JP3497322B2 - Continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission mainly applied to motorcycles, automobiles and other vehicles.

[0002]

2. Description of the Related Art As a continuously variable transmission, for example, Japanese Patent Publication No. 7-2
As disclosed in Japanese Patent No. 6676, it is known that a fixed displacement axial hydraulic pump and a variable displacement axial hydraulic motor are coaxially arranged and are connected via a hydraulic closed circuit.

[0003]

In the continuously variable transmission as described above, the axial hydraulic pump and the hydraulic motor extending relatively long in the axial direction are arranged in the axial direction, so that the axial dimension is long as a whole. Inevitably, it is difficult to make it compact.

The present invention has been made in view of such circumstances, and an object thereof is to provide a compact continuously variable transmission whose axial dimension is greatly reduced.

[0005]

In order to achieve the above object, the present invention has an input shaft and an output shaft arranged coaxially, and is radially arranged on a cylinder body fixedly mounted on the input shaft. a plurality of first plungers, together with these first plunger surrounds engaged relatively movably in their outer ends, impart reciprocating each first plunger with the rotation of the sheet <br/> cylinder body , First of which its reciprocating stroke can be adjusted
It constitutes a radial type first hydraulic pump of the variable capacity pump ring and surrounding a plurality of second plunger disposed radially in said cylinder body, these second plunger while being fixed to said output shaft to relatively movable engaged with their outer ends, fixed displacement radial type second hydraulic pressure and a second pump ring to provide a reciprocating movement of a constant stroke each second plunger with the relative rotation between said cylinder body configure pump, to further the cylinder body, a high pressure oil passage discharged hydraulic oil from the second hydraulic pump while being sucked hydraulic oil to the <br/> first hydraulic pump, the first
A low pressure oil passage sucked hydraulic oil to the second hydraulic pump with discharged hydraulic oil from the hydraulic pump is provided, wherein the
A mission containing one hydraulic pump and a second hydraulic pump
Bearings for the input shaft and output shaft in the case respectively
The first feature is that it is supported through .

[0006] The present invention, in addition to the first feature, by controlling the eccentric direction and the eccentric amount with respect to the cylinder body of the <br/> first pump ring, the capacity of the first hydraulic pump The second feature is that the setting can be made equal to that of the second hydraulic pump.

[0007] The present invention, in addition to the first or second aspect may set the first pump ring to zero capacity of the first hydraulic pump by shifting concentrically positions of the cylinder body This is the third feature.

Furthermore, the present invention is directed to the first, second or third aspect.
In addition to features, by reversing the direction of eccentricity with respect to the cylinder body of the first pump ring, the first
The fourth characteristic is that the hydraulic pump discharges the hydraulic oil to the high pressure oil passage and can suck the hydraulic oil from the low pressure oil passage.

[0009] Furthermore, the present invention includes first, second, in addition to the third or fourth feature, the cylinder body is fixed fitted to the outer periphery of the input shaft, and these cylinder body
With a low pressure oil passage is formed annularly between the opposed circumferential surfaces of the input shaft, which communicates with the oil reservoir, that is formed annularly on the cylinder body a high pressure oil passage so as to surround the low-pressure oil path first It is characterized by 5.

Furthermore, the present invention is directed to the first, second, third,
In addition to the fourth or fifth aspect, the input shaft and the output shaft
Support the outer end to the mission case via bearings.
On the other hand, at the inner end of the output shaft, through a bearing
A support cylinder that supports the inner end of the input shaft is integrally formed, and
Support cylinder is supported on the mission case via bearings
The second pump ring integrally with the tip of the support cylinder.
The sixth feature is that they are connected in series .

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention will be described based on the embodiments of the present invention shown in the accompanying drawings.

In FIG. 1, 1 is an input shaft connected to a motor of a vehicle, 2 is an output shaft connected to drive wheels of the vehicle, and these shafts 1 and 2 are coaxially arranged and continuously variable transmission according to the present invention. It is connected via the machine T.

At the inner end of the output shaft 2, a support cylinder 3 concentrically surrounding the inner end of the input shaft 1 is integrally formed. Between the support cylinder 3 and the input shaft 1, both shafts 1, 2 are provided. The ball bearing 4 that allows the relative rotation of the above is inserted.

The input and output shafts 1 and 2 are supported by ball bearings 6 and 7 at the left and right ends of a mission case 5 accommodating the continuously variable transmission T, and the support cylinder 3 is further attached to the transmission case 5. Is supported by a ball bearing 8 at an intermediate portion of. And the ball bearing 6
Between the input shaft 1 and the mission case 5 outside the
An oil seal 9 is installed, and a ball bearing 7,
8 between the output shaft 2 and the mission case 5
The il seal 10 is interposed.

The continuously variable transmission T is constructed by connecting a variable displacement radial type first hydraulic pump P ₁ and a constant displacement radial type second hydraulic pump P ₂ to each other via a hydraulic closed circuit. .

As shown in FIGS. 1 and 2, the first hydraulic pump P ₁ is provided on a cylinder body 12 concentrically connected to the input shaft 1 via a spline 11 so as to open on the outer peripheral surface thereof. A plurality of radial arrays (5 in the illustrated example)
Main cylinder holes 13 and first plungers 14 slidably fitted in these cylinder holes 13, respectively.
A first pump ring 15 is provided which surrounds the group of plungers 14 and engages with the outer ends thereof so as to be slidable in the circumferential direction. The first plunger 14 is provided in each first cylinder hole 13. A spring 16 for urging in the engagement direction with 15 is housed.

A boss 15a formed on one side of the first pump ring 15 is supported by the transmission case 5 via a pivot 17 parallel to the input shaft 1, and is predetermined to one side of the cylinder body 12. Distance e ₁ (see FIG. 7 (a)) is eccentric to a first eccentric position A and a predetermined distance e ₂ (see FIG. 10 (a)) is eccentric to a second eccentric position C which is eccentric. It is designed to be movable, and an eccentric position (see FIG. 9 (a)) B concentric with the cylinder body 12 exists between the eccentric positions A and C. First pump ring 1
The first and second eccentric positions A and C of No. 5 are provided on one and the other inner end walls of the recess 18 formed on the inner peripheral wall of the mission case 5 with the stopper arm 15b projecting on the other side of the ring 15. It is defined by abutting. A return spring 19 that constantly urges the first pump ring 15 toward the first eccentric position A is interposed between the transmission case 15 and the ring 15, and resists the urging force of the return spring 19. A gear shift lever 20 capable of swinging the ring 15 from the first eccentric position A to the second eccentric position C is pivotally supported on the mission case 5.
1 is done. The shift lever 20 is operated manually or by an automatic actuator. Thus, when the cylinder body 12 rotates, the first pump ring 15 is
The first and second plungers 14 can be reciprocated according to the amount of eccentricity, and the suction and discharge strokes can be repeated.

As shown in FIGS. 1 and 3, the second hydraulic pump P ₂ has a plurality of (in the illustrated example, a plurality of) second radial pumps P _{2 which} are provided so as to be opened on the outer peripheral surface of the cylinder body 12.
A cylinder hole 23, a second plunger 24 slidably fitted in each of the second cylinder holes 23, and a group of the second plungers 24 is surrounded to engage with outer ends thereof so as to be slidable in the circumferential direction. And a second pump ring 25, and a spring 26 that biases each second plunger 24 in the engagement direction with the second pump ring 25 in each second cylinder hole 23.
Is stored.

The second pump ring 25 is integrally connected to the support cylinder 3 of the output shaft 2 and is eccentric to the cylinder body 12 by a predetermined distance e ₃ (see FIG. 7A). Will be placed. Thus, this second pump ring 25
When the cylinder body 12 rotates, each second plunger 24 can be reciprocated to repeat the suction and discharge strokes.

As shown in FIG. 1, the first hydraulic pump P ₁ and the second hydraulic pump P ₂ are arranged separately from each other on one end side and the other end side of the cylinder body 12, and an input shaft is provided at an intermediate portion between them. An annular low pressure oil passage 28 that surrounds 1 and an annular high pressure oil passage 29 that further surrounds the low pressure oil passage 28 are provided. The low pressure oil passage 28 is defined by an annular groove formed on the outer peripheral surface of the input shaft 1 and the inner peripheral surface of the cylinder body 12, and the high pressure oil passage 29 is formed on the cylinder body 12.

In the cylinder body 12, the same number as the first cylinder holes 13 is provided, and the same number as the first cylinder holes 13 adjacent to the inside of the first cylinder holes 13 and radially extending and the second cylinder holes 23. A second valve hole 32 is provided adjacent to the inside of the second group of cylinder holes 23 and extending radially. Each first valve hole 31 penetrates the high pressure oil passage 29 from the outer peripheral surface of the cylinder body 12 to reach the low pressure oil passage 28.
A first pump port 33 that extends laterally from the adjacent first cylinder hole 13 is opened on the inner surface of the valve hole 31. Each second valve hole 32 also penetrates the high pressure oil passage 29 from the outer peripheral surface of the cylinder body 12 and reaches the low pressure oil passage 28.
A second pump port 34, which extends laterally from the adjacent second cylinder hole 23, opens on the inner surface of the valve hole 32.

As shown in FIGS. 1 and 4, the first valve hole 31
A spool-type first switching valve 35 is slidably fitted in each of the first and second switching valves 35, and a first switching ring 37 surrounding the first switching valve 35 is slidably engaged with the outer ends of the first switching valve 35. It As shown in FIG. 4, the first switching ring 37 is fixed to the mission case 5 with a bolt 39 at a position eccentric to the cylinder body 12 by a predetermined distance e ₄ .

When the cylinder body 12 rotates, each first switching valve 35 is engaged with the first switching ring 37 by its own centrifugal force and the centrifugal oil pressure of the hydraulic oil in the low pressure oil passage 28. Be kept in a state. Therefore, the first switching ring 37 is
As the cylinder body 12 rotates, each first switching valve 35 is reciprocated between the radially inner position and the outer position of the cylinder body 12.

At this time, if the first pump ring 15 occupies the first eccentric position A, the first pump port 33 corresponding to the first plunger 14 during the discharge stroke is driven by the first switching valve 35 to the low pressure oil passage. Second pump port 34 corresponding to the second plunger 24 during the suction stroke while being in communication with 28.
Is communicated with the high-pressure oil passage 29 by the first switching valve 37.

If the first pump ring 15 occupies the second eccentric position C, contrary to the above, the first pump port 33 corresponding to the first plunger 14 in the discharge stroke is the first switching valve 35. While communicating with the high pressure oil passage 29 by
The first pump port 33 corresponding to the first plunger 14 during the intake stroke is communicated with the low pressure oil passage 28 by the first switching valve 35.

As shown in FIGS. 1 and 5, the second valve hole 32
Similarly, a spool-type second switching valve 36 is slidably fitted in each of them, and a second switching ring 38 surrounding them is engaged with the outer ends of these second switching valves 36 so as to be slidable in the circumferential direction. To be done. The second switching ring 38 is integrally connected to the first pump ring 25, and has the cylinder body 12
Is arranged so as to be eccentric by a predetermined distance e ₅ .

When the cylinder body 12 rotates, each second switching valve 36 is engaged with the second switching ring 38 by its own centrifugal force and the centrifugal oil pressure of the hydraulic oil in the low pressure oil passage 28. Be kept in a state. Therefore, the second switching ring 38
Causes the second switching valves 36 to reciprocate between the radially inner position and the outer position of the cylinder body 12 in accordance with the relative rotation with the cylinder body 12. The second switching valve 36 allows the second pump port 34 corresponding to the second plunger 24 during the intake stroke to communicate with the low-pressure oil passage 28, while the second pump port corresponding to the second plunger 24 during the discharge stroke. 34 communicates with the high pressure oil passage 29.

In the above, the low and high pressure oil passages 28, 29,
The first and second valve holes 31 and 32 and the first and second pump ports 33 and 34 constitute a closed hydraulic circuit that connects the first and second hydraulic pumps P ₁ and P ₂ .

Referring again to FIG. 1, the low pressure oil passage 28 is connected to the input shaft 1 and a series of replenishment oil passages 40 formed on the side wall of the mission case 5 to form an oil sump 4 at the bottom of the mission case 5.
Connect to 1. An oil filter 42 is installed at the inlet of the supply oil passage 40, and a dust sump 44 communicating with the oil sump 41 via the through hole 43 is provided in the bottom wall of the mission case 5.
Is provided.

[0030] In FIG 1及 beauty 6, the cylinder body 1
2 includes three blocks 12 that are axially stacked to form the first and second cylinder holes 13 and 23, the low and high pressure oil passages 28 and 29, and the first and second pump ports 33 and 34.
It is divided into a, 12b and 12c, and these are joined by a plurality of bolts 47 with the seal rings 45 and 46 sandwiched therebetween. That is, as clearly shown in FIG. 6, the first and second silin
The holes 13 and 23 are provided on both the left and right outer blocks 12a and 12
c, and the high pressure oil passage 29 has a pair of annular grooves 29a formed on both end surfaces of the central block 12b,
29b and a plurality of through holes 29 that intersect the first and second valve holes 31 and 32 adjacent to each other and communicate between the annular grooves 29a and 29b.
c, and the open surfaces of the annular grooves 29a, 29b are closed by the blocks 12a, 12b, 12c on both outer sides. Further, the first and second pump ports 33, 34 are bored in the respective facing surfaces of the blocks 12a, 12b, 12c.

Next, the operation of this embodiment will be described with reference to FIGS. 7 to 10. In each of the above drawings, (a) is a schematic cross-sectional view of the first and second hydraulic pumps,
(B) is a developed schematic view of the first and second hydraulic pumps P ₁ and P ₂ .

<State in which the gear ratio is continuously large (see FIG. 7)> In this state, the first pump ring 15 is moved to the first eccentric position A.
(See FIG. 2) controls the displacement of the first hydraulic pump P ₁ to be equal to that of the second hydraulic pump P ₂ .

Therefore, when the input shaft 1 is rotated, the cylinder body 12 which rotates integrally with the input shaft 1 causes relative rotation between the first pump ring 15 and the second pump ring 25. At this time, in the first hydraulic pump P ₁ , as described above, the first hydraulic pump P ₁ corresponding to the first plunger 14 in the discharge stroke is operated.
The pump port 33 is connected to the low pressure oil passage 28, and the first pump port 33 corresponding to the first plunger 14 during the suction stroke is connected to the high pressure oil passage 29.
The hydraulic oil is sucked in from and discharged to the low pressure oil passage 28.

On the other hand, in the second hydraulic pump P ₂ , the second pump port 3 corresponding to the second plunger 24 during the suction stroke.
4 communicates with the low pressure oil passage 28, and the second pump port 34 corresponding to the second plunger 24 in the discharge stroke communicates with the high pressure oil passage 29. The hydraulic oil is discharged to the passage 29.

Moreover, since the two hydraulic pumps P ₁ and P _{2 have} the same capacity, the total amount of hydraulic oil discharged from the first hydraulic pump P ₁ to the low pressure oil passage 28 during one revolution of the cylinder body 12 is the second hydraulic pump. Inhaled by P ₂ and the second hydraulic pump P ₂
The total amount of hydraulic oil discharged to the high-pressure oil passage 29 is sucked into the first hydraulic pump P ₁ . Therefore, the first and second plungers 14 and 24 repeat reciprocating motions respectively, and simply sliding on the inner peripheral surfaces of the first and second pump rings 15 and 25 does not generate rotational torque, and the output shaft 2 keeps stopped.

<The gear ratio is, for example, 2 (see FIG. 8)> The first pump ring 15 is located between the first eccentric position A (see FIG. 2) and the non-eccentric position B, that is, the position where the amount of eccentricity is en. It shifted to control the first displacement of the hydraulic pump P ₁ to half the second displacement of the hydraulic pump P ₂ in. By doing so, the first hydraulic pump P can be operated during one rotation of the cylinder body 12.
_{Since the} amount of hydraulic oil ₁ sucked from the high-pressure oil passage 29 is half the amount of hydraulic oil discharged from the second hydraulic pump P ₂ to the high-pressure oil passage 29, the second hydraulic pump P ₂ has the remaining half of hydraulic oil. The reaction force at the time of discharging the liquid acts on the second pump ring 25 from the second plunger 24 during the discharge stroke, and rotates the output shaft 2 via the ring 25. As a result, the output shaft 2 makes a half rotation while the input shaft 1 makes one rotation.

<State of Gear Ratio 1 (see FIG. 9)> The first pump ring 15 is shifted to the non-eccentric position B (see FIG. 2) to control the displacement of the first hydraulic pump P ₁ to zero.
By doing so, the second hydraulic pump P ₂ causes the high-pressure oil passage 29 to move.
Since the hydraulic oil discharged to the first hydraulic pump P ₁ is not sucked at all and loses its place of travel, all the second plungers 24 are in a hydraulic lock state and are turned on by the cylinder body 12 and the second pump ring 25, and the output shaft 1 , 2 are integrally connected, so that both shafts 1 and 2 rotate at the same speed.

<Gear ratio is 0.66 (see FIG. 10)
)> The first pump ring 15 is shifted to the second eccentric position C (see FIG. 2) so that the suction region and the discharge region of the first hydraulic pump P ₁ are reversed and the capacity thereof is changed to the first position. 2 Set to half the capacity of the hydraulic pump P ₂ . With this arrangement, during one revolution of the cylinder body 12, the first hydraulic pump P ₁ has a capacity of one half that of the second hydraulic pump P _{2 and} the corresponding first pump port by the first plunger 14 during the discharge stroke. The second pump port 3 corresponding to the second plunger 24 that has discharged the hydraulic oil from the high pressure oil passage 29 to the high pressure oil passage 29 and has been in the discharge stroke of the second hydraulic pump P ₂ until then.
4, the second plunger 24 moves to the expansion stroke, and the expansion thrust force accelerates the second pump ring 25 by a half rotation in the rotation direction of the cylinder body 12. Eventually, the gear ratio becomes 1: 1.5 = 0.66, and the speed is increased.

As is clear from the above, by continuously shifting the first pump ring 15 from the first eccentric position A to the second eccentric position C, the gear ratio between the input and output shafts 1, 2 is infinite. It is possible to control steplessly from the (neutral state) to the speed increasing state, so that the vehicle can be started smoothly and overdrive can be performed at high speed to reduce fuel consumption.

While the cylinder body 12 is rotating, the oil in the oil sump 41 is sucked from the replenishment oil passage 40 to the low pressure oil passage 28 by the action of centrifugal force and is stored therein. Therefore, the first and second plungers 14 and 24 and the first and second switching valves 35 and 3
The amount of hydraulic oil leaking from the sliding surface of 6 is the low pressure oil passage 28.
Will be replenished immediately from.

By the way, in the continuously variable transmission T, since the radial type first and second hydraulic pumps P ₁ and P ₂ are constructed on a common cylinder body 12, the conventional axial type is used. Compared with a combination of a hydraulic pump and a motor, the axial dimension can be greatly reduced and the size can be reduced. Moreover, as described above, the gear ratio can be controlled steplessly from the infinite state to the speed increasing state only by shifting the first pump ring 15, so that the range of application to various vehicles is extremely wide.

The support cylinder 3 formed at the inner end of the output shaft 2 is supported by the mission case 5 via a ball bearing 8 , and the support cylinder 3 is supported via a ball bearing 4.
Since supporting the inner end of the input shaft 1, in the small space of <br/> axis direction of the transmission case 5 to the inner end of both shafts 1 and 2 firmly supported on the transmission case 5, the support rigidity Can be increased. Moreover, the second pump ring 2 is attached to the support cylinder 3.
Since 5 are integrally connected, the thrust force of the second plunger 24 and its reaction force can be supported between the support cylinder 3 and the input shaft 1, thereby reducing the load burden on the mission case 5 and reducing its thin wall. The weight can be reduced.

The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention.

[0044]

As described above, according to the first feature of the present invention, a plurality of input shafts and output shafts are arranged coaxially and are radially arranged on a cylinder body fixed to the input shafts. a first plunger, surrounding these first plunger engages movable relative to their outer ends to, the give reciprocate in the first plunger with the rotation of the cylinder body, the reciprocating stroke A variable displacement radial type first hydraulic pump is configured with an adjustable first pump ring,
Also a plurality of second plunger disposed radially in said cylinder body, surrounds these second plunger while being fixed to the output shaft relatively movable engaged with their outer ends, the said cylinder constitutes a radial second hydraulic pump of a fixed capacity and the second pump ring to provide a reciprocating movement of a constant stroke each second plunger with the relative rotation of the body, the further the cylinder body, the first hydraulic pump is the sucked hydraulic oil to the second hydraulic pump with discharged and the high pressure oil passage discharged hydraulic oil from the second hydraulic pump with the intake, the working oil from the first hydraulic pump hydraulic oil to A low pressure oil passage is provided, and the first hydraulic pump is provided.
Front of the mission case containing the pump and the second hydraulic pump.
Since the input shaft and the output shaft are supported by bearings respectively , the first pump has a smaller axial dimension and is more compact than the conventional axial type hydraulic pump and hydraulic motor combination. It is possible to provide a continuously variable transmission capable of continuously controlling the gear ratio by shifting the ring.

[0045] According to a second aspect of the present invention, the first
In addition to the features, by controlling the eccentric direction and the eccentric amount with respect to the cylinder body of the first pump ring, since the capacity of the first hydraulic pump and adapted to be set equal to that of the second hydraulic pump, By controlling the gear ratio to infinity, it is possible to smoothly start the vehicle under any load condition.

Further, according to the third feature of the present invention, the first
Or in addition to the second feature, before by shifting the first pump ring concentrically positioned between the <br/> cylinder body
Since the capacity of the first hydraulic pump can be set to zero, the gear ratio can be controlled to 1 so that the vehicle can be operated at high speed.

Furthermore, according to the fourth aspect of the present invention,
First, in addition to the second or third feature, by reversing the direction of eccentricity with respect to the cylinder body of the first pump ring, discharges hydraulic fluid of the first hydraulic pump to the high pressure oil passage, low pressure oil passage Since the hydraulic oil can be sucked in from the above, the gear ratio can be controlled to the increased speed state to correspond to the further high speed operation of the vehicle and contribute to the reduction of fuel consumption.

Furthermore, according to the fifth feature of the present invention,
First, second, in addition to the third or fourth feature, fixed fitted to the cylindrical <br/> Dabodi the outer periphery of the input shaft, these
The low pressure oil passage between the opposed circumferential surfaces of the cylinder body and the input shaft so as to form a ring, which communicates with the oil reservoir, is formed in an annular high pressure oil passage in the cylinder body so as to surround the low pressure oil passage Therefore, the hydraulic oil can be replenished to the low-pressure oil passage by utilizing the centrifugal force, and a dedicated replenishment pump is unnecessary.

Further, according to the sixth feature of the present invention,
In addition to the first, second, third, fourth or fifth characteristic,
Place the outer ends of the input and output shafts in the mission case.
While supporting through the ring, at the inner end of the output shaft,
A support cylinder that supports the inner end of the input shaft through a bearing.
Is integrally formed, and the support cylinder
Support the mission case and put the second pump ring in front.
Since it is integrally connected to the tip of the support cylinder,
Enters in a small space in the axial direction of the shaft and supports the inner end of the output shaft
Firmly support the mission case via the
The rigidity can be increased and at the same time the thrust of the second plunger
And reaction force between the support cylinder and the input shaft to support the mission
To reduce the load on the case and reduce its thickness and weight.
You can

[Brief description of drawings]

FIG. 1 is a vertical sectional side view of a continuously variable transmission according to the present invention.

FIG. 2 is a sectional view taken along line 2-2 of FIG.

FIG. 3 is a sectional view taken along line 3-3 of FIG.

4 is a front sectional view taken along line 4-4 of FIG.

5 is a sectional view taken along line 5-5 of FIG.

FIG. 6 is a partially enlarged view of FIG.

FIG. 7 is an explanatory view of the operation when the gear ratio is infinite.

FIG. 8 is an explanatory view of the operation in the state of the gear ratio 2.

FIG. 9 is an explanatory view of the operation in the state where the gear ratio is 1.

FIG. 10 is an operation explanatory view in a state where the gear ratio is 0.66.

[Explanation of symbols]

1 ... Input shaft 2 ... Output shaft 3 ... Support tube 5: Mission case 6 ... Ball bearing 7: Ball bearing 12 ... Cylinder body 13 ... First cylinder hole 14 ... First plunger 15 ... First pump ring 23 ... second cylinder hole 24 ... Second plunger 25 ... Second pump ring 28 ... Low-pressure oil passage 29 ... High-pressure oil passage 41 ... Oil sump T: continuously variable transmission

Claims (6)

(57) [Claims] 1. A plurality of first axially arranged input shafts (1) and output shafts (2) arranged coaxially and radially arranged on a cylinder body (12) fixed to the input shaft (1). a plunger (14), these first plunger (14) engaged to move relative to their outer ends to surround the reciprocating each first plunger with the rotation (14) of said cylinder body (12) together give, arranged its constitute a radial-type first hydraulic pump of the variable displacement out first pump ring capable of modulating the reciprocating stroke with (15) (P _1), also radially to said cylinder body (12) is a plurality of second plungers (24) is, the output shaft (2) in conjunction with the fixed surrounding these second plunger (24) engages movable relative to their outer ends, the said cylinder Body (12)
It constitutes a radial second hydraulic pump fixed displacement out with second pump ring to provide a reciprocating movement of a constant stroke (25) (P ₂₎ in each of the second plungers with relative rotation (24) and, further the cylinder body the (12), the second with sucked hydraulic oil to the first hydraulic pump (P ₁₎
High pressure oil passage discharged hydraulic oil from the hydraulic pump (P ₂₎ and (29), hydraulic fluid to the second hydraulic pump (P ₂₎ with discharged hydraulic fluid from the first hydraulic pump (P ₁₎ low pressure oil passage and (28) provided to be inhaled, said first hydraulic
Accommodates the pump (P ₁ ) and the second hydraulic pump (P ₂ )
The input shaft (1) and the output shaft in the mission case (5)
A continuously variable transmission characterized in that (2) is supported via bearings (6, 7), respectively . 2. The method of claim (1) as described, by controlling the eccentric direction and the eccentric amount to the cylinder body (12) of the first pump ring (15), said first hydraulic pump (P ₁ capacity), characterized in that it has adapted to set equal to that of the second hydraulic pump (P _2), the continuously variable transmission. 3. A process according to claim (1) or (2) in those described, the first by shifting the first pump ring (15) concentrically positioned between the cylinder body (12)
A continuously variable transmission characterized in that the capacity of a hydraulic pump (P ₁ ) can be set to zero. 4. The cylinder body (1) of the first pump ring (15) according to claim (1), (2) or (3).
By reversing the direction of eccentricity with respect to 2), the first hydraulic pump (P ₁₎ is discharged hydraulic oil to the high pressure oil passage (29) and adapted to suck the hydraulic fluid from the low pressure oil passage (28) A continuously variable transmission characterized in that 5. A method according to claim (1), fixed fitted to the outer periphery of (2), (3) or (4) as described, the cylinder body (12) said input shaft (1), These cylinder bodies (12) and
A low pressure oil passage (28) is formed in an annular shape between the opposed peripheral surfaces of the input shaft (1) and communicates with an oil sump (41) so as to surround the low pressure oil passage (28). In front of (29)
Serial characterized by being formed in a ring cylinder body (12), continuously variable transmission. 6. Claims (1), (2), (3), (4)
Alternatively, in the structure described in (5), the outer ends of the input shaft (1) and the output shaft (2) are connected to the
The bearing case (5) is supported by bearings (6, 7).
On the other hand, at the inner end of the output shaft (2), bearings
Support for supporting the inner end of the input shaft (1) through (4)
The tube (3) is integrally formed, and the support tube (3) is formed into a bearing.
Support the mission case (5) through the guide (8).
Then, the second pump ring (25) is attached to the support cylinder (3).
A continuously variable transmission characterized by being integrally connected to the tip of the .