is rotatably supported at one end of the outer circumference in the direction of the axis C by a motor cover 37 connected to the case 12 via a bearing 35a, and the other end of the outer circumference in the direction of the axis C is placed via a bearing 35b. 12 is rotatably supported. Further, the output side rotating shaft 32 is rotatably supported by the case 12 via a bearing 36 or the like.

  The input-side rotating shaft 30 has outer peripheral teeth 38 formed on the outer peripheral surface facing the output-side rotating shaft 32 in the axis C direction. On the output-side rotating shaft 32, outer peripheral teeth 40 having the same shape as the outer peripheral teeth 38 of the input-side rotating shaft 30 are formed on the outer peripheral surface on the side facing the input-side rotating shaft 30 in the axis C direction. On the inner peripheral side of the rotor shaft 34 of the second electric motor MG2 formed in a cylindrical shape, inner peripheral teeth 42 that are spline-fitted with the outer peripheral teeth 38 and the outer peripheral teeth 40 are formed. The outer peripheral teeth 38 of the input side rotating shaft 30 and the inner peripheral teeth 42 of the rotor shaft 34 are spline-fitted, and the outer peripheral teeth 40 of the output side rotating shaft 32 and the inner peripheral teeth 42 of the rotor shaft 34 are splined. It is mated. The outer peripheral teeth 38 of the input-side rotary shaft 30 and the inner peripheral teeth 42 of the rotor shaft 34 are spline-fitted to each other so that the input-side rotary shaft 30 and the rotor shaft 34 can be connected to each other so that power can be transmitted (relative rotation is impossible). A spline fitting portion 50 is formed. Further, the outer peripheral teeth 40 of the output-side rotary shaft 32 and the inner peripheral teeth 42 of the rotor shaft 34 are spline-fitted to each other so that power can be transmitted between the output-side rotary shaft 32 and the rotor shaft 34 (relative rotation is impossible). A spline fitting portion 52 is formed to be connected to. Note that the spline fitting portion 52 corresponds to the fitting portion of the present invention.

  A rotor 46 constituting the second electric motor MG2 is fixed to the outer peripheral surface of the rotor shaft 34, and a stator 48 constituting the second electric motor MG2 is disposed on the outer peripheral side of the rotor 46. The rotor 46 is configured by laminating a plurality of steel plates. Similarly, the stator 48 is configured by laminating a plurality of steel plates, and is fixed to the case 12 so as not to rotate by a bolt (not shown). In addition, coil ends 60 wound around the stator 48 are disposed on both sides of the stator 48 in the axis C direction.

  In the power transmission device 10 configured as described above, when the torque of the engine 8 is transmitted to the input side rotary shaft 30, the spline fitting portion 50 between the input side rotary shaft 30 and the rotor shaft 34 is used. Torque is transmitted to the rotor shaft 34. Further, torque is transmitted to the output-side rotary shaft 32 via a spline fitting portion 52 between the rotor shaft 34 and the output-side rotary shaft 32. Therefore, even if the torque is not output from the second electric motor MG <b> 2, the play formed in the spline fitting portion 50 between the input side rotating shaft 30 and the rotor shaft 34 is packed and generated in the spline fitting portion 50. The rattling noise is suppressed.

  By the way, when the torque input to the automatic transmission 20 is zero, the backlash formed by the spline fitting portion 52 between the rotor shaft 34 and the output-side rotating shaft 32 is not clogged. Sound may be generated. In order to solve this problem, in this embodiment, the rubber elastic body 54 is located near the spline fitting portion 52 in the direction of the axis C and between the portions where the rotor shaft 34 and the output-side rotating shaft 32 overlap in the radial direction. Is inserted. The rubber elastic body 54 corresponds to the elastic body of the present invention.

  An annular annular groove 56 is formed on the outer peripheral surface of the output side rotating shaft 32, and an annular rubber elastic body 54 is accommodated in the annular space formed by the annular groove 56. The rubber elastic body 54 has an annular shape (ring shape) and has a substantially circular cross section. Further, in a state where it is assembled between the output side rotating shaft 32 and the rotor shaft 34, it is compressed and deformed by being pressed by the output side rotating shaft 32 and the rotor shaft 34.

  Further, the rubber elastic body 54 is prevented from slipping with the outer peripheral surface of the output-side rotating shaft 32 and also with rubber elastic so as to prevent slipping with the inner peripheral surface of the rotor shaft 34. The friction coefficient μ between the body 54 and the output side rotation shaft 32 and the rotor shaft 34 is adjusted. For example, the surface roughness (surface roughness) of the rubber elastic body 54 is set so that the friction coefficient μ for preventing the slipping can be secured.

  An axial oil passage 72 parallel to the axis C and a first radial oil passage 74 that communicates the axial oil passage 72 and the annular groove 56 (annular space) are formed in the output-side rotating shaft 32. Yes. Further, the output-side rotating shaft 32 is formed with a second radial oil passage 75 that communicates the axial oil passage 72 and the supply oil passage 73 formed in the case 12. The first radial oil passages 74 are round holes extending radially outward from the axial oil passage 72, and are formed, for example, at four locations at equal angular intervals in the circumferential direction. The first radial oil passage 74 is opened at the groove bottom of the annular groove 56, and the vicinity of the connection portion of the first radial oil passage 74 with the annular groove 56 is formed in a stepped shape. In a state where the rubber elastic body 54 is assembled, the rubber elastic body 54 is pressed radially inward by the rotor shaft 34, so that a part of the rubber elastic body 54 is in the first radial oil passage 74. To be pushed into. Thus, a part of the rubber elastic body 54 is embedded in the first radial oil passage 74, so that the first radial oil passage 74 is closed by the rubber elastic body 54. A portion of the rubber elastic body 54 that is pushed into the first radial oil passage 74 functions as a pressure receiving portion 68 that directly receives the hydraulic pressure of the hydraulic oil supplied to the first radial oil passage 74. The axial oil passage 72, the first radial oil passage 74, and the second radial oil passage 75 correspond to the oil passage of the present invention.

  As a result, the hydraulic oil supplied from the hydraulic control circuit (not shown) to the supply oil passage 73 of the case 12 is supplied to the first radial oil passage 74 through the second radial oil passage 75 and the axial oil passage 72. Then, the rubber elastic body 54 is pressed radially outward by the hydraulic pressure of the hydraulic oil. Accordingly, the rubber elastic body 54 is pressed against the rotor shaft 34 by the hydraulic pressure of the hydraulic oil.

  Further, the output-side rotation shaft 32 is formed with a first outer periphery inlay surface 76 between the outer peripheral teeth 40 and the annular groove 56 in which the rubber elastic body 54 is accommodated in the direction of the axis C. Further, a second outer spigot surface 78 is formed on the output side rotating shaft 32 at a position separating the annular groove 56 from the first outer spigot surface 76 in the axis C direction. That is, the second outer peripheral spigot surface 78 is formed at a position away from the first outer peripheral spigot surface 76 and the annular groove 56 in the direction of the axis C with reference to the outer peripheral teeth 40 of the output side rotating shaft 32. Therefore, an annular groove 56 in which the rubber elastic body 54 is accommodated is formed between the first outer periphery inlay surface 76 and the second outer periphery inlay surface 78 in the axis C direction.

  Further, on the inner peripheral side of the rotor shaft 34, an inner peripheral spigot surface 80 that is fitted to the first outer peripheral spigot surface 76 and the second outer peripheral spigot surface 78 after assembly is formed. The inner peripheral spigot surface 80 is set to a length that can be fitted to the first outer peripheral spigot surface 76 and the second outer peripheral spigot surface 78 in the axis C direction after assembly.

  When the first outer spigot surface 76 and the inner peripheral spigot surface 80 are fitted, it is a clearance fit, but the first outer spigot surface 76 and the inner peripheral spigot surface 80 are fitted together without rattling. The dimensions (dimension tolerance) of the outer peripheral inlay surface 76 and the inner peripheral inlay surface 80 are set. In addition, when the second outer peripheral spigot surface 78 and the inner peripheral spigot surface 80 are fitted, although they are clearance fits, the second outer peripheral spigot surface 78 and the inner peripheral spigot surface 80 are fitted together without rattling. The dimensions (dimension tolerance) of the second outer periphery inlay surface 78 and the inner periphery inlay surface 80 are set. In FIG. 2, a portion where the first outer spigot surface 76 of the output side rotary shaft 32 and the inner peripheral spigot surface 80 of the rotor shaft 34 are fitted together is defined as a first spigot portion 82, A portion where the two outer spigot surfaces 78 and the inner peripheral spigot surface 80 of the rotor shaft 34 are fitted together is defined as a second spigot portion 84. Thus, the first spigot portion 82 is formed between the spline fitting portion 52 and the rubber elastic body 54 in the axis C direction, and is adjacent to the rubber elastic body 54 in the axis C direction. A second spigot portion 84 is formed at a position opposite to the first spigot portion 82.

  The dimensions of the output side rotating shaft 32 and the rotor shaft 34 constituting the first inlay part 82 are made equal to the dimensions of the output side rotating shaft 32 and the rotor shaft 34 constituting the second inlay part 84. Specifically, the diameter (outer diameter) of the part where the first outer periphery inlay surface 76 of the output side rotating shaft 32 is formed and the part of the portion where the second outer periphery inlay surface 78 of the output side rotating shaft 32 is formed. The diameter (outer diameter) is equal. Further, in the rotor shaft 34, the diameter (inner diameter) of the hole in the portion where the inner peripheral spigot surface 80 of the first spigot portion 82 is formed is the portion where the inner peripheral spigot surface 80 of the second spigot portion 84 is formed. Is equal to the diameter (inner diameter) of the hole.

  3 is a cross-sectional view of the first spigot portion 82 of FIG. In FIG. 3, the left side is a view of the first spigot portion 82 as viewed from the direction of the axis C, and the right side is a view of the first spigot portion 82 as viewed from the outside in the radial direction.

  As shown in FIG. 3, when the first outer peripheral spigot surface 76 is viewed from the direction of the axis C, the first outer peripheral spigot surface 76 has grooves 86 parallel to the axis C passing through both sides in the axis C direction at equal angular intervals. A plurality of places (four places in this embodiment) are formed. By forming the groove 86 in the first outer spigot surface 76, a gap parallel to the axis C is formed between the first outer spigot surface 76 and the inner peripheral spigot surface 80 of the first spigot portion 82. Yes. Here, separately from the first radial oil passage 74, an oil passage (not shown) communicating with the annular space formed by the annular groove 56 is formed, and the lubricating oil is supplied from the oil passage. ing. The rubber elastic body 54 is cooled by the lubricating oil supplied from the oil passage. The lubricating oil that has cooled the rubber elastic body 54 is discharged through the groove 86. That is, the groove 86 functions as a lubricating oil discharge port.

  Further, the rubber elastic body 54 is sandwiched between the first inlay portion 82 and the second inlay portion in the direction of the axis C, so that the collapse allowance (deformation allowance) of the rubber elastic body 54 after assembly is stabilized. That is, since the eccentricity of the output side rotating shaft 32 and the rotor shaft 34 is suppressed by the first inlay portion 82 and the second inlay portion 84, the rubber elastic body 54 is attached to the rubber elastic body 54 in a state where the rubber elastic body 54 is assembled. The variation in the applied elastic energy is suppressed, and the variation in the holding torque by the rubber elastic body 54 for each product (device) is suppressed. Here, the holding torque is a torque generated by compressing and deforming the rubber elastic body 54 and acting in a direction in which the output-side rotating shaft 32 and the rotor shaft 34 are held without rattling.

  The rubber elastic body 54 is compressed and deformed between the output-side rotary shaft 32 and the rotor shaft 34 after assembly, so that the contact surface between the output-side rotary shaft 32 and the rubber elastic body 54, and the rotor A pressing force is generated between the shaft 34 and the contact surface of the rubber elastic body 54 to press the surfaces perpendicularly. Since a frictional resistance based on the pressing force and the coefficient of friction between the contact surfaces is generated, the rubber shaft 54 holds the rotor shaft 34 and the output-side rotating shaft 32 in the circumferential direction without rattling. Holding torque is generated. Therefore, in the spline fitting portion 52, even if the backlash in the rotational direction between the outer peripheral teeth 40 and the inner peripheral teeth 42 is not clogged, the rotor shaft 34 and the output side rotating shaft 32 are caused by the rubber elastic body 54. It is held without rattling. Therefore, rattling noise generated at the spline fitting portion 52 is suppressed.

  Further, in a state where the rubber elastic body 54 is assembled, a part of the rubber elastic body 54 is embedded in the first radial oil path 74, so that the first radial oil path 74 is made of the rubber elastic body 54. Blocked by. When the rubber elastic body 54 is pressed radially outward by the hydraulic pressure of the hydraulic oil in the first radial oil passage 74, the pressing force with which the rubber elastic body 54 presses the rotor shaft 34 increases, and the rubber The holding torque by the elastic body 54 increases. That is, in addition to the holding torque generated when the rubber elastic body 54 is compressed and deformed, the holding torque due to the hydraulic pressure of the first radial oil passage 74 is added, thereby increasing the holding torque.

  As described above, according to this embodiment, since the rubber elastic body 54 is interposed between the output-side rotary shaft 32 and the rotor shaft 34, the spline between the output-side rotary shaft 32 and the rotor shaft 34 is used. Even when the backlash formed in the fitting portion 52 is not clogged, both the output side rotary shaft 32 and the rotor shaft are held without backlash by the rubber elastic body 54, so that the spline fitting The rattling noise generated in the part 52 can be suppressed.

  In addition, according to the present embodiment, the rubber elastic body 54 is formed with the pressure receiving portion 68 that receives the hydraulic pressure of the hydraulic oil supplied from the output-side rotating shaft 32, so that the first elastic oil passage 74 is provided with the pressure receiving portion 68. The pressure receiving portion 68 is pressed by the hydraulic pressure of the supplied hydraulic oil, and the rubber elastic body 54 is pressed against the rotor shaft 34. In this way, in addition to the holding torque generated when the rubber elastic body 54 is compressed and deformed, a higher holding torque can be obtained by pressing the rubber elastic body 54 against the rotor shaft 34 by hydraulic pressure. .

  Next, another embodiment of the present invention will be described. In the following description, parts common to those in the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.

  FIG. 4 is a cross-sectional view of a power transmission device 100 according to another embodiment of the present invention, and corresponds to FIG. 2 of the above-described embodiment. When the power transmission device 10 of the above-described embodiment and the power transmission device 100 of the present embodiment are compared, the structure of the rubber elastic body and the mechanism for applying hydraulic pressure to the rubber elastic body are different. Hereinafter, the mechanism different from the above-described embodiment will be mainly described.

  The rubber elastic bodies 104 of the present embodiment are formed in a substantially spherical shape, and a plurality of rubber elastic bodies 104 are arranged at equal angular intervals in the circumferential direction. Specifically, for example, four elastic body accommodation holes 108 are formed at equal angular intervals on the outer peripheral surface of the output-side rotating shaft 102, and the rubber elastic body 104 is placed in the elastic body accommodation hole 108. Each is housed. Further, the elastic body accommodation hole 108 is connected to a first radial oil passage 110 described later. The rubber elastic body 104 corresponds to the elastic body of the present invention.

  The output-side rotating shaft 102 is formed with an axial oil passage 112 parallel to the axis C and a first radial oil passage 110 that communicates the axial oil passage 112 and the elastic body accommodation hole 108. Further, the output-side rotating shaft 102 is formed with a second radial oil passage 114 that communicates the axial oil passage 112 and the supply oil passage 73 formed in the case 12. Note that the output-side rotating shaft 102 corresponds to the first rotating shaft and one rotating shaft of the present invention, and the first radial oil passage 110, the axial oil passage 112, and the second radial oil passage 114 correspond to the present invention. It corresponds to the oil passage.

  A piston 116 is provided in the first radial oil passage 110. The piston 116 has a bottomed cylindrical shape, and an outer peripheral surface thereof is slidably fitted into an inner peripheral wall surface of the first radial oil passage 110. Further, it is assumed that an O-ring (not shown) is fitted between the outer peripheral surface of the piston 116 and the inner peripheral wall surface of the first radial oil passage 110. Accordingly, the piston 116 partitions the first radial oil passage 110 and the elastic body accommodation hole 108 in an oil-tight manner. One surface of the bottomed portion of the piston 116 is in contact with the rubber elastic body 104. Further, the other surface of the bottomed portion of the piston 116 receives the hydraulic pressure of the hydraulic oil in the first radial oil passage 110.

  By being configured as described above, the hydraulic oil supplied to the supply oil passage 73 of the case 12 passes through the second radial oil passage 114 and the axial oil passage 112 to the first radial oil passage 110. Supplied. At this time, the bottomed portion of the piston 116 is pressed radially outward by the hydraulic pressure of the hydraulic oil, whereby the piston 116 presses the rubber elastic body 104 radially outward, and the rubber elastic body 104 is driven by the piston 116 into the rotor shaft. 34 is pressed. Thus, since the pressing force with which the rubber elastic body 104 presses the rotor shaft 34 increases, the holding torque by the rubber elastic body 104 increases. That is, in addition to the holding torque generated when the rubber elastic body 104 is compressed and deformed, the holding torque due to the hydraulic pressure of the first radial oil passage 110 is added, thereby increasing the holding torque. The surface 118 pressed by the piston 116 of the rubber elastic body 104 corresponds to the pressure receiving portion of the present invention.

  As described above, this embodiment can provide the same effects as those of the above-described embodiment. Specifically, the rubber elastic body 104 indirectly receives the hydraulic pressure of the hydraulic oil supplied from the output-side rotating shaft 102 via the piston 116. As a result, the rubber elastic body 104 is urged radially outward and pressed against the rotor shaft 34, thereby increasing the holding torque. In this way, in addition to the holding torque generated when the rubber elastic body 104 is compressed and deformed, the holding torque is also generated when the rubber elastic body 104 is pressed against the rotor shaft 34 by hydraulic pressure. Holding torque can be obtained.

  FIG. 5 is a cross-sectional view of the first spigot portion 120 that is still another embodiment of the present invention, and corresponds to FIG. 3 of the above-described embodiment. In FIG. 5, only the first outer peripheral spigot surface 122 of the output-side rotating shaft 32 constituting the first spigot portion 120 is shown. In FIG. 5, the left side is a view of the first spigot portion 120 (first outer peripheral spigot surface 122) viewed from the direction of the axis C, and the right side is the first spigot portion 120 (first outer peripheral spigot surface 122) from the radially outer side. FIG.

  As shown in FIG. 5, when the first outer spigot surface 122 constituting the first spigot portion 120 is viewed from the direction of the axis C, grooves 124 passing through both sides in the direction of the axis C are equiangular on the first spigot surface 122. A plurality of locations (4 locations in this embodiment) are formed at intervals. As shown on the right side of FIG. 5, the groove 124 of this embodiment is not formed parallel to the axis C, but is twisted with respect to the axis C. That is, when the groove 124 is viewed from the outside in the radial direction, it is formed obliquely toward the circumferential direction.

  Even when the above-described first outer periphery inlay surface 122 is applied in place of the above-described first outer periphery inlay surface 76, the same effect as in the above-described embodiment can be obtained. Further, since the groove 124 of the first outer peripheral inlay surface 122 is formed to be twisted, the lubricating oil passing through the groove 124 is smoothly discharged so as to be pushed out of the groove 124.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the above-described embodiment, the power transmission device 10 is a hybrid power transmission device including two electric motors, but the present invention is not necessarily limited to the hybrid power transmission device of the present embodiment. For example, the present invention may be applied to a hybrid power transmission device including one electric motor or a power transmission device not including an electric motor. The present invention can be appropriately applied to any power transmission device that includes a fitting portion that is coupled to the power transmission device by fitting a pair of rotating shafts to each other. That is, the present invention is not limited to the spline fitting portion between the rotor shaft and the output side rotating shaft.

  In the above-described embodiment, the automatic transmission 20 is a stepped transmission with four forward stages, but the number of shift stages and the internal connection configuration are not particularly limited. Further, instead of the stepped automatic transmission 20, a continuously variable transmission such as a belt type continuously variable transmission may be applied.

  In the above-described embodiment, the first radial oil passages 74 and 110 are formed in four locations in the circumferential direction, but the number of the first radial oil passages 74 and 110 is not necessarily limited to four locations. You may change suitably. Further, the rubber elastic body 104 may be appropriately changed according to the number of the first radial oil passages 110.

  In the above-described embodiment, the first radial oil passage 74 is formed on the output-side rotating shaft 32 side. However, an oil passage is formed on the rotor shaft 34 side, and a rubber elastic body is formed by the oil pressure of the oil passage. 54 may be configured to be pressed against the output side rotation shaft 32.

  Further, in the above-described embodiment, the rubber elastic body 54 is formed in an annular shape, but the first radial oil passage is only in a portion that is fitted into the first radial oil passage 74 of the rubber elastic body 54. You may change a shape so that it may fit in 74 easily.

  In the above-described embodiment, the piston 116 is fitted into the first radial oil passage 110. However, the rubber elastic body 104 is directly fitted into the first radial oil passage 110 without the piston 116. It does not matter. In this case, the shape of the rubber elastic body 104 may be appropriately changed according to the shape of the first radial oil passage 110.

  In the above-described embodiment, the rubber elastic bodies 54 and 104 are made of rubber, but may be made of other materials such as resin.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

10, 100: Power transmission device 32, 102: Output side rotating shaft (first rotating shaft)
34: Rotor shaft (second rotary shaft)
52: Spline fitting part (fitting part)
54, 104: Rubber elastic body (elastic body)
68: Pressure receiving portion 72, 112: Axial direction oil passage (oil passage)
74, 110: first radial oil passage (oil passage)
75, 114: second radial oil passage (oil passage)

Claims (1)

In a vehicle power transmission device configured to include a fitting portion that is coupled so that power can be transmitted by fitting a first rotating shaft and a second rotating shaft that are arranged around a common axis.
An elastic body is interposed between the first rotating shaft and the second rotating shaft in the vicinity of the fitting portion in the direction of the axis,
An oil passage through which hydraulic oil is supplied is formed inside one of the first rotary shaft and the second rotary shaft,
The elastic body is formed with a pressure receiving portion that directly or indirectly receives the hydraulic pressure of the hydraulic oil supplied from the oil passage in a direction toward the other rotating shaft side. Power transmission device.

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