JPH0689830B2 - Hydrostatic continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of Industrial Application The present invention relates to a hydrostatic stepless system in which a hydraulic closed circuit is formed between a swash plate hydraulic pump and a swash plate hydraulic motor. Regarding the transmission.

(2) Conventional Technology As the continuously variable transmission, the present applicant constructs a cylinder block by coaxially integrally coupling a pump cylinder of a swash plate hydraulic pump and a motor cylinder of a swash plate hydraulic motor to each other. An annular inner oil passage and an annular outer oil passage surrounding the inner oil passage are concentrically formed in the cylinder block, and the pump reciprocates between an outer position and an inner position in the radial direction of the cylinder block. A large number of first distribution valves that alternately connect a large number of cylinder holes in the cylinder to the oil passages, and a large number of cylinder holes of the motor cylinder by reciprocating between the radially outer position and the inner position. A large number of second distribution valves, which are alternately communicated with the oil passages, are radially arranged, and the first distribution valve group is provided with relative rotation between the cylinder block and the input member of the hydraulic pump. A first eccentric wheel that reciprocates each first distribution valve to communicate the cylinder hole on the discharge stroke side of the pump cylinder with the outer oil passage and the cylinder hole on the suction stroke side with the inner oil passage. In the second distribution valve group, the second distribution valves are reciprocated in accordance with the rotation of the cylinder block so that the cylinder holes on the expansion stroke side of the motor cylinder are set to the outer oil passages and the cylinder holes on the contraction stroke side. A structure in which second eccentric wheels that respectively communicate with the inner oil passages are engaged has been previously proposed (see Japanese Patent Application No. 61-15529). In itself, the outer oil passage is constituted by a simple annular groove, and the first and second distribution valves are aligned in the axial direction of the cylinder block so as to penetrate the annular groove.

(3) Problems to be Solved by the Invention Since the outer oil passage serves to transfer high-pressure hydraulic oil from the hydraulic pump to the hydraulic motor, transmission by bubbles contained in the hydraulic oil is included. Considering the decrease in efficiency, it is desirable to make the volume of the oil passage as small as possible.

However, in the configuration proposed above, even if an attempt is made to reduce the groove width of the annular groove that constitutes the outer oil passage in order to reduce the volume of the outer oil passage, the first oil lined in the axial direction of the cylinder block is aligned.
Since it is hindered by the second distribution valve, it is difficult to obtain an outer oil passage having a small volume.

The present invention has been made in view of the above circumstances, and the hydrostatic continuously variable transmission capable of sufficiently reducing the volume of the outer oil passage to improve the transmission efficiency and further downsizing the cylinder block. The purpose is to provide.

B. Configuration of the Invention (1) Means for Solving the Problems In order to achieve the above-mentioned object, the present invention provides an outer oil passage having an annular groove and staggered recesses on both side walls of the annular groove. A plurality of recesses that
And a second distribution valve is provided.

(2) Action The outer oil passage is composed of an annular groove and a large number of recesses formed in zigzag on both side walls thereof, and the first and second distribution valve groups are arranged so as to penetrate these recesses. Therefore, the groove width of the annular groove can be narrowed to a necessary minimum without being interfered with by both distribution valve groups, and an outer oil passage having a small volume can be obtained.

Moreover, the first and second distribution valve groups are also arranged in a staggered arrangement in accordance with the large number of recesses in the staggered arrangement. Therefore, the cylinder block of both distribution valves can be secured while the wall thickness of the cylinder block between both distribution valves is sufficiently secured. The axial distance can be shortened.

(3) Examples Hereinafter, examples of the present invention will be described with reference to the drawings. First, referring to FIGS. 1 and 2, the engine E of the motorcycle is shown.
Power from the crankshaft 1 to the chain type primary speed reducer 2, the hydrostatic continuously variable transmission T, and the chain secondary speed reducer 3
Is sequentially transmitted to the rear wheels (not shown).

The continuously variable transmission T is composed of a constant displacement type swash plate hydraulic pump P and a variable displacement type swash plate hydraulic motor M, and a crankcase 4 supporting the crankshaft 1 is used as a casing.
Accommodated in it.

The hydraulic pump P is an output sprocket 2a of the primary speed reducer 2.
An input cylinder shaft 5 as an input member that is detachably coupled with a plurality of connecting pins 16 (only one is shown in the drawing), and a needle bearing 6 is provided to the inner peripheral wall of an intermediate portion of the input cylinder shaft 5 to interpose it. A pump cylinder 7 that is rotatably fitted, and a large number of pump plungers 9 that are slidably fitted into a large number and odd numbered cylinder holes 8, 8 ... Of an annular array provided in the pump cylinder 7 so as to surround the center of rotation. , 9 and the pump swash plate 10 that contacts the outer ends of these pump plungers 9,9.
And, in order to keep the pump swash plate 10 inclined at a constant angle with respect to the axis of the pump cylinder 7 about the virtual trunnion axis O ₁ which is orthogonal to the axis of the pump cylinder 7, the back surface of the swash plate 10 is thrust. It is composed of a pump swash plate holder 12 supported by a roller bearing 11. The pump swash plate holder 12 is spline-fitted 13 on the inner peripheral wall of the outer end of the input cylinder shaft 5 so as to be disengageable, and is temporarily fixed by a circlip 14.

Thus, the pump swash plate 10 can reciprocate the pump plungers 9, 9 ... While the input cylinder shaft 5 is rotating to repeat the suction and discharge strokes.

In order to improve the followability of the pump plunger 9 to the pump swash plate 10, a coil spring 15 for urging the pump plunger 9 in the extension direction is contracted in the cylinder hole 8.

On the other hand, the hydraulic motor M includes a motor cylinder 17 coaxially arranged to the left of the pump cylinder 7 and a large number of odd cylinder holes arranged in an annular array in the motor cylinder 17 so as to surround the rotation center. A large number of motor plungers 19, 19 ... which are respectively slidably attached to 18, 18 ... And a motor swash plate 20 which abuts on the outer ends of these motor plungers 19, 19.
A trunnion shaft 22 having a half-moon-shaped cross section that supports the back surface of the motor swash plate 20 as a flat surface via a thrust roller bearing 21, and a swash plate anchor 23 that rotatably supports the cylindrical surface of the trunnion shaft 22. Composed of. Swashplate anchor 23
Is fixed to the crankcase 4 with a bolt 26 together with a cylindrical cylinder holder 24 connected to the right end thereof. The cylinder holder 24 is mounted on the motor cylinder 17 via the needle bearing 25.
The outer periphery of is rotatably supported.

The swash plate anchor 23 and the cylinder holder 24 are previously connected to each other by bolts 27.

In order to prevent the trunnion shaft 22 from rotating in a predetermined angle while allowing the trunnion shaft 22 to rotate, a swash plate anchor 23 is formed.
A bolt 29 is fixed to one end surface of the trunnion shaft 22 through an arcuate elongated hole 28 centered on the axis O ₂ of the trunnion shaft 22 (see FIGS. 2 and 18).

The motor swash plate 20 is actuated by rotation of the trunnion shaft 22 between an upright position that is perpendicular to the axis of the motor cylinder 17 and a maximum tilt position that tilts at a certain angle. In the state, as the motor cylinder 17 rotates, the motor plungers 19, 19 ... Can be reciprocated to repeat the expansion and contraction strokes.

In order to improve the followability of the motor plunger 19 with respect to the motor swash plate 20, a coil spring 30 that biases the motor plunger 19 in the extension direction is contracted in the cylinder hole 18.

The pump cylinder 7 and the motor cylinder 17 form an integral cylinder block B, and the output shaft 31 is passed through the center of the cylinder block B. The motor cylinder 17 is attached to the flange 31a formed integrally with the outer periphery of the output shaft 31.
The outer end of the pump cylinder 7 is struck, the pump cylinder 7 is spline-fitted to the output shaft 31, and the circlip 34 abutting against the outer end of the pump cylinder 7 via the seat plate 33 is locked to the output shaft 31. The cylinder block B is fixed to the output shaft 31.

The right end of the output shaft 31 has a pump swash plate 10 and a pump swash plate holder 12
And the right side wall of the crankcase 4, and the knock pin 35 and the split cotter are provided on the outer periphery of the right end portion.
A drive gear 39 and a thrust roller bearing 40 for a replenishment pump 38, which will be described later, are sequentially interposed between the support cylinder 37 fixed by 36 and the pump swash plate holder 12. The right end of the output shaft 31 is rotatably supported by the crankcase 4 via the support cylinder 37 and the ball bearing 41.

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

The left end of the output shaft 31 is the motor swash plate 20 and the trunnion shaft.
22 and the swash plate anchor 23. The swash plate anchor 23 and the support cylinder 45 extend so as to penetrate the left side wall of the crankcase 4 and the crankcase 4. Between the swash plate anchor 23 side and the retainer
46 and a thrust roller bearing 47 are sequentially interposed.
The left end of the output shaft 31 is rotatably supported by the swash plate anchor 23 via the needle bearing 48 and the retainer 46.

Further, an input sprocket 3a of the secondary reduction gear 3 is fixed to the left end of the output shaft 31 outside the crankcase 4 with a bolt 49.

In this way, all the constituent members of the transmission T from the sprocket 2a to the sprocket 3a are assembled as one assembly on the output shaft 31, so that the transmission T can be attached to and detached from the crankcase 4 very easily. Can be done.

The output shaft 31 has 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, and a motor swash plate 20.
A hemispherical aligning body 51 that engages with the inner peripheral surface of the pump so as to be tiltable in all directions is fitted, and these serve to align the pump swash plate 10 and the motor swash plate 20.

The swash plates 10 and 20 are strengthened in alignment, and the pump swash plate 10
And the pump plungers 9,9 ... Group, the motor swash plate 20 and the motor plungers 19,19 .. Spherical recesses 10a, 20a for engaging the spherical end portions 9a, 19a of the respective are formed.

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

In the cylinder block B, between the cylinder holes 8, 8 ... Group of the pump cylinder 7 and the cylinder holes 18, 18 ... Group of the motor cylinder 17, annular inner oil passages arranged concentrically around the output shaft 31. 52, the outer oil passage 53, the annular partition between the oil passages 52, 53 and the outer wall of the outer oil passage 53 are radially penetrated through the cylinder holes 8, 8 ... And 18, 18 ... Hole 54,5
4 and the second valve holes 55, 55, and the adjacent cylinder holes 8, 8 ... and the first valve holes 54, 54 ... and a large number of pump ports a, a. Holes 18, 18 ... and second valve holes 55, 5
A large number of motor ports b, b ... Which communicate with each other are provided.

The inner oil passage 52 is formed as an annular groove on each circumferential surface facing the cylinder block B and the output shaft 31.

As shown in FIGS. 4 and 5, the outer oil passage 53 has an annular dovetail groove 58 formed in the outer periphery of the cylinder block B and staggered arrangement on both side walls of the dovetail groove 58. It is composed of a plurality of semi-circular recessed portions 59, 59 ... Perforated, and the open surfaces of the dovetail groove 58 and the recessed portions 59, 59 ... Are closed by a sleeve 60 welded to the outer peripheral surface of the cylinder block B.
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 have the staggered arrangement of the recesses 5
Are arranged so as to penetrate through the bottom wall of the hydraulic pump 9, and the cylinder holes 8, 8 of the hydraulic pump P and the cylinder holes 18, 18 of the hydraulic pump P are correspondingly shifted in phase in the circumferential direction. There is.

By doing so, the wall thickness of the cylinder block B between the first and second valve holes 54, 54 can be increased while the space between the valve holes 54, 55 is narrowed along the axial direction of the cylinder block B. This can contribute to downsizing of the cylinder block B.

Also, when high oil pressure is introduced into the outer oil passage 53, the dovetail groove 58
Even if both side walls of the cylinder are expanded and deformed, the deformation increases the surface pressure of the fitting portion of the cylinder block B and the sleeve 60, so that oil leakage from the fitting portion can be prevented.

The first valve holes 54, 54 ... Have spool-type first distribution valves 61, 61.
, And second spool valves 62, 62, ... Also slidably engaged with the second valves 55, 55, respectively. And the first
Distribution valves 61, 61 ... A first eccentric ring 63 that surrounds the distribution valves 61, 61.
However, a second eccentric ring 64 surrounding the second distribution valves 62, 62 ... Is engaged via ball bearings 65, 66, respectively. Distribution valve
The outer ends of 61, 61 ... are the first concentric relationship with the first eccentric ring 63.
The compulsory wheel 67 and the outer ends of the second distribution valves 62, 62 ... Are connected to each other by a second compulsory wheel 68 concentric with the second eccentric wheel 64. The connection structure thereof will be described later.

The first eccentric ring 63 is detachably fixed to the outer circumference of the input cylinder shaft 5 by a headed pin 70 and a clip 71, and as shown in FIG. 6, from the center of the output shaft 31 along the eccentric direction line X _1. It is held at a position eccentric for a predetermined distance ε ₁ . The eccentric direction line X ₁ is
A constant angle θ from the virtual trunnion axis O _{1 of the} pump swash plate 10 in the relative rotation direction R of the pump cylinder 7 with respect to the input cylinder shaft 5.
It is set to the position delayed by _one . The angle θ ₁ can be easily adjusted by changing the spline fitting position between the input cylinder shaft 5 and the pump swash plate holder 12.

When a relative rotation occurs between the input cylinder shaft 5 and the pump cylinder 7, each first distribution valve 61 is moved to the first eccentric ring 63 by the first eccentric ring 63.
The valve hole 54 is reciprocated between the radially inner position and the outer position of the pump cylinder 7 with a stroke that is twice the eccentricity ε ₁ .

In FIG. 6, the discharge region of the hydraulic pump P is indicated by D, and the suction region is indicated by S. In the discharge region D, the first distribution valve 61 is at a position N ₁ (hereinafter referred to as an eccentric neutral position) orthogonal to the eccentric direction line X _1.
From the cylinder hole 8 to the outer oil passage 53 by the pump plunger 9 during the discharge process while moving the corresponding inner port side from the inner oil passage 53 while communicating the corresponding pump port a with the outer oil passage 53. Hydraulic fluid is pumped to.

In the suction region S, the first distribution valve 61 is moving from the eccentric neutral position N ₁ to the outer position side so that the corresponding pump port a communicates with the inner oil passage 52 and does not communicate with the outer oil passage 53. , The inner oil passage 52 by the pump plunger 9 during the suction process
The hydraulic oil is sucked into the cylinder hole 8 from.

Further, at the eccentric neutral position N ₁ , the first distribution valve 61 makes the corresponding pump port a incommunicable with both oil passages 52 and 53. In this case, the 6th
As shown in FIG. A, the land portion 61a of the first distribution valve 61 that closes the pump port a is provided with a predetermined valve closing margin l ₁ only on the outer oil passage 53 side.

In this way, the discharge area D of the hydraulic pump P is retarded by the angle θ ₁ as compared with the case where the eccentric direction line X ₁ is matched with the virtual trunnion axis O ₁ , and the suction area S is larger than the discharge area D. Set to wide angle.

As shown in FIGS. 1, 2 and 8, the second eccentric wheel 64 is provided between the clutch-on position n and the clutch-off position f via a support shaft 75 and a pivot shaft 76 parallel to the output shaft 31. Are swingably connected. The support ring 75 is detachably fixed to the outer circumference of the cylinder holder 24 via a plurality of headed pins 77 and clips 78.

The eccentric direction line X ₂ of the second eccentric ring 64 is the trunnion axis O ₂
From being set to a position by a predetermined angle theta ₂ binary angle in the rotational direction R of the motor cylinder 17, the eccentricity is a clutch-on position n in epsilon _2, a large becomes epsilon ₃ than epsilon ₂ in the clutch off position f is there.

Thus, when the motor cylinder 17 rotates when the second eccentric wheel 64 occupies the clutch-on position n, each second distribution valve 62 is rotated.
Is the eccentric amount ε in the second valve hole 55 due to the second eccentric ring 64.
_A stroke twice as long as two strokes is reciprocated between the radially inner position and the outer position of the motor cylinder 17.

In FIG. 9, the expansion region of the hydraulic motor M is indicated by Ex and the contraction region thereof is indicated by Sh. In the expansion region Ex, the second distribution valve 62 is moving from the eccentric neutral position N ₂ to the inner position side so that the corresponding motor port b communicates with the outer oil passage 53 and the inner oil passage 53.
High pressure hydraulic oil is supplied from the outside oil passage 53 to the cylinder hole 18 of the motor plunger 19 in the expansion stroke.

In the contraction region Sh, the second distribution valve 62 moves from the eccentric neutral position N ₂ to the outer position side, and the corresponding motor port b
To communicate with the inner oil passage 52 and the outer oil passage 53,
The hydraulic oil is discharged from the cylinder hole 18 of the motor plunger 19 to the inner oil passage 52 during the contraction process.

Further, at the eccentric neutral position N ₂ , the second distribution valve 62 makes the corresponding motor port b incommunicable with both oil passages 52 and 53. In this case, the 9th
As shown in FIG. A, the land 62a that closes the motor port b of the valve 62 has a predetermined valve closing allowance l only on the outer oil passage 53 side.
_Two are provided.

In this way, the expansion region Ex of the hydraulic motor M is advanced by an angle θ ₂ compared with the case where the eccentric direction line X ₂ is aligned with the trunnion axis O ₂ , and the contraction region Sh is wider than the expansion region Ex. Is set to.

When the second eccentric wheel 64 occupies the clutch off position f,
When the motor cylinder 17 rotates, as shown in FIG. 10, each second distribution valve 62 causes the second eccentric ring 64 to make the stroke in the second valve hole 55 twice as much as the eccentric amount ε _3. Is reciprocated between the radially inner position and the outer position, and at the inner and outer positions thereof, the second distribution valve 62 opens the outer oil passage 53 to the outside of the cylinder block B.

A pair of pump ports a are provided for each cylinder hole 8 and are arranged side by side in a direction perpendicular to the sliding direction of the first distribution valve 61. The motor port b also has a single cylinder hole.
A pair of 18 is provided side by side in the direction perpendicular to the sliding direction of the second distribution valve 62. In this way, the pump port a
Also, it is possible to open and close the corresponding ports a and b with relatively short strokes of the distribution valves 61 and 62 while ensuring a large total passage area of the motor port b.

Referring again to FIG. 8, the second eccentric wheel 64 has a contact plate 79 fixed to the peripheral wall of the second eccentric wheel 64 on the side opposite to the pivot shaft 76 with screws 80, and the cam shaft 81 pivotally supported by the crankcase 4 has the contact plate 79. It is engaged with 79 so that it can be pushed towards the clutch-off position f of the second eccentric wheel 64. An operation wire 83 is connected to a clutch lever 82 fixed to the outer end of the cam shaft 81, and a return spring 84 for the lever 82 is compressed between the clutch lever 82 and the crankcase 4. Further, the second eccentric wheel 64 is biased toward the clutch-on position n side by the set spring 85. The set spring 85 is contracted between the retainer 87 fixed to the outer circumference of the second eccentric ring 64 with a screw 86 and the support ring 75.

Therefore, the second eccentric wheel 64 is normally held at the clutch-on position n by the force of the set spring 85, but
When the cam shaft 81 is rotated as indicated by the arrow by the pulling operation of 83, the cam shaft 81 is swung to the clutch-off position f.

In the above structure, the second eccentric wheel 64 is connected to the clutch-on position n.
When the input cylinder shaft 5 of the hydraulic pump P is rotated from the primary reduction gear device 2 while being held at 1, the discharge and suction strokes are alternately given to the pump plungers 9, 9 ... By the pump swash plate 10.

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

The high-pressure hydraulic oil sent to the outer oil passage 53 is in the expansion hole Ex of the hydraulic motor M and is located in the cylinder hole 18 of the motor plunger 19.
On the other hand, the hydraulic oil is discharged from the cylinder hole 18 to the inner oil passage 52 by the motor plunger 19 existing in the contraction area Sh.

During this time, the reaction torque that the pump cylinder 7 receives from the pump swash plate 10 via the pump plunger 9 in the discharge stroke,
The cylinder block B is rotated by the sum of the reaction torque that the motor cylinder 17 receives from the motor swash plate 20 via the motor plunger 19 in the expansion stroke, and the rotation 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.

Therefore, if the capacity of the hydraulic motor M is changed from zero to a certain value, the gear ratio can be changed from 1 to a certain required value. Moreover, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, the motor swash plate is
The gear ratio can be controlled steplessly from 1 to a certain value by tilting from 20 upright positions to a certain tilt position.

By the way, in the hydraulic pump P, since the suction region S is set to be wider than the discharge region D, even if the back pressure of the pump plunger 9 in the suction stroke is much lower than that of the pump plunger 9 in the discharge stroke, the cylinder hole The inhalation efficiency of No. 8 can be effectively increased. As a result, the efficiency of the hydraulic pump P can be improved as a whole even if the discharge area D is sacrificed to some extent.

In order to maximize the efficiency, it is best to set the suction area S to 180 °.

The discharge region D, the angle theta ₁ as compared with the case where align your eccentric direction line X ₁ of the first eccentric ring 63 to the virtual trunnion axis O ₁
Since the pump plunger 9 is retarded by a certain amount, the pump plunger 9 receives a large compressive load from the pump swash plate 10 from when the pump plunger 9 contracts a certain amount past the maximum extension point. 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 the phenomenon is significantly reduced.

On the other hand, in the hydraulic motor M, the contraction area Sh is expanded to the expansion area.
Since the angle is set wider than Ex, the back pressure of the motor plunger 19 during the contraction stroke can be sufficiently lowered, and the efficiency of the hydraulic motor M can be improved as a whole even if the expansion region Ex is slightly sacrificed.

In order to maximize the efficiency, it is best to set the contraction area Sh to 180 °.

Further, since the expansion region Ex is advanced by the angle θ ₂ compared to the case where the eccentric direction line X ₂ of the second eccentric ring 64 is aligned with the trunnion axis O ₂ , the motor plunger 19 in the expansion stroke has the maximum extension point. Before reaching, the thrust reaction force of the motor swash plate 20 is released early. As a result, the motor plunger
Since the maximum bending moment generated in 19 is reduced, the prying phenomenon between the motor plunger 19 and the peripheral edge of the cylinder hole 18 is alleviated, and the friction loss due to the phenomenon is significantly reduced.

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

During operation of the hydraulic pump P and the hydraulic motor M, the pump swash plate 10
, And the motor swash plate 20 receive thrust loads in the opposite directions from the pump plungers 9, 9 ... Group, and the motor plungers 19, 19 ... group, but the thrust load received by the pump swash plate 10 is the thrust roller bearing 11 and the pump skew. Plate holder
12, thrust roller bearing 40, support cylinder 37 and cotter
The thrust load that is supported by the output shaft 31 via the motor 36 and that is received by the motor swash plate 20 is a thrust roller bearing 21, a trunnion shaft 22, a swash plate anchor 23, and a thrust roller bearing.
It is also supported by the output shaft 31 via the support tube 47, the support cylinder 45 and the cotter 44. Therefore, the thrust load is
However, it does not act on the crankcase 4 supporting the shaft 31 at all.

As shown in FIGS. 6 and 7, the connection structure of the first distribution valve 61 and the compulsory wheel 67 is such that a small-diameter neck portion 61b formed in the distribution valve 61 and the neck portion 61b are engaged with each other. The elongated hole 89 is formed in the support ring 75 in the circumferential direction, and one end of the elongated hole 89 is connected with an enlarged diameter hole 90 so that the large diameter portion of the outer end of the distribution valve 61 can pass therethrough. Therefore, if the distribution valve 61 is inserted into the expanded diameter hole 90 and the shin portion 61b is aligned with the elongated hole 89 and then the compulsory wheel 67 is rotated in the circumferential direction, the shin portion 61b is engaged with the elongated hole 89. can do. In order to maintain this engagement state, at least 1
Elastic plugs 91 are fitted into the two expanded holes 90.

As shown in FIGS. 11 and 12, the connection structure between the second distributing valve 62 and the compulsory wheel 68 is the same as the above-mentioned first distributing valve 61 and the compulsory wheel 67.
Since the structure is the same as that of the connection structure with, the same reference numerals are given to the corresponding parts, and the detailed description thereof will be omitted.

In FIG. 1, FIG. 2, FIG. 17, and FIG. 8, a gear shift control device 93 for controlling the angle of the motor swash plate 20 is connected to the trunnion shaft 22. This shift control device 93
Besides the trunnion shaft 22, a bolt 94 and a pair of knock pins 95, 9
Sector gear 96 fixed by 5 and this sector gear 9
The worm gear 97 meshes with the worm gear 6, and a forward / reverse-rotatable DC electric motor 99 that connects the drive shaft 98 to the worm gear 97. Is rotatably supported by bearings 102 and 103. Further, the stator of the electric motor 99 is fixed at a proper position of the crankcase 4.

In the above, the sector gear 96 and the worm gear 97 can decelerate the rotation of the drive shaft 98 and transmit the rotation to the trunnion shaft 22. However, when the reverse load is applied from the trunnion shaft 22, the speed reducer 106 becomes a locked state.

Thus, when the electric motor 99 is rotated in the normal direction or the reverse direction, the rotation is decelerated and transmitted from the worm gear 97 to the sector gear 96, and further transmitted to the trunnion shaft 22, which is directed in the standing direction of the motor swash plate 20 or It can be rotated in the tilt direction.

Further, when the electric motor 99 is stopped and the motor swash plate 20 is held at an arbitrary angle, the motor swash plate 20 moves to the motor plungers 19,1.
9 ... Even if a moment in the standing or tilting direction is received from the group and the moment is transmitted to the sector gear 96 via the trunnion shaft 22, the worm gear 97 cannot be driven from the sector gear 96, so both gears 96, 97 are locked. In this state, the trunnion shaft 22 is not allowed to rotate, so that the motor swash plate 20 is securely held at the position at that time.

In order to restrict the standing position and tilting position of the motor swash plate 20 by the electric motor 99, the sector gear 96 is provided with an arcuate restriction groove 104 concentric therewith, and is slidably engaged with the restriction groove 104. The matching stopper pin 105 is fixed to the gear box 101.

Referring again to FIGS. 1 and 2, a main oil passage 108 having a deep stop is bored at the center of the output shaft 31, and the main oil passage 108 extends over substantially the entire length thereof. Is installed.

The open end of the main oil passage 108 is communicated with the oil sump 110 at the bottom of the crankcase 4 via the replenishment pump 38, and the reinforcing pump 38 is driven by the drive gear 39 splined to the input cylinder shaft 5. Therefore, during the rotation of the input cylinder shaft 5, the oil sump 110 is always
The oil inside is fed to the main oil passage 108 by the reinforcement pump 38.

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

The replenishment hole 111 is provided with a first check valve 112 for preventing the backflow of oil from the inner oil passage 52, and the check valve 112 is an output shaft.
A leaf spring 114 surrounding 31 is urged in the valve closing direction.

Thus, during reverse load operation, that is, during engine braking, the hydraulic motor M acts as a pump and the hydraulic pump P acts as a motor, so that the outer oil passage 53 is at a low pressure and the inner oil passage 52 is at a high pressure. Change from the inner oil passage 52 to the supply hole
The hydraulic oil tries to flow back to 111, but the backflow is blocked by the first check valve 112. Thus, the hydraulic motor M
The reverse load is reliably transmitted from the hydraulic pump P to the hydraulic pump P, and a good engine braking effect is obtained.

The oil sent to the main oil passage 108 is also sent to the lubricating oil passages 117, 118 via the pair of radial left and right orifices 115, 116 provided in the output shaft 31. These lubricating oil passages 117,118
Is formed as an annular groove on the outer periphery of the output shaft 31 so as to face the inner peripheral surfaces of the pump cylinder 9 and the motor cylinder 17.

The oil sent to the lubricating oil passage 117 on the right side is introduced into the input cylinder shaft 5 through the axial oil groove 119 provided in the spline fitting portion 32 of the output shaft 31 with the cylinder block B. Thus, the pump swash plate 10, the pump plunger 9, the thrust roller bearing 11, the needle bearing in the input cylinder shaft 5
42, the seat plate 53, the aligning body 50, etc. are lubricated.

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

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

The oil sent to the lubricating oil passage 118 on the left is the motor cylinder 17
Is introduced into the swash plate anchor 23 and the cylinder holder 24 through an oil groove 121 which is provided so as to traverse the flange 31a of the output shaft 31 with which the end of the shaft contacts. Thus, the swash plate anchor 23
Also, the motor swash plate 20 in the cylinder holder 24, the motor plunger 19, the thrust roller bearing 21, the trunnion shaft 2
2. The aligning body 51, the needle bearings 25, 48, etc. are lubricated.

Further, in order to satisfactorily lubricate the needle bearing 48, a small hole 122 communicating with the main oil passage 108 is formed in the output shaft 31 in the vicinity of 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
Is a radial oil passage 123 that connects the inner end to the oil groove 121 by passing between two cylinder holes 18, 18 that are adjacent to each other in the always sliding section of the motor plunger 19, and the outside of this oil passage 123. An axial oil passage 124 is provided to communicate the end with the outer oil passage 53.

At that time, the oil passage 123 in the radial direction is machined with a drill having a diameter larger than the thickness of the partition wall between the two cylinder holes 18, 18 in order to obtain the passage cross-sectional area as large as possible. For this reason, a side hole indicated by reference numeral 125 comes into contact with the inner walls of the two cylinder holes 18, 18, but since the side hole 125 is closed by the motor plunger 19 which is always in sliding contact with the cylinder hole 18, the side hole is formed. There is no fear that the hydraulic oil in the cylinder hole 18 will leak out through the 125.

A second check valve 113 that prevents the reverse flow of the hydraulic oil from the outer oil passage 53 is interposed in the oil passage 124 in the axial direction. This second check valve 1
The valve seat 126 that cooperates with 13 also functions as a plug that closes the perforation port 124a of the oil passage 124. The second check valve 113 is biased by the spring 127 toward the valve seat 126.

Therefore, during normal load operation in which the outer oil passage 53 has a high pressure, the second check valve 113 maintains the closed state to prevent the hydraulic oil from flowing from the outer oil passage 53 to the oil passage 124 side. Oil passage 5
At the time of engine braking where the pressure is low at 3, the second check valve 113 opens due to the leakage of hydraulic oil from the hydraulic closed circuit. Therefore, the hydraulic oil flows from the main oil passage 108 through the oil groove 121 and the oil passages 123, 124 sequentially to the outside oil. Replenished to road 53.

FIGS. 19 to 21 show another embodiment of the present invention. When the second eccentric wheel 64 is operated to the clutch off position f, the second distribution valve 62 causes the outer oil passage 53 and the inner oil passage 52. It is designed to communicate with each other. This can also cut off power transmission between the hydraulic pump P and the hydraulic motor M. Incidentally, in the figure, the same reference numerals are given to the portions corresponding to the previous embodiment.

C. Effects of the Invention As described above, according to the present invention, the outer oil passage, the annular groove,
Since the first and second distribution valve groups are formed so as to penetrate the recesses, the first and second distribution valve groups are formed. The width of the annular groove can be narrowed to the required minimum without being interfered by
It is possible to obtain an outer oil passage having a small volume, and thus it is possible to suppress a decrease in transmission efficiency due to bubbles in the high-pressure hydraulic oil filling the outer oil passage. Moreover, since the first and second distribution valve groups are also arranged in a zigzag manner, the cylinder block axial distance between the distribution valves can be sufficiently shortened while ensuring a sufficient thickness of the cylinder block between the distribution valves. It is possible,
Therefore, a compact cylinder block having a short axial length can be obtained.

[Brief description of drawings]

1 to 18 show a first embodiment of the present invention. FIG. 1 is a vertical plan view of a hydrostatic continuously variable transmission provided in a power transmission system of a motorcycle, and FIG. FIG. 1 is a longitudinal rear view, FIG. 3, FIG. 4, and FIG. 5 are III-III line and IV of FIG.
-IV line and VV line sectional drawing, FIG. 6 is VI-VI of FIG.
FIG. 6A is an enlarged sectional view around the first distributing valve when the eccentric neutral position is reached in FIG. 6, and FIG.
VII-VII line sectional view, FIG. 8 is a VIII-VIII line sectional view of FIG. 1, FIG. 9 is a IX-IX line sectional view of FIG. 1 (clutch ON state), and FIG. 9A is FIG. FIG. 10 is an enlarged cross-sectional view around the second distributing valve when the eccentric neutral position is reached, FIG. 10 is an operation diagram of FIG. 9 (clutch-off state), and FIG. 11 is a XI arrow view of FIG.
FIG. 12 is a front view of the second distributing valve, FIGS.
XIII-XIII line and XIV-XIV line sectional drawing of the figure, FIG.
16 is an enlarged view of a part of the figure, FIG. 16 is a sectional view taken along line XVI-XVI in FIG. 15, FIG. 17 is a sectional view taken along line XVII-XVII in FIG. 2, and FIG. 18 is a sectional view taken along the arrow XVIII in FIG. FIGS. 19 to 21 show a second embodiment of the present invention. FIG. 19 is a sectional view corresponding to FIG. 10, FIG. 20 is a front view of the second distributing valve, and FIG. XX in Figure 20
It is a sectional view taken along the line I-XXI. E ... Engine, M ... Hydraulic motor, P ... Hydraulic pump, T ... Continuously variable transmission 5 ... Input cylinder shaft as input member, 7 ... Pump cylinder, 8 ... Cylinder hole, 9 ... Pump plunger, 10 ...
… Pump swash plate, 17 …… Motor cylinder, 18 …… Cylinder hole, 19 …… Motor plunger, 20 …… Motor swash plate, 52…
… Inner oil passage, 53 …… Outer oil passage, 54 …… First valve hole, 55 ……
2nd valve hole, 58 …… annular dovetail groove, 59 …… recess, 60 …… sleeve, 61 …… first distribution valve, 62 …… second distribution valve, 63 ……
1st eccentric wheel, 64 ... 2nd eccentric wheel

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Yoshihiro Nakajima 1-4-1 Chuo, Wako-shi, Saitama Inside Honda R & D Co., Ltd. (72) Inventor Seiji Yamazaki 1-4-1 Chuo, Wako, Saitama Incorporated at Honda R & D Co., Ltd. (72) Sumio Tagawa Inventor Sumio 1-4-1 Chuo, Wako, Saitama Incorporated Honda R & D Co., Ltd. (56) References JP 61-153057 (JP, A) British patent 745543 (GB, A)

Claims (2)

[Claims] Claim: What is claimed is: 1. A pump cylinder of a swash plate hydraulic pump and a motor cylinder of a swash plate hydraulic motor are coaxially integrally connected to each other to form a cylinder block. An annular outer oil passage that surrounds the oil passage is concentrically formed, and reciprocates between the radially outer position and the inner position of the cylinder block to form a large number of cylinder holes in the pump cylinder, respectively. To a plurality of first distributing valves which alternately communicate with each other, and a plurality of first distributing valves which similarly reciprocate between an outer position and an inner position in the radial direction to alternately communicate a plurality of cylinder holes of the motor cylinder with the oil passages. The two distribution valves are respectively arranged radially, and the first distribution valve group applies reciprocating motion to each first distribution valve as the cylinder block and the input member of the hydraulic pump rotate relative to each other. A cylinder block on the discharge stroke side of the da is engaged with the outer oil passage, and a cylinder hole on the suction stroke side is communicated with the inner oil passage, and a second divergence valve group is provided with a cylinder block. A second eccentric wheel that reciprocates each second distribution valve in accordance with the rotation of the cylinder so that the cylinder hole on the expansion stroke side of the motor cylinder communicates with the outer oil passage and the cylinder hole on the contraction stroke side communicates with the inner oil passage. In the hydrostatic continuously variable transmission formed by engaging with each other, the outer oil passage is composed of an annular groove and a large number of recessed portions formed in zigzag on both side walls of the annular ring, and penetrates these recessed portions. A hydrostatic continuously variable transmission characterized in that the first and second distribution valve groups are arranged as described above. 2. The structure according to claim 1, wherein the annular groove is formed in a dovetail-shaped cross section, and the open surface of the annular groove is closed by a sleeve fixed to the outer peripheral surface of the cylinder block. A hydrostatic continuously variable transmission.