JP2013036480A - Vehicular power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular power transmission device which prevents bubbles generated by agitating a lubricating oil from entering a communication hole of a case.SOLUTION: In the vehicular power transmission device, in the communication hole 46h side upper part of an annular space 70 in a transaxle case 46, lubricating oil inlets 46i, 46j are provided which are disposed being separated by a predetermined distance in the circumferential direction of the annular space 70 from a transaxle case 46 inside opening of the communication hole 46h. A hydraulic fluid flowing in at the lubricating oil inlets 46i, 46j flows down from positions separated by the predetermined distance in the circumferential direction of the annular space 70 from the inside opening of the communication hole 46h in the communication hole 46h side upper part of the annular space 70 in the transaxle case 46 onto the outer circumferential surface 16b of a clutch drum 16a. Therefore, when the bubbles generated by agitating the lubricating oil are going to enter the communication hole 46h side of the annular space 70, they collide with the hydraulic fluid flowing in at the lubricating oil inlets 46i, 46j, so that the bubbles are eliminated.

Description

  The present invention relates to a vehicle power transmission device, and more particularly to a technique for preventing leakage of a lubricant from a breather device provided in the vehicle power transmission device.

  For example, as shown in Patent Documents 1 to 3, a type of vehicle power transmission device includes a case that houses a power transmission member that transmits power of a prime mover and is lubricated by lubricating oil, and an upper portion of an outer peripheral wall portion of the case A communication hole that communicates the outside of the case with the inside of the case, and is provided in the communication hole, and the gas in the case is led out of the case through the communication hole. Some have a breather device that suppresses pressure rise.

  As shown in FIGS. 9 and 10, the vehicle power transmission device as described above has a power transmission member (clutch drum) 100a having, for example, a bottomed cylindrical shape that transmits the power of the prime mover and is lubricated by lubricating oil. A case 110 that accommodates the forward / reverse switching device 100 and an upper portion of the outer peripheral wall portion 110a of the case 110 are formed between an inner wall surface 110b of the outer peripheral wall portion 110a of the case 110 and an outer peripheral surface of the power transmission member 100a. A communication hole 110c that allows the formed annular space 120 to communicate with the outside of the case 110, and the communication hole 110c, and the gas in the case 110 is led out of the case 110 through the communication hole 110c. And a breather device 130 that suppresses the pressure increase in the case 110.

  In the vehicle power transmission device as described above, the lubricating oil that lubricates the forward / reverse switching device 100 is agitated by rotating the forward / reverse switching device 100 at a rotational speed substantially equal to the rotational speed of the prime mover. In some cases, bubbles of lubricating oil may be generated in the case 110. Moreover, the dashed-dotted arrows A1 and A2 shown in FIG. 9 virtually indicate that bubbles generated by the agitation of the lubricating oil by the forward / reverse switching device 100 are filled in the case 110. .

  In the conventional vehicle power transmission device, as shown in FIGS. 9 and 10, bubbles generated when the lubricant is agitated by the forward / reverse switching device 100 enter the communication hole 110 c of the case 110 through the annular space 120. In order to prevent entry, the inner wall surface 110b of the case 110 in the annular space 120 has a plurality of protrusions that block a part of the annular space 120 at a predetermined distance from the inner opening of the communication hole 110b to increase the reach distance. A barrier 110d is formed.

JP 2007-263239 A JP 2009-144846 A JP-A-10-325457

  However, in the vehicle power transmission device as described above, as shown in FIG. 10, the protruding barrier 110 d is merely a part that blocks a part of the annular space 120 in a labyrinth shape to increase the reach distance. When bubbles continue to be generated from the directions of the arrows A1 and A2, the bubbles reach the communication hole 110c of the case 110. Therefore, when the air in the case 110 expands as the temperature rises and the air in the case 110 is released from the breather device 130, the bubbles, that is, the lubricating oil leaks out of the case 110 together with the air. There was a problem. The arrow of the dashed-two dotted line shown in FIG. 10 shows a mode that the said bubble enters into the communicating hole 110c of the case 110. As shown in FIG.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to transmit power for a vehicle that prevents bubbles generated by agitation of lubricating oil from entering the communication hole of the case. To provide an apparatus.

  To achieve this object, the gist of the present invention is that: (a) a case that houses a power transmission member that transmits power of a prime mover and is lubricated by lubricating oil; and an upper portion of an outer peripheral wall portion of the case. And a communication hole formed in the communication hole for communicating the outside of the case with the inner wall surface of the case and the annular space between the power transmission members, and the gas in the case is removed from the communication hole through the communication hole. A power transmission device for a vehicle having a breather device that suppresses an increase in pressure in the case by being led out to the outside of the case, and (b) from an inner opening of the communication hole in the upper portion of the annular space in the case A lubricating oil inflow port arranged at a predetermined distance in the circumferential direction is provided.

  According to the vehicle power transmission device of the present invention, (b) a lubricating oil inflow port disposed at a predetermined distance in the circumferential direction from the inner opening of the communication hole is provided in the upper portion of the annular space in the case. ing. For this reason, the outer peripheral surface of the power transmission member from a position where the lubricating oil flowing in from the lubricating oil inflow port is separated from the inner peripheral opening of the communication hole in the upper part of the annular space in the case by a predetermined distance in the circumferential direction. Therefore, when bubbles generated by stirring the lubricating oil try to enter the communication hole side of the annular space, the bubbles hit the lubricating oil introduced from the lubricating oil inlet and disappear. As a result, the amount of bubbles generated by the stirring of the lubricating oil is reduced, so that the bubbles are prevented from entering the communication hole of the case by the lubricating oil introduced from the lubricating oil inlet.

  Here, it is preferable that (a) the annular space protrude from the inside opening of the communication hole of the outer peripheral wall portion of the case and the lubricating oil inlet toward the outer peripheral side of the power transmission member. (B) The lubricating oil introduced from the lubricating oil inlet is caused to flow down along the receiving surface of the plate-like protrusion. For this reason, the lubricating oil flowing in from the lubricating oil inlet is caused to flow down along the receiving surface of the plate-like protrusion, and flows down in the form of a curtain from the lower end edge of the plate-like protrusion. The gap between the outer peripheral surface of the plate and the plate-like protrusion is covered with the lubricating oil that flows down in a curtain shape, and the bubbles that pass through the gap toward the communication hole are preferably eliminated.

  Preferably, (a) the plate-like protrusion is provided on the side away from the communication hole in the circumferential direction, protrudes from the outer peripheral side of the power transmission member to the upper portion of the inner peripheral wall of the case, and transmits the power. A receiving projection that receives the lubricating oil introduced from the lubricating oil inlet between the outer peripheral surface of the member and temporarily stores the lubricating oil; and (b) the receiving surface of the receiving projection and the power transmission Another object is to further include a lubricating oil outlet opening between the outer peripheral surface of the member. For this reason, the lubricating oil flowing in from the lubricating oil inlet is temporarily stored by the receiving projection, and the stored lubricating oil is sucked in from the lubricating oil outlet, so from the lubricating oil inlet The lubricating oil that has flowed in is preferably suppressed from accumulating at the bottom of the case that houses the power transmission member, and the amount of inflow of lubricating oil can be increased, and the lubricating oil accumulated at the bottom of the case Stirring resistance when the power transmission member rotates is preferably reduced.

  Preferably, the lubricating oil introduced from the lubricating oil inlet is a part of the lubricating oil for lubricating the power transmission member in the case, and therefore the lubricating oil for lubricating the power transmission member is diverted. Therefore, the amount of lubricating oil flowing in from the lubricating oil inlet can be suitably secured.

  Preferably, (a) a hydraulic circuit including a relief type pressure regulating valve that regulates the hydraulic oil pumped from the oil pump by escaping a part of the hydraulic oil is provided. The lubricating oil introduced from the oil inlet is relief oil discharged from the relief type pressure regulating valve. For this reason, when the prime mover where the lubricating oil is stirred at a relatively high rotational speed at which bubbles are likely to be generated, the amount of discharge from the oil pump that is rotationally driven by the prime mover increases and is discharged from the relief type pressure regulating valve. The amount of relief oil supplied increases, so that bubbles generated by stirring the lubricating oil can enter the communication hole of the case by a sufficient amount of lubricating oil introduced from the lubricating oil inlet. Is prevented. As a result, the relief oil discharged from the relief type pressure regulating valve can be directly introduced from the lubricating oil inlet, so that the amount of lubricating oil introduced from the lubricating oil inlet can be suitably secured.

1 is a skeleton diagram illustrating a configuration of a vehicle power transmission device to which the present invention is applied. It is the II-II perspective view of FIG. 1 explaining the structure of a transaxle case. FIG. 3 is an enlarged view of FIG. 2 for explaining a pair of lubricating oil inlets and a pair of plate-like protrusions formed in the transaxle case. FIG. 4 is a hydraulic circuit diagram illustrating a hydraulic circuit to which hydraulic oil flowing from the lubricating oil inlet illustrated in FIG. 3 is supplied. FIG. 5 is a cross-sectional view taken along line VV of FIG. 3 for explaining a state in which hydraulic oil flowing in from one of a pair of lubricating oil inlets flows down along the receiving surface of the plate-like protrusion. FIG. 5 is a cross-sectional view of FIG. 3 cut along the alternate long and short dash line shown in FIG. FIG. 4 is a cross-sectional view taken along the line VI-VI in FIG. 3 for explaining a state in which hydraulic oil flowing in from the other of the pair of lubricating oil inlets flows down along the receiving surface of the plate-like protrusion. It is a figure explaining the structure of the transaxle case of another Example, and is a figure corresponding to FIG. 2 of the above-mentioned Example. It is a figure explaining a pair of receiving protrusion part and a pair of lubricating oil outlet which were formed in the transaxle case of another Example, and is a figure corresponding to FIG. 3 of the above-mentioned Example. It is a figure explaining the transaxle case of the conventional vehicle power transmission device. It is a figure explaining the problem of the some protruding barrier formed in the conventional transaxle case.

  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 for easy understanding, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a skeleton diagram illustrating the configuration of a vehicle power transmission device 10 to which the present invention is applied. The vehicle power transmission device 10 is a horizontal automatic transmission that is suitably employed in an FF (front engine / front drive) type vehicle. An engine (prime mover) 12 is used as a driving power source. I have. The output of the engine 12 composed of an internal combustion engine is the crankshaft of the engine 12, the torque converter 14 as a fluid transmission device, the forward / reverse switching device 16, the belt type continuously variable transmission (CVT) 18, the reduction gear. It is transmitted to the differential gear device 22 via the device 20 and distributed to the left and right drive wheels 24L and 24R.

  The torque converter 14 includes a pump impeller 14p connected to the crankshaft of the engine 12 and a turbine impeller 14t connected to the forward / reverse switching device 16 via a turbine shaft 26 corresponding to an output side member of the torque converter 14. And power transmission is performed via a fluid. A lock-up clutch 28 is provided between the pump impeller 14p and the turbine impeller 14t. Further, the pump impeller 14p includes a mechanical oil pump 30 that generates a source pressure for performing the shift control of the continuously variable transmission 18, the belt clamping pressure control, the engagement release control of the lockup clutch 28, and the like. They are connected and operated in conjunction with the rotation of the engine 12.

  The forward / reverse switching device 16 is composed mainly of a forward clutch C1 and a reverse brake B1 and a double pinion type planetary gear device 16p, and the turbine shaft 26 of the torque converter 14 is integrally connected to the sun gear 16s. The input shaft 32 of the continuously variable transmission 18 is integrally connected to the carrier 16c, while the carrier 16c and the sun gear 16s are selectively connected via the forward clutch C1, and the ring gear 16r is connected to the reverse brake B1. The housing is selectively fixed to a housing which is a non-rotating member. Both the forward clutch C1 and the reverse brake B1 are hydraulic friction engagement devices that are frictionally engaged by a hydraulic actuator.

  When the forward clutch C1 is engaged and the reverse brake B1 is released, the forward driving force is transmitted to the continuously variable transmission 18 side. Further, when the reverse brake B1 is engaged and the forward clutch C1 is released, the drive force in the reverse direction is transmitted to the continuously variable transmission 18 side. When the forward clutch C1 and the reverse brake B1 are both released, the forward / reverse switching device 16 enters a neutral state in which power transmission is interrupted.

  The continuously variable transmission 18 includes a drive-side variable pulley 34 having a variable effective diameter, which is an input-side member provided on the input shaft 32, and a driven-side having a variable effective diameter, which is an output-side member, provided on the output shaft 36. A variable pulley 38 and a transmission belt 40 wound around the variable pulleys 34 and 38 are provided, and power is transmitted through a frictional force between the variable pulleys 34 and 38 and the transmission belt 40. .

  The variable pulleys 34 and 38 are fixed rotation bodies 34 a and 38 a fixed to the input shaft 32 and the output shaft 36, respectively, and are not rotatable relative to the input shaft 32 and the output shaft 36 and are movable in the axial direction. The movable rotating bodies 34b and 38b provided, and a drive-side hydraulic actuator 34c and a driven-side hydraulic actuator 38c as hydraulic actuators that apply thrust to change the V-groove width between them are configured and driven. The hydraulic oil pressure to the side hydraulic actuator 34c is controlled by the hydraulic circuit 82 (see FIG. 4), so that the V groove widths of the variable pulleys 34 and 38 change, and the engagement diameter (effective diameter) of the transmission belt 40 changes. Is changed, and the gear ratio γ (= input shaft rotational speed / output shaft rotational speed) is continuously changed.

  As shown in FIG. 1, the vehicle power transmission device 10 can transmit the output of the engine 12 to the differential gear device 22 via the forward / reverse switching device 16, the continuously variable transmission 18, and the reduction gear device 20. A transaxle case member 42 that houses the forward / reverse switching device 16, the continuously variable transmission 18, the reduction gear device 20, and the differential gear device 22 is provided. The transaxle case member 42 includes a transaxle rear cover 44 and a transaxle case (case) 46 that rotatably accommodate the drive side variable pulley 34 and the driven side variable pulley 38 of the continuously variable transmission 18, and the transformer. The axle case 46 includes a forward / reverse switching device 16, a reduction gear device 20, and a transaxle housing 48 that rotatably accommodates the differential gear device 22. As shown in FIG. 1, the transaxle case member 42 is configured such that a transaxle rear cover 44, a transaxle case 46, and a transaxle housing 48 are integrally fixed by a fixing member 50 such as a bolt. .

  In the transaxle case 46, as shown in FIG. 1, in the transaxle case 46, an accommodation space 52 in which the continuously variable transmission 18 is accommodated, the forward / reverse switching device 16, the reduction gear device 20, and a differential gear. A wall portion 46 a is formed to separate the housing space 54 in which the device 22 is housed, and the oil pump 30 formed in the transaxle housing 48 and the housing space 54 formed in the transaxle case 46 and the transaxle housing 48. Also, a blocking wall 58 that blocks between the housing space 56 that houses the torque converter 14 and the like is fixed by a fixing member 60 such as a bolt. In addition, as shown in FIG. 1, the transaxle case 46 has its transaxle case 46 guided to the outside of the transaxle case 46 by introducing the expansion air in the accommodation space 54 of the transaxle case 46 as the temperature changes. A breather device 62 that suppresses an increase in the internal pressure is attached.

  As shown in FIG. 2, a cylindrical housing hole 46 b for housing the forward / reverse switching device 16 and an output shaft 36 of the continuously variable transmission 18 are rotated through a bearing 64 in the wall portion 46 a of the transaxle case 46. A support hole 46c that supports the shaft member 20b, a support hole 46d that rotatably supports the shaft member 20b of the driven gear 20a of the reduction gear device 20 via a bearing 66, and an output shaft 22a of the differential gear device 22 via a bearing 68. And a support hole 46e that is rotatably supported. Also, the circular dash-dot line shown in FIG. 2 virtually shows the driven gear 20a and drive gear 20c of the reduction gear device 20 and the ring gear 22b of the differential gear device 22.

  As shown in FIG. 2, a substantially bottomed cylindrical clutch drum (power transmission member) 16 a is fixed to the turbine shaft 26 of the torque converter 14 so as not to rotate relative to the forward / reverse switching device 16. Is transmitted to the turbine shaft 26, when the forward clutch C1 or the reverse brake B1 is engaged, the power of the engine 12 is transmitted to the input shaft 32 of the continuously variable transmission 18 via the clutch drum 16a. Is transmitted. As shown in FIG. 2, when the clutch drum 16a is accommodated in the transaxle case 46, a part of the outer peripheral surface 16b of the clutch drum 16a protrudes from the accommodation hole 46b of the wall portion 46a to the engine 12 side. It becomes a state.

  As shown in FIG. 2, the transaxle case 46 includes an outer peripheral edge of a wall portion 46 a of the transaxle case 46 so as to surround the clutch drum 16 a, the reduction gear device 20, and the differential gear device 22 of the forward / reverse switching device 16. An outer peripheral wall portion 46f protruding from the engine 12 to the engine 12 side, an annular annular space 70 formed between the inner wall surface 46g of the outer peripheral wall portion 46f and the outer peripheral surface 16b of the clutch drum 16a, and the annular space 70 In order to communicate with the outside of the transaxle case 46, a columnar communication hole 46h drilled in the upper part of the outer peripheral wall portion 46f of the transaxle case 46 is provided.

  As shown in FIGS. 2 and 3, the breather device 62 is formed in a cylindrical shape so that the male screw portion 72 a that is oil-tightly engaged with the female screw on the inner peripheral surface of the communication hole 46 h communicates with the inside and outside of the transaxle case 46. A longitudinal cylindrical breather body 72 having a through hole 72b penetrating through the center and attached to the internal thread of the inner peripheral surface of the communication hole 46h, and the outer side of the transaxle case 46 of the through hole 72b of the breather body 72 A disc-shaped valve element 74 seated on the periphery of the opening 72c so as to close the opening 72c of the cylinder, and a cap 76 attached to the valve element 74 and the outer end of the transaxle case 46 of the breather body 72. And a coiled spring 78 interposed in a preloaded state between the bottom surface 76a and the seating of the valve element 74 to prevent outside water from entering the accommodating space 54. It has become to so that.

  Therefore, when the air in the transaxle case 46 expands as the temperature in the transaxle case 46 increases, the valve element 74 of the breather device 62 resists the biasing force of the spring 78 by the expanded air. Since it is separated from the periphery of the opening 72c of the through hole 72b of 72, the expanded air in the transaxle case 46 is discharged to the outside of the transaxle case 46, and the pressure increase in the transaxle case 46 is suppressed.

  As shown in FIG. 3, a pair of the annular space 70 is disposed at a predetermined distance in the circumferential direction of the annular space 70 from the opening inside the transaxle case 46 of the communicating hole 46h at the upper part, that is, the portion on the communicating hole 46h side. The lubricating oil inlets 46 i and 46 j are formed in the wall portion 46 a of the transaxle case 46 so as to open in a direction parallel to the axis C. Further, as shown in FIG. 3, the transaxle case 46 protrudes toward the clutch drum 16a from between the opening of the communication hole 46h of the outer peripheral wall portion 46f and the lubricating oil inlets 46i and 46j, respectively. A pair of plate-like protrusions 46k and 46l that block the outer periphery of 70 are formed on the outer peripheral wall 46f of the transaxle case 46. Of the pair of plate-like protrusions 46k and 46l, the plate-like protrusion 46l located on the downstream side in the rotation direction F of the clutch drum 16a is formed to be slightly inclined with respect to the vertical line and protrude toward the rotation direction F. The plate-like protrusion 46k located on the upstream side in the rotation direction F is inclined so as to go to the upstream side in the rotation direction F toward the lower side, that is, the rotation center C.

FIG. 4 shows a relief-type pressure regulating valve 80 that regulates hydraulic oil (lubricating oil) pumped from an oil pump 30 driven by the engine 12 by releasing a part of the hydraulic oil and outputs a line pressure PL. It is a hydraulic circuit diagram which shows the hydraulic circuit 82 containing. The relief type pressure regulating valve 80 includes an oil chamber that receives a control pressure _PSLS output from a linear solenoid valve (not shown), and a command that an electronic control unit (not shown) commands based on the throttle opening. By controlling the control pressure P _SLS of the linear solenoid valve by the signal, the line pressure PL is controlled to the optimum hydraulic pressure.

  As shown in FIG. 4, the relief oil discharged from the relief type pressure regulating valve 80, i.e., hydraulic oil, passes through the oil passage 84 and a pair of lubricating oil inlets 46 i formed in the wall portion 46 a of the transaxle case 46. 46j can also flow into the transaxle case 46. 2 and FIG. 3 virtually indicate the flow of hydraulic oil flowing into the transaxle case 46 from the lubricating oil inlets 46i and 46j.

  As shown in FIGS. 5 and 6, the plate-like protrusions 46k and 46l are each formed in a long flat plate shape in the direction of the axis C of the clutch drum 16a, and the lower ends of the plate-like protrusions 46k and 46l. The edges 46m and 46n are formed in parallel with the outer peripheral surface 16b of the clutch drum 16a. Further, as shown in FIG. 3, the receiving surface 46o of the plate-like protrusion 46k is inclined with respect to the vertical direction in order to receive the hydraulic oil flowing in the direction parallel to the axis C from the lubricating oil inlet 46i. ing. Further, as shown in FIG. 3, the receiving surface 46p of the plate-like protrusion 46l becomes downstream in the rotation direction F toward the rotation center C so as to receive a part of the hydraulic oil flowing in from the lubricating oil inlet 46j. It inclines with a small inclination as compared with the inclination of the plate-like protrusion 46k.

  When hydraulic oil flows in from the lubricating oil inlets 46i and 46j, the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j is caused to flow down along the receiving surfaces 46o and 46p of the plate-like protrusions 46k and 46l. . As a result, as shown in FIGS. 5 and 6, as the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j flows downstream of the receiving surfaces 46o and 46p, the hydraulic oil flows into the lubricating oil inlets 46i and 46i. The clutch drum 16a in the form of a curtain from the lower edges 46m and 46n of the plate-like projections 46k and 46l flows to the side away from the lubricating oil inlets 46i and 46j of the receiving surfaces 46o and 46p by the momentum flowing in from 46j. Therefore, the gaps 86 and 88 between the outer peripheral surface 16b of the clutch drum 16a and the plate-like protrusions 46k and 46l are covered with the hydraulic oil that flows down in the form of a curtain. Also, the broken-line arrows shown in FIGS. 5 and 6 virtually indicate the flow of the hydraulic oil flowing into the transaxle case 46 from the lubricating oil inlets 46i and 46j.

  Here, as shown in FIGS. 2 and 3, the forward / reverse switching device 16 having the clutch drum 16a housed in the transaxle case 46 is supplied via an oil passage 26a formed in the turbine shaft 26, for example. The hydraulic oil that is lubricated by the hydraulic oil and lubricates the forward / reverse switching device 16 is agitated when the forward / backward switching device 16 is rotated by the engine 12 to generate bubbles in the transaxle case 46. There is a case.

  Next, the state in the annular space 70 when bubbles generated in the transaxle case 46 continue to be generated will be described with reference to FIGS. 2 and 3. Dotted arrows B1 and B2 shown in FIGS. 2 and 3 virtually indicate the direction in which bubbles generated when the hydraulic oil is stirred by the forward / reverse switching device 16 fills the transaxle case 46. Is.

  As shown in FIGS. 2 and 3, when the engine 12 in which hydraulic oil is stirred at a relatively high rotational speed at which bubbles are likely to be generated in the transaxle case 46 is high, the oil pump is rotationally driven by the engine 12. 30, the amount of relief oil discharged from the relief type pressure regulating valve 80 increases, and the amount of relief oil discharged from the relief type pressure regulating valve 80 increases, so that a relatively large amount of oil flows from the lubricating oil inlets 46 i and 46 j through the oil passage 84 of the hydraulic circuit 82. Hydraulic oil is caused to flow into the transaxle case 46. The hydraulic oil flows down along the receiving surfaces 46o and 46p of the plate-like protrusions 46k and 46l, and the hydraulic oil flows from the lower edges 46m and 46n of the plate-like protrusions 46k and 46l to the outer peripheral surface 16b of the clutch drum 16a. Flows down in the form of a curtain, so that the gaps 86 and 88 between the outer peripheral surface 16b of the clutch drum 16a and the plate-like protrusions 46k and 46l are covered with the hydraulic oil that flows down in the form of a curtain.

  As a result, when the bubbles generated by stirring the hydraulic oil move in the annular space 70 in the directions of the arrows B1 and B2 and attempt to pass through the plate-like protrusions 46k and 46l, the bubbles are injected into the lubricating oil inlet 46i. The bubbles disappear when they hit the curtain-like hydraulic oil flowing in from 46j and 46j, so that the bubbles are prevented from reaching the communication hole 46h of the transaxle case 46. Further, as shown in FIG. 3, the clutch drum 16a is rotated in the direction of arrow F by the power of the engine 12, and bubbles generated by stirring the hydraulic oil are indicated by an arrow B1 in the same direction as the arrow F direction. The receiving surface 46o of the plate-like projection 46k receives and flows down all of the hydraulic oil flowing in from the lubricating oil inlet 46i, and therefore the plate-like projection 46k. The film thickness of the curtain-like hydraulic oil that flows down from the lower end edge 46m is suitably increased, and the bubbles that enter from the direction of the arrow B1 are preferably eliminated.

  As described above, according to the vehicle power transmission device 10 of the present embodiment, on the communication hole 46 h side of the annular space 70 in the transaxle case 46, the annular space 70 extends from the opening inside the transaxle case 46 of the communication hole 46 h. Lubricating oil inlets 46i and 46j arranged at a predetermined distance in the circumferential direction are provided. For this reason, since the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j flows down to the outer peripheral surface 16b of the clutch drum 16a, bubbles generated by the stirring of the hydraulic oil enter the communication hole 46h side of the annular space 70. When trying to enter, the bubbles disappear by the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j. As a result, the amount of bubbles generated by agitation of the hydraulic oil is reduced, so that the bubbles are prevented from entering the communication hole 46h of the transaxle case 46.

  Further, according to the vehicle power transmission device 10 of the present embodiment, the clutch is provided between the opening inside the transaxle case 46 of the communication hole 46h in the outer peripheral wall 46f of the transaxle case 46 and the lubricating oil inlets 46i and 46j. Plate-like protrusions 46k and 46l projecting toward the outer peripheral side of the drum 16a and blocking a part of the annular space 70 are provided, and the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j is supplied to the plate-like protrusion 46k. And 46l along the receiving surfaces 46o and 46p. For this reason, the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j flows down in a curtain form from the lower edges 46m and 46n of the plate-like protrusions 46k and 46l, so the outer peripheral surface 16b of the clutch drum 16a and the plate-like protrusion 46k. The gaps 86 and 88 between the first and second holes 46l and 46l are covered with the hydraulic oil flowing down in the form of a curtain, and the bubbles that pass through the gaps 86 and 88 toward the communication hole 46h are preferably eliminated.

  Further, according to the vehicle power transmission device 10 of the present embodiment, the hydraulic circuit 82 including the relief type pressure regulating valve 80 that regulates the hydraulic oil fed from the oil pump 30 by releasing a part of the hydraulic oil. The hydraulic oil that is provided and flows from the lubricating oil inlets 46 i and 46 j is relief oil that is discharged from the relief type pressure regulating valve 80. For this reason, at the time of high rotation of the engine 12 in which the hydraulic oil is stirred at a relatively high rotational speed at which bubbles are likely to be generated, the discharge amount from the oil pump 30 that is rotationally driven by the engine 12 increases, and the relief type pressure regulating valve 80 Since the supply amount of the relief oil discharged from the oil increases, bubbles generated by stirring the hydraulic oil are communicated with the transaxle case 46 by a sufficient amount of the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j. It is prevented from entering the hole 46h. As a result, the relief oil discharged from the relief type pressure regulating valve 80 can be directly introduced from the lubricating oil inlets 46i and 46j, so that the amount of hydraulic oil flowing from the lubricating oil inlets 46i and 46j can be suitably secured. .

  Another embodiment of the present invention will be described. In the following other embodiments, portions common to the embodiments are denoted by the same reference numerals and description thereof is omitted.

  The transaxle case 46 of the vehicle power transmission device of the present embodiment is the same as that of the first embodiment except that the transaxle case 46 is provided with a pair of receiving projections 46q and 46r and a pair of lubricating oil outlets 46s and 46t. The transaxle case 46 is substantially the same. 7 and 8 show a pair of receiving projections 46q and 46r formed on the wall 46a of the transaxle case 46 and a pair of lubricating oil outlets 46s formed on the wall 46a of the transaxle case 46. It is a figure explaining 46t.

  As shown in FIGS. 7 and 8, the pair of receiving projections 46q and 46r are arranged so that the wall portion of the transaxle case 46 is located away from the communication hole 46h from the plate-like projections 46k and 46l in the circumferential direction of the annular space 70. 46a is formed in the transaxle case 46 so as to protrude from the outer peripheral surface 16b side of the clutch drum 16a to the outer peripheral wall portion 46f to block a part of the annular space 70, and is long in the direction of the axis C of the clutch drum 16a. It is formed in a flat plate shape. Further, as shown in FIG. 7, the receiving surfaces 46u and 46v of the pair of receiving projections 46q and 46r receive hydraulic oil flowing from the lubricating oil inlets 46i and 46j between the outer peripheral surface 16b of the clutch drum 16a. In order to suitably receive and temporarily store the hydraulic oil, with respect to the straight lines D1 and D2 connecting the shaft center C of the clutch drum 16a and the end portions of the receiving protrusions 46q and 46r on the outer peripheral side of the clutch drum 16a. The ends of the receiving projections 46q and 46r opposite to the outer peripheral side of the clutch drum 16a are inclined so as to approach the communication hole 46h. Also, the circular dash-dot line shown in FIG. 7 virtually shows the driven gear 20a and the drive gear 20c of the reduction gear device 20 and the ring gear 22b of the differential gear device 22. Also, the broken-line arrows shown in FIGS. 7 and 8 virtually indicate the flow of the hydraulic oil that has flowed into the transaxle case 46 from the lubricating oil inlets 46i and 46j.

  Further, as shown in FIGS. 7 and 8, for example, a pair of lubricating oil outlets 46s and 46t directly or indirectly connected to the suction side port of the oil pump 30 are provided with receiving protrusions 46q in the transaxle case 46. And 46r and the receiving surfaces 46u and 46v of the clutch drum 16a and the outer peripheral surface 16b of the clutch drum 16a. Further, when the hydraulic oil is stored in the pair of lubricating oil outlets 46s and 46t by the receiving protrusions 46q and 46r, the hydraulic oil is stored from the lubricating oil outlets 46s and 46t through an oil passage (not shown). The stored hydraulic oil flows out into an oil pan (not shown).

  7 and 8 indicate the direction in which bubbles generated when the hydraulic oil is agitated by the forward / reverse switching device 16 fills the transaxle case 46 in a virtual manner. In the transaxle case 46 of the present embodiment, as in the first embodiment, the bubbles generated by the stirring of the hydraulic oil move in the directions of arrows E1 and E2 so that the annular space 70 communicates. When trying to enter the hole 46h side, the bubbles come into contact with the curtain-like hydraulic oil flowing in from the lubricating oil inlets 46i and 46j, and the bubbles disappear. Therefore, the bubbles generated when the hydraulic oil is stirred are transaxle case 46. It is prevented from entering the communication hole 46h.

  According to the vehicle power transmission device 10 of the present embodiment, the outer circumferential wall portion is provided from the outer circumferential side of the clutch drum 16a at the position away from the communication hole 46h from the plate-like projections 46k and 46l in the circumferential direction of the annular space 70. A receiving protrusion 46q that protrudes toward the communication hole 46h side of 46f and receives hydraulic oil from the lubricating oil inlets 46i and 46j between the outer peripheral surface 16b of the clutch drum 16a and temporarily stores the hydraulic oil; 46r and lubricating oil outlets 46s and 46r opened between the receiving surfaces 46u and 46v of the receiving protrusions 46q and 46r and the outer peripheral surface 16b of the clutch drum 16a. For this reason, the hydraulic oil flowing in from the lubricating oil inlets 46g and 46t is temporarily stored by the receiving projections 46q and 46r, and the stored hydraulic oil is sucked from the lubricating oil outlets 46s and 46t. The hydraulic oil flowing in from the lubricating oil inlets 46i and 46j is preferably suppressed from accumulating at the bottom of the transaxle case 46 housing the clutch drum 16a, that is, the forward / reverse switching device 16, and the amount of hydraulic oil flowing in is increased. In addition, the stirring resistance when the clutch drum 16a is rotated by the hydraulic oil accumulated at the bottom of the transaxle case 46 is preferably reduced.

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

  For example, in the vehicle power transmission device 10 of the present embodiment, the power from the engine 12 is transmitted, but the power transmitted to the vehicle power transmission device 10 of the present embodiment is limited to the power from the engine 12. For example, power such as an electric motor may be transmitted.

  Further, in the vehicle power transmission device 10 of the present embodiment, the annular space 70 is formed between the inner wall surface 46g of the transaxle case 46 and the clutch drum 16a of the forward / reverse switching device 16, The annular space 70 of the vehicle power transmission device 10 of this embodiment is formed anywhere between the power transmission member that transmits the power of the engine 12 in the transaxle case member 42 of the vehicle power transmission device 10. In this case, the breather device 62 is appropriately attached.

  Further, in the vehicle power transmission device 10 of the present embodiment, the hydraulic oil flowing in from the lubricating oil inlets 46i and 46j is caused to flow down to the receiving surfaces 46o and 46p of the plate-like protrusions 46k and 46l. Although it flowed down from the lower end edges 46m and 46n of the portions 46k and 46l in a curtain shape, the plate-like protrusions 46k and 46l need not necessarily be formed in the transaxle case 46 of the vehicle power transmission device 10 of this embodiment. In addition, the flow of the hydraulic oil from the lubricating oil inlets 46i and 46j, preferably in a sprayed state, causes the bubbles to strike the hydraulic oil and disappear, and the amount of bubbles generated when the hydraulic oil is agitated is reduced. However, the accuracy is lower than that in the case where the projections 46k and 46l are provided, but they are introduced from the lubricating oil inlets 46i and 46j. Thereby preventing the air bubbles from entering the communication hole 46h of the transaxle case 46 by hydraulic oil.

  Further, in the vehicle power transmission device 10 of the present embodiment, the hydraulic oil that is introduced from the lubricating oil inlets 46i and 46j is the relief oil that is discharged from the relief type pressure regulating valve 80, but in this embodiment, It is not always necessary to use the relief oil discharged directly from the relief type pressure regulating valve 80. For example, a part of the working oil for lubricating the forward / reverse switching device 16 in the transaxle case 46 is used as the lubricating oil inlets 46i and 46j. The hydraulic fluid can be introduced from the lubricating oil inlets 46i and 46j in various ways based on the knowledge of those skilled in the art.

  Although not illustrated one by one, the present invention can be implemented in variously modified and improved modes based on the knowledge of those skilled in the art.

10: Vehicle power transmission device 12: Engine (motor)
16a: Clutch drum (power transmission member)
30: Oil pump 46: Transaxle case (case)
46f: outer peripheral wall 46g: inner wall 46h: communication hole 46i, 46j: lubricating oil inlet 46k, 46l: plate-like protrusion 46o, 46p: receiving surface 46q, 46r: receiving protrusion 46s, 46t: lubricating oil outlet 46u, 46v: receiving surface 62: breather device 70: annular space 80: relief type pressure regulating valve 82: hydraulic circuit

Claims (5)

A case that houses a power transmission member that transmits the power of the prime mover and is lubricated by lubricating oil; and an upper portion of the outer peripheral wall portion of the case; and the outside of the case, the inner wall surface of the case, and the power transmission member A communication hole that communicates with the annular space therebetween, and a breather device that is provided in the communication hole and that suppresses a pressure increase in the case by deriving the gas in the case from the communication hole to the outside of the case A vehicle power transmission device comprising:
A vehicular power transmission device provided with a lubricating oil inflow port disposed at a predetermined distance in a circumferential direction from an inner opening of the communication hole at an upper portion of the annular space in the case. A plate-like protrusion that protrudes from the inside opening of the communication hole of the outer peripheral wall portion of the case and the lubricating oil inlet toward the outer peripheral side of the power transmission member and blocks a part of the annular space is provided. ,
2. The vehicle power transmission device according to claim 1, wherein the lubricating oil introduced from the lubricating oil inflow port is caused to flow down along the receiving surface of the plate-like protrusion. It is provided on the side away from the communication hole of the plate-like protrusion in the circumferential direction, protrudes from the outer peripheral side of the power transmission member to the upper part of the inner peripheral wall of the case, and between the outer peripheral surface of the power transmission member A receiving protrusion that receives the lubricating oil flowing in from the lubricating oil inlet and temporarily stores the lubricating oil;
The vehicular power transmission device according to claim 2, further comprising a lubricating oil outlet opening between a receiving surface of the receiving projection and an outer peripheral surface of the power transmission member.   The vehicular power transmission device according to any one of claims 1 to 3, wherein the lubricating oil introduced from the lubricating oil inlet is part of the lubricating oil for lubricating the power transmission member in the case. A hydraulic circuit including a relief type pressure regulating valve that regulates the hydraulic oil pumped from the oil pump by releasing a part of the hydraulic oil;
The vehicular power transmission device according to any one of claims 1 to 3, wherein the lubricating oil introduced from the lubricating oil inflow port is a relief oil discharged from the relief type pressure regulating valve.

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