JP2566465B2 - Plunger type hydraulic unit and hydraulic type continuously variable transmission using this hydraulic unit - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic unit used as a hydraulic pump, a hydraulic motor, and the like, and a hydraulic continuously variable transmission configured using this hydraulic unit.

(Prior Art) Having a cylinder radially arranged around a main shaft and a plunger slidably inserted in the cylinder,
BACKGROUND ART A radial hydraulic unit (hydraulic pump or hydraulic motor) in which a plunger is slid in a cylinder by an eccentric cam that eccentrically rotates with respect to a main shaft has been conventionally known. To give you one example,
There is one disclosed in Japanese Patent Publication No. 45-39365. The hydraulic unit disclosed in this publication uses a ball as a plunger, and is configured to reciprocate in the radial direction in the cylinder by an eccentric cam member arranged on the outer peripheral side to perform a pump or motor action. There is.

The radial hydraulic unit is not limited to such a configuration, and a hydraulic actuator is configured by a cylinder radially arranged so as to surround the main shaft and a plunger slidably disposed in the cylinder. An eccentric cam eccentrically attached to the shaft is often used to reciprocate the plunger. In the case of a hydraulic unit configured to attach an eccentric cam to such a shaft, conventionally, the shaft is driven to rotate the eccentric cam integrally with the shaft,
It was designed to move the plunger back and forth.

(Problems to be Solved by the Invention) In order to variably control the capacity of such a hydraulic unit,
A structure that can variably control the amount of eccentricity of the eccentric cam should be adopted, but since the eccentric cam rotates together with the shaft, there is a problem that the structure for variably controlling the amount of eccentricity tends to be complicated. Although a radial type unit is taken as an example here for convenience of explanation, even in the case of an axial hydraulic unit, when the cam member (that is, the swash plate) rotates together with the shaft, the inclination of the swash plate is controlled. There is a problem that the structure for doing so tends to be complicated.

Further, such a hydraulic unit can be used as both a hydraulic pump and a hydraulic motor.
No. 45-39365) discloses a hydraulic continuously variable transmission in which a hydraulic pump and a hydraulic motor are combined and the capacities of both are variably controlled to continuously control the speed ratio. Such a hydraulic continuously variable transmission is required to be as simple and compact as possible. Further, when such a hydraulic continuously variable transmission is used in an automobile or the like, it is possible and easy to perform variable control of the pump and motor capacities, and it is possible to sufficiently respond to various traveling demands. Is desirable.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a plunger type hydraulic unit in which the variable capacity control by a cam is easy and the structure for the control is simple. It is an object of the present invention to provide a hydraulic continuously variable transmission that uses a hydraulic unit and has a simple and compact configuration and is compatible with various controls.

B. Configuration of the Invention (Means for Solving the Problems) In order to achieve such an object, a hydraulic unit according to the present invention includes a main shaft fixedly held in a housing and an axial center of the main shaft. An eccentric crank pin integrally formed with this main shaft,
An eccentric collar that is rotatably attached to the crankpin and has an outer peripheral surface that is eccentric from the crankpin axis, a rotational position adjustment mechanism that adjusts the rotational position of this eccentric collar on the crankpin, and an outer peripheral surface of the eccentric collar. A cylinder casing in which a connecting ring rotatably disposed on the upper side and a plurality of cylinder holes radially formed so as to surround the connecting ring coaxially with the main shaft and rotatably in the housing are formed. And a plurality of plungers, each of which is slidably inserted in the cylinder hole in the radial direction and has an inner diameter side end portion connected to a connecting ring, is mounted on the eccentric collar according to the rotation of the cylinder casing. The rotating coupling ring causes the plunger to reciprocate within the cylinder bore. The rotation position adjusting mechanism includes an internal gear formed concentrically with the crank pin on the side surface of the eccentric collar, and a cylindrical rotating sleeve concentrically and rotatably arranged on the main shaft. An external gear that is concentric with the main shaft and meshes with the internal gear at the end of the rotary sleeve, and a rotary position adjusting means that adjusts the rotary position of the rotary sleeve from the outside of the housing. To be done.

The rotating position adjusting means is composed of a worm gear fixed to the rotating sleeve concentrically therewith, and a worm pinion rotatably supported by the housing and meshing with the worm gear. The worm pinion is provided outside the housing. It is preferable to be configured so that it can be rotated from.

Furthermore, it operates according to the rotation of the cylinder casing,
A distribution mechanism that connects the hydraulic oil inflow port and the inside of the cylinder hole of the plunger in the expansion stroke is provided.This distribution mechanism is configured to rotate coaxially with the main shaft so that the rotation phase can be adjusted to adjust the rotational position. It is preferable that the rotational phase of the distribution mechanism is adjusted according to the rotational position adjustment of the eccentric collar on the crank pin by the mechanism.

The hydraulic continuously variable transmission according to the present invention includes a transmission housing, a pump cylinder casing and a motor cylinder casing that are integrally connected to each other and rotatably disposed in the transmission housing, and these casings. A plurality of pump plungers and a plurality of motor plungers which are respectively slidably inserted and arranged, a drive pump shaft coaxially arranged with the pump cylinder casing and rotatably arranged in the transmission housing, and eccentric to the pump shaft. A mounted pump cam member, a pump coupling ring rotatably disposed on the pump cam member, coupled to the pump plunger to reciprocate the pump plunger according to rotation of the pump shaft, and a motor cylinder. Arranged coaxially with the casing and fixed in the transmission housing Motor shaft, a motor cam member that is eccentrically attached to the motor shaft, and a motor plunger that is rotatably disposed on the motor cam member and that is connected to the motor plunger in response to the reciprocating motion of the pump plunger. A connecting ring for the motor that rotates the cylinder, and a distribution mechanism that operates according to the rotation of both cylinder casings and that supplies the hydraulic oil discharged according to the reciprocating movement of the pump plunger into the cylinder hole of the motor plunger in the expansion stroke. Composed of.

In this hydraulic continuously variable transmission, a motor shaft is integrally formed with a motor crank pin eccentric from the shaft center, and a motor cam member is rotatably attached to the motor crank pin and the motor crank pin is attached. It is preferable that the motor eccentric collar has an outer peripheral surface eccentric from the shaft center and a rotational position adjusting mechanism that adjusts the rotational position of the motor eccentric collar on the motor crankpin. It is configured so that it can be rotated coaxially with the rotation position adjustment mechanism, and the rotation phase adjustment mechanism adjusts the rotation phase of the distribution mechanism according to the rotation position adjustment of the motor eccentric collar on the motor crank pin. It is preferably configured to do so.

(Operation) When using the hydraulic unit having the above configuration,
Since the cam member is attached to the fixedly held main shaft, the mechanism for variably controlling the eccentricity amount, the tilt angle, etc. of the cam member is simple, and the variable control is also easy.

In the case of the hydraulic continuously variable transmission having the above configuration, the pump cam member causes the pump plunger to reciprocate in the cylinder hole to suck and discharge oil. By variably controlling, it becomes a variable hydraulic pump. Similarly, in the hydraulic motor, the reciprocating stroke when the motor plunger is reciprocated in the cylinder hole by the oil discharged from the hydraulic pump is variably controlled to make the variable displacement hydraulic motor. Becomes For this reason,
By making at least one of the pump and the motor variable-capacity controllable, it is possible to obtain a hydraulic continuously variable transmission capable of continuously controlling the gear ratio. In this case, since the pump cylinder casing and the motor cylinder casing are connected, it is possible to directly supply the discharge oil from the pump cylinder casing, which has a high pressure during driving, to the motor cylinder casing, and the oil passage structure for this is provided. Easy and easy.

By connecting the pump cylinder casing and the motor cylinder casing in this way, a hydromechanical transmission (HMT) is constructed. Therefore, the displacement of the hydraulic motor can be variably controlled to zero. For example, since the pump cylinder casing and the motor cylinder casing are connected to each other, the pump shaft and the motor cylinder are in the hydraulically locked state and are directly connected to each other, and the gear ratio of 1.0 is obtained. At this time, the driving force of the pump shaft is 100% mechanically transmitted through both cylinder casings.

Moreover, if the capacity of the hydraulic pump is set to zero, the discharge amount from the hydraulic pump becomes zero, so the rotation of the hydraulic motor stops,
The transmission can be placed in a neutral state.

(Examples) Hereinafter, preferred examples of the present invention will be described with reference to the drawings.

FIG. 1 shows a hydraulic continuously variable transmission CVT according to the present invention. This hydraulic continuously variable transmission CVT is composed of a radial hydraulic pump P and a radial hydraulic motor M arranged in the transmission housing 1. These hydraulic pumps P
Both the hydraulic motor M and the hydraulic motor M are capable of variably controlling their capacities. One or both of the capacities are variably controlled to continuously change the rotation of the transmission input shaft 12 to continuously output the transmission output shaft.
Propagate to 91.

The transmission housing 1 is divided into three parts, and the hydraulic pump P and the hydraulic motor M are arranged in the first space 8a surrounded by the first housing 1a and the second housing 1b, and the second housing 1b and the first housing 1b are provided. Second space 8b surrounded by 3 housings 1c
An output gear train is arranged inside.

First, the hydraulic pump P will be described with reference to FIG. 2 showing a cross section along the arrow II-II.

The hydraulic pump P has a pump casing 11, which is integrally coupled with a motor casing 51 described later and is rotatably supported by the transmission housing 1 via ball bearings 2a and 2b. This casing 11
Is configured by tightening the left and right casings 11a and 11b divided into two with a plurality of bolts 35.

The pump main shaft 12 projects outward to enable driving from the outside, and its inner end surface has a crankpin 14 having an axis C ₂ eccentric from the axis C ₁ of the main shaft 12 by a distance L _1. Is formed integrally with the main shaft 12. The tip of the crank pin 14 is a shaft support member 13
It is fitted and coupled to. The pump main shaft 12, the crank pin 14, and the shaft support member 13 are integrally supported rotatably by the pump casing 11 via ball bearings 32a and 32b, and the rotation axis thereof is the axis C ₁ . Therefore, the shaft center C ₂ of the crankpin 14 revolves around the shaft center C ₁ . In addition, a needle bearing 3 described later is provided between the main shaft 12 and the bearing 32a.
4 and a rotating sleeve 16 are provided.

The crank pin 14, the distance from the crank pin axis C ₂ L ₂
An eccentric collar 15 having an axial center C ₃ that is eccentrically mounted is rotatably attached. An internal gear 15a is formed on the right side of the eccentric collar 15, and the internal gear 15a meshes with the external gear 16a of the rotating sleeve 16.

The rotating sleeve 16 is rotatable with respect to the main shaft 12 by a needle bearing 34. However,
A sliding sleeve 17 having an internal tooth spline 17b that meshes with an external tooth spline 12a of the shaft 12 is attached to the main shaft 12 so as to be slidable in the axial direction. The spline 17a meshes with the internal spline 16b of the rotating sleeve 16. Therefore, the main shaft 12, the sliding sleeve 17, the rotating sleeve 16
And the eccentric collar 15 rotates integrally. In this case, the axis C ₃ of the eccentric collar 15 makes an orbital motion about the axis C ₁ of the main shaft 12.

As can be seen from such a configuration, the internal gear 15a of the eccentric collar 15, the rotating sleeve 16 and the sliding sleeve 17 constitute a restraint means for restraining the rotation of the eccentric collar 15, and the restraint means and the eccentric collar 15 are provided. The cam member for a pump referred to in the claims is constituted by and.

Here, the inner tooth spline 17b of the sliding sleeve 17 and the outer tooth spline 12a of the main shaft 12 are straight splines, and the outer tooth spline 17a of the sliding sleeve 17 is
The inner tooth spline 16b of the rotating sleeve 16 is a helical spline. For this reason, when the sliding sleeve 17 is slid in the axial direction, the rotating sleeve is rotated by the helical spline.
16 is rotated relative to the main shaft 12. The rotation of the rotating sleeve 16 is performed by the eccentric collar 1 via the gears 16a and 15a.
5, the eccentric collar 15 is rotated about the crank pin 14. As can be seen from this, the above-mentioned restraint means has a position adjusting function for adjusting the rotational position of the eccentric collar 15.

In this example, the internal tooth spline 17 of the sliding sleeve 17 is
b and the external tooth spline 12a of the main shaft 12 are straight splines, and the external tooth spline 17a of the sliding sleeve 17 and the internal tooth spline 16b of the rotating sleeve 16 are helical splines, but the reverse configuration is also possible, and Both may be helical splines.

The movement of the axis C ₃ in the case of the rotation of the eccentric collar 15 third
Shown in the figure. In this figure, the eccentric collar 15 is rotated 90 ° clockwise with respect to the crank pin 14.
Initially, the shaft center C ₁ of the main shaft 12, the shaft center C ₂ of the crank pin 14 and the shaft center C ₃ of the eccentric collar 15 are positioned on the same straight line. When it is rotated 90 degrees around 14, the axis of the eccentric collar 15 becomes
Move to the position indicated by C ₃ ′. Because of this, the main shaft
The distance between the axis C _{1 of} 12 and the axis C ₃ of the eccentric collar 15 (the radius of revolution of the axis C ₃ of the eccentric collar 15 with respect to the axis C ₁ of the main shaft 12) L ₃ is the distance L ₃ ′ (< L ₃ ).

It should be noted that this distance L ₃ is the maximum in the above-mentioned initial state (the state where C ₁ , C ₂ , and C ₃ are aligned on the same straight line as shown in the figure), and from this state, the rotation of the eccentric collar 15 is changed. Accordingly, the distance L ₃ gradually decreases, and becomes the minimum when the distance L ₃ rotates 180 °. In the case of this minimum, the eccentricity L ₁ axis C ₂ relative to the axis C _1, the axis C ₂
When the eccentric distance L ₂ of the axis C ₃ with respect to is equal, the distance (revolution radius) L ₃ becomes zero.

That is, the eccentric distance (revolution radius) L ₃ of the eccentric collar 15 with respect to the main shaft 12 can be changed by moving the sliding sleeve 17 in the axial direction. The movement of the sliding sleeve 17 is performed by engaging the tip end 18a with a bearing 17c attached to the end portion of the sliding sleeve 17 and rotating a lever 18 rotatable about a shaft 19.

On the other hand, a coupling ring 20 is attached to the eccentric collar 15 by a needle bearing 33 so as to be relatively rotatable. Therefore, the connecting ring 20 can rotate on the eccentric collar 15 about the axis C ₃ . Further, seven pump cylinders 25 are radially arranged around the connecting ring 20 in a radial direction. Each of these cylinders 25 is swingably attached to the pump casing 11 at a pair of trunnion portions 25b.

The cylinder holes 25a of the cylinders 25 are open to the inner diameter side, and the six pump plungers 22 and the one pump plunger 23 are arranged in each cylinder hole 25a from the inner diameter side.
Is slidably inserted. 6 pump plungers
The inner diameter side end portions 22a of the respective 22 are rotatably connected to six arm portions 20a formed on the connecting ring 20 by pins 21. The remaining one pump plunger 23 is integrally connected to the connecting ring 20 at its inner diameter side end 23a.

The internal space of the cylinder hole 25a communicates with the second circuit oil passage 4b formed in the pump casing 11 through the oil passage hole 25c formed in the left trunnion portion 25b. This second circuit oil passage 4b
Is a check valve 35 that allows only the oil flow in the inflow direction.
Connected to the first circuit oil passage 4a via a third valve via a check valve 36 that allows only the oil flow in the outflow direction.
It also connects to the circuit oil passage 4c.

The first circuit oil passage 4a is connected to the oil sump in the transmission housing via the first to fifth replenishment oil passages 3a to 3e. In addition,
The first replenishment oil passage 3a is an oil passage formed in the transmission housing 1 and communicating with the oil sump, and the second replenishment oil passage 3b is attached to the transmission housing 1 and to an oil delivery member 95 protruding into the motor shaft 52. The formed oil passage, the third
The replenishment oil passage 3c is formed in the motor shaft 52 so as to penetrate therethrough in the axial direction. The fourth oil passage 3d and the fifth oil passage 3e are connected to the oil delivery member 37 fixed to the body 81 of the distribution mechanism. The oil passage is formed and communicates as shown in the figure.

Next, the configuration of the hydraulic motor M will be described. In addition,
The main part of this motor M is similar to the hydraulic pump P, and its structure is very similar.

The casing 51 of the motor is configured by tightening two divided left and right casings 51a and 51b with a plurality of bolts (not shown), and is integrally connected to the pump casing 11.

At the left end of the motor main shaft 52, a holding member 6 fixedly coupled to the transmission housing 1 with bolts 6a.
And is splined. Therefore, the motor main shaft 52 is fixedly held. A crank pin 54 having an axis C ₅ eccentric from the axis C ₄ of the main shaft 52 by a distance L ₄ is integrally formed with the main shaft 52 on the right end surface of the shaft 52. The tip of the crank pin 54 is fitted and coupled to the shaft support member 53. The motor main shaft 52, the crank pin 54, and the shaft support member 53 integrally support the motor casing 51 via ball bearings 71a and 71b so that the motor casing 51 is rotatable, and the rotation axis thereof is the axis C ₄ . The main shaft 52 and the bearing 71a
Between the bearing 73 and the rotating sleeve described later.
56 are provided.

The crank pin 54, the distance L ₅ from the crank pin axis C ₅
An eccentric collar 55 having an eccentric shaft center C ₆ is rotatably attached. An internal gear 55a is formed on the left side of the eccentric collar 55, and the internal gear 55a meshes with the external gear 56a of the rotating sleeve 56.

The rotating sleeve 56 is mounted on the main shaft by the bearing 73.
Although it is rotatable with respect to 52, a worm gear 57 is attached to the left end of the rotating sleeve 56 by spline coupling, and this worm gear 57 meshes with a worm pinion 58 supported by the transmission housing 1. are doing. Normally, the worm pinion 58 is held stationary, so that the rotating sleeve 56 and the eccentric collar 55 are held stationary like the motor main shaft 52.

However, the worm pinion 58 can be rotated from the outside, and the rotation sleeve 56 can be rotated relative to the main shaft 52 by rotating the pinion 58. The rotation of the rotating sleeve 56 is transmitted to the eccentric collar 55 via the gears 56a and 55a, and the eccentric collar 55 is rotated about the crank pin 54.

When the eccentric collar 55 rotates, the movement of the shaft center C ₆ is
Shown in the figure. In this figure, the eccentric collar 55 is rotated 90 ° clockwise with respect to the crank pin 54.
Initially, the axis C ₄ of the main shaft 52, the axis C ₆ of axis C ₅ and the eccentric collar 55 of the crank pin 54 is located alongside on the same straight line, eccentric collar 55 from this state crankpin When it is rotated 90 ° around 54, the axis of the eccentric collar 55 becomes
Move to the position indicated by C ₆ ′. Because of this, the main shaft
L ₆ (revolution radius for the axis C ₄ of the main shaft 52 of axis C ₆ of the eccentric collar 55) the axis C ₄ and the eccentric distance between the axis C ₆ color 55a of 52, the distance L ₆ '(< L ₆ ).

Note that this distance L ₆ is the same as in the case of the hydraulic pump P.
It is the maximum in the first state above (the state where C ₄ , C ₅ and C ₆ are aligned on the same straight line as shown in the figure), and from this state the eccentric collar
It becomes the minimum when 55 turns 180 degrees. In the case of this minimum, the shaft for the eccentric distance L _4, the axis C ₅ axis C ₅ relative to the axis C ₄ C ₆
When the eccentricity distance L ₅ is equal to, the distance (revolution radius) L ₆ is zero.

On the other hand, a coupling ring 60 is attached to the eccentric collar 55 by a needle bearing 74 so as to be relatively rotatable. Therefore, the connecting ring 60 can rotate on the eccentric collar 55 around the axis C ₆ . Further, five motor cylinders 65 are radially arranged around the connecting ring 60 in the radial direction. Each of the cylinders 65 is swingably attached to the motor casing 51 at a pair of trunnion portions 65b.

The cylinder hole 65a of each cylinder 65 is opened to the inner diameter side, and four motor plungers 62 and one motor plunger 63 are arranged in each cylinder hole 65a from the inner diameter side.
Is slidably inserted. 4 motor plungers
The inner diameter side ends 62a of the respective 62 are rotatably connected to four arm portions 60a formed on the connecting ring 60 by pins 61. The remaining one motor plunger 63 has its inner diameter side end portion 63a integrally connected to the connecting ring 60.

The internal space of the cylinder hole 65a communicates with a fourth circuit oil passage 4d formed in the motor casing 51 through an oil passage hole 65c formed in the right trunnion portion 65b.

The fourth circuit oil passage 4d is selectively communicated with the above-described first circuit oil passage 4a or third circuit oil passage 4c by the distribution mechanism 80 arranged at the joint between the pump casing 11 and the motor casing 51. It is supposed to do. The distribution mechanism 80 will be described with reference to FIG. 1 and FIG. 5 showing a cross section taken along the arrow VV.

The distribution mechanism 80 includes a pump and a motor casing 1.
It has a body 81 sandwiched between 1 and 51, and in this body 81, spool insertion holes 81a extending in the radial direction corresponding to each cylinder 65 of the hydraulic motor M are formed at five locations.
A distribution spool 82 is slidably inserted into each spool insertion hole 81a, and the outer end of each spool 82 is a bearing.
The inner race 85a of 85 is held by the inner race 85a by a holding member 84 while being in contact with the inner peripheral surface of the inner race 85a.

Outer race 85b of bearing 85 is worm gear 8
The worm gear 86 is press-fitted to the inner circumference of the worm gear 6 and is rotatably supported by the transmission housing 1. However, the bearing 85 is eccentrically fitted to the worm gear 86 by press fitting, and the center of rotation of the worm gear 86 is the same as the axis C ₄ of the motor main shaft 52, but the center of rotation of the bearing 85 is the center of the main shaft 52. Center C ₇ eccentric from C ₄
Is. For this reason, when the body 81 is rotated about the axis C ₄ , the spool 82 receives the bearing 85 in the insertion hole 81a.
Performs reciprocating motion for a distance equivalent to the amount of eccentricity of the axial center C ₇ .

The worm gear 86 meshes with a worm pinion 87 rotatably supported by the transmission housing 1. The shaft end 87a of the worm pinion 87 projects to the outside of the housing 1. By rotating the shaft end 87a,
The worm gear 86 can be externally rotated about the axis C _4, and the axis C ₇ of the bearing 85 revolves around the axis C ₄ in response to this rotation.

The body 81 has a first communication hole communicating with the first circuit oil passage 4a.
5a, a second communication hole 5b communicating with the fourth circuit oil passage 4d, and a third communication hole 5b.
A third communication hole 5c that communicates with the circuit oil passage 4c is formed in communication with the spool insertion hole 81a. Further, a spool groove 82a as shown in the drawing is formed in the spool 82, and according to the reciprocating motion of the spool 82 in the spool insertion hole 81a,
The spool groove 82a allows the first communication hole 5a and the second communication hole 5b to communicate with each other, and the second communication hole 5b and the third communication hole 5c to communicate with each other. Specifically, the distribution spool
When 82 is moved outward, the second communication hole 5b and the third communication hole 5c
When the distribution spool 82 is moved inward, the first communication hole 5a and the second communication hole 5b are communicated with each other.

The operation of the hydraulic continuously variable transmission CVT configured as above will be described.

The transmission CVT is driven by rotating the pump main shaft (transmission input shaft) 12. When the pump main shaft 12 is driven to rotate, this shaft
The eccentric collar 15 rotates integrally with 12, and the connecting ring 20 rotatably attached to the eccentric collar 15 revolves around the axis C ₃ of the eccentric collar 15 centered on the axis C ₁ of the pump main shaft 12. Perform the same orbital movement as the exercise. Therefore, the pump plungers 22 and 23 connected to the connecting ring 20 reciprocate in the cylinder hole 25a of the pump cylinder 25.

Here, the pump plunger 23 is integrally connected to the connecting ring 20, but this is the same as the other plunger 22.
When it is rotatably connected by 21, the connecting ring 20 freely rotates relative to the pump casing 11 as shown in FIG. Therefore, the coupling ring 20 also rotates in the A direction in response to the rotation of the main shaft 12 in the A direction, and the outer surface of the cylinder 25 comes into contact with the flange 35d for the bolt 35 of the casing 11b as shown in the drawing. Plunger 22 if flange 11d is far enough
However, there is a problem in that the piston 22 comes out of the cylinder 25, which does not allow the plunger 22 to reliably move back and forth. For this reason, in this example, one plunger 23 is integrally coupled to the coupling ring 20 to prevent relative rotation displacement of the coupling ring 20 with respect to the casing 11 beyond a predetermined value. As a result, the pump plungers 22 and 23 smoothly reciprocate within the cylinder hole 25a of the pump cylinder 25 as the connecting ring 20 revolves.

When the plungers 22 and 23 reciprocate in this way,
By the action of the check valves 35 and 36, oil is sucked into the cylinder chamber where the plungers 22 and 23 are in the expansion stroke from the first circuit oil passage 4a through the second circuit oil passage 4b, and from the cylinder chamber in the contraction stroke. Oil is discharged to the third circuit oil passage 4c through the second circuit oil passage 4b. In this case, each plunger
22 and 23 are connected to connection ring 20, so connection ring 2
It is possible to transmit forces and movements from 0 to the plungers 22 and 23 in both directions of pushing and pulling the plungers 22 and 23. Therefore, it is possible to cause the oil to be sucked into the cylinder chamber in the expansion stroke without a problem even if the charge pump does not pressurize the suction side.

The oil discharged to the third circuit oil passage 4c is supplied by the distribution mechanism 80 to the motor cylinder hole 65a on the expansion stroke side through the third communication hole 5c and the second communication hole 5b, and the cylinder hole 65a. The inner motor plunger 62 or 63 is moved in the expansion direction. In response to the movement of the motor plungers 62, 63 in the expansion direction, the connecting ring 60 connected to the motor plungers 62, 63 rotates on the eccentric collar 55, and the motor cylinder casing 51 is rotationally driven. This rotation is caused by the drive gear 51 formed at the end of the cylinder casing 51.
It is transmitted to the transmission output shaft 91 via c and the driven gear 91a meshing with this.

The motor plungers 62, 63 on the contracting side are contracted as the motor cylinder casing 51 rotates, and the oil in the cylinder hole 65a into which the plungers 62, 63 are inserted is distributed by the distribution mechanism 80 to the second communication hole 5b. Then, it is discharged to the first circuit oil passage 4a through the first communication hole 5a, returned to the suction side of the pump P, and circulated again.

When the pump main shaft 12 is driven in this way, the oil discharged from the hydraulic pump P is supplied to the hydraulic motor M, which drives the hydraulic motor M. The oil that has driven the hydraulic motor M is discharged to the first circuit oil passage 4a and is again sucked into the hydraulic pump P.
〜Supplemented by inhaling from the fifth replenishment oil passages 3a to 3e.

In the above drive, the amount of oil discharged from the hydraulic pump P corresponds to the relative rotational speed between the pump main shaft 12 and the pump casing 11. The pump casing 11 is rotatably supported and is integrally connected to the motor cylinder casing 51. Therefore, if the displacement is constant, the amount of oil discharged from the hydraulic pump P is proportional to the rotational speed difference between the pump main shaft 12 and the motor cylinder casing 51.

Here, the capacity of the hydraulic pump P (the amount of discharged oil per one rotation) is proportional to the reciprocating stroke of the pump plungers 22 and 23. This reciprocating stroke can be variably controlled by rotating the lever 18 and adjusting the eccentric distance L ₃ of the eccentric collar 15. In this case, as shown in FIG. 3, the shaft center C ₁ of the main shaft 12, the shaft center C ₂ of the crank pin 14, and the shaft center C ₃ of the eccentric collar 15 were positioned on the same straight line as shown in the drawing. In the state, the eccentric distance L ₃ is the maximum, and from this state, the distance L ₃ gradually decreases in accordance with the rotation of the eccentric collar 15, and this is 180
Since it becomes the minimum when it is turned, the pump capacity can be variably controlled continuously from the maximum to the minimum by controlling the rotation of the lever 18.

Incidentally, the eccentricity L ₁ axis C ₂ relative to the axis C _1, when the eccentricity L ₂ axes C ₃ relative to the axis C ₂ are equal, the minimum distance value (radius of revolution) L ₃ becomes zero, The minimum value of the pump capacity is zero. That is, even if the pump main shaft 12 rotates, the amount of oil discharged from the pump becomes zero, whereby a neutral state of the transmission can be obtained.

Similarly, the hydraulic motor M has a capacity of 58
It is possible to variably control from the maximum capacity to the minimum capacity according to the rotation of the. In this case, the shaft center C ₄ of the main shaft 52
For an eccentric distance L ₄ of axis C ₅ of the crank pin 54, when the eccentricity L ₅ of the axis C ₆ of the eccentric collar 55 with respect to the axis C ₅ of the crank pins 54 are equal, the capacity of the hydraulic motor M The minimum value of is zero.

Therefore, the rotation amount of the lever 18 and the worm pinion
By appropriately controlling the rotation amount of 58, the ratio of the output rotation (the rotation of the transmission output shaft 91) to the input rotation (the rotation of the pump main shaft 12) (= input rotation / output rotation), that is, The gear ratio can theoretically be controlled infinitely from infinity to 1.0. In this case, the gear ratio becomes infinite when the hydraulic motor M has a predetermined displacement and the displacement of the hydraulic pump P is very close to zero. Further, the hydraulic pump P has a predetermined displacement, the displacement of the hydraulic motor M is zero, and the gear ratio is 1.0 (the pump shaft and the motor casing are directly connected).

In the distribution mechanism 80, the cylinder hole on the expansion stroke side
In order to supply the oil from the hydraulic pump P into the cylinder 65a and to return the oil in the cylinder hole 65a on the contraction stroke side to the suction side of the hydraulic pump P, the ball bearing 85 mounted eccentrically in the farthest point direction (the sixth position). The arrow R direction in the figure, which is the direction in which the spool 82 is pushed out to the outermost side, is the farthest point direction of the eccentric collar 55 (the direction indicated by the arrow P, which is the direction in which the motor plunger 62 is positioned at the top dead center). It becomes a right angle position.

In this case, when the worm pinion 58 is rotated to rotate the eccentric collar 55 around the crank pin 54 in order to change the discharge amount of the hydraulic motor M, the farthest point direction of the eccentric collar 55 also changes. For example, as described in FIG. 4, when the eccentric collar 55 to about 90 ° rotation of the crank pin 54, the center of the eccentric collar 55 is moved from C ₆ to C ₆ ', the farthest point the direction arrow P Move 45 ° from direction Q. Therefore, in this case, in the distribution mechanism 80, the ball bearing 85 eccentrically mounted is mounted in the farthest point direction (spool).
It is also necessary to move 45 ° in the direction of pushing 82 to the outermost side, and this movement is performed by the rotation of the worm pinion 87.

In addition, a ball bearing with a warm pinion 87
The direction of the farthest point of 85 is opposite to the above, that is, 180
In the case of the method of rotating by a degree, the motor M rotates in the opposite direction. That is, the reverse setting of this transmission CVT can be performed by the worm pinion 87.

In the above, the example in which the hydraulic continuously variable transmission CVT is constituted by the hydraulic pump P and the hydraulic motor M has been shown. Next, a radial plunger hydraulic unit HU which is constituted as a single unit and is used as a hydraulic pump or a hydraulic motor. This will be described with reference to FIG.

This hydraulic unit HU is a housing 101 with a three-part configuration.
(101a, 101b, 101c), in the housing 101,
The hydraulic motor M is configured by incorporating parts having a similar configuration.

A casing 151 including left and right casings 151a and 151b that are bolted together is rotatably supported by the housing 101 via a pair of ball bearings 102a and 102b. The main shaft 152 extends in the axial direction at the center of the casing 151, and is arranged so as to be rotatable relative to the casing by bearings 103a and 103b. The main shaft 152 is a holding member fixed to the housing 101.
106 is splined and fixedly held.

A crankpin 154 having an axis C ₅ eccentric from the axis C ₄ of the main shaft 152 by a distance L ₄ is integrally formed with the main shaft 152 on the right end surface of the shaft 152.
The tip of the crank pin 154 is fitted and coupled to the shaft support member 153. These main shaft 152, crank pin
154 and the shaft support member 153 are integrally fixed and held.

The crankpin 154 has a distance L from the crankpin axis C ₅
An eccentric collar 155 having an axis C ₆ eccentric by ₅ is rotatably attached. The internal gear formed on the left side of the eccentric collar 155 meshes with the external gear of the rotating sleeve 156.

The rotating sleeve 156 is rotatable with respect to the main shaft 152, but the worm gear 1 is provided at the left end of the rotating sleeve 156.
57 is attached and the worm gear 157 meshes with the worm pinion 158. By rotating the pinion 158, the rotating sleeve 156 can be rotated relative to the main shaft 152. The rotation of the rotating sleeve 156 is transmitted to the eccentric collar 155, and the eccentric collar 155 is rotated about the crank pinion 154.

The movement of the shaft center C _{6 in} the case of the rotation of the eccentric collar 155 is the same as in the case of the hydraulic motor shown in FIG.

On the other hand, a connecting ring 160 is attached to the eccentric collar 155 by a needle bearing 174 so as to be relatively rotatable.
Therefore, the connecting ring 160 has an eccentric collar 1 centered on the axis C _6.
It is possible to rotate on 55. Furthermore, this connecting ring
Five cylinders 165 are radially arranged around 160. Each of these cylinders 165 is swingably attached to the motor casing 151 at a pair of trunnion portions 165b. The cylinder hole of each cylinder 165 is opened to the inner diameter side, and four plungers 162 and one plunger 1 are arranged in each cylinder hole from the inner diameter side.
63 is slidably inserted. The structure of these parts is the same as the parts of the hydraulic motor M described above, and therefore the description thereof is omitted.

The internal space of the cylinder hole communicates with the second oil passage 104b formed in the casing 151 through the oil passage hole 165c formed in the left trunnion portion 165b. The first circuit oil passage 104a is connected to the distribution mechanism 180 that is connected to the casing 151.

The distribution mechanism 180 includes a body 181 integrally connected to a casing 151, and a distribution spool inserted in a spool insertion hole formed in the body 181 corresponding to each cylinder 65.
182, a worm gear 186 rotatably supported by the housing 101, a worm pinion 187 that meshes with the worm gear 186, and a ball bearing 185 that connects the outer end of the distribution spool 182 and the worm pinion,
Its structure is the same as that of the distribution mechanism 80 described above.

The body 181 has a second communication hole 105b communicating with the second oil passage 104b and a first communication hole 105a communicating with the first oil passage 104a.
And a first communication hole 105c communicating with the third oil passage 104c are formed so as to communicate with the spool insertion hole, respectively. When the body 181 is rotated together with the casing 151, the spool 182 is reciprocated in the insertion hole as in the case of the hydraulic motor M described above, and by the action of the groove formed in the spool,
The first communication hole 105a and the second communication hole 105b communicate with each other, or
The communication hole 105b and the third communication hole 105c may communicate with each other. The first oil passage 104a communicates with the discharge port 111, and the third oil passage 1
04c communicates with the suction port 110.

Further, the casing 151 is connected to the shaft 191 via a gear formed at the left end, and the rotation of the casing 151 is the shaft 191.
To be transmitted to.

The hydraulic unit HU having the above configuration can be used as both a hydraulic motor and a hydraulic pump.

When used as a hydraulic motor, pressure oil is supplied from the suction port 110 into the third oil passage 104c. This pressure oil is sent into the cylinder hole of the cylinder 165 on the expansion stroke side by the action of the distribution mechanism 80, and the plunger 16 in this cylinder hole is
Move 2 or 163 in the direction of expansion. Plunger 162,
Depending on the movement of 163 in the direction of inflation, these plungers 16
The connecting ring 160 to which the 2,163 are connected rotates on the eccentric collar 155, and the casing 151 is rotationally driven. This rotation is transmitted to the shaft 191 via a drive gear formed at the end of the casing 151 and a driven gear that meshes with the drive gear, and the shaft 191 is driven to rotate.

It should be noted that the motor plungers 162, 163 on the contraction side contract as the casing 151 rotates, and the plunger 16
The oil in the cylinder hole into which 2,163 is inserted is discharged to the discharge port 111 by the distribution mechanism 180 through the second communication hole 105b and the first oil passage 104a.

On the other hand, when using this hydraulic unit HU as a hydraulic pump, it is sufficient to drive the shaft 191 to rotate, and
The oil sucked from the suction port 110 is discharged from the discharge port 111.

The positional relationship between the suction port and the discharge port may be reversed.

In any case, the capacity of the worm pinion 158 can be variably controlled by rotating the worm pinion 158, but the operation thereof is the same as that of the hydraulic motor M described above, and the description thereof will be omitted.

C. As described above, in the hydraulic unit according to the present invention, the main shaft is fixedly held, the cam member is attached to this shaft, and the cylinder casing is rotatably arranged around the main shaft. The mechanism for variably controlling the eccentricity amount, the inclination angle, etc. of the cam member is simple, and the control is easy.

Further, in the hydraulic continuously variable transmission according to the present invention, the pump cam member reciprocates the pump plunger in the cylinder hole to suck and discharge oil, and the stroke of the reciprocating motion at this time is variably controlled. By doing so, it becomes a variable hydraulic pump, and similarly, in the hydraulic motor, it becomes a variable displacement hydraulic motor by variably controlling the reciprocating stroke when the motor plunger reciprocates in the cylinder hole by the oil discharged from the hydraulic pump. . Therefore, by providing at least one of the pump and the motor with variable displacement control, it is possible to obtain a hydraulic continuously variable transmission that can continuously control the speed ratio. In this case, since the pump cylinder casing and the motor cylinder casing are connected, it is possible to directly supply the discharge oil from the pump cylinder casing, which has a high pressure during driving, to the motor cylinder casing, and the oil passage structure for this is provided. Easy and easy.

[Brief description of drawings]

FIG. 1 is a sectional view showing a hydraulic continuously variable transmission according to the present invention, and FIG. 2 is an arrow II of a hydraulic pump constituting the continuously variable transmission.
-II is a sectional view taken along line II, Fig. 3 is a schematic view showing the positional relationship of the shaft centers of the respective members of the hydraulic pump, and Fig. 4 is the position of the shaft centers of the respective members of the hydraulic motor constituting the continuously variable transmission. FIG. 5 is a schematic view showing the relationship, FIG. 5 is a cross-sectional view of the distribution mechanism of the continuously variable transmission along arrow VI-VI, FIG. 6 is a cross-sectional view showing a part of the hydraulic pump taken out, and FIG. It is sectional drawing which shows the example of the hydraulic unit which concerns on this invention. 1 …… Transmission housing, 11 …… Pump casing 12 …… Pump main shaft 14 …… Crank pin, 15 …… Eccentric collar 51 …… Motor main shaft 54 …… Crank pin, 55 …… Eccentric collar 60 …… Guide Ring, 62 …… Motor plunger 65 …… Motor cylinder, 82 …… Distribution spool CVT …… Hydraulic continuously variable transmission P …… Hydraulic pump, M …… Hydraulic motor

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A 61-52453 (JP, A) JP-A 62-4963 (JP, A) JP-A 48-45730 (JP, A) JP-B 41- 16626 (JP, B1) Japanese Patent Publication Sho 36-7975 (JP, B1) US Patent 2159005 (US, A)

Claims (4)

(57) [Claims] 1. A housing, a main shaft fixedly held in the housing, a crank pin formed integrally with the main shaft so as to be eccentric from an axis of the main shaft, and rotated by the crank pin. An eccentric collar that is freely attached and has an outer peripheral surface that is eccentric from the axis of the crankpin, a rotational position adjusting mechanism that adjusts the rotational position of the eccentric collar on the crankpin, and an outer peripheral surface of the eccentric collar. A coupling ring rotatably disposed in the housing, a plurality of cylinder holes coaxially with the main shaft and rotatably disposed in the housing, and radially extending to surround the coupling ring. And a cylinder casing that is slidably inserted in the cylinder hole in the radial direction. A plurality of plungers whose inner diameter side ends are connected to the coupling ring, and the plunger reciprocates in the cylinder hole by the coupling ring that rotates on the eccentric collar according to the rotation of the cylinder casing. The rotational position adjusting mechanism is arranged on the side surface of the eccentric collar so as to be concentric with the crank pin and on the main shaft so as to be concentrically and rotatably therewith. A cylindrical rotating sleeve provided, an external gear that is concentric with the main shaft at the end of the rotating sleeve and meshes with the internal gear, and the rotational position of the rotating sleeve is the housing. 2. A plunger type hydraulic unit comprising: a rotating position adjusting means for adjusting the rotating position from the outside. 2. The rotating position adjusting means comprises a worm gear concentrically fixed to the rotating sleeve, and a worm pinion rotatably supported by the housing and meshing with the worm gear. The plunger type hydraulic unit according to claim 1, wherein the worm pinion is rotatable from the outside of the housing. 3. A distribution mechanism, which operates in response to rotation of the cylinder casing and connects the hydraulic oil inflow port and the inside of the cylinder hole of the plunger in the expansion stroke, the distribution mechanism being coaxial with the main shaft. It is possible to adjust the rotation phase by rotating the distribution mechanism according to the rotation position adjustment of the eccentric collar on the crank pin by the rotation position adjustment mechanism. The plunger type hydraulic unit according to claim 1, wherein the hydraulic unit is a plunger type hydraulic unit. 4. A transmission housing, a pump cylinder casing and a motor cylinder casing which are integrally connected to each other and are rotatably arranged in the transmission housing, and slidably inserted into these casings respectively. A plurality of pump plungers and a plurality of motor plungers, a drive pump shaft coaxially arranged with the pump cylinder casing and rotatably arranged in the transmission housing, and a pump eccentrically attached to the pump shaft. Cam member, a pump connecting ring that is rotatably disposed on the pump cam member, is connected to the pump plunger, and reciprocates the pump plunger according to rotation of the pump shaft; The transmission housing is coaxial with the motor cylinder casing. A motor shaft fixedly arranged in the ring, a motor cam member eccentrically attached to the motor shaft, a motor cam member rotatably arranged on the motor cam member, and the motor plunger connected to the motor cam member. And a connecting ring for a motor that rotates the motor cylinder casing in response to the reciprocating movement of the pump plunger, and a hydraulic oil that operates according to the rotation of both the cylinder casings and is discharged according to the reciprocating movement of the pump plunger. And a distribution mechanism for supplying into the cylinder hole of the motor plunger in the expansion stroke, the motor shaft integrally has a motor crank pin eccentric from its axial center, the motor cam member, It is rotatably attached to this motor crank pin and A motor eccentric collar having an eccentric outer peripheral surface, and a rotational position adjusting mechanism for adjusting the rotational position of the motor eccentric collar on the motor crank pin, and the distribution mechanism rotates coaxially with the motor shaft. The rotational phase can be adjusted by adjusting the rotational phase of the distribution mechanism in accordance with the rotational position adjustment of the motor eccentric collar on the motor crankpin by the rotational position adjusting mechanism. A hydraulic continuously variable transmission characterized by.