JPS63140166A - Swash plate type hydraulic device - Google Patents

Abstract

PURPOSE:To stabilize the property of the device in the caption as well as to obtain good assembling performance by providing a cylinder holder for rotatably supporting a cylinder block in connection to a swash-plate anchor, and attaching an eccentric to the cylinder holder. CONSTITUTION:A swash-plate anchor 23 rotatably supporting the cylindrical surface of a trunnion shaft 22 is fixed to a crank case 4 together with a cylindrical cylinder-holder 24 by means of a bolt 26. The cylinder holder 24 rotatably supports the outer periphery of a motor cylinder 17 through a needle bearing 25, and an eccentric 64 is attached to the cylinder holder 24. Therefore, not only the mutual phase of eccentric direction lines of the swash-plate type trunnion shaft 22 and the eccentric 64 but also eccentric quantity of the eccentric 64 with respect to a cylinder block can be correctly set as desired, thereby stabilizing the property of the device in the caption. In addition, this hydraulic device can be assembled before its incorporation in a casing so as to exhibit good assembling performance.

Description

Detailed Description of the Invention A8 Object of the Invention (1) Industrial Application Field The present invention relates to a swash plate type hydraulic device used as a swash plate type hydraulic pump or a hydraulic motor, and in particular, to a swash plate type hydraulic device used as a swash plate type hydraulic pump or a hydraulic motor. A cylinder block having annular high-pressure oil passages and low-pressure oil passages, a group of plungers that slide into the cylinder holes, and a plunger that engages with the protruding ends of this group of plungers, and as the cylinder block rotates, each plunger A swash plate that provides reciprocating motion, and a swash plate that is arranged radially on the cylinder block and that reciprocates between a radially outer position and an inner position of the cylinder block to alternately use each cylinder hole as a high-pressure oil passage and a low-pressure oil passage. A swash plate type hydraulic system that includes a group of distribution valves that communicate with each other, and an eccentric wheel that circumscribes the group of distribution valves and is arranged eccentrically with respect to the center of rotation of the cylinder block, giving reciprocating motion to each distribution valve as the cylinder block rotates. Concerning improvements to equipment.

(2) Prior Art This swash plate type hydraulic system has already been proposed by the present applicant and is publicly known from Japanese Patent Laid-Open No. 153057/1983.

(3) Problems to be Solved by the Invention In such a swash plate type hydraulic device, the phase relationship between the trunnion axis of the swash plate and the eccentric direction line of the eccentric wheel in the rotational direction of the cylinder block has a large effect on the characteristics of the device. However, in conventional systems, the swash plate is supported by a swash plate anchor supported by a stationary casing, and the eccentric wheel is supported by a casing, which are different support systems. It is difficult to set the mutual phase of the trunnion axis of the plate and the eccentric direction line of the eccentric wheel as desired.

The present invention has been made in view of the above circumstances, and allows the mutual phase of the trunnion axis of the swash plate and the eccentric direction line of the eccentric wheel to be set accurately as desired, and also enables assembly before being incorporated into the casing. It is an object of the present invention to provide the swash plate type hydraulic device which is easy to assemble.

B0 Structure of the Invention (1) Means for Solving Problems In order to achieve the above object, a cylinder holder that rotatably supports a cylinder block is attached to a swash plate anchor that supports a swash plate and is fixed to a casing. The cylinder holder is connected in series with an eccentric wheel attached to the cylinder holder, which is referred to as vf@.

(2) Function The swash plate anchor and cylinder holder are the same support system that is connected to each other, and the swash plate is supported by the swash plate anchor, and the eccentric ring is attached to the cylinder holder, so processing errors and assembly errors may occur. Therefore, there is very little phase shift between the trunnion axis of the swash plate and the eccentric direction line of the eccentric wheel.

Further, since the cylinder block is rotatably supported by the cylinder holder that supports the eccentric wheel, the amount of eccentricity of the eccentric wheel with respect to the cylinder block can also be accurately set.

Moreover, since the swash plate, cylinder block, and eccentric wheel are supported by the support system separate from the casing, the hydraulic system assembly can be constructed before being assembled into the stationary casing.

(3) Examples Examples of the present invention will be described below with reference to the drawings. First, in Figures 1 and 2, the motorcycle engine E
The power is transmitted from the crankshaft 1 to the chain 2 primary reduction gear 2, the hydrostatic continuously variable transmission T, and the chain type secondary reduction gear 3.
are sequentially transmitted to the rear wheels (not shown).

The continuously variable transmission T includes a constant displacement swash plate hydraulic pump P and a variable displacement swash plate hydraulic motor M according to the present invention, and is housed in a crankcase 4 that supports the crankshaft 1 as a casing.

The hydraulic pump P is connected to the output sprocket 2 of the primary reduction gear 2.
a is removably connected to the input cylinder shaft 5 through a plurality of connecting pins 16 (only one is shown in the figure), and to the inner peripheral wall of the intermediate portion of the input cylinder shaft 5 through a needle bearing 6 so as to be relatively rotatable. The pump cylinder 7 to be fitted, and the cylinder holes 8, 8, .
A large number of pump plungers 9, 9... are combined together, a pump swash plate 1O contacts the outer ends of these pump plungers 9, 9..., and this pump swash plate 1O is connected to the pump cylinder 7.
A pump swash plate holder that supports the back surface of the swash plate 10 via a thrust roller bearing 11 to maintain the swash plate 10 in a state tilted at a constant angle with respect to the axis of the pump cylinder 7 about a virtual trunnion axis &101 that is orthogonal to the axis of the pump cylinder 7. It consists of 12. The pump swash plate holder 12 is removably spline-fitted to the inner circumferential wall of the outer end of the input cylinder shaft 5 and is temporarily fixed by a circlip 14 .

Thus, when the input cylinder shaft 5 rotates, the pump swash plate lO can give reciprocating motion to the pump plungers 9, 9, . . . to repeat the suction and discharge strokes.

In order to improve the followability of the pump plunger 9 with respect to the pump swash plate 10, a coil spring 15 that biases the pump plunger 9 in the expansion direction is compressed in the cylinder hole 8.

On the other hand, the hydraulic motor M includes a motor cylinder 17 disposed coaxially with the pump cylinder 7 and to the left thereof, and a large number of odd number of cylinder holes arranged in an annular manner surrounding the rotation center of the motor cylinder 17. A large number of motor plungers 19.19 each slidably connected to 18.18...
..., a motor swash plate 20 that comes into contact with the outer ends of these motor plungers 19, 19, and this motor swash plate 20.
The trunnion shaft 22 has a half-moon cross section and supports the flat back surface of the trunnion shaft 22 via a thrust roller bearing 21, and a swash plate anchor 23 rotatably supports the cylindrical surface of the trunnion shaft 22. The swash plate anchor 23 is fixed to the crankcase 4 with bolts 26 together with a cylindrical cylinder holder 24 continuous to its right end. Cylinder holder 24
is connected to the motor cylinder 17 via the needle bearing 25.
Rotatably supports the outer periphery of the

Incidentally, the swash plate anchor 23 and the cylinder holder 24 are attached to the bolt 2.
7 and are bound to each other in advance.

In order to allow rotation of the trunnion shaft 22 by a predetermined angle while preventing its axial movement, a bolt 29 is inserted through an arcuate elongated hole 28 centered on the axis o2 of the trunnion shaft 22, which is drilled in the swash plate anchor 23. is fixed to one end surface of the trunnion shaft 22 (see FIGS. 2 and 18).

The motor swash plate 20 is actuated by the rotation of the trunnion shaft 22 between an upright position perpendicular to the axis of the motor cylinder 17 and a maximum tilt position tilted at an angle. Now, motor cylinder 1
With the rotation of 7, the motor plungers 19, 19... can be given reciprocating motion to repeat the expansion and contraction strokes.

In order to improve the ability of the motor plunger 19 to follow the motor swash plate 20, a coil spring 30 that biases the motor plunger 19 in the direction of extension is compressed in the cylinder hole 18.

The pump cylinder 7 and the motor cylinder 17 constitute a negative-shaped cylinder block B, and the output shaft 31 is passed through the center of the cylinder block B.

Then, the outer end of the motor cylinder 17 is brought into contact with a flange 31a integrally formed on the outer periphery of the output shaft 31, and the pump cylinder 7 is spline-fitted 32 to the output shaft 31.
The cylinder block B is fixed to the output shaft 31 by locking the circlip 34, which contacts the outer end of the pump cylinder 7 via the seat plate 33, to the output shaft 31.

The right end of the output shaft 31 extends through the pump swash plate 10, the pump swash plate holder 12, and the right side wall of the crankcase 4, and is fixed to the outer periphery of this right end with a knock pin 35 and a split cock 36. Between the support tube 37 and the pump swash plate holder 12, a drive gear 39 and a thrust roller bearing 40 for a replenishment pump 38, which will be described later, are successively interposed from the holder 12 side. The right end portion of the output shaft 31 is rotatably supported by the crankcase 4 via the support cylinder 37 and ball bearing 41.

The drive gear 39 is spline-fitted to the input cylinder shaft 5 similarly to the pump swash plate holder 12, and is rotatably supported by the output shaft 31 via a needle bearing 42.

The left end of the output shaft 31 extends through the motor swash plate 20, the trunnion shaft 22, the swash plate anchor 23, and the left side wall of the crankcase 4, and is spline-coupled 43 to the outer periphery of this left end. A retainer 46 and a thrust roller bearing 47 are interposed in order from the swash plate anchor 23 side between the support cylinder 45 fixed by the split stopper 44 and the swash plate anchor 23. The left end portion of the output shaft 31 is rotatably supported by the swash plate anchor 23 via a needle bearing 48 and the retainer 46.

Furthermore, a bolt 49 is attached to the left end of the output shaft 31, and the input gear block 3a of the secondary reduction gear 3 is attached to the outside of the crankcase 4.
It is fixed in place.

In this way, from sprocket 2a to sprocket 3
Since all the constituent members of the transmission T up to a are assembled as one assembly on the output shaft 31, the transmission T can be attached to and removed from the crankcase 4 extremely easily.

The output shaft 31 includes a hemispherical centering body 50 that engages with the inner peripheral surface of the pump swash plate 10 so as to be tiltable in all directions relative to the inner peripheral surface of the motor swash plate 20 , and a centering body 50 that is tiltable in all directions relative to the inner peripheral surface of the motor swash plate 20 . A hemispherical centering body 51 that can be engaged is fitted, and these provide an aligning effect to the pump swash plate IO and the motor swash plate 20.

The alignment action of each swash plate 10, 20 is strengthened, and the rotation direction between the pump swash plate 10 and the pump plungers 9, 9, . To prevent slippage, each swash plate 10.20 has a spherical end 9a, 19a of the corresponding plunger 9, 19.
Spherical recesses toa and 20a are respectively formed to engage the two.

A hydraulic closed circuit is formed between the hydraulic pump P and the hydraulic motor M as follows.

The cylinder block B includes cylinder holes 8, 8... of the pump cylinder 7 and cylinder holes 1 of the motor cylinder 17.
8.18...An annular inner oil passage 52 and an outer oil passage 53 arranged concentrically around the output shaft 31 between the groups
and the same number of first valve holes 54 as the cylinder holes 8, 8, . . . and 18, 18, . ,5
4... and the first valve holes 54, 55..., and a large number of pump ports a that interconnect the adjacent cylinder holes 8, 8... and the first valve holes 54, 54... a..., adjacent cylinder holes 18゜l8... and second valve holes 55, 55
A large number of motor boats b, b... which communicate with each other.
・And is provided.

Note that the inner and outer oil passages 52 and 53 correspond to the low pressure and high pressure oil passages of the present invention.

The inner oil passage 52 is connected to the cylinder block B and the output shaft 3.
1 is formed as an annular groove on each circumferential surface facing each other.

As shown in FIGS. 4 and 5, the outer oil passages 53 are arranged in an annular dovetail groove 58 cut on the outer periphery of the cylinder block B and in a staggered arrangement on both side walls of the dovetail groove 58. The sleeve 60 is made up of a plurality of semicircular recesses 59, 59, . Closed by The outer oil passage 53 having such a configuration is advantageous in minimizing the high pressure volume.

The first and second valve holes 54, 55 are arranged so as to pass through the bottom walls of the staggered recesses 59, 59, and correspond to the cylinder holes 8, 8 of the hydraulic pump P.・・・
. . and the cylinder hole 18° 18 of the hydraulic pump P are out of phase in the circumferential direction.

In this way, while increasing the wall thickness of the cylinder block B between the first and second valve holes 54.55, both valve holes 54.55
The interval along the axial direction of the cylinder block B can be narrowed, which can contribute to making the cylinder block B more compact.

Furthermore, even if the both side walls of the dovetail groove 58 undergo expansion deformation when high oil pressure is introduced into the outer oil passage 53, the surface pressure at the fitting portion of the cylinder block B and the sleeve 60 increases due to the deformation. Therefore, oil leakage from the fitting portion can be prevented.

The first valve holes 54, 54... are provided with spool-type first distribution valves 61, 61..., and the second valve holes 55, 55...
... also has a spool-type second distribution valve 62°62.
... are rubbed together. and the first distribution valve 61.6
A first eccentric ring 63 surrounding the second distribution valves 62, 62, . the first to force their engagement.
The outer ends of the distribution valves 61, 61... are mutually connected to the first eccentric wheel 63.
The first force ring 67 is concentric with the second distribution valve 6.
The outer end portions of 2, 62, . Their connection structure will be described later.

The first eccentric wheel 63 is removably fixed to the outer periphery of the input cylinder shaft 5 by a head pin 70 and a clip 71, and as shown in FIG. It is held at a position offset by a distance t1. The eccentric direction line Xl corresponds to the virtual trunnion axis 0.0 of the pump swash plate 10.
The pump cylinder 7 is set at a position retarded by a certain angle θ1 in the relative rotational direction R of the pump cylinder 7 with respect to the input cylinder shaft 5. The angle θ1 can be easily adjusted by changing the spline fitting position between the manual cylinder shaft 5 and the pump swash plate holder 12.

Therefore, when relative rotation occurs between the input cylinder shaft 5 and the pump cylinder 7, each first distribution valve 61 is stroked a distance twice the eccentricity ε1 in the first valve hole 54 by the first eccentric wheel 63. The pump cylinder 7 is reciprocated between a radially inner position and an outer position.

In FIG. 6, the discharge area of the hydraulic pump P is shown as D, and the suction area is shown as S. In the discharge area, the first distribution valve 61 is moving from a position Nl perpendicular to the eccentric direction line 53 and disconnected from the inner oil passage 52, the pump plunger 9 during the discharge stroke.
As a result, hydraulic oil is force-fed from the cylinder hole 8 to the outer oil passage 53.

In the suction region S, the first distribution valve 61 is at an eccentric neutral position N,
The corresponding pump boat a is communicated with the inner oil passage 52 and disconnected from the outer oil passage 53, and the pump plunger 9 is moved from the inner oil passage 52 to the cylinder hole 8 during the suction stroke. Hydraulic oil is sucked in.

Further, at the eccentric neutral position N1, the first distribution valve 61 disconnects the corresponding pump boat a from both oil passages 52 and 53. In this case, as shown in FIG. 6A, the land portion 61a of the first distribution valve 61 that closes the pump boat a has an outer oil passage 53.
Predetermined valve closing allowance only on the side 2. is provided.

In this way, the discharge area of the hydraulic pump P is arranged so that the eccentric direction line X is aligned with the virtual trunnion axis 0. The angle is retarded by an angle θ1 compared to the case where the angle θ1 matches the angle θ1, and the suction area S is set to a wider angle than the discharge area.

As shown in FIG. 1, FIG. 2, and FIG. are connected so that they can swing.

The support ring 75 is detachably fixed to the outer periphery of the cylinder holder 24 via a plurality of headed pins 77 and clips 78.

The eccentric direction line X2 of the second eccentric wheel 64 is set at a position advanced by a certain angle θ2 from the trunnion shaft 1tlAoz in the rotational direction R of the motor cylinder 17, and the eccentricity is ε2 at the clutch-on position n. At the clutch-off position Wf, ε3 is larger than ε2.

Thus, when the second eccentric wheel 64 occupies the clutch-on position n, when the motor cylinder 17 rotates, each second distribution valve 62 is caused by the second eccentric wheel 64 to adjust the eccentricity Mc2 to 2 in the second valve hole 55. The motor cylinder 17 is reciprocated between a radially inner position and an outer position with a stroke of twice the distance.

In FIG. 9, the expansion region of the hydraulic motor M is indicated by EX, and the contraction region is indicated by sh. In the expansion region Ex, the second distribution valve 62
is moving from the eccentric neutral position CN2 to the inner position side, communicates the corresponding motor port b with the outer oil passage 53, closes the inner oil passage 52, and connects the motor plunger in the expansion stroke from the outer oil passage 53. High-pressure hydraulic oil is supplied to the cylinder holes 18 of 19 .

In the contraction region sh, the second distribution valve 62 is at the eccentric neutral position N2.
The corresponding motor port b is communicated with the inner oil passage 52 and disconnected from the outer oil passage 53, and the cylinder hole 18 of the motor plunger 19 during the contraction stroke is moved from the cylinder hole 18 of the motor plunger 19 to the inner oil passage 52. Hydraulic oil is drained to.

Further, at the eccentric neutral position N2, the second distribution valve 62 disconnects the corresponding motor boat b from both oil passages 52 and 53. In this case, as shown in FIG. 9A, the land portion 62a of the liquid valve 62 that closes the motor boat b is provided with a predetermined valve closing margin 12 only on the outer oil passage 53 side.

In this way, the expansion region Ex of the hydraulic motor M is advanced by an angle θ compared to the case where the eccentric direction line Xz coincides with the trunnion axis 02, and the contraction region sh is set to a wider angle than the expansion region Ex. be done.

Further, when the motor cylinder 17 rotates when the second center wheel 64 occupies the clutch-off position f, each second distribution valve 62 is moved to the second center by the second eccentric wheel 64, as shown in FIG.
The radial inner position of the motor cylinder 17 with a stroke of twice the eccentricity ε in the valve hole 55, and ``
:Moved back and forth between the inner and outer positions,
The second distribution valve 62 opens the outer oil passage 53 to the outside of the cylinder block B.

A pair of the pump boats a are arranged per cylinder hole 8 in a direction perpendicular to the sliding direction of the first distribution valve 61. Further, a pair of the motor boats b are also provided for each cylinder hole 18 in a line perpendicular to the sliding direction of the second distribution valve 62. In this way, it is possible to open and close the corresponding boats a and b with a relatively short stroke of each distribution valve 61, 62 while ensuring a large overall passage area of the pump port a and motor boat +-b.

Referring again to FIG. 8, the second eccentric 64 has its pivot 7.
A contact plate 79 is fixed to the peripheral wall opposite to 6 with screws 80,
A camshaft 81 supported by the crankcase 4 is engaged with the abutment plate 79 so as to be able to push the abutment plate 79 toward the clutch-off position f of the second eccentric wheel 64 . This camshaft 81
The operating wire 8 is connected to the clutch lever 82 fixed to the outer end of the clutch lever 82.
3 is connected, and a return spring 84 of the clutch lever 82 is compressed between the clutch lever 82 and the crankcase 4.

Further, the second eccentric wheel 64 is urged toward the clutch-on position n by the set spring 85. The set spring 85 is attached to a retainer 8 fixed to the outer periphery of the second eccentric shaft 64 with screws 86.
7 and the support ring 75.

Therefore, the second eccentric 64 normally has a set spring 85
However, when the camshaft 81 is rotated in the direction of the arrow by the pulling operation of the operating wire 83, it is swung to the clutch-off position.

In the above configuration, when the input cylinder shaft 5 of the hydraulic pump P is rotated from the primary reduction gear 2 while the second eccentric wheel 64 is held at the clutch-on position n, the pump swash plate 10 causes the pump plungers 9, 9, . . . Exhalation and suction strokes are applied alternately.

The pump plunger 9 pumps hydraulic oil from the cylinder hole 8 to the outer oil passage 53 while passing through the discharge area, and pumps hydraulic oil from the inner oil passage 52 to the cylinder hole 8 while passing through the suction area S. Inhale.

The high pressure hydraulic oil sent to the outer oil passage 53 is supplied to the hydraulic motor M.
Hydraulic oil is supplied to the cylinder hole 18 of the motor plunger 19 in the expansion region Ex, while the hydraulic oil is discharged from the cylinder hole 18 to the inner oil passage 52 by the motor plunger 19 in the contraction region sh.

During this period, the pump cylinder 7 receives reaction torque from the pump swash plate 10 via the pump plunger 9 in the discharge stroke, and the motor cylinder 17 receives reaction torque from the motor plunger 1 in the expansion stroke.
The cylinder block B is rotated by the sum of the reaction torque received from the motor swash plate 20 via the motor 9, and the rotational torque is transmitted from the output shaft 31 to the secondary reduction gear 3.

In this case, the gear ratio of the output shaft 31 to the input cylinder shaft 5 is given by the following equation.

Capacity of Hydraulic Pump P Therefore, if the capacity of hydraulic motor M is changed to a value consisting of zero, the transmission ratio can be changed to a required value consisting of one. Moreover, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, by tilting the motor swash plate 20 from the upright position to the inclined position, the gear ratio can be controlled steplessly up to a value of 1. I can do it.

By the way, in the hydraulic pump P, the suction area S is set to be wider than the discharge area, so even if the back pressure of the pump plunger 9 in the suction stroke is much lower than that of the bomb plunger 9 in the discharge stroke, the cylinder The suction efficiency of the holes 8 can be effectively increased. As a result, the overall efficiency of the hydraulic pump P can be improved even if the discharge area is sacrificed to some extent.

In addition, in order to increase the efficiency as much as possible, the suction area S should be set at 180°.
It is best to do so.

In addition, the discharge area is the eccentric direction line of the first eccentric wheel 63 x 1
Since the pump plunger 9 is retarded by the angle θ compared to the case where the trunnion axis O1 coincides with the virtual trunnion axis O1, the pump plunger 9 receives a large compressive load from the pump swash plate 10 from the time it contracts by the amount past the maximum extension point. It turns out. As a result, the maximum bending moment generated in the pump plunger 9 is reduced, so that the prying phenomenon between the pump plunger 9 and the opening edge of the cylinder hole 8 is alleviated, and the friction loss due to this phenomenon is significantly reduced.

On the other hand, in the hydraulic motor M, since the contraction area sh is set at a wider angle than the expansion area Ex, the back pressure of the motor plunger 19 during the contraction stroke can be sufficiently lowered, even if the expansion area Ex is sacrificed to some extent. Overall, the efficiency of the hydraulic motor M can be improved.

In addition, in order to increase the efficiency as much as possible, the contraction area sh should be set to 180
It is best to take °.

Further, the expansion region Ex is the eccentric direction line X of the second eccentric wheel 64.
, compared to the case where , is aligned with the trunnion axis o2, the angle θ
Since the angle was advanced by 2, the motor plunger 1 on the expansion stroke
9 is released from the thrust reaction force of the motor swash plate 20 at an early stage before reaching the maximum extension point. As a result, the maximum bending moment generated in the motor plunger 19 is reduced, so that the prying phenomenon between the motor plunger 19 and the circumferential edge of the cylinder hole 18 is alleviated, and the friction loss due to this phenomenon is significantly reduced.

During such operation, if the second eccentric wheel 64 is swung to the clutch-off position f, the high-pressure outer oil passage 53 is opened to the outside of the cylinder block B by the second distribution valve 62, so that the hydraulic motor M is High-pressure hydraulic oil is no longer supplied, and power transmission between the hydraulic pump P and the hydraulic motor M is cut off. That is, a so-called clutch-off state is obtained.

While the hydraulic pump P and hydraulic motor M are in operation, the pump swash plate 1
0 receives thrust loads in opposite directions from the pump plungers 9, 9... group, and the motor swash plate 20 receives thrust loads in opposite directions from the motor plungers 19, 19... groups, but the thrust load that the pump swash plate 10 receives is due to the thrust rollers. The output shaft 31 is connected via the bearing 11, the pump swash plate holder 12, the thrust roller bearing 40, the support tube 37, and the shaft 36.
The thrust load received by the motor swash plate 20 is supported by the thrust roller bearing 21, the trunnion shaft 22,
Similarly, it is supported by the output shaft 31 via the swash plate anchor 23, thrust roller bearing 47, support tube 45, and spool 44. Therefore, the above thrust load is applied to the output shaft 31
This only produces tensile stress on the shaft 31, but does not act on the crankcase 4 supporting the shaft 31 at all.

The connection structure between the first distribution valve 61 and the forced width 67 is as follows.
As shown in FIG. 7 and FIG. 7, the distributing valve 61 includes a small-diameter neck 61b and a circumferential long hole 89 bored in the support ring 75 so that the neck 61b engages with the neck 61b. An enlarged diameter hole 90 is connected to one end of the elongated hole 89 so that the large diameter portion of the outer end of the distribution valve 61 can pass therethrough. Therefore, the enlarged diameter hole 9
0, insert the distribution valve 61 into the hole 89, align its neck 61b with the elongated hole 89, and then rotate the forced width 67 in the circumferential direction.
The neck portion 61b can be engaged with the elongated hole 89, and in order to maintain this engaged state, at least one enlarged diameter hole 90 is provided.
An elastic plug 91 is fitted into the.

The connection structure between the second distribution valve 62 and the forcing shaft 68 is similar to that of the first
As shown in FIGS. 1 and 12, the first distribution valve 61 described above
Since the connection structure between this and the forcing shaft 67 is the same, corresponding parts are given the same reference numerals and detailed explanation thereof will be omitted.

1, 2, 17, and 8, a speed change control device 93 for controlling the angle of the motor swash plate 20 is connected to the trunnion shaft 22. As shown in FIG. This speed change control device 93 includes a sector gear 96 fixed to the other end of the trunnion shaft 22 by a bolt 94 and a pair of knock pins 95, 95, and a worm gear 9 meshing with the sector gear 96.
7, and a positive shaft that connects a drive shaft 98 to this worm gear 97.

The worm gear 97 is formed of a reversible DC electric motor 99, and a bearing 102.1 is attached to a gear box 101 fixed to the crankcase 4 with bolts 100.
It is rotatably supported via 03. Also, the electric motor 9
A stator 9 is fixed in place on the crankcase 4.

In the above, the sector gear 96 and the worm gear 97 constitute a speed reduction device 106 that can reduce the rotation of the drive shaft 98 and transmit it to the trunnion shaft 22, but becomes locked when receiving a reverse load from the trunnion shaft 22.

Therefore, when the electric motor 99 is rotated forward or reverse, the rotation is reduced and transmitted from the worm gear 97 to the sector gear 96, and further transmitted to the trunnion shaft 22, which rotates the rotation in the upright direction of the motor swash plate 20 or It can be rotated in the tilting direction.

Also, when the electric motor 99 is stopped and the motor swash plate 20 is held at an arbitrary angle, the motor swash plate 20 receives a moment in the standing or tilting direction from the motor plunge group 19.19... and that moment is transferred to the trunnion. Even if the transmission is transmitted to the sector gear 96 via the shaft 22, the worm gear 97 cannot be driven from the sector gear 96, so both gears 96 and 97 exhibit a lock 4J[, which does not allow rotation of the trunnion shaft 22, and therefore prevents the motor from tilting. The plate 20 is securely held in its current position.

In order to regulate the upright position and tilted position of the motor swash plate 20 by the electric motor 99, an arc-shaped regulation groove 104 concentric with the sector gear 96 is bored, and the sector gear 96 is slidably engaged with the regulation groove 104. A matching stopper pin 105 is fixed to the gear box 101.

1 and 2 again, a main oil passage 108 is bored in the center of the output shaft 31 and has a dead end at the back, and an oil filter is installed in this main oil passage 108 over almost its entire length. 1
09 is installed.

The open end of the main oil passage 10B communicates with the oil sump 110 at the bottom of the crankcase 4 via the replenishment pump 38.
8 is the drive gear 39 spline-coupled to the human-powered cylinder shaft 5;
Driven from. Therefore, while the input cylinder shaft 5 is rotating, the oil in the oil reservoir 110 is constantly pumped into the main oil passage 10 by the replenishing pump 38.
8.

The oil sent to the main oil passage 108 is filtered by an oil filter 109 and then sent to the inner oil passage 52 via a radial supply hole 111 formed in the output shaft 31. In this way, the hydraulic closed circuit between the hydraulic pump P and the hydraulic motor M is replenished with leaked hydraulic oil.

The supply hole 111 is provided with a first check valve 112 that prevents oil from flowing backward from the inner oil passage 52.
12 is biased in the valve closing direction by a temporary spring 114 provided surrounding the output shaft 31.

Therefore, during reverse load operation, that is, during engine braking, the hydraulic motor M performs a pump action and the hydraulic pump P performs a motor action, so that the outer oil passage 53 is at low pressure and the inner oil passage 52 is at high pressure. Instead, the hydraulic oil tries to flow back from the inner oil passage 52 to the supply hole 111, but this backflow is blocked by the first check valve 112. In this way, the reverse load is reliably transmitted from the hydraulic motor M to the hydraulic pump P, and a good engine braking effect can be obtained.

The oil sent to the main oil passage 10B also flows through a pair of radial left and right orifices 115 and 116 provided on the output shaft 31.
The oil is sent to lubricating oil passages 117 and 118 via. These lubricating oil passages 117 and 118 are formed as annular grooves on the outer periphery of the output shaft 31, facing the inner peripheral surfaces of the pump cylinder 9 and the motor cylinder 17.

The oil sent to the right lubricating oil passage 117 is introduced into the input cylinder shaft 5 through an axial oil groove 119 provided in the spline fitting portion 32 of the output shaft 31 with the cylinder block B. In this way, the pump swash plate 10, pump plunger 9, thrust roller bearing 11, needle bearing 42, seat plate 33, centering body 50, etc. in the input cylinder shaft 5 are lubricated.

Furthermore, in order to properly lubricate the thrust roller bearing 11 and needle bearing 42, both bearings 1
A small hole 120 communicating with the main oil passage 108 is bored in the output shaft 31 in the vicinity of 1.42.

The oil that has finished lubricating the needle bearing 42 is then diffused by centrifugal force to the thrust roller bearing 40.
Lubricate.

The oil sent to the left lubricating oil passage 11B flows into the swash plate anchor 23 and the cylinder holder 24 through an oil groove 121 provided to cross the flange 31a of the output shaft 31, which the end of the motor cylinder 17 contacts. will be introduced in In this way, the motor swash plate 20, motor plunger 19, thrust roller bearing 21, trunnion shaft 22, alignment body 51, needle bearings 25, 48, etc. in the swash plate anchor 23 and cylinder holder 24 are lubricated.

Furthermore, in order to properly lubricate the needle bearing 48, a small hole 122 communicating with the main oil passage 108 is bored in the output shaft 31 near the bearing 48.

The oil that has finished lubricating the needle bearing 48 is then diffused by centrifugal force to lubricate the thrust roller bearing 47.

In FIGS. 2, 15, and 16, the motor cylinder 17 has its inner end inserted into the oil groove 121 through two adjacent cylinder holes 18 and 18 in the constant sliding area of the motor plunger 19. A connecting radial oil passage 123 and an axial oil passage 124 that communicates the outer end of this oil passage 123 with the outer oil passage 53 are bored.

In this case, in order to obtain as large a passage cross-sectional area as possible, the radial oil passage 123 is formed in the two cylinder holes 18.1.
It is machined using a drill with a diameter larger than the thickness of the partition walls between 8. For this reason, the side hole 125 is located on the inner wall of the two cylinder holes 18, 1f3.
Reference numeral 5 denotes a motor plunger 1 that constantly slides into the cylinder hole 18.
9, there is no risk of the hydraulic oil in the cylinder hole 18 leaking through the side hole 125.

A second check valve 113 that prevents backflow of hydraulic oil from the outer oil passage 53 is interposed in the axial oil passage 124 . This second
The valve seat 126 that cooperates with the check valve 113 also functions as a plug that closes the perforation 124a of the oil passage 124. The second check valve 113 is urged toward the valve seat 126 by a spring 127.

Therefore, during normal load operation when the outer oil passage 53 is at high pressure, the second check valve 113 maintains the closed state and prevents the hydraulic oil from flowing from the outer oil passage 53 to the oil passage 124 side.
During engine braking when the pressure in the outer oil passage 53 is low, the second check valve 113 opens as hydraulic oil leaks from the hydraulic closed circuit, so that the oil groove 121 and the oil passage 123 are removed from the main oil passage 108.
, 124 in order to supply hydraulic oil to the outer oil passage 53.

19 to 21 show another embodiment of the present invention, in which when the second eccentric wheel 64 is operated to the flanch-off position f, the second distribution valve 62 controls the outer oil passage 53 and the inner oil passage 5.
It is designed to communicate between the two. This also allows power transmission between the hydraulic pump P and the hydraulic motor M to be interrupted.

In the figure, parts corresponding to those in the previous embodiment are given the same reference numerals.

C1 Effects of the Invention As described above, according to the present invention, a cylinder holder that rotatably supports a cylinder block is connected to a swash plate anchor that supports a swash plate and is fixed to a casing, and an eccentric Since the ring is installed, not only the mutual phase of the swash plate's trunnion axis and the eccentric direction line of the eccentric wheel, but also the eccentricity of the eccentric wheel with respect to the cylinder block can be adjusted as desired without being affected by processing errors or assembly errors. A swash plate type hydraulic system that can be set accurately and has stable characteristics can be obtained.

Moreover, 1. This hydraulic system can be assembled before being incorporated into the casing, and has good assembly performance6.

[Brief explanation of the drawing]

1 to 18 show a first embodiment of the present invention, in which FIG. 1 is a longitudinal cross-sectional plan view of a hydrostatic continuously variable transmission installed in a power transmission system of a motorcycle, and FIG. The longitudinal rear view of Fig. 1, Fig. 3, Fig. 4, and Fig. 5 are the m-m line of Fig. 2, IV
-IV line and VV line cross-sectional view, Figure 6 is vr of Figure 1
-vr line sectional view, Figure 6A is an enlarged sectional view around the first distribution valve when it comes to the eccentric neutral position in Figure 6, Figure 7 is a cross-sectional view of the ■-■ gland in Figure 6, and Figure 8 is the 1 is a sectional view taken along the line ■-■, FIG. 9 is a sectional view taken along the line IX-IX in FIG. 10 is the operation '1g (clutch off state) in FIG. 9, FIG. 11 is a view taken in the direction of arrow XI in FIG. 9, FIG. 12 is a front view of the second distribution valve, and FIG. 13 and Fig. 14 is Fig. 12 (7) XI[I-X
I[[[ line and XrV-XrV line sectional view,
An enlarged view of a part of the figure, Figure 16 is xvt-xv of Figure 15.
An X-ray cross-sectional view, Figure 17 is a cross-sectional view taken along the X■-X■ line in Figure 2,
Figure 18 is a view from the X■ arrow in Figure 2, and Figures 19 to 21.
The figure shows the second embodiment of the present invention, and FIG. 19 shows the first embodiment.
20 is a front view of the second distribution valve, and FIG. 21 is a sectional view taken along the line xxr-xxr in FIG. 20. B... Cylinder block, M... Hydraulic motor as a swash plate type hydraulic device, 0□... Trunnion axis of the swash plate 20, Xz... Eccentric direction line of the eccentric wheel 64, ε2... Same eccentricity Quantity, 4...Crankcase as casing, ■8...
- Cylinder hole, 20... Swash plate, 22... Trunnion shaft, 23... Swash plate anchor, 24... Cylinder holder, 52... Inner oil passage as a low pressure oil passage, 53... Outer oil passage as a high-pressure oil passage, 62...distribution valve, 64...
・Eccentric wheel

Claims (1)

[Claims] A cylinder block having an annular array of cylinder holes and concentrically arranged annular high-pressure oil passages and low-pressure oil passages, a plunger group that slides into the cylinder hole group, and a cylinder that engages with the protruding end of the plunger group. A swash plate that provides reciprocating motion to each plunger as the block rotates, and a swash plate that is arranged radially on the cylinder block and that reciprocates between the radially outer and inner positions of the cylinder block and connects each cylinder hole to a high-pressure oil path. and a distribution valve group that communicates alternately with the distribution valve group and the low-pressure oil passage, and an eccentricity that circumscribes the distribution valve group and is arranged eccentrically with respect to the center of rotation of the cylinder block, giving reciprocating motion to each distribution valve as the cylinder block rotates. In a swash plate type hydraulic system equipped with a ring, a cylinder holder that rotatably supports a cylinder block is connected to a swash plate anchor that supports a swash plate and is fixed to a casing, and an eccentric wheel is attached to this cylinder holder. A swash plate type hydraulic device.