JPH03329A - Hydraulic power transmission coupling - Google Patents

Abstract

PURPOSE:To increase durability at low cost by providing a valve means for varying the opening area of a flow resistance producing means in one rotating member and also providing a diaphragm mechanism operated pneumatically for controlling the valve means integrally together with the valve means. CONSTITUTION:A needle valve 38(valve means) for varying the opening area of an orifice 28, a means to produce flow resistance, is stored free to move in a plug member 39 in which a rotor 1 is inserted, and a diaphragm mechanism 40 rotated together with the valve 38 as an unit and controlling the movement of the valve 38 is provided integrally at the rear end of the valve 38. When a negative pressure at the first port 49 with the second port 50 vent to the atmosphere, the negative pressure acts on the first chamber 42A through an A Chamber 48A and a connecting hole 41A, and the valve 38 is moved to the left by a diaphragm 43 to choke the orifice 28. Accordingly, a transmission torque is increased according to the negative pressure. As a result, the transmission torque can be controlled freely by varying negative pressure irrespective of a difference in rotating speed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic power transmission joint used for distributing driving force in a vehicle.

[Conventional technology] Conventional vane pump type hydraulic power transmission joints include:
For example, there is one disclosed in Japanese Patent Application Laid-Open No. 61-249827.

Further, as a conventional plunger pump type hydraulic power transmission joint, for example, there is one disclosed in Japanese Patent Application Laid-Open No. 101567/1983.

There are two types of these structurally as follows.

The first type has a solenoid valve in a fixed part that does not rotate, and controls the joint by supplying controlled hydraulic pressure to the interior of the joint through a rotary shaft seal.

In the second type, a solenoid valve is provided on a rotating joint, and power is supplied to the solenoid valve from a fixed part through a slot or a ring to control the joint.

[Problems to be Solved by the Invention] However, in the former case, with such conventional hydraulic power transmission joints, oil leakage from the rotating shaft seal occurs frequently (not only does control accuracy deteriorate, but also However, there was a problem in that an expensive hydraulic power source was required.

In the latter case, there is a problem that when the joint rotates at high speeds, the brushes dance, causing the power supply to be cut off and control to be impossible.Moreover, maintenance is required to prevent the brushes from dancing and the slip ring from wearing out. There was a problem that the cost was high.

Another problem was that it could not be applied to large joints because the electromagnetic force generated was small.

The present invention was made in view of these conventional problems, and is a hydraulic power transmission system that can improve durability at low cost and also provide the necessary performance even with large joints. The purpose is to provide fittings.

[Means for Solving the Problem] In order to achieve the above object, the present invention provides a hydraulic pump driven by a rotational speed difference between a first rotating member and a second rotating member that are relatively rotatable. , a hydraulic power transmission joint comprising a flow resistance generating means for generating flow resistance in a discharge path of the hydraulic pump, and in which the flow resistance controls the transmission torque between the first and second rotating members. A valve means for making the opening area of the resistance generating means variable is provided within the one rotating member, and a diaphragm mechanism that is operated by air pressure to control the valve means is provided integrally with the valve means.

[Function] In the present invention, a diaphragm mechanism is integrally attached to a valve means that changes the opening area of an orifice serving as a flow resistance generating means, and the valve means is controlled, and the operation of the diaphragm mechanism is controlled by air pressure supplied from the outside. Because of this, the control accuracy does not deteriorate like in the past.
Also, no expensive hydraulic power source is required.

Furthermore, durability does not deteriorate due to wear, and costs can be reduced. Furthermore, since the diaphragm can generate a large amount of force, the required performance can be achieved even with large joints.

[Example] Embodiments of the present invention will be described below based on the drawings.

1 to 3 are diagrams showing a first embodiment of the present invention,
This applies to vehicles based on rear-wheel drive vehicles.

First, to explain the configuration, in Fig. 1, 1 is the front drive shaft (first rotating member) which is the output shaft (
Hereinafter, the rotor 1 is the casing 2, 3
is rotatably supported via bearings 4 and 5.

A driven sprocket 7 is rotatably supported on the rotor 1 via a needle bearing 6, and a chain 9 is installed between the driven sprocket 7 and the drive sprocket 8. In addition, 10 is an output flange, 11 is a nut, 12.13 is an oil seal, 14 is a stop ring, and 15 is a thrust washer.

A plurality of plunger chambers 16 are formed in the rotor 1 in the axial direction, and a plurality of plungers 17 that reciprocate in one direction are housed in the plunger chamber 16. A cam surface 18A is formed on the inner surface of the cam housing (second rotating member) 18 fixed to the driven sprocket 7,
The plunger 17 is in sliding contact with the cam surface 18A. In addition,
The plunger 17 and the plunger chamber 16 collectively constitute a hydraulic pump.

Reference numeral 19 denotes a suction passage communicating with the plunger chamber 16, and a suction valve 20 is interposed in the suction passage 19. That is,
The suction valve 20 is provided coaxially with the plunger chamber 16 and at the bottom. A return spring 21 holds the suction valve 20, and a plug 22 holding the return spring 21 is held by the return spring 23 of the plunger 17.

Reference numeral 24 denotes a discharge passage that opens in the side wall of the plunger chamber 16 and is formed toward the center of the rotor 1. A discharge valve 25 is interposed in the discharge passage 24 via a return spring 26.

Further, a main passage 27 is formed in the center of the rotor 1, and the main passage 27 communicates with the discharge passage 24 through an orifice 28, which is a means for generating flow resistance.
is connected to.

Further, the main passage 27 communicates with the suction passage 19 via a passage 30 formed in the rotor 1.

Further, 31 is a plug that holds the return spring 26, 32 is a piston, and 33 is a spring that holds the piston 32. Also, 34°35 is an oil seal,
36 is a stop ring, and 37 is a thrust washer.

Here, 38 is a needle valve (valve means) that makes the opening area of the orifice 28 variable, and the needle valve 38 is movably housed in a plug member 39 inserted into the rotor 1. A seal member 66 is interposed between the plug member 39 and the casing 3.

A diaphragm mechanism 40 that rotates together with the needle valve 38 and controls movement of the needle valve 38 is integrally attached to the rear end of the needle valve 38 . The diaphragm mechanism 40 includes a diaphragm cover 41, a diaphragm 43 that defines the inside of the diaphragm cover 41 into a first chamber 42A and a second chamber 42B, a diaphragm plate 44 that supports the diaphragm 43, and a needle valve 38.
and a return spring 45 that urges the.

46 is a cover that houses the diaphragm mechanism 40;
A cover 46 is attached to the casing 3. The inside of the cover 46 is connected to the A chambers 48A and B through the seal member 47.
The A chamber 48A communicates with the first chamber 42A through the communication hole 41A, the B chamber 48B communicates with the second chamber 42B through the opening 41B, and the A chamber 48A communicates with the first boat 42A. 49, and a second boat 50 opens into the B chamber 48B. Therefore, by controlling the air pressure of the first boat 49 and the second boat 50 from the outside,
Diaphragm mechanism 40 can be controlled.

Next, FIG. 2 shows the arrangement of the joints.

In FIG. 2, 51 is an engine, 52 is a transmission, and 53 is a transfer.

A main shaft 54 is rotatably supported within the transfer 53 by the casings 2 and 3 via bearings 55 and 56, and the main shaft 54 is provided with a drive sprocket 8. A driven sprocket 7 connected to a drive sprocket 8 by a chain 9 is rotatably supported by the rotor 1 via a needle bearing 6. The rotor 1 incorporates the joint 57 described above.

In addition, 58 is the right front wheel, 59 is the left front wheel, 60 is the right rear wheel, 6
1 is the left rear wheel, 62 is the front wheel side differential gear device,
63 is a rear wheel side differential gear device, 64 is a front wheel side propeller shaft, and 65 is a rear wheel side propeller shaft.

Next, the effect will be explained.

When a rotation difference occurs between the cam housing 18, which rotates integrally with the driven sprocket 7, and the rotor 1, the plunger 17, which is in the discharge stroke, is pushed in the axial direction by the cam surface 18A, and the fluid in the plunger chamber 16 is discharged. It is pushed out to the discharge passage 24 via the valve 25.

As a result, the needle valve 38 is connected to the return spring 4.
5 to the right in the figure to open the orifice 28. In this case, the return spring 45 is connected to the first port 49
When the negative pressure of the joint is "0", the transmission torque of the joint is set to be approximately "0".

Therefore, as shown in FIG. 3, if the negative pressure in the first port 49 is increased with the second port 50 open to the atmosphere, the negative pressure will flow into the first chamber 42A via the A chamber 48A1 communication hole 41A. As a result, the diaphragm 43 moves the needle valve 38 to the left in the figure to squeeze the orifice 28, and the transmitted torque t increases in accordance with the negative pressure. the result,
Regardless of the rotational speed difference ΔN, the transmitted torque t can be freely controlled by changing the negative pressure. The negative pressure may be controlled by a current proportional valve or the like, and in some cases, the negative pressure sucked into the engine may be directly used.

In this way, in this embodiment, the opening area of the orifice 28 is controlled by the diaphragm mechanism 40, so unlike the conventional system, oil leakage does not occur, control accuracy does not deteriorate, and expensive Does not require hydraulic power source.

Further, unlike in the conventional case, power supply failures do not occur, and durability does not deteriorate due to wear. Furthermore, since a large force can be produced by the diaphragm 43, the required performance can be obtained even with a large joint.

Next, FIGS. 4 and 5 are diagrams showing a second embodiment of the present invention.

In FIG. 4, 71 is an orifice valve having an orifice 72, and the orifice valve 71 is provided in a passage 74 between the high pressure chamber 29 and the main passage 27 via a return spring 73. 75 is a holding member that holds the return spring 73.

Next, the operation when both the first port 49 and the second port 50 are opened to the atmosphere will be described. In this case, the diaphragm mechanism 40 does not operate.

As shown in FIG. 5, the orifice valve 71 does not move until the discharge pressure of the high pressure chamber 29 reaches tl, and the orifice 72 provides the normal characteristics indicated by A.

When the discharge pressure t of the high pressure chamber 29 exceeds tl, the orifice valve 71 moves and the orifice 72 is connected to the needle valve 3.
8 and enters the locked state (see B). Further, when the discharge pressure t of the high pressure chamber 29 increases and reaches t2, the needle valve 38 moves to the right against the return spring 45. Therefore, as shown by C in Figure 5,
It becomes a relief characteristic and can limit the torque t.

Next, the operation when the first port 49 is opened to the atmosphere and the second port 50 is set to negative pressure will be described. Since the negative pressure acts on the second chamber 42B through the opening 41B of the B chamber 48B1, the needle valve 38 is moved to the right by the diaphragm 43. Therefore, since the t IJ fitting 72 is not closed by the needle valve 38, it is not locked as shown in FIG. 5D. In other words, it returns to its normal characteristics.

This control releases the hydraulic lock when the accelerator is released in order to prevent the hydraulic lock from occurring in tight corners and the like. Note that other effects are the same as in the above embodiment.

[Effects of the Invention] As described above, according to the present invention, the diaphragm mechanism is integrally attached to the valve means that makes the opening area of the orifice variable, the valve means is controlled, and air pressure is supplied to the diaphragm mechanism. Since this can be easily performed, durability and control accuracy can be improved, and costs can be reduced, such as not requiring an expensive hydraulic power source. Furthermore, since the diaphragm can generate a large amount of force, the required performance can be achieved even with large joints.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing the first embodiment of the present invention, Fig. 2 is a diagram showing the arrangement of the joint, Fig. 3 is a graph showing torque characteristics, and Fig. 4 is a diagram showing the second embodiment of the invention. The cross-sectional view and FIG. 5 are graphs showing torque characteristics. In the figure, 1... Rotor (first rotating member), 2.3... Casing, 4.5... Bearing, 6... Needle bearing, 7... Driven sprocket, 8... Drive sprocket, 9... Chain, 10... Output flange, 11... Nut, 12.13... Oil seal, 14... Stop ring, 15... Thrust washer, 16... Plan Jar chamber, 17... Plunger 18... Cam housing (second rotating member) 18A.
...Cam surface, 19...Suction path, 20...Suction valve, 21...Return spring, 22...Plug, 3...Return spring, 4...Discharge path, 5... Discharge valve, 6... Return spring, 7... Main passage, 8... Orifice, 9... High pressure chamber, 0... Passage, 1... Plug, 2... Piston, 3. ... Return spring, 4.35... Oil seal, 6... Stop ring, 7... Thrust washer, 8... Needle valve, 9... Plug member, 0... Diaphragm mechanism, 1 ... Diaphragm cover 41A... Communication hole, 41B... Opening, 42A... First chamber, 42B... Second chamber, 43... Diaphragm, 44... Diaphragm plate, 45. ... Return spring, 46... Cover 47... Seal member, 48A... Room A, 48B... Room B, 49... First port, 50... Second boat, 51...・Engine, 52...Transmission, 53...Transfer 54...Main shaft, 55.56...Bearing, 57...Coupling, 58...Right front wheel, 59...Left front wheel, 60 ...Right rear wheel, 61...Left rear wheel, 62...Front wheel side differential gear device, 63...
- Rear wheel side differential gear device, 64... Front wheel side propeller shaft, 65... Rear wheel side propeller shaft 66... Seal member, 71... Orifice valve, 72... Orifice, 73... Return spring, 74... Passage, 75... Holding member. Patent applicant: Fuji Iron Works Co., Ltd.

Claims (2)

[Claims] (1) A hydraulic pump driven by a difference in rotational speed between a first rotating member and a second rotating member that are relatively rotatable, and a flow resistance generating means that generates flow resistance in a discharge path of the hydraulic pump. In the hydraulic power transmission joint in which the transmission torque between the first and second rotating members is controlled by the flow resistance, the valve means for making the opening area of the flow resistance generation means variable is connected to the one rotation member. 1. A hydraulic power transmission joint, characterized in that a diaphragm mechanism is provided inside the valve means and is integrally provided with the valve means, the diaphragm mechanism being operated by pneumatic pressure to control the valve means. (2) The inside of the cover that houses the diaphragm mechanism is divided into two chambers by a sealing member, and the diaphragm mechanism is operated by controlling the air pressure in these two chambers from the outside. The hydraulic power transmission joint according to claim 1.