JPH0716038U - Hydraulic power transmission coupling - Google Patents

Abstract

(57) [Abstract] [Purpose] The purpose of the hydraulic power transmission joint is to reduce the cost, improve the reliability, and downsize the joint. [Structure] A deformable membrane member 62 for holding a predetermined amount of gas in a state of being separated from oil is provided inside the joint, and an elastic deformation thicker than the membrane portion is formed around the outer diameter or inner diameter of the membrane member 62. Possible bead portions 64, 65 are provided, and a cover member 66 for fixing the bead portions 64, 65 in a compressed state is provided between the housing 1 of the joint and the housing 1 and the bead portion 64 are in close contact with each other to seal oil. The bead portion 65 and the cover member 66 are closely attached to each other to seal the gas.

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]

 As a conventional hydraulic power transmission joint, there is, for example, one shown in FIG. 6 (see Japanese Utility Model Laid-Open No. 15859/1989). In FIG. 6, this hydraulic power transmission joint has an accumulator structure in which a deformable flexible membrane 102 traps air in a sheet metal cover 101.

The sheet metal cover 101 is provided so as to cover the outer periphery of the joint body 103, and an oil chamber 104 is formed between the sheet metal cover 101 and the joint body 103. In order to prevent oil leakage from the oil chamber 104, O-rings 105 and 106 are provided between the sheet metal cover 101 and the joint body 103. The sheet metal cover 101 is positioned by a stopper ring 107. A deformable flexible film 102 is hermetically fixed inside the sheet metal cover 101, and an air chamber 108 for confining air is formed between the sheet metal cover 101 and the flexible film 102.

An inner end portion 109 of the flexible film 102 is fixed to an inner circumference of a bending portion 110 of the sheet metal cover 101, and an outer end portion 111 of the flexible film 102 is an upper portion of the sheet metal cover 101 via an iron frame 112. It is fixed to the inner wall 113. When the temperature of the joint rises and the enclosed oil enclosed in the joint thermally expands, the oil in the oil chamber 104 compresses the flexible membrane 102. Thus, the thermal expansion of the enclosed oil is absorbed by the flexible membrane 102.

[0005]

[Problems to be solved by the device]

 However, in such a conventional hydraulic power transmission joint, a double seal portion is required which is a seal portion between the flexible membrane and the sheet metal cover and a seal portion between the sheet metal cover and the joint body. Yes, the cost is high. Moreover, since the seal portion is doubled, the reliability is lowered.

Further, since the seal portion of the flexible membrane itself requires a large space, the size of the joint becomes large. The present invention has been made in view of such conventional problems, and a bead portion thicker than the film thickness is provided on the inner and outer diameter portions of the flexible membrane, and the bead portion is sandwiched between the housing and the sheet metal cover. It is an object of the present invention to provide a hydraulic power transmission joint that is low in cost, has high reliability, and can be downsized.

[0007]

[Means for Solving the Problems]

 In order to achieve the above-mentioned object, the present invention provides a hydraulic pump provided between input / output shafts capable of relative rotation, and driven by differential rotation of the both shafts; A flow resistance generating means for generating a flow resistance of; and an accumulator mechanism for absorbing a volume change of oil sealed inside; a hydraulic power transmission joint for transmitting a torque according to a rotational speed difference between the two shafts; A deformable membrane member that keeps a predetermined amount of gas separated from oil is provided inside the joint, and an elastically deformable bead portion thicker than the membrane portion is provided around the outer or inner diameter of the membrane member. And a cover member for fixing the bead portion in a compressed state between the housing of the joint, and sealing the oil by the close contact between the housing and the bead portion, and the bead portion. Characterized by sealing the gas by contact of said cover member.

Further, the present invention is characterized in that an inner cover for restricting excessive deformation of the membrane member and determining a volume of a gas chamber formed between the membrane member and the cover member is provided in the housing. To do.

[0009]

[Action]

 According to the hydraulic power transmission joint of the present invention having such a configuration, the deformable membrane member that keeps a predetermined amount of gas separated from oil is provided inside the joint, and A bead portion that is thicker than the membrane portion and elastically deformable is provided around the outer or inner diameter of the member, and a cover member that fixes the bead portion in a compressed state is provided between the housing and the joint housing. Since the oil is sealed by the close contact between the bead portion and the bead portion, and the gas is sealed by the close contact between the bead portion and the cover member, a component for sealing the cover member is not required, and the cost can be reduced.

Further, since the seal portion is reduced, reliability can be improved. Further, since the bead portion does not require a large space, the joint can be downsized.

[0011]

【Example】

 Embodiments of the present invention will be described below with reference to the drawings. 1 to 5 are views showing an embodiment of the present invention. FIG. 1 is a sectional view according to an embodiment of the present invention. First, the structure will be described. In FIG. 1, reference numeral 1 denotes a housing, and the housing 1 is connected to an output shaft (not shown) and rotates integrally with the output shaft.

The housing 1 is composed of a housing non-magnetic portion 1A made of a non-magnetic material and another portion made of a magnetic material including the member 2 having the spline 2A. Reference numeral 3 denotes a cam, and the cam 3 is supported on the inner surface of the housing 1 so as to be rotatable by a predetermined angle. The cam 3 has a cam surface 3A composed of a plurality of cam peaks and cam valleys, and has a plurality of projections 3B for positioning and torque transmission on the outer periphery thereof where the cam peaks are on the side surfaces.

When the projection 3B of the cam 3 is engaged with the notch 1B formed in the housing 1 and the cam 3 rotates integrally with the housing 1 in the rotation direction of the rotor 4, when the rotation direction of the rotor 4 changes, The cam 3 circulates together with the rotor 4, rotates until the projection 3B of the cam 3 contacts the notch 1B of the housing 1, and then rotates integrally with the housing 1. The rotor 4 is rotatably housed in the housing 1, is coupled to the input shaft 5, and rotates together with the input shaft 5.

A plurality of plunger chambers 6 are formed in the rotor 4 in the axial direction, and a plurality of plungers 7 slide in the plunger chamber 6 via a return spring 8 which also functions as a preload mechanism. It is stored freely. Further, the rotor 4 is formed with a plurality of intake / exhaust holes 9 so as to communicate with the respective plunger chambers 6. The valve side surface of the rotor 4 is shown in FIG.

A plurality of suction / discharge holes 9 are formed in the rotor 4 in the circumferential direction, and the suction / discharge holes 9 communicate with the plunger chambers 6, respectively. A spline 10 is formed on the inner circumference of the rotor 4, and the rotor 4 is spline-coupled to the input shaft 5. Referring again to FIG. 1, reference numeral 11 denotes a rotary valve as a valve body in which an intake port 12 and a discharge port 13 are formed. The rotary valve 11 engages a notch 1B of the housing 1 with a protrusion 14 to make the housing 1 Positioned and fixed to.

Further, the discharge port 13 communicates with the high pressure chamber 15, and an orifice 16 as a flow resistance generating means is formed at the outlet of the high pressure chamber 15. Further, a relief hole 17 communicating with the high pressure chamber 15 is formed in the rotary valve 11, and the relief hole 17 is opened on the back side of the rotary valve 11. A discharge hole 18 is formed in the rotary valve 11, and the discharge hole 18 communicates with the suction port 12 and opens on the back side of the rotary valve 11. The discharge hole 18 discharges the oil accumulated in the third port 19 formed on the surface side of the rotary valve 11 when transmitting the torque.

Next, FIG. 3 shows the front side of the rotary valve 11. In FIG. 3, a plurality of suction ports 12 that open to the outer circumference of the rotary valve 11 are formed in the circumferential direction, and a plurality of discharge ports 13 are formed between the suction ports 12. The third port 19 is formed on the inner diameter side of the suction port 12 and the discharge port 13, and has a bearing pad portion 20 which is flush with the valve surface of the rotary valve 11.

The third port 19 may be formed on the cross section side of the rotor 4, but here it is formed on the surface side of the rotary valve 11. A plurality of oil drain holes 21 communicating with the third port 19 are formed in the rotary valve 11, and the oil drain holes 21 are opened on the back surface of the rotary valve 11. The oil drain hole 21 drains the oil accumulated in the third port 19 when it is not free, and the high pressure oil flows back from the oil drain hole 21 to the third port 19 when it is free. There is.

An outflow passage 22 is formed on the outer periphery of the rotary valve 11, and the oil discharged from the orifice 16 flows out from the outflow passage 22 to the low pressure chamber in the joint. That is, the outflow passage 22 allows the oil discharged from the orifice 16 to flow to the plunger chamber 6 side rather than to the oil chamber side in which the movable magnetic body described later is provided. Referring again to FIG. 1, reference numeral 23 denotes a retainer provided in contact with the rotary valve 11. The retainer 23 is supported by the bearing 24 and rotates integrally with the housing 1. A seal ring 25 is interposed between the retainer 23 and the input shaft 5, the seal ring 25 prevents oil leakage, and a stopper ring 26 provided on the inner circumference of the housing 1 moves the retainer 23 to the right in the figure. Prevent.

A first groove 27 communicating with the orifice 16 of the rotary valve 11 is formed in the retainer 23, and the first groove 27 communicates with the outflow passage 22. Reference numeral 28 denotes a lock valve. The lock valve 28 is slidably inserted into the retainer 23 and projects into the first groove 27 to open and close the orifice 16. The lock valve 28 is concentrically arranged with the orifice 16 and has a conical or spherical shape at its tip and is made of a rod-shaped member thicker than the orifice hole diameter, and directly closes the orifice 16.

A second groove 29 communicating with each discharge port 13 of the rotary valve 11 and the high pressure chamber 15 is formed in the retainer 23, and a third groove 30 communicating with the relief hole 17 of the rotary valve 11 is formed. Has been formed. Reference numeral 31 is a relief valve. The relief valve 31 is slidably inserted into the retainer 23 and protrudes into the third groove 30 to open and close the relief hole 17.

The relief valve 31 is concentrically arranged with the relief hole 17 and has a conical or spherical shape, and is made of a rod-shaped member thicker than the relief hole diameter so as to directly close the relief hole 17. The oil discharge hole 21 communicating with the third port 19 and the discharge hole 18 of the rotary valve 11 also communicate with the third groove 30.

Reference numeral 33 is a free valve. The free valve 33 is slidably inserted into the retainer 23 and protrudes into the third groove 30 to open and close the discharge hole 18. The free valve 33 is a rod-shaped member having a conical shape or a spherical shape at the distal end arranged concentrically with the discharge hole 18 and having a diameter larger than the diameter of the discharge hole, and directly closes the discharge hole 18. A movable magnetic body 34 generates a magnetic attraction force by energizing the solenoid coil 35, and the movable magnetic body 34 is movably accommodated in the housing 1. When a weak current is applied to the solenoid coil 35, the upper side of the movable magnetic body 34 is attracted to the retainer 23 side, the lock valve 28 is activated, and a strong current is applied to the solenoid coil 35. Is sucked toward the retainer 23, and the free valve 33 and the relief valve 31 are operated via the reversing lever 36.

Next, FIG. 4 shows the movable magnetic body 34 and the reversing lever 36. In FIG. 4, a return spring 37 is interposed between the lower side of the movable magnetic body 34 and the retainer 23. Therefore, when the solenoid coil 35 is weakly energized, the upper side of the movable magnetic body 34 is attracted to the retainer 23 side, and the lock valve 28 is activated. On the other hand, when the solenoid coil 35 is strongly energized, the entire circumference of the movable magnetic body 34 is retained. The free valve 33 and the relief valve 31 are actuated by suction to the 23 side. That is, the free valve 33 closes the discharge hole 18, and the relief valve 31 opens the relief hole 17.

Further, a relief pressure setting spring 38 is provided between the lower side of the reversing lever 36 and the retainer 23, and the pressure of the high pressure chamber 15 is set to the relief pressure setting spring 38 when the characteristic is the normal characteristic or the lock characteristic. When the set value of is exceeded, the relief valve 31 operates to open the relief hole. This can prevent the generation of excessive torque. The reversing lever 36 is provided with a fulcrum 39, and the reversing lever 36 swings around the fulcrum 39 to operate the free valve 33 and the relief valve 31.

When the oil is not free, the oil accumulated in the third port 19 is discharged from the discharge hole 18 through the oil discharge hole 21 and the third groove 30. When free, the oil in the high pressure chamber 15 flows back to the oil drain hole 21 through the relief hole 17 and the third groove 30, and then flows to the third port 19. Referring again to FIG. 1, reference numeral 61 denotes an inner cover formed of a non-magnetic sheet metal. The outer peripheral portion of the inner cover 61 is inserted into the housing 1, and the inner peripheral portion is fixed to the retainer 23. The inner cover 61 has a function as a stopper that blocks the rightward movement of the movable magnetic body 34, and the fulcrum 39 of the reversing lever 36 is in contact with the inner cover 61.

Further, the inner cover 61 is formed to have a predetermined shape, and restricts the excessive deformation of the deformable rubber film 62 as a film member. Elastically deformable bead portions 64 and 65, which are thicker than the membrane portion 63, are integrally formed on the inner and outer diameter portions of the rubber membrane 62, respectively. The bead portions 64 and 65 are sandwiched between the housing 1 and the housing 1 in a compressed state by an outer cover 66 as a cover member.

The outer diameter portion of the outer cover 66 is fitted into the V-shaped groove 1 C of the housing 1, and the inner diameter portion is inserted so as to abut the inner wall of the opening of the retainer 23. A gas chamber 67 is formed between the outer cover 66 and the rubber film 62, and a predetermined amount of gas (for example, air) is confined in the gas chamber 67. Further, an oil chamber 68 is formed between the inner cover 61 and the rubber film 62, and oil enters and leaves the oil chamber 68 through a communication hole 69 formed in the inner cover 61.

As described above, the bead portions 64 and 65 of the rubber film 62 are sandwiched between the housing 1 and the outer cover 66, so that the gas and the oil can be kept in a separated state. The housing 1 and the bead portion 64 are brought into close contact with each other to prevent the oil in the oil chamber 68 from leaking to the outside. Further, the outer cover 66 and the bead portion 65 are brought into close contact with each other to prevent the air in the gas chamber 67 from leaking.

Reference numeral 46 denotes a first magnetic frame, and the first magnetic frame 46 is fixed to an external member by a bolt 47 and is held in a non-contact state with a joint. The first magnetic frame 46 is arranged concentrically with respect to the joint shaft, and the solenoid coil 35 is housed in the first magnetic frame 46. Reference numeral 48 is a second magnetic frame, and the second magnetic frame 48 is fixed to the housing 1. The first and second magnetic frames 46 and 48 and the solenoid coil 35 as a whole constitute an actuator that operates the movable magnetic body 34 by an external signal.

Reference numerals 49 and 50 are oiling holes, 51 is a seal ring, 52 is a needle bearing, and 53 is a stopper ring. Next, the operation will be described. When the temperature of the joint does not rise, as shown in FIG. 1, the oil sealed inside the joint does not thermally expand, and therefore the oil does not flow into the oil chamber 68 from the communication hole 69. It is inflated by the gas trapped in 67.

On the other hand, when the temperature of the joint rises, as shown in FIG. 5, the oil sealed in the joint thermally expands and enters the oil chamber 68 through the communication hole 69. Therefore, the rubber film 62 is deformed, and the gas trapped in the gas chamber 67 is compressed. In this way, the rubber film 62 absorbs the thermal expansion of oil and functions as an accumulator.

In this embodiment, the bead portions 64 and 65 seal the space between the housing 1 and the outer cover 66 and the rubber film 62 and the outer cover 66. O-rings for seals are not required, and costs are low. Further, in the past, the seal portion was doubled, but in the present embodiment, since the seal portion is reduced, the reliability can be improved.

Further, since the rubber film 62 can be provided along the inner cover 61, the volume of the gas chamber 67 can be increased, and the joint can be downsized.

[0035]

[Effect of device]

 As described above, according to the present invention, the oil is sealed by the bead portion of the housing member and the bead portion of the membrane member, and the air is sealed by the bead portion and the cover member. Since the parts for sealing are unnecessary, the cost can be reduced.

Further, since the seal portion is reduced, reliability can be improved. Further, since the volume of the gas chamber formed by the membrane member can be widened, the joint can be downsized.

[Brief description of drawings]

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

FIG. 2 is a diagram showing a valve side surface of a rotor.

[Figure 3] Surface view of rotary valve

FIG. 4 is a diagram showing a movable magnetic body and a reversing lever.

FIG. 5 is an explanatory diagram of the operation

FIG. 6 is a diagram showing a conventional example.

[Explanation of symbols]

 1: Housing 1A: Housing non-magnetic part 1B: Notch 1C: V groove 2: Member 2A: Spline 3: Cam 3A: Cam surface 3B: Protrusion 4: Rotor 5: Input shaft 6: Plunger chamber 7: Plunger 8 : Return spring 9: Suction / discharge hole 10: Spline 11: Rotary valve 12: Suction port 13: Discharge port 14: Protrusion 15: High pressure chamber 16: Orifice 17: Relief hole 18: Discharge hole 19: Third port 20: Bearing Pad part 21: Oil drain hole 22: Outflow path 23: Retainer 24: Bearing 25: Seal ring 26: Stopper ring 27: First groove 28: Lock valve 29: Second groove 30: Third groove 31: Relief Valve 33: Free valve 34: Movable magnetic body 35: Solenoid coil 36: Reversing lever 37: Return spring 38 Relief pressure setting spring 39: fulcrum 46: first magnetic frame 47: bolt 48: second magnetic frame 49, 50: oiling hole 51: seal ring 52: needle bearing 53: stopper ring 61: inner cover 62: rubber film 63: Membrane part 64, 65: Bead part 66: Outer cover (cover member) 67: Gas chamber 68: Oil chamber 69: Communication hole

Claims (2)

[Scope of utility model registration request] 1. A hydraulic pump provided between relatively rotatable input / output shafts and driven by differential rotation of the both shafts; a flow provided at an outlet of the hydraulic pump to generate flow resistance of discharge oil. A resistance generating means; an accumulator mechanism for absorbing a volume change of oil sealed inside; a hydraulic power transmission joint for transmitting torque according to a rotational speed difference between the both shafts; a predetermined amount of gas inside the joint A deformable membrane member that keeps the oil separated from the oil is provided, and an elastically deformable bead portion thicker than the membrane portion is provided at the periphery of the outer diameter or the inner diameter of the membrane member. A cover member for fixing the bead portion in a compressed state is provided between the housing and the bead portion to seal the oil, and the bead portion and the cover member are closely attached to each other. A hydraulic power transmission joint that seals gas. 2. An inner cover for restricting excessive deformation of the membrane member and for determining the volume of a gas chamber formed between the membrane member and the cover member is provided in the housing. Hydraulic power transmission joint.