JPH0583475U - Hydraulic power transmission coupling - Google Patents

Abstract

(57) [Summary] (Correction) [Purpose] With regard to a hydraulic power transmission joint used for distributing driving force of a vehicle, the structure is simple, the cost is low, and the drawback of the check valve is eliminated. To do. A plurality of suction ports 28 and a discharge port 29 which are in sliding contact with the rotor shaft 6 and are positioned in a predetermined relationship by a cam surface 17 and act as a suction valve and a discharge valve according to a positional relationship with a suction / discharge hole 25. The valve body formed on the front surface, the high pressure chamber 30 which is provided on the valve body and communicates with the discharge port 29 and opens on the rear surface of the valve body, the seal member 33 provided around the high pressure chamber 30, and the seal member 33 are pressed. The thrust bearing 34, the support member 35 that supports the thrust bearing 34, and the positioning member 36 that positions the support member 35, the thrust bearing 34, and the valve body.

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 has proposed the following hydraulic power transmission joint in Japanese Patent Application No. 4-2558. That is, this hydraulic power transmission joint is provided between the input / output shafts that are relatively rotatable, is connected to the one shaft, and a housing that forms a container for enclosing oil inside is housed in the housing. And a cam having a cam surface having two or more ridges on its inner diameter surface, which is coupled for torque transmission with the housing; and is rotatably housed in the housing while being connected to the other shaft. A rotor in which a plurality of plunger chambers are formed in the radial direction; and a plurality of plunger chambers are housed in each of the plurality of plunger chambers so as to be reciprocally movable under the pressure of a return spring, and when the two shafts rotate relative to each other. A plurality of plungers driven by cam surfaces; a suction / discharge hole that opens to one end surface of the rotor and communicates with the plunger chamber; a slide on the end surface of the rotor In addition, a valve body that is positioned in a predetermined relationship with the cam and that has a plurality of suction ports and discharge ports formed on the surface that act as a suction valve and a discharge valve depending on the positional relationship with the suction and discharge holes. A high pressure chamber provided inside the valve body and communicating with a discharge port; a piston chamber provided on the back surface of the valve body and communicating with the high pressure chamber; and housed in the piston chamber movably in the axial direction. A preload piston that acts on the housing by the pressure of the high pressure chamber to generate a load so as to press the valve body against the rotor; and a means for generating flow resistance at the outlet of the high pressure chamber.

[0003]

[Problems to be solved by the device]

 However, in such a conventional hydraulic power transmission joint, since the cam surface and the valve are separately positioned, the structure is complicated, the accuracy is difficult to obtain, and the manufacturing cost is high. Further, since the preload piston is provided in the rotary valve, the structure is complicated, and the piston is expensive because high accuracy is required to prevent leakage. Moreover, since a reaction force of hydraulic pressure is generated between the housing and the retainer, both are heavy and highly rigid.

Further, since the joint is a rotating part, these cause noise and vibration. In addition, since the rotary valve is pressed against the rotor by the preload spring, the structure becomes complicated. Further, when the check valve is used as the intake valve and the discharge valve in the radial piston type, there is a drawback that the check valve may not operate properly.

The present invention has been made in view of such conventional problems, and has a simple structure, a low cost, and a hydraulic power transmission which can eliminate the drawbacks of a check valve. The purpose is to provide a fitting.

[0006]

[Means for Solving the Problems]

 In order to achieve the above object, the present invention provides 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 on an inner diameter surface thereof. A rotor shaft connected to the other shaft and rotatably housed in the housing and having a plurality of plunger chambers formed in a radial direction; and a return spring pressed against each of the plurality of plunger chambers. A plurality of plungers that are received and reciprocally received and that are driven by the cam surfaces when the two shafts relatively rotate; and a suction / discharge hole that is formed in the rotor shaft and communicates with the plunger chamber. ; Is in sliding contact with the rotor shaft, and is positioned in a predetermined relationship by the cam surface and the protrusion, and is positioned in a suction valve and a suction valve depending on a positional relationship with the suction / discharge hole. A plurality of suction ports acting as discharge valves, a valve body having discharge ports formed on the surface, a high pressure chamber that is provided in the valve body and communicates with the discharge port and opens on the back side of the valve body, and around the high pressure chamber. A seal member provided, a thrust bearing that presses the seal member, a support member that supports the thrust bearing, a positioning member that positions the support member, the thrust bearing, and the valve body, and an outlet portion of the high pressure chamber. And a flow resistance generating means for generating flow resistance provided in the.

[0007]

[Action]

 In the present invention, the cam surface is provided long in the axial direction, and this cam surface is used as it is for positioning the valve body. For this reason, the notch processing provided in the retainer for positioning the valve element is not necessary, and conventionally, some positioning mechanism was required between the housing and the retainer, but this is also unnecessary. Further, although dimensional accuracy errors are accumulated between these, in the present invention, the problems are solved because of the simple structure.

Further, since the seal ring is provided as a seal member around the high pressure chamber on the back surface of the valve body, oil leakage from here can be completely prevented. The seal ring generally has a squeeze allowance and is assembled with a positioning member such as a snap ring so that the seal ring is squeezed to a normal position. The crushing margin of the seal ring is determined by the dimensional accuracy from the contact surface of the valve element of the rotor shaft to the groove of the snap ring and the total dimension of the valve element, thrust bearing, and supporting member, but the seal dimension is generally The crushing margin is large, and it is possible to assemble it to fully demonstrate its characteristics. If it is necessary to accurately control the rotational resistance of the valve element, the characteristics of the joint can be assembled with high precision by selectively assembling the thickness of the snap ring or spacer.

Further, since the reaction force of the hydraulic pressure generated on the back surface of the valve body is confined inside the contact surface of the valve body of the rotor shaft and inside the groove of the snap ring, it is necessary to increase the rigidity of the housing and the retainer more than necessary. There is no. In addition, the pressing force required until the valve body generates hydraulic pressure is also given by the elasticity of the seal ring when the seal ring is assembled, so there is no need for a mechanism such as a preload spring to press the rotor shaft of the valve body.

Further, since the overall structure is simplified and the rigidity of the housing and the retainer can be reduced, the weight is reduced and the level of sound, vibration, etc. is lowered and it is possible to sufficiently cope with high speed rotation.

[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. 1 to 5, reference numeral 1 denotes a case such as a transfer, 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 also with 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 the rotor shaft 6 has a hollow portion 8 formed therein. 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 an end block connected to an output shaft (not shown). The end block 16 is integrally welded to a housing 18 having a cam surface 17 elongated in the axial direction. It constitutes a rotating member.

The end 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.

Further, the rotor shaft 6 is formed with a suction / discharge hole 25 so as to communicate with each plunger chamber 22. Reference numeral 26 is a rotary valve as a valve element, and a plurality of suction passages 27, suction ports 28 and discharge ports 29 which act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes 25 are formed on the surface thereof. A high-pressure chamber 30 communicating with the discharge port 29 is formed inside thereof, and the high-pressure chamber 30 is open on the back surface of the rotary valve 26. The opening of the high pressure chamber 30 is closed by the thrust plate 31.

A seal ring groove 32 is formed around the opening of the high pressure chamber 30 on the back surface of the rotary valve 26, and a seal ring (sealing member) 33 is inserted into the seal ring groove 32. The seal ring 33 prevents oil from leaking from the high-pressure chamber 30 and presses the rotary valve 26 toward the rotor shaft 6 by its elasticity. Reference numeral 34 is a thrust bearing, and the thrust bearing 34 presses the seal ring 33 via the thrust plate 31.

The thrust bearing 34 is supported by a retaining plate (supporting member) 35, and the retaining plate 35, the thrust bearing 34, and the rotary valve 26 are positioned by a snap ring (positioning member) 36. An orifice 37 as a flow resistance generating means is formed at the outlet of the high pressure chamber 30, and the orifice 37 can communicate with the suction passage 27.

The rotary valve 26 has a positioning protrusion 38 that engages with the cam surface 17 of the housing 18. The rotary valve 26 constitutes a timing member that determines the opening / closing timing, and the cam surface 17 and the projection 38 constitute a positioning mechanism that regulates the phase relationship between the housing 18 and the rotary valve 26. The cam surface 17 has a length such that the housing 18 and the rotary valve 26 can freely rotate relative to each other in one step of the plunger stroke, for example, in the range of 45 °.

When the plunger 23 is in the intake stroke, there is a positional relationship in which the intake port 28 of the rotary valve 26 and the intake / discharge hole 25 of the rotor shaft 6 communicate with each other, and the intake passage 27, the intake port 28, and the rotor shaft of the rotary valve 26 are connected. Oil can be sucked into the plunger chamber 22 through the suction / discharge holes 25 of No. 6. When the plunger 23 is in the discharge stroke, the relationship is the reverse of the suction stroke, and the suction / discharge hole 25 of the rotor shaft 6 communicates with the discharge port 29 of the rotary valve 26 and the high pressure chamber 30.

Therefore, the oil discharged from the plunger chamber 22 flows from the discharge port 29 to the high pressure chamber 30. The friction torque between the rotor shaft 6 and the rotary valve 26 is set by the elasticity of the seal ring 33, the thrust bearing 34, the retaining plate 35, and the snap ring 36 with a slight preload. .. Therefore, when the direction of the differential rotation changes, the rotary valve 26 revolves together with the rotor shaft 6, and the positioning protrusion 38 of the rotary valve 26 rotates until it comes into contact with the cam surface 17 of the housing 18. It rotates (see FIG. 5). As a result, the intake / discharge hole 25 is forcibly opened / closed at a predetermined timing even during normal rotation or reverse rotation.

Reference numeral 39 denotes an accumulator piston that rotates integrally with the housing 18, and the accumulator piston 39 moves so as to absorb the expansion of oil. A return spring 41 is interposed between the accumulator piston 39 and the cover 40. Note that 42 and 43 are oil seals, 44 is a needle bearing, and 45 and 45a are O-rings.

Next, the operation will be described. When there is no difference in rotation between the housing 18 and the rotor shaft 6, the plunger 23 does not operate and torque is not transmitted. At this time, the plunger 23 is pressed against the cam surface 17 by the return spring 24. Next, when a difference in rotation occurs between the housing 18 and the rotor shaft 6, the plunger 23 in the discharge stroke is pushed inward by the cam surface 17 of the housing 18.

Therefore, the plunger 23 pushes the oil in the plunger chamber 22 into the high pressure chamber 30 from the suction / discharge hole 25 and the discharge port 29 of the rotary valve 26. The oil pushed out into the high pressure chamber 30 is supplied to the suction passage 27 through the orifice 37. At this time, the hydraulic pressure in the high pressure chamber 30, the discharge port 29 and the plunger chamber 22 rises due to the resistance of the orifice 37, and a reaction force is generated in the plunger 23. 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.

When the housing 18 further rotates, the suction stroke is started, and the oil in the suction passage 27 is sucked into the plunger chamber 22 through the suction port 28 and the suction / discharge hole 25 of the rotary valve 26, and the plunger 23 is held in the housing 18. Return along the cam surface 17 of. As described above, in this embodiment, the cam surface 17 of the housing 18 is formed to be long in the axial direction, and the protrusion 38 of the rotary valve 26 is engaged with the rotary valve 26 to position the rotary valve 26. The structure is simple.

Further, since the seal ring 33 is provided around the opening of the high pressure chamber 30 on the back surface of the rotary valve 26, oil leakage can be prevented. Further, the elasticity of the seal ring 33 pushes the rotary valve 26 against the rotor shaft 6 side, so that a preload spring is not required and the structure is simplified. Since the hydraulic reaction force generated on the back surface of the rotary valve 26 is enclosed in the contact surface of the rotary valve 26 of the rotor shaft 6 and the inside of the groove of the snap ring 36, it is not necessary to increase the rigidity of the housing 18.

Since the rigidity of the housing 18 can be lowered, the weight can be reduced, and the sound and vibration levels can be lowered. Furthermore, since the rotary valve system can be used, the drawbacks of the check valve can be eliminated. 6 and 7 are views showing another embodiment of the present invention.

The present embodiment is different from the previous embodiment in the rotary valve and the seal structure, the structure other than this is exactly the same, and the hydraulic pressure generated by the differential is taken out for each plunger. Is. 6 and 7, reference numeral 51 is a housing having a cam surface 52, and 53 is a rotary valve having a projection 54 that engages with the cam surface 52.

A high pressure chamber 56 communicating with an intake / discharge hole formed in the rotor shaft is formed in the rotary valve 53, and the high pressure chamber 56 is opened on the back surface of the rotary valve 53. Orifices 57 are formed at the outlets of the high pressure chambers 56, and oval seal ring grooves 58 are formed around the openings of the high pressure chambers 56. Elliptical seal rings 59 are inserted in the seal ring grooves 58, respectively. Reference numeral 60 is an intake passage, and 61 is an intake port.

Although the hydraulic pressure in the high pressure chamber 30 of the above-described embodiment is always constant during constant operation rotation, in this embodiment, although the pressure fluctuates due to rotation, the torque transmission characteristic has the same result. Also in this embodiment, the same effect as that of the above embodiment can be obtained.

[0030]

[Effect of the device]

 As described above, according to the present invention, the structure of the valve body positioning mechanism is simplified and the cost can be reduced. Further, since the preload piston and the preload spring are unnecessary, the structure is simple and the cost can be reduced. Further, it is not necessary to increase the rigidity of the housing and the like, and the weight can be reduced. Also, since the system can be used with a rotary valve, the drawbacks due to the check valve can be eliminated.

[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 cross-sectional view taken along the line CC of FIG.

FIG. 4 is a sectional view taken along the line BB of FIG.

FIG. 5 is a sectional view showing engagement between the housing and the rotary valve.

FIG. 6 is a view showing another embodiment of the present invention.

FIG. 7 is a rear view of FIG.

[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: End block 17: Cam surface 18: Housing 19: Flat part 20: Inlay part 21: Bolt hole 22: Plunger chamber 23: Plunger 24: Return spring 25: Suction / discharge hole 26: Rotary Valve 27: Suction path 28: Suction port 29: Discharge port 30: High pressure chamber 31: Thrust plate 32: Seal ring groove 33: Seal ring (seal member) 34: Thrust bearing 35: Retaining plate (support member) 36: Snap Ring (positioning member) 37: Orifice 38: Protrusion 39: Aki Multer piston 40: Cover 41: Return spring 42, 43: Oil seal 44: Needle bearing 45, 45a: O-ring 51: Housing 52: Cam surface 53: Rotary valve 54: Protrusion 56: High pressure chamber 57: Orifice 58: Seal ring Groove 59: Seal ring 60: Suction path 61: Suction port

Claims (1)

[Scope of utility model registration request] 1. A housing provided between relatively rotatable input / output shafts, connected to the one shaft, and having a cam surface having two or more ridges on an inner diameter surface thereof; and a housing connected to the other shaft. At the same time, it is stored rotatably in the housing,
A rotor shaft having a plurality of plunger chambers formed in the radial direction; reciprocally housed in each of the plurality of plunger chambers under the pressure of a return spring, and the cam when the two shafts relatively rotate. A plurality of plungers driven by surfaces; suction and discharge holes formed in the rotor shaft and communicating with the plunger chamber; slidably contacting the rotor shaft, and positioned in a predetermined relationship by the cam surface and a protrusion, A plurality of suction ports that act as suction valves and discharge valves depending on the positional relationship with the suction and discharge holes, a valve body having a discharge port formed on the surface, and a valve body provided on the valve body and communicating with the discharge port on the back surface of the valve body. A high pressure chamber that opens, a seal member provided around the high pressure chamber, a thrust bearing that presses the seal member, and a thrust bearing. A support member that supports the support member, a positioning member that positions the support member, the thrust bearing, and the valve body; and a flow resistance generation unit that is provided at the outlet of the high-pressure chamber and that generates flow resistance. Hydraulic power transmission coupling.