JP7109356B2 - oil pump drive - Google Patents

Description

The present invention relates to an oil pump drive device for driving an oil pump mounted on a vehicle or the like.

Conventionally, there has been disclosed a driving device for constantly driving an oil pump using an input-switching clutch mechanism that outputs rotation input from two drive-side members as rotation of one output member (for example, See Patent Document 1).

In the oil pump driving device described in Patent Document 1, two one-way clutches are coaxially arranged side by side in the axial direction, and the inner rings of the two one-way clutches are integrated to form a common inner ring. The outer wheels of the two one-way clutches are driven by a drive member on the engine side or the electric motor side, which is an internal combustion engine. It selectively communicates with the common inner ring.

JP 2012-67862 A

2. Description of the Related Art In recent years, electric motors used as drive devices for vehicles have been designed to have higher rotation speeds and higher outputs. If such a high-speed motor is used as the input-side power source of a conventional oil-pump drive device, a high-speed rotation load is applied to the oil pump, which may cause durability problems such as seizure. It is possible to lower the input rotation from the high-speed motor by providing a separate speed reduction mechanism between the high-speed motor and the oil pump drive device, but in the limited space of the vehicle, a large number of peripheral devices are also arranged. Therefore, it is difficult to secure a space for separately installing such a speed reduction mechanism.

The present invention has been made in view of such circumstances, and an oil pump capable of decelerating the rotation input from the input side power source and transmitting it to the oil pump drive shaft without increasing the installation space. An object of the present invention is to provide a driving device.

In order to solve the above problems, an oil pump drive device according to the present invention includes:
Equipped with two one-way clutches arranged coaxially with the pump drive shaft of the oil pump,
Rotation is transmitted from drive members different from each other to the respective outer rings of the two one-way clutches,
the two one-way clutches selectively transmit rotation of the respective outer rings to the pump drive shaft via torque transmission members;
An oil pump drive device comprising a reduction mechanism on one of the outer diameter sides of the two one-way clutches for reducing rotation transmitted from the corresponding drive member and transmitting the rotation to the outer ring of the one one-way clutch,
A transmission clutch is provided coaxially with the speed reduction mechanism,
The speed change clutch is characterized in that the corresponding driving member and the speed reduction mechanism can be joined together and can be separated from each other.

ADVANTAGE OF THE INVENTION According to this invention, the oil pump drive device which can reduce the rotation input from an input-side power source, and can transmit it to an oil pump drive shaft can be provided, without causing the increase in installation space.

FIG. 1 is a model diagram of a speed reduction structure of an oil pump driving device according to a first embodiment of the present invention. FIG. 2 is a model diagram of the speed reduction structure of the oil pump driving device according to the second embodiment of the present invention. FIG. 3 is a cross-sectional view along the axial direction of the oil pump driving device according to the first embodiment. 4 is a sectional view taken along the line II--II in FIG. 3. FIG.

An embodiment of an oil pump drive device according to the present invention will be described below with reference to the drawings.

The present embodiment relates to a hybrid vehicle having a drive system that uses both an internal combustion engine and an electric motor (hereinafter simply referred to as "engine" and "motor", respectively). An oil pump driving device for driving a circulating oil pump.

First, the direction of the oil pump driving device in this embodiment will be defined. In this embodiment, the axial direction, radial direction, and circumferential direction refer to the axial direction, radial direction, and circumferential direction with respect to the first and second one-way clutches provided in the oil pump drive device. That is, it means the axial direction, radial direction, and circumferential direction with respect to the rotation axis of the inner or outer ring of the first and second one-way clutches. Regarding the axial direction, in FIGS. 1, 2 and 3, the right side of the paper surface is defined as one axial direction side, and the left side of the paper surface is defined as the other axial direction side. the other side in the axial direction. Regarding the circumferential direction, in FIG. 4, the direction of rotation to the right of the paper surface is the direction toward one side of the circumferential direction or clockwise, and the direction of rotation to the left of the paper surface is the direction toward the other side of the circumferential direction or counterclockwise. direction.

FIG. 1 is a model diagram of a speed reduction structure of an oil pump driving device according to a first embodiment of the present invention.
FIG. 2 is a model diagram of a speed reduction structure of an oil pump driving device according to a second embodiment of the present invention, showing a speed reduction structure also having a speed change mechanism.
FIG. 3 is a cross-sectional view along the axial direction of the oil pump driving device according to the first embodiment, and also shows an outline of the cross section of the oil pump driven by the oil pump driving device.
FIG. 4 is a cross-sectional view taken along the line II--II in FIG. 3, showing a cross section of the first one-way clutch.

The oil pump driving device according to the first embodiment of the present invention and the oil pump driving device according to the second embodiment are substantially the same, and the rotation transmitted from the motor is decelerated and transmitted to the one-way clutch. have different deceleration structures.
As shown in FIG. 1, the oil pump driving device 1 according to the first embodiment includes a first one-way clutch 21 and a second one-way clutch 23. As shown in FIG. The first one-way clutch 21 is for transmitting the driving force of the motor M, which is the power source, to the oil pump P, and the second one-way clutch 23 is for transmitting the driving force of the engine E, which is the power source, to the oil pump P. It is for

The reduction structure according to the first embodiment includes a planetary gear A between the motor M and the first one-way clutch 21, as shown in FIG. The rotation of the motor M transmitted by the rotation transmission mechanism (not shown) on the motor M side is decelerated through the planetary gear A and transmitted to the first one-way clutch 21 . The reduced rotation of the motor M is transmitted to the pump drive shaft 7 of the oil pump P via the first one-way clutch 21 . That is, the oil pump P is driven by the rotational driving force of the motor M which has been reduced in speed.

The oil pump driving device 1 according to the second embodiment includes a first one-way clutch 21 and a second one-way clutch 23 having the same configuration as that of the first embodiment. The speed reduction structure according to the second embodiment further includes a speed change clutch B in addition to the planetary gear A between the motor M and the first one-way clutch 21, as shown in FIG. The transmission clutch B and the planetary gear A are provided coaxially. Other configurations are the same as those of the first embodiment.

The speed change clutch B is in an engagement state (hereinafter referred to as a first engagement state) in which a rotation transmission mechanism (not shown) on the motor M side and the planetary gear A are connected, and in a state in which the rotation of the motor M side is connected without the planetary gear A. It has a configuration capable of switching between a second engagement state in which the transmission mechanism and the first one-way clutch 21 are connected. That is, when the speed change clutch B is in the first engaged state, the rotation transmission mechanism on the motor M side is connected to the planetary gear A, and the rotation of the motor M transmitted by the rotation transmission mechanism on the motor M side is reduced by the planetary gear A. , the reduced rotation is transmitted to the pump drive shaft 7 of the oil pump P via the first one-way clutch 21 . Therefore, the oil pump P is driven by the rotational driving force of the motor M which has been reduced in speed.

On the other hand, when the speed change clutch B is in the second engaged state, the rotation transmission mechanism on the motor M side and the first one-way clutch 21 are connected without the planetary gear A interposed therebetween. That is, when the speed change clutch B is in the second engagement state, the rotation of the motor M transmitted by the rotation transmission mechanism on the side of the motor M is not decelerated and is transmitted to the first one-way clutch 21 at a constant speed. is transmitted to the pump drive shaft 7 of the oil pump P via the first one-way clutch 21 . Thus, in the speed reduction structure of the oil pump driving device 1 according to the second embodiment, the speed change clutch B reduces the rotation of the motor M via the planetary gear A in accordance with the rotation speed of the motor M and transmits it to the oil pump P. , and a switching mechanism for transmitting to the oil pump P at a constant speed without deceleration when there is no need to decelerate. That is, the speed reduction structure of the oil pump driving device 1 according to the second embodiment switches the rotation of the motor M transmitted by the rotation transmission mechanism on the side of the motor M between speed reduction and constant speed via the speed change clutch B, thereby It can be transmitted to the pump P.

A specific configuration of the oil pump driving device 1 according to the first embodiment will be described below.
As shown in FIG. 3, the oil pump driving device 1 according to the first example of the present embodiment is provided adjacent to the other side of the oil pump 2 in the axial direction. Specifically, the oil pump 2 includes a pump case 5 composed of a pump body 3 and a pump cover 4 , a pump rotor 6 , and a pump drive shaft 7 . It is provided on the pump drive shaft 7 adjacent to the other side of the oil pump 2 in the axial direction.

A pump body 3 of the oil pump 2 is fixed to a vehicle body structure (not shown). The pump body 3 is provided with a pump chamber forming recessed portion 8 that is recessed toward one side in the axial direction and opens toward the other side in the axial direction. The cross-sectional shape of the pump chamber forming recess 8 as viewed from the axial direction is circular. A recessed portion 9 recessed toward one side in the axial direction is formed in the central portion of the bottom portion of the pump chamber forming recessed portion 8 . One axial end of the pump drive shaft 7 is rotatably arranged in the recess 9 .

The pump cover 4 includes a main body portion 10 having a predetermined axial thickness and extending in the radial direction, and a cylindrical projecting portion 11 projecting from the other axial side end surface of the main body portion 10 toward the other axial side. and Further, one through hole 12 is formed in the pump cover 4 so as to axially pass through the projecting portion 11 and the main body portion 10 . Therefore, the projecting portion 11 is cylindrical. A pump drive shaft 7 is rotatably inserted through the through hole 12 . The pump drive shaft 7 is inserted through the through hole 12 and rotatably supported by the pump cover 4 . In this manner, the pump drive shaft 7 is radially supported by the pump cover 4 over a wide area in the axial direction. The other end in the axial direction of the pump drive shaft 7 is rotatably arranged in an axial recess 16 formed in a wall-like support portion 15 that is a structure on the vehicle body side.

The pump cover 4 is fixed to the pump body 3 in such a state that one axial end face of the main body 10 covers the opening of the pump chamber forming recess 8 of the pump body 3 on the other axial side to close the opening. . A pump chamber 13 in which the pump rotor 6 is accommodated is formed by the one axial end face of the main body portion 10 of the pump cover 4 and the pump chamber forming concave portion 8 of the pump body 3 .

The pump rotor 6 is composed of an inner rotor (not shown) and an outer rotor (not shown). The inner rotor is connected to the portion on one side of the pump drive shaft 7 in the axial direction, and the inner rotor and the pump drive shaft 7 rotate integrally. As the inner rotor rotates in the pump chamber 13 , oil is drawn into the pump chamber 13 through a suction port (not shown) of the pump chamber 13 and discharged out of the pump chamber 13 through a discharge port 14 of the pump chamber 13 . Thus, the oil pump 2 is driven by the rotation of the pump drive shaft 7 . That is, the pump drive shaft 7 is a shaft for driving the oil pump 2 .

An oil pump drive device 1 according to this embodiment is a device for driving a pump drive shaft 7 . The oil pump drive device 1 includes two one-way clutches arranged on the pump drive shaft 7 of the oil pump 2 on the other axial side of the oil pump 2 . The two one-way clutches are arranged side by side in the axial direction on the same axis as the pump drive shaft 7, and are arranged in order of the first one-way clutch 21 and the second one-way clutch 23 from one side in the axial direction to the other side in the axial direction. there is

In this embodiment, the first one-way clutch 21 is for transmitting the driving force of the motor, which is the power source, to the oil pump 2, and the second one-way clutch 23 is for transmitting the driving force of the engine, which is the power source, to the oil pump. 2 for transmission. The first one-way clutch 21 and the second one-way clutch 23 have a common inner ring 25 in which respective inner rings are integrated. The common inner ring 25 is fixed to the pump drive shaft 7 as will be described later, and the oil pump drive device 1 is configured to selectively transmit the drive force of the engine and the drive force of the motor to the pump drive shaft 7. . In addition, in the following description, the common inner ring of the first one-way clutch 21 and the second one-way clutch 23 is simply referred to as "inner ring 25". Further, in the following description, of the configuration of the second one-way clutch 23, the configuration similar to that of the first one-way clutch 21 will be described with reference to FIG.

As shown in FIGS. 3 and 4, the first one-way clutch 21 has an outer ring 21a spaced radially outwardly from the inner ring 25 and arranged coaxially with the inner ring 25 and rotatable relative to the inner ring 25. and a plurality of (five in this embodiment) rollers 21b interposed between the inner ring 25 and the outer ring 21a at predetermined intervals in the circumferential direction, and the rollers 21b are arranged in a direction to connect the inner ring 25 and the outer ring 21a. It comprises a biasing coil-shaped or accordion-shaped spring 21c and a plurality (five in this embodiment) of block bearings 21d for maintaining the radial spacing between the inner ring 25 and the outer ring 21a. The roller 21b is a torque transmission member that connects the inner ring 25 and the outer ring 21a and transmits torque between the inner ring 25 and the outer ring 21a.

The second one-way clutch 23 has an outer ring 23a spaced radially outward from the inner ring 25 and arranged coaxially with the inner ring 25 so as to be relatively rotatable. Thus, the first one-way clutch 21 and the second one-way clutch 23 are provided with independent outer rings 21a and 23a, respectively. The radial spacing between the inner ring 25 and the outer ring 23a of the second one-way clutch 23 is the same as the radial spacing between the inner ring 25 and the outer ring 21a of the first one-way clutch 21. Between the clutch 23 and the outer ring 23a, a torque transmission member and a block bearing having the same configuration as the first one-way clutch 21 are provided. That is, as shown in FIGS. 3 and 4, the second one-way clutch 23 includes a plurality of (five in this embodiment) rollers 23b interposed at predetermined intervals in the circumferential direction, and the rollers 23b arranged on the inner ring 25 and the outer ring. a coil-shaped or accordion-shaped spring 23c that urges the inner ring 25 and the outer ring 23a in a direction to join them together; , is equipped with

In this embodiment, the five rollers 21b of the first one-way clutch 21 and the five rollers 23b of the second one-way clutch 23 are arranged at the same circumferential positions with respect to the inner ring 25, respectively. In other words, the five rollers 21b of the first one-way clutch 21 and the five rollers 23b of the second one-way clutch 23 correspond one-to-one, and the corresponding two rollers 21b and 23b are aligned along the axial direction. are placed. Similarly, the five block bearings 21d of the first one-way clutch 21 and the five block bearings 23d of the second one-way clutch 23 are in one-to-one correspondence, and the corresponding two block bearings 21d and 23d are arranged axially. are arranged side by side.

The inner ring 25 includes a cylindrical main body portion 27 having a predetermined length in the axial direction, and a connecting portion 29 formed by protruding radially inward from the inner peripheral surface of the other axial end portion of the main body portion 27 . consists of A spline 31 is formed on the inner diameter portion of the connecting portion 29 . The inner ring 25 is fixed to the pump drive shaft 7 by fitting the splines 31 of the connecting portion 29 to the splines 32 formed on the outer peripheral surface of the pump drive shaft 7 . With this configuration, the inner ring 25 and the pump drive shaft 7 rotate together.

The body portion 27 of the inner ring 25 is arranged radially outward of the projecting portion 11 of the pump cover 4 when viewed in the axial direction, and overlaps the projecting portion 11 of the pump cover 4 in the radial direction. are arranged to have That is, the main body portion 27 of the inner ring 25 has a portion that radially overlaps the pump drive shaft 7 and the projecting portion 11 of the pump cover 4 . The one axial end face of the body portion 27 of the inner ring 25 axially faces the other axial end face of the body portion 10 of the pump cover 4 with a gap therebetween. A surface on one side in the axial direction of the connecting portion 29 of the inner ring 25 is axially opposed to an end surface on the other side in the axial direction of the projecting portion 11 of the pump cover 4 with a gap therebetween. Further, the inner peripheral surface of the main body portion 27 of the inner ring 25 slides and rotates with respect to the outer peripheral surface of the projecting portion 11 of the pump cover 4 . That is, the inner ring 25 is rotatably supported by the projecting portion 11 of the pump cover 4 .

As shown in FIG. 4 , a plurality of recesses 33 are formed on the outer peripheral surface of the body portion 27 of the inner ring 25 so as to be recessed radially inward. In this embodiment, five recesses 33 are formed at predetermined intervals in the circumferential direction. The recessed portion 33 is formed over the entire axial length of the outer peripheral surface of the body portion 27 . A roller 21 b of the first one-way clutch 21 and a roller 23 b of the second one-way clutch 23 are arranged in the recess 33 . The bottom surface of the recess 33 forms a cam surface 35 with which the roller 21b of the first one-way clutch 21 and the roller 23b of the second one-way clutch 23 are engaged. The cam surface 35 is an inclined surface that is inclined in a direction in which the radial distance between the inner peripheral surface of the outer ring 21a and the inner peripheral surface of the outer ring 23a increases from one circumferential end of the recess 33 toward the other circumferential end.

Since the roller 21b of the first one-way clutch 21 and the roller 23b of the second one-way clutch 23 are arranged side by side in the axial direction as described above, the roller 21b of the first one-way clutch 21 is engaged with the cam surface 35. The mating portion and the portion with which the roller 23b of the second one-way clutch 23 engages are formed side by side in the axial direction.

The roller 21b is a cylindrical member. The roller 21 b is arranged in the recess 33 so that the axial direction of the roller 21 b itself is parallel to the axial directions of the outer ring 21 a and the inner ring 25 . The roller 21 a slides or rolls on the cam surface 35 of the recess 33 . The roller 23b also has the same configuration as the roller 21b.

The block bearing 21d gradually decreases in circumferential dimension from the upper and lower ends in the radial direction toward the central portion in the radial direction, and both sides in the circumferential direction are constricted in the central portion. A plurality of block bearings 21d (five in this embodiment) are arranged at predetermined intervals in the circumferential direction, and maintain the radial interval between the outer ring 21a and the inner ring 25, and hold the outer ring 21a and the inner ring 25 concentrically. ing. The block bearing 23d also has the same configuration as the block bearing 21d.

A retainer 37 is arranged between the inner ring 25 and the outer rings 21a and 23a to hold the rollers 21b, 23b, block bearings 21d and 23d. As shown in FIGS. 3 and 4, the retainer 37 includes a first annular portion 39 disposed on one side in the axial direction of the rollers 21b of the first one-way clutch 21 and a roller 23b of the second one-way clutch 23 in the axial direction. It is composed of a second annular portion 41 arranged on the other side, and a plurality of first column portions 43 and a plurality of second column portions 45 axially connecting the first annular portion 39 and the second annular portion 41 . ing. The first column portion 43 and the second column portion 45 form one set in this order from one side in the circumferential direction to the other side in the circumferential direction. 5 sets) are provided in the embodiment.

As shown in FIG. 3 , a flange 47 that protrudes radially inward is formed on the inner diameter side edge of the first annular portion 39 of the retainer 37 , and the other surface of the flange 47 in the axial direction faces the inner ring 25 . is in contact with the end face on one side in the axial direction of the A flange 49 protruding radially inward is formed on the inner diameter side edge of the second annular portion 41 of the retainer 37 , and the surface of the flange 49 on one side in the axial direction corresponds to the end surface on the other side in the axial direction of the inner ring 25 . are in contact with With such a configuration, the retainer 37 is restricted from moving in the axial direction.

As shown in FIG. 4 , a protruding portion 51 that protrudes radially inward and extends in the axial direction is formed on the inner peripheral portion of the first column portion 43 of the retainer 37 . The projecting portion 51 engages with an axial groove 53 formed in the outer peripheral surface of the inner ring 25 . Due to this engagement, relative rotation of the retainer 37 with the inner ring 25 is restricted, and the retainer 37 rotates integrally with the inner ring 25 .

As shown in FIG. 4, the surface of the first column portion 43 of the retainer 37 on the other side in the circumferential direction is formed into a curved surface corresponding to the concave shape of the surface on the one side in the circumferential direction of the block bearings 21d and 23d. 21d and 23d are in contact with the entire surface on one side in the circumferential direction. A surface of the second column portion 45 of the retainer 37 on one side in the circumferential direction is formed into a curved surface corresponding to the concave shape of the surface on the other side in the circumferential direction of the block bearings 21d and 23d. It is in contact with the entire surface of the side. With this configuration, the block bearings 21d and 23d are restrained from moving in the circumferential direction by the first column portion 43 and the second column portion 45, and are also prevented from rattling outward in the radial direction.

The surface of the first column portion 43 of the retainer 37 on one side in the circumferential direction and the surface of the second column portion 45 on the other side in the circumferential direction face each other in the circumferential direction with a predetermined gap therebetween. One roller 21b and one roller 23b are arranged in a space 55 formed by the surface of the first columnar portion 43 on one side in the circumferential direction and the surface of the second columnar portion 45 on the other side in the circumferential direction. A concave portion 57 is formed in a portion on one side in the axial direction, and a concave portion 58 having the same configuration as the concave portion 57 is formed in a portion on the other side in the axial direction. A spring 21c is arranged in the concave portion 57 for biasing the roller 21b in the engaging direction with the cam surface 35, ie, one side in the circumferential direction, and the concave portion 58 pushes the roller 23b in the engaging direction with the cam surface 35, ie, in the circumferential direction. A spring 23c is arranged for biasing to one side.

A thrust washer 61 is arranged between the second one-way clutch 23 and the support portion 15 . Thrust washer 61 is fixed to support portion 15 in a state in which relative rotation with respect to support portion 15 is restricted by fixing pin 62 . Thrust washer 61 has an inner diameter portion in contact with the other axial end face of inner ring 25 and an outer diameter portion in contact with the other axial end face of outer ring 23a. That is, the thrust washer 61 is a thrust bearing for the inner ring 25 and the outer ring 23 a of the second one-way clutch 23 .

A thrust washer 63 is arranged between the outer ring 21 a of the first one-way clutch 21 and the outer ring 23 a of the second one-way clutch 23 . Thrust washer 63 is fixed to one axial end surface of outer ring 23 a of second one-way clutch 23 by fixing pin 64 . The outer ring 21a of the first one-way clutch 21 slides and rotates against the surface of the thrust washer 63 on one side in the axial direction.

Rotation of the output shaft of the motor (not shown) is transmitted to an annular first driving member 65 that drives the outer ring 21a of the first one-way clutch 21 via a gear mechanism (not shown). In this embodiment, the rotation of the first drive member 65 is transmitted to the outer ring 21a of the first one-way clutch 21 via a speed reduction mechanism provided on the outer diameter side of the outer ring 21a of the first one-way clutch 21. That is, the rotation of the motor output shaft transmitted to the first drive member 65 is decelerated and transmitted to the outer ring 21 a of the first one-way clutch 21 . The configuration of the speed reduction mechanism will be described later.

In the first one-way clutch 21, when the outer ring 21a rotates clockwise in FIG. 4 with respect to the inner ring 25, the roller 21b engages with the cam surface 35 of the inner ring 25 and the inner peripheral surface of the outer ring 21a, thereby rotating the outer ring 21a and the inner ring. 25 are coupled to rotate together, and the rotation is transmitted from the outer ring 21a to the inner ring 25. As shown in FIG. On the other hand, when the outer ring 21a rotates counterclockwise with respect to the inner ring 25 in FIG. In this state, rotation is not transmitted from the outer ring 21a to the inner ring 25. As shown in FIG.

Rotation of the output shaft of the engine (not shown) is transmitted to an annular second drive member 67 that drives the outer ring 23a of the second one-way clutch 23 via a gear mechanism (not shown). A gear 68 is formed on the outer peripheral portion of the second driving member 67 . A gear 69 that meshes with the gear 68 of the second driving member 67 is formed on the outer peripheral portion of the outer ring 23 a of the second one-way clutch 23 . Therefore, the outer ring 23 a of the second one-way clutch 23 rotates in the opposite direction to the second driving member 67 . The rotation of the second driving member 67 is transmitted to the outer ring 23 a of the second one-way clutch 23 via a gear 69 meshing with the gear 68 of the second driving member 67 .

In the second one-way clutch 23, when the outer ring 23a rotates clockwise in FIG. 4 with respect to the inner ring 25, the roller 23b engages the cam surface 35 of the inner ring 25 and the inner peripheral surface of the outer ring 23a, and the outer ring 23a and the inner ring are engaged. 25 are coupled to rotate together, and the rotation is transmitted from the outer ring 23a to the inner ring 25. As shown in FIG. On the other hand, when the outer ring 23a rotates counterclockwise relative to the inner ring 25 in FIG. In this state, rotation is not transmitted from the outer ring 23a to the inner ring 25. As shown in FIG.

Next, the speed reduction mechanism of the first one-way clutch 21 will be explained.
The outer ring 21a of the first one-way clutch 21 has an inner cylindrical portion 71 and an annular flange portion 72 integrally formed with the cylindrical portion 71 and extending radially outward from the outer peripheral surface of the cylindrical portion 71. ing. The flange portion 72 is formed in the axially central portion of the cylindrical portion 71 . The surface of the flange portion 72 on one side in the axial direction and the outer peripheral surface of the first portion 73 of the cylindrical portion 71 extending to the one side in the axial direction from the flange portion 72 are substantially perpendicular when viewed in the radial direction. A second portion 74 of the cylindrical portion 71 extending on the other side in the axial direction from the flange portion 72 has an outer diameter dimension larger than that of the first portion 73 of the cylindrical portion 71 . The other axial end surface of the second portion 74 of the cylindrical portion 71 contacts and slides on the thrust washer 63 . When the outer ring 21a idles with respect to the inner ring 25, the inner peripheral surface of the cylindrical portion 71 slides on the outer peripheral surface of the block bearing 21d, and the roller 21b rolls or slides on the inner peripheral surface of the cylindrical portion 71. do.

A plurality of pinion gears 75 are arranged at predetermined intervals in the circumferential direction on one axial side surface of the flange portion 72 of the outer ring 21a. These pinion gears 75 are arranged on the outer diameter side of the outer ring 25a so as not to mesh with each other. Each pinion gear 75 is rotatably attached to a shaft member 76 that protrudes perpendicularly to one axial side surface of the flange portion 72 of the outer ring 21a. That is, the pinion gear 75 is rotatably attached to the flange portion 72 of the outer ring 21a about the shaft member 76. As shown in FIG. In this embodiment, as shown in FIG. 4, eight shaft members 76 are provided and eight pinion gears 75 are arranged. The center of the virtual circle C connecting the shaft members 76 of the eight pinion gears 75 is coaxial with the rotation axis of the outer ring 21a.

One external gear 78 that meshes with the eight pinion gears 75 on the outer diameter side of the outer ring 21a is arranged on the inner diameter side of the virtual circle C connecting the shaft members of the eight pinion gears 75 . The external gear 78 is arranged coaxially with the outer ring 21a. The external gear 78 has a cylindrical portion 80 having a gear 79 formed on its outer periphery that meshes with the pinion gear 75, and an annular inward flange portion 81 extending radially inward from one axial end of the cylindrical portion 80. It consists of The external gear 78 is fixed to the pump case 5 in a state in which relative rotation with the pump case 5 is restricted, that is, in a state in which rotation is restricted. Specifically, the surface of the pump cover 4 of the oil pump 2 on the other side in the axial direction is formed with an annular recess 82 that is recessed toward the one side in the axial direction. The portion 81 is fixed to the inside of the recess 82 with a fixing pin 83 , thereby being fixed to the pump cover 4 .

The other axial end surface of the cylindrical portion 80 of the external gear 78 axially faces the one axial surface of the radially outward flange portion 72 of the outer ring 21a with a gap therebetween. The inner peripheral surface of the cylindrical portion 80 of the external gear 78 radially faces the outer peripheral surface of the first portion 73 of the cylindrical portion 71 of the outer ring 21a with a gap therebetween. The other axial surface of the inward flange portion 81 of the external gear 78 axially faces the one axial end surface of the cylindrical portion 71 of the outer ring 21a. A thrust washer 84 is interposed between the inward flange portion 81 of the external gear 78 and one axial end surface of the cylindrical portion 71 of the outer ring 21a. The thrust washer 84 is fixed to the inward flange portion 81 of the external gear 78 by a fixing member (not shown).

The outer ring 21a of the first one-way clutch 21 and the outer ring 23a of the second one-way clutch 23 are arranged between the external gear 78 fixed to the pump cover 4 and the support portion 15 between the thrust washer 84, the thrust washer 63, and the thrust washer 84. It is axially supported via a washer 61 .

One internal gear 85 meshing with the eight pinion gears 75 is arranged radially outward of the flange portion 72 of the outer ring 21a, that is, on the outer diameter side of the virtual circle C connecting the shaft members 76 of the eight pinion gears 75. . The internal gear 85 is arranged coaxially with the outer ring 21a. The internal gear 85 is formed in a cylindrical shape extending in the axial direction, and a gear 86 that meshes with the pinion gear 75 is formed at one axial end of the inner peripheral portion. The axial central portion of the inner peripheral portion of the internal gear 85 is formed to have a larger inner diameter than the one axial end portion of the inner peripheral portion, and is continuous with the one axial end portion via a stepped portion 87 . ing. The stepped portion 87 is engaged with the outer edge portion of the surface on one side in the axial direction of the flange portion 72 of the outer ring 21 a. An axial central portion of the inner peripheral portion of the internal gear 85 radially faces the outer peripheral surface of the flange portion 72 of the outer ring 21a with a gap therebetween. Alternatively, the axial central portion of the inner peripheral portion of the internal gear 85 may be configured to slide smoothly on the outer peripheral surface of the flange portion 72 of the outer ring 21a.

Two circumferential grooves 88 and 89 are formed adjacent to each other in the axial direction on the other axial side portion of the inner peripheral portion of the internal gear 85 . A thrust washer 90 is attached to the circumferential groove 88 on one side in the axial direction. A snap ring 91 is attached to the circumferential groove 89 on the other side in the axial direction, thereby restricting movement of the thrust washer 90 to the other side in the axial direction. The surface of the thrust washer 90 on one side in the axial direction axially faces the surface on the other side in the axial direction of the flange portion 72 of the outer ring 21a, contacts the surface on the other side in the axial direction of the flange portion 72, and is smooth. slide to. In the internal gear 85, the stepped portion 87 on the inner peripheral side engages with the outer edge portion of the surface on the one axial side of the flange portion 72 of the outer ring 21a, and the thrust washer 90 engages on the other axial side of the flange portion 72 of the outer ring 21a. Axial movement is restricted by contact with the surface of

A gear 92 is formed on the outer peripheral portion of the internal gear 85 . A gear 92 on the outer periphery of the internal gear 85 meshes with a gear 93 on the outer periphery of the first driving member 65 to which the rotation of the output shaft of the motor is transmitted. Therefore, the internal gear 85 rotates in the opposite direction to the first drive member 65 .

An internal gear 85 to which the rotation of the output shaft of the motor is transmitted; a plurality of pinion gears 75 arranged on the flange portion 72 of the outer ring 21a of the first one-way clutch 21 and meshing with the internal gear 85; , a plurality of pinion gears 75 and an external gear 78 meshing with each other constitute a reduction mechanism of the first one-way clutch 21 . The internal gear 85, the outer ring 21a having the flange portion 72, the plurality of pinion gears 75, and the external gear 78 constitute a planetary gear A (see FIG. 1) in FIG. That is, the internal gear 85, the pinion gear 75, the outer ring 21a, and the external gear 78 constitute the ring gear, pinion gear, planetary carrier, and sun gear of the planetary gear A, respectively.

Next, the operation of the speed reduction mechanism of the first one-way clutch 21 and the operation of the oil pump driving device 1 of this embodiment will be described.

Rotation of the output shaft of the motor (not shown) is transmitted to the first driving member 65 that drives the first one-way clutch 21, and when the first driving member 65 rotates counterclockwise in FIG. Gear 85 rotates clockwise. Thus, the rotation of the output shaft of the motor transmitted to the first drive member 65 is transmitted to the speed reduction mechanism provided on the outer ring 21 a of the first one-way clutch 21 . When the internal gear 85 rotates clockwise, the rotation is transmitted to the pinion gears 75 meshing with the gear 86 on the inner circumference of the internal gear 85 . Since the pinion gear 75 also meshes with the external gear 78 fixed to the pump cover 4 in a state where rotation is restricted, the plurality of pinion gears 75 to which the rotation of the internal gear 85 is transmitted are each connected to the shaft member 76. and move clockwise while meshing with the gear 86 of the internal gear 85 and the gear 79 of the external gear 78 . As the plurality of pinion gears 75 rotate clockwise and move clockwise, the flange portion 72 of the outer ring 21a rotates clockwise. That is, the outer ring 21a of the first one-way clutch 21 rotates clockwise.

Here, in the reduction mechanism of the first one-way clutch 21 constituting the planetary gear A, the internal gear 85 is an input element, the external gear 78 is a fixed element, and the outer ring 21a is an output element. Therefore, the motor rotation input to the internal gear 85 is reduced in speed via the pinion gear 75 and the external gear 78 and transmitted to the outer ring 21a. As described above, according to this embodiment, even if high rotation of the motor is transmitted to the first driving member 65, the rotation of the motor is transmitted to the outer ring 21a of the first one-way clutch 21 at a reduced speed.

It should be noted that how much the rotation of the motor transmitted to the first drive member 65 is decelerated before being transmitted to the outer ring 21a of the first one-way clutch 21 depends on the performance of the motor and the oil pump 2, and the performance of the first one-way clutch 21. It is designed with comprehensive consideration of torque capacity and other factors.

When the outer ring 21a of the first one-way clutch 21 rotates clockwise, the roller 21b engages the cam surface 35 of the inner ring 25 and the inner peripheral surface of the outer ring 21a, and the outer ring 21a and the inner ring 25 are coupled to rotate integrally. Rotation is transmitted from the outer ring 21 a to the inner ring 25 . The rotation of the inner ring 25 causes the pump drive shaft 7 to rotate, thereby driving the oil pump 2 .

On the other hand, the rotation of the output shaft of the engine (not shown) is transmitted to the second driving member 67 that drives the second one-way clutch 23, and when the second driving member 67 rotates counterclockwise in FIG. It rotates in the opposite direction to the outer ring 23 a of the second one-way clutch 23 , and the rotation of the second driving member 67 is transmitted to the outer ring 23 a of the second one-way clutch 23 . When the outer ring 23a of the second one-way clutch 23 rotates clockwise, the roller 23b engages the cam surface 35 of the inner ring 25 and the inner peripheral surface of the outer ring 23a, and the outer ring 23a and the inner ring 25 are coupled to rotate together. Rotation is transmitted from the outer ring 23 a to the inner ring 25 . The rotation of the inner ring 25 causes the pump drive shaft 7 to rotate, thereby driving the oil pump 2 .

The pump driving device 1 of this embodiment selectively selects the reduced motor rotation transmitted to the outer ring 21a of the first one-way clutch 21 and the engine rotation transmitted to the outer ring 23a of the second one-way clutch 23. It is transmitted to the inner ring 25, thereby driving the oil pump 2 at all times. When the outer ring 21a of the first one-way clutch 21 and the outer ring 23a of the second one-way clutch 23 rotate simultaneously, the pump driving device 1 transmits the rotation of the faster one of the outer ring 21a and the outer ring 23a to the inner ring. do. At this time, the slower rotating one of the outer ring 21 a and the outer ring 23 a rotates counterclockwise relative to the inner ring 25 and is idle with respect to the inner ring 25 .

When the oil pump 2 is driven, lubricating oil discharged from the discharge port 14 of the pump chamber 13 is supplied to oil passages 94 , 95 and 96 provided inside the pump cover 4 and the pump drive shaft 7 . , through these oil passages 94, 95, 96 to the lubricating parts of the first one-way clutch 21 and the second one-way clutch 23, and to other drive-related devices (not shown).

Next, the effects of the oil pump driving device 1 according to this embodiment will be described.
Since the oil pump driving device 1 according to the present embodiment is provided with the speed reduction mechanism configured as described above, the rotation of the motor is reduced and transmitted to the outer ring 21a of the first one-way clutch 2.BR>P. . Therefore, even if a high rotation motor is applied as a vehicle drive device, the oil pump 2 is not subjected to a high rotation load. As a result, seizing of the oil pump 2 can be prevented even if a high-speed motor is used.

In addition, the oil pump drive device 1 according to this embodiment is provided with a speed reduction mechanism on the outer diameter side of the outer ring 21 a of the first one-way clutch 21 . Therefore, according to this embodiment, it is not necessary to separately secure a space for providing a speed reduction mechanism between the motor and the oil pump driving device 1 . Therefore, it is possible to realize the oil pump driving device 1 compatible with a high rotation motor without increasing the installation space as compared with the conventional oil pump driving device.
Further, since the oil pump driving device 1 is provided with a speed reduction mechanism on the outer diameter side of the outer ring 21a of the first one-way clutch 21, the speed reduction mechanism is arranged at substantially the same axial position as the outer ring 21a of the first one-way clutch 21. It is As a result, it is possible to suppress an increase in the axial dimension of the first one-way clutch 21 and further the axial dimension of the oil pump drive device 1 .

It should be noted that the oil pump driving device 1 according to this embodiment is not limited to the above embodiment, and modifications are possible. For example, the torque transmission members of one or both of the first one-way clutch 21 and the second one-way clutch 23 may be sprags instead of rollers. Also, the number of torque transmission members can be appropriately adjusted.

Further, the type of the oil pump driven by the oil pump drive device 1 according to this embodiment is not limited, and for example, an internal gear pump, an external gear pump, a vane pump, or the like can be used.

As described above, the oil pump driving apparatus according to the second embodiment includes the speed change clutch B coaxially with the speed reduction mechanism of the first embodiment, ie, the planetary gear A (see FIG. 2). Also, the number of pinion gears used in the planetary gear A is not limited by specification settings. The speed change clutch B is provided on the outer diameter side of the first one-way clutch, like the planetary gear A of the first embodiment. Since other configurations are the same as those of the oil pump driving device according to the first embodiment, detailed description thereof will be omitted.

1 Pump drive device 2 Oil pump 3 Pump body 4 Pump cover 5 Pump case 7 Pump drive shaft 15 Support part 21 First one-way clutch 21a Outer ring 21b Roller 23 Second one-way clutch 23a Outer ring 23b Roller 25 Inner ring 35 Cam surface 37 Cage 61 thrust washer 65 first drive member 67 second drive member 75 pinion gear 78 external gear 85 internal gear

Claims (2)

Equipped with two one-way clutches arranged coaxially with the pump drive shaft of the oil pump,
Rotation is transmitted from drive members different from each other to the respective outer rings of the two one-way clutches,
the two one-way clutches selectively transmit rotation of the respective outer rings to the pump drive shaft via torque transmission members;
An oil pump drive device comprising a reduction mechanism on one of the outer diameter sides of the two one-way clutches for reducing rotation transmitted from the corresponding drive member and transmitting the rotation to the outer ring of the one one-way clutch,
A transmission clutch is provided coaxially with the speed reduction mechanism,
The oil pump drive device according to claim 1, wherein the speed change clutch is capable of connecting the corresponding driving member and the reduction mechanism, and further capable of disconnecting the connection . The speed reduction mechanism includes an external gear having external teeth formed coaxially with the outer ring of the one one-way clutch and on an outer diameter side of the outer ring and fixed to the oil pump;
a plurality of pinion gears provided rotatably on the outer diameter side of the outer ring and meshing with the external gear;
2. The oil pump driving device according to claim 1 , further comprising an internal gear that rotates integrally with the driving member and meshes with the plurality of pinion gears.

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