JPH0781618B2 - Radial plunger type fluid transmission - Google Patents

Description

Description: BACKGROUND OF THE INVENTION The present invention relates to a cylinder and a plan.
The jar extends radially (radially) around the shaft.
It consists of a fluid pump and a fluid motor that are installed together.
Related to radial plunger type fluid transmission
To do. 2. Description of the Related Art Such a radial plunger type fluid
It consists of pumps, fluid motors, and combinations of these.
Conventional fluid transmissions have been widely used
It For example, JP-A-3-37465 and JP-A-3-37465.
No. 103646, Japanese Patent Laid-Open No. 4-262158, etc.
There is one disclosed in. A radial plunger type
Radial plan by combining pump and motor
Ja-type fluid transmission can be configured
Conventionally, however, the fluid pump and the fluid motor were arranged in parallel.
Was arranged in the fluid transmission. Therefore, the conventional radio
In the case of Alplunger type fluid transmission,
Its axial length should be at least the fluid pump and fluid model.
The total length of each axis is
The directional length becomes large, and the transmission is small and compact.
There was a problem that it was difficult to configure compactly. It
Moreover, in conventional transmissions, from the fluid pump
Supply discharge fluid (oil) to the adjacent fluid motor
The length of the oil passage tends to be long and pressure loss in this oil passage, etc.
As a result, the power transmission efficiency of the transmission may decrease.
There was a problem of rinsing. The present invention has been made in view of these problems.
Easy to make small and compact, and high transmission efficiency
Providing a radial plunger type fluid transmission
The purpose is to do. Means and Actions for Solving the Problems Such eyes
Radial plunger type fluid according to the present invention
The transmissions are coaxial with each other and relatively rotatable.
Pump shaft and motor shaft by casing
These pumps and motor shafts are rotatably supported.
Of both shafts on the same plane perpendicular to the axis of
Pump pumps radiating from the axis and lined up in the circumferential direction
And arrange the cylinder and motor cylinder
Mounted on the casing, each of these pump cylinders and
Slide the motor into the cylinder holes of the motor cylinders.
Pump plunger and motor plunger, insert the pump
The rotation of the pump shaft is controlled by the side motion conversion mechanism.
To the plunger and transfer this to the cylinder of each pump cylinder.
Reciprocating motion in the hole, and through the motor side motion conversion mechanism
Each motor plan in the cylinder hole of each motor cylinder
Converts the reciprocating motion of the Ja to the rotary motion of the motor shaft
Is configured. As described above, the pump cylinder and the motor system are
Place the Lindner on the same plane, which is perpendicular to the shaft center of both shafts.
If they are arranged radially on the surface and lined up in the circumferential direction,
Then, both cylinders should be lined up in the circumferential direction on this plane in the axial direction.
When both cylinders are installed so that they overlap each other,
The axial dimension required for
The axial dimension of the transmission is shortened
To make this transmission smaller and more compact
can do. In addition, this allows the pump cylinder
And the motor cylinder can be installed close to each other.
The oil passage connecting the pump cylinder and the motor cylinder
Therefore, the pressure loss is reduced and the transmission
The power transmission efficiency of the option can be improved. In this case, the pump shaft and the motor
Of the shaft ends facing each other, one inside the other
As it enters, it overlaps in the axial direction,
It is placed between both shafts at this overlap.
Bearings rotate both shafts relative to each other
It is good to construct so that they can freely support each other. Special in this case
A pair of bearings axially separated from each other
The bearings on one side are
The shaft and motor shaft are rotatably supported.
Arranged in a position that overlaps with one of the rings in the axial direction,
It is preferable from the viewpoint of strength. Pump side motion conversion mechanism and motor side motion
At least one of the conversion mechanisms is a pump shaft or
The first gear fixed coaxially on the motor shaft and the case
The first gear is supported while being rotatably supported by the single
Eccentric from the meshing second gear and the rotation shaft of this second gear
Crank pin integrally formed with the second gear at
Pump plunger or motor plunger
It is desirable to connect the crank pin to the crank pin. like this
If this is done, the transmission can be made more compact.
It Further, a pump side motion conversion mechanism and a motor
The side motion conversion mechanism is connected to the pump shaft and motor, respectively.
The first pump drive gear fixed coaxially on the shaft.
And the first motor drive gear and the casing can rotate relative to each other
Is supported by the first pump drive gear and meshes with the first pump drive gear.
Two pump drive gears and the rotating shaft of this second pump drive gear
Is formed integrally with the second pump drive gear at a position eccentric from
The pump crankpin and the casing can rotate relative to each other
Is supported by the first motor drive gear and meshes with the first motor drive gear.
Two-motor drive gear and rotation shaft of this second-motor drive gear
Is integrally formed with the second motor drive gear at a position eccentric from
Motor crank pin and pump plunge
The motor and the pump crankpin, and
Connect the plunger and the motor crank pin, and
Drive gear integrally with the pump shaft, and
This ring is used as a motor shaft
The external gear formed on the outer circumference of the gear is the first motor drive gear.
Configured to mesh with the second motor drive gear
Preferably. Further, the pump shaft and the motor shuff
The sun gear arranged coaxially with the
Planetaripi that revolves around this sun gear
Nion and this planetary pinion are supported for rotation.
Carrier that rotates coaxially with the gear, and planetary pini
It has internal teeth that mesh with ON and rotates on the same axis as the sun gear.
A planetary gear set consisting of a rotating ring gear is installed.
Connect the pump shaft and the input shaft, and
Separate output shaft and motor shaft from output shaft
Is installed to configure the planetary gear set.
Input gear and carrier respectively
Data shaft or output shaft
The transmission can also be configured. like this
The transmission with higher power transmission efficiency
Can be obtained. In this case, the pump shaft and the input shuffle
And the sun gear are connected to the input shaft,
Output the carrier by connecting the ring gear to the motor shaft
It is preferably connected to the shaft. In addition, this planet
Install the tally gear set into the pump cylinder and motor cylinder.
Placed on the same plane as the plane
Is preferred. This way, the transmission
It can be made more compact. On the other hand, the pump shaft and the motor shuff
Has a shaft that is eccentric from its rotation axis
An eccentric part is provided, and the eccentric part is
Motion to the pump plunger and motor plunger.
Transmit or reciprocate by converting to either reciprocating motion.
The session can also be configured. If you do this
A mechanism for reciprocating the pump or motor plunger.
Can be easy. In this case, the shaft of this eccentric part is placed on the eccentric part.
An eccentric collar with an eccentric outer peripheral surface is rotatably mounted
A ring guide ring on the eccentric collar.
Mounted on site, pump plunger and motor plunge
Slide one of the inner ends onto the guide ring.
Mounting and variably adjusting the rotational position of the eccentric collar on the eccentric part.
Adjust the eccentric amount of the shaft center of the outer peripheral surface of the eccentric collar.
It is preferable to provide a trowel adjusting mechanism. Do this
Then, the reciprocating straw of the pump or motor plunger
Adjustment can be performed with a simple mechanism. Incidentally, instead of the annular guide ring, an annular connecting ring is used.
Attach the tie ring rotatably on the eccentric collar and
Either the plunger or the motor plunger
Attach the inner end by pivoting it to this connecting ring
Adjustment mechanism and connecting ring that revolves without rotating.
A bull mechanism may be provided. Even with this configuration,
Adjusting the reciprocating stroke of the ranger with a simple mechanism
You can Preferred embodiments of the present invention will now be described with reference to the drawings.
An example will be described. Radius according to the first embodiment of the present invention
Fig. 1 shows the plunger type hydraulic transmission TM1.
And shown in FIG. Fig. 1 shows the pump plunger.
FIG. 2 is a half cross-sectional view showing a part, and FIG.
FIG. This transmission TM1
Is a bolt-connected right casing 1 and a left casing
Mounted on the side of the right casing 1
Installed by covering the right cover 3 and the side surface of the left casing 2.
And the left cover 4 that has been opened. At the center of the right and left casings 1, 2,
The pump shaft 11 is supported by the rings 5a and 5b.
And the motor shaft 21 are coaxially and rotatably arranged.
Has been. The left end 11c of the pump shaft 11 has a left cover.
It protrudes outward from 4 and is driven through this part.
It is supposed to be. That is, the pump shaft 11
Also serves as the input shaft. Motor shaft 21 is right end
The part 21c projects outward from the right cover 3, and from this part
The output is taken out, and the motor shaft 21
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 rushes into this insertion hole 11a, and at this portion
Both shafts 11 and 21 overlap. That
Both shafts 11 and 2 in this overlap portion
A pair of left and right bearings 6a and 6b are disposed between the
This ensures that both shafts 11 and 21 are in phase with each other.
It can rotate freely. Both shafts 11 and 21
The axial load acting on the bearings is also generated on these bearings 6a and 6b.
In this example, the bearing 6a on the left side is
The motor shaft 11 is rotatably supported with respect to the thing 2.
It is arranged so as to axially overlap the bearing 5a
It This will reduce the load on the bearing 6a.
And is advantageous in 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
ing. The first pump drive gear 11b and the first pump drive gear 11b
1 The motor drive gear 21b and the surrounding so as to radially,
Four pump cranks at equal intervals and alternately
The member 12 and the motor crank member 22 are as shown in FIG.
It is installed in. The pump crank member 12 includes a pair of left and right bearings.
The left and right casings 1 and 2 via the rings 14a and 14b.
It is rotatably supported. Pump crank member 12
Is a second pump drive gear 12a coaxial with the rotation axis thereof,
With the pump crankshaft 12b eccentric from the rotating shaft
And the second pump drive gear 12a is the first pump drive
It meshes with the gear 11b. Therefore, the homp shaft 11
Is driven to rotate, the pump crank member 12 is driven to rotate.
Be moved. At this time, the pump crankshaft 12b is eccentric
Since the pump crank member 12 rotates,
The crankshaft 12b is the rotation shaft of the pump crank member 12.
Revolves around. In addition, this pump crank member
12 is a second pump drive gear 12a and a pump clan
And a member that integrally includes the shaft 12b and the pump clan.
A support member 12c into which the shaft 12b is press-fitted and joined.
It is composed of On the other hand, the motor crank member 22 is
The left and right casings 1, via the bearings 24a, 24b
A second shaft that is rotatably supported by 2 and that is coaxial with its rotation axis.
The motor drive gear 22a and the motor drive eccentric from the rotary shaft
It has a rank axis 22b. Second motor drive gear 2
Since 2a meshes with the first motor drive gear 21b,
When the crank member 22 is rotationally driven, the motor shuffle
21 is driven to rotate. This motor crank part
The material 22 includes the second motor drive gear 22a and the motor clutch.
A member integrally including the crankshaft 22b and the motor clutch.
And a support member 22c into which the link shaft 22b is press-fitted and coupled.
Composed of. First pump drive gear 11b and first motor drive
Passes through the axially intermediate portion of the dynamic gear 21b, the pump and the motor
Located on a plane perpendicular to the shafts 11 and 21, 4 each
Each pump cylinder 16 and motor cylinder 26
They are arranged alternately and at equal intervals as shown in FIG.
As shown in FIGS. 1 and 2, both cylinders 16 and 26 are
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. Each cylinder 16, 26 is opened radially inward.
Cylinder holes 16a and 26a that are opened are formed.
Pump cylinders 16a and 26a from the inside in the radial direction.
Plunger portion 15a of runner 15 and motor plan
The plunger portion 25a of the jar 25 is slidably inserted
There is. Both cylinders 16 and 26 have corresponding pom
Diameter of the crank crank member 12 and the motor crank member 22
It is located outside in the direction of
Plungers 15 and 2 inserted in the solder holes 16a and 26a
Crank member 1 to which inner ends 15b and 25b of 5 correspond
2,22 crank pins 12b and 22b are pivotally supported
It Here, as described above, the pump crank portion
When the material 12 is rotated, the pump crank is eccentric from its rotation axis.
Since the rank shaft 12b revolves around this rotation axis,
Connected to the pump crankshaft 12b of the vehicle
Plunger 15 swings pump cylinder 16
While reciprocating, it reciprocates in the cylinder hole 16a. Similarly,
The motor plunger 25 is a cylinder of the motor cylinder 26.
When reciprocating in the hole 26a, the motor crankshaft 22
b is revolved and the motor crank member 22 is rotated.
It Trunnion portion 16 of each pump cylinder 16
A communication hole 16c communicating with the cylinder hole 16a is formed in b.
Similarly, the tranny of each motor cylinder 26 is
The communication hole 26 that communicates with the cylinder hole 26a
c is formed. These communication holes 16c and 26c are
Oil passages 1a and 1b formed in the right casing 1 respectively
Corresponding pump distribution valve 30 and motor
It communicates with the distribution valve 40. Therefore, it is also shown in FIG.
The pump distribution valve 30 to the pump cylinder 16
Correspondingly four are arranged, the motor distribution valve 40 is a motor
Four cylinders are provided corresponding to the 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
Inside the pump valve spool 31 slidably arranged
Have. The valve hole 35 has a corresponding pump.
The oil passage 1a communicating with the cylinder hole 16a of the cylinder 16 is
It is open. The outer end of this pump valve spool 31
It is pressed inward by the spring 32, and the inner end 31b is
The pump connected to the pump crank member 12
It contacts the outer peripheral surface 39 a of the valve cam 39. this
The outer peripheral surface 39a of the cam 39 is a diaper as shown in FIG.
It has a snake-like shape, and with the pump crank member 12
When the pump valve cam 39 is rotated to the outer peripheral surface 3
Pump valve spool 31 is pushed by 9a
It reciprocates in the valve hole 35. When the pump crank member 12 rotates,
Pump plan connected via pump crankshaft 12b
The jar 15 fits inside the cylinder hole 16a of the pump cylinder 16.
Since it reciprocates, the pump valve spool 31 moves forward and backward.
The return movement is synchronized with the reciprocating movement of the pump plunger 15.
The outer peripheral surface 39a of the pump valve cam 39 is a pump clamp.
The pump plunger 15 moves downward in accordance with the rotation of the crank member 12.
In the process of moving from dead center to top dead center (discharging process
The spool 31 by the biasing force of the spring 32.
Push down (move inward), while pump plunger
When 15 is in the process of moving from top dead center to bottom dead center
(When in the suction stroke)
Push up against the bias (move outward). As a result, the pump plunger 15 discharges.
When in the stroke, through the groove 31a of the spool 31
The oil passage 1a and the discharge oil passage 37 communicate with each other, and the pump plunger
15 is pushed out from the inside of the cylinder hole 16a according to the movement of
The operating oil coming out is discharged through the communication hole 16c and the oil passage 1a.
It is sent to the oil outlet 37. Then, the check valve 33
It is pushed open and supplied to the communication oil passage 38. This connecting oil passage 3
8 is formed through the inside of the casing (however,
(Not shown), communicating with the oil supply passage 47 of the motor distribution valve 40
And discharge from the pump cylinder 16 as described above.
The supplied hydraulic oil is supplied from the connecting oil passage 38 to the supply oil passage 47.
Supplied. On the other hand, the pump plunger 15 is in the suction stroke.
At some time, the oil passage 1 is passed through the groove 31a of the spool 31.
a and the first return oil passage 36 communicate with each other, and
The returned hydraulic oil responds to the movement of the pump plunger 15.
Then, it is sucked into the cylinder hole 16a. The motor distribution valve 40 is provided in the right casing 1.
Motor valve hole 45 formed by extending in the radial direction
The motor valve spool 41 slidably arranged inside
The valve hole 45 has a corresponding motor cylinder.
The oil passage 1b communicating with the cylinder hole 26a of 26 is opened.
There is. The outer end of the motor valve spool 41 is attached by a spring 42.
Is pressed inward, the inner end 41b projects inward,
Motor valve cam coupled to the motor crank member 22
It is in contact with the outer peripheral surface 49a of 49. Outside of this cam 49
As shown in FIG. 4, the circumferential surface 49a also has the pump valve cam 3
It has a rice ball shape similar to that of the motor
The motor valve cam 49 is rotated together with the brake member 22.
And the outer peripheral surface 49a pushes the motor valve sp
The roll 41 reciprocates in the motor valve hole 45. It is connected through the motor crankshaft 22b.
The motor plunger 25 is connected to the motor cylinder 26
When reciprocating in the hole 26a, the motor crank member 22
The motor valve spool 41 reciprocates because it rotates.
The movement is also synchronized with the reciprocating movement of the motor plunger 25. Mo
The outer peripheral surface 49a of the data valve cam 49 is a motor crank.
The motor plunger 25 is top dead according to the rotation of the member 22.
When it is in the process of moving from the point to the bottom dead center (in the supply process,
(Sometimes) push the spool 41 with the bias of the spring 42.
Lower (move inward), while motor plunger 2
5 is in the process of moving from bottom dead center to top dead center (
(While in the out stroke), bias the spool 41 with the spring 42.
Push up against (move outward). As a result, the motor plunger 25 is supplied.
When in the stroke, through the groove 41a of the spool 41
The oil passage 1b and the supply oil passage 47 communicate with each other, and
Hydraulic oil sent from the cylinder 16 to the oil supply passage
It is supplied into the cylinder hole 26a of the motor cylinder 26,
Upon receiving this hydraulic pressure, the motor plunger 25 moves toward the bottom dead center.
Be moved. On the other hand, the motor plunger 25
At some time, the oil passage 1 is passed 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 used in the intake stroke.
Inside the pump cylinder hole 16a of the pump plunger 15
Sent. Radial plunge configured as described above
The operation of the hydraulic transmission TM1 will be described.
In this transmission TM1, the input shuffling
The pump shaft 11 acting as a rotor is rotationally driven.
Thereby, the first and second pump drive gears 11b, 1
The pump crank member 12 is rotated via 2a,
Plunger 15 reciprocates in pump cylinder 16
It This reciprocating motion distributes the discharged hydraulic oil to the pump.
It is supplied to the motor cylinder 26 by the action of the valve 30.
The motor plunger 26 moves in the motor cylinder 26.
Be revived. This causes the motor crank member 22 to rotate.
Is driven to rotate, and this is driven by the first and second motor drive gears 21.
It is transmitted to the motor shaft 21 via b and 22a,
The motor shaft 21 acting as a force shaft rotates
Be moved. However, with only the above-mentioned structure, the pump shuffle
By transmitting the rotation of the motor 11 to the motor shaft 21,
The gear ratio is constant, and the transmission (transmission)
Does not play a role. For this reason,
In the transmission TM1, the gear ratio is variably controlled.
A gear change control valve mechanism 50 for
Will be described below. The shift control valve mechanism 50 is attached to the left cover 4.
It slides in the spool hole 53 that extends in the radial direction.
Has a timing valve spool 51 that is freely inserted.
To do. The outer end of the spool 51 is attached to the inside by a spring 52.
The inner end portion 51b of the spool 51 is urged to project inward.
The outer peripheral surface of the timing cam 63 of the timing mechanism 60.
Abut. This shift control valve mechanism 50 is used for each pump
Each spool hole is provided corresponding to the cylinder 16.
51 communicates with the communication hole 16c of the pump cylinder 16.
Thus, the relief valve hole 56, drain groove 57 and
A drain hole 58 is formed. In addition, the relief bar
The first return oil from the lube hole 56 through the casings 1 and 2.
A bypass oil passage 59 communicating with the passage 36 extends. Lily
The relief valve spooe is slidable in the valve hole 56.
This relief valve spool is equipped with
55 is pushed by a spring and the right end of the relief valve hole 56
It is designed to block the opening. Timing of insertion into spool hole 53
The valve spool 51 has a land portion 51a.
In response to the movement of the reel 51, the land portion 51 causes the drain hole 58 to
Is designed to be blocked. Inner end of this spool 53
The outer peripheral surface of the timing cam 63 with which the portion 51b abuts is shown in FIG.
The lower part 63a and the higher part 63b are formed as shown in FIG.
And have. The timing cam 63 will be described later.
Is rotated in synchronization with the rotation of the pump shaft 11.
Then, according to this rotation, the timing valve spool 51
Is reciprocated in the spool hole 53. First, the spool 51 is spooled in this way.
The operation when reciprocating in the hole 53 will be described.
The inner end portion 51b of the spool 51 is set to the low position of the timing cam 63.
When contacting the portion 63a, the timing valve
The pool 51 is in the state shown in FIG. 1, and the land portion 51a is drained.
It is located at a position to close the hole 58. Also, the relief bar
Relief valve spool 55 arranged in the 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 oil pressure of the discharge oil from the pump cylinder 16
The spool 55 receives the orifice 55a.
Is provided, and the hydraulic oil in the communication hole 16c is spooled.
It also flows into the hole 56, and the relief valve spool 55
It receives this discharge hydraulic pressure from both sides. Therefore, the pressure receiving area difference
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. This right move
The relief valve spool 55 is
It blocks the road 59. On the other hand, the inner end portion 51b of the spool 51 is tied.
When in contact with the high portion 63b of the ming cam 63,
The timing valve spool 51 will be in the state shown in FIG.
When the drain portion 51a moves to the outer diameter side of the drain hole 58,
The hole 58 opens into the space inside the casing. For this reason,
The valve valve spool 55 discharges from the pump cylinder 16.
When the oil pressure of the oil is taken out, this oil pressure causes the relief valve
The spool 55 is pushed in and moves left as shown in FIG.
It As a result, the communication hole 16c communicates with the bypass oil passage 59.
The oil discharged from the pump cylinder 16 is a bypass oil passage.
It is discharged from 59 to the first return oil passage 36. For this reason,
When, the discharge oil from the pump cylinder 16 is
Not sent to Linda 26. As can be seen from the above description, the timing
By controlling the position of the valve spool 51, the pump
Amount of oil sent from motor cylinder 16 to motor cylinder 26
The pump shaft 1 can be controlled by
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. The position of the timing valve spool 51
The position of the motor shaft 11 is controlled according to the rotation of the motor shaft 11.
A timing mechanism 60 for rotating the ming cam 63 is provided.
Has been. This timing mechanism 60 is a pump shuffle.
Sun gear 61 attached to the gland 11 and this sun gear
61 and planetary pinion 62 that meshes with 61
Carrier 64 that holds the talipinion 62 rotatably
And an internal ring gear that meshes with the planetary pinion 62
The timing cam 63 having a
A phase adjustment driven gear 65 integrally connected to the rear 64,
Of the left cover 4 as well as meshing with the phase adjustment driven gear 65 of
And a phase rotatably supported by the left casing 2
It is composed of an adjusting drive gear 66. The phase adjustment drive gear 66 is normally fixed and held.
As a result, the carrier 64 is also fixedly held. others
Therefore, when the pump shaft 11 is driven to rotate, the pump shaft
The sun gear 61 is rotated together with the shaft 11, and this
Turn the timing cam 63 via the planetary pinion 62.
Turn over. In this way, the timing cam 63
It is rotated in synchronization with the shaft 11, but this timing
Ng cam 63 from the pump cylinder 16 as described above.
Since the discharge amount is adjusted, the timing cam 63
Is the reciprocating movement of the pump plunger 15, namely the pump clan
It is necessary to operate in synchronization with the rotation of the locking member 12. Therefore, the teeth of the first pump drive gear 11b are
Number Z1, number of teeth Z2 of second pump drive gear 12a, timing
Number of teeth Zs of the sun gear 61 of the gearing mechanism 60 and timing
The number of teeth Zr of the ring gear of the Gucam 63 and the pump crank
Rotational speed Nc of member 12 and rotation of timing cam 63
The relationship with the number Nr is: Nr / Nc = (Zs.Z2) / (Zr.Z1) = 1 / n However, each number of teeth is set so that n is an integer. Do this
And drive the pump shaft 11 to
When the material 12 is rotated n times, the timing cam 63
Rotates once. In this example, the setting is such that n = 3.
Therefore, the timing cam 63 has three lower parts 63.
It has a and a high portion 63b. With the length of the lower part 63a
The length of the high portion 63b is equal to
The timing bar is
The lube spool 51 moves up, and the remaining half moves down.
It The reciprocating stroke of the pump plunger 15 and the discharge amount
Is shown in FIG. 7, and the suction of the pump plunger 15 is
Intake hydraulic oil in the stroke corresponding to the entry stroke,
Discharge the hydraulic oil in the stroke corresponding to the discharge stroke.
It The amount of hydraulic oil at this time changes like a sine curve.
To do. FIG. 7A shows a timing valve spool.
When the lever 51 is moved upward during the stroke indicated by the arrow A
Is shown. In this case, during the stroke indicated by A
Does not affect the suction operation in the suction stroke, but
Is no longer discharged and the hatching in the figure
The applied amount is not discharged. In this way
The amount of oil discharged from the binder 16 is adjusted. Here, the length of the stroke indicated by A is tie
The length of the lower part 63a and the higher part 63b of the ming cam 63
Corresponding and cannot be changed, but this stroke phase
Is variably adjustable. This adjustment is phase
Rotating the shaft 66a of the adjusting drive gear 66 from the outside
Can be done by. Thus, for example, in FIG.
Move the stroke indicated by A as shown in (B).
If, for example, all the discharged oil is sent to the motor cylinder 26,
You can get the highest speed ratio. Ie the phase
This is achieved by controlling the rotational position of the adjusting drive gear 66.
It is possible to control the transmission ratio of the transmission TM1.
Wear. In the above, the pump shaft 11
Drive power to the motor shaft 21
As I explained, the pump and motor are reversed and the motor shaft
21 is used as a pump shaft,
Drive and use pump shaft 11 as motor shaft
It is configured to take out power from this shaft 11.
May be. Next, the radial according to the second embodiment of the present invention.
Plunger hydraulic transmission TM2
This will be described with reference to FIG. This transmission TM
2 is the transmission TM1 according to the first embodiment.
It has a configuration similar to that of the first embodiment.
Parts different in configuration from Lance Mission TM1 and its parts
Only the peripheral portion is shown in FIG. For this reason,
Same as the transmission TM1 according to the first embodiment.
The same number is attached to a part and the description thereof is omitted. This transmission TM2 has an input system.
A pump shaft 111 that also serves as a shaft and a pump shaft
Bearings 106a and 106b on the shaft 111
The motor shaft 121 rotatably arranged and the right cover
-Output shaft 155 protruding outward from the right side
Which have a power transmission planetary gear mechanism 150.
Are linked together. The pump shaft 111 is
Rotated by the left casing 102 via the ring 105a.
It is rotatably supported and the motor shaft 121 is a bearing.
Rotatably by the right casing 101 via 105b
Supported, the output shaft 155 has a bearing 105c.
Is rotatably supported by the right cover 103 through
It The power transmission planetary gear mechanism 150 is
Sun gear 1 splined to the pump shaft 111
51 and a ring gear connected to the motor shaft 121
154, the sun gear 151 and the ring gear 15
4 planetary pinion 152 meshing with 4 is rotatably held
The carrier 153 is composed of a carrier 153 to be carried.
Is coupled to the output shaft 155. The motor shaft 121 is driven by the first motor.
Gear 122 is splined and attached
This first motor drive gear 122 is a motor crank
The material 22 meshes with the second motor drive gear 22a. others
Therefore, when the pump shaft 111 is driven,
The rotation of the gear 111 causes the first and second pump drive gears 11 to rotate.
It is transmitted to the pump plunger 15 via 1b and 12a.
It Then, with the transmission TM1 of the first embodiment,
Similarly, the oil discharged from the pump cylinder 16 causes
The motor plunger 12 is reciprocated to move the motor shaft 12
1 is rotationally driven. In this example, the motor shaft 121
Rotation of the ring of the power transmission planetary gear mechanism 150.
It is transmitted to the gear 154. Further, in this example, the pump shaft 111
The rotation is performed by the first and second pump drive gears 111b, 12
Not only is it transmitted to the pump cylinder 15 via a.
Sun gear 15 of power transmission planetary gear mechanism 150
It is also transmitted to 1. Therefore, the output shaft 155 is
Driving force of motor shaft 121 and pump shaft 1
It will be driven by the driving force of 11, which is more efficient.
Power transmission can be performed. In this example, the pump distribution valve
130 to the check valve 131 on the suction side and the check valve on the discharge side.
It is composed of a valve 135. Suction side check bar
A return oil passage 132 is installed at a portion opened and closed by the lube 131.
And is opened and closed by the discharge side check valve 135.
A discharge oil passage 136 is provided in the portion. Because of this, vomiting
The oil passage is pushed by the pump plunger 15 in the outstroke.
The hydraulic oil discharged to 101a is the check valve on the discharge side.
135 is pushed open and flows into the discharge oil passage 136,
Check the intake side when the injector 15 is in the intake stroke.
The valve 131 opens and the return oil passage 132 pumps
The hydraulic oil is sucked into the hole 16a. Radial plan according to the third embodiment of the present invention
The Ja-type hydraulic transmission TM3 is shown in FIG.
It This transmission TM3 is the same as the second embodiment.
Transmission TM2 related to and power transmission planetar
Only the arrangement position of the re-gear mechanism 170 is different,
This is the same as the transmission TM2 of the second embodiment.
Is. Specifically, the power transmission planetary gear mechanism
170 is almost the center of this transmission TM3
Part, that is, the pump plunger 15 and the motor plug
It is installed so that it is located on the same plane as the engine 25 in the axial direction.
This is the same as the transmission TM2 of the second embodiment.
different. With this configuration, the transmission T
The axial dimension of M3 is shortened to make the overall size smaller and more compact.
It becomes easy to make the same. It should be noted that this configuration
Therefore, the sun gear 171 is integrated with the pump shaft 161.
Is formed, and the first motor is driven on the outer circumference of the ring gear 174.
The gear 174a is formed. And the carrier 17
3 is coupled to the output shaft 165. In the second and third embodiments, the pom
Drive the shaft (input shaft) 111, 161
It is explained that power is transmitted to the output shafts 155 and 165.
As I mentioned, the pump and motor are reversed and the 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, the radial according to the fourth embodiment of the present invention.
Plunger hydraulic transmission TM4,
This will be described with reference to FIGS. 10 and 11. Note that FIG.
FIG. 11 is a half sectional view showing a pump plunger portion, and FIG.
It is a half cross-sectional view showing a motor plunger portion. This tran
Mission TM4 is a right casing 201, left case
Ring 202, right cover 203 and left cover 204
To do. Inside the right and left casings 201, 202
Bearings 205a and 205b support the center, and
The pump shaft 211 and the motor shaft 221 are coaxial.
It is rotatably arranged above. Pump shaft 211
The left end portion 211c is projected outward from the left cover 204.
It is designed to be driven through this part,
The pump shaft 211 also serves as an input shaft. Mo
The right end 221c of the shaft 221 is the right cover 203.
So that the output is taken out from this part.
The motor shaft 221 also serves as the output shaft.
is doing. An insertion hole is formed at the right end of the pump shaft 211.
211a is formed on the left side of the motor shaft 221.
The end portion 221a projects into the insertion hole 211a,
Both shafts 211 and 221 overlap each other
is doing. And, both sides in this overlap part
Between the shafts 211 and 221, a pair of left and right needle plates
Arings 206a and 206b are provided, and
So that both shafts 211 and 221 can rotate relative to each other.
Has become. 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 shaft is
211 is eccentric from the rotational axis C1 by a distance L1.
Is made. That is, the axis of the outer peripheral surface of the right end portion 211b
The center C2 is separated from the rotation axis C1 by a distance L1. So
Then, on the right end portion 211b, the eccentric collar is rotatably attached.
-212 is attached. Outside the eccentric collar 212
The peripheral surface is the axial center of the outer peripheral surface of the pump shaft right end portion 211b.
It is eccentric from C2 by a distance L2, and its axis
The center C3 is separated from the axis C2 by a distance L2. The eccentric collar 212 is the pump shaft 211.
Although it is rotatably attached to b, both are
They are connected via a peak adjusting mechanism 230. straw
The adjustment mechanism 230 splices the pump shaft 211.
The first sun gear 231 that is coupled and attached to the
1st planetary pinion 2 that meshes with 1 sun gear 231
33 and the first planetary pinion 233 are rotatably supported.
Carrier 232 to carry and first planetary pinion 23
And a first ring gear 234 that meshes with the third ring gear
234 adjacent to and coupled to the left casing 202.
Second ring gear 236 and second ring gear 236
The second planetary pinion 235 and the second planetary gear that mesh with each other.
And the second sun gear 237 that meshes with the talipinion 235.
Have. The first and second planetary pinion 23
3, 235 are both through the pinion shaft 232a
Are rotatably supported by a carrier 232. External teeth are formed on the outer periphery of the first ring gear 234.
The stroke adjusting gear 239 is formed by meshing with the external teeth.
Is attached. This stroke adjustment gear 239
The shaft portion 239a of the
The adjustment gear 239 can be driven to rotate.
ing. Connected to the second sun gear 237 by spline connection.
A tying collar 238 is rotatably attached.
An internal gear 238a is formed at the right end of the connecting collar 238.
Has been. On the other hand, on the left side of the eccentric collar 212,
The inner tooth gear 238a.
And the external gear 212a mesh with each other to form an eccentric collar 212.
The connecting collar 238 is connected. In the stroke adjusting mechanism 230 having the above structure
The stroke adjusting gear 239 is normally held stationary.
Has been. Therefore, the pump shaft 211 is rotated
Then, through the stroke adjusting mechanism 239, the above-mentioned
The eccentric collar 212 connected to the pump shaft 21
It rotates together with 1. An annular guide is provided on the eccentric collar 212.
A ring 213 is rotatably attached. That
Release the guide ring 213 as shown in FIG.
Surrounded in a radiating manner, positioned at equal intervals and alternately,
Five pump plungers 215 and five pumps each
Cylinder 216, motor plunger 225 and motor
And a data cylinder 226. The pump cylinder 216 is a left and right trunnion.
Shake to the left and right casings 201 and 202 at the portion 216c.
It is movably supported and its cylinder hole 216a is
It is open to the circumference. Each cylinder hole 216a has a sliding
A pump plunger 215 is inserted in the
The inner end portion 215a of the plunger 215 has the guide ring 2
It is in sliding contact with the outer peripheral surface of 13. As mentioned above, eccentric color
The axis C3 of the outer peripheral surface of the -212 is
It is eccentric with respect to the rotation axis C1. For this reason,
The eccentric collar 212 is rotated together with the shaft 211.
Then, each pump plunger 215 has a function of adjusting the eccentricity of the shaft center C3.
Is reciprocated in the pump cylinder 216 for the corresponding distance.
It Therefore, the rotating shaft of the pump shaft 211
Deviation of the axial center C3 of the outer peripheral surface of the eccentric collar 212 with respect to C1
If the core distance is variably adjusted, the pump plunger 215 moves forward.
The return stroke can be variably controlled. Is the pump cylinder 216
The amount of discharged oil can be variably controlled. Axis for rotation axis C1
The eccentric distance of the center C3 is adjusted by the stroke adjusting mechanism 230.
This is performed by rotating the stroke adjusting gear 239 of. For this stroke adjustment, see FIG.
I will explain. FIG. 3 shows the rotation of the pump shaft 211.
Rolling axis C1 (this is the same as the rotation axis of the motor shaft 221)
The outer circumference of the right end portion 211b of the pump shaft 211.
Axis C2 of the surface and axis C of the outer peripheral surface of the eccentric collar 212
3 shows the positional relationship of 3 and the solid line shows these 3
When the axes C1, C2 and C3 are arranged on the same straight line
Is shown. As described above, the rotation axis C1 and the axis C2
Is separated by a distance L1 and the axis C2 and the axis C3 are separated by a distance L2.
Since they are separated from each other, the axes C1, C2 and C3 are aligned on the same straight line.
When the rotation is being performed, the rotation axis C1 and the axis C3 are separated by a distance L3.
(= L1 + L2) apart, and the rotation axis C1 and the axis at this time
The distance from the heart C3 is the maximum. From this state, the stroke adjusting mechanism 230
When the stroke adjusting gear 239 is rotated, the first sangui
The second sun gear 237 is rotated relative to the ya 231.
It Therefore, the eccentricity of the pump shaft 211 is reduced.
-212 is relatively rotated. Eccentric collar 212 is a pump
Rotatably on the outer peripheral surface of the right end portion 211b of the shaft 211
Since it is arranged, this rotation causes the eccentric collar 21.
2 is an axial center of the outer peripheral surface of the right end portion 211b.
Rotate around C2. 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 shown by the chain double-dashed line,
C3 moves to the position indicated by C3 '. As a result, the rotation axis
The eccentric distance of the axis C3 with respect to C1 is L3 '(<L3)
Becomes shorter. In this way, the stroke adjustment gear 23
By rotating 9, the eccentric distance L3 of the shaft center C3
After adjusting and rotating the pump shaft 211,
Variable adjustment of the reciprocating stroke of the pump plunger 215
You can 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 reciprocating in 16, the suction and discharge of hydraulic oil
Through the communication hole 216c. Communication hole 216c
Is a suction side check valve 251 and a discharge side check valve.
Connected to a pump distribution valve 250 consisting of
Operation by the action of this pump distribution valve 250.
Oil suction and discharge control are performed. This pump distribution valve
Reference numeral 250 denotes a transmitter according to the second embodiment shown in FIG.
Is the same as the pump distributor valve 130
Therefore, the description is omitted. In this way, the pump cylinder 216
The hydraulic fluid discharged from the
Is sent to the motor distribution valve 240. Motor distribution valve
The block 240 is a transformer according to the first embodiment shown in FIG.
Same as the motor distribution valve 40 used in
And is reciprocated by the motor valve cam 249.
It has a motor valve spool 241. This will
The oil discharged from the pump cylinder 216 is discharged in the suction stroke.
It is supplied into the data cylinder 226. The motor cylinder 226 is shown in FIG.
Is located on the same plane as the pump cylinder 216.
The left and right cables are installed in the trunnion section 226b.
It is swingably supported by the singles 201 and 202.
It The cylinder hole 226a of the motor cylinder 226 has an inner circumference.
Side opening and formed on the trunnion portion 226b.
The communication hole 226c is opened. This cylinder hole 2
26a, the motor plunger 225 is slidably inserted.
The inner end 225a of the motor plunger 225
Connected to the crankshaft 225a of the motor crank member 222
Has been done. The motor crank member 222 is the second motor.
The drive gear 222a and the crankshaft 222b are integrally provided.
And the crankshaft 222b are press-fitted and joined.
And a supporting member 222c. This motor class
The link member 222 includes left and right bearings 224a, 224.
Rotation by the left and right casings 201, 201 via b
Currently supported. The second motor drive gear 222a is
A first motor drive integrally formed with the motor shaft 221.
It meshes with the dynamic gear 221b. For this reason, the pump
The motor plunger 225 is driven by the oil discharged from the binder 215.
Is reciprocated, and the motor crank member 222 is rotationally driven.
This rotation causes the rotation of the first and second motor drive gears 22.
2a, 221b to the motor shaft 221
Then, the motor shaft 221 is driven. In the fourth embodiment, the pump shaft
(Input shaft) 211 is driven to drive the motor shaft (output
(Power shaft) 221 has been described as transmitting power.
However, the pump and motor are reversed and the motor shaft 221
Drive this shaft 221 by using it as a pump shaft
The pump shaft 211 is used as a motor shaft.
Configured to take power from the lever shaft 211
May be. Next, the radial according to the fifth embodiment of the present invention
Plunger hydraulic transmission TM5,
This will be described with reference to FIGS. This transmission
Option TM5 is related to the fourth embodiment shown in FIGS.
Transmission TM4 and pump drive mechanism are different
Since the other configurations are the same,
A single number is given and its description is omitted. In this transmission TM5
Is the motor shaft when the right end 311a of the pump shaft 311 is
Both shafts are projected into the insertion hole 321a of the shaft 321.
A bearing 306a disposed between 311 and 321;
Relative rotation is possible via 306b. Pump
A protrusion 311b is formed in the middle of the shaft 311.
As shown in FIG. 16, the outer peripheral surface of the protrusion 311b is
And a distance L1 from the rotation axis C1 of the pump shaft 311
The eccentric shape is formed. Then, the protrusion 311b is wound around the outer circumference.
An eccentric collar 312 is rotatably attached. this
The outer peripheral surface of the eccentric collar 312 is the outer peripheral surface of the protrusion 311b.
Has a shape eccentric from the axis C2 of
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, this example
Transmission TM5 also has eccentric collar 3
12 is a pump shear via a stroke adjusting mechanism 230.
It is connected to the bus 311. Therefore, the eccentric collar 3
12 rotates integrally with the pump shaft 311. In addition,
The trocar adjustment mechanism 230 is the same as that described above,
Eccentricity is produced by rotating the trowel adjustment gear 239.
The eccentric amount of the axial center C3 of the outer peripheral surface of the collar 312 is variably adjusted.
You can On the eccentric collar 312, it is rotatably connected.
A tie ring 313 is attached. This connecting ring
313 to the pump plunger 3 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 are arranged radially at equal intervals.
315 is in the cylinder hole 216a of the pump cylinder 216.
It is slidably inserted. Here, the pump shaft 311 is rotationally driven.
Then, the eccentric collar 312 rotates integrally with this, and the eccentric collar
Connection ring 31 rotatably mounted on 312
3 makes an orbital motion by the eccentric collar 312, and
The pump plunger 315 connected to the pump 313 is the pump.
Reciprocating motion is performed in the cylinder 216. In addition, this revolution
When moving, the connecting ring 313 does not rotate and 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 has a double mechanism
Mechanism is provided. Double mechanism is left casing
First internal gear 361 fixed to 202 and eccentric collar
External gear mounted rotatably on side of 312
362 and the connecting ring 313 are integrally formed on the left side surface of the connecting ring 313.
And a second internal gear 363 that has been formed. As shown
So that 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 number of teeth of the first internal gear 361 and the second internal gear 363 are equal.
Yes. Further, the first internal gear 361 is connected to the pump shaft 31.
It is arranged so as to be concentric with the rotation axis C1 of
The tooth gear 362 is the same as the shaft center C2 of the outer peripheral surface of the protrusion 311b.
The second internal gear 363 is arranged so as to be the center.
To be concentric with the axial center C3 of the outer peripheral surface of the eccentric collar 312.
It is installed in. Use the double mechanism configured as described above.
For example, the eccentric collar 312 together with the pump shaft 311
When rotated, the connecting ring 313 does not rotate
It is possible to revolve around the rotation axis C1. Na
For the detailed operation of the double mechanism, see Japanese Patent Laid-Open No. 4-2.
No. 62158 and known,
The description is omitted. In the fifth embodiment, the pump shaft
(Input shaft) 311 is driven to drive the motor shaft (output
Force shaft) 321 is described as transmitting power.
However, the pump and motor are reversed and the motor shaft 321
Drive this shaft 321 by using it as a pump shaft
The pump shaft 311 is used as the motor shaft.
It is configured to take out power from the lever shaft 311
May be. Next, the radial according to the sixth embodiment of the present invention.
Plunger type hydraulic transmission TM6,
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
To be done. Therefore, it is different from the transmission TM5
The structure, that is, the power transmission planetary gear mechanism 450 and
And the configuration of the peripheral portion thereof will be described. The power transmission planetary gear mechanism 450 is
At the right end of the pump shaft 411 which also serves as the force shaft
The sun gear 451 and the sun gear 45 which are integrally formed
Planetary pinion 453 that meshes with 1, and planetary
Carrier 452 holding pinion 453 rotatably
And the ring gear 4 that meshes with the planetary pinion 453.
And 54. The carrier 452 has an output shaft 455.
External teeth formed on the outer circumference of the ring gear 454 by being coupled with
The gear 454a is the second motor of the motor crank member 222.
It meshes with the drive gear 222a. Therefore, in this example,
Ring gear 454 is used as a motor shaft
It In this transmission TM6
When the pump shaft 411 is driven,
The rotation of the shaft 411 is pumped through the connecting ring 313.
It is transmitted to the Langer 315. And similar to the previous example
Then, the oil discharged from the pump cylinder 216 causes the motor to move.
When the tap plunger 225 is reciprocated, the motor crank member
222 is rotationally driven. In this example, the motor crank
The rotation of the material 222 is performed by the power transmission planetary gear mechanism 450.
Of the ring gear 454. Further, in this example, the pump shaft 411
The rotation is performed by the pump cylinder 31 via the connecting ring 313.
5 power transmission planetary gear machine
It is also transmitted to the sun gear 451 of the structure 450. For this reason,
The output shaft 455 extends from the motor crank member 222.
Receiving the driving force of the pump shaft and the driving force of the pump shaft 411
Will be driven, and efficient power transmission will be performed
be able to. In the sixth embodiment, the pump shaft
(Input shaft) 411 is driven to output shaft 455
I explained that the power is transmitted to the
Reversed and use output shaft 455 as input shaft
Drives the lever shaft 455 to drive the pump shaft 411.
Is used as the output shaft to move from this shaft 411.
It may be configured to extract force. As described above, the radiator according to the present invention
Alplunger fluid transmissions are
Shaft and motor shuff that can rotate relative to each other
The casing is rotatably supported by the casing, and these pumps
And a substantially flat plate perpendicular to the shaft center of the motor shaft
Radially and circumferentially extending from the axis of both shafts on the surface
Arrange pump cylinders and motor cylinders side by side
And attach them to the casing,
In the cylinder holes of the pump cylinder and motor cylinder
Sliding freely, pump plunger and motor plunge, respectively
And the pump side through the pump side motion conversion mechanism.
The rotation of the shaft is transmitted to each pump plunger and
Move the motor back and forth in the cylinder hole of the pump cylinder.
Cylinder hole of each motor cylinder through side motion conversion mechanism
Reciprocating motion of each motor plunger in the motor shaft
It is configured to convert into rotational motion of. Thus, the pump cylinder and the motor system are
Place the Lindner on the same plane, which is perpendicular to the shaft center of both shafts.
If they are arranged radially on the surface and lined up in the circumferential direction,
This transmission is shortened by shortening the axial dimension of the transmission.
The size and size of the session can be reduced. Furthermore
Short the oil passage that connects the pump cylinder and the motor cylinder.
It is easy to reduce the pressure loss and reduces the pressure loss.
Can improve the power transmission efficiency of the mission
It The pump side motion conversion mechanism and the motor
At least one of the side motion conversion mechanisms, the pump shaft
The first gear fixed coaxially on the motor shaft
Is supported by the casing for relative rotation and
The second gear that meshes with the first gear and the rotation shaft of this second gear
A crank integrally formed with the second gear at an eccentric position
It consists of a pin and a pump plunger or motor
It is desirable to connect the runner and the crankpin,
This will make the transmission more compact.
Can be converted to Further, the pump shaft and the motor shuff
The sun gear arranged coaxially with the
Planetaripi that revolves around this sun gear
Nion and this planetary pinion are supported for rotation.
Carrier that rotates coaxially with the gear, and planetary pini
It has internal teeth that mesh with ON and rotates on the same axis as the sun gear.
A planetary gear set consisting of a rotating ring gear is installed.
Connect the pump shaft and the input shaft, and
Separate output shaft and motor shaft from output shaft
Is installed to configure the planetary gear set.
Input gear and carrier respectively
Data shaft or output shaft
The transmission can also be configured. like this
The transmission with higher power transmission efficiency
Can be obtained. In this case, the pump shaft and the input shuffle
And the sun gear are connected to the input shaft,
Output the carrier by connecting the ring gear to the motor shaft
It is preferably connected to the shaft. In addition, this planet
Install the tally gear set into the pump cylinder and motor cylinder.
Placed on the same plane as the plane
Is preferred. This way, the transmission
It can be made more compact. Further, the pump side motion conversion mechanism and the motor
The side motion conversion mechanism is connected to the pump shaft and motor, respectively.
The first pump drive gear fixed coaxially on the shaft.
And the first motor drive gear and the casing can rotate relative to each other
Is supported by the first pump drive gear and meshes with the first pump drive gear.
Two pump drive gears and the rotating shaft of this second pump drive gear
Is formed integrally with the second pump drive gear at a position eccentric from
The pump crankpin and the casing can rotate relative to each other
Is supported by the first motor drive gear and meshes with the first motor drive gear.
Two-motor drive gear and rotation shaft of this second-motor drive gear
Is integrally formed with the second motor drive gear at a position eccentric from
Motor crank pin and pump plunge
The motor and the pump crankpin, and
Connect the plunger and the motor crank pin, and
Drive gear integrally with the pump shaft, and
This ring is used as a motor shaft
The external gear formed on the outer circumference of the gear is the first motor drive gear.
Configured to mesh with the second motor drive gear
Preferably. On the other hand, the pump shaft and the motor shuff
Has a shaft that is eccentric from its rotation axis
An eccentric part is provided, and the eccentric part is
Motion to the pump plunger and motor plunger.
Transmit or reciprocate by converting to either reciprocating motion.
The session can also be configured. If you do this
A mechanism for reciprocating the pump or motor plunger.
Can be easy. In this case, if the shaft of this eccentric part is placed on the eccentric part,
An eccentric collar with an eccentric outer peripheral surface is rotatably mounted
A ring guide ring on the eccentric collar.
Mounted on site, pump plunger and motor plunge
Slide one of the inner ends onto the guide ring.
Mounting and variably adjusting the rotational position of the eccentric collar on the eccentric part.
Adjust the eccentric amount of the shaft center of the outer peripheral surface of the eccentric collar.
It is preferable to provide a trowel adjusting mechanism. Do this
Then, the reciprocating straw of the pump or motor plunger
Adjustment can be performed with a simple mechanism. Incidentally, instead of the annular guide ring, an annular connecting ring is used.
Attach the tie ring rotatably on the eccentric collar and
Either the plunger or the motor plunger
Attach the inner end by pivoting it to this connecting ring
Adjustment mechanism and connecting ring that revolves without rotating.
A bull mechanism may be provided. Even with this configuration,
Adjusting the reciprocating stroke of the ranger with a simple mechanism
You can

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view showing the configuration of a radial plunger 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 reference numerals] 1, 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 speed change control valve mechanism 60 timing mechanism

Claims (1)

Claim: What is claimed is: 1. A casing, a pump shaft rotatably supported with respect to the casing, coaxial with the pump shaft, and provided on the pump shaft.
The casing is arranged so as to be rotatable relative to the casing.
A motor shaft which is rotatably supported with respect grayed, on a plane perpendicular to the axis of the pump and motor shafts, a plurality of which is attached to the casing are arranged in the shaft sincerely spreads radially The pump cylinder, a plurality of pump plungers slidably inserted in the cylinder holes of each of these pump cylinders, and the pump and the motor shaft at right angles to the shaft center.
A plurality of motor cylinders which are arranged radially on the plane and which are arranged radially from the axis and are attached to the casing; a plurality of motor plungers slidably inserted into the cylinder holes of the respective motor cylinders; A pump side motion conversion mechanism that converts the rotational motion of the shaft into the reciprocating motion of the pump plunger in the cylinder hole of each pump cylinder; and the reciprocating motion of the motor plunger in the cylinder hole of each motor cylinder. A plane on which the pump cylinder is arranged and the motor cylinder, which is composed of a motor-side motion conversion mechanism that converts rotational movement of the motor shaft.
The surface where the connector is placed is the same or close in the axial direction.
Located on the same plane as above,
The binder and the motor cylinder are arranged side by side in the circumferential direction.
Radial plunger fluid transmission, wherein are. 2. The pump cylinder and the motor system
The number of linters is the same, and they are almost on the same plane.
2. Arranged alternately side by side.
Radial plunger type fluid transmission described in
N. 3. The pump shaft and the motor shaft overlap each other in the axial direction so that one of the opposite end portions of the pump shaft and the motor shaft enters the inside of the other, and at this overlap portion, the pump shaft and the motor shaft are overlapped. The radial plunger type fluid transmission according to claim 1 or 2 , wherein both shafts are coaxially supported by a bearing arranged therebetween so as to be rotatable relative to each other. 4. A pair of the bearings apart axially are disposed in the overlapping portion, one of the pair of bearings, rotatably supporting the pump shaft and the motor shaft to said casing The radial plunger type fluid transmission according to claim 3 , wherein the radial plunger type fluid transmission is arranged at a position that substantially overlaps with one of the bearings. 5. Axial position is the same or close to each other.
The surface on which the pump cylinder is disposed and the motor shaft
The surface on which the binder is placed is positioned above the overlap portion.
It arranges, It is characterized by things.
Radial plunger type fluid transmission. 6. At least one of the pump-side motion converting mechanism and the motor-side motion converting mechanism includes a first gear which is fixed coaxially to the pump shaft or on the motor shaft, relatively rotatably to said 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 radial plunger type fluid transmission according to any one of claims 1 to 5 , wherein a plunger and said crank pin are connected. 7. The pump-side motion converting mechanism is arranged in an axial direction.
Circumferentially on the same or close plane
The pump cylinders and motors arranged alternately side by side.
Is arranged on one side in the axial direction of the pump cylinder, and the motor-side motion conversion mechanism is
And on the other side of the motor cylinder in the axial direction.
Radius according to any one of claims 1 to 6, characterized in that
Le plunger fluid transmission. 8. A disposed on the pump shaft and the motor shaft coaxially sun gear, a planetary pinion and sun gear meshed revolves around the sun gear, and rotatably supporting the planetary pinion 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 The radial plunger type fluid transmission according to claim 1. 9. and said input shaft and said pump shaft is formed integrally, the sun gear is connected to the input shaft, the ring gear is coupled to the motor shaft, and connecting the carrier to said output shaft The radial plunger type fluid transmission according to claim 8 , which is characterized by being provided. 10. A disposed on the pump shaft and the motor shaft coaxially sun gear, a planetary pinion and sun gear meshed revolves around the sun gear, and rotatably supporting 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. Characterized by being The radial plunger type fluid transmission according to claim 1. 11. is formed in said motor shaft and said output shaft is integral, wherein the sun gear is connected to the output shaft, the ring gear is connected to the pump shaft, and connecting the carrier to the input shaft The radial plunger type fluid transmission according to claim 10 , which is characterized by being provided. 12. The planetary gear set, one of the claim 8-11, wherein said pump cylinder and said motor cylinder are arranged located substantially on the same plane as the plane which is disposed Radial plunger type fluid transmission according to Crab. Wherein said pump-side motion converting mechanism and the motor-side motion converting mechanism, respectively, a first pump drive gear and the first motor drive gear which is fixed coaxially to the pump shaft and on the motor shaft, wherein 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 to 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. Radial plunger fluid transmission according to claim 12, characterized in that it is configured to drive gear meshing. 14. 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 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 12 , wherein the radial plunger type fluid transmission is configured to mesh with a drive gear. 15. The eccentric portion is provided having an axis offset from its axis of rotation on one of the pump shaft and the motor shaft, the motion converting mechanism of the crank motion of the eccentric portion and the pump plungers and the motor plungers The radial plunger type fluid transmission according to claim 1, characterized in that the fluid is converted into either one of the reciprocating motions. 16. An eccentric collar having an outer peripheral surface eccentric from the axis of the eccentric portion is rotatably mounted on the eccentric portion, an annular guide ring is rotatably mounted on the eccentric collar, and the pump plunger and 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. claim 1, characterized in that a stroke adjusting mechanism for adjusting
5. The radial plunger type fluid transmission according to item 5 . 17. 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. 16. The radial plunger type fluid transmission according to claim 15 , wherein a stroke adjusting mechanism for adjusting and a double mechanism for revolving the connecting ring without rotating are provided. 18. A disposed on the pump shaft and the motor shaft coaxially sun gear, a planetary pinion and sun gear meshed revolves around the sun gear, and rotatably supporting the planetary pinion 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. Characterized by being Claims 15 to 1
7. The radial plunger type fluid transmission according to any one of 7 . 19. and the pump shaft and said input shaft is integrally formed, the sun gear is connected to the input shaft, the ring gear is coupled to the motor shaft, wherein the carrier is connected to said output shaft The radial plunger type fluid transmission according to claim 18 , characterized in that: 20. 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 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. Characterized by being Claims 15 to 1
7. The radial plunger type fluid transmission according to any one of 7 . 21. 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. 21. The radial plunger type fluid transmission according to claim 20 , wherein: 22. The planetary gear set, one of the claims 18 to 21, characterized in that it is provided located substantially on the same plane as the plane in which the pump cylinder and the motor cylinder are arranged Radial plunger type fluid transmission according to Crab.