JP2011252559A - Hydraulic power transmission joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a temperature lock function and an initial torque-up function in the same unit.SOLUTION: The hydraulic power transmission joint includes an oil low-pressure chamber where a rotational speed difference is generated between an input shaft and an output shaft, a plurality of plunger chambers for supplying oil to an oil high-pressure path on the basis of an oil pressure difference generated according to the rotational speed difference, and an orifice 102 for controlling a flow speed of oil flowing through an oil path for circulating oil from the high-pressure path to the low-pressure chamber, and generates torque by fluid resistance of the orifice to transmit power in the hydraulic power transmission joint. The hydraulic power transmission joint further includes an initial pin 112 for opening/closing the orifice, a temperature lock mechanism part projected at a prescribed temperature to press the initial pin, thereby closing the orifice, and an initial torque-up mechanism part for pressing the initial pin till oil pressure at the orifice reaches prescribed pressure to close the orifice.

Description

The present invention is used for a hydraulic power transmission joint, and particularly when the oil temperature of the joint abnormally rises, the hydraulic pressure operates to stop the pump action so as not to raise the oil temperature, and can further increase the initial torque. The present invention relates to a hydraulic power transmission joint having a mechanism.

  A hydraulic power transmission joint used for vehicle front / rear wheel driving force distribution appropriately distributes driving force from a driving source such as an engine to front and rear wheels according to the traveling state of the vehicle. It is necessary to obtain a small torque according to the operating rotational speed of the front and rear wheels when the vehicle turns, and to transmit a large torque on bad roads and slopes.

  As a conventional hydraulic power transmission joint, for example, in Japanese Patent Application Laid-Open No. 2004-332858, when the oil in the hydraulic power transmission joint reaches a predetermined high temperature, the flow resistance is maximized by closing the oil passage. Discloses a lock structure that eliminates the differential between the input and output shafts. This is because when the high torque continues, the oil temperature rises, and when the temperature exceeds the specified temperature, a safety device is activated to reduce the differential between the input and output shafts by operating the oil lock mechanism to protect the joint. This is to prevent the climb.

  FIG. 7 shows a cross section of a drain mechanism of a hydraulic power transmission joint disclosed in Japanese Patent Application Laid-Open No. 2004-332858. FIG. 7A shows a state before the oil reaches the predetermined temperature, and FIG. 7B shows a state when the oil reaches the predetermined temperature.

  In FIG. 7A, the left end portion of the valve block 244 is provided with a concave portion 244a on the outside, and a hole is formed from the concave portion 244a toward the center, and the hole is further larger than the first storage chamber 202a. The second storage chamber 202b is formed in the middle so as to have a diameter. The right side of the first storage chamber 202a forms a restricting portion 204 constricted in a conical shape, and the right end of the restricting portion 204 communicates with the high-pressure passage 208 via a small-diameter orifice 206.

  In the first storage chamber 202a, a plunger 212 having a conical shape at the right end is inserted through a spring 214 and is urged to the left. A thermo switch 218 is mounted in the second storage chamber 202b with a spring 220 interposed therebetween and is biased to the right. A concave portion 212b is formed at the left end of the plunger 212, and the head pin 219 of the thermo switch 218 is in contact with the concave portion 212b. The left end of the spring 220 is in contact with a spring stopper 202 embedded in the valve block 244. Further, a drain passage 222 is formed in the first storage chamber 202a and communicates with the low pressure chamber.

  FIG. 7B shows a state where the thermo switch 218 is activated and the orifice 206 is closed when the oil temperature rises and reaches a predetermined temperature. In a hydraulic power transmission joint, the oil temperature rises due to sliding friction as the differential rotational speed of the front and rear wheels increases. When the temperature exceeds a predetermined temperature, the thermo switch 218 operates, the head pin 219 protrudes, and the plunger 212 is moved in the right direction. Therefore, the leading end portion 212a of the plunger 212 comes into contact with the restricting portion 204, and the orifice 206 is closed. As a result, the oil passage is cut off, the flow resistance is maximized, and the differential between the input and output shafts can be eliminated.

  FIG. 8 shows the relationship between the differential rotational speed ΔN and the torque ΔT when the lock mechanism in the hydraulic power transmission joint shown in FIG. 7 is used. As the differential rotational speed ΔN increases, the torque ΔT also increases. For example, when the differential rotational speed ΔN is continuously driven at N1, the thermo switch 218 is activated and reaches the orifice 206 when the predetermined temperature is reached. Is closed and the differential rotation speed ΔN becomes zero.

  For example, Japanese Patent Laid-Open No. 8-193627 discloses a hydraulic power transmission joint that can simultaneously obtain an auto-lock torque characteristic and an initial torque increase.

  FIG. 9 shows a cross section of the drain mechanism used in the hydraulic power transmission joint disclosed in Japanese Patent Laid-Open No. 8-193627.

  In FIG. 9, a discharge port 304 is formed in the rotary valve 302. Further, the rotary valve 302 is formed with a high-pressure chamber 306 communicating with the discharge port 304 through the through-hole 314. The high-pressure chamber 306 is provided with a collar member 315, and a plug 312 is screwed into the collar member 315. Yes. A storage chamber 310 that stores a ball-shaped valve body 308 is formed inside the collar member 315. The storage chamber 310 communicates with the through hole 314 and the discharge port 304 through an opening 318 formed in the rotary valve 302. A valve seat 320 is formed in the storage chamber 310, and when the flow rate of the communication hole 324 exceeds a predetermined value, the valve body 308 moves to the right in the figure due to the negative pressure caused by the flow and is seated on the valve seat 320. An opening 316 on the outlet side is formed following the valve seat 320, and an orifice 326 is formed on the rotary valve 302 following the opening 316.

  The communication hole 324 connects the storage chamber 310 of the collar member 315 and the storage hole 334 that stores the pin member 338 that holds the valve body 308. The pin member 338 is urged by a spring 342 as an elastic member to press and hold the valve body 308. In the gap between the communication hole 324 and the pin portion 322 of the pin member 338, an orifice 326 is formed as a flow resistance generating means. A step portion 332 having a larger diameter than the pin portion 322 is formed integrally with the pin portion 322, and a base end portion 336 having a larger diameter than the step portion 332 is formed integrally with the step portion 332.

  In the initial state, the hydraulic pressure that pushes the pin portion 322 of the pin member 338 in the right direction is smaller than the biasing force of the spring 342, so the orifice 326 is closed by the step portion 332 of the base end portion 336. When the hydraulic pressure increases and exceeds a predetermined value, the valve body 308 moves to the right and presses the pin member 338, and the pin member 338 moves to the right against the spring 342 and the orifice 326 is opened. Is done. When the oil pressure further rises and exceeds a predetermined value, the valve body 308 is seated on the valve seat 320 and closes the opening 316, thereby closing the orifice 326.

  Torque is not transmitted when there is no rotational difference between the front and rear wheels, but when there is a rotational difference, oil in the plunger chamber is pushed out to the discharge port 304. The oil pushed out to the discharge port 304 is pushed out from the drain hole 330 through the orifice 326. At this time, the orifice 326 is closed by the step 332 of the pin member 338 by the spring force of the spring 342 at the initial hydraulic pressure. When the hydraulic pressure further increases, the pin member 338 moves to the right, and the step portion 332 of the pin member 338 opens the orifice 326 to generate a rotation difference.

  When the hydraulic pressure in the storage chamber 310 further increases, the valve body 308 comes into contact with the valve seat 320 and blocks the flow of oil. This locks the torque.

FIG. 10 shows the relationship between the differential rotational speed ΔN and the torque ΔT in the hydraulic power transmission joint of FIG. In the initial state in which differential rotation occurs, when the initial torque T0 is greater than 0 and reaches a certain differential rotation speed N2, the torque ΔT is locked at Tm, and both initial torque up and auto-lock torque characteristics are obtained. The torque characteristics are obtained at the same time.

JP 2004-332858 A JP-A-8-193627

  However, in such a hydraulic power transmission joint, in the temperature lock mechanism in the drain mechanism part of the hydraulic power transmission joint disclosed in, for example, Japanese Patent Application Laid-Open No. 2004-332858, the torque characteristics are reduced due to auto-locking. However, there is a problem that the initial torque when the differential rotation occurs is low.

  Further, in the initial torque up mechanism in the drain mechanism portion of the hydraulic power transmission joint disclosed in, for example, Japanese Patent Laid-Open No. 8-193627, the initial torque when differential rotation occurs is high, but at the time of turning, etc. There is a problem that auto-locking may occur when auto-locking is unnecessary.

  Since the temperature lock mechanism and the initial torque increase mechanism provided in the hydraulic passage are both attached to the orifice of the hydraulic passage assembly portion, they cannot be attached at the same time, and the advantages of each mechanism cannot be satisfied at the same time. It was.

The present invention provides a hydraulic power transmission joint that constitutes a temperature lock mechanism and an initial torque-up mechanism in a single unit and is attached to an orifice of a hydraulic passage assembly to realize a temperature lock function and an initial torque-up function. With the goal.

The present invention relates to a hydraulic power transmission joint,
An opening / closing member that is provided in an oil passage generated by a difference in rotational speed between an input shaft and an output shaft capable of relative rotation, and that opens and closes the oil passage;
A temperature lock mechanism that closes the oil flow path by pressing the opening and closing member when a predetermined temperature is reached;
An initial torque-up mechanism that is provided adjacent to the temperature lock mechanism and closes the oil flow path by pressing the opening and closing member until the oil pressure in the oil flow path reaches a predetermined pressure;
It is provided with.

Here, the hydraulic power transmission joint is
A first storage chamber for storing the initial torque-up mechanism and a second storage chamber for storing the temperature lock mechanism;
The first storage chamber includes a temperature lock pin having an opening / closing member stopper, an initial pressure setting spring that biases the initial pin in the opposite direction of the oil flow path, an initial pin of the open / close member that closes the oil flow path, and an oil flow. A drain passage for draining oil flowing in from the road,
The second storage chamber has a temperature switch that operates by detecting the temperature of the oil, a temperature switch pin that protrudes by the operation of the temperature switch and moves the opening and closing member in the direction of the oil flow path, and a support portion that supports the temperature switch. A support portion support spring for pressing the support portion against the step portion of the second storage chamber and the first storage chamber, a spring stop portion for positioning and pressing the support portion support spring, a second storage chamber and a hydraulic type A storage chamber opening communicating with the low pressure chamber in the power transmission joint,
When it is detected that the oil is at a predetermined temperature and the temperature switch is activated, the oil flow path is closed by the initial pin of the opening / closing member.

The initial torque up mechanism is
In the initial torque-up mechanism, the initial pressure setting spring that urges the opening / closing member in the direction of the oil flow path is temperature-locked in order to close the oil flow path until the pressure of the oil flow path reaches a predetermined pressure. Prepare for the pins.

The temperature lock pin is provided with an opening / closing member guide and a means for discharging oil generated by the movement of the opening / closing member.

According to the present invention, since the drain mechanism in which the temperature lock mechanism and the initial torque-up mechanism are integrated in the same unit, the hydraulic power transmission joint prevents the oil temperature from increasing at the time of high differential rotation. In the initial stage when the dynamic rotational speed is generated, the initial torque-up mechanism can be configured in a small size. As a result, the degree of freedom in design is increased, and it can be manufactured at a low cost.

Sectional view of a hydraulic power transmission joint to which the present invention is applied The rear view of the rotor which attaches the drain mechanism part of the hydraulic power transmission coupling which applies this invention, and the front view of a valve Sectional view of initial state of drain mechanism according to the present invention Sectional view at the time of torque generation of the drain mechanism according to the present invention Sectional view at the time of temperature lock operation of the drain mechanism according to the present invention The figure which shows the relationship between differential rotation speed (DELTA) N and torque (DELTA) T of the hydraulic type power transmission coupling which attached the drain mechanism part by this invention. Sectional view of a conventional temperature lock mechanism The figure which shows the relationship between the differential rotation speed and torque of the hydraulic power transmission coupling provided with the conventional temperature lock mechanism. Sectional view of a conventional initial torque-up mechanism The figure which shows the relationship between the differential rotation speed and torque of the hydraulic power transmission coupling provided with the conventional initial torque-up mechanism.

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall cross-sectional view of a hydraulic power transmission joint 10 to which the present invention is applied. In FIG. 1, the cam ring 12 has a cam surface 14 having two or more peaks. The cam ring 12 functions as a cam by the cam surface 14. The rotor 16 is housed rotatably in the cam housing 18. The rotor 16 is engaged with the main shaft 20 and rotates integrally with the main shaft 20. A drive pinion gear (not shown) is inserted and fixed in the main shaft 20, and the main shaft 20 rotates integrally with the drive pinion gear 22.

  A plurality of plunger chambers 24 are formed in the rotor 16 in the axial direction, and a plurality of plungers 26 are slidably accommodated in the plunger chamber 24 via return springs 28. A suction path 30 is formed on the head side of the plunger 26, and the suction path 30 communicates with the low pressure chamber 32. The suction passage 30 and the plunger chamber 24 communicate with each other through a communication hole 34, and the communication hole 34 is opened and closed by a suction one-way valve 36 made of a ball.

  A valve seat 38 is formed inside the plunger chamber 24, and a suction one-way valve 36 is seated on the valve seat 38. A check plug 40 is provided at the stepped portion of the valve seat 38, and a check spring 41 for pressing and positioning the suction one-way valve 36 is interposed between the check plug 40 and the suction one-way valve 36. Yes.

  A return spring 28 is interposed between the check plug 40 and the bottom of the rotor 16. A discharge hole 42 is formed in the rotor 16, and the discharge hole 42 communicates with the plunger chamber 24. A discharge one-way valve 44 made of a ball is provided in the discharge hole 42. That is, the valve seat 46 is formed in the discharge hole 42, and the discharge one-way valve 44 is seated on the valve seat 46.

  A high pressure passage 50 communicating with the discharge hole 42 of the rotor 16 is formed in the valve 48. A regulating member 52 projects from the high-pressure passage 50 and is provided on the valve 48. The regulating member 52 positions the discharge one-way valve 44 at a predetermined position. The valve 48 has an orifice 102 from the high-pressure passage 50 through a high-pressure chamber 88, and a drain mechanism is disposed.

  When the plunger 26 is in the suction process, the suction one-way valve 36 provided at the head of the plunger 26 is opened, and oil is sucked into the plunger chamber 24 through the low pressure chamber 32, the suction path 30, and the communication hole 34. At this time, the discharge one-way valve 44 provided in the discharge hole 42 of the rotor 16 is closed to prevent the backflow of oil from the high-pressure passage 50.

  When the plunger 26 is in the discharge process, the discharge one-way valve 44 is opened, and the oil in the plunger chamber 24 passes through the discharge hole 42, the high-pressure passage 50, the high-pressure chamber 88, the orifice 102, and the drain mechanism, and then drains. It flows into the low pressure chamber 32 through the port 54 and the drain passage 56. At this time, the one-way valve for suction 36 is closed to prevent the oil from leaking from the communication hole 34 and the suction path 30 to the low-pressure chamber 32.

  A bearing retainer portion 58 is provided in the cam housing 18, and the bearing retainer portion 58 and the cam housing 18 rotate integrally. The bearing retainer portion 58 is formed with a through hole 60, and the through hole 60 communicates with the low pressure chamber 32. Needle bearings 62 and 64 are interposed between the bearing retainer portion 58 and the valve 48, and between the bearing retainer portion 58 and the main shaft 20, and between the bearing retainer portion 58 and the main shaft 20, oil is provided. A seal 66 is provided, and the oil seal 66 prevents oil from flowing out.

  An accumulator piston 68 for absorbing thermal expansion and contraction of oil is slidably provided outside the bearing retainer portion 58, and an accumulator chamber 70 is formed by the accumulator piston 68. The accumulator chamber 70 communicates with the low pressure chamber 32 through the through hole 60 of the bearing retainer portion 58.

  O-rings 71 and 72 for preventing oil leakage are interposed between the accumulator piston 68 and the cam housing 18 and between the accumulator piston 68 and the bearing retainer 58, respectively. The outer peripheral end of the accumulator retainer 74 is fixed to the cam housing 18. A return spring 76 is interposed between the accumulator retainer 74 and the bottom of the accumulator piston 68.

  The cam ring 12 is formed in a concave R surface on the cam surface 14. The cam ring 12 and the plunger 26 have a concave R surface and a concave spherical shape, respectively, and a ball 78 is inserted between the cam ring 12 and the plunger 26, and the sliding portion of the cam ring 12 and the plunger 26 at the torque generation site has a three-dimensional curved surface shape. .

  FIG. 2 is a view for explaining a coupling portion between the rotor 16 and the valve 48. FIG. 2A is a rear view of the rotor 16 as viewed from the valve 48 side. FIG. 2B is a front view of the valve 48 coupled to the rotor 16 as viewed from the rotor side. FIG. 2 shows a case where there are nine plunger chambers 24. The rotor 16 and the valve 48 are positioned and fixed through the pin 80 in the pin hole 82.

  The high-pressure path 50 is made common by forming a high-pressure chamber groove 84 in the shape of a groove in the valve 48 of the discharge port 42 from each plunger chamber 24. The high pressure chamber groove 84 is provided with a high pressure passage port 86 and a high pressure chamber 88 through which oil flows into the drain mechanism. Further, a drain passage 56 for discharging the oil of the drain mechanism portion to the low pressure chamber 32 is provided. The oil circulates from the low pressure chamber 32 through the plunger chamber 24, the high pressure passage 50, the high pressure passage port 86, and the high pressure chamber 88 and again flows through the drain mechanism portion to the low pressure chamber 32. The flow of oil is controlled by a drain mechanism housed in the valve 48 part.

  3 to 5 are cross-sectional views showing a drain mechanism 100 according to the present invention. FIG. 3 shows a drain mechanism in an initial state in which the hydraulic input / output shaft does not generate operational rotation in the hydraulic power transmission joint. FIG. 4 shows a state of the drain mechanism in the case where the operation rotation is generated and the torque is generated according to the operation rotation speed. FIG. 5 shows the state of the drain mechanism when the temperature of the oil is increased by operating rotation and the temperature lock is activated.

  In FIG. 3, an orifice 102 is provided in the high-pressure chamber 88 that communicates with the high-pressure passage 50 in the bubble 48. Following the orifice 102, a first storage chamber 104 and a second storage chamber 106 having a larger diameter than the first storage chamber 104 are provided. The second storage chamber 106 is provided with a storage chamber port 108 a in the storage chamber block 108 and communicates with the low pressure chamber 32. The initial pin stopper 119 may have the same structure as the temperature lock pin 116.

  The right side of the first storage chamber 104 forms a restricting portion 110 constricted in a conical shape, and the right end of the restricting portion 110 is a small-diameter orifice 102. The first storage chamber 104 is provided with an initial pin 112 whose right end tip is conical, an initial pressure setting spring 114, a temperature lock pin 116, and an initial pin stopper 119. The initial pin 112 is disposed so as to penetrate the center portion of the temperature lock pin 116 and is slidable between the initial pin stopper 119 provided on the temperature lock pin 116 and the restricting portion 110.

  Furthermore, the initial pin 112 includes an initial pressure setting spring 114 so as to press the head portion 112a against the restricting portion 110 with a predetermined pressure using the temperature lock pin 116 as a base. Further, the first storage chamber 104 has a temperature switch return spring 117, and urges the temperature lock pin 116 toward the second storage chamber 106 side. Further, a drain passage 56 is formed in the first storage chamber 104 and communicates with the low pressure chamber 32.

  The second storage chamber 106 includes a temperature switch 115, a temperature switch pin 118 that protrudes when the temperature switch 115 is activated, a support 120 that supports the temperature switch 115, a temperature switch support spring 122, and a spring stopper. A recess 128 through which the pin 127 penetrates and a storage chamber port 108 a provided in the second storage chamber 106 and communicating with the low pressure chamber 32 are provided.

  The support portion 120 in the second storage chamber 106 is integral with the temperature switch 115, and is urged toward the first storage chamber 104 by the support portion support spring 124 to support the temperature switch 115. The left side of the support portion support spring 124 abuts on a spring stopper 126, and the spring stopper 126 is positioned by a spring stopper pin 127.

  The temperature switch 115 is provided with a temperature switch pin 118 and is biased toward the first storage chamber 104 by temperature switch support springs 122 and 124. The temperature lock pin 116 is in contact with the support portion 120 and performs initial positioning of the temperature lock pin 116.

  The temperature detection of the temperature switch detects the oil temperature of the low-pressure chamber 32 flowing from the storage chamber port 108a.

  In the initial state, the differential rotation between the input and output shafts does not occur, and the pressure difference ΔP between the low pressure chamber 32 and the high pressure chamber 88 is smaller than the spring pressure set by the initial pressure setting spring 114. As described above, the leading end 112 a of the initial pin 112 is in contact with the restricting portion 110 and closes the orifice 102. For this reason, the oil from the high pressure chamber 88 does not flow into the low pressure chamber 32, and the hydraulic pressure difference ΔP increases to obtain an initial torque increase.

  The initial torque can be adjusted by changing the spring load of the initial pressure setting spring 114.

  Further, when the hydraulic pressure difference ΔP becomes larger and the hydraulic pressure difference ΔP becomes larger than the spring pressure set by the initial pressure setting spring 114, the initial pin 112 is fixed to the initial pin against the spring pressure of the initial pressure setting spring 114. The head portion 112a moves away from the restricting portion 110 and opens the orifice 102.

  FIG. 4 is a diagram showing a state where the hydraulic pressure difference ΔP is larger than the spring pressure set by the initial pressure setting spring 114 and the orifice 102 is opened. Oil from the high pressure chamber 88 flows through the high pressure passage 50 and the high pressure chamber 88, passes through the orifice 102, and flows into the low pressure chamber 32 through the drain passage 56. At this time, since the diameter of the orifice 102 is small, flow resistance is generated when oil flows. When the differential rotation speed ΔN is small, the flow rate of oil is low and the flow resistance is small. However, when the differential rotation speed ΔN increases and the oil flow rate increases, the flow resistance at the orifice 102 increases. For this reason, torque proportional to the square of the differential rotation speed ΔN is transmitted.

  As the differential rotational speed ΔN increases, the oil temperature of the cam surface 14 and the plunger 26 shown in FIG. When the oil temperature becomes equal to or higher than the predetermined temperature, the temperature switch 115 is activated, the temperature switch pin 118 protrudes, pushes the initial pin stop 119, and moves the temperature lock pin 116 and the initial pin 112 toward the orifice 102.

  FIG. 5 shows the drain mechanism 100 when the temperature switch 115 is activated. When the temperature switch pin 118 protrudes, the initial pin stopper 119 provided on the temperature lock pin 116 is pushed toward the orifice 102 against the spring pressure of the temperature switch return spring 117. Since the initial pin stopper 119 is fixed to the temperature lock pin 116, the temperature lock pin 116 moves toward the orifice 102.

  At this time, the initial pin 112 that is in contact with the initial pin stop 119 is also pushed by the initial pin stop 119 and moves toward the orifice 102, and the leading end 112 a of the initial pin 112 contacts the restricting portion 110, so that the orifice 102 is closed.

  As a result, the flow of oil from the high pressure chamber 88 to the low pressure chamber 32 is blocked, and the oil in the plunger chamber 24 in FIG. 1 does not flow out through the discharge hole 42, so that the movement of the plunger 26 is restricted and the ball 78 is restricted. And remains pressed against the cam surface 14. In this state, the rotation of the cam housing 18 is transmitted to the drive pinion gear 22 as it is, so that the plunger 26 and the cam surface 14 do not rotate the ball 78 and do not generate frictional heat. There is no rise.

  FIG. 6 is a diagram showing the differential rotational speed ΔN and torque ΔT between the input and output shafts of the hydraulic power transmission joint 10 to which the drain mechanism 100 of the present invention is applied. The horizontal axis represents the differential rotational speed ΔN, and the vertical axis represents the torque ΔT. When the hydraulic power transmission joint 10 is in the initial state, the orifice 102 of the drain mechanism 100 is closed by the leading end 112a of the initial pin 112, so that the initial torque is increased to T0.

  When the hydraulic pressure difference ΔP increases and the initial pin 112 moves against the initial pressure setting spring 114, the orifice 102 is opened, and the oil flows from the high pressure passage 50 through the high pressure chamber 88 into the first storage chamber 104. Torque is generated by the fluid resistance at the orifice 102, and the operating rotational speed ΔN increases and the torque ΔT increases according to the curve a in FIG.

  When the temperature of the oil reaches a predetermined temperature (explained in FIG. 6 assuming that the differential rotation speed ΔN is N1), the temperature switch 116 is activated to close the orifice 102, so that the oil flow is interrupted. As shown by a curve b2 in FIG.

  A curve c in FIG. 6 shows the relationship between the differential rotational speed ΔN and the torque ΔT when the drain mechanism of the present invention is not applied. As is apparent from comparison with the curve c, when the drain mechanism according to the present invention is applied, an initial torque-up function and a torque temperature lock function can be obtained even with a single drain mechanism.

Although the hydraulic power transmission joint to which the drain mechanism according to the present invention is applied has been described above, the present invention includes appropriate modifications that do not impair the object and advantages thereof, and is further limited by the numerical values shown in the above embodiments. Will not receive.

10: Hydraulic power transmission joint 12: Cam ring 14: Cam surface 16: Rotor 18: Cam housing 20: Main shaft 22: Drive pinion gear 24: Plunger chamber 26: Plunger 28: Return spring 30: Suction passage 32: Low pressure chamber 34 : Communication hole 36: One-way valve for suction 38: Valve seat 40: Check plug 42: Discharge hole 44: One-way valve for discharge 46: Valve seat 48: Valve 50: High-pressure passage 52: Restricting member 54: Drain port 56: Drain passage 58: Bearing retainer 60: Through hole 62, 64: Needle bearing 66: Oil seal 68: Accumulator piston 70: Accumulator chamber 71, 72: O-ring 74: Accumulator retainer 76: Return spring 78: Ball 80: Pin 82: Pin hole 84: groove for high-pressure road 86: high Road port 88: High-pressure chamber 100: Drain mechanism 102: Orifice 104: First storage chamber 106: Second storage chamber 108: Storage chamber port 110: Restriction portion 112: Initial pin 112a: Lead portion 114: Initial pressure setting spring 115 : Temperature switch 118: Temperature switch pin 120: Support part 122: Temperature switch support spring 124: Support part support spring 126: Spring stop

Claims (4)

An opening / closing member that is provided in an oil passage generated by a difference in rotational speed between an input shaft and an output shaft capable of relative rotation, and that opens and closes the oil passage;
A temperature locking mechanism that closes the oil passage by pressing the opening and closing member when a predetermined temperature is reached;
An initial torque-up mechanism that is provided adjacent to the temperature lock mechanism and closes the oil flow path by pressing the opening and closing member until the oil pressure in the oil flow path reaches a predetermined pressure;
A hydraulic power transmission joint characterized by comprising:
In the hydraulic power transmission joint according to claim 1,
A first storage chamber for storing the initial torque-up mechanism, and a second storage chamber for storing the temperature lock mechanism;
The first storage chamber includes a temperature lock pin having an opening / closing member stopper, a temperature switch return spring that biases the temperature lock pin in the direction of the oil passage, an opening / closing member that closes the oil passage, A drain passage for discharging oil flowing in from the oil flow path,
The second storage chamber includes a temperature switch that operates by detecting the temperature of oil, a temperature lock pin that protrudes by the operation of the temperature switch, and moves the opening / closing member in the direction of the oil flow path, and the temperature switch. A support portion for supporting, a support portion support spring for pressing the support portion against the step portion of the second storage chamber and the first storage chamber, and a spring stop portion for positioning and pressing the support portion support spring. A storage chamber opening communicating with the second storage chamber and the low pressure chamber in the hydraulic power transmission joint,
Closing the oil flow path with the opening and closing member when the temperature switch is activated by detecting that the oil has a predetermined temperature,
Hydraulic power transmission joint characterized by
The hydraulic power transmission joint according to claim 1 or 2,
The initial torque up mechanism is
An initial for biasing the opening / closing member in a direction opposite to the oil flow path in order to close the oil flow path until the pressure of the oil flow path reaches a predetermined pressure in the temperature lock mechanism. Having a pressure setting spring on the temperature lock pin;
Hydraulic power transmission joint characterized by
The hydraulic power transmission joint according to claim 1 or 2,
A hydraulic power transmission joint, wherein the temperature lock pin is formed with an opening / closing member guide and a means for discharging oil generated by the movement of the opening / closing member.

Images