JP2815736B2 - Hydraulic power transmission coupling - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic power transmission coupling applied to driving force distribution of an automobile.

[0002]

2. Description of the Related Art Conventionally, as such a hydraulic power transmission coupling, for example, Japanese Patent Application No. 1-154228 (Japanese Unexamined Patent Application Publication No.
-56720). The hydraulic power transmission joint is provided with a hydraulic pump driven by a rotational speed difference between a relatively rotatable first rotary member and a large rotary member, and a hydraulic pump having a discharge passage in response to an external control signal. Flow resistance control means for generating flow resistance,
An electromagnetic actuator that acts on a central portion of the first or second rotating member in an axial direction of the first or second rotating member by controlling a transmission torque between the first and second rotating members by an external control signal. By directly operating the flow resistance control means by this electromagnetic actuator,
The torque transmission characteristic between the first and second rotating members is controlled.

[0003] Here, the electromagnetic actuator comprises a magnetic frame fixed to a non-rotating third member, a solenoid coil integrally housed in the magnetic frame, and a magnetic field when a current is supplied to the solenoid coil. A movable magnetic body that generates a magnetic attractive force between the frame and the movable magnetic body,
The joint is covered with a cover made of a non-magnetic material which keeps the oil tight in the joint and is kept out of contact with the magnetic frame.

[0004]

However, FIG.
As shown in (1), in general, an electromagnetic actuator using direct current has a characteristic that when an air gap length in a magnetic path changes, a magnetic attraction force changes even when a current having the same current value is supplied. Further, in a mechanical structure such as a transfer, the positional relationship between the components becomes worse in the axial direction than in the radial direction due to the stacking of many components in the axial direction and the difference in thermal expansion due to the material.

In a conventional hydraulic power transmission joint, a magnetic circuit constituting a magnetic actuator is formed independently of a joint main body, and a magnetic attraction force acts directly between a movable magnetic body and a magnetic frame. It has become. Therefore, when such a conventional hydraulic power transmission joint is incorporated in the transfer or the like, the axial positional relationship between the magnetic frame fixed to the case side of the transfer and the movable magnetic body in the joint body is determined. Even if a current of the same current value is supplied to the solenoid coil without stability, the magnetic attractive force acting on the movable magnetic body is not stable, so that it cannot be applied to continuous variable control or the like that requires control accuracy. was there.

In the conventional hydraulic power transmission coupling, since a non-magnetic cover is interposed between the magnetic frame and the movable magnetic body, at least an air gap between the movable magnetic body and the magnetic frame is provided. The gap is separated by the thickness of the cover made of the non-magnetic material, and the magnetoresistance increases, so that the magnetomotive force required to drive the movable magnetic material also increases.

In addition, when the facing area of the air gap is increased in order to reduce the magnetic resistance, there is a problem that the length of the actuator portion becomes longer. The present invention has been made in view of such conventional problems, and has as its object to provide a hydraulic power transmission coupling that does not have the above-described problems by improving the structure of an electromagnetic actuator. I do.

[0008]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention is provided on first and second rotating shafts which can rotate relative to each other, and the differential between the first and second rotating shafts is provided. A hydraulic pump driven by rotation, a control valve for controlling pressure oil of the hydraulic pump, and an actuator for operating the control valve by an external signal; and a rotational speed of the first and second rotating shafts. In a hydraulic power transmission coupling for transmitting a torque corresponding to a difference and a control signal from the outside, a third non-rotating
Been a member fixed, is held in coaxially and non-contact state and the joint is magnetically coupled through the radial gap between the movable magnetic body constituting the actuator be in the hands該継A magnetic frame, a solenoid coil provided integrally with the magnetic frame, and a housing and a rotary valve which are made of a magnetic material and form a magnetic path together with the magnetic frame.
That the joint component, with is movably accommodated in the axial direction in the joint, are magnetically coupled via an axial gap between said joint component, wherein when a current is passed to the solenoid coil A movable magnetic body that controls the control valve by generating a magnetic attraction force in the axial direction between the joint constituent members, and a short circuit of a magnetic circuit in the joint provided between the movable magnetic body and the magnetic frame. And a non-magnetic cover that becomes a part of a container that keeps the oil tight is provided, and the control valve is controlled electrically and mechanically from outside the joint without contact.

Further, of the magnetic poles of the north pole and the south pole of the magnetic frame,
At least one magnetic pole is the in the radial direction gap portion
The magnetic circuit is formed without interposing a cover .

[0010]

According to the hydraulic power transmission joint of the present invention having such a configuration, the joint constituting member is made a part of a magnetic circuit,
A magnetic attraction force is directly generated between the joint constituting member and the movable magnetic body. Further, the magnetic coupling between the magnetic frame fixed to the non-rotating third member and the magnetic circuit in the joint has a dimension. It is performed through a radial gap with excellent stability, so even if the axial positional relationship between the joint and the magnetic frame slightly fluctuates, it is possible to suppress the fluctuation of the magnetic attractive force acting on the movable magnetic body. Delicate control can be performed by the current flowing through the solenoid coil.

Therefore, not only discontinuous switching control such as ON / OFF control, but also continuous variable control optimal for the vehicle can be performed. Further, since the magnetic frame has a structure that covers the joint body and the radial gap is formed in the joint outer diameter, the length of the joint can be reduced. Further, at least one of the magnetic poles of the N pole and the S pole of the magnetic frame forms a magnetic circuit without interposing a non-magnetic member in the radial gap portion. Thus, the size of the solenoid coil can be reduced, and the cost can be reduced. Further, power consumption can be reduced.

[0012]

An embodiment of the present invention will be described below with reference to the drawings. In FIG. 1 showing the overall structure, reference numeral 2 denotes an input shaft to which a driving force is input, and 4 denotes a housing made of a magnetic material rotatably supported on the input shaft 2 via a bearing 6. Spline joint 8 formed in
Is connected to an output shaft (not shown).

An accumulator piston 10 which is slidable concentrically with the center axis Q is accommodated in a piston chamber formed on the spline joint 8 side of the housing 4, and is interposed by a retainer 12 fixed inside the housing 4. The return chamber 14 is urged leftward by a mounted return spring 14, and the piston chamber is sealed by an oil seal 16 and an O-ring 17.

Reference numeral 18 denotes a thrust needle 2
0, and the cam surface 2 of the cam 18
2, a plurality of cam ridges and cam valleys are alternately formed one by one as shown in FIG. Also, on the outer periphery of the cam 18,
The projections 18a are provided at predetermined intervals, and the same number of positioning projections 4a are provided inside the housing 4, and the cams 18 are formed within an angle θ at which these projections 18a do not abut.
Is rotatable.

Here, the angle θ at which the cam 18 can rotate with respect to the housing 4 is set to θ ≒ π / Nc, where Nc is the number of cam ridges of the cam 18. In this embodiment, the number Nc of the cam peaks and the cam valleys is set to five. Reference numeral 24 denotes a rotor spline-fitted to the input shaft 2, and a plurality of plunger chambers 26 are formed along the circumferential direction. The number of plunger chambers 26 is determined by a predetermined relationship based on the number Nc of cam ridges provided on the cam surface 22 of the cam 18. In this embodiment, nine plungers are provided for five cam lobes. Chambers 26 are formed at equal intervals.

A plunger 28 is accommodated in each plunger chamber 26 via a return spring 30 so as to be able to move forward and backward, and a suction / discharge hole 32 is formed at the bottom of each plunger chamber 26. Reference numeral 34 denotes a rotary valve, which is integrally fixed to the inner wall of the housing 4 to rotate integrally therewith, and to rotate the input shaft 2 via a ball bearing 36.
Are supported so as to be relatively rotatable with respect to

On the surface of the rotary valve 34 facing the rotor 24, five suction ports 38 and five discharge ports 40 are provided.
Are formed alternately at equal intervals, and the suction port 38 is further formed with a suction passage 42 communicating with an oil supply portion 44 outside the rotor 24. The discharge port 40 is not shown in FIG. 1 for explanation because it is located at a location that cannot be represented in the vertical cross-sectional view of FIG. 1. However, as shown in FIG. The low pressure suction passage 42 and the oil supply unit 44 do not communicate with each other, but communicate with a high pressure chamber 46 to be described later via a discharge passage 45. That is, the suction port 38 is provided for supplying oil from the low-pressure suction passage 42 to the suction / discharge hole 32 of the rotor 24 that is in the suction stroke, and the discharge port 40 is connected to the suction / discharge hole 32 of the rotor 24 that is in the discharge stroke. It is provided to supply the discharged pressure oil to a high-pressure chamber 46 described later via a discharge path 45.

Next, the relative relationship among the cam 18, the rotor 24, the plunger 28 and the rotary valve 34 will be described with reference to FIGS.
It will be described in detail together with. First, in FIG. 4, a cam 18 is mounted inside the housing 4, and a plurality of projections 4a, 18a provided respectively allow relative rotation within a predetermined angle θ range. As described above, since the cam surface 22 of the cam 18 is formed with five cam ridges and cam valleys, the angle β formed between the uppermost point of each cam ridge and the lowermost point of the cam valley is 36. °. Further, the nine plungers 28 facing the cam surface are positioned at 40 ° intervals, as shown by the dashed-dotted circle in FIG.

As shown in FIG. 5, a rotary valve 34 is provided with five suction ports 3 on a surface facing the rotor 24.
8 and the discharge port 40 are provided alternately, so that the angle γ formed by the suction port 38 and the discharge port 40 is 36 °. Further, the plunger 28 and the suction / discharge hole 32 face the rotor 24 in opposition to the suction port 38 and the discharge port 40, as shown by a dashed line circle.

When the rotor 24 rotates relative to the housing 4 and the rotary valve 34 in the direction of arrow D in FIG. 4, the cam 18 rotates together with the rotor 24,
When the projection 4a of the housing 4 comes into contact with the projection 18a of the cam 18, the relative rotation stops, and the cam surface 22
The plunger 28, which operates from the cam valley to the cam valley, operates in the discharge stroke to discharge the pressure oil in the plunger chamber 26 from the suction / discharge hole 32, while the plunger operates from the cam valley to the cam valley. Reference numeral 28 indicates the operation of the suction stroke, and sucks oil into the plunger chamber 26. Further, the same suction / discharge process is performed even when the rotation is performed in the direction opposite to the arrow D.

A plurality of notches 34 a of the rotary valve 34 shown in FIG. 5 are provided for fitting and fixing to the inner wall of the housing 4. The vertical sectional view of FIG.
3 shows a cross section of the entire joint in a positional relationship along the line α-α, and a partial longitudinal sectional view of FIG. 3 shows a cross section of the positional relationship between the discharge port 40 and the plunger 28 where the discharge process is performed in FIG. For example, a portion indicated by a two-dot chain line δ in the drawing) is shown.

Referring again to FIG. 1, the structure of the rotary valve 34 is formed with a high-pressure chamber 46 communicating with all the discharge ports 40 (see FIG. 3).
6, a first spool hole 47 penetrating in a direction parallel to the central axis Q is formed.
A first spool 48 is inserted therein so as to be able to advance and retreat.
Further, the suction passage 42 is provided at a location different from the first spool hole 47.
A communication hole 52 is formed which communicates with the communication shaft and penetrates to the left end of the rotary valve 34.

The rotary valve 34 has a high-pressure chamber 4
A second spool hole 49 is formed to communicate with the other end of the second spool 6 and penetrate in a direction parallel to the central axis Q. A second spool 50 is inserted into the second spool hole 49 so as to be able to advance and retreat. . An orifice 54 is formed between one end of the second spool hole 49 and the suction passage 42. Reference numeral 56 denotes a cap-shaped cover made of a non-magnetic material, which is fixed to one end of the housing 4 with a retaining ring 58 and is sealed from the input shaft 2.

Reference numeral 60 denotes a movable magnetic body made of a ferromagnetic material, and has a first spool 48 and a second spool 50 at one end.
Is stuck. Reference numeral 62 denotes a cup-shaped positioning member made of a non-magnetic material, one end of which is loosely fitted to the movable magnetic material 60. Reference numeral 64 denotes a first spring interposed between one end of the movable magnetic body 60 and the end face of the rotary valve 34, and acts so as to separate the movable magnetic body 60 from the rotary valve 34.

Reference numeral 66 denotes a second spring interposed between one end of the movable magnetic body 60 and the positioning member 62, and acts in a direction to increase the distance between the movable magnetic body 60 and the positioning member 62. Furthermore, the structure of the movable magnetic body 60 and the positioning member 62 will be described with reference to FIG. 6. A large-diameter hole into which the input shaft 2 is inserted is formed at each bottom end. A locking groove 60a into which the locking projection 62a of the positioning member 62 is loosely fitted from the inside is formed.

A first spring 64 is disposed between the outside of the positioning member 62 and the inside of the movable magnetic body 60, and the first spring 64 acts to separate the movable magnetic body 60 and the rotary valve 34. . Since the second spring 66 is interposed between the inside of the bottom end 62b of the positioning member 62 and the inside of the movable magnetic body 60, it acts so as to widen the mutual gap only between the movable magnetic body 60 and the positioning member 62. .

Referring again to FIG. 1, reference numeral 68 denotes a magnetic frame made of a magnetic material constituting a magnetic solenoid, 70 denotes a solenoid coil mounted on the magnetic frame 68, and the magnetic frame 68 faces the outer end of the housing 4. The solenoid coil 70 is formed in a cylindrical shape having a portion 68a fitted from the outside and a portion 68b opposed to the movable magnetic body 60.
The magnetic frame 68 is concentrically mounted on the magnetic frame 68.

As shown in detail in FIG. 3, one end 68a of the magnetic frame 68 is not in contact with the outer end surface of the housing 4 via a relatively narrow air gap X.
The distance between the other end 68b of the magnetic frame 68 and the movable magnetic body 60 is made as small as possible, and the space between the other end 68b and the cover 56 is not in contact with the narrow air gap Y. Further, an air gap Z is provided in which the distance between the movable magnetic body 60 and the rotary valve 34 is L2 when the movable magnetic body 60 is moved to the leftmost position by the first spring 64. When a current is supplied to the solenoid coil 70, the end portions 68a and 68b of the magnetic frame 68, the movable magnetic body 60, the rotary valve 34, the housing 4, and the respective air gaps X and Y as shown by the dotted lines in FIG. , Z are formed, and the movable magnetic body 34 is controlled to move toward the rotary valve 34 by a magnetic force generated according to the amount of current at that time.

In this embodiment, when no current is supplied to the solenoid coil 70 (hereinafter, referred to as a first control mode).
By supplying the first control current having the current value I1, the magnetic force F1 generated by the magnetic path generated between the magnetic frame 68, the movable magnetic body 60, the rotary valve 34, and the housing 4,
The movable magnetic body 60 is opposed to the spring force of the first spring 64.
Is moved by a fixed distance (hereinafter, referred to as a second control mode), the second control mode of the current value I2 (where I2> I1)
Is supplied, the magnetic force F2 (where F2> F1) is generated by the magnetic path generated between the magnetic frame 68, the movable magnetic body 60, the rotary valve 34, and the housing 4.
Against the spring force of the first and second springs 64, 66,
When moving the movable magnetic body 60 by a certain distance (hereinafter, referred to as
A control mode for performing three types of position settings (hereinafter referred to as a third control mode) is set. In order to obtain these three types of control modes, the magnetic forces F1 and F2 by the control current in each control mode and the first mode are set. , Second springs 64, 6
As shown in FIG. 7, the relationship between the spring forces f1 and f2 of FIG.
Is set.

That is, in the first control mode in which no current flows through the solenoid coil 70, the movable magnetic body 60 is moved to the leftmost position by the first spring 64.
The amount of displacement of the movable magnetic body 60 is less than a fixed gap L1 provided between the bottom end 62b of the positioning member 62 and the end face of the rotary valve 34, and a normal torque transmission characteristic described later is obtained.

Next, in the second control mode, the spring force f1 of the first spring 64 and the spring force f1 of the second spring 66 are larger than the spring force f1 of the first spring 64.
Magnetic force F1 (ie, f1) smaller than the sum f1 + f2
1 <F1 <f1 + f2)
Is supplied. Thereby, the displacement amount L of the movable magnetic body 60 is in the range of L1 <L <L2, and the free characteristic described later is obtained.

In the third control mode, the spring force f1 of the first spring 64 and the spring force f2 of the second spring 66
And the magnetic force F2 (ie, f1 + f2 <F2) that is larger than the sum f1 + f2 and smaller than the magnetic force F3 within a certain safe range.
A second control current having a current value I2 for generating <F3) is supplied. Thus, the movable amount L of the movable magnetic body 60 is in the range of L2 <L <L3, and the lock characteristic described later is obtained.

As shown in FIG. 3, L1 is the movable stroke of the positioning member 62, that is, the bottom end 62b of the positioning member 62 and the rotary valve 34 when the movable magnetic body 60 moves to the leftmost position. L2 is a movable stroke of the movable magnetic body 60, that is, a gap between the movable magnetic body 60 and the end of the rotary valve 34 when the movable magnetic body 60 is moved to the leftmost position. is there.

Next, the operation of the embodiment having such a structure will be described. First, when the first control mode in which no current is supplied to the solenoid coil 70 is set, the movable magnetic body 60 is not affected by the electromagnetic solenoid as shown in FIG.
And is stopped by the leftmost spring 64. As a result, the first spool 48 closes the connection between the high-pressure chamber 46 and the communication hole 52, while the second spool 50 brings the high-pressure chamber 46 and the orifice 54 into communication.

The positional relationship between the cam 18, the rotor 24 and the rotary valve 34 in the first control mode is as shown in a sectional view of FIG. Then, when a rotational speed difference occurs between the cam 18 and the rotor 24, when a certain plunger 28 is in a suction stroke (in a case indicated by an upper arrow).
Is a positional relationship in which the suction port 38 of the rotary valve 34 and the suction / discharge hole 32 of the plunger chamber 26 communicate with each other. When in the stroke (indicated by a downward arrow), the relationship is opposite to that of the suction stroke, and the stroke leads to the plunger chamber 26 formed in the rotor 24. Such a suction stroke and a discharge stroke of the plunger 28 correspond to nine plungers 28 in FIG.
And the discharge side and the suction side communicate with each other through the orifice 54 of the rotary valve 34, so that a pressure corresponding to the flow resistance of the orifice 54 is generated on the discharge side. A torque transmission having characteristics such as a characteristic curve A of FIG. 12 is performed. The torque transmission characteristic A is adjusted according to the inner diameter of the orifice 54.

When a second control mode for supplying the first control current I1 to the solenoid coil 70 is set, a magnetic path is formed between the magnetic frame 68, the movable magnetic body 60, the rotary valve 34 and the housing 4, As shown in FIG.
The movable magnetic body 60 moves to the right by the magnetic force F1 corresponding to the first control current I1, and the bottom end 6 of the positioning member 62
2b stops at the position where it contacts the rotary valve 34.
At the same time, the first spool 48 also moves to the right by the amount that the gap between the bottom end 62b of the positioning member 62 and the rotary valve 34 disappears. As a result, the high pressure chamber 46 and the communication hole 52
The gap is opened, and the pressure oil in the high-pressure chamber 46 falls to the low-pressure suction path 42 side irrespective of the position of the second spool 50. Therefore, a so-called free state as shown by a characteristic curve B in FIG. 12 is obtained, and transmission torque cannot be obtained.

When a third control mode for supplying the second control current I2 to the solenoid coil 70 is set, FIG.
As shown in FIG. 1, the magnetic path corresponding to the control current I2 is
8, a magnetic force F2 generated between the movable magnetic body 60, the rotary valve 34 and the housing 4 (where F2> F
According to 1), the movable magnetic body 60 moves and stops until it comes into contact with the rotary valve 34 against the first and second springs 64 and 66. As a result, the first spool 48 closes the space between the high-pressure chamber 46 and the communication hole 52, and at the same time, the second spool 50 closes the space between the high-pressure chamber 46 and the orifice 54. Therefore, even if a difference in rotation speed occurs between the rotor 24 and the cam 18 and the pressure oil in the high-pressure chamber 46 rises due to the discharge stroke, the pressure oil is not released, so that a so-called lock as shown by the characteristic curve C in FIG. The properties of the state are obtained.

As described above, according to this embodiment, the first and second spools 48 and 50 are moved three by moving the movable magnetic body 60 by the magnetic frame 68 and the solenoid coil 70 provided outside in a non-contact manner. By setting the position, a normal torque transmission, a free state, and a locked state can be switched and set. Furthermore, the joint components such as the housing 4 and the rotary valve 34 are part of a magnetic circuit, and a magnetic attraction force is directly generated between the joint components and the movable magnetic body 60. The magnetic coupling between the magnetic frame 68 fixed to the member (not shown) and the magnetic circuit in the joint is performed via a radial gap having excellent dimensional stability. Even if the positional relationship in the axial direction slightly fluctuates, the fluctuation of the magnetic attraction acting on the movable magnetic body 60 can be suppressed, and delicate control can be performed by the current flowing through the solenoid coil.

Therefore, not only discontinuous switching control such as ON / OFF control, but also continuous variable control optimal for the vehicle can be performed. In addition, the magnetic frame 68 covers the joint body, and the radial gap is formed at the joint outer diameter, so that the joint length can be shortened.
Further, at least one of the N pole and the S pole of the magnetic frame 68 forms a magnetic circuit without interposing a non-magnetic member in the radial gap, so that the magnetic resistance is further increased. The solenoid coil 70 can be reduced.
And the price can be reduced. Further, power consumption can be reduced.

Next, a second embodiment will be described with reference to FIG. This embodiment is different from the first embodiment shown in FIG. 1 in that the position of the accumulator piston 10 is changed and the structure of the control mechanism for setting the torque transmission, free state and locked state is changed. It relates to a transmission coupling. The configuration will be described with reference to FIG.
Denotes an input shaft to which a driving force is input, and 82 denotes a housing rotatably supported by the input shaft 80 via a bearing 84. An output shaft (not shown) is connected to a spline joint 86 formed at a side end of the housing 82. Are connected.

Further, the housing 82 includes a bearing 84
And a cylindrical second portion 82a made of a ferromagnetic material rotatably supported by the input shaft 80 via the input shaft 80, and a cylindrical second portion 82 made of a non-magnetic material and connected to the end of the first portion 82a. The portion 82b is formed by integrally fixing a cylindrical third portion 82c made of a ferromagnetic material and further connected to the end of the second portion 82b by a connecting screw or welding (not shown).

Reference numeral 88 denotes a cam having the same shape as that shown in FIG.
2 and rotatably supported by the housing 82 and the input shaft 80. Reference numeral 94 denotes a rotor spline-fitted to the input shaft 80, and a plurality of plunger chambers 96 are formed along the circumferential direction. The number of plunger chambers 96 is determined by a predetermined relationship based on the number Nc of cam ridges provided on the cam surface 89 of the cam 88, as in the first embodiment. 9 plunger rooms 96
Are formed at equal intervals.

A plunger 98 is accommodated in each plunger chamber 96 via a return spring 100 so as to be able to move forward and backward, and a suction / discharge hole 102 is formed at the bottom of each plunger chamber 96. 104 is the housing 8
2 and a plurality of suction ports 106 and discharge ports 1 are provided on the surface facing the suction and discharge holes 102 in the same manner as described in the first embodiment.
08 are formed alternately, the suction port 106 communicates with a low-pressure suction passage 110, and the discharge port 108 communicates with a high-pressure chamber 112. Then, the rotor 94 and the rotary valve 1
When the plunger 98 advances and retreats along the cam ridge and the cam valley of the cam 88, the suction and discharge strokes are performed between the suction and discharge holes 102 and the suction and discharge ports 106 and 108.

Reference numeral 114 denotes a retainer, and the bearing 11
6 and rotatably supported by the input shaft 80,
By adhering to the back surface of the rotary valve 104,
The high pressure chamber 112 is integrated with the rotary valve 104 while being sealed. An accumulator piston 118 is provided in a sealed state between the inside of the third portion 82c of the housing 82 and the retainer 114, and is provided between the accumulator piston and the retainer 120 fixed to the end of the third portion 82c. The return spring 122 interposed is always elastically biased to the left in FIG.

Reference numeral 124 denotes an annular movable magnetic body made of a ferromagnetic material which is disposed inside the third portion 82c and is provided so as to be able to move forward and backward in a direction parallel to the central axis Q. Rotary valve 104
And is urged away from the first positioning member 126. 126 is a first portion 82a of the housing 82
An annular first positioning member 128 made of a magnetic material fixed to the inside of the third portion 82c is a second positioning member fixed to the inside of the third portion 82c. Specifies the stroke range. Note that FIG.
When the movable magnetic body 124 comes to the most retracted position in contact with the second positioning member 128 as shown in FIG.
The gap between the positioning member 126 and the movable magnetic body 124 is designed to be an air gap Z with a predetermined interval L1.

Reference numeral 130 denotes a spool which is fixed to the movable magnetic member 124 and operates integrally, and has a leading end inserted into a spool insertion hole which communicates with the high pressure chamber 112 formed in the rotary valve 104. Further, an annular groove 132 is formed in a peripheral end portion of the first spool 130,
Switching between opening and closing between the high-pressure chamber 112 and the low-pressure suction passage 126 is controlled in accordance with the position at which the spool 130 moves forward and backward together with the movable magnetic body 124.

A relief valve 134 is supported at the other end of the movable magnetic body 124 so as to be able to move forward and backward. The relief valve 134 is biased toward the rotary valve 104 by a relief spring 136 interposed between the movable magnetic body 124 and the movable magnetic body 124. The body 124 moves forward and backward as the body 124 moves forward and backward. A communication groove 138 is formed on a side surface of the relief valve 134 for communicating a discharge side of an orifice 140 described later with a piston chamber 139 of the low-pressure accumulator piston 118.

Reference numeral 140 denotes an orifice communicating with the high-pressure chamber 112. Opening / closing control is performed in accordance with the position at which the relief valve 134 moves forward and backward. Reference numeral 142 denotes a magnetic frame made of a ferromagnetic material fixed to a fixing member (not shown) outside the housing. The first and second portions 82a and 82c of the housing have extremely narrow air gaps X and Y. Provided in a non-contact manner.

Reference numeral 144 denotes a solenoid coil wound around the magnetic frame 142. As shown in FIG. 13, the gap between the distal end of the relief valve 134 and the discharge end of the orifice 140 when the movable magnetic body 124 is at the most retracted position is designed to be a predetermined value L2. The relationship between the gap L1 between the first positioning member 126 and the movable magnetic body 124 is L1> L2.

Therefore, as shown in FIG. 13, when the movable magnetic member 124 comes to the most retracted position (hereinafter referred to as a first control position), the annular groove 132 of the spool 130
Is located in the rotary valve 104, so that the high pressure chamber 112
And the suction passage 110 are shut off, and at the same time, the orifice 140
Is in an open state, and torque transmission described later is performed.
Also, against the spring force f1 of the return spring 125,
When the movable magnetic body 124 moves forward by the distance L2 (hereinafter, referred to as a second control position), the tip of the relief valve 134 closes the orifice 140, and at the same time, the annular groove 132 of the spool 130 moves between the high-pressure chamber 112 and the suction passage 110. To communicate. In this state, the oil pressure in the high pressure chamber 112 is
, So that it will be in a free state described later.

Further, the movable magnetic body 124 is most advanced to abut against the first positioning member 126 against the spring force f1 + f2 of the return spring 125 and the relief spring 136 (the spring force of the relief spring 136 is f2). The relief spring 136 contracts and the tip of the relief valve 134 keeps the orifice 140 closed, while the annular groove 132 of the spool 130 Since the vehicle moves forward to a position where communication is not established, the connection between the high-pressure chamber 112 and the suction passage 110 is shut off. In this state,
Since the hydraulic pressure in the high-pressure chamber 112 is not released, a locked state described later is established.

When the relief valve 134 has the orifice 1
When opening and closing the valve 40, a function as a poppet valve is exhibited by the balance between the oil pressure of the high-pressure chamber 112 and the spring force f2 of the relief spring 136, and the opening and closing operation is performed smoothly. If no current is supplied to the solenoid coil 144, the movable magnetic body 124 can be set to the first control position.

The movable magnetic body 124 is moved to the second control position by supplying a predetermined current I1 to the solenoid coil 144. That is, the solenoid coil 144
When a predetermined current I1 is supplied to the housing 82, the magnetic force is applied via the magnetic frame 142, the first portion 82a and the third portion 82c of the housing 82, the first positioning member 126, the movable magnetic body 124, and the air gaps X, Y, and Z. A path is formed, whereby the magnetic force F1 that is stronger than the spring force f1 of the return spring 125 and weaker than the spring force f1 + f2 of the return spring 125 and the relief spring 136 (ie, f1 <F1 <).
f1 + f2) is generated, and the movable magnetic body 124 is moved to the second control position.

In order to move the movable magnetic body 124 to the third control position, a predetermined current I2 (I
2> I1). That is, when the predetermined current I2 is supplied to the solenoid coil 144, the magnetic frame 1
42, a first portion 82a and a third portion 82c of the housing 82, a first positioning member 126, a movable magnetic body 124
And a magnetic path is formed through the air gaps X, Y, and Z,
As a result, the magnetic force F2 is stronger than the spring force f1 + f2 of the return spring 125 and the relief spring 136.
(That is, f1 + f2 <F2) occurs and the movable magnetic body 12
4 to a third control position.

According to this embodiment, in the torque transmission state, the torque transmission characteristic shown in the characteristic A of FIG. 12 is obtained by the operation of the hydraulic pump and the flow resistance of the orifice 140, and in the free state, the characteristic shown in the characteristic B of FIG. In the locked state, the characteristic shown by the characteristic C in FIG. 12 is obtained. Further, since the magnetic resistance due to the air gap is reduced, the movable magnetic body 124 can be driven efficiently, and the size of the solenoid coil can be reduced and the power consumption can be reduced.

Next, a third embodiment will be described with reference to FIG. This embodiment relates to a further modified embodiment of the second embodiment shown in FIG. 13, and in particular, the cam 88 of the hydraulic pump shown in FIG.
In No. 4, the cam is formed integrally with the housing.
Further, the retainer 114 in FIG. 13 has a different structure and the like.

The structure will be described with reference to FIG.
Is an input shaft to which driving force is input, and 152 is a bearing 15
An output shaft (not shown) is connected to a spline joint 156 formed at a side end of the first portion 152, which is a first portion of the housing rotatably supported by the input shaft 150 via the first shaft 152. . 158 is a second portion of the housing made of a magnetic material, 160 is a third portion of the housing made of a non-magnetic material, and 162 is a fourth portion of the housing made of a magnetic material. 4 are connected in series and integrated by connecting screws (not shown) or welding.

Inside the first portion 152, a cam surface 164 similar to the cam shown in FIG. 2 is formed. For example, five cam ridges and cam valleys are alternately formed by five. 166 is
The rotor is a spline fit to the input shaft 150, and a plurality of plunger chambers 168 are formed along the circumferential direction. The number of plunger chambers 168 is determined by a predetermined relationship based on the number Nc of cam ridges provided on the cam surface 164, as in the first embodiment.
Plunger chambers 168 are formed at equal intervals.

A plunger 170 is accommodated in each plunger chamber 168 via a return spring 172 so as to be able to move forward and backward, and a suction / discharge hole 174 is formed at the bottom of each plunger chamber 166. 176 is a rotary valve fitted and fixed inside the housing,
As shown in the first embodiment, the suction and discharge holes 17
A plurality of suction ports 178 and discharge ports 180 are alternately formed on the surface facing the suction port 4, the suction ports 178 communicate with a low-pressure suction path 182, and the discharge ports 180 are connected to the high-pressure chamber 18.
It communicates with 4. Then, the rotor 166 and the rotary valve 176 rotate relative to each other, and the plunger 170 moves forward and backward along the cam peaks and the cam valleys of the cam surface 164, so that the suction port 174 and the suction port 178 and the discharge port 180 The operation of the suction and discharge stroke is performed.

Reference numeral 186 denotes a retainer made of a non-magnetic material, which is rotatably supported on the input shaft 150 via a bearing 188, and is fixed to the housing by a fixing member 190. An accumulator piston 192 is provided between the inside of the fourth portion 162 of the housing and the retainer 186 in a sealed state.
14 is provided by a return spring 196 interposed between a retainer 194 fixed to the end of the portion 162 of FIG.
Is always elastically biased to the left.

Reference numeral 198 denotes an annular movable magnetic body made of a ferromagnetic material which is disposed inside the third portion 162 and is provided so as to be able to advance and retreat in a direction parallel to the central axis Q. By rotary valve 1
It is biased away from 76. Reference numeral 200 denotes an annular positioning member made of a magnetic material fixed to a side end of the second portion 158 of the housing. The annular positioning member 200 sets a movable stroke of the movable magnetic material 198 according to a distance from the retainer 194. The stroke L1 is set in the same manner as in the second embodiment shown in FIG.
When 98 comes to the most retracted position where it contacts the retainer 194, the air gap Z is the gap L1 between the positioning member 200 and the movable magnetic body 198.

Reference numeral 202 denotes a spool which is fixed to the movable magnetic body 198 and operates integrally, and has a leading end inserted into a spool insertion hole which communicates with a high pressure chamber 184 formed in the rotary valve 176. Further, the spool 202
An annular groove 204 is formed at the peripheral end of the spool 202, and controls opening and closing between the high-pressure chamber 184 and the low-pressure suction passage 182 in accordance with the position where the spool 202 moves forward and backward together with the movable magnetic body 198.

Reference numeral 206 denotes a relief valve supported at the other end of the movable magnetic body 198 so as to be able to move forward and backward, and is biased toward the rotary valve 176 by a relief spring (not shown) interposed between the movable magnetic body 198 and the movable valve. While moving, the movable magnetic body 198 moves forward and backward with the forward and backward movement. or,
A communication groove 208 is formed on a side surface of the relief valve 206 for communicating a discharge side of an orifice 210 described later with a low-pressure housing inner chamber.

Reference numeral 210 denotes an orifice communicating with the high-pressure chamber 184. Opening / closing control is performed in accordance with the position at which the relief valve 206 moves forward and backward. Numeral 212 denotes a magnetic frame made of a ferromagnetic material fixed to a fixing member (not shown) outside the housing, and extremely narrow air gaps X and Y are formed between the second portion 158 and the fourth portion 162 of the housing. Provided in a non-contact manner.

Reference numeral 214 denotes a solenoid coil wound around the magnetic frame 212. As shown in FIG. 14, the gap between the tip of the relief valve 206 and the discharge end of the orifice 210 when the movable magnetic body 198 is at the most retracted position is designed to be a predetermined value L2. The relationship between the gap L1 between the member 200 and the movable magnetic body 198 is L1> L2.

Therefore, as shown in FIG. 14, when the movable magnetic body 198 comes to the most retracted position (hereinafter, referred to as a first control position), the annular groove 204 of the spool 202
Is located in the rotary valve 176, so that the high pressure chamber 184
And the suction path 182 are shut off, and at the same time, the orifice 210
Is in an open state, and torque transmission described later is performed.
Also, the spring force f of the return spring (not shown)
When the movable magnetic body 198 moves forward by a distance L2 (hereinafter, referred to as a second control position) against the relief valve 2, the relief valve 2
06 closes the orifice 210, and at the same time, the annular groove 204 of the spool 202
Communication between the two. In this state, the hydraulic pressure of the high-pressure chamber 184 falls into the suction passage 182, so that a free state described later is established.

Further, the movable magnetic body 198 is most advanced against the positioning member 200 against the spring force f1 + f2 of the return spring and the relief spring (not shown) (the spring force of the relief spring is f2). When the relief spring is moved to the position (hereinafter, referred to as a third control position), the relief spring is contracted to release the relief valve 20.
6 keeps the orifice 210 closed,
On the other hand, since the annular groove 204 of the spool 202 advances to a position where it does not communicate with the high-pressure chamber 184, the space between the high-pressure chamber 184 and the suction passage 182 is shut off. In this state, the high pressure chamber 184
Since no hydraulic pressure is released, a locked state described later is established.

When the relief valve 206 has the orifice 2
When the opening and closing operation of the valve 10 is performed, the function as a poppet valve is exhibited by the balance between the oil pressure of the high-pressure chamber 184 and the spring force f1 of the relief spring, and the opening and closing operation is performed smoothly. When no current is supplied to the solenoid coil 214, the movable magnetic body 198 can be set at the first control position.

The movable magnetic body 198 is moved to the second control position by supplying a predetermined current I1 to the solenoid coil 214. That is, the solenoid coil 214
When the predetermined current I1 is supplied to the magnetic frame 212, the second portion 158 and the fourth portion 162 of the housing, the positioning member 200, the movable magnetic body 198, and the air gaps X, Y,
A magnetic path is formed via Z, thereby generating a magnetic force F1 stronger than the spring force f1 of the return spring and weaker than the spring force f1 + f2 of the return spring and the relief spring (that is, f1 <F1 <f1 + f2), and the movable magnetic force is generated. Move body 198 to the second control position.

In order to move the movable magnetic body 198 to the third control position, a predetermined current I2 (I
2> I1). That is, when the predetermined current I2 is supplied to the solenoid coil 214, the magnetic frame 2
12, housing second part 158 and fourth part 16
2. A magnetic path is formed through the positioning member 200, the movable magnetic body 198, and the air gaps X, Y, and Z, whereby the magnetic force F2 (ie, f1 + f2 <) is greater than the spring force f1 + f2 of the return spring and the relief spring.
F2) occurs to move the movable magnetic body 198 to the third control position.

According to this embodiment, in the torque transmission state, the torque transmission characteristic shown in the characteristic A of FIG. 12 is obtained by the operation of the hydraulic pump and the flow resistance of the orifice 210, and in the free state, the characteristic shown in the characteristic B of FIG. In the locked state, the characteristic shown by the characteristic C in FIG. 12 is obtained. Further, since the configuration is such that the magnetic resistance due to the air gap is reduced, the movable magnetic body 198 can be driven efficiently, and the size of the solenoid coil can be reduced and power consumption can be reduced.

[0072]

As described above, according to the present invention, the joint constituting member is a part of a magnetic circuit, and a magnetic attraction force is directly generated between the joint constituting member and the movable magnetic body. Since the magnetic coupling between the magnetic frame fixed to the third member that does not rotate and the magnetic circuit in the joint is performed through a radial gap having excellent dimensional stability, the coupling between the joint and the magnetic frame is Even if the positional relationship in the axial direction fluctuates somewhat, fluctuations in the magnetic attraction force acting on the movable magnetic body can be suppressed, and fine control can be performed by a current flowing through the solenoid coil.

Therefore, not only discontinuous switching control such as ON / OFF switching, but also continuous variable control optimal for the vehicle can be performed. Further, since the magnetic frame has a structure that covers the joint body and the radial gap is formed in the joint outer diameter, the length of the joint can be reduced. Further, at least one of the magnetic poles of the N pole and the S pole of the magnetic frame forms a magnetic circuit without interposing a non-magnetic member in the radial gap portion. Thus, the size of the solenoid coil can be reduced, and the cost can be reduced. Further, power consumption can be reduced.

[Brief description of the drawings]

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

FIG. 2 is a perspective view showing a shape of a cam.

FIG. 3 is a partial cross-sectional view for explaining a positional relationship between a high-pressure chamber and a discharge port.

FIG. 4 is an explanatory diagram showing a positional relationship between a cam and a plunger.

FIG. 5 is an explanatory diagram showing a structure of a rotary valve and a positional relationship between plungers.

FIG. 6 is a perspective view showing shapes of a movable magnetic body and a positioning member.

FIG. 7 is an explanatory diagram illustrating a relationship between a driving force for driving the movable magnetic body and a spring force of a spring provided on the movable magnetic body.

FIG. 8 is a partial cross-sectional view for explaining an operation during torque transmission.

FIG. 9 is a cross-sectional view showing a cam and a plunger portion developed on a straight line in order to further explain the operation during torque transmission.

FIG. 10 is a partial cross-sectional view for explaining an operation in a free state.

FIG. 11 is a partial cross-sectional view for explaining an operation in a locked state.

FIG. 12 is a characteristic diagram showing power transmission characteristics.

FIG. 13 is a cross-sectional view showing a main part structure for describing a structure of a second embodiment.

FIG. 14 is a cross-sectional view showing a main part structure for describing a structure of a third embodiment.

FIG. 15 is an explanatory diagram for explaining a problem of the related art.

[Explanation of symbols]

2; input shaft 4; housing 4a; protrusion 8; spline joint 10; accumulator piston 18; cam 18a; protrusion 22; cam surface 24; rotor 26; plunger chamber 28; plunger 30; return spring 32; Notch 38; suction port 40; discharge port 42; suction path 44; oil supply section 45; discharge path 46; high-pressure chamber 47; first spool hole 48; first spool 49; Hole 50; second spool 52; communication hole 54; orifice 56; cover 58; retaining ring 60; movable magnetic body 60a; locking groove 62; positioning member 62a; locking projection 62b; bottom end 64; Spring 66; second spring 68; magnetic frame 70; solenoid coil 80, 150; input shaft 82; 86, 156; spline joint 88; cams 89, 164; cam surfaces 94, 166; rotors 96, 168; plunger chambers 98, 170; plungers 100, 172; return springs 102, 174; suction and discharge holes 104, 176; Valves 106, 178; Suction ports 108, 180; Discharge ports 110, 182; Suction paths 112, 184; High pressure chambers 114, 186; Retainers 118, 192; Accumulator pistons 124, 198; Movable magnetic bodies 130, 202; 204; annular groove 125; return springs 126, 128, 200; positioning members 134, 206; relief valves 138, 208; communication groove 139; piston chamber 136; relief springs 140, 210; 2; magnetic frame 144, 214; solenoid coil 152, 158, 160, 162;
Fourth part 190; fixing member X, Y, Z; air gap

Claims (2)

(57) [Claims] 1. A hydraulic pump provided on first and second rotating shafts rotatable relative to each other and driven by differential rotation of the first and second rotating shafts, and controlling hydraulic oil of the hydraulic pump. Hydraulic power for transmitting a torque according to a rotational speed difference between the first and second rotating shafts and an external control signal, the control valve comprising: a control valve that operates the control valve according to an external signal; A transmission coupling fixed to a third member that does not rotate, held concentrically with the coupling and in a non-contact state, and coupled with a movable magnetic body that is inside the coupling and constitutes the actuator ; A magnetic frame magnetically coupled between the magnetic frames via a radial gap, a solenoid coil provided integrally with the magnetic frame, and a housing formed of a magnetic material and forming a magnetic path together with the magnetic frame
And a coupling component member comprising a rotary member and a rotary valve. The coupling component member is housed in the coupling so as to be movable in the axial direction, and is magnetically coupled via an axial gap between the coupling component member and the solenoid coil. A movable magnetic body that controls the control valve by generating an axial magnetic attraction force with the joint constituent member when energized, and a movable magnetic body provided between the movable magnetic body and the magnetic frame; A non-magnetic cover that is a part of a container that keeps the oil tight while preventing a short circuit in the magnetic circuit of the above, and that the control valve is electrically and mechanically non-contacted from outside of the joint to control the control valve. A hydraulic power transmission coupling characterized by: 2. The hydraulic power transmission coupling according to claim 1, wherein at least one of the magnetic poles of the N pole and the S pole of the magnetic frame is magnetically disposed without interposing the cover in the radial gap. A hydraulic power transmission coupling characterized by forming a circuit.