JPH06201018A - Radial plunger type fluid transmission - Google Patents

Abstract

(57) [Summary] [Purpose] To obtain a radial plunger type fluid transmission that is easy to be made small and compact and has high transmission efficiency. A pump shaft 11 and a motor shaft 21 which are coaxial with each other and are rotatable relative to each other are rotatably supported by casings 1 and 2, and the pump and motor shaft 1
The pump cylinders 16 and the motor cylinders 26 are arranged in a radial pattern extending from the shaft centers of both shafts on substantially the same plane perpendicular to the shaft centers of the shafts 1, 21 and are attached to the casings 1, 2. Then, the pump plungers 15 and the motor plungers 25 are slidably inserted into the cylinder holes of the pump cylinders 16 and the motor cylinders 26, respectively, and the pump plungers 15 reciprocate in the cylinder holes according to the rotation of the pump shaft 11. Then, the reciprocating motion of the motor plunger that reciprocates by the hydraulic pressure discharged from the pump cylinder 16 is converted into the rotational motion of the motor shaft.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a radial plunger type fluid transmission composed of a fluid pump and a fluid motor in which a cylinder and a plunger are arranged so as to extend around a shaft in a radial direction.

2. Description of the Related Art Radial plunger type fluid pumps, fluid motors, and fluid transmissions constructed by combining them have been widely used. For example, JP-A-3-37465 and JP-A-3-37465.
There are those disclosed in Japanese Patent Laid-Open No. 103646, Japanese Patent Laid-Open No. 4-262158 and the like. A radial plunger type fluid transmission can be constructed by combining a radial plunger type pump and a motor, but conventionally, a fluid transmission was constructed by arranging a fluid pump and a fluid motor in parallel. .

[0002]

Therefore, in the case of the conventional radial plunger type fluid transmission,
The axial length is at least the total of the axial lengths of the fluid pump and the hydraulic motor, which increases the axial length, making it difficult to configure the transmission in a compact and compact size. It was In addition, in the conventional transmission, the oil passage for supplying the fluid discharged from the fluid pump (oil) to the adjacent fluid motor is apt to be long, and the power transmission efficiency of the transmission is lowered due to the pressure loss in the oil passage. There was a problem that it was easy.

The present invention has been made in view of these problems.
It is an object of the present invention to provide a radial plunger type fluid transmission that is easy to be made small and compact and has high transmission efficiency.

[0004]

In order to achieve such an object, the radial plunger type fluid transmission according to the present invention rotatably supports a pump shaft and a motor shaft, which are coaxial with each other and are relatively rotatable, by a casing. , Arranging the pump cylinders and motor cylinders extending radially from the shaft centers of both shafts on the substantially same plane perpendicular to the shaft centers of these pump and motor shafts, and mounting them in a casing. A pump plunger and a motor plunger are slidably inserted into the cylinder bores of the cylinder, and the rotation of the pump shaft is transmitted to each pump plunger via the pump side motion conversion mechanism. Reciprocate with the motor side It is configured to convert via a converting mechanism the reciprocating movement of the motor plungers in the cylinder bore of the motor cylinder to rotary motion of the motor shaft.

When the pump cylinders and the motor cylinders are radially arranged side by side on substantially the same plane perpendicular to the shaft centers of both shafts in this way, the axial dimension of the transmission is shortened and the transmission is made compact. , Can be made compact. Further, it is easy to shorten the oil passage connecting the pump cylinder and the motor cylinder, and it is possible to reduce the pressure loss and improve the power transmission efficiency of the transmission.

In this case, one end of the pump shaft facing the motor shaft and the other end of the motor shaft facing each other are axially overlapped so as to enter the other end.
It is preferable that both shafts be supported so as to be rotatable relative to each other by a bearing disposed between the shafts at the overlap portion. In this case, in particular, a pair of bearings are arranged in the overlap portion so as to be separated from each other in the axial direction, and one bearing is arranged in a position that axially overlaps with one of the bearings that rotatably support the pump shaft and the motor shaft in the casing. What to do
It is preferable from the viewpoint of strength.

At least one of the pump-side motion converting mechanism and the motor-side motion converting mechanism is supported by a first gear coaxially fixed to the pump shaft or the motor shaft and a casing so as to be rotatable relative to the first gear. It is preferable that the second gear meshes with the second gear and a crank pin integrally formed with the second gear at a position eccentric from the rotation shaft of the second gear, and that the crank pin is connected to the pump plunger or the motor plunger. By doing so, the transmission can be made more compact.

Further, the pump-side motion converting mechanism and the motor-side motion converting mechanism are respectively rotatable relative to the casing, the first pump driving gear and the first motor driving gear fixed coaxially on the pump shaft and the motor shaft, respectively. A second pump drive gear that is supported by the first pump drive gear and meshes with the first pump drive gear; a pump crankpin integrally formed with the second pump drive gear at a position eccentric from the rotation axis of the second pump drive gear; A second motor drive gear that is rotatably supported by the second motor drive gear and that meshes with the first motor drive gear, and a motor integrally formed with the second motor drive gear at a position eccentric from the rotation axis of the second motor drive gear. It consists of a crank pin, and connects the pump plunger and pump crank pin, and The first pump drive gear is integrally formed with the pump shaft by connecting with the crank pin, the ring gear is used as a motor shaft, and the external gear formed on the outer periphery of the ring gear is used as the first motor drive gear to form a second motor drive gear. It is preferably configured to mesh with the motor drive gear.

Further, a sun gear disposed coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and a sun gear that rotatably supports the planetary pinion. A planetary gear set including a carrier that rotates on the same axis and a ring gear that has inner teeth that mesh with the planetary pinion and that rotates on the same axis as the sun gear is provided, and the pump shaft and the input shaft are connected together to form a pump shaft and a motor shaft. Alternatively, an output shaft may be provided separately from the above, and the sun gear, the ring gear, and the carrier that form the planetary gear set may be connected to any of the input shaft, the motor shaft, and the output shaft to form a transmission. With this configuration, a transmission having higher power transmission efficiency can be obtained.

In this case, the pump shaft and the input shaft are integrally formed, and the sun gear is connected to the input shaft,
Preferably, the ring gear is connected to the motor shaft and the carrier is connected to the output shaft. Further, it is preferable that the planetary gear set is disposed on substantially the same plane as the plane on which the pump cylinder and the motor cylinder are disposed. By doing so, the transmission can be made more compact.

On the other hand, one of the pump shaft and the motor shaft is provided with an eccentric portion having an axis eccentric from its rotation axis, and the motion conversion mechanism causes the crank motion of this eccentric portion to occur in either the pump plunger or the motor plunger. The transmission can also be configured to convert to reciprocating motion. In this way, the mechanism for reciprocating the pump or the motor plunger can be simplified.

In this case, an eccentric collar having an outer peripheral surface eccentric from the shaft of the eccentric portion is rotatably mounted on the eccentric portion, and an annular guide ring is rotatably mounted on the eccentric collar to provide a pump plunger and a motor. A stroke adjustment mechanism that adjusts the rotational position of the eccentric collar on the eccentric part by variably adjusting the eccentric amount of the shaft center of the outer peripheral surface of the eccentric collar. Is preferably provided. With this configuration, the reciprocating stroke of the pump or the motor plunger can be adjusted with a simple mechanism.

In place of the annular guide ring, an annular connecting ring is rotatably mounted on the eccentric collar, and one of the inner ends of the pump plunger and the motor plunger is pivotally supported on this connecting ring, and the stroke is set. An adjusting mechanism and a double mechanism for revolving the connecting ring without rotating may be provided. Even with this configuration, the reciprocating stroke of the plunger can be adjusted with a simple mechanism.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described below with reference to the drawings. A radial plunger type hydraulic transmission TM1 according to the first embodiment of the present invention is shown in FIGS. 1 is a half sectional view showing the pump plunger portion, and FIG. 2 is a half sectional view showing the motor plunger portion. This transmission TM1
Has a right casing 1 and a left casing 2 that are bolted together, a right cover 3 that is attached to cover the side surface of the right casing 1, and a left cover 4 that is attached to cover the side surface of the left casing 2.

The pump shaft 11 is supported by bearings 5a and 5b at the centers of the right and left casings 1 and 2, respectively.
A motor shaft 21 is coaxially and rotatably arranged. The left end portion 11c of the pump shaft 11 projects outward from the left cover 4 and is driven through this portion. That is, the pump shaft 11
Also serves as the input shaft. The right end portion 21c of the motor shaft 21 projects outward from the right cover 3 and the output is taken out from this portion.
Also serves as the output shaft.

The insertion hole 1 is provided at the right end of the pump shaft 11.
1a is formed, and the left end portion 2 of the motor shaft 21 is formed.
1a projects into this insertion hole 11a, and both shafts 11 and 21 overlap at this portion. Then, both shafts 11 and 2 in this overlapping portion
A pair of left and right bearings 6a and 6b are provided between the shafts 1, so that the shafts 11 and 21 can rotate relative to each other. Both shafts 11 and 21
Since the axial load acting on the bearings 6a and 6b also acts on the bearings 6a and 6b, the left bearing 6a is axially overlapped with the bearing 5a that rotatably supports the motor shaft 11 with respect to the left casing 2. It is arranged. This makes it possible to reduce the load on the bearing 6a, which is advantageous in terms of strength.

A first portion is provided on the outer peripheral portion of the right end of the pump shaft 11.
The pump drive gear 11b is formed, and the motor shaft 21
A first motor drive gear 21b is formed on the left outer peripheral portion of the. Then, the first pump drive gear 11b and the first motor drive gear 21b are radially surrounded,
Four pump crank members 12 and four motor crank members 22 are arranged at equal intervals and alternately, as shown in FIG.

The pump crank member 12 is rotatably supported by the left and right casings 1 and 2 via the left and right bearings 14a and 14b. Pump crank member 12
Is a second pump drive gear 12a coaxial with the rotation axis thereof,
It has a pump crankshaft 12b which is eccentric from the rotary shaft, and the second pump drive gear 12a meshes with the first pump drive gear 11b. Therefore, the homp shaft 11
When is driven to rotate, the pump crank member 12 is driven to rotate. At this time, since the pump crank shaft 12b is eccentric, the pump crank shaft 12b revolves around the rotation shaft of the pump crank member 12 according to the rotation of the pump crank member 12. The pump crank member 12 is composed of a member integrally including the second pump drive gear 12a and the pump crank shaft 12b, and a support member 12c into which the pump crank shaft 12b is press-fitted and coupled.

On the other hand, the motor crank member 22 includes the left and right casings 1 and 2 via left and right bearings 24a and 24b.
A second shaft that is rotatably supported by 2 and that is coaxial with its rotation axis.
It has a motor drive gear 22a and a motor crankshaft 22b that is eccentric from the rotating shaft. Second motor drive gear 2
Since 2a meshes with the first motor drive gear 21b, when the motor crank member 22 is rotationally driven, the motor shaft 21 is rotationally driven. The motor crank member 22 is composed of a member integrally including the second motor drive gear 22a and the motor crank shaft 22b, and a support member 22c into which the motor crank shaft 22b is press-fitted and coupled.

Four pump cylinders 16 and four pump cylinders 16 are provided, each passing through the axial center between the first pump drive gear 11b and the first motor drive gear 21b and located on a plane perpendicular to the pump and the motor shafts 11 and 21. The motor cylinders 26 are alternately arranged at equal intervals as shown in FIG.
As shown in FIG. 1 and FIG. 2, both cylinders 16 and 26 have trunnion arms 16b and 26 protruding left and right, respectively.
b, and the trunnion arms 16b and 26b
Both cylinders 16 and 26 are connected to the left and right casings 1 and 2 via the
It is supported so that it can be swung freely.

Cylinder holes 16a and 26a are formed in the cylinders 16 and 26 so as to open inward in the radial direction, and the plunger portion 15a of the pump plunger 15 and the motor plunger 25 are inserted into the cylinder holes 16a and 26a from the inside in the radial direction. The plunger portion 25a is inserted slidably. Both cylinders 16 and 26 are arranged radially outward of the corresponding pump crank member 12 and motor crank member 22, respectively, and the plungers 15 and 26 inserted into the cylinder holes 16a and 26a as described above. Two
Crank member 1 to which inner ends 15b and 25b of 5 correspond
It is pivotally supported by 2,22 crank pins 12b and 22b.

Here, as described above, when the pump crank member 12 is rotated, the pump crank shaft 12b which is eccentric from the rotation shaft revolves around this rotation shaft, and therefore is pivotally supported by the pump crank shaft 12b. The connected pump hoop plunger 15 reciprocates in the cylinder hole 16a while swinging the pump cylinder 16. Similarly,
When the motor plunger 25 reciprocates in the cylinder hole 26 a of the motor cylinder 26, this causes the motor crankshaft 22 to move.
b is revolved, and the motor crank member 22 is rotated.

Trunnion portion 16 of each pump cylinder 16
A communication hole 16c that communicates with the cylinder hole 16a is formed in b. Similarly, a communication hole 26c that communicates with the cylinder hole 26a is formed in the trunnion portion 26b of each motor cylinder 26.
c is formed. These communication holes 16c and 26c are respectively formed in the oil passages 1a and 1b formed in the right casing 1.
Through the corresponding pump distribution valve 30 and motor distribution valve 40. Therefore, as shown in FIG. 4, four pump distribution valves 30 are provided corresponding to the pump cylinders 16, and four motor distribution valves 40 are provided corresponding to the motor cylinders 16.

The pump distribution valve 30 is provided in the right casing 1.
A pump valve hole 35 formed in the radial direction on the
It has a pump valve spool 31 slidably disposed therein. An oil passage 1a communicating with the cylinder hole 16a of the corresponding pump cylinder 16 is opened in the valve hole 35. The outer end of the pump valve spool 31 is pressed inward by the spring 32, and the inner end 31b projects inward and abuts on the outer peripheral surface 39a of the pump valve cam 39 coupled to the pump crank member 12. . As shown in FIG. 4, the outer peripheral surface 39 a of the cam 39 has a rice ball shape, and when the pump valve cam 39 is rotated together with the pump crank member 12, the outer peripheral surface 3 a is formed.
Pushed by 9a, the pump valve spool 31 reciprocates in the pump valve hole 35.

When the pump crank member 12 rotates, the pump plunger 15 connected through the pump crank shaft 12b reciprocates in the cylinder hole 16a of the pump cylinder 16, so that the reciprocating motion of the pump valve spool 31 is the pump plunger. Synchronize with 15 reciprocating motions.
The outer peripheral surface 39a of the pump valve cam 39 has the spool 31 when the pump plunger 15 is in the process of moving from the bottom dead center to the top dead center according to the rotation of the pump crank member 12 (in the discharge process). When the pump plunger 15 is in the process of moving from the top dead center to the bottom dead center (in the suction process), the spool 31 is pushed down by the biasing force of the spring 32 (moved inward). Push up against the bias (move outward).

As a result, when the pump plunger 15 is in the discharge stroke, the oil passage 1a communicates with the discharge oil passage 37 via the groove portion 31a of the spool 31, and is pushed out of the cylinder hole 16a according to the movement of the pump plunger 15. The hydraulic oil coming in is sent to the discharge oil passage 37 through the communication hole 16c and the oil passage 1a. Then, the check valve 33 is pushed open to be supplied to the communication oil passage 38. This connecting oil passage 3
8 is formed through the inside of the casing (however, not shown), communicates with the supply oil passage 47 of the motor distribution valve 40, and the working oil discharged from the pump cylinder 16 as described above is It is supplied to the supply oil passage 47 from the communication oil passage 38.

On the other hand, when the pump plunger 15 is in the suction stroke, the oil passage 1 is routed through the groove 31a of the spool 31.
The hydraulic fluid returned to the first return oil passage 36 is sucked into the cylinder hole 16a according to the movement of the pump plunger 15.

The motor distribution valve 40 is provided in the right casing 1.
Motor valve hole 45 formed by extending in the radial direction
It has a motor valve spool 41 slidably arranged therein, and an oil passage 1b communicating with a cylinder hole 26a of a corresponding motor cylinder 26 is opened in this valve hole 45. The outer end of the motor valve spool 41 is pressed inward by the spring 42, and the inner end 41b projects inward.
It is in contact with the outer peripheral surface 49a of the motor valve cam 49 coupled to the motor crank member 22. As shown in FIG. 4, the outer peripheral surface 49a of the cam 49 also has a pump valve cam 3
When the motor valve cam 49 is rotated together with the motor crank member 22, the outer peripheral surface 49a pushes the motor valve spool 41 so that the motor valve spool 41 reciprocates in the motor valve hole 45. .

When the motor plunger 25 connected through the motor crank shaft 22b reciprocates in the cylinder hole 26a of the motor cylinder 26, the motor crank member 22 is moved.
, The reciprocating motion of the motor valve spool 41 is also synchronized with the reciprocating motion of the motor plunger 25. The outer peripheral surface 49a of the motor valve cam 49 has the spool 41 when the motor plunger 25 is in the process of moving from the top dead center to the bottom dead center (in the supply process) according to the rotation of the motor crank member 22. It is pushed down (moved inward) by the force of the spring 42, while the motor plunger 2
When 5 is in the process of moving from the bottom dead center to the top dead center (in the discharging process), the spool 41 is pushed up against the bias of the spring 42 (moved outward).

As a result, when the motor plunger 25 is in the supply stroke, the oil passage 1b and the supply oil passage 47 communicate with each other via the groove 41a of the spool 41, and the oil is fed from the pump cylinder 16 to the supply oil passage as described above. The hydraulic oil coming in
It is supplied into the cylinder hole 26a of the motor cylinder 26,
Upon receiving this hydraulic pressure, the motor plunger 25 is moved to the bottom dead center.

On the other hand, when the motor plunger 25 is in the discharge stroke, the oil passage 1 is routed through the groove 41a of the spool 41.
b and the second return oil passage 46 communicate with each other, and the motor plunger 2
5, the hydraulic oil in the motor cylinder 26 becomes the second
It is discharged to the return oil passage 46. In addition, this second return oil passage 4
6 communicates with the first return oil passage 36 through the inside of the casing, and the hydraulic oil discharged as described above is sent into the pump cylinder hole 16a of the pump plunger 15 in the suction stroke.

The operation of the radial plunger type hydraulic transmission TM1 constructed as above will be described.
In this transmission TM1, the pump shaft 11 acting as an input shaft is rotationally driven.
Thereby, the first and second pump drive gears 11b, 1
The pump crank member 12 is rotated via 2a, and the pump plunger 15 reciprocates in the pump cylinder 16. Due to this reciprocation, the discharged hydraulic oil is supplied to the motor cylinder 26 by the action of the pump distribution valve 30, and the motor plunger 26 is reciprocated in the motor cylinder 26. As a result, the motor crank member 22 is rotationally driven, and this drives the first and second motor drive gears 21.
The motor shaft 21 which is transmitted to the motor shaft 21 via b and 22a and acts as an output shaft is rotationally driven.

However, with the above structure alone, the rotation of the pump shaft 11 is simply transmitted to the motor shaft 21,
The gear ratio is constant and does not play a role as a transmission. Therefore, the transmission TM1 of this example is provided with the shift control valve mechanism 50 for variably controlling the gear ratio, which will be described below.

The shift control valve mechanism 50 has a timing valve spool 51 slidably inserted in a spool hole 53 formed in the left cover 4 so as to extend in the radial direction. The outer end of the spool 51 is biased inward by the spring 52, and the inner end 51b of the spool 51 projects inward and abuts the outer peripheral surface of the timing cam 63 of the timing mechanism 60. The shift control valve mechanism 50 is provided corresponding to each pump cylinder 16, and each spool hole 51 and the communication hole 16c of the pump cylinder 16 are communicated with each other so that the relief valve hole 56, the drain groove 57, and the drain groove 57 A drain hole 58 is formed. Further, a bypass oil passage 59 communicating with the first return oil passage 36 extends from the relief valve hole 56 through the casings 1 and 2. A relief valve spool 55 is slidably disposed in the relief valve hole 56, and the relief valve spool 55 is pressed by a spring to close the right end opening of the relief valve hole 56.

The timing valve spool 51 inserted in the spool hole 53 has a land portion 51a, and the land portion 51 has a drain hole 58 according to the movement of the spool 51.
Is designed to be blocked. The outer peripheral surface of the timing cam 63 with which the inner end portion 51b of the spool 53 contacts is shown in FIG.
The lower part 63a and the higher part 63b are formed as shown in FIG.
And have. As will be described later, the timing cam 63 is rotated in synchronization with the rotation of the pump shaft 11, and in response to this rotation, the timing valve spool 51 is rotated.
Is reciprocated in the spool hole 53.

First, the operation when the spool 51 is reciprocated in the spool hole 53 in this way will be described.
When the inner end portion 51b of the spool 51 is in contact with the lower portion 63a of the timing cam 63, the timing valve spool 51 is in the state shown in FIG. 1, and the land portion 51a is located at the position closing the drain hole 58. In addition, the relief valve spool 55 arranged in the relief valve hole 56.
Is pushed by the spring and moved to the right. This spool 5
The communication hole 16c of the pump cylinder 16 is opposed to the right end of the pump cylinder 5, and receives the hydraulic pressure of the oil discharged from the pump cylinder 16, but the spool 55 has an orifice 55a.
Is provided, the hydraulic oil in the communication hole 16c flows into the spool hole 56, and the relief valve spool 55 receives the discharge hydraulic pressure from both sides. Therefore, due to the difference in pressure receiving area and the spring pressing force, the relief valve spool 55
Is held in a state of being moved to the right as shown in FIG. In this right-moved state, the relief valve spool 55 blocks the bypass oil passage 59.

On the other hand, when the inner end portion 51b of the spool 51 is in contact with the high portion 63b of the timing cam 63,
The timing valve spool 51 is in the state shown in FIG. 5, the land 51a moves to the outer diameter side of the drain hole 58, and the drain hole 58 opens into the casing inner space. Therefore, when the relief valve spool 55 receives the hydraulic pressure of the oil discharged from the pump cylinder 16, the hydraulic valve pushes the relief valve spool 55 to the left as shown in FIG. As a result, the communication hole 16c communicates with the bypass oil passage 59, and the oil discharged from the pump cylinder 16 is discharged from the bypass oil passage 59 to the first return oil passage 36. Therefore, at this time, the oil discharged from the pump cylinder 16 is not sent to the motor cylinder 26.

As can be seen from the above description, by controlling the position of the timing valve spool 51, the amount of oil sent from the pump cylinder 16 to the motor cylinder 26 can be controlled, whereby the pump shaft 1
The ratio of the rotation speed of the motor shaft 21 to the rotation of 1
That is, the gear ratio can be variably controlled.

In order to control the position of the timing valve spool 51, a timing mechanism 60 for rotating the timing cam 63 according to the rotation of the motor shaft 11 is provided. The timing mechanism 60 includes a sun gear 61 attached to the pump shaft 11, a planetary pinion 62 that meshes with the sun gear 61, and a carrier 64 that rotatably holds the planetary pinion 62.
A timing cam 63 having an internal toothed ring gear that meshes with the planetary pinion 62, a phase adjustment driven gear 65 that is integrally connected to the carrier 64 by a pin 64a, and the left cover 4 that meshes with the phase adjustment driven gear 65.
And a phase adjustment drive gear 66 rotatably supported by the left casing 2.

The phase adjusting drive gear 66 is normally fixed and held, and thus the carrier 64 is also fixed and held. Therefore, when the pump shaft 11 is rotationally driven, the sun gear 61 is rotated together with the pump shaft 11, which causes the timing cam 63 to rotate via the planetary pinion 62. As described above, the timing cam 63 is rotated in synchronization with the pump shaft 11, but since the timing cam 63 is for adjusting the discharge amount from the pump cylinder 16 as described above, the timing cam 63 is.
Must be operated in synchronization with the reciprocating movement of the pump plunger 15, that is, the rotation of the pump crank member 12.

Therefore, the number of teeth Z1 of the first pump drive gear 11b, the number of teeth Z2 of the second pump drive gear 12a, the number of teeth Zs of the sun gear 61 of the timing mechanism 60 and the number of teeth Zr of the ring gear of the timing cam 63, The relationship between the rotational speed Nc of the pump crank member 12 and the rotational speed Nr of the timing cam 63 is expressed as Nr / Nc = (Zs.Z2) / (Zr.Z1) = 1 / n, where n is an integer. The number of teeth is set. With this arrangement, when the pump shaft 11 is driven to rotate the pump crank member 12 n times, the timing cam 63
Rotates once.

In this example, the setting is such that n = 3, and therefore, the timing cam 63 has three lower portions 63.
It has a and a high portion 63b. The length of the low portion 63a is equal to the length of the high portion 63b, so that the timing valve spool 51 moves up in half of the total reciprocating stroke of the pump plunger 15 and moves down in the other half. The relationship between the reciprocating stroke of the pump plunger 15 and the discharge amount is shown in FIG. 7, in which the working oil is sucked in the stroke corresponding to the suction stroke of the pump plunger 15,
The hydraulic oil is discharged in the stroke corresponding to the discharge stroke. The amount of hydraulic oil at this time changes like a sine curve.

FIG. 7A shows a case where the timing valve spool 51 is moved upward during the stroke indicated by the arrow A. In this case, during the stroke indicated by A, the suction operation in the suction stroke is not affected, but the hydraulic oil is not discharged in the discharge stroke, and the hatched portion in the figure is not discharged. In this way, the amount of oil discharged from the pump cylinder 16 is adjusted.

Here, the length of the stroke indicated by A cannot be changed in accordance with the lengths of the low portion 63a and the high portion 63b of the timing cam 63, but this stroke phase can be variably adjusted. . This adjustment can be performed by externally rotating the shaft 66a of the phase adjustment drive gear 66. Thus, for example, in FIG.
As shown in (B), if the stroke indicated by A is moved, all the discharged oil is sent to the motor cylinder 26, and in this case, the maximum speed ratio can be obtained. That is, the gear ratio control of the transmission TM1 can be performed by controlling the rotational position of the phase adjustment drive gear 66.

In the above, the pump shaft 11
Although it has been described that the motor is driven to transmit the power to the motor shaft 21, the pump and the motor are reversed, the motor shaft 21 is used as the pump shaft to drive the shaft 21, and the pump shaft 11 is used as the motor shaft. The power may be taken out from the shaft 11.

Next, regarding the radial plunger type hydraulic transmission TM2 according to the second embodiment of the present invention,
This will be described with reference to FIG. This transmission TM
2 is the transmission TM1 according to the first embodiment.
Since it has a configuration similar to that of FIG. 8, only a portion having a different configuration from the transmission TM1 according to the first embodiment and its peripheral portion are shown in FIG. Therefore, in the following, the same parts as those of the transmission TM1 according to the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

This transmission TM2 has a pump shaft 111 which also serves as an input shaft, a motor shaft 121 which is rotatably disposed on the pump shaft 111 by bearings 106a and 106b, and protrudes rightward and outward from the right cover 103. Output shaft 155, which is connected via a power transmission planetary gear mechanism 150. The pump shaft 111 is rotatably supported by the left casing 102 via the bearing 105a, the motor shaft 121 is rotatably supported by the right casing 101 via the bearing 105b, and the output shaft 155 is right by the bearing 105c. It is rotatably supported by the cover 103.

The power transmission planetary gear mechanism 150 includes a sun gear 1 splined to the pump shaft 111.
51, a ring gear 154 coupled to the motor shaft 121, the sun gear 151 and the ring gear 15
4 and a carrier 153 that rotatably holds the planetary pinion 152 that meshes with the carrier 4.
Is coupled to the output shaft 155.

A first motor drive gear 122 is splined and attached to the motor shaft 121, and the first motor drive gear 122 meshes with a second motor drive gear 22a of the motor crank member 22. Therefore, when the pump shaft 111 is driven, the rotation of the pump shaft 111 causes the first and second pump drive gears 11 to rotate.
It is transmitted to the pump plunger 15 via 1b and 12a. Then, similarly to the transmission TM1 of the first embodiment, the motor plunger 25 is reciprocated by the oil discharged from the pump cylinder 16, and the motor shaft 12
1 is rotationally driven. In this example, the motor shaft 121
Is transmitted to the ring gear 154 of the power transmission planetary gear mechanism 150.

Further, in this example, the rotation of the pump shaft 111 is caused by the rotation of the first and second pump drive gears 111b and 12b.
The sun gear 15 of the power transmission planetary gear mechanism 150 is not only transmitted to the pump cylinder 15 via a.
It is also transmitted to 1. Therefore, the output shaft 155 is
Driving force of motor shaft 121 and pump shaft 1
It is driven by receiving the driving force of 11, and efficient power transmission can be performed.

In this example, the pump distribution valve 130 is composed of a suction side check valve 131 and a discharge side check valve 135. A return oil passage 132 is provided in a portion opened and closed by the suction side check valve 131, and a discharge oil passage 136 is provided in a portion opened and closed by the discharge side check valve 135. Therefore, the hydraulic oil pushed by the pump plunger 15 in the discharge stroke and discharged to the oil passage 101a pushes the discharge side check valve 135 to flow into the discharge oil passage 136, and when the pump plunger 15 is in the suction stroke. The suction side check valve 131 is opened and the working oil is sucked from the return oil passage 132 into the pump cylinder hole 16a.

FIG. 9 shows a radial plunger hydraulic transmission TM3 according to the third embodiment of the present invention. This transmission TM3 differs from the transmission TM2 according to the second embodiment only in the disposition position of the power transmission planetary gear mechanism 170, and the basic configuration is the same as the transmission TM2 of the second embodiment.

Specifically, the power transmission planetary gear mechanism 170 is arranged so as to be located substantially in the center of the transmission TM3, that is, in the same plane as the pump plunger 15 and the motor plunger 25 in the axial direction. It is different from the transmission TM2 of the second embodiment. With this configuration, the transmission T
It becomes easy to make the size of M3 smaller and compact by shortening the axial dimension of M3. It should be noted that, because of this structure, the sun gear 171 is integrated with the pump shaft 161.
And a first motor drive gear 174a is formed on the outer periphery of the ring gear 174. And the carrier 17
3 is coupled to the output shaft 165.

In the second and third embodiments, the pump shafts (input shafts) 111 and 161 are driven to transmit the power to the output shafts 155 and 165, but the pump and the motor are reversely rotated. Output shaft 15
This shaft 1 using 5,165 as the input shaft
55, 165 to drive the pump shaft 111, 161
Is used as an output shaft, this shaft 111, 16
The power may be taken out from No. 1.

Next, regarding a radial plunger type hydraulic transmission TM4 according to a fourth embodiment of the present invention,
This will be described with reference to FIGS. 10 and 11. Note that FIG.
Is a half sectional view showing a pump plunger portion, and FIG. 11 is a half sectional view showing a motor plunger portion. The transmission TM4 has a right casing 201, a left casing 202, a right cover 203 and a left cover 204.

Pump shafts 211 and motor shafts 221 are coaxially and rotatably disposed in the centers of the right and left casings 201 and 202, supported by bearings 205a and 205b. Pump shaft 211
Has a left end portion 211c protruding outward from the left cover 204, and is driven through this portion.
The pump shaft 211 also serves as an input shaft. The right end portion 221c of the motor shaft 221 projects outward from the right cover 203, and the output is taken out from this portion. The motor shaft 221 also serves as the output shaft.

An insertion hole 211a is formed in the right end portion of the pump shaft 211, and the left end portion 221a of the motor shaft 221 projects into the insertion hole 211a, where both shafts 211 and 221 overlap each other. There is. A pair of left and right needle bearings 206a and 206b are arranged between the shafts 211 and 221 in the overlapping portion, so that the shafts 211 and 221 can rotate relative to each other. The left needle bearing 206a
Is arranged so as to overlap the bearing 205a in the axial direction,
The structure is advantageous in terms of strength.

The right end portion 211b of the pump shaft 211
As shown in FIG. 12, the outer peripheral surface of the pump is eccentric from the rotation axis C1 of the pump shaft 211 by a distance L1. That is, the axis C2 of the outer peripheral surface of the right end portion 211b is separated from the rotation axis C1 by the distance L1. An eccentric collar 212 is rotatably mounted on the right end portion 211b. The outer peripheral surface of the eccentric collar 212 is eccentric from the axial center C2 of the outer peripheral surface of the pump shaft right end portion 211b by a distance L2, and the axial center C3 thereof is separated from the axial center C2 by a distance L2.

The eccentric collar 212 is the pump shaft 211.
Although they are rotatably attached to b, they are connected via a stroke adjusting mechanism 230. The stroke adjusting mechanism 230 includes a first sun gear 231 spline-coupled to the pump shaft 211 and a first planetary pinion 2 that meshes with the first sun gear 231.
33, a carrier 232 that rotatably supports the first planetary pinion 233, and a first planetary pinion 23.
3, a first ring gear 234 that meshes with the third ring gear, a second ring gear 236 that is adjacent to the first ring gear 234 and that is coupled to the left casing 202, a second planetary pinion 235 that meshes with the second ring gear 236, and a second planetary pinion 235. And a second sun gear 237 that meshes with. The first and second planetary pinion 23
Both 3, 235 are rotatably supported by a carrier 232 via a pinion shaft 232a.

External teeth are formed on the outer periphery of the first ring gear 234, and the stroke adjusting gear 239 meshes with the external teeth.
Is attached. This stroke adjustment gear 239
The shaft portion 239a of the above is protruding outward so that the stroke adjusting gear 239 can be rotationally driven. A connecting collar 238 is rotatably attached to the second sun gear 237 by spline connection, and an internal gear 238a is formed at the right end of the connecting collar 238. On the other hand, an external gear 212a is formed on the left side surface of the eccentric collar 212, and these internal gears 238a are formed.
And the external gear 212a mesh with each other, and the eccentric collar 212 and the coupling collar 238 are coupled.

In the stroke adjusting mechanism 230 having the above structure, the stroke adjusting gear 239 is normally fixed and held. Therefore, when the pump shaft 211 is rotated, the eccentric collar 212 connected as described above via the stroke adjusting mechanism 239 causes the pump shaft 21 to move.
It rotates together with 1.

An annular guide ring 213 is rotatably mounted on the eccentric collar 212. Then, as shown in FIG. 12, the guide rings 213 are radially surrounded so that they are alternately arranged at equal intervals.
Five pump plungers 215 and five pump cylinders 216, and a motor plunger 225 and a motor cylinder 226 are provided.

The pump cylinder 216 is swingably supported by the left and right casings 201 and 202 at the left and right trunnion portions 216c, and its cylinder hole 216a is open to the inner peripheral side. A pump plunger 215 is slidably inserted into each cylinder hole 216a, and an inner end portion 215a of each pump plunger 215 is attached to the guide ring 2a.
It is in sliding contact with the outer peripheral surface of 13. As described above, the axis C3 of the outer peripheral surface of the eccentric collar 212 is eccentric with respect to the rotation axis C1 of the pump shaft 211. Therefore, when the eccentric collar 212 is rotated together with the pump shaft 211, each pump plunger 215 is reciprocated in the pump cylinder 216 by a distance corresponding to the amount of eccentricity of the shaft center C3.

Therefore, if the eccentric distance of the shaft center C3 of the outer peripheral surface of the eccentric collar 212 with respect to the rotation axis C1 of the pump shaft 211 is variably adjusted, the reciprocating stroke of the pump plunger 215 can be variably controlled, and the discharge from the pump cylinder 216 can be performed. The amount of oil can be variably controlled. The stroke adjusting mechanism 230 adjusts the eccentric distance of the axis C3 with respect to the rotation axis C1.
This is performed by rotating the stroke adjusting gear 239 of.

This stroke adjustment will be described with reference to FIG. In FIG. 3, the rotational axis C1 of the pump shaft 211 (this coincides with the rotational axis of the motor shaft 221), the axial center C2 of the outer peripheral surface of the right end portion 211b of the pump shaft 211 and the axial center of the outer peripheral surface of the eccentric collar 212. C
3 shows the positional relationship of No. 3, and the solid line shows the case where these three axes C1, C2, C3 are arranged side by side on the same straight line. As described above, the rotation axis C1 and the axis C2 are separated by the distance L1, and the axis C2 and the axis C3 are separated by the distance L2.
Therefore, when the axes C1, C2 and C3 are aligned on the same straight line, the rotation axis C1 and the axis C3 are separated by a distance L3.
The distance is (= L1 + L2), and the distance between the rotation axis C1 and the axis C3 at this time is the maximum.

When the stroke adjusting gear 239 of the stroke adjusting mechanism 230 is rotated from this state, the second sun gear 237 is relatively rotated with respect to the first sun gear 231. Therefore, the eccentric collar 212 is rotated relative to the pump shaft 211. Since the eccentric collar 212 is rotatably arranged on the outer peripheral surface of the right end portion 211b of the pump shaft 211, this rotation causes the eccentric collar 21 to rotate.
The axis C3 of the outer peripheral surface of No. 2 rotates around the axis C2 of the outer peripheral surface of the right end portion 211b.

As a result, for example, as shown in FIG.
The axis C3 rotates 90 degrees clockwise around the axis C2,
The eccentric collar 212 moves to the position indicated by the chain double-dashed line, and the axis C3 moves to the position indicated by C3 '. As a result, the eccentric distance of the shaft center C3 with respect to the rotation shaft C1 becomes L3 ′ (<L3), which is short. In this way, the stroke adjustment gear 23
By rotating 9, the eccentric distance L3 of the shaft center C3 is adjusted, and when the pump shaft 211 is rotated,
The reciprocating stroke of the pump plunger 215 can be variably adjusted.

Trunnion portion 21 of pump cylinder 216
6b has a communication hole 216c communicating with the cylinder hole 216a.
Is formed, and the pump shaft 211 is formed as described above.
The pump plunger 215 moves the cylinder hole 2 according to the rotation of the cylinder.
When the reciprocating motion is carried out in the 16, the hydraulic oil is sucked and discharged through the communication hole 216c. Communication hole 216c
Is connected to a pump distribution valve 250 including a suction side check valve 251 and a discharge side check valve 255, and the action of the pump distribution valve 250 controls the suction and discharge of hydraulic oil. This pump distribution valve 250 is the same as the pump distribution valve 130 of the transmission TM2 according to the second embodiment shown in FIG. 8, and therefore its explanation is omitted.

In this way, the hydraulic oil discharged from the pump cylinder 216 is sent to the motor distribution valve 240 via the pump distribution valve 250. The motor distribution valve 240 is the same as the motor distribution valve 40 used in the transmission TM3 according to the first embodiment shown in FIG. 2, and has a motor valve spool 241 reciprocated by a motor valve cam 249. As a result, the oil discharged from the pump cylinder 216 is supplied into the motor cylinder 226 in the suction stroke.

As shown in FIG. 12, the motor cylinder 226 is disposed on the same plane as the pump cylinder 216 and is swingably supported by the left and right casings 201 and 202 in the trunnion portion 226b. . The cylinder hole 226a of the motor cylinder 226 is open to the inner peripheral side and communicates with a communication hole 226c formed in the trunnion portion 226b. This cylinder hole 2
A motor plunger 225 is slidably inserted into the motor 26a, and an inner end portion 225a of the motor plunger 225 is connected to a crank shaft 225a of a motor crank member 222.

The motor crank member 222 is composed of a member integrally having a second motor drive gear 222a and a crank shaft 222b, and a support member 222c into which the crank shaft 222b is press-fitted and coupled. The motor crank member 222 includes left and right bearings 224a, 224.
It is rotatably supported by the left and right casings 201, 201 via b. The second motor drive gear 222a is
It meshes with a first motor drive gear 221b formed integrally with the motor shaft 221. For this reason, the oil discharged from the pump cylinder 215 causes the motor plunger 225 to
When the motor crank member 222 is rotationally driven, this rotation causes the first and second motor drive gears 22 to rotate.
It is transmitted to the motor shaft 221 via 2a and 221b, and the motor shaft 221 is driven.

In the fourth embodiment, the pump shaft (input shaft) 211 is driven to transmit the power to the motor shaft (output shaft) 221, but the pump and the motor are rotated in reverse to drive the motor shaft 221. May be used as a pump shaft to drive the shaft 221, and the pump shaft 211 may be used as a motor shaft to take out power from the shaft 211.

Next, regarding the radial plunger type hydraulic transmission TM5 according to the fifth embodiment of the present invention,
This will be described with reference to FIGS. This transmission TM5 is different from the transmission TM4 according to the fourth embodiment shown in FIGS. 10 and 11 only in the pump driving mechanism and the like, and other configurations are the same. Therefore, the same parts are designated by the same reference numerals. The description is omitted.

In this transmission TM5, the right end portion 311a of the pump shaft 311 projects into the insertion hole 321a of the motor shaft 321, and the bearings 306a arranged between the shafts 311 and 321 are provided.
Relative rotation is possible via 306b. A protrusion 311b is formed in the middle of the pump shaft 311, and an outer peripheral surface of the protrusion 311b is formed in a shape eccentric from the rotation axis C1 of the pump shaft 311 by a distance L1 as shown in FIG. .

An eccentric collar 312 is rotatably mounted on the outer circumference of the protrusion 311b. The outer peripheral surface of the eccentric collar 312 is eccentric by a distance L2 from the axis C2 of the outer peripheral surface of the protrusion 311b,
The axis C3 is separated from the axis C2 by a distance L2.

The internal gear 3 is provided on the left side surface of the eccentric collar 312.
12a is formed, and this is the stroke adjusting mechanism 2
Connection collar 33 connected to the second sun gear 237 of 30
No. 8 external gear 338a is meshed. That is, also in the transmission TM5 of this example, the eccentric collar 3
12 is connected to a pump shaft 311 via a stroke adjusting mechanism 230. Therefore, the eccentric collar 3
12 rotates integrally with the pump shaft 311. The stroke adjusting mechanism 230 is the same as that described above, and by rotating the stroke adjusting gear 239, the eccentric amount of the shaft center C3 of the outer peripheral surface of the eccentric collar 312 can be variably adjusted.

A connecting ring 313 is rotatably mounted on the eccentric collar 312. The pump plunger 3 is connected to the connecting ring 313 via the connecting pin 313a.
The inner ends 315a of 15 are connected. In this example, 5
The individual pump plungers 315, as shown in FIG.
The pump plungers 315 are radially arranged at equal intervals, and the pump plungers 315 are slidably inserted into the cylinder holes 216 a of the pump cylinder 216.

When the pump shaft 311 is rotationally driven here, the eccentric collar 312 rotates integrally therewith, and the connecting ring 31 rotatably mounted on the eccentric collar 312.
The eccentric collar 312 makes an orbital motion, and the pump plunger 315 connected to the connecting ring 313 reciprocates in the pump cylinder 216. During this revolving movement, the connecting ring 313 does not rotate, but its axis C3 (the axis of the connecting ring 313 is an eccentric collar 312).
Of the pump shaft 31)
It is necessary to revolve around the first rotation axis C1.

In order to perform such an orbital movement, the transmission TM5 is provided with a mechanism called a double mechanism. The double mechanism includes a first internal gear 361 fixed to the left casing 202, an external gear 362 rotatably mounted on a side portion of the eccentric collar 312, and an integral structure on the left side surface of the connecting ring 313. It is composed of the formed second internal gear 363. As shown, the first internal gear 361 and the external gear 362 mesh with each other,
The external gear 362 and the second internal gear 363 mesh with each other,
The first internal gear 361 and the second internal gear 363 have the same number of teeth. Further, the first internal gear 361 is connected to the pump shaft 31.
1 is arranged so as to be concentric with the rotating shaft C1, and the external gear 362 is arranged so as to be concentric with the axial center C2 of the outer peripheral surface of the protruding portion 311b. Are arranged so as to be concentric with the axis C3 of the outer peripheral surface of the eccentric collar 312.

By using the double mechanism constructed as above, when the eccentric collar 312 is rotated together with the pump shaft 311, the connecting ring 313 can be revolved around the rotation axis C1 without rotating. . For the detailed operation of the double mechanism, see Japanese Patent Laid-Open No. 4-2.
Since it is disclosed in Japanese Patent No. 62158 and is publicly known, its explanation is omitted.

In the fifth embodiment, the pump shaft (input shaft) 311 is driven to transmit the power to the motor shaft (output shaft) 321, but the pump and the motor are rotated in reverse to drive the motor shaft 321. May be used as a pump shaft to drive the shaft 321, and the pump shaft 311 may be used as a motor shaft to take out power from the shaft 311.

Next, regarding the radial plunger type hydraulic transmission TM6 according to the sixth embodiment of the present invention,
This will be described with reference to FIG. This transmission T
M6 is the transmission TM according to the fifth embodiment.
5, a power transmission planetary gear mechanism 450 is added. Therefore, only the configuration different from the transmission TM5, that is, the configuration of the power transmission planetary gear mechanism 450 and its peripheral portion will be described.

The power transmission planetary gear mechanism 450 includes a sun gear 451 integrally formed with a right end portion of a pump shaft 411 which also serves as an input shaft, and a sun gear 45.
1, a planetary pinion 453 that meshes with the carrier 1, and a carrier 452 that rotatably holds the planetary pinion 453.
And the ring gear 4 that meshes with the planetary pinion 453.
And 54. The carrier 452 has an output shaft 455.
The external gear 454a formed on the outer circumference of the ring gear 454 meshes with the second motor drive gear 222a of the motor crank member 222. Therefore, in this example, the ring gear 454 is used as the motor shaft.

In this transmission TM6, when the pump shaft 411 is driven, the rotation of the pump shaft 411 is transmitted to the pump plunger 315 via the connecting ring 313. Then, similarly to the above-described example, the motor plunger 225 is reciprocated by the oil discharged from the pump cylinder 216, and the motor crank member 222 is rotationally driven. In this example, the rotation of the motor crank member 222 is caused by the power transmission planetary gear mechanism 450.
Of the ring gear 454.

Further, in this example, the rotation of the pump shaft 411 is rotated by the coupling ring 313.
5 is also transmitted to the sun gear 451 of the power transmission planetary gear mechanism 450. For this reason,
The output shaft 455 is driven by receiving the driving force from the motor crank member 222 and the driving force of the pump shaft 411, so that efficient power transmission can be performed.

In the sixth embodiment, the pump shaft (input shaft) 411 is driven to output the output shaft 455.
Although it has been described that the power is transmitted to the pump shaft 411, the pump and the motor are reversed and the output shaft 455 is used as the input shaft to drive the shaft 455 and
May be used as an output shaft to take out power from the shaft 411.

[0087]

As described above, the radial plunger type fluid transmission according to the present invention rotatably supports the pump shaft and the motor shaft which are coaxial and relatively rotatable with each other by the casing, and the shafts of the pump and the motor shaft. The pump cylinders and motor cylinders are arranged in a radial pattern extending from the shaft center of both shafts on the same plane perpendicular to the center, and they are mounted on the casing, and slide in the cylinder holes of each pump cylinder and motor cylinder. Freely insert the pump plunger and motor plunger respectively, and transmit the rotation of the pump shaft to each pump plunger via the pump side motion conversion mechanism, and reciprocate this in the cylinder hole of each pump cylinder to make the motor side movement. Each motor series through the conversion mechanism The reciprocation of the motor plungers in a Da of the cylinder bore is configured to convert the rotational motion of the motor shaft.

When the pump cylinders and the motor cylinders are thus radially arranged side by side on substantially the same plane perpendicular to the shaft centers of both shafts, the axial dimension of the transmission is shortened and the transmission is made compact. , Can be made compact. Further, it is easy to shorten the oil passage connecting the pump cylinder and the motor cylinder, and it is possible to reduce the pressure loss and improve the power transmission efficiency of the transmission.

At least one of the pump-side motion converting mechanism and the motor-side motion converting mechanism is supported by the first gear fixed coaxially on the pump shaft or the motor shaft and the casing so as to be rotatable relative to the first gear. A second gear that meshes with the first gear and a crank pin that is integrally formed with the second gear at a position eccentric from the rotation axis of the second gear are used to connect the pump plunger or the motor plunger to the crank pin. Desirable,
By doing so, the transmission can be made more compact.

Further, a sun gear arranged coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and a sun gear that rotatably supports the planetary pinion. A planetary gear set including a carrier that rotates on the same axis and a ring gear that has inner teeth that mesh with the planetary pinion and that rotates on the same axis as the sun gear is provided. Alternatively, an output shaft may be provided separately from the above, and the sun gear, the ring gear, and the carrier that form the planetary gear set may be connected to any of the input shaft, the motor shaft, and the output shaft to form a transmission. With this configuration, a transmission having higher power transmission efficiency can be obtained.

In this case, the pump shaft and the input shaft are integrally formed, and the sun gear is connected to the input shaft,
Preferably, the ring gear is connected to the motor shaft and the carrier is connected to the output shaft. Further, it is preferable that the planetary gear set is disposed on substantially the same plane as the plane on which the pump cylinder and the motor cylinder are disposed. By doing so, the transmission can be made more compact.

Further, the pump-side motion converting mechanism and the motor-side motion converting mechanism are respectively rotatable relative to the casing and the first pump driving gear and the first motor driving gear fixedly mounted coaxially on the pump shaft and the motor shaft. A second pump drive gear that is supported by the first pump drive gear and meshes with the first pump drive gear; a pump crankpin integrally formed with the second pump drive gear at a position eccentric from the rotation axis of the second pump drive gear; A second motor drive gear that is rotatably supported by the second motor drive gear and that meshes with the first motor drive gear, and a motor integrally formed with the second motor drive gear at a position eccentric from the rotation axis of the second motor drive gear. It consists of a crank pin, and connects the pump plunger and pump crank pin, and The first pump drive gear is integrally formed with the pump shaft by connecting with the crank pin, the ring gear is used as a motor shaft, and the external gear formed on the outer periphery of the ring gear is used as the first motor drive gear to form a second motor drive gear. It is preferably configured to mesh with the motor drive gear.

On the other hand, an eccentric portion having an axis eccentric to the rotation shaft is provided on either one of the pump shaft and the motor shaft, and the motion converting mechanism causes the crank motion of this eccentric portion to occur on either one of the pump plunger and the motor plunger. The transmission can also be configured to convert to reciprocating motion. In this way, the mechanism for reciprocating the pump or the motor plunger can be simplified.

In this case, an eccentric collar having an outer peripheral surface eccentric from the axis of the eccentric portion is rotatably mounted on the eccentric portion, and an annular guide ring is rotatably mounted on the eccentric collar to provide a pump plunger and a motor. A stroke adjustment mechanism that adjusts the rotational position of the eccentric collar on the eccentric part by variably adjusting the eccentric amount of the shaft center of the outer peripheral surface of the eccentric collar. Is preferably provided. With this configuration, the reciprocating stroke of the pump or the motor plunger can be adjusted with a simple mechanism.

In place of the annular guide ring, an annular connecting ring is rotatably mounted on the eccentric collar, and one of the inner ends of the pump plunger and the motor plunger is pivotally supported on this connecting ring to attach the stroke. An adjusting mechanism and a double mechanism for revolving the connecting ring without rotating may be provided. Even with this configuration, the reciprocating stroke of the plunger can be adjusted with a simple mechanism.

[Brief description of drawings]

FIG. 1 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to a first embodiment of the present invention.

FIG. 2 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to the first embodiment of the present invention.

FIG. 3 is a sectional view showing an arrangement of cylinders and plungers in the radial plunger type hydraulic transmission according to the first embodiment of the present invention.

FIG. 4 is a cross-sectional view showing an array of pump distribution valves and motor distribution valves in the radial plunger hydraulic transmission according to the first embodiment of the present invention, and their configurations.

FIG. 5 is a cross-sectional view showing a configuration of a shift control valve mechanism in the radial plunger type hydraulic transmission according to the first embodiment of the present invention.

FIG. 6 is a cross-sectional view showing the shape of a timing cam of a valve timing mechanism that constitutes this shift control valve mechanism.

FIG. 7 is a graph showing changes in the amount of oil discharged from a pump cylinder controlled by the shift control valve mechanism.

FIG. 8 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to a second embodiment of the present invention.

FIG. 9 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to a third embodiment of the present invention.

FIG. 10 is a sectional view showing the configuration of a radial plunger hydraulic transmission according to a fourth embodiment of the present invention.

FIG. 11 is a sectional view showing the configuration of a radial plunger hydraulic transmission according to a fourth embodiment of the present invention.

FIG. 12 is a cross-sectional view showing an arrangement of cylinders and plungers in a radial plunger type hydraulic transmission according to a fourth embodiment of the present invention.

FIG. 13 is a schematic view showing a positional relationship between a rotary shaft of a pump shaft, an axial center of an outer peripheral surface of a pump shaft right end portion and an axial center of an outer peripheral surface of an eccentric collar in a radial plunger hydraulic transmission according to a fourth embodiment of the present invention. It is a figure.

FIG. 14 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to a fifth embodiment of the present invention.

FIG. 15 is a sectional view showing a configuration of a radial plunger type hydraulic transmission according to a fifth embodiment of the present invention.

FIG. 16 is a sectional view showing an arrangement of cylinders and plungers in a radial plunger hydraulic transmission according to a fifth embodiment of the present invention.

FIG. 17 is a sectional view showing a configuration of a radial plunger hydraulic transmission according to a sixth embodiment of the present invention.

[Explanation of symbols]

 1, 2 Casing 3, 4 Cover 11 Pump shaft 12, 22 Crank member 15, 25 Plunger 16, 26 Cylinder 21 Motor shaft 30 Pump distribution valve 40 Motor distribution valve 50 Gear shift control valve mechanism 60 Timing mechanism

Claims (19)

[Claims] 1. A casing, a pump shaft rotatably supported by the casing, a motor shaft coaxially disposed with the pump shaft, and rotatably supported by the casing, and a pump and A plurality of pump cylinders arranged radially on the plane perpendicular to the axis of the motor shaft and extending from the axis, and attached to the casing, and slidably inserted into the cylinder holes of each pump cylinder. A plurality of pump plungers, and a plurality of motor cylinders mounted on the casing in a radial arrangement extending from the axis on a plane parallel to the plane that is the same as or close to the plane. A plurality of motor plungers slidably inserted in the cylinder holes of each motor cylinder, A pump-side motion conversion mechanism that converts the rotational motion of the pump shaft into the reciprocating motion of the pump plunger in the cylinder hole of each pump cylinder, and the reciprocating motion of each of the motor plungers in the cylinder hole of each motor cylinder. A radial plunger type fluid transmission, comprising: a motor-side motion conversion mechanism that converts motion into rotational motion of the motor shaft. 2. The pump shaft and the motor shaft overlap each other in the axial direction so that one end of the pump shaft and the motor shaft which face each other enter into the inside of the other, and at this overlap part, the pump shaft and the motor shaft are overlapped. 2. The radial plunger type fluid transmission according to claim 1, wherein the shafts are rotatably supported relative to each other by a bearing disposed therebetween. 3. A pair of bearings are axially spaced apart from each other in the overlap portion, and one of the pair of bearings rotatably supports the pump shaft and the motor shaft in the casing. The radial plunger type fluid transmission according to claim 2, wherein the radial plunger type fluid transmission is arranged at a position that substantially overlaps with one of the bearings to be axially moved. 4. At least one of the pump-side motion converting mechanism and the motor-side motion converting mechanism is rotatable relative to a first gear coaxially fixed to the pump shaft or the motor shaft and the casing. A second gear that is supported and meshes with the first gear; and a crankpin integrally formed with the second gear at a position eccentric from the rotation shaft of the second gear, and the pump plunger or the motor The plunger and the crank pin are connected to each other, which is characterized in that
Radial plunger type fluid transmission according to any one of 1. 5. A sun gear disposed coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and the planetary pinion is rotatably supported. A carrier rotating coaxially with the sun gear, and a planetary gear set including a ring gear having internal teeth meshing with the planetary pinion and rotating coaxially with the sun gear, and an input shaft connected to the pump shaft. An output shaft that is separate from the pump shaft and the motor shaft, and the sun gear, the ring gear, and the carrier that form the planetary gear set are connected to any of the input shaft, the motor shaft, and the output shaft. Is characterized by Radial plunger fluid transmission according to claim 1. 6. The pump shaft and the input shaft are integrally formed, the sun gear is connected to the input shaft, the ring gear is connected to the motor shaft, and the carrier is connected to the output shaft. The radial plunger type fluid transmission according to claim 5, wherein 7. A sun gear disposed coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and rotatably supports the planetary pinion. A carrier that rotates coaxially with the sun gear, and a planetary gear set that includes a ring gear that has internal teeth that mesh with the planetary pinion and that rotates coaxially with the sun gear, and the pump shaft and the motor shaft are Having a separate input shaft and an output shaft connected to the motor shaft, the sun gear, the ring gear and the carrier constituting the planetary gear set are respectively connected to one of the input shaft, the pump shaft and the output shaft. Is characterized by Radial plunger fluid transmission according to claim 1. 8. The motor shaft and the output shaft are integrally formed, the sun gear is connected to the output shaft, the ring gear is connected to the pump shaft, and the carrier is connected to the input shaft. The radial plunger fluid transmission according to claim 7, wherein the radial plunger fluid transmission is provided. 9. The planetary gear set is disposed so as to be located substantially on the same plane as the plane on which the pump cylinder and the motor cylinder are disposed. Radial plunger type fluid transmission according to Crab. 10. A pump-side motion conversion mechanism and a motor-side motion conversion mechanism, respectively, a first pump drive gear and a first motor drive gear fixed coaxially on the pump shaft and the motor shaft, respectively. A second pump drive gear which is rotatably supported by the casing and meshes with the first pump drive gear;
A pump crankpin integrally formed with the second pump drive gear at a position eccentric from the rotation axis of the pump drive gear, and a second motor rotatably supported by the casing and meshing with the first motor drive gear. A drive gear and a motor crankpin integrally formed with the second motor drive gear at a position eccentric from the rotation shaft of the second motor drive gear are provided, and the pump plunger and the pump crankpin are connected to each other. The motor plunger and the motor crankpin are connected, the first pump drive gear is formed integrally with the pump shaft, the ring gear is used as the motor shaft, and is formed on the outer periphery of the ring gear. An external gear is used as the first motor drive gear, and the second motor is used. The radial plunger type fluid transmission according to claim 9, which is configured to mesh with a drive gear. 11. A first pump drive gear and a first motor drive gear, wherein the pump-side motion conversion mechanism and the motor-side motion conversion mechanism are coaxially fixed on the pump shaft and the motor shaft, respectively, and A second pump drive gear which is rotatably supported by the casing and meshes with the first pump drive gear;
A pump crankpin integrally formed with the second pump drive gear at a position eccentric from the rotation axis of the pump drive gear, and a second motor rotatably supported by the casing and meshing with the first motor drive gear. A drive gear and a motor crankpin integrally formed with the second motor drive gear at a position eccentric from the rotation shaft of the second motor drive gear are provided, and the pump plunger and the pump crankpin are connected to each other. The motor plunger and the motor crankpin are connected, the first motor drive gear is formed integrally with the motor shaft, the ring gear is used as the pump shaft, and is formed on the outer periphery of the ring gear. An external gear is used as the first pump drive gear and the second pump is used. The radial plunger type fluid transmission according to claim 9, which is configured to mesh with a drive gear. 12. An eccentric portion having an axis eccentric from a rotation shaft of the pump shaft or the motor shaft is provided, and the motion conversion mechanism causes the crank motion of the eccentric portion to occur in the pump plunger and the motor plunger. The radial plunger type fluid transmission according to claim 1, characterized in that the fluid is converted into either one of the reciprocating motions. 13. An eccentric collar having an outer peripheral surface eccentric from the shaft of the eccentric portion is rotatably mounted on the eccentric portion, and an annular guide ring is rotatably mounted on the eccentric collar. One of the inner ends of the motor plunger is slidably attached to the guide ring, and the rotational position of the eccentric collar is variably adjusted on the eccentric portion to change the eccentric amount of the axial center of the outer peripheral surface of the eccentric collar. The stroke adjusting mechanism for adjusting is provided.
2. The radial plunger type fluid transmission according to 2. 14. An eccentric collar having an outer peripheral surface eccentric from the axis of the eccentric portion is rotatably mounted on the eccentric portion, and an annular connecting ring is rotatably mounted on the eccentric collar, and the pump plunger and One of the inner ends of the motor plungers is pivotally attached to the connecting ring, and the rotational position of the eccentric collar is variably adjusted on the eccentric portion to change the eccentric amount of the axial center of the outer peripheral surface of the eccentric collar. The radial plunger type fluid transmission according to claim 12, wherein a stroke adjusting mechanism for adjusting and a double mechanism for revolving the connecting ring without rotating are provided. 15. A sun gear disposed coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and the planetary pinion is rotatably supported. A carrier that rotates coaxially with the sun gear, and a planetary gear set including a ring gear that has internal teeth that mesh with the planetary pinion and that rotates coaxially with the sun gear, and an input shaft that is connected to the pump shaft. An output shaft that is separate from the pump shaft and the motor shaft, and the sun gear, the ring gear, and the carrier that form the planetary gear set are respectively connected to the input shaft, the motor shaft, and the output shaft. Characterized by being That claim 12-1
4. The radial plunger type fluid transmission according to any one of 4 above. 16. The pump shaft and the input shaft are integrally formed, the sun gear is connected to the input shaft, the ring gear is connected to the motor shaft, and the carrier is connected to the output shaft. 16. The radial plunger type fluid transmission according to claim 15, wherein: 17. A sun gear disposed coaxially with the pump shaft and the motor shaft, a planetary pinion that meshes with the sun gear and revolves around the sun gear, and the planetary pinion is rotatably supported. A carrier that rotates coaxially with the sun gear, and a planetary gear set that includes a ring gear that has internal teeth that mesh with the planetary pinion and that rotates coaxially with the sun gear, and the pump shaft and the motor shaft are Having a separate input shaft and an output shaft connected to the motor shaft, the sun gear, the ring gear and the carrier constituting the planetary gear set are respectively connected to the input shaft, the pump shaft and the output shaft. Characterized by being That claim 12-1
4. The radial plunger type fluid transmission according to any one of 4 above. 18. The pump shaft and the input shaft are integrally formed, the sun gear is connected to the input shaft, the ring gear is connected to the motor shaft, and the carrier is connected to the output shaft. 18. The radial plunger type fluid transmission according to claim 17, characterized in that: 19. The planetary gear set is arranged so as to be located substantially on the same plane as the plane on which the pump cylinder and the motor cylinder are arranged. Radial plunger type fluid transmission according to Crab.