JPH10238609A - Axial piston machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To surely lubricate the contact surface of a swash plate while reducing agitating resistance of oil. SOLUTION: In this machine, a substantially cylindrical collar member 72 is arranged between a motor shaft 17 of a radial piston motor 25 and a through- hole 38b of a motor swash plate 38 arranged on its radially outside. Nine oil holes 72 are formed on the collar member 72 so as to face to two oil holes 17e radially branched from an oil passage 17a formed inside the motor shaft 17. Oil is supplied from the two oil holes 17e to an oil distribution chamber 73 on an inner periphery of the collar member 72, and evenly distributed to a contact surface 38c of the motor swash plate 38. The motor swash plate 38 is lubricated with certainly without being impregnated with oil.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial piston pump or an axial piston in which a piston is supported in a plurality of cylinder holes formed in a cylinder so as to surround the axis thereof, and the piston is reciprocated in an axial direction by a swash plate. Motor related.

[0002]

2. Description of the Related Art A hydrostatic continuously variable transmission combining an axial piston pump and an axial piston motor is known from Japanese Patent Application Laid-Open No. 5-263899.

Since the piston of an axial piston pump or an axial piston motor comes into contact with the contact surface of a swash plate via a shoe, it is necessary to supply oil to the contact surface for lubrication. In the above-mentioned conventional apparatus, the contact surface is lubricated by filling oil into a casing accommodating an axial piston pump and an axial piston motor.

[0004]

However, when oil is filled in the casing to lubricate the contact surface of the swash plate, the oil is agitated by the rotating cylinder and piston. There is a problem that occurs.

The present invention has been made in view of the above circumstances, and has as its object to surely lubricate the contact surface of a swash plate while reducing the stirring resistance of lubricating oil.

[0006]

According to the first aspect of the present invention, the oil supplied from the oil passage of the rotating shaft through the opening of the rotating shaft is received by the inner peripheral surface of the collar member. The oil is supplied evenly to the contact surface of the swash plate through oil holes formed at a plurality of positions in the circumferential direction of the collar member.
Even if the number of openings of the rotating shaft is set small to secure the strength of the rotating shaft, the oil supplied from the opening is evenly distributed in the circumferential direction from the oil hole of the collar member to enhance the lubrication effect. Can be. Since a sufficient lubricating effect can be obtained without immersing the swash plate in oil, the oil stirring resistance is reduced.

According to the second aspect of the present invention, when a part of the oil supplied from the oil hole of the collar member leaks through the gap between the through hole of the swash plate and the outer peripheral surface of the rotating shaft, the oil is removed. Although it cannot contribute to the lubrication of the contact surface, by closing the gap with the closing member, the oil can effectively act on the contact surface to enhance the lubrication effect.

[0008]

1 to 10 show one embodiment of the present invention. FIG. 1 is an overall side view of a hydraulic and mechanical transmission for an automobile, and FIG. 2 is an enlarged view of a portion A in FIG. FIG. 3 is an enlarged longitudinal sectional view of a portion B in FIG. 1, FIG. 4 is a schematic diagram of the device transmission system,
5 is an enlarged view of a part 5 of FIG. 2, FIG. 6 is an enlarged view of a main part of FIG. 3, FIG. 7 is a sectional view taken along line 7-7 of FIG. 6, FIG. 8 is a sectional view taken along line 8-8 of FIG. 3 is an enlarged view of a main part of FIG. 3, and FIG. 10 is a diagram showing a relationship between a swash plate angle of the transmission and an overall speed ratio.

As shown in FIG. 2 to FIG.
The mechanical transmission device T includes a mechanical transmission device 1 and a hydrostatic continuously variable transmission 2. An engine E as a prime mover is provided on the front side of the mechanical transmission device 1 so as to sandwich the mechanical transmission device 1, and a continuously variable transmission is provided on the rear side. The transmissions 2 are respectively arranged, and these are housed inside the transmission case C. Further, the hydraulic pump 24 and the hydraulic motor 25 of the continuously variable transmission 2 including the axial piston pump and the axial piston motor are accommodated in an inner case Ci provided in the transmission case C, and the mechanical transmission device 1 of the inner case Ci is provided. The valve plate 27 of the continuously variable transmission 2 is joined to the open end face on the side so as to close it. The inner case Ci is divided into a first case half 42 and a second case half 43, and the first and second case halves 42 and 43 are separated by a plurality of bolts 44 (only one is shown in FIG. 3). It is connected to the valve plate 27.

The hydraulic / mechanical transmission 1 includes an input shaft 9 connected to a crankshaft 7 of an engine E via a torque damper 8, and a power collecting shaft 17 arranged coaxially with the input shaft 9.
And an intermediate shaft 18 concentrically disposed so as to surround the power collecting shaft 17, and a pump shaft 10 disposed in parallel with the power collecting shaft 17, and the input shaft 9 is provided with a ball on a front end wall of the transmission case C. It is supported via a bearing 19. The power collecting shaft 17 also serving as a motor shaft has a front end supported by the input shaft 9 via a needle bearing 20 and a rear end supported by a rear end wall of the inner case Ci via a ball bearing 21. The front and rear ends of the intermediate shaft 18 are supported by the outer periphery of the power collecting shaft 17 via needle bearings 22, 22, and the rear end of the intermediate shaft 18 is supported by the valve plate 27 via the needle bearing 23. Therefore, the intermediate portion of the power collecting shaft 17 is supported by the valve plate 27 via the intermediate shaft 18. The pump shaft 10 has a front end on a front end wall of the transmission case C via a ball bearing 45 and a rear end on an inner case Ci via a ball bearing 46.
The intermediate portion of the rear end wall is supported by the valve plate 27 via the needle bearing 47.

A parking gear 59, a speed sensor gear 60 and a coupling member 48 are spline-coupled to the rear end of the power gathering shaft 17 projecting rearward from the ball bearing 21 supported by the inner case Ci.
7 is fixed by a nut 61 screwed into the nut 7. A coupling member 48 protruding outward from a rear end wall of the transmission case C is connected to a propeller shaft (not shown) connected to driving wheels of the vehicle. The rear end of the pump shaft 10 protruding from the ball bearing 46 is connected to the ball bearing 4.
6 is fixed to the inner race 6 by a nut 62.

The mechanical transmission 1 transmits the power supplied from the engine E to the power collecting shaft 17 and the intermediate shaft 18, and transmits the power distributed to the intermediate shaft 18 to the pump shaft 10. And an interlocking device 4.

The power split device 3 is of a planetary gear type, and is rotatably supported by a carrier 11 fixed to the input shaft 9 and a pinion shaft 12 provided on the carrier 11 in parallel with the input shaft 9. A pair of first pinion gears 13 and second pinion gears 14 integrally connected to each other,
A pair of first and second sun gears 15 and 16 are provided which mesh with the first and second pinion gears 13 and 14 and are arranged on the same axis as the input shaft 9. The large-diameter first sun gear 15 is provided on the intermediate shaft. A small diameter second sun gear 16 is spline-coupled to the power collecting shaft 17 and is integrally formed with the power collecting shaft 17.
At this time, the second sun gear 16 is connected to the input shaft 9 and the first sun gear 1.
5 so as to be sandwiched between them. The second pinion gear 14 and the second sun gear 16 meshing with each other are constituted by helical gears.

The interlocking device 4 comprises a large-diameter helical gear 49 formed integrally with the intermediate portion of the intermediate shaft 18 and a small-diameter helical gear 50 formed integrally with the pump shaft 10 and meshing with the large-diameter helical gear 49. And is arranged so as to be sandwiched between the power split device 3 and the valve plate 27.

The continuously variable transmission 2 comprises a hydraulic pump 24, a hydraulic motor 25, and a valve plate 27 having a hydraulic closed circuit 26 for interconnecting these.

A hydraulic pump 24 is spline-coupled to the pump shaft 10 and movably contacts a hydraulic distribution surface 27a of a valve plate 27. The pump cylinder 28 is provided to surround the axis of the pump cylinder 28. A variable angle pump swash plate in which a plurality of pump pistons 30 movably supported by a large number of cylinder holes 29 in an annular arrangement and a shoe 31 movably contacted at the tip of each pump piston 30 are movably contacted. 32 and a variable capacity type. That is, the pump swash plate 32 has a semi-cylindrical trunnion shaft 32a, which is rotatably supported by a pump swash plate anchor 33 fixed to the inner case Ci.
Thereby, the pump swash plate 32 can increase or decrease the reciprocating stroke of each pump piston 30 according to the increase or decrease of the inclination angle α from the upright position orthogonal to the axis of the trunnion shaft 32a.

On the other hand, the hydraulic motor 25 is
And a motor cylinder 34 movably contacting the hydraulic distribution surface 27a of the valve plate 27, and a plurality of cylinder holes 35 in an annular arrangement provided around the axis of the motor cylinder 34 so as to surround the axis. A variable displacement motor piston is provided with a large number of supported motor pistons 36 and a variable angle motor swash plate 38 that movably contacts a shoe 37 attached to the tip of each motor piston 36 so as to swing freely. . That is, the motor swash plate 38 has a semi-cylindrical trunnion shaft 38a, which is rotatably supported by a motor swash plate anchor 39 fixed to the inner case Ci. As a result, the motor swash plate 38 is moved to the trunnion shaft 38a.
The reciprocating stroke of each motor piston 36 can be increased or decreased according to the increase or decrease of the inclination angle β from an upright position orthogonal to the axis of the motor piston 36.

A replenishing pump 40 for replenishing the hydraulic closed circuit 26 with oil leakage and for supplying oil for lubricating and cooling the components is provided with a transmission case C so as to be driven by the input shaft 9. Attached to the outer surface of the front end wall.

The lock-up device 41, which can fix the pump shaft 10 in a timely manner using the discharge oil pressure of the supply pump 40, is provided with a front end wall of the transmission case C and the pump shaft 10
Between the power split device 3 and the interlocking device 4 with the valve plate 27,
And are arranged so as to be radially adjacent to each other.

The lock-up device 41 is fixed to the front end wall of the transmission case C from the inside, and has a bottomed cylindrical cylinder 51 surrounding the end of the pump shaft 10. , A return spring 54 for urging the piston 53 toward the hydraulic chamber 52, and a pump shaft 1 in the cylinder 51.
0, and a pressure receiving plate 56 supported by an open end of the cylinder 51.
And a plurality of outer friction plates 57 movably spline-coupled to the inner periphery of the cylinder 51 between the piston 53 and the pressure receiving plate 56, and also movable to the outer periphery of the lock-up center 55 between the piston 53 and the pressure receiving plate 56. It is composed of a plurality of inner friction plates 58 which are splined and alternately overlapped with the outer friction plates 57. Thus, the discharge oil pressure of the replenishing pump 40 is controlled via a control valve (not shown) in the hydraulic chamber 5.
2, the piston 53 moves toward the pressure receiving plate 56 to sandwich the inner and outer friction plates 57 and 58, and the pump shaft 10 can be braked via the lock-up center 55 by the frictional contact therebetween. . The braking reaction force at this time is received by the front end wall of the transmission case C via the cylinder 51.

Next, the lubrication system of the hydraulic / mechanical transmission T will be described.

As apparent from FIGS. 2 and 5, a replenishment pump 40 composed of an external gear pump in which a pair of external gears (only one external gear is shown) is meshed with each other, is provided on the front surface of the transmission case C. The pump body 65 is housed inside the combined pump body 65, and its front surface is covered with a pump cover 66. An oil passage 67 connected to a discharge port (not shown) of the replenishing pump 40 is formed on a coupling surface between the transmission case C and the pump body 65, and the oil passage 67 radially penetrates the input shaft 9 in an oil hole. It communicates with the front end of the power collecting shaft 17 via 9a. In order to prevent oil from leaking from the gap between the input shaft 9 and the pump body 65 and the transmission case C,
A seal member 68 is arranged between the pump body 65 and the input shaft 9, and a seal member 69 is arranged between the transmission case C and the input shaft 9.

As is clear from FIGS. 2 and 3, a blind oil passage 17a is formed inside the power collecting shaft 17 at the front end thereof. The oil is supplied to the oil passage 17 a of the power collecting shaft 17 through the oil passage 67 and the oil hole 9 a of the input shaft 9. At four positions in the axial direction of the oil passage 17a of the power collecting shaft 17, the power collecting shaft 1
Oil holes 17b to 17e penetrating radially through the hole 7 are formed. The oil that has passed through the frontmost oil hole 17b lubricates and cools the front needle bearing 20, and
The first through an oil passage 11a formed in the carrier 11 in the radial direction and an oil passage 12a formed in the pinion shaft 12 in the axial direction.
The second pinion gears 13 and 14 are lubricated and cooled.

The oil passing through the second oil hole 17c from the front passes through an oil hole 49a penetrating the large-diameter helical gear 49, and lubricates and cools the thrust bearing 70 disposed between the large-diameter helical gear 49 and the carrier 11, Further, the thrust bearing 78 disposed between the large-diameter helical gear 49 and the valve plate 27, the spline portion of the first sun gear 15, and the needle bearing 22 are lubricated and cooled. The oil that has passed through the third oil passage 17d from the front lubricates and cools the contact portion between the motor cylinder 34 and the hydraulic distribution surface 27a of the valve plate 27, and lubricates and cools the needle bearings 22 and 23. .

As is apparent from FIG. 6, the motor cylinder 34 is supported by the power collecting shaft 17 by a spline 71 formed at the end on the motor swash plate 38 side so as to be movable in the axial direction. A substantially cylindrical collar member 7 is provided on the outer periphery of the power collecting shaft 17.
The rear end of the collar member 72 is supported, and the inner periphery of the front end of the collar member 72 fits the outer periphery of the rear end of the spline 71 of the motor cylinder 34. As a result, an annular oil distribution chamber 73 is defined between the power collecting shaft 17 and the collar member 72, and the two rearmost oil holes 17e of the power collecting shaft 17 are opened in the oil distribution chamber 73, and the collar member is opened. Nine oil holes 72a formed at equal intervals in the circumferential direction in the motor swash plate 3
8 through hole 38b.

Thus, the two oil holes 17 of the power collecting shaft 17
The oil supplied from e to the oil distribution chamber 73 is evenly scattered radially outward from the nine oil holes 72a of the collar member 72, and effectively lubricates and cools the contact surface 38c of the motor swash plate 38. At this time, the axial positions of the nine oil holes 72a are determined so that the oil is reliably supplied to the contact surface 38c even if the inclination angle of the motor swash plate 38 changes. If a plurality of oil holes 72a are formed at a plurality of positions in the axial direction of the collar member 72, more uniform oil supply becomes possible regardless of the inclination angle of the motor swash plate 38.

In the embodiment, two oil holes 17e of the power collecting shaft 17 are formed. However, by increasing the number, the contact surface 38c of the motor swash plate 38 can be evenly formed even if the collar member 72 is eliminated. Can be lubricated and cooled. However, when a large number of oil holes 17e are formed in the power collecting shaft 17, there is a problem that the strength of the power collecting shaft 17 is reduced. On the other hand, according to the present embodiment, while securing the strength by forming the minimum number of oil holes 17 e in the power collecting shaft 17,
The contact surface 38 is formed by the large number of oil holes 72a of the collar member 72.
c can enhance the lubricating effect.

As described above, according to the present embodiment, lubrication and cooling can be performed without immersing the pump swash plate 32 or the motor swash plate 38 in oil. Can be minimized.

When the oil supplied to the contact surface 38c of the motor swash plate 38 from the oil hole 72a of the collar member 72 flows out through the through hole 38b of the motor swash plate 38 to the side opposite to the contact surface 38c, the oil is It cannot contribute to lubrication and cooling of the contact surface 38c. In order to prevent oil from flowing out through the through hole 38b of the motor swash plate 38, a closing member 74 for closing the through hole 38b is provided.

As is clear from FIGS. 6 and 8, the motor swash plate 38 is formed in a substantially rectangular shape, and the contact surface 38c is formed on one side thereof, and a substantially rectangular guide which is long in the vertical direction is formed on the other side. A recess 38d is formed. Further, the through hole 38b of the motor swash plate 38 is formed in an oblong shape that is long in the vertical direction so as to prevent interference with the power collecting shaft 17 when the motor swash plate 38 is inclined. The closing member 74 movably supported by the guide recess 38d is formed of an octagonal plate, and has a circular opening 74a through which the power gathering shaft 17 penetrates at a central portion thereof. A pair of long holes 74b that are long in the vertical direction are formed. The closing member 74 penetrates through the pair of long holes 74b, and the motor swash plate 38
The two bolts 75 screwed into the guide hole prevent movement from the guide recess 38d while allowing vertical movement.

When the closing member 74 is inclined together with the motor swash plate 38, the diameter of the opening 74a of the closing member 74 is slightly smaller than the diameter of the power collecting shaft 17 so that the closing member 74 can be inclined with respect to the power collecting shaft 17. Largely formed. Since the closing member 74 is urged downward by gravity, the closing member 74 is supported with the upper end of the opening 74a in contact with the upper end of the power collecting shaft 17. Further, since the closing member 74 is eccentric with respect to the center of the trunnion shaft 38a of the motor swash plate 38, when the closing member 74 is fixed to the motor swash plate 38, the opening 74a interferes with the power collecting shaft 17 and the motor swash plate 38 is moved. Although the inclination becomes impossible, the above problem is solved by moving the closing member 74 up and down with the inclination of the motor swash plate 38.

By closing the gap between the through hole 38b of the motor swash plate 38 and the power collecting shaft 17 with the closing member 74 as described above, the oil supplied from the collar member 72 to the motor swash plate 38 is removed from the through hole 38b. It can be effectively supplied to the contact surface 38c without escape. Moreover, since the closing member 74 can move up and down with respect to the motor swash plate 38, the closing member 74 is prevented from interfering with the power collecting shaft 17 when the motor swash plate 38 is tilted.

The discharge port of the supply pump 40 (see FIG. 2) is connected to an oil passage 10a formed inside the pump shaft 10 via an oil passage 76 formed in the transmission case C and an oil pipe 77 (see FIG. 3). Connected to the rear end. As shown in FIG. 9, oil holes 10 b, 10 c, and 10 d extending in a radial direction are branched from three axial positions of an oil passage 10 a of the pump shaft 10. The oil supplied from the oil holes 10b and 10c is
The contact portion between the pump cylinder 28 and the hydraulic distribution surface 27a of the valve plate 27 and the needle bearing 47 are lubricated and cooled.

The rearmost two oil holes 10 of the pump shaft 10
The oil supplied from the contact surface 32 of the pump swash plate 32
While lubricating and cooling c, a collar member 72 and a closing member 74 are provided to evenly supply oil to the contact surface 32c at that time. The structures and functions of the collar member 72 and the closing member 74 of the pump shaft 10 are the same as those of the power collecting shaft 17 described above, and therefore, redundant description will be omitted.

Next, the motor cylinder 3 of the hydraulic motor 25
A structure for elastically pressing the pressure plate 4 against the hydraulic distribution surface 27a of the valve plate 27 will be described.

As is clear from FIGS. 6 and 7, the spring 81 housed in a compressed state in the space between the inner periphery of the motor cylinder 34 and the outer periphery of the power collecting shaft 17 has its front end at the front end of the motor cylinder 34. The inner periphery is supported by a washer 83 fixed by a clip 82. Three guide holes 34a penetrating the motor cylinder 34 in the axial direction are formed at 120 ° intervals radially outside the spline 71 that spline-connects the motor cylinder 34 to the power collecting shaft 17. The front end of a pin 84 movably supported by the guide hole 34a is supported by the rear end of the spring 81 via a washer 85 movably in the axial direction, and the rear end of the pin 84 is the front end of the collar member 72. Supported by As a result, the spring force of the rear end of the spring 81 is transmitted to the inner case Ci via the washer 85, the three pins 84, the collar member 72, and the ball bearing 21, and the spring 81
Is transmitted to the motor cylinder 34 via the washer 83 and the clip 82, so that the front end of the motor cylinder 34 is resiliently pressed against the hydraulic distribution surface 27a of the valve plate 27.

The motor cylinder 34 and the spring 81 are assembled from behind the power collecting shaft 17 (on the side of the motor swash plate 38). That is, the washer 85, the spring 81, the washer 83, and the clip 82 are assembled on the inner periphery of the motor cylinder 34 in advance, and the motor cylinder 34 is inserted from the rear end side of the power collecting shaft 17 and connected by the spline 71. Subsequently, after inserting the pin 84 into the guide hole 34a of the motor cylinder 34, the collar member 7 is
2. The motor swash plate 38 and the motor swash plate anchor 39 are inserted, and the ball bearing 21 is fixed to the inner case Ci so that the rear end of the collar member 72 is pushed forward. Then, the parking gear 59, the speed sensor gear 60, and the coupling member 48 are inserted into the power collecting shaft 17 and fixed with the nut 61.

As described above, the pin 84 is disposed movably in the axial direction outside the spline 71 in the radial direction, and the elastic force of the rear end of the spring 81 is applied to the rear end of the inner case Ci via the pin 84. By transmitting the force, the motor cylinder 34 can be biased toward the valve plate 27. As a result, it is not necessary to form a step on the power collecting shaft 17 to support the rear end of the spring 81, so that the motor cylinder 34 and the spring 81 can be assembled from the motor swash plate 38 side. The degree improves.

Similarly, in the hydraulic pump 24,
The front and rear ends of a pin 84 movably supported in a guide hole 28a provided in the pump cylinder 28 are
By supporting the rear end 1 and the front end of the collar member 72, the pump cylinder 28 and the spring 81 can be assembled from the pump swash plate 32 side.

As is apparent from FIG. 9, the ball bearing 46 supporting the pump shaft 10 on the inner case Ci is
The pump shaft 10 is supported by a cotter 86 fitted in an annular groove 10e. At this time, a step 72b is formed at the rear end of the collar member 72 supported on the outer periphery of the pump shaft 10, and the front and outer peripheral surfaces of the cotter 86 are pressed by the step 72b, so that no special parts are required. The cotter 86 can be reliably prevented from coming off.

Next, the operation of this embodiment will be described.

When the power of the engine E is supplied from the crankshaft 7 to the input shaft 9 via the torque damper 8, the power is distributed to the pinion gears 13 and 14 of different diameters via the pinion shaft 12 of the carrier 11, and the power is reduced to the small diameter. 1st pinion gear 1
The power distributed to 3 is transmitted from the large-diameter first sun gear 15 to the pump shaft 10 via the intermediate shaft 18 and the interlocking device 4. Therefore, assuming that the lock-up device 41 is in a non-operating state, the pump cylinder 28 of the hydraulic pump 24 is rotationally driven by the pump shaft 10. And pump swash plate 3
2 and the motor swash plate 38 are inclined at an appropriate angle from the upright position, the pump piston 30 opens the cylinder hole 29 with a stroke corresponding to the inclination angle α of the pump swash plate 32 for one rotation of the pump cylinder 28. Since one reciprocation and discharge and suction operations are performed, each cylinder hole 29
Is discharged from the motor cylinder 34 through the high pressure side of the hydraulic closed circuit 26 of the valve plate 27.
5 to give an inflating action to the corresponding motor piston 36, and when the piston 36 presses the motor swash plate 38, the rotational direction component of the reaction force rotates the motor cylinder 34 via the motor piston 36, The power is transmitted to the power collecting shaft 17. Then, the motor piston 36 having completed the expansion operation is subjected to a contraction operation this time by the motor swash plate 38, and the oil discharged from the corresponding cylinder hole 35 passes through the low pressure side of the hydraulic closed circuit 26 to perform the suction operation. It is sucked into the cylinder hole 29 of the pump piston 30. Thus, in the hydraulic motor 25, the motor piston 36 reciprocates with a stroke corresponding to the inclination angle β of the motor swash plate 38, and the motor cylinder 34 makes one rotation together with the power collect shaft 17 for each reciprocation.

By the way, the respective capacities of the hydraulic pump 24 and the hydraulic motor 25 correspond to the corresponding pistons 30, 36, respectively.
, Ie, the angles α, β of the swash plates 32, 38, the speed ratio of the continuously variable transmission 2
Can be steplessly controlled by changing the angles α and β of

On the other hand, the power distributed to the large-diameter second pinion gear 14 is directly supplied from the small-diameter second sun gear 16 to the power collecting shaft 17 to drive it.

As described above, one of the powers of the engine split by the power split device 3 is transmitted to the power collecting shaft 17 after being steplessly shifted by the hydrostatic continuously variable transmission 2, and the other is driven by the power Since the power is transmitted directly to the collective shaft 17, power transmission can be performed while satisfying both the performance of the continuously variable transmission and the transmission efficiency. Then, the power joined by the power collective shaft 17 is transmitted to a propeller shaft (not shown) via the coupling member 48 to drive the drive wheels.

Next, referring to FIG.
The relationship between the inclination angles α and β of the swash plates 32 and 38 in the mechanical transmission T and the overall speed ratio e will be described.

In the diagram, the horizontal axis represents the total speed ratio e,
The vertical axes represent the inclination angles α and β of the pump swash plate 32 and the motor swash plate 38. (1) When the overall speed ratio e = a α = 0 for the pump swash plate 32 and β = βma for the motor swash plate 38
It is when each is controlled by x. Since the capacity of the hydraulic pump 24 becomes zero by α = 0, even if the pump cylinder 28 is driven from the pump shaft 10, the pump piston 30
Does not stroke, the hydraulic pressure cannot be generated in the hydraulic closed circuit 26, and the hydraulic motor 25 does not operate. Therefore, all the power of the engine E supplied to the input shaft 9 is consumed for idling of the pump cylinder 28 with substantially no load, and the power collecting shaft 17 does not rotate. As a result, the overall speed ratio is e
= 0 (infinite reduction ratio). (2) When the total speed ratio e = a to b This is an area where the angle α of the pump swash plate 32 is gradually increased to αmax while the motor swash plate 38 is maintained at β = βmax. That is, as the angle α increases, the capacity of the hydraulic pump 24 increases, the hydraulic motor 25 is operated accordingly, and the transmission of power to the power collecting shaft 17 is also started. As a result, the overall speed ratio e increases. (3) When the Total Speed Ratio e = b to c This is a region where the angle β of the motor swash plate 38 is gradually reduced from βmax to 0 while the pump swash plate 32 is maintained at α = αmax. Since the capacity of the hydraulic motor 25 decreases due to the decrease in the angle β, the rotation speed of the pump cylinder 28 gradually decreases due to an increase in the load on the hydraulic pump 24, and stops at β = 0. On the contrary, since the rotation speed of the power collecting shaft 17 gradually increases, the total speed ratio e becomes β = 0.
Is the largest. That is, the transmission state is substantially achieved by only the mechanical transmission unit 1.

At this time, if the lock-up device 41 is operated, the pump shaft 10 can be mechanically fixed. Power loss due to hydraulic leak can be prevented. (4) When the total speed ratio is e = a to d With the motor swash plate 38 held at β = βmax, the pump swash plate 32 moves in the negative direction from α = 0, that is, the direction opposite to the forward movement from the upright position. This is the area that tilts toward. In this region, the direction in which hydraulic pressure is discharged from the hydraulic pump 24 to the hydraulic closed circuit 26 is reversed, so that the high-pressure side and the low-pressure side of the hydraulic closed circuit 26 are opposite to those at the time of forward movement, and the motor cylinder 34 rotates in the reverse direction. The shaft 17 can be reversed.

Incidentally, in such a hydraulic / mechanical transmission T, the motor cylinder 34 and the motor piston 36 of the hydraulic motor 25 are urged in directions away from each other by a hydraulic reaction force. The cylinder 28 and the pump piston 30 are urged in directions away from each other by a hydraulic reaction force. As a result, the motor cylinder 34 urged rightward by the hydraulic reaction force in FIG.
The motor piston 36 urged leftward by the hydraulic reaction force while urging the valve plate 27 movably in contact therewith to the right is moved to the inner case via the motor swash plate 38 and the motor swash plate anchor 39. The first case half 42 of Ci is urged to the left. The pump cylinder 28 urged rightward by the hydraulic reaction force urges the valve plate 27 with which it movably contacts to the right, and the pump piston 30 urged leftward by the hydraulic reaction force. Urges the first case half 42 of the inner case Ci to the left via the pump swash plate 32 and the pump swash plate anchor 33. Thus, the first
A tensile load acts on the bolt 44 connecting the case half 42 and the second case half 43.

On the other hand, in FIG. 2 and FIG. 3, the second pinion gear 14 and the second sun gear 16, both of which are helical gears,
Since the power collective shaft 17 formed integrally with the sun gear 16 is urged rightward, the urging force is transmitted from the power collective shaft 17 to the nut 61, the speed sensor gear 60, and the parking gear 5.
9 and ball bearing 21 through inner case Ci
Of the first case half 42 is urged rightward. The thrust force generated by the engagement of the large-diameter helical gear 49 and the small-diameter helical gear 50 causes the small-diameter helical gear 50
Is integrally urged rightward, and this urging force is applied to the first shaft of the inner case Ci from the pump shaft 10 via the nut 62 and the ball bearing 46.
The case half 42 is urged rightward. The right thrust force generated by the helical gear is equal to the inner case Ci.
Acts in the direction in which it is pressed toward the valve plate 27 to offset the tensile load acting on the bolt 44, so that the bolt 44 can be made small in diameter or the number of bolts 44 can be reduced.

When the hydraulic / mechanical transmission T is used as a transmission for a vehicle, even when the driving force is transmitted from the engine side to the wheel side (during acceleration),
Even when the driving force is transmitted from the wheel side to the engine side (during deceleration), the axial load generated by the hydraulic pump 24 and the hydraulic motor 25 is the same, but the axial load generated by the helical gear is Go in the opposite direction. At this time, when the driving force is transmitted from the engine side to the wheel side (during acceleration), the gear teeth of the helical gear can be offset by the axial load generated by the helical gear by the axial load generated by the hydraulic pressure. Is set.
This makes it possible to effectively cancel the load during acceleration of the vehicle in which the load increases due to a large transmission torque of the hydraulic / mechanical transmission T.

Although the embodiments of the present invention have been described in detail, various design changes can be made without departing from the gist of the present invention.

For example, the hydraulic pump 24 and the hydraulic motor 2
Either one of 5 can be configured as a fixed capacity type by fixing a corresponding swash plate. The closing member 7
Reference numeral 4 is not limited to the embodiment, and if one can prevent oil from flowing out through the through holes 32b, 38b of the swash plates 32, 38, for example, one end is fixed to the swash plates 32, 38,
A member such as a rubber boot having the other end in contact with the collar member 72 so as to be relatively rotatable may be used.

[0054]

As described above, according to the first aspect of the present invention, the cylindrical collar member is arranged with a gap around the outer periphery of the rotary shaft so as to cover the opening of the oil passage of the rotary shaft. And
Since a plurality of oil holes are formed at a plurality of positions in the circumferential direction of the collar member than the opening of the oil passage, the oil supplied from the opening of the oil passage is received by the collar member, and the oil is circumferentially formed from the plurality of oil holes. Can be distributed.
Therefore, the contact surface of the swash plate can be evenly lubricated while reducing the number of openings in the oil passage and increasing the strength of the rotating shaft. Moreover, since it is not necessary to immerse the swash plate in oil, the generation of stirring resistance can be prevented, and the loss of driving force can be reduced.

According to the second aspect of the present invention,
On the other side of the swash plate, a closing member for closing the gap between the through hole of the swash plate and the outer peripheral surface of the rotating shaft is provided, so that the oil supplied to the contact surface of the swash plate passes through the through hole of the swash plate. It is possible to prevent the oil from escaping through and to ensure a sufficient amount of oil for lubricating the contact surface.

[Brief description of the drawings]

FIG. 1 is an overall side view of a hydraulic / mechanical transmission according to the present invention.

FIG. 2 is an enlarged sectional view of a portion A in FIG.

FIG. 3 is an enlarged vertical sectional view of a portion B in FIG. 1;

FIG. 4 is a schematic diagram of a transmission system of the transmission.

FIG. 5 is an enlarged view of a part of FIG. 2;

FIG. 6 is an enlarged view of a main part of FIG. 3;

FIG. 7 is a sectional view taken along line 7-7 of FIG. 6;

8 is a sectional view taken along line 8-8 in FIG. 6;

FIG. 9 is an enlarged view of a main part of FIG. 3;

FIG. 10 is a diagram showing a relationship between a swash plate angle and an overall speed ratio of the hydrostatic continuously variable transmission in the transmission.

[Explanation of symbols]

 Reference Signs List 10 pump shaft (rotating shaft) 10a oil passage (oil passage) 17 power collecting shaft (rotating shaft) 17a oil passage (oil passage) 28 pump cylinder (cylinder) 29 cylinder hole 30 pump piston (piston) 32 pump swash plate (slanting) Plate) 32b through hole 32c contact surface 34 motor cylinder (cylinder) 35 cylinder hole 36 motor piston (piston) 38 motor swash plate (swash plate) 38b through hole 38c contact surface 72 collar member 72a through hole (oil hole) 74 closing member

Claims (2)

[Claims] A cylinder (28, 34) rotatably supported by a rotating shaft (10, 17), and a cylinder (28, 34) formed so as to surround the axis of the rotating shaft (10, 17). Multiple cylinder holes (29,3
5), a plurality of pistons (30, 36) supported in the cylinder holes (29, 35) movably in the axial direction, and a through hole (32) through which the rotating shaft (10, 17) passes through the center.
b, 38b) and a piston (3
0, 36) contact surface (32c, 38c) with which the end contacts
A swash plate (32, 38) having a swash plate (32, 38); and a rotary shaft (10, 17) passing through the inside of a rotary shaft (10, 17) to lubricate contact surfaces (32c, 38c) of the swash plate (32, 38). Oil passage (10
a, 17a), wherein a cylindrical collar member (72) is connected to the oil passage (10a, 10a, 17a).
A gap is arranged on the outer periphery of the rotating shaft (10, 17) so as to cover the opening of the oil passage (17a). An axial piston machine characterized in that a number of oil holes (72a) are also formed. 2. A gap between a through hole (32b, 38b) of the swash plate (32, 38) and an outer peripheral surface of the rotating shaft (10, 17) is closed on the other side of the swash plate (32, 38). The axial piston machine according to claim 1, characterized in that a closing member (74) is provided.