JPH0133692B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention utilizes the action of a tapered needle roller that rolls between a circumscribed conical surface formed on one rotating body and an inscribed conical surface formed on the other rotating body.
This invention relates to a clutch operation control device for a one-way clutch that transmits power between the two rotating bodies when the rotating body rotates in one direction on the drive side, but cuts off the power when the rotating body rotates in the other direction. be.

A one-way clutch function is provided by utilizing the action of a tapered needle roller that rolls between a circumscribed conical surface formed on one rotating body and an inscribed conical surface formed on the other rotating body. In a one-way clutch, when the driving side rotating body rotates in one direction, power is transmitted to the driven side rotating body, but when the driving side rotating body rotates in the other direction, the power is cut off. No power is transmitted to the rotating body on the driven side.

By the way, in order to fully utilize the functions of the one-way clutch using the tapered needle roller of the above type and further expand its usage,
It is desirable to provide a one-way clutch with a function that can interrupt the transmission of power to the driven rotating body at any time, as needed, regardless of the rotational direction of the driving rotating body. There has been no suitable one-way clutch having such a function or a device for controlling the above-mentioned clutch operation of a one-way clutch.

Therefore, the present invention provides a one-way clutch function by utilizing the action of a tapered needle roller that rolls between a circumscribed conical surface formed on one rotating body and an inscribed conical surface formed on the other rotating body. This is an operation control device for a one-way clutch that is equipped with a one-way clutch, and does not require a special power cutoff device other than the one-way clutch, and can cut off the transmission of power to the rotating body on the driven side at any time as necessary. The control operation can be performed smoothly and reliably even with small control operation inputs and extremely short operation strokes. It is an object of the present invention to provide a clutch actuation control device that is simple and highly practical.

In order to achieve this object, the present invention provides a first power transmission shaft and a second power transmission shaft between which power is to be transmitted; an outer rotating body supported by a transmission shaft, and having a circumscribed conical surface formed on the inner circumferential side with the rotation axis as an axis of symmetry; supported by the second transmission shaft so as to rotate together with the second transmission shaft; on the outer circumferential side, with the rotation axis as an axis of symmetry,
an inner rotating body formed with an inscribed conical surface that maintains a uniform distance between the circumferential conical surface and the circumferential conical surface; are held at a constant interval in the direction, and are each held so as to be inscribed in the circumscribed conical surface and circumscribed to the inscribed conical surface in a twisted arrangement state under a constant torsion angle with respect to the rotation axis. a one-way clutch having a plurality of tapered needle rollers; an axial movement allowing device for allowing relative movement in the axial direction between the outer rotating body and the inner rotating body; The relative positional relationship in the axial direction between the inner and circumscribed conical surfaces is determined by a transmission position where the inner and circumscribed conical surfaces are in contact with each other via the tapered needle roller, and a power cutoff position where the contact between the inner and circumscribed conical surfaces is released. and a power transmission capacity for reducing the power transmission capacity of a transmission device interposed between the input side transmission shaft of the two transmission shafts and the drive source. The axial movement control device includes at least a changing device, and the axial movement control device includes:
A hydraulic actuating device such as a hydraulic cylinder connected to at least one of the inner and outer rotating bodies, and a hydraulic actuating device interposed between the hydraulic actuating device and a hydraulic power source, The power transmission capacity changing device includes a switching valve that switches between a first operating state that can be held in the power transmission position and a second operating state that can be held in the power cutoff position, and the power transmission capacity changing device The switching operation is configured such that the hydraulically actuated device can be operated during switching from the first operating state to the second operating state.

An embodiment of the present invention will be described below with reference to the drawings. First, in FIG. 1, one-way clutch 1
has a first transmission shaft 2 and a second transmission shaft 3, and a cylindrical outer rotating body 5 is integrally formed at the shaft end of the first transmission shaft 2 via a flange portion 4. At the same time, on the inner peripheral side of the outer rotating body 5, there is a circumscribed conical surface 6 whose symmetry axis is the rotation axis a of the outer rotating body 5.
is formed so as to widen toward the second power transmission shaft 3 side.

A small-diameter protrusion 8 protruding from the center of the shaft end surface of the second power transmission shaft 3 is rotatably inserted into a support hole 7 formed in the center of the shaft end surface of the first power transmission shaft 2 via a bearing 9. The inner rotating body 1 is fitted onto the outer circumferential surface of the shaft end of the second power transmission shaft 3 via a spline 10 constituting the axial movement permitting device of the present invention.
The inner periphery of 1 is spline-coupled.

A portion of the inner rotating body 11 near the first transmission shaft 2 on the outer circumferential side has a symmetry axis with the common rotational axis a of the outer rotating body 5 and the inner rotating body 11, and a uniform surface with the circumscribed conical surface 6. An annular raceway groove 12 is formed which has an inscribed conical surface 13 that maintains a distance as a bottom surface and has a pair of axially opposing movement limiting walls 14 and 15 as side surfaces.

In the gap between the circumscribed conical surface 6 and the inscribed conical surface 13, as shown in the developed view in FIG. It can be inscribed in the circumscribed conical surface 6 and circumscribed in the inscribed conical surface 13 while being held by a roller holder 16 such as a cage so as to maintain an attitude twisted by a certain twist angle θ with respect to the axis a. In this way, a plurality or a large number of tapered needle rollers 17 are installed.

Although the function as a one-way clutch does not essentially change regardless of which of the first transmission shaft 2 and the second transmission shaft 3 is connected to the drive side, for convenience of explanation, the first transmission shaft 2 is connected to the driving side as an input shaft, and the second transmission shaft 3 is connected to the driven side as an output shaft, normally, the first transmission shaft 2
When rotates in the direction of arrow X, no torque is transmitted between the outer rotating body 5 and the inner rotating body 11 due to the action of the tapered needle roller 17, and no power is transmitted to the second transmission shaft 3. On the contrary, when the first power transmission shaft 2 rotates in the direction of the arrow Y, torque is transmitted between the outer rotating body 5 and the inner rotating body 11 due to the action of the tapered needle roller 17, and the second Power is transmitted to the transmission shaft 3.

An annular fork engagement groove 18 having a pair of axially opposing contact surfaces 19 and 20 as side surfaces is formed at a position close to the raceway groove 12 on the outer peripheral side of the inner rotating body 11. The tip of a fork 23 formed at the tip of the shift rod 22 is slidably engaged in the fitting groove 18, and the base end of the shift rod 22 is held together with the cylinder cover 25 by a fixture 26. Hydraulically operated cylinder 27 fixed to fixed wall 24
It is connected using a circlip or the like to a hydraulically actuated piston 28 that is in sliding contact therewithin. A wave spring 21 that generates an elastic force in the axial direction is interposed between the tip of the fork 23 and the contact surface 19 near the first power transmission shaft 2.

The cylinder chamber in the hydraulic cylinder 27 is divided into a second oil chamber 29 and a second oil chamber 30 by the hydraulic piston 28.
Due to the resilient force of the return spring 31 inserted into the second oil chamber 30, the inner rotary body 11 is always resiliently moved in the direction of separating the inner rotary body 11 from the outer rotary body 5 in the axial direction.

A port 58 is formed in the cylinder cover 25, and the first oil chamber 29 is connected through this port 58.
When pressure oil is introduced into the hydraulically actuated piston 28
The second oil chamber 30 resists the pressing force of the return spring 31.
side, so that the fork 23 is in the wave spring 2
1 to elastically press the inner rotating body 11 toward the outer rotating body 5 side. In this state, due to the action of the tapered needle roller 17, the first power transmission shaft 2
When the first transmission shaft 2 rotates in the direction of the arrow Y, the power is transmitted to the second transmission shaft 3, and when the first transmission shaft 2 rotates in the direction of the arrow X, the power is cut off and the power is transmitted to the second transmission shaft 3.
is not transmitted.

Further, a port 60 is formed in the end wall of the hydraulic cylinder 27, and a port 83 is formed in the side wall. Pressure oil is supplied into the second oil chamber 30 through the port 60 among these ports. When the hydraulic piston 28 is introduced, the hydraulic piston 28 is pushed toward the first oil chamber 29 by the pressing force of the return spring 31 and the oil pressure in the second oil chamber 30. the result,
Since the fork 23 is moved in the direction of separating the inner rotating body 11 from the outer rotating body 5, the second power transmission shaft 3
No power is transmitted to the first transmission shaft 2 regardless of the rotational direction of the first transmission shaft 2. Thus, the shift rod 22, the fork 23, the hydraulically actuated cylinder 27, the hydraulically actuated piston 28, etc. are part of the axial movement control device A of the present invention for controlling the relative positional relationship between the outer rotating body 5 and the inner rotating body 11. It constitutes.

Next, a hydraulic circuit device for smoothly and reliably performing the control operation of the axial movement control device A will be described.

Hydraulic oil sucked up from the oil tank T and pressurized by the pump P, which is a hydraulic power source, flows through oil passages 32, 33,
34, a hydraulically operated transmission device 3, such as a hydraulic clutch or a fluid converter, interposed between the drive source and the first transmission shaft 2 via an orifice 35;
At the same time, the oil is sent to the manual control valve 38 via an oil path 37 branched from the oil path 33. The oil passage 32 further includes a hydraulic response switching valve 3.
9, and surplus oil in the oil passage 32 is returned to the oil tank T via a relief valve 40. In addition, the oil passage between the orifice 35 and the hydraulically operated transmission 36 is connected via an oil passage 79 to temporarily reduce the power transmission capacity of the hydraulically operated transmission 36 so that the outer rotating body 5 and the inner rotating body 1
1 to the power cutoff position.

The hydraulic pressure response switching valve 39 has a cylinder chamber 42 and a piston 43 that is in sliding contact in the axial direction within the cylinder chamber 42. A pilot oil chamber 44 is formed on one end surface side of the piston 43 within the cylinder chamber 42. At the same time, a spring chamber 45 is formed on the other end side, and the piston 43 is constantly pressed toward the pilot oil chamber 44 by a pressing spring 46 inserted into the spring chamber 45. piston 43
are three narrow diameter portions 47, 4 successively adjacent in the axial direction.
8, 49, and the cylinder chamber 42 has a port 50 communicating with the pump P via the oil passage 32,
A port 51 that communicates with the first oil chamber 29 of the hydraulic cylinder 27 via an oil passage 57 and a port 58;
A port that communicates with the second oil chamber 30 of the hydraulic cylinder 27 via an oil passage 59 and a port 60, and communicates with the port 63 of the power transmission capacity changing device 41 via an oil passage 61 and a fixed or variable orifice 62. 52, and a port 53 communicating with the oil tank T.
54, a port 55 that communicates with ports 65, 65' of the manual control valve 38 via an oil passage 64, and a port 56 that communicates the spring chamber 45 with the atmosphere. Then, when pilot oil is introduced into the pilot oil chamber 44, the piston 43 moves against the pressing force of the pressing spring 46, so that the narrow diameter portion 48 communicates with the ports 50 and 51. The narrow diameter portion 47 communicates between the ports 52 and 54,
Further, when the pilot oil chamber 44 is communicated with the oil tank T, the piston 43 is pressed by the pressure spring 46 and moves, so that the small diameter portion 48 is connected to the port 50.
and the port 52, and the small diameter portion 49
is configured to communicate between ports 51 and 53.

The manual control valve 38 has a cylinder part 66 and a control piston 67 that is slidably fitted into the cylinder part 66. Cylinder part 66
is a port 6 that communicates with the pilot oil chamber 44 of the hydraulic response switching valve 39 via an oil passage 64 and a port 55.
5, 65', a port 74 communicating with the pump P via the oil passages 37, 33, 32, a port 90 communicating with the oil tank T, and an elastic engagement member 71 for holding the control piston 67 in a set position. The control piston 67 has a narrow diameter portion 68 and an elastic engagement member 71 formed near the outer end protruding from the cylinder portion 66 and accommodated in the recess 70. and the control piston 6.
7, and a reference line 72 drawn on the outer end thereof. Then, on the fixed surface, an indication scale 73 with N, D, etc. displayed is drawn, and the reference line 7 is moved by an appropriate manual operation means.
When the control piston 67 is set so that the port 2 is positioned at the D position, the narrow diameter portion 68 is connected to the port 65, 6.
5' is connected to the port 74, and the reference line 72 is connected to the port 74.
When the control piston 67 is set in position, the narrow diameter portion 68 is configured to communicate the ports 65, 65' with the port 90.

The power transmission capacity changing device 41 includes a small-diameter cylinder chamber 76 and a large-diameter cylinder chamber 77 that are adjacent to each other with a shoulder 75 in between, and a small-diameter piston 84 that is slidably fitted into the small-diameter cylinder chamber 76. One portion has a shouldered piston 85 formed so as to be in sliding contact within the small-diameter cylinder chamber 76, and the remaining portion to be in sliding contact within the large-diameter cylinder chamber 77. The small diameter cylinder 76 is connected to the orifice 35 and the hydraulically operated transmission device 36 through an oil passage 79 at its end wall.
The large diameter cylinder 77 has a port 78 communicating with the oil passage 34 between the two, and a port 80 adjacent to the port 78 and communicating with the oil tank T, and the large diameter cylinder 77 has the oil passage 82, The port 81 communicates with the hydraulic cylinder 27 via the port 83, and the shoulder 75 communicates with the cylinder chamber 42 of the hydraulic response switching valve 39 via the oil passage 61, the orifice 62, and the port 52. oil road 59,
The second of hydraulically actuated cylinder 27 via port 60
It also has a port 63 that communicates with the inside of the oil chamber 30.

A pressure spring 88 is disposed within a spring chamber 86 formed between the end wall of the large diameter cylinder 77 and the shouldered piston 85.
is inserted into the spring chamber 87 formed between the shouldered piston 85 and the small diameter piston 84.
A pressure spring 89 having a pressure force smaller than that of the pressure spring 88 is inserted inside. Therefore, normally the shouldered piston 85 is in contact with the shoulder 75, and the small diameter piston 85 is in contact with the port 75.
However, when pressure oil is introduced into the port 63, the pressure oil that enters the gap formed between the shoulder portion 75 and the shoulder portion of the shouldered piston 85 is blocked. When the shoulder piston 85 is moved against the pressing force of the pressing spring 88, the pressing force of the pressing spring 89 is correspondingly weakened, and as a result, the port 7
The hydraulic oil that has flowed into port 8 presses and moves the small diameter piston 84 to open ports 78 and 80.
The oil pressure of the hydraulic oil in the oil passage 34 after passing through the orifice 35 is reduced, and the power transmission capacity of the hydraulically operated transmission device 36 is reduced.

With the above structure, when the one-way clutch 1 is to have a one-way clutch function, the outer rotating body 5 and the inner rotating body 11
When attempting to set the relative positional relationship in the axial direction between the
Position and set the control piston 67 of the manual control valve 38 so that it is in the D position of 3. Then,
The pressure oil discharged from the pump P flows through oil passages 32, 33,
37, ports 74, 65 and 65', oil passage 64,
The pilot oil flows sequentially through the ports 55 into the pilot oil chamber 44 as pilot oil, and presses and moves the piston 43 against the pressing force of the pressing spring 46. As a result, the oil discharged from the pump P flows through the oil passage 32, the port 50,
51, oil passage 57, and port 58 into the first oil chamber 29, and presses and moves the hydraulic piston 28 against the pressing force of the return spring 31. During this time, the hydraulic oil in the second oil chamber 30 flows back to the oil tank T via the port 60, the oil passage 59, and the ports 52 and 54. At this time, the power transmission capacity changing device 41 does not operate at all. Thus, the inner rotating body 1
1 is elastically pressed and moved in the direction approaching the outer rotating body 5 by the fork 23 via the wave spring 21, and as a result, when the first transmission shaft 2 rotates in the direction of the arrow X, the second transmission shaft 3 Power is not transmitted to the first power transmission shaft 2, but when the first power transmission shaft 2 rotates in the direction of arrow Y, power is transmitted to the second power transmission shaft 3.
In this manner, the one-way clutch 1 performs a one-way clutch function.

When the one-way clutch 1 is intended to cut off the power regardless of the rotational direction of the first transmission shaft 2, the relative positional relationship in the axial direction between the outer rotary body 5 and the inner rotary body 11 is set to the power cutoff position. When placing the control piston 67 of the manual control valve 38 so that the reference line 72 is at the N position of the indication scale 73.
Position and set. Then, the pilot oil chamber 44 is connected to the port 55, the oil passage 64, and the port 65.
and 65', and communicates with the oil tank T through the port 90, so the piston 43 is pressed by the pressure spring 46 and communicates between the ports 50 and 52, and also between the ports 51 and 53. As a result, the oil discharged from the pump P is
The oil flows into the second oil chamber 30 through the ports 50, 52, the oil passage 59, and the port 60 in order to press and move the hydraulically actuated piston 28, and further passes through the oil passage 61, the orifice 62, and the port 63 in order. The shouldered piston 85 is pressed and moved against the pressing force of the pressing spring 88. At this time, the first oil chamber 29 includes the port 58, the oil passage 57, and the port 5.
It is communicated with the oil tank T via 1 and 53.

At this time, either the first transmission shaft 2 is rotating in the direction of arrow X and power is not transmitted to the second transmission shaft 3, or the first transmission shaft 2 is rotating in the direction of arrow Y. Even if power is transmitted to the second transmission shaft 3, if the transmitted torque at that time is relatively small, the inner rotating body 11 tends to move away from the outer rotating body 5, so the hydraulically operated piston 28 is immediately pushed toward the first oil chamber 29, but when the first transmission shaft 2 is rotating in the direction of arrow Y and power is being transmitted to the second transmission shaft 3,
If the transmitted torque at that time is relatively large,
Since the inner rotating body 11 is strongly biting into the outer rotating body 5 side, the inner rotating body 11 immediately touches the outer rotating body 5.
cannot move away from the At this time, the pressure oil introduced into the port 63 while being throttled by the orifice 62 presses and moves the shouldered piston 85 relatively gently against the press spring 88, and as a result, the pressing force of the press spring 89 weakens. The small-diameter piston 84 is pressed by the hydraulic pressure in the oil passage 34 after passing through the orifice 35, and the port 7
8 and port 80 are communicated, and the oil passage 34 between the orifice 35 and the hydraulically operated transmission 36 is communicated with the oil tank T. Thus, the hydraulic pressure in the oil passage 34 between the orifice 35 and the hydraulically operated transmission 36 is reduced, and the power transmission capacity of the hydraulically operated transmission 36 is reduced, so that the torque of the first transmission shaft 2 is reduced. As the torque transmitted between the outer rotating body 5 and the inner rotating body 11 decreases, the inner rotating body 11 moves in the direction away from the outer rotating body 5 while receiving the moving force from the fork 23. do. When the hydraulic piston 28 passes through the port 83, the pressure oil in the second oil chamber 30 flows into the spring chamber 86 via the port 83, the oil passage 82, and the port 81, so that the shouldered piston 85 is immediately activated. The small-diameter piston 84 returns to the position where it abuts the shoulder 75, and as a result, the small-diameter piston 84 blocks the connection between the ports 78 and 80, so that the power transmission capacity of the hydraulically operated transmission 36 immediately recovers to the size before the reduction. . In this way, the relative positional relationship in the axial direction between the outer rotating body 5 and the inner rotating body 11 is placed at the power cutoff position, and the one-way clutch 1 cuts off the power regardless of the rotational direction of the transmission shaft 2. can do.

As described above, according to the present invention, the first power transmission shaft and the second power transmission shaft between which power is to be transmitted; the first power transmission shaft rotates together with the first power transmission shaft; an outer rotating body supported by the second power transmission shaft so as to rotate together with the second power transmission shaft; an inner rotating body formed with an inscribed conical surface that maintains a uniform distance between the circumscribed conical surface and the circumscribed conical surface; are inscribed in the circumscribed conical surface and are arranged at a constant distance from each other in the circumferential direction, and each is twisted at a constant angle of rotation with respect to the axis of rotation. an axial movement permitting device for permitting relative movement in the axial direction between the outer rotary body and the inner rotary body in a one-way clutch having: a plurality of tapered needle rollers held so as to be circumscribed on a tangential conical surface; and a relative positional relationship in the axial direction between the outer rotary body and the inner rotary body, a transmission position where the inner and circumscribed conical surfaces are in contact via the tapered needle roller, and the inner and circumscribed conical surfaces. an axial movement control device for controlling a power cutoff position for releasing the contact between A hydraulic actuating device such as an operating cylinder, a first operating state that is interposed between the hydraulic actuating device and a hydraulic source and capable of holding both the rotating bodies in the transmission position, and the power source. Since it has a switching valve that switches between a second operating state in which it can be held in the cutoff position, it is possible to disconnect and disconnect between both transmission shafts simply by relatively displacing the inner and outer rotating bodies in the axial direction. This can be done reliably, and therefore, the power can be cut off at any time as needed between both transmission shafts, which are rotated in the clutch connection direction and are in a power transmission state, without the need for a special power cutoff device other than the one-way clutch. The structure is simple and can contribute to cost reduction. In particular, since the connection between both rotating bodies is made by contact between the inner and circumscribed conical surfaces with a tapered needle roller interposed in between, it is possible to connect both rotating bodies by simply slightly displacing both rotating bodies in the axial direction. The contact/disconnection switching operation between the surfaces, and therefore the contact/disconnection switching operation between the two rotating bodies, can be completed quickly and reliably, and during the switching, both the rotating bodies and the tapered needle roller are long relative to each other in the direction of the rotational axis. There is no need for sliding, and as a result of the above, the operating force required to switch between the two rotating bodies is reduced, and the operating stroke can be significantly shortened. The capacity can be increased, which greatly contributes to making the device more compact and reducing costs.

Further, a power transmission capacity changing device is provided for reducing the power transmission capacity of the transmission device interposed between the input side transmission shaft of the two transmission shafts and the drive source, and this power transmission capacity changing device is configured such that it can operate while the hydraulic operating device is being switched from the first operating state to the second operating state by the switching operation of the switching valve, so that both rotating bodies are in the transmission position. When shifting to the power cut-off position from Even if the transmission torque between both transmission shafts is large and the taper needle roller is strongly bitten into the conical surface, the biting state can be easily released and the transition from the transmission state to the power cutoff state of the clutch can be smoothly and easily. can be made to do so.

[Brief explanation of drawings]

FIG. 1 is a hydraulic circuit diagram of a clutch actuation control device for a one-way clutch according to an embodiment of the present invention;
The figure is a developed view of the main parts of FIG. 2, 3... First and second transmission shafts, 5... Outer rotating body, 6... Circumscribed conical surface, 10... Axial movement permitting device, 11... Inner rotating body, 13... Inscribed conical surface , 17... Taper needle roller, 27... Hydraulic cylinder, 36... Transmission device, 39... Switching valve, 41... Power transmission capacity changing device, A... Axial direction movement control device, P... Hydraulic power source , a... Rotation axis, θ... Torsion angle.

Claims (1)

[Claims] 1 A first transmission shaft 2 and a second transmission shaft 3 between which power is to be transmitted; supported by the first transmission shaft 2 so as to rotate together with the first transmission shaft 2; an outer rotary body 5 having a circumscribed conical surface 6 formed thereon with the axis of symmetry about the rotation axis a;
An inner rotating body 11 is supported by a transmission shaft 3, and has an inscribed conical surface 13 formed on its outer circumferential side with the rotation axis a as an axis of symmetry and maintaining a uniform distance between it and the circumscribed conical surface 6. A constant distance is maintained in the circumferential direction between the circumferential conical surface 6 and the inscribed conical surface 13, and each of them is aligned with the rotation axis a.
a plurality of tapered needle rollers 17 held so as to be inscribed in the circumscribed conical surface 6 and circumscribed to the inscribed conical surface 13 in a twisted arrangement state under a constant twist angle θ; The one-way clutch has an axial movement permitting device 10 that allows relative movement in the axial direction between the outer rotating body 5 and the inner rotating body 11; The relative positional relationship in the axial direction is
Control is performed between a power transmission position where the inner and circumscribed conical surfaces 13 and 6 are in contact via the tapered needle roller 17 and a power cutoff position where the contact between the inner and circumscribed conical surfaces 13 and 6 is released. and a power transmission capacity that reduces the power transmission capacity of a transmission device 36 interposed between the input side transmission shaft 2 of the two transmission shafts 2 and 3 and the drive source. The axial movement control device A includes at least a changing device 41, and the axial movement control device A
A hydraulic actuating device such as a hydraulic actuating cylinder 27 connected to at least one of The power transmission capacity changing device 41 has a switching valve 39 that is operated to switch between a first operating state in which it can be held at the power cut-off position and a second operating state in which it can be held in the power cutoff position.
A one-way clutch, characterized in that the hydraulic actuator can be operated during switching from the first operating state to the second operating state by the switching operation of the switching valve 39. Actuation control device.