CA1299062C - Continuosly variable transmission having distribution valve means - Google Patents
Continuosly variable transmission having distribution valve meansInfo
- Publication number
- CA1299062C CA1299062C CA000615888A CA615888A CA1299062C CA 1299062 C CA1299062 C CA 1299062C CA 000615888 A CA000615888 A CA 000615888A CA 615888 A CA615888 A CA 615888A CA 1299062 C CA1299062 C CA 1299062C
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- cylinder
- motor
- pressure oil
- pump
- hydraulic
- Prior art date
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Abstract
ABSTRACT OF THE DISCLOSURE.
A static hydraulic pressure type continuously variable transmission formed with a hydraulic closed circuit between a swashplate type hydraulic pump and a swashplate type hydraulic motor, the hydraulic motor being constructed such that its motor cylinder is integrally connected to an output shaft which extends through a motor swashplate and a swashplate holder for supporting the back surface of the motor swashplate, a swashplate anchor for supporting the back surface of the swashplate holder being axially immovably connected to the output shaft through a thrust bearing, and that the swashplate anchor is unrotatably connected to a casing which rotatably supports the output shaft. The motor cylinder and a pump cylinder of the hydraulic pump are provided coaxially with the hydraulic closed circuit interposed therebetween.
The hydraulic closed circuit is provided with a distribu-tion valve for bringing low and high pressure oil passages, which are in communication with cylinder bores of the pump cylinder, into selective communication with cylinder bores of the motor cylinder, and a clutch valve for con-trolling communication between the low and high pressure oil passages Where the swashplate type hydraulic motor is of a variable capacity type, means is provided which adjusts an angle of inclination of the motor swashplate to effect speed change control.
A static hydraulic pressure type continuously variable transmission formed with a hydraulic closed circuit between a swashplate type hydraulic pump and a swashplate type hydraulic motor, the hydraulic motor being constructed such that its motor cylinder is integrally connected to an output shaft which extends through a motor swashplate and a swashplate holder for supporting the back surface of the motor swashplate, a swashplate anchor for supporting the back surface of the swashplate holder being axially immovably connected to the output shaft through a thrust bearing, and that the swashplate anchor is unrotatably connected to a casing which rotatably supports the output shaft. The motor cylinder and a pump cylinder of the hydraulic pump are provided coaxially with the hydraulic closed circuit interposed therebetween.
The hydraulic closed circuit is provided with a distribu-tion valve for bringing low and high pressure oil passages, which are in communication with cylinder bores of the pump cylinder, into selective communication with cylinder bores of the motor cylinder, and a clutch valve for con-trolling communication between the low and high pressure oil passages Where the swashplate type hydraulic motor is of a variable capacity type, means is provided which adjusts an angle of inclination of the motor swashplate to effect speed change control.
Description
~299~62 BACKGROUND OF THE INVENTION
This invention is a third divisional from Canadian Patent Application S.N. 498587 filed December 24, 1985.
The field of the present invention relates to static hydraulic pressure type continuously variable transmissions, and more particularly to such transmissions in which a hydraulic closed circuit is formed between a swashplate type hydraulic pump and a swashplate type hydraulic motor.
A static hydraulic pressure type continuously variable transmission of the type herein referred to is disclosed, for example, in Japanese Patent Application Laid~Open No. 70,968/82 Specification and Japanese Patent Publication No. 38,467/84 Specification.
In conventional static hydraulic pressure type continuously variable transmissions, a motor cylinder and a motor swashplate of a hydraulic motor are independently supported on a casing. This can result in a great thrust load, applied to the motor swashplate from a group of motor plungers in sliding contact with the motor cylinder being borne by the casing during operation. Accordingly, such a casing is preferably formed with a highly rigid wall thickness, which can be heavy.
In addition, a pump cylinder of such a hydraulic pump and a motor cylinder of such a hydraulic motor are concentrically arranged with the former disposed internally of the latter. In such an arrangement the extexnal large-diameter motor cylinder is heavy.
Furthermore, in a conventional static hydraulic pressure type continuously variable transmission, a pump cylinder of the ~29~C~62 hydraulic pump is pressed in sliding contact aga1nst a distribution board fixedly mounted on the motor cylinder of the hydraulic motor so that working fluiZs of the hydraulic pump and hydraulic motor are transferred through an oil path extending through the rotary sliding surfaces. Because of this, pressurized oil tends to leak from between the opposed rotary sliding surfaces of the distribu-tion board and the pump cylinder, leading to deterioration of transmission efficiency due to such leakage.
In addition, in a conventional apparatus provided with a variable capacity swashplate type hydraulic motor, a hydraulic servo is connected to a motor swashplate to lightly adjust an angle of inclination of the motor swashplate, as is well known.
However, the hydraulic servo~motor has a complicated construction and is expensive.
More~ver, in a conventional construction, a clutch valve and its operating system, which control communication between the discharge and intake sides of the hydraulic pump for regulating power transmission from the hydraulic pump to the hydraulic motor, project axially from the end of the hydraulic motor increasing the overall length of he transmission. This is particularly txue where the hydraulic pump and the hydraulic motor are disposed on one and the same axis.
SUMMARY OF THE INVENTION
It is the primary object of the present invention to inexpensively provide a static hydraulic pressuxe type continuously variable transmission which is free from the disadvantages noted ~L~9go62 above, and which is light-weight and small, and has excellent transmission e~ficiency.
The invention herein claimed is a static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder; a hydraulic motor having a motor cyllnder; and a hydraulic closed circuit between the hydraulic pump and motor, the hydraulic closed circuit having a high pressure oil passage and a low pressure oil passage which are defined in the pump and motor cylinders in a manner distanced from each other; wherein a number of cylinder bores are arranged in the pump cylinder and in the motor cylinder to slidably receive therein a number of plungers, respectively; and wherein a number o~ distribution valves ar~ disposed in at least one of the pump cylinder and the motor cylinder, said number of distribution valves being rotatahle in response to rotation of said at least one cylinder and alternately communlcating the cylinder bores of said at least one cylinder with the hlgh pre~sure oil passage and low pressure oil passage, respectively, while being drlven externally of the cylinder to perform a reciprocating movement by a distributor valve driving means which is located outside of said one cylinder.
The invention fur her provides a swashplate type hydraulic system comprising: a cylinder block having a number of cylinder bores annularly arranged therein; a number of plungers each slidably received in one of the cylinders bores; a ~washplate engaging those ends of said plungers which protrude from the cylinder bores; and a high pressure oil passage and a low pressure . !, ;
~L299~62 oil passage which are defined in the cylinder block in a manner distanced from each other; wherein a working oil is transferred between these high and low oil pressura passages and the cylinder bores durin~ relative rotation between the cylinder block and the swashplate; wherein a plurality of distribution valves are disposed in the cylinder block to alternately communicate the cylinder bores with said high pressure oil passage and low : pressure oil passage, respectively, while being urged to perform a reciprocating movement by a distribution valve drivlng means; and wherein said distribution valve driving means is disposed outside of the cylinder block and is adapted to drive the distribution valves at positions outside of the cylinder block in response to the relative rotation between the cylinder block and the swashplate.
~29906~
BRIEF DESCRIPTION OF THE DRAWINGS
The drawings show one embodiment of the present invention.
Figure 1 is a longitudinal plan view of a static hydraulic pressure type continuously variable transmission incorporated in a power transmission system of a motor-cycle;
Figures 2 and 3 are sectional views taken on line II~II
and line III-III, respectively, of Figure l; and Figure 4 is an exploded perspective view of major components of Figure i.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The present application will now be described in the environment of the parent application.
Referring now to the drawings and more particularly to Figure 1, power of a motor-cycle engine is transmitted from a crank shaft 1 to an unshown rear wheel via a chain type primary reduction gear 2, a static hydraulic pressure type continuously variable -.
, ' ~2990~2 transmission T and a chain type secondary reduction gear 3.
The continuously variable transmission T comprises a swashplate type hydraulic pump P of a constant capacity type and a swashplate type hydraulic motor M of a variable capacity type, which are accommodated within a crank case 4 as a casing which carries a crank shaft 1.
The hydraulic pump P comprises a cup-like input member 5 integrally provided with an output sprocket 2a of the primary reduction gear 2. A pump cylinder 7 is relatively rotatably fitted in the inner peripheral wall of the input memher 5 through a needle bearing 6. Pump plungers 9, 9 ... are slidably fitted in a plural-ity and odd-number of annularly disposed cylinder bores 8, 8 provided in the pump cylinder 7 so as to surround the rotary center thereof, and a pump swashplate 10 is in contact with the outer ends of the pump plungers 9, 9 ...
The back surface of the pump swashplate 10 is rotatably supported on the inner end wall of the input member 5 in an atti-tude inclined by a predetermined angle with respect to the axis of the pump cylinder 7 through a thrust roller bearing 11. When input member 5 ~s rotated, the pump plungers 9, 9 .... are recipro-cated to repeatedly effect suction and exhaust strokes.
The back surface of the input member 5 is supported on a support sleeve 13 through a thrust roller bearing 12.
~: On the other hand, the hydraulic motor ~ comprises a motor cylinder 17 coaxially and closely coupled to the pump cylinder 7. A support shaft 24 and an output shaft 25 are ~299062 ~7~ 70488-~
integrally formed to central parts of both inner and outer ends of the motor cylinder 17 and extending in an axial direction. Motor plungers 19, 19 ... are respectively slidably fitted in a plurality and odd-number of annu~arly disposed cylinder~bores 18, 18 ...
provided in the motor cylinder 17 so as to surround the rotary center thereof. A motor swashplate 20 is in contact with outer ends of the motor plungers 19, 19 .... A swashplate holder 22 for supporting the back surface of the motor swashplate 20 through a thrust roller bearing 21 is positioned in a swashplate anchor 23 for suppoxting the back surface of the swashplate holder 22.
The motor swashplate 20 is tiltingly movable between an upright position at right angles to the axis of the motor cylinder 17 and a position inclined at a certain angle. At the inclined position, the motor plungers 19, 19 ... are reciprocated upon rotation of the motor cylinder 17 to repeatedly effect expansion and contraction strokes.
The aforesaid support shaft 24 extends through the cen-tral portion of the pump cylinder 7. A nut 26 is threadedly en-gaged with the support shaft 24 to retain the pump cylinder 7 and the motor cylinder 17 integrally connected to each other. The support shaft 24 further extends through the input member 5 and rotatably supports the input member 5 through a needle bearing 27.
On the outer periphery of the support shaft 24, the support sleeve 13 is splined-fitted and secured by means of a nut 30. The support shaft 24 is rotatably supported in the cran~ case 4 through the support tube 13 and a roller bearing 31.
129~0~i2 The aforesaid output shaft 25 extends through the central portion of the motor swashplate 20, the swashpla~e holder 22 and the swashplate anchor 23. A support sleeve 33 for support-ing the back surface of the swashplate anchor 23 through a thrust roller bearing 32 is splined-fitted to the end of the shaft 25 and is secured by means of a nut 34 with an input sprocket 3a of the secondary reduction gear 3. The output shaft 25 is rotatably supported on the crank case 4 through the support sleeve 33 and a roller bearing 35.
Secured to the support shaft 24 is a spherical spline member 36 in spline engagement with the lnner peripheral surface of the pump swashplate 10 in a manner relatively tiltable in all directions, and secured to the output shaft 25 is a spherical spline member 37 in spline engagement with the inner peripheral surface of the motor swashplate 20 relatively tiltably in all directions. The couplings of the spiral spline members 36 and 37 with the swashplates 10 and 20 suppresses to a minimal extent frictional contact between the group of pump plungers 9, 9 ... and the pump swashplate 10 and between the motor plungers 19, 19 and the motor swashplate 20.
Between the hydraulic pump P and the hydraulic motor M
is formed a hydraulic closed circuit as described hereinafter.
In the motor cylinder 17, an annular high pressure oil passage 40 and an annular low pressure oil passage 41 to encircle the oil passage 40 are provided between the group of cylinder bores 8, 8 ... of the pump cylinder 7 and the group of cylinder bores ~L299~2 _9_ 70488-~
18, 18 ... of the motor cylinder 17. The high pressure oil pas-sage 40 communicates ~ith the cylinder bores 8, 8 ... of the pump cylinder 7 through discharge valves 42, 42 .... The low pressure oil passage 41 also communicates with the cylinder bores 8, 8 ...
through intake valves 43, 43 ... Accordingly, the discharge valves 42 and the intake valves 43 are respectively provided in the same number as that of the pump plungers 9, 9 ....
These high and low pressure oil passages 40, 41 are both communicated with the cylind~er bores 18, 18 ... of the motor cylinder 17 through respective distribution valves 44, 44 Accordingly, the distribution valves 44 are provided in the same number as that of the motor plungers 19, 19 .O..
The distribution valves 44, 44 ..., which are of a spool type, are slidably fitted into valve holes 45, 45 ... radlally provided in the motor cylinder 17 between the group of cylinder bores 18, 18 ... and the high and low pressure oil passages 40, 41.
When the valve 44 occupies the radial inward position in the valve hole 45, there is provided a communication between the corresponding cylinder bore 18 and high pressure oil passage 40 whilst the cylinder bore 18 is shut off from the low pressure oil passage 41, and when the valve 44 occupies the radial outward position in the valve hole 45, there is provided a communication between the cor-responding cylinder bore 18 and low pressure oil passage 41 whilst the bore is cut o~f its communication with the high pressure oil passage 40.
Valve springs 46, 46 ... for biasing the distribution valves 44, 44 ... radially and outwardly are accommodated within the valve holes 45, 45 ... to control the distribution valves 44, 44 ..., and the inner peripheral surface of an eccentric ring 47 is engaged with the outer end of each distribution valve 44.
The eccentric ring 47 is formed of an inner race of a ball bearing 48 snapped in and secured to the crank case 4, and as shown in Figure 2. The ring 47 is installed at such a position that the center thereof is to be eccentric a 2redetermined distance ~ from the center of the motor cylinder 17 in a direction of the tilting axis 0 of the motor swashplate 20. Accordingly, when the motor cylinder rotates, each of the distribution valves 44 takes the stroke of 2 , which is twice of the eccentric amount Ç of the eccentric ring 47, within the valve hole 45 and reciprocates be-tween the aforesaid outward position and inward position.
The distribution valve 44 also functions to bring a replenishing oil passage 49 into communication with the low pres-sure oil passage 41 when the valve assumes the inward position in the valve hole 45. The replenishing oil passage 49 is provi~ed in the central portion of the support shaft 24 and connected to the discharge port of a replenishing pump 50.
The pump 50 is driven by the crank shaft 1 to supply oil stored in an oil reservoir 51 at the bottom of the crank case 4 to the oil passage 49 under relatively low pressure.
Referrlng to Figures 1, 3 and 4, an outer peripheral surface 20a of the moior swashplate 20 is formed into a spherical surface having its center at the tilting axis 0. A spherical recess 52 is formed in the front surface of the swashplate hoIder ~' ~29.~06~:
22 so as to receive the motor swashplate 20 along with the thrust roller bearing 21. A back surface 22a of the swashplate holder 22 is formed in a circular surface about the tilting axis 0 of the motor swashplate 20, and a semi-cylindrical recess 53 is formed in the front surface of the swashplate anchor 23 so as to support the swashplate holder 22 rotatably about the tilting axis O. This swashplate anchor 23 is connected to the crank case 4 through locating pins 54 so that the anchor may not be rotated about the output shaft 25.
A pair of trunnion shafts SS, 55' aligned on the tilting axis O are integrally projected on both ends of the swashplate holder 22, the trunnion shafts 55, 55' being rotatably supported on the swashplate anchor 23 throùgh needle bearings 56. In other words, the tilting axis 0 is defined by the trunnion shafts 55, 55'.
An operating lever 57 is fixedly mounted on the outer end of one trunnion shaft 55.
When the trunnion sha~t 55 is rotated by the operating lever 57, the swashplate holder 22 integral therewith also rotates and the latter can be tilted even during the rotation of :~ the motor swashplate 20.
With the arrangement as described above, when the input member 5 of the hydraulic pump P is rotated from the primary reduction gear 2, suction and exhaust strokes are alternately im-parted by the pump swashplate 10 to the pump plungers 9, 9 Then, each pump plunger 9, in suction stroke~ intakes worklng fluid ~L29~)62 -12- 70488-~
from the low pressure oil passage 41, and in exhaust stroke, feeds high press~re working fluid to the high pressure oil passage 40.
The high pressure working fluid fed to the high pres-sure oil passage 40 is supplied to a cylinder bore 18 through the distribution valve 44 at the inward position to force a motor plunger 19 in an expansion stroke. The working fluid within a cylinder bore 18 being moved by a motor plunger 19 in a contrac-tion stroke is discharged into the low pressure oil passage 41 through the distribution valve 44 at the outward position.
During this operation, the p~np cylinder 7 and motor cylinder 17 are rotated by the sum of reaction torque received by the pump cylinder 7 from the pump swashplate 10 through the pump plungers 9 in an exhaust stroke and reaction torque received by the motor cylinder 17 from the motor swashplate 20 through the motor plunger 19 in an expansion stroke. This rotary torque is trans-mitted from the output shaft 25 to the secondary reduction gear 3.
In this case, the speed change ratio of the output shaft 25 with respect to the input member 5 is given by the following equation:
Speed change - Capacity of hydraulic motor M
speed ratio 1 Capacity of hydraulic pump P
Thus~ if the capacity of the hydraulic motor M is changed from zero to a certain value, the speed change ratio can changed from 1 to a required value.
Incidentally, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, the motor '~.
.
1;~9~0~i2 -13- 70488-~
swashplate 20 can be tilted from an upright position to an inclined position to thereby steplessly control the ratio from 1 to a cer-tain value.
During the operation of the hydraulic pump P and hydrau-lic motor M as described above, the pump swashplate 10 and motor swashplate 20 receive the opposite thrust load from the group of pump plungers 9, 9 ... and the group of motor plungers 19, 19, ...
respectively. The thrust load applied to the pump swashplate 10 is carried by the support shaft 24 through the thrust roller bearing 11, input member 5, thrust roller bearing 12, support sleeve 13 and nut 30. The thrust load applied to the motor swash-plate 20 is carried by the output shaft 25 through the thrust roller bearing 21, swashplate holder 22j swashplate anchor 23, thrust roller bearing 32, support sleeve 33, sprocket 3a and nut 34. Since the support shaft 24 and output shaft 25 are integrally connected together through the motor cylinder 17, the aforesaid thrust load merely gives rise to tensile stress caused in the motor cylinder 17 system and exerts no action on the crank case 4 which supports the support shaft 24 and the output shaft ~5~
If worklng fluid~leaks from the hydraulic closed circuit between the hydraulic pump P and the hydraulic motor M during the aforementioned operation, when the distribution valve 44 assumes the inward position in the valve hole 45, working fluid in the leaked amount is replenished from the replenishing oil passage 49 to the low pressure oil passage 41 through that distribution valve 45.
~99~
Turning again to Figure 1, a speed change control device 60 is connected to the operating lever 57 of the trunnion shaft 55 for the tilting operation of the motor swashplate 20.
The speed change control device 60 comprises a cylinder 61 secured to the swashplate anchor 23, and a pair of first and second pistons 621, 622 which are slidably fitted in the cylinder 61 and are oppo-sed to each other so as to hold a tip end of the operating lever 57 therebetween in their rotary direction. The pistons 621, 622 are arranged so as to enable rotation of the operating lever 57 by their sliding movement.
The first and second pistons 621, 622 define first and second oil chambers 631~ 632 against respective opposed end walls of the cylinder 61. There chambers 631, 632 accommodate therein springs 641, 642 for urging the corresponding pistons 621, 622 to-- ward the operating lever 57.
The first and second oil chambers 631r 632 communicate with each other through a hyaraulic conduit 66 incorporating there-in a speed change control valve 65. The conduit is fi}led working fluid.
The speed change control valve 65 comprises a fixed valve casing 67 and a rotary valve 69 rotatably fitted in a valve port 68 of the valve casing 67. The rotary valve 69 is operated for rotation between a hold position A, a speed reduction position B and a speed increasing position C on hoth sides of the position A by means of a speed change lever 70 secured to the outer end of the rotary valve 69.
90~Z
-15- 70488~
The rotary valve 69 is provided with a communication port 72 incorporating a check valve 71. The valve casing 67 in-cludes a irst forked port 731 connected to the first oil chamber 631 and opening to one side of the valve port 68, and a second forked port 732 connected to the second oil chamber 632 and open-ing to the other side of the valve port 68. The communication port 72 is designed such that in`the hold position A of the rotary valve 69, the communication port 72 does not communicate with either forked ports 731~ 732; in the speed reduction position B, the port 72 communicates with both the forked ports 731~ 732 to allow a flow of oil only in one direction from the former 731 to the latter 732; and in the speed increasing position C, the port 72 communicates with both forked ports 731~ 732 50 as to allow oil flow only in the direction from the latter 732 to the former 731.
Since the:number of the motor plungers 19, 19 ... is odd, the thrust load applied by the group of motor plungers 19, 19 ... to the motor swashplate 20 during the rotation of the motor cylinder 17 alternately varies in intensity between one side and the other with the-tilting axis of the motor swashplate 20 as a border. Vibratory tilting ~orque acts on the motor swashplate 20.
This vibratory tilting torque alternately acts as a pressing force on the first and second pistons 621, 622 through the operating lever 57.
With this, when the speed change lever 70 is shifted to the reduction position B as shown, the flow of oil from the first oil chamber 631 to the second oil chamber 632 is permitted by ~29~062 the check valve 71 but the opposite flow is inhibited. Thus, when the pressing ~orce acts on the first piston 621 from the operating lever 57, the oil flows from the first oil chamber 631 to the second oil chamber 632. As a consequence of this, both the pistons 621, 622 are moved toward the first oil chamber 631 to turn the operating lever 57 in the direction of increasing the inclina-tion of the motor swashplate 20.
When the lever 70 is shifted to the increasing position C, the flow of oil from the second oil chamber 632 to the first oil chamber 631 is permitted by the check valve 71 but the opposite flow is inhibited. Thus, when the pressing force acts on the second piston 622 from the operating lever 57, the oil flows from : the second oil chamber 632 to the first oil chamber 531~ As a consequence of this, both the pistons 621, 622 are moved toward the second oil chamber 632 to turn the operating lever 57 toward the upright position of the motor swashplate 20.
When the speed change lever 70 is returned to the hold position A, communication between both the oil chambers 631, 632 is completely cut off and the flow of oil therebetween is inhibited.
Therefore, both the pistons~621, 622 become unable to move. The operating lever 57 is held at its position to lock the motor swash-plate 20 at the upright position or incl~ned position.
Between the high and low pressure oil passages 40, 4I, there is provided one or more piston type clutch valves 80. This ; clutch valve 80 is slidably fitted in a radial valve port ~1 which extends from the high pressure oil passage 40 to the low pressure , . . .
~L299062 oil passage 40 and opens to the outer peripheral surface of the motor cylinder 17. When the valve occupies the radial inward position (clutch ON position) in the valve port 81, both the oil passages 40, 41 are interrupted. When the valve occupies the radial outward position (clutch OFF position), both the oil passages 40, 41 are brought into communication with each other.
In order that the clutch valve 80 is urged toward the clutch OFF position, the inner end thereof receives oil pressure from the high pressure oil passage 40. A common clutch control ring 82 is slidably provided around the outer periphery of the pump cylinder 7 and is engaged with the outer end of valve a.
The clutch control ring 82 includes a cylindrical inner peripheral surface 82a for defining the clutch ON position of the clutch valve 80 and a tapered surface 82b joined to one end o said inner peripheral surface to define the clutch OFF position of the clutch valve 80. The ring is urged by means of a spring 83 toward - the side wherein the clutch valve 80 is held in the clutch ON posi-tion. This spring 83 is compressed between~the clutch control ring 82 and a retainer 84 engaged on the outer periphery of the pump cylinder 7.
The clutch control ring 82 is connected to a not-shown clutch operating lever through a shift fork 85, an intermediate lever 86 and a clutch wire 87. The shift fork 85 engages an outer peripheral groove 88 of the clutch control ring 82, and an operat-ing rod 89 secured to the base of the shift fork 85 extends through the crank case 4 and is operatively connected to the intermediate 1291~62 lever 86.
With this, when the clutch control ring 82 is moved to the right as viewed in the figure against the force of the spring 83 through the shift fork 85 by pulling the clutch wire 87, the tapered surface 82b of the clutch control ring 82 assumes a posi-tion opposed to the clutch valve 80. Therefore the clutch valve 80 is moved by the pressure of the high pressure oil passage 40 to the outward position, namel~, to the clutch OFF position. As the result, the high pressure oil passage 40 and low pressure oil passage 41 are short-circuited through the valve port 81, and so the pressure of the high pressure oil passage 40 is lowered to dis-able the feed of pressure oil to the hydraulic motor M to make the hydraulic motor M inoperative. In this case, if a plurality of clutch valves 80 are arranged in the circumferential direction of the high and low pressure oil passag*s 40, 41, the shor~-circuiting resistance of both the oil passages 40, 41 is decreased.
When the clutch control ring 82 is moved to left to operate the clutch valve 80 toward the clutch ON position, the workiny fluid is circulated between the hydraulic pump P and the hydraulic motor M through the high and low pressure oil passages 40, 41 in a manner as previously mentioned, and the hydraulic motor M is returned to its operating condition.
In an intermediate position between the a~oresaid right-ward position and leftward position of the clutch control ring 82, a communication opening between both the oil passages 40, 41 is moderately adjusted and the working fluid may be cirzulated aceord-ing to the degree of opening thereof to place the hydraulic motor M in a half-clutch state.
.
' ~ .
This invention is a third divisional from Canadian Patent Application S.N. 498587 filed December 24, 1985.
The field of the present invention relates to static hydraulic pressure type continuously variable transmissions, and more particularly to such transmissions in which a hydraulic closed circuit is formed between a swashplate type hydraulic pump and a swashplate type hydraulic motor.
A static hydraulic pressure type continuously variable transmission of the type herein referred to is disclosed, for example, in Japanese Patent Application Laid~Open No. 70,968/82 Specification and Japanese Patent Publication No. 38,467/84 Specification.
In conventional static hydraulic pressure type continuously variable transmissions, a motor cylinder and a motor swashplate of a hydraulic motor are independently supported on a casing. This can result in a great thrust load, applied to the motor swashplate from a group of motor plungers in sliding contact with the motor cylinder being borne by the casing during operation. Accordingly, such a casing is preferably formed with a highly rigid wall thickness, which can be heavy.
In addition, a pump cylinder of such a hydraulic pump and a motor cylinder of such a hydraulic motor are concentrically arranged with the former disposed internally of the latter. In such an arrangement the extexnal large-diameter motor cylinder is heavy.
Furthermore, in a conventional static hydraulic pressure type continuously variable transmission, a pump cylinder of the ~29~C~62 hydraulic pump is pressed in sliding contact aga1nst a distribution board fixedly mounted on the motor cylinder of the hydraulic motor so that working fluiZs of the hydraulic pump and hydraulic motor are transferred through an oil path extending through the rotary sliding surfaces. Because of this, pressurized oil tends to leak from between the opposed rotary sliding surfaces of the distribu-tion board and the pump cylinder, leading to deterioration of transmission efficiency due to such leakage.
In addition, in a conventional apparatus provided with a variable capacity swashplate type hydraulic motor, a hydraulic servo is connected to a motor swashplate to lightly adjust an angle of inclination of the motor swashplate, as is well known.
However, the hydraulic servo~motor has a complicated construction and is expensive.
More~ver, in a conventional construction, a clutch valve and its operating system, which control communication between the discharge and intake sides of the hydraulic pump for regulating power transmission from the hydraulic pump to the hydraulic motor, project axially from the end of the hydraulic motor increasing the overall length of he transmission. This is particularly txue where the hydraulic pump and the hydraulic motor are disposed on one and the same axis.
SUMMARY OF THE INVENTION
It is the primary object of the present invention to inexpensively provide a static hydraulic pressuxe type continuously variable transmission which is free from the disadvantages noted ~L~9go62 above, and which is light-weight and small, and has excellent transmission e~ficiency.
The invention herein claimed is a static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder; a hydraulic motor having a motor cyllnder; and a hydraulic closed circuit between the hydraulic pump and motor, the hydraulic closed circuit having a high pressure oil passage and a low pressure oil passage which are defined in the pump and motor cylinders in a manner distanced from each other; wherein a number of cylinder bores are arranged in the pump cylinder and in the motor cylinder to slidably receive therein a number of plungers, respectively; and wherein a number o~ distribution valves ar~ disposed in at least one of the pump cylinder and the motor cylinder, said number of distribution valves being rotatahle in response to rotation of said at least one cylinder and alternately communlcating the cylinder bores of said at least one cylinder with the hlgh pre~sure oil passage and low pressure oil passage, respectively, while being drlven externally of the cylinder to perform a reciprocating movement by a distributor valve driving means which is located outside of said one cylinder.
The invention fur her provides a swashplate type hydraulic system comprising: a cylinder block having a number of cylinder bores annularly arranged therein; a number of plungers each slidably received in one of the cylinders bores; a ~washplate engaging those ends of said plungers which protrude from the cylinder bores; and a high pressure oil passage and a low pressure . !, ;
~L299~62 oil passage which are defined in the cylinder block in a manner distanced from each other; wherein a working oil is transferred between these high and low oil pressura passages and the cylinder bores durin~ relative rotation between the cylinder block and the swashplate; wherein a plurality of distribution valves are disposed in the cylinder block to alternately communicate the cylinder bores with said high pressure oil passage and low : pressure oil passage, respectively, while being urged to perform a reciprocating movement by a distribution valve drivlng means; and wherein said distribution valve driving means is disposed outside of the cylinder block and is adapted to drive the distribution valves at positions outside of the cylinder block in response to the relative rotation between the cylinder block and the swashplate.
~29906~
BRIEF DESCRIPTION OF THE DRAWINGS
The drawings show one embodiment of the present invention.
Figure 1 is a longitudinal plan view of a static hydraulic pressure type continuously variable transmission incorporated in a power transmission system of a motor-cycle;
Figures 2 and 3 are sectional views taken on line II~II
and line III-III, respectively, of Figure l; and Figure 4 is an exploded perspective view of major components of Figure i.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The present application will now be described in the environment of the parent application.
Referring now to the drawings and more particularly to Figure 1, power of a motor-cycle engine is transmitted from a crank shaft 1 to an unshown rear wheel via a chain type primary reduction gear 2, a static hydraulic pressure type continuously variable -.
, ' ~2990~2 transmission T and a chain type secondary reduction gear 3.
The continuously variable transmission T comprises a swashplate type hydraulic pump P of a constant capacity type and a swashplate type hydraulic motor M of a variable capacity type, which are accommodated within a crank case 4 as a casing which carries a crank shaft 1.
The hydraulic pump P comprises a cup-like input member 5 integrally provided with an output sprocket 2a of the primary reduction gear 2. A pump cylinder 7 is relatively rotatably fitted in the inner peripheral wall of the input memher 5 through a needle bearing 6. Pump plungers 9, 9 ... are slidably fitted in a plural-ity and odd-number of annularly disposed cylinder bores 8, 8 provided in the pump cylinder 7 so as to surround the rotary center thereof, and a pump swashplate 10 is in contact with the outer ends of the pump plungers 9, 9 ...
The back surface of the pump swashplate 10 is rotatably supported on the inner end wall of the input member 5 in an atti-tude inclined by a predetermined angle with respect to the axis of the pump cylinder 7 through a thrust roller bearing 11. When input member 5 ~s rotated, the pump plungers 9, 9 .... are recipro-cated to repeatedly effect suction and exhaust strokes.
The back surface of the input member 5 is supported on a support sleeve 13 through a thrust roller bearing 12.
~: On the other hand, the hydraulic motor ~ comprises a motor cylinder 17 coaxially and closely coupled to the pump cylinder 7. A support shaft 24 and an output shaft 25 are ~299062 ~7~ 70488-~
integrally formed to central parts of both inner and outer ends of the motor cylinder 17 and extending in an axial direction. Motor plungers 19, 19 ... are respectively slidably fitted in a plurality and odd-number of annu~arly disposed cylinder~bores 18, 18 ...
provided in the motor cylinder 17 so as to surround the rotary center thereof. A motor swashplate 20 is in contact with outer ends of the motor plungers 19, 19 .... A swashplate holder 22 for supporting the back surface of the motor swashplate 20 through a thrust roller bearing 21 is positioned in a swashplate anchor 23 for suppoxting the back surface of the swashplate holder 22.
The motor swashplate 20 is tiltingly movable between an upright position at right angles to the axis of the motor cylinder 17 and a position inclined at a certain angle. At the inclined position, the motor plungers 19, 19 ... are reciprocated upon rotation of the motor cylinder 17 to repeatedly effect expansion and contraction strokes.
The aforesaid support shaft 24 extends through the cen-tral portion of the pump cylinder 7. A nut 26 is threadedly en-gaged with the support shaft 24 to retain the pump cylinder 7 and the motor cylinder 17 integrally connected to each other. The support shaft 24 further extends through the input member 5 and rotatably supports the input member 5 through a needle bearing 27.
On the outer periphery of the support shaft 24, the support sleeve 13 is splined-fitted and secured by means of a nut 30. The support shaft 24 is rotatably supported in the cran~ case 4 through the support tube 13 and a roller bearing 31.
129~0~i2 The aforesaid output shaft 25 extends through the central portion of the motor swashplate 20, the swashpla~e holder 22 and the swashplate anchor 23. A support sleeve 33 for support-ing the back surface of the swashplate anchor 23 through a thrust roller bearing 32 is splined-fitted to the end of the shaft 25 and is secured by means of a nut 34 with an input sprocket 3a of the secondary reduction gear 3. The output shaft 25 is rotatably supported on the crank case 4 through the support sleeve 33 and a roller bearing 35.
Secured to the support shaft 24 is a spherical spline member 36 in spline engagement with the lnner peripheral surface of the pump swashplate 10 in a manner relatively tiltable in all directions, and secured to the output shaft 25 is a spherical spline member 37 in spline engagement with the inner peripheral surface of the motor swashplate 20 relatively tiltably in all directions. The couplings of the spiral spline members 36 and 37 with the swashplates 10 and 20 suppresses to a minimal extent frictional contact between the group of pump plungers 9, 9 ... and the pump swashplate 10 and between the motor plungers 19, 19 and the motor swashplate 20.
Between the hydraulic pump P and the hydraulic motor M
is formed a hydraulic closed circuit as described hereinafter.
In the motor cylinder 17, an annular high pressure oil passage 40 and an annular low pressure oil passage 41 to encircle the oil passage 40 are provided between the group of cylinder bores 8, 8 ... of the pump cylinder 7 and the group of cylinder bores ~L299~2 _9_ 70488-~
18, 18 ... of the motor cylinder 17. The high pressure oil pas-sage 40 communicates ~ith the cylinder bores 8, 8 ... of the pump cylinder 7 through discharge valves 42, 42 .... The low pressure oil passage 41 also communicates with the cylinder bores 8, 8 ...
through intake valves 43, 43 ... Accordingly, the discharge valves 42 and the intake valves 43 are respectively provided in the same number as that of the pump plungers 9, 9 ....
These high and low pressure oil passages 40, 41 are both communicated with the cylind~er bores 18, 18 ... of the motor cylinder 17 through respective distribution valves 44, 44 Accordingly, the distribution valves 44 are provided in the same number as that of the motor plungers 19, 19 .O..
The distribution valves 44, 44 ..., which are of a spool type, are slidably fitted into valve holes 45, 45 ... radlally provided in the motor cylinder 17 between the group of cylinder bores 18, 18 ... and the high and low pressure oil passages 40, 41.
When the valve 44 occupies the radial inward position in the valve hole 45, there is provided a communication between the corresponding cylinder bore 18 and high pressure oil passage 40 whilst the cylinder bore 18 is shut off from the low pressure oil passage 41, and when the valve 44 occupies the radial outward position in the valve hole 45, there is provided a communication between the cor-responding cylinder bore 18 and low pressure oil passage 41 whilst the bore is cut o~f its communication with the high pressure oil passage 40.
Valve springs 46, 46 ... for biasing the distribution valves 44, 44 ... radially and outwardly are accommodated within the valve holes 45, 45 ... to control the distribution valves 44, 44 ..., and the inner peripheral surface of an eccentric ring 47 is engaged with the outer end of each distribution valve 44.
The eccentric ring 47 is formed of an inner race of a ball bearing 48 snapped in and secured to the crank case 4, and as shown in Figure 2. The ring 47 is installed at such a position that the center thereof is to be eccentric a 2redetermined distance ~ from the center of the motor cylinder 17 in a direction of the tilting axis 0 of the motor swashplate 20. Accordingly, when the motor cylinder rotates, each of the distribution valves 44 takes the stroke of 2 , which is twice of the eccentric amount Ç of the eccentric ring 47, within the valve hole 45 and reciprocates be-tween the aforesaid outward position and inward position.
The distribution valve 44 also functions to bring a replenishing oil passage 49 into communication with the low pres-sure oil passage 41 when the valve assumes the inward position in the valve hole 45. The replenishing oil passage 49 is provi~ed in the central portion of the support shaft 24 and connected to the discharge port of a replenishing pump 50.
The pump 50 is driven by the crank shaft 1 to supply oil stored in an oil reservoir 51 at the bottom of the crank case 4 to the oil passage 49 under relatively low pressure.
Referrlng to Figures 1, 3 and 4, an outer peripheral surface 20a of the moior swashplate 20 is formed into a spherical surface having its center at the tilting axis 0. A spherical recess 52 is formed in the front surface of the swashplate hoIder ~' ~29.~06~:
22 so as to receive the motor swashplate 20 along with the thrust roller bearing 21. A back surface 22a of the swashplate holder 22 is formed in a circular surface about the tilting axis 0 of the motor swashplate 20, and a semi-cylindrical recess 53 is formed in the front surface of the swashplate anchor 23 so as to support the swashplate holder 22 rotatably about the tilting axis O. This swashplate anchor 23 is connected to the crank case 4 through locating pins 54 so that the anchor may not be rotated about the output shaft 25.
A pair of trunnion shafts SS, 55' aligned on the tilting axis O are integrally projected on both ends of the swashplate holder 22, the trunnion shafts 55, 55' being rotatably supported on the swashplate anchor 23 throùgh needle bearings 56. In other words, the tilting axis 0 is defined by the trunnion shafts 55, 55'.
An operating lever 57 is fixedly mounted on the outer end of one trunnion shaft 55.
When the trunnion sha~t 55 is rotated by the operating lever 57, the swashplate holder 22 integral therewith also rotates and the latter can be tilted even during the rotation of :~ the motor swashplate 20.
With the arrangement as described above, when the input member 5 of the hydraulic pump P is rotated from the primary reduction gear 2, suction and exhaust strokes are alternately im-parted by the pump swashplate 10 to the pump plungers 9, 9 Then, each pump plunger 9, in suction stroke~ intakes worklng fluid ~L29~)62 -12- 70488-~
from the low pressure oil passage 41, and in exhaust stroke, feeds high press~re working fluid to the high pressure oil passage 40.
The high pressure working fluid fed to the high pres-sure oil passage 40 is supplied to a cylinder bore 18 through the distribution valve 44 at the inward position to force a motor plunger 19 in an expansion stroke. The working fluid within a cylinder bore 18 being moved by a motor plunger 19 in a contrac-tion stroke is discharged into the low pressure oil passage 41 through the distribution valve 44 at the outward position.
During this operation, the p~np cylinder 7 and motor cylinder 17 are rotated by the sum of reaction torque received by the pump cylinder 7 from the pump swashplate 10 through the pump plungers 9 in an exhaust stroke and reaction torque received by the motor cylinder 17 from the motor swashplate 20 through the motor plunger 19 in an expansion stroke. This rotary torque is trans-mitted from the output shaft 25 to the secondary reduction gear 3.
In this case, the speed change ratio of the output shaft 25 with respect to the input member 5 is given by the following equation:
Speed change - Capacity of hydraulic motor M
speed ratio 1 Capacity of hydraulic pump P
Thus~ if the capacity of the hydraulic motor M is changed from zero to a certain value, the speed change ratio can changed from 1 to a required value.
Incidentally, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, the motor '~.
.
1;~9~0~i2 -13- 70488-~
swashplate 20 can be tilted from an upright position to an inclined position to thereby steplessly control the ratio from 1 to a cer-tain value.
During the operation of the hydraulic pump P and hydrau-lic motor M as described above, the pump swashplate 10 and motor swashplate 20 receive the opposite thrust load from the group of pump plungers 9, 9 ... and the group of motor plungers 19, 19, ...
respectively. The thrust load applied to the pump swashplate 10 is carried by the support shaft 24 through the thrust roller bearing 11, input member 5, thrust roller bearing 12, support sleeve 13 and nut 30. The thrust load applied to the motor swash-plate 20 is carried by the output shaft 25 through the thrust roller bearing 21, swashplate holder 22j swashplate anchor 23, thrust roller bearing 32, support sleeve 33, sprocket 3a and nut 34. Since the support shaft 24 and output shaft 25 are integrally connected together through the motor cylinder 17, the aforesaid thrust load merely gives rise to tensile stress caused in the motor cylinder 17 system and exerts no action on the crank case 4 which supports the support shaft 24 and the output shaft ~5~
If worklng fluid~leaks from the hydraulic closed circuit between the hydraulic pump P and the hydraulic motor M during the aforementioned operation, when the distribution valve 44 assumes the inward position in the valve hole 45, working fluid in the leaked amount is replenished from the replenishing oil passage 49 to the low pressure oil passage 41 through that distribution valve 45.
~99~
Turning again to Figure 1, a speed change control device 60 is connected to the operating lever 57 of the trunnion shaft 55 for the tilting operation of the motor swashplate 20.
The speed change control device 60 comprises a cylinder 61 secured to the swashplate anchor 23, and a pair of first and second pistons 621, 622 which are slidably fitted in the cylinder 61 and are oppo-sed to each other so as to hold a tip end of the operating lever 57 therebetween in their rotary direction. The pistons 621, 622 are arranged so as to enable rotation of the operating lever 57 by their sliding movement.
The first and second pistons 621, 622 define first and second oil chambers 631~ 632 against respective opposed end walls of the cylinder 61. There chambers 631, 632 accommodate therein springs 641, 642 for urging the corresponding pistons 621, 622 to-- ward the operating lever 57.
The first and second oil chambers 631r 632 communicate with each other through a hyaraulic conduit 66 incorporating there-in a speed change control valve 65. The conduit is fi}led working fluid.
The speed change control valve 65 comprises a fixed valve casing 67 and a rotary valve 69 rotatably fitted in a valve port 68 of the valve casing 67. The rotary valve 69 is operated for rotation between a hold position A, a speed reduction position B and a speed increasing position C on hoth sides of the position A by means of a speed change lever 70 secured to the outer end of the rotary valve 69.
90~Z
-15- 70488~
The rotary valve 69 is provided with a communication port 72 incorporating a check valve 71. The valve casing 67 in-cludes a irst forked port 731 connected to the first oil chamber 631 and opening to one side of the valve port 68, and a second forked port 732 connected to the second oil chamber 632 and open-ing to the other side of the valve port 68. The communication port 72 is designed such that in`the hold position A of the rotary valve 69, the communication port 72 does not communicate with either forked ports 731~ 732; in the speed reduction position B, the port 72 communicates with both the forked ports 731~ 732 to allow a flow of oil only in one direction from the former 731 to the latter 732; and in the speed increasing position C, the port 72 communicates with both forked ports 731~ 732 50 as to allow oil flow only in the direction from the latter 732 to the former 731.
Since the:number of the motor plungers 19, 19 ... is odd, the thrust load applied by the group of motor plungers 19, 19 ... to the motor swashplate 20 during the rotation of the motor cylinder 17 alternately varies in intensity between one side and the other with the-tilting axis of the motor swashplate 20 as a border. Vibratory tilting ~orque acts on the motor swashplate 20.
This vibratory tilting torque alternately acts as a pressing force on the first and second pistons 621, 622 through the operating lever 57.
With this, when the speed change lever 70 is shifted to the reduction position B as shown, the flow of oil from the first oil chamber 631 to the second oil chamber 632 is permitted by ~29~062 the check valve 71 but the opposite flow is inhibited. Thus, when the pressing ~orce acts on the first piston 621 from the operating lever 57, the oil flows from the first oil chamber 631 to the second oil chamber 632. As a consequence of this, both the pistons 621, 622 are moved toward the first oil chamber 631 to turn the operating lever 57 in the direction of increasing the inclina-tion of the motor swashplate 20.
When the lever 70 is shifted to the increasing position C, the flow of oil from the second oil chamber 632 to the first oil chamber 631 is permitted by the check valve 71 but the opposite flow is inhibited. Thus, when the pressing force acts on the second piston 622 from the operating lever 57, the oil flows from : the second oil chamber 632 to the first oil chamber 531~ As a consequence of this, both the pistons 621, 622 are moved toward the second oil chamber 632 to turn the operating lever 57 toward the upright position of the motor swashplate 20.
When the speed change lever 70 is returned to the hold position A, communication between both the oil chambers 631, 632 is completely cut off and the flow of oil therebetween is inhibited.
Therefore, both the pistons~621, 622 become unable to move. The operating lever 57 is held at its position to lock the motor swash-plate 20 at the upright position or incl~ned position.
Between the high and low pressure oil passages 40, 4I, there is provided one or more piston type clutch valves 80. This ; clutch valve 80 is slidably fitted in a radial valve port ~1 which extends from the high pressure oil passage 40 to the low pressure , . . .
~L299062 oil passage 40 and opens to the outer peripheral surface of the motor cylinder 17. When the valve occupies the radial inward position (clutch ON position) in the valve port 81, both the oil passages 40, 41 are interrupted. When the valve occupies the radial outward position (clutch OFF position), both the oil passages 40, 41 are brought into communication with each other.
In order that the clutch valve 80 is urged toward the clutch OFF position, the inner end thereof receives oil pressure from the high pressure oil passage 40. A common clutch control ring 82 is slidably provided around the outer periphery of the pump cylinder 7 and is engaged with the outer end of valve a.
The clutch control ring 82 includes a cylindrical inner peripheral surface 82a for defining the clutch ON position of the clutch valve 80 and a tapered surface 82b joined to one end o said inner peripheral surface to define the clutch OFF position of the clutch valve 80. The ring is urged by means of a spring 83 toward - the side wherein the clutch valve 80 is held in the clutch ON posi-tion. This spring 83 is compressed between~the clutch control ring 82 and a retainer 84 engaged on the outer periphery of the pump cylinder 7.
The clutch control ring 82 is connected to a not-shown clutch operating lever through a shift fork 85, an intermediate lever 86 and a clutch wire 87. The shift fork 85 engages an outer peripheral groove 88 of the clutch control ring 82, and an operat-ing rod 89 secured to the base of the shift fork 85 extends through the crank case 4 and is operatively connected to the intermediate 1291~62 lever 86.
With this, when the clutch control ring 82 is moved to the right as viewed in the figure against the force of the spring 83 through the shift fork 85 by pulling the clutch wire 87, the tapered surface 82b of the clutch control ring 82 assumes a posi-tion opposed to the clutch valve 80. Therefore the clutch valve 80 is moved by the pressure of the high pressure oil passage 40 to the outward position, namel~, to the clutch OFF position. As the result, the high pressure oil passage 40 and low pressure oil passage 41 are short-circuited through the valve port 81, and so the pressure of the high pressure oil passage 40 is lowered to dis-able the feed of pressure oil to the hydraulic motor M to make the hydraulic motor M inoperative. In this case, if a plurality of clutch valves 80 are arranged in the circumferential direction of the high and low pressure oil passag*s 40, 41, the shor~-circuiting resistance of both the oil passages 40, 41 is decreased.
When the clutch control ring 82 is moved to left to operate the clutch valve 80 toward the clutch ON position, the workiny fluid is circulated between the hydraulic pump P and the hydraulic motor M through the high and low pressure oil passages 40, 41 in a manner as previously mentioned, and the hydraulic motor M is returned to its operating condition.
In an intermediate position between the a~oresaid right-ward position and leftward position of the clutch control ring 82, a communication opening between both the oil passages 40, 41 is moderately adjusted and the working fluid may be cirzulated aceord-ing to the degree of opening thereof to place the hydraulic motor M in a half-clutch state.
.
' ~ .
Claims
THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINIED AS FOLLOWS:
1. A static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder;
a hydraulic motor having a motor cylinder; and a hydraulic closed circuit between the hydraulic pump and motor, the hydraulic closed circuit having a high pressure oil passage and a low pressure oil passage which are defined in the pump and motor cylinders in a manner distanced from each other; wherein a number of cylinder bores are arranged in the pump cylinder and in the motor cylinder to slidably receive therein a number of plungers, respectively; and wherein a number of distribution valves are disposed in at least one of the pump cylinder and the motor cylinder, said number of dis-tribution valves being rotatable in response to rotation of said at least one cylinder and alternately communicating the cylinder bores of said at least one cylinder with the high pressure oil passage and low pressure oil passage, respectively, while being driven externally of the cylinder to perform a reciprocating move-ment by a distributor valve driving means which is located outside of said one cylinder.
2. The transmission of claim 1, wherein said distribution valves project outside from the at least one cylinder and at projecting parts thereof engage the distribution valve driving means.
3. The transmission of claim 1, wherein the high and low pressure oil passages are disposed concentrically with respect to each other.
4. The transmission of claim 3, wherein said distribution valves are arranged radially in said at least one cylinder and are adapted to reciprocate between radially inner and outer positions in the one cylinder.
5. The transmission of claim 1 or 4, wherein said distribution valves are provided for the respective cylinder bores.
6. The transmission of claim 1, wherein said distribution valves project outside from the at least one cylinder and at projecting parts thereof engage the distribution valve driving means and wherein said distribution valves are arranged radially in said at least one cylinder and are adapted to reciprocate between radially outer and inner positions in that cylinder.
7. A swashplate type hydraulic system comprising: a cylinder block having a number of cylinder bores annularly arranged therein;
a number of plungers each slidably received in one of the cylinder bores; a swashplate engaging those ends of said plungers which protrude from the cylinder bores; and a high pressure oil passage and a low pressure oil passage which are defined in the cylinder block in a manner distanced from each other; wherein a working oil is transferred between these high and low oil pressure passages and the cylinder bores during relative rotation between the cylinder block and the swashplate; wherein a plurality of distribution valves are disposed in the cylinder block to alternately communicate the cylinder bores with said high pressure oil passage and low pressure oil passage, respectively, while being urged to perform a re-ciprocating movement by a distribution valve driving means; and wherein said distribution valve driving means is disposed outside of the cylinder block and is adapted to drive the distribution valves at positions outside of the cylinder block in response to the relative rotation between the cylinder block and the swashplate.
8. The system of claim 7, wherein said high and low pressure oil passages are disposed concentrically with respect to each other.
9. The system of claim 7, wherein said swashplate is supported by a member which is rotatable relative to the cylinder block.
10. The system of claim 7, wherein said distribution valves are arranged radially in the cylinder block.
11. The system of claim 10, wherein said distribution valves are adapted to reciprocate between radially inner and outer positions in the cylinder block.
12. The system of claim 11, wherein said high and low pressure oil passages are disposed concentrically with respect to each other.
13. The system of claim 7, wherein the distribution valves are disposed for the respective cylinder bores.
14. The system of claim 7, wherein said distribution valves project outside of the cylinder block and are placed in engagement with and driven by said distribution valve driving means at positions outside of the cylinder block.
15. The system of claim 14, wherein said high and low pressure oil passages are disposed concentrically with respect to each other whereas the distribution valves are arranged radially in the cylinder block and are adapted to reciprocate between radially inner and outer positions in the cylinder block.
16. The system of claim 15, wherein the distribution valves are disposed for the respective cylinder bores.
17. A static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder;
a hydraulic motor having a motor cylinder; a hydraulic closed circuit between said hydraulic pump and motor; and a transmission shaft; said pump cylinder and said motor cylinder being integrally connected with each other to form a cylinder block which is dis-posed on said transmission shaft; wherein a number of pump cylinder bores are arranged in said pump cylinder and a number of motor cylinder bores are arranged in said motor cylinder; wherein said hydraulic closed circuit is integrally formed with said cylinder block between said pump cylinder and said motor cylinder and comprises a high pressure oil passage and a low pressure oil passage, said pump cylinder bores and motor cylinder bores being placed in communication with said high pressure oil passage and said low pressure oil passage via a distribution device; said distribution device comprising a plurality of distribution valves which are rotatable in response to rotation of said cylinder block and which are operable to alternately communicate said motor and pump cylinder bores with said high pressure oil passage and low pressure oil passage, respectively, said distribution valves pro-jecting outside of said cylinder block and at projected parts there-of engaging with and being driven by a distribution valve driving means which is disposed outside of said cylinder block.
18. The transmission of claim 17, wherein said high pressure oil passage and said low pressure oil passage are arranged annularly within said cylinder block and one of said oil passages encircles the other, and wherein said distribution valves reciprocate between said annular high and low pressure oil passages.
19. The transmission of claim 18, wherein said annular high and low pressure oil passages are disposed concentrically with said transmission shaft and said distribution valves perform reciprocat-ing motions between a radially inner position and a radially outer position in the cylinder block.
20. The transmission of claim 19, wherein said distribution valve driving means is an eccentric ring positioned eccentric with respect to an axis of said cylinder block.
21. The transmission of claim 20, wherein said plurality of distribution valves are disposed in a radial arrangement.
22. The transmission of claim 17, wherein each of the dis-tribution valves receives at an inner end thereof an oil pressure urging the valve toward said distribution valve driving means.
23. The transmission of claim 17, wherein said distribution valves place said motor cylinder bores into alternate communication with said high pressure oil passage and said low pressure oil passage.
24. The transmission of claim 17, wherein said low pressure oil passage is communicated with an oil feed passage.
25. A static hydraulic pressure type continuously variable transmission comprising: a swashplate type hydraulic pump having a pump cylinder and a number of pump cylinder bores annularly arranged in said pump cylinder; a swashplate type hydraulic motor having a motor cylinder and a number of motor cylinder bores annularly arranged in said motor cylinder; a hydraulic closed circuit between said hydraulic pump and said hydraulic motor; and an output shaft; said pump cylinder and said motor cylinder being integrally connected to said output shaft; wherein said hydraulic closed circuit comprises an annular high pressure oil passage communicating with all the pump cylinder bores through a discharge valve, an annular low pressure oil passage communicating with the pump cylinder bores through an intake valve, said high and low pressure oil passages being formed concentrically with respect to each other between said pump cylinder bores and said motor cylinder bores, and a distribution valve adapted to reciprocate between a radial outward position and a radial inward position so as to bring said motor cyllnder bores into alternate communication with said high and low pressure oil passages, said distribution valve projecting outside of said motor cylinder and being associated at a projected part thereof with an eccentric actuating device and being driven to make reciprocating motion by the eccentric actuating device located outside of the motor cylinder in response to rotation of said pump cylinder and said motor cylinder whereby each of said motor cylinder bores is brought into communication with said high pressure oil passage during expansion strokes thereof and is brought into communication with said low pressure oil passage during contraction strokes thereof.
26. The transmission of claim 25, wherein a plurality of said distribution valves are radially provided.
27. The transmission of claim 26, wherein the number of said distribution valves corresponds to that of said motor cylinder bores.
28. The transmission of claim 25, wherein said eccentric actuating device comprises an eccentric ring having a center located at a position eccentric with respect to the axis of rotation of said motor cylinder.
29. The transmission of claim 28, wherein said eccentric ring is supported on a casing.
30. The transmission according to claim 28, wherein said eccentric ring is formed by an inner race of a ball bearing secured to a casing.
31. The transmission of claim 25, 26, or 27 wherein said distribution valve brings said low pressure oil passage into com-munication with a replenishing oil passage when said low pressure oil passage is cut off communication with said motor cylinder bores.
32. The transmission of claim 25, 26, 27, 28, 29 or 30 wherein said hydraulic motor is of a variable capacity type.
33. The transmission of claim 31, wherein said hydraulic motor is of a variable capacity type.
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINIED AS FOLLOWS:
1. A static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder;
a hydraulic motor having a motor cylinder; and a hydraulic closed circuit between the hydraulic pump and motor, the hydraulic closed circuit having a high pressure oil passage and a low pressure oil passage which are defined in the pump and motor cylinders in a manner distanced from each other; wherein a number of cylinder bores are arranged in the pump cylinder and in the motor cylinder to slidably receive therein a number of plungers, respectively; and wherein a number of distribution valves are disposed in at least one of the pump cylinder and the motor cylinder, said number of dis-tribution valves being rotatable in response to rotation of said at least one cylinder and alternately communicating the cylinder bores of said at least one cylinder with the high pressure oil passage and low pressure oil passage, respectively, while being driven externally of the cylinder to perform a reciprocating move-ment by a distributor valve driving means which is located outside of said one cylinder.
2. The transmission of claim 1, wherein said distribution valves project outside from the at least one cylinder and at projecting parts thereof engage the distribution valve driving means.
3. The transmission of claim 1, wherein the high and low pressure oil passages are disposed concentrically with respect to each other.
4. The transmission of claim 3, wherein said distribution valves are arranged radially in said at least one cylinder and are adapted to reciprocate between radially inner and outer positions in the one cylinder.
5. The transmission of claim 1 or 4, wherein said distribution valves are provided for the respective cylinder bores.
6. The transmission of claim 1, wherein said distribution valves project outside from the at least one cylinder and at projecting parts thereof engage the distribution valve driving means and wherein said distribution valves are arranged radially in said at least one cylinder and are adapted to reciprocate between radially outer and inner positions in that cylinder.
7. A swashplate type hydraulic system comprising: a cylinder block having a number of cylinder bores annularly arranged therein;
a number of plungers each slidably received in one of the cylinder bores; a swashplate engaging those ends of said plungers which protrude from the cylinder bores; and a high pressure oil passage and a low pressure oil passage which are defined in the cylinder block in a manner distanced from each other; wherein a working oil is transferred between these high and low oil pressure passages and the cylinder bores during relative rotation between the cylinder block and the swashplate; wherein a plurality of distribution valves are disposed in the cylinder block to alternately communicate the cylinder bores with said high pressure oil passage and low pressure oil passage, respectively, while being urged to perform a re-ciprocating movement by a distribution valve driving means; and wherein said distribution valve driving means is disposed outside of the cylinder block and is adapted to drive the distribution valves at positions outside of the cylinder block in response to the relative rotation between the cylinder block and the swashplate.
8. The system of claim 7, wherein said high and low pressure oil passages are disposed concentrically with respect to each other.
9. The system of claim 7, wherein said swashplate is supported by a member which is rotatable relative to the cylinder block.
10. The system of claim 7, wherein said distribution valves are arranged radially in the cylinder block.
11. The system of claim 10, wherein said distribution valves are adapted to reciprocate between radially inner and outer positions in the cylinder block.
12. The system of claim 11, wherein said high and low pressure oil passages are disposed concentrically with respect to each other.
13. The system of claim 7, wherein the distribution valves are disposed for the respective cylinder bores.
14. The system of claim 7, wherein said distribution valves project outside of the cylinder block and are placed in engagement with and driven by said distribution valve driving means at positions outside of the cylinder block.
15. The system of claim 14, wherein said high and low pressure oil passages are disposed concentrically with respect to each other whereas the distribution valves are arranged radially in the cylinder block and are adapted to reciprocate between radially inner and outer positions in the cylinder block.
16. The system of claim 15, wherein the distribution valves are disposed for the respective cylinder bores.
17. A static hydraulic pressure type continuously variable transmission comprising: a hydraulic pump having a pump cylinder;
a hydraulic motor having a motor cylinder; a hydraulic closed circuit between said hydraulic pump and motor; and a transmission shaft; said pump cylinder and said motor cylinder being integrally connected with each other to form a cylinder block which is dis-posed on said transmission shaft; wherein a number of pump cylinder bores are arranged in said pump cylinder and a number of motor cylinder bores are arranged in said motor cylinder; wherein said hydraulic closed circuit is integrally formed with said cylinder block between said pump cylinder and said motor cylinder and comprises a high pressure oil passage and a low pressure oil passage, said pump cylinder bores and motor cylinder bores being placed in communication with said high pressure oil passage and said low pressure oil passage via a distribution device; said distribution device comprising a plurality of distribution valves which are rotatable in response to rotation of said cylinder block and which are operable to alternately communicate said motor and pump cylinder bores with said high pressure oil passage and low pressure oil passage, respectively, said distribution valves pro-jecting outside of said cylinder block and at projected parts there-of engaging with and being driven by a distribution valve driving means which is disposed outside of said cylinder block.
18. The transmission of claim 17, wherein said high pressure oil passage and said low pressure oil passage are arranged annularly within said cylinder block and one of said oil passages encircles the other, and wherein said distribution valves reciprocate between said annular high and low pressure oil passages.
19. The transmission of claim 18, wherein said annular high and low pressure oil passages are disposed concentrically with said transmission shaft and said distribution valves perform reciprocat-ing motions between a radially inner position and a radially outer position in the cylinder block.
20. The transmission of claim 19, wherein said distribution valve driving means is an eccentric ring positioned eccentric with respect to an axis of said cylinder block.
21. The transmission of claim 20, wherein said plurality of distribution valves are disposed in a radial arrangement.
22. The transmission of claim 17, wherein each of the dis-tribution valves receives at an inner end thereof an oil pressure urging the valve toward said distribution valve driving means.
23. The transmission of claim 17, wherein said distribution valves place said motor cylinder bores into alternate communication with said high pressure oil passage and said low pressure oil passage.
24. The transmission of claim 17, wherein said low pressure oil passage is communicated with an oil feed passage.
25. A static hydraulic pressure type continuously variable transmission comprising: a swashplate type hydraulic pump having a pump cylinder and a number of pump cylinder bores annularly arranged in said pump cylinder; a swashplate type hydraulic motor having a motor cylinder and a number of motor cylinder bores annularly arranged in said motor cylinder; a hydraulic closed circuit between said hydraulic pump and said hydraulic motor; and an output shaft; said pump cylinder and said motor cylinder being integrally connected to said output shaft; wherein said hydraulic closed circuit comprises an annular high pressure oil passage communicating with all the pump cylinder bores through a discharge valve, an annular low pressure oil passage communicating with the pump cylinder bores through an intake valve, said high and low pressure oil passages being formed concentrically with respect to each other between said pump cylinder bores and said motor cylinder bores, and a distribution valve adapted to reciprocate between a radial outward position and a radial inward position so as to bring said motor cyllnder bores into alternate communication with said high and low pressure oil passages, said distribution valve projecting outside of said motor cylinder and being associated at a projected part thereof with an eccentric actuating device and being driven to make reciprocating motion by the eccentric actuating device located outside of the motor cylinder in response to rotation of said pump cylinder and said motor cylinder whereby each of said motor cylinder bores is brought into communication with said high pressure oil passage during expansion strokes thereof and is brought into communication with said low pressure oil passage during contraction strokes thereof.
26. The transmission of claim 25, wherein a plurality of said distribution valves are radially provided.
27. The transmission of claim 26, wherein the number of said distribution valves corresponds to that of said motor cylinder bores.
28. The transmission of claim 25, wherein said eccentric actuating device comprises an eccentric ring having a center located at a position eccentric with respect to the axis of rotation of said motor cylinder.
29. The transmission of claim 28, wherein said eccentric ring is supported on a casing.
30. The transmission according to claim 28, wherein said eccentric ring is formed by an inner race of a ball bearing secured to a casing.
31. The transmission of claim 25, 26, or 27 wherein said distribution valve brings said low pressure oil passage into com-munication with a replenishing oil passage when said low pressure oil passage is cut off communication with said motor cylinder bores.
32. The transmission of claim 25, 26, 27, 28, 29 or 30 wherein said hydraulic motor is of a variable capacity type.
33. The transmission of claim 31, wherein said hydraulic motor is of a variable capacity type.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP277816/84 | 1984-12-26 | ||
| JP59277816A JPS61153057A (en) | 1984-12-26 | 1984-12-26 | Static hydraulic type continuously variable transmission |
| CA000498587A CA1279233C (en) | 1984-12-26 | 1985-12-24 | Static hydraulic pressure type continuously variable transmission |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000498587A Division CA1279233C (en) | 1984-12-26 | 1985-12-24 | Static hydraulic pressure type continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1299062C true CA1299062C (en) | 1992-04-21 |
Family
ID=25670880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000615888A Expired - Fee Related CA1299062C (en) | 1984-12-26 | 1990-10-05 | Continuosly variable transmission having distribution valve means |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1299062C (en) |
-
1990
- 1990-10-05 CA CA000615888A patent/CA1299062C/en not_active Expired - Fee Related
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| Date | Code | Title | Description |
|---|---|---|---|
| MKLA | Lapsed |