JPH0583473U - Hydraulic power transmission coupling - Google Patents

Abstract

(57) [Summary] (Correction) [Purpose] The purpose of the present invention is to simplify the structure and reduce the cost of a hydraulic power transmission joint used for distributing the driving force of a vehicle. [Structure] Housing 18, rotor and plunger chamber 2
2 is provided with a plunger 23, and a suction hole 25 formed in the head of the plunger 23;
One-way valve 2 as an intake valve housed inside
6; a high pressure chamber 33 formed in the rotor and communicating with the plunger chamber 22; and a flow resistance generating means formed at the outlet of the high pressure chamber 33.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a hydraulic power transmission joint used for distributing a driving force of a vehicle.

[0002]

[Prior Art]

 The applicant of the present invention has proposed the following hydraulic power transmission joint in Japanese Patent Application Laid-Open No. 2-89821. That is, this hydraulic power transmission joint is provided between the input and output shafts that can rotate relative to each other, and is provided with flow rate generating means for flowing an amount of fluid according to the rotational speed difference between the two shafts. In the rotation difference sensitive joint in which the transmission torque between the input and output shafts is controlled, the flow rate generating means is a first rotating member integrally formed with one of the input and output shafts and having a cam surface on an inner peripheral portion. A second rotary member that is integrally formed with the other of the input / output shaft and is inserted into the cam surface; and a second rotary member that is supported by the second rotary member and that is in sliding contact with the cam surface. A cam body that reciprocates in the radial direction at the time of rotation, a plurality of fluid chambers that change in volume as the cam body reciprocates, and a fluid that connects between the fluid chambers formed in the second rotating member via orifices. And the shape of the cam surface The total value of transmission torque generated by rotation is set to be almost equal at all relative rotation angle positions, and the forward and reverse rotation sides of relative rotation are set to have a difference in torque transmission characteristics. ..

[0003]

[Problems to be solved by the device]

 However, such a conventional hydraulic power transmission joint has the following problems. (1) Since the one-way valve is inside the rotor, the shaft cannot be passed through the center. Therefore, when trying to mount the unit on a vehicle, the first and second rotating shafts have a flat surface and a spigot on the end faces of the unit, and are attached by bolts, which is complicated and heavy, and there is no overhang from the mounting unit. It becomes larger, and the excitation force on the vehicle tends to become larger. (2) Since the oil outlet of the orifice is close to the inlet of the one-way valve, the high temperature oil ejected from the orifice is sucked into the piston, and the temperature of the oil becomes high, which easily causes deterioration of the oil. (3) The seating surface of the ball of the one-way valve must be accurate in order to prevent high-pressure leakage, and it is desirable to perform a leak test when the rotor is completed as a unit, but it is already necessary to process the orifice circuit. It is difficult to do a leak test only for this part. Further, since the rotor has many valve seat surfaces, if even one is defective, the expensive rotor becomes defective. (4) Since the check ball receives centrifugal force due to rotation, it is necessary to design the spring force in consideration of usage conditions.

The present invention has been made in view of such conventional problems, and an object thereof is to simplify the structure and reduce the cost.

[0005]

[Means for Solving the Problems]

 According to another aspect of the present invention, there is provided a housing provided between input / output shafts capable of relative rotation, connected to the one shaft, and having a cam surface having two or more ridges. A rotor coupled to the other shaft and forming a plurality of plunger chambers; housed in each of the plurality of plunger chambers under the pressure of a return spring so as to be capable of reciprocating movement, and relative to the two shafts. A plurality of plungers driven by the cam surface during rotation; a suction hole formed in the head of the plunger; a suction valve and a one-way valve housed inside the plunger; A high pressure chamber that is formed and communicates with the plunger chamber; and a flow resistance generation unit that is formed at the outlet of the high pressure chamber.

Further, according to the present invention, the one-way valve includes a check ball, a check spring, and a retainer. Also, in the present invention, the weight of the check ball is reduced.

[0007]

[Action]

 In the present invention, since the one-way valve is put in the plunger, the inner diameter of the rotor shaft can be made large, and by passing the mounting bolt to another unit, it is simple and lightweight, and the overhang can be reduced. , It is possible to suppress the excitation force to the vehicle to a small level.

Further, since the orifice is provided on the side of the rotor shaft to divide the oil suction hole of the plunger, the high temperature oil ejected from the orifice comes into contact with the housing and the accumulator piston to radiate heat and be sucked. Therefore, the rapid deterioration of oil is alleviated. In addition, the function check of the one-way valve can be done by sub-assembling the check spring of the check ball and the retainer in the plunger. It can exert various functions.

Further, since the check ball receives a centrifugal force when the joint rotates, it is sufficient to push the check spring with a light force. Normally, when operating this hydraulic coupling, it is often necessary to run under conditions of medium speed or lower, and it is not necessary to consider that the valve will not open due to centrifugal force, but if it is used at high speed, the weight should be reduced. Operation is possible if the check valve is made lighter.

[0010]

【Example】

 Embodiments of the present invention will be described below with reference to the drawings. 1 to 6 are views showing an embodiment of the present invention. First, the configuration will be described. In FIGS. 1 and 2, reference numeral 1 denotes a case such as a transformer, and one end of an input shaft 3 is rotatably supported by the case 1 via a bearing 2. The input shaft 3 is formed with a male spline portion 4 and a screw portion 5.

Reference numeral 6 denotes a rotor shaft (first rotating member) of a joint 7 connected to the input shaft 3, and a hollow portion 8 is formed in the rotor shaft 6. A step portion 9 is formed in the hollow portion 8, and a small-diameter portion 10 on the right side of the step portion 9 is formed with a female spline portion 11 which is fitted to the spline portion 4 of the input shaft 3. The rotor shaft 6 and the input shaft 3 are spline-fitted by the spline portions 11 and 4, the washer 12 is inserted into the threaded portion 5 until it abuts on the step portion 9, and the nut 13 is fastened.

The cylindrical surface of the outer diameter portion 14 of the rotor shaft 6 is precision-finished, and an oil seal 15 is interposed between the outer diameter portion 14 and the case 1. Reference numeral 16 is a thrust block connected to an output shaft (not shown). The thrust block 16 is integrally welded to a housing 18 having a cam surface 17 elongated in the axial direction. It constitutes two rotating members.

The thrust block 16 is formed with a flat surface portion 19, a spigot portion 20, and a bolt hole 21, respectively. A plurality of plunger chambers 22 are formed in the rotor shaft 6 in the radial direction, and a plurality of plungers 23 are slidably accommodated in the plunger chamber 22 via return springs 24.

A suction hole 25 is formed in the head of the plunger 23, and a one-way valve 26 as a suction valve is housed inside the plunger 23. The one-way valve 26 includes a check ball 27 seated in the suction hole 25, a check spring 28 that supports the check ball 27, and a retainer 29 that holds the check spring 28.

As shown in FIG. 3, the retainer 29 has a plurality of notches 30 and an opening 31 so that oil can easily flow from the suction hole 25. Further, as the one-way valve 26, a lightweight check ball 32 as shown in FIG. 4 may be used. In this case, it can be used at high speed.

Reference numeral 33 denotes a high pressure chamber formed in the rotor shaft 6, and the high pressure chamber 33 communicates with the plunger chamber 22. An orifice 34 as a flow resistance generating means is formed at the outlet of the high pressure chamber 33. Reference numeral 35 is a retainer plate, and the retainer plate 35 supports the rotor shaft 6 at a predetermined position with respect to the housing 18. The retainer plate 35 is positioned by the snap ring 36.

Reference numeral 37 denotes an accumulator piston that rotates together with the housing 18, and the accumulator piston 37 moves according to the internal pressure and absorbs the thermal expansion of the enclosed oil. A return spring 39 is interposed between the accumulator piston 37 and the retainer 38, and an oil seal 40 is interposed between the accumulator piston 37 and the rotor shaft 6.

Reference numeral 41 is an oil seal, 42 is a needle bearing, and 43 is an O-ring. Next, the operation will be described. When a difference in rotation occurs between the housing 18 and the rotor shaft 6, the plunger 23 in the discharge stroke is pushed radially by the cam surface 17 of the housing 18.

The oil in the plunger chamber 22 is supplied from the high pressure chamber 33 through the orifice 34 to the low pressure chamber 44. At this time, the hydraulic pressure in the plunger chamber 22 and the high pressure chamber 33 increases due to the resistance of the orifice 34, and a reaction force is generated in the plunger 23. A torque is generated by rotating the housing 18 against the Plunger reaction force, and the torque is transmitted between the housing 18 and the rotor shaft 6.

That is, in FIG. 2, assuming that the housing 18 is fixed and the rotor shaft 6 rotates in the direction of the arrow, the plungers 23A and 23D transmit the torque to the cam surface 17, but the cam surface 17 The characteristics are changed to 15 °, 15 °, and 15 °, and the first 15 ° is a curve that gradually increases the torque. It is constant between 15 ° and 30 ° with rotation. Since the plungers 23A and 23D are pushed in at a speed of, a constant torque is transmitted, and the cam curve is set so that the pushing speed gradually decreases between 30 ° and 45 °.

Therefore, the plungers 23A and 23D transmit the torque only during 45 ° (see FIG. 5, A). Next, the plungers 23B and 23E transmit torque in the same manner, and the plungers 23C and 23F similarly transmit torque (see FIGS. 5, B and C). Therefore, the torque is transmitted so that the total torque of each plunger 23 becomes constant in any phase of the rotation (see FIG. 5, D).

On the other hand, when the rotational speed changes, the amount of oil changes, so that the torque is proportional to the square of the relative rotation between the rotor shaft 6 and the housing 18, as shown in E of FIG. Will be. As shown in FIG. 5, the plunger 23 does not generate a large force toward the center of the head in the vicinity of 0 ° and in the vicinity of 45 °, so that the surface pressure due to the pressing does not become so large. When the plunger 23 transmits a large torque, for example, in the case of the plungers 23A and 23D, the surface pressure becomes large at 15 ° to 30 °, but in this case, the plungers 23A and 23D and the cam surface 17 of the housing 18 come into contact with each other. Is deviated from the tops of the plungers 23A and 23D and is not affected by the suction hole 25. If there is a problem in surface pressure on the driving side, it may be possible to slightly shift the hole position to the non-driving side.

In addition, since the stroke amount of the plunger 23 is small in the suction condition near 0 ° and 45 °, the movement amount of oil is small and the opening does not need to be large, but the suction amount is around 15 ° to 30 °. Since the amount is large, an opening is required, but it can be seen from FIG. 2 that the area is sufficiently wider than the orifice diameter. In the present embodiment, since the one-way valve 26 is housed in the plunger 23, the inner diameter portion of the rotor shaft 6 can be made large and the mountability on the vehicle can be improved.

Since the orifice 34 is formed at the outlet of the high pressure chamber 33 of the rotor shaft 6 and is provided far from the suction hole 25, it is possible to prevent the temperature of the oil from rising and to mitigate the deterioration. The one-way valve 26 is composed of a check ball 27, a check spring 28, and a retainer 29, so that oil leakage can be easily checked in the sub-assembly state.

Since the check ball 28 receives centrifugal force when the joint 7 rotates, the check spring 28 need only be pushed with a light force. When the joint 7 is used even at high speed, the check ball 32 has a reduced weight. Can be used.

[0026]

[Effect of the device]

 As described above, according to the present invention, the structure can be simplified, the excitation force on the vehicle can be suppressed, and the cost can be reduced.

[Brief description of drawings]

FIG. 1 is a diagram showing an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is a perspective view of a retainer.

FIG. 4 is a diagram showing another one-way valve.

FIG. 5 is a graph showing the relationship between rotation angle and transmission torque.

FIG. 6 is a graph showing torque characteristics

[Explanation of symbols]

 1: Case 2: Bearing 3: Input shaft 4: Spline part 5: Screw part 6: Rotor shaft 7: Joint 8: Hollow part 9: Step part 10: Small diameter part 11: Spline part 12: Washer 13: Nut 14: Outer Diameter part 15: Oil seal 16: Thrust block 17: Cam surface 18: Housing 19: Flat part 20: Inlay part 21: Bolt hole 22: Plunger chamber 23: Plunger 23A-23F: Plunger 24: Return spring 25: Suction port 26: One-way valve 27: Check ball 28: Check spring 29: Retainer 30: Notch 31: Opening 32: Check ball 33: High pressure chamber 34: Orifice (flow resistance generating means) 35: Retainer plate 36: Snap ring 37: Accumulator piston 38: Lite Na 39: return spring 40, 41: oil seal 42: needle bearing 43: O-ring 44: low-pressure chamber

Claims (3)

[Scope of utility model registration request] 1. A housing provided between relatively rotatable input / output shafts, which is connected to said one shaft and which forms a cam surface having two or more peaks; and which is connected to said other shaft. A rotor having a plurality of plunger chambers; housed in each of the plurality of plunger chambers so as to be reciprocally movable under the pressure of a return spring, and driven by the cam surface when the two shafts rotate relative to each other; A plurality of plungers; a suction hole formed in the head of the plunger; a one-way valve as a suction valve housed inside the plunger; a high pressure formed in the rotor and communicating with the plunger chamber A hydraulic power transmission joint comprising: a chamber; and a flow resistance generating means formed at an outlet of the high pressure chamber. 2. The hydraulic power transmission joint according to claim 1, wherein the one-way valve comprises a check ball, a check spring and a retainer. 3. The hydraulic power transmission joint according to claim 2, wherein the weight of the check ball is light.