JPH05321951A - Hydraulic power transmission joint - Google Patents

Abstract

PURPOSE:To improve driving performance in a hydraulic power transmission joint for distributing driving force of an automobile by electrically and mechanically controlling a hydraulic valve of a hydraulic pump with combination of a magnetic circuit, a movable magnetic body, and a solenoid coil. CONSTITUTION:A solenoid is composed of a magnetic frame 68 and a solenoid coil 70. A narrow air gap X is formed between one end 68a of the magnetic frame 68 and an outer end surface of a housing 4 bringing about a non-contact condition. The other end 68b of the magnetic frame 68 is opposed to a movable magnetic body 60. A gap between opposed parts can be reduced to a minimum, while a narrow air gap Y is formed between the end 68b and a cover 56, for keeping a non-contact condition. An air gap Z of L2 is formed between the movable magnetic body 60 and a rotary valve 34. A magnetic passage is formed through the movable magnetic body 60, the rotary valve 34, the housing 4, the air gaps X to Z by supplying electricity to the solenoid coil 70. The movable magnetic body 60 is shifted to the side of the rotary valve 34 for switching controlling according to the electric current rate.

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 joint applied to drive force distribution of a vehicle.

[0002]

2. Description of the Related Art Conventionally, as such a hydraulic power transmission joint, for example, there is one disclosed in JP-A-1-154228. This hydraulic power transmission joint is a hydraulic pump driven by a rotational speed difference between a relatively rotatable first rotary member and a second rotary member, and a discharge passage of the hydraulic pump according to a control signal from the outside. And a flow resistance control means for generating a flow resistance,
To control the transmission torque between the second rotating members,
Further, by providing an electromagnetic actuator acting in the axial direction in the central portion of the first or second rotating member and directly operating the flow resistance control means by the electromagnetic actuator, It is configured to control the torque transmission characteristic between the two rotating members.

Here, the electromagnetic actuator includes a magnetic frame fixed to a non-rotating third member, a solenoid coil integrally housed in the magnetic frame, and a magnetic coil when a current is supplied to the solenoid coil. And a movable magnetic body that generates a magnetic attraction force between the frame and the movable magnetic body,
The joint is covered with a cover made of a non-magnetic material which holds the oil tightness and is kept in non-contact with the magnetic frame.

[0004]

However, as shown in FIG.
As shown in (1), generally, the electromagnetic actuator based on direct current has a characteristic that when the air gap length in the magnetic path changes, the magnetic attraction force changes even when a current of the same current value is supplied. Further, in a mechanical structure such as a transfer, due to a large number of parts stacked in the axial direction and differences in thermal expansion due to materials, the positional relationship between the parts is less accurate in the axial direction than in the radial direction.

In the conventional hydraulic power transmission joint, the magnetic circuit constituting the magnetic actuator is constructed independently of the joint body, and the magnetic attraction force acts directly between the movable magnetic body and the magnetic frame. It has become. Therefore, when such a conventional hydraulic power transmission joint is built in the transfer or the like, the positional relationship in the axial direction between the magnetic frame fixed to the case side of the transfer and the movable magnetic body in the joint body is small. It is not stable, and even if the same current value is supplied to the solenoid coil, the magnetic attraction force that acts on the movable magnetic body is not stable, so it cannot be applied to continuous variable control that requires control accuracy. was there.

Further, in the conventional hydraulic power transmission joint, since the nonmagnetic cover is interposed between the magnetic frame and the movable magnetic body, the air gap between the movable magnetic body and the magnetic frame is at least this. Since the gap is separated by the thickness of the cover of the non-magnetic material and the magnetic resistance increases, there has been a problem that the magnetomotive force required to drive the movable magnetic material also increases.

Further, if 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 long. The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a hydraulic power transmission joint without the above problems by improving the structure of an electromagnetic actuator. To do.

[0008]

SUMMARY OF THE INVENTION In order to achieve such an object, the present invention is provided on first and second rotating shafts which are capable of relative rotation, and the differential between the first and second rotating shafts. A rotary pump driven by rotation, a control valve for controlling the pressure oil of the hydraulic pump, and an actuator for operating the control valve in response to a signal from the outside, and the rotational speeds of the first and second rotary shafts. In the hydraulic power transmission joint that transmits the torque according to the difference and the control signal from the outside, the third non-rotating
A magnetic frame that is fixed to the member of FIG. 1 and is held concentrically with the joint in a non-contact state, and that is magnetically coupled to a member that constitutes the actuator inside the joint via a radial gap. A solenoid coil integrally provided in the magnetic frame, a joint component made of a magnetic material to form a magnetic path with the magnetic frame, and housed in the joint so as to be movable in the axial direction, and the joint. It is magnetically coupled with a component through an axial gap, and when the solenoid coil is energized, an axial magnetic attraction force is generated with the joint component to control the control valve. A movable magnetic body and a non-magnetic member that prevents a short circuit of the magnetic circuit in the joint and is a part of a container that holds oil tightness,
The control valve is controlled from the outside of the joint electrically and mechanically without contact.

Of the magnetic poles of the N pole and the S pole of the magnetic frame,
At least one magnetic pole forms a magnetic circuit without interposing a non-magnetic member in the radial gap portion.

[0010]

According to the hydraulic power transmission joint of the present invention having such a structure, the joint constituent member is part of the magnetic circuit,
A magnetic attraction force is directly generated between the joint component and the movable magnetic body, and the magnetic coupling between the magnetic frame fixed to the non-rotating third member and the magnetic circuit in the joint is determined. Since the radial gap with excellent stability is used, even if the axial positional relationship between the joint and the magnetic frame fluctuates slightly, fluctuations in the magnetic attraction force acting on the movable magnetic body can be suppressed. Therefore, it is possible to perform delicate control by the current flowing through the solenoid coil.

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

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. In FIG. 1, which shows the overall structure, 2 is an input shaft to which a driving force is input, 4 is a housing made of a magnetic material supported by an input shaft 2 via a bearing 6 so as to be relatively rotatable, and a side end of the housing 4 is provided. Spline joint 8 formed on
An output shaft (not shown) is connected to.

An accumulator piston 10 slidable concentrically with the central axis Q is housed in a piston chamber formed on the spline joint 8 side of the housing 4, and is inserted into a retainer 12 fixed inside the housing 4. The mounted return spring 14 biases the piston to the left, and the oil chamber 16 and the O-ring 17 seal the piston chamber.

Reference numeral 18 denotes a housing 4 in which a thrust needle 2 is provided.
The cam surface of the cam 18 is a cam provided through
2, a plurality of cam peaks and cam valleys are alternately formed one by one, as shown in FIG. Also, on the outer periphery of the cam 18,
Protrusions 18a are provided at predetermined intervals, and the same number of positioning protrusions 4a are provided inside the housing 4, and the cam 18 is provided within an angle θ at which these protrusions 18a, 4a 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 peaks of the cam 18. In this embodiment, the number Nc of cam peaks and cam valleys is set to 5 each. A rotor 24 is spline-fitted to the input shaft 2 and has a plurality of plunger chambers 26 formed in the circumferential direction. The number of the plunger chambers 26 is determined by a predetermined relationship based on the number Nc of the cam crests provided on the cam surface 22 of the cam 18, and in this embodiment, there are 9 plungers for 5 cam crests. The chambers 26 are formed at equal intervals.

A plunger 28 is housed in each of the plunger chambers 26 so as to be movable back and forth via a return spring 30, and an intake / discharge hole 32 is formed at the bottom of each of the plunger chambers 26. Reference numeral 34 denotes a rotary valve, which rotates integrally by fitting and fixing it on the inner wall of the housing 4, and also through the ball bearing 36.
It is supported so as to be rotatable relative to.

Five intake ports 38 and five discharge ports 40 are provided on the surface of the rotary valve 34 facing the rotor 24.
Are alternately formed at equal intervals, and the suction port 38 is further formed with a suction passage 42 that communicates with the oil supply portion 44 outside the rotor 24. The discharge port 40 is not shown in FIG. 1 for the sake of explanation because it is located at a position that cannot be represented in the vertical cross-sectional view of FIG. 1, but as shown in FIG. The low pressure suction passage 42 and the oil supply portion 44 do not communicate with each other, but communicate with a high pressure chamber 46 described later via a discharge passage 45. That is, the suction port 38 is for supplying oil from the low-pressure suction passage 42 to the suction / discharge hole 32 of the rotor 24 in the suction stroke, and the discharge port 40 is from the suction / discharge hole 32 of the rotor 24 in the discharge stroke. It is provided to supply the pressure oil to be discharged to a high pressure chamber 46 described later through the discharge passage 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.
Will be described in detail with. First, in FIG. 4, a cam 18 is mounted inside the housing 4, and a plurality of protrusions 4a and 18a provided on each of them enable relative rotation within a predetermined angle θ. As described above, the cam surface 22 of the cam 18 has five cam ridges and cam valleys, so that the angle β formed between the highest point of each cam ridge and the lowest point of each cam valley is 36. It has become °. Further, the nine plungers 28 facing the cam surface are located at 40 ° intervals, as indicated by the circle shown by the alternate long and short dash line in FIG.

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

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 with the rotor 24, and
When the projection 4a of the housing 4 and the projection 18a of the cam 18 come into contact with each other, their relative rotation is stopped, and the cam surface 22
The plunger 28, which operates from the cam valley to the cam mountain, operates in the discharge stroke to discharge the pressure oil in the plunger chamber 26 from the intake / discharge hole 32, while the plunger 28 operates from the cam mountain to the cam valley. Reference numeral 28 indicates the operation of the suction stroke to suck the oil into the plunger chamber 26. Further, even if the rotation is in the direction opposite to the arrow D, the same suction / discharge stroke is performed.

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

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

Further, the rotary valve 34 includes a high pressure chamber 4
A second spool hole 49 communicating with the other end of 6 and penetrating in the direction parallel to the central axis Q is formed, and the second spool 50 is inserted into the second spool hole 49 so as to be able to move forward and backward. .. 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 by a retaining ring 58 and is sealed from the input shaft 2.

Reference numeral 60 is a movable magnetic body made of a ferromagnetic body, 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 that is interposed between one end of the movable magnetic body 60 and the end surface of the rotary valve 34, and acts so as to separate the movable magnetic body 60 and the rotary valve 34.

Reference numeral 66 is a second spring interposed between one end of the movable magnetic body 60 and the positioning member 62, and acts in a direction to widen the distance between the movable magnetic body 60 and the positioning member 62. Further, referring to FIG. 6, the structure of the movable magnetic body 60 and the positioning member 62 will be described. Each of the bottom ends of the movable magnetic body 60 has a large diameter hole into which the input shaft 2 is inserted. A locking groove 60a into which the locking projection 62a of the positioning member 62 is loosely fitted is formed.

A first spring 64 is arranged between the outer side of the positioning member 62 and the inner side of the movable magnetic body 60. The first spring 64 acts so as to separate the movable magnetic body 60 and the rotary valve 34. .. Further, 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 distance only between the movable magnetic body 60 and the positioning member 62. ..

Referring again to FIG. 1, 68 is a magnetic frame made of a magnetic material forming a magnetic solenoid, 70 is a solenoid coil mounted on the magnetic frame 68, and the magnetic frame 68 faces the outer end of the housing 4. Is formed into a tubular shape having a portion 68a fitted from the outside and a portion 68b facing the movable magnetic body 60.
In contrast, the magnetic frame 68 is concentrically mounted.

As shown in detail in FIG. 3, one end portion 68a of the magnetic frame 68 is not in contact with the outer end surface of the housing 4 through a relatively narrow air gap X,
Further, the facing 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 other end 68b and the cover 56 are not in contact with each other by the narrow air gap Y. Further, when the movable magnetic body 60 is moved to the leftmost side by the first spring 64, an air gap Z is provided so that the distance between the movable magnetic body 60 and the rotary valve 34 becomes L2. When a current is supplied to the solenoid coil 70, the ends 68a and 68b of the magnetic frame 68, the movable magnetic body 60, the rotary valve 34, the housing 4, and the air gaps X and Y of the magnetic frame 68 are supplied as shown by the dotted lines in FIG. , Z, a magnetic path is formed, and the movable magnetic body 34 is controlled to move to the rotary valve 34 side by the magnetic force generated according to the amount of current at that time.

In this embodiment, when no current is passed through the solenoid coil 70 (hereinafter referred to as the first control mode)
By supplying the first control current having the current value I1, the magnetic force F1 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 resists the spring force of the first spring 64.
When moving a certain distance (hereinafter referred to as the second control mode), the second value of the current value I2 (where I2> I1)
By supplying the control current of the magnetic field 68, the movable magnetic body 60, the rotary valve 34 and the housing 4, magnetic force F2 (however, F2> F1) by the magnetic path is generated.
Against the spring force of the first and second springs 64, 66,
When moving the movable magnetic body 60 by a certain distance (hereinafter,
(Hereinafter referred to as a third control mode), a control mode for performing three types of position setting is set, and 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 control mode are set. , Second springs 64, 6
The relationship between the spring forces f1 and f2 of 6 is as shown in FIG.
It is set.

That is, in the first control mode in which no current is passed through the solenoid coil 70, the movable magnetic body 60 is moved to the leftmost side by the first spring 64.
The displaceable amount of the movable magnetic body 60 is less than a constant gap distance L1 provided between the bottom end 62b of the positioning member 62 and the end surface 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 is larger than the spring force f1 of the first spring 64, and the spring force f1 of the second spring 66 is larger than the spring force f1 of the first spring 64.
2 and a magnetic force F1 smaller than the total f1 + f2 (that is, f
1 <F1 <f1 + f2) current value I1
Supply a first control current of the. As a result, the displaceable amount L of the movable magnetic body 60 falls within 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 are used.
And a magnetic force F2 smaller than the magnetic force F3 within a certain safety range (that is, f1 + f2 <F2).
A second control current having a current value I2 that causes <F3) is supplied. As a result, the displaceable amount L of the movable magnetic body 60 falls within 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 is moved to the leftmost side. L2 is a gap distance between the movable magnetic body 60 and the end portion of the rotary valve 34 when the movable magnetic body 60 is moved to the left. is there.

Next, the operation of the embodiment having such a structure will be described. First, when the first control mode in which the current is not supplied to the solenoid coil 70 is set, the movable magnetic body 60 is not affected by the electromagnetic solenoid as shown in FIG.
Is urged to the leftmost side by the spring 64 and becomes stationary. 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 among the cam 18, the rotor 24, and the rotary valve 34 in the first control mode is as shown in a sectional view of a linear development. When a rotational speed difference occurs between the cam 18 and the rotor 24, a certain plunger 28 is in the suction stroke (indicated by an upper arrow).
Has 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, and oil is sucked into the plunger chamber 26 from the suction passage 42 through the suction / discharge hole 32 of the rotor 24, and a certain plunger 28 discharges it. When it is in the stroke (indicated by the lower arrow), it has an opposite relationship to the suction stroke and leads to the plunger chamber 26 formed in the rotor 24. The suction stroke and the discharge stroke of the plunger 28 are shown in FIG.
Since the discharge side and the suction side communicate with each other via the orifice 54 of the rotary valve 34, a pressure corresponding to the flow resistance of the orifice 54 is generated on the discharge side, and the pressure between the cam 18 and the rotor 24 is increased. The torque transmission having the characteristic as indicated by the characteristic curve A of 12 is performed. The torque transmission characteristic A is adjusted according to the inner diameter of the orifice 54.

When the 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 magnetic force F1 corresponding to the first control current I1 moves the movable magnetic body 60 to the right, and the bottom end 6 of the positioning member 62 is moved.
2b stops at the position where it abuts the rotary valve 34.
At the same time, the first spool 48 also moves to the right as much as there is no gap between the bottom end 62b of the positioning member 62 and the rotary valve 34. As a result, the high pressure chamber 46 and the communication hole 52
The space is opened, and regardless of the position of the second spool 50, the pressure oil in the high pressure chamber 46 is lost to the low pressure suction passage 42 side. Therefore, the so-called free state as shown by the characteristic curve B in FIG. 12 is obtained, and the transmission torque cannot be obtained.

When the third control mode for supplying the second control current I2 to the solenoid coil 70 is set, as shown in FIG.
As shown in FIG. 1, the magnetic path corresponding to the control current I2 is the magnetic frame 6
8, the movable magnetic body 60, the rotary valve 34, and the housing 4 generate a magnetic force F2 (where F2> F
By 1), the movable magnetic body 60 moves and stands still against the rotary valve 34 against the first and second springs 64 and 66. As a result, the first spool 48 closes between the high pressure chamber 46 and the communication hole 52, and at the same time, the second spool 50 closes between the high pressure chamber 46 and the orifice 54. Therefore, even if the rotational speed difference is generated 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, and so-called lock as shown by the characteristic curve C in FIG. The characteristics of the state are obtained.

As described above, according to this embodiment, the movable magnetic body 60 is moved by the magnetic frame 68 and the solenoid coil 70 which are provided outside in a non-contact manner, so that the first and second spools 48 and 50 are moved to three positions. By setting the position, it is possible to switch between normal torque transmission, free state, and locked state. Furthermore, the housing 4, the rotary valve 34, and other joint components are used as a part of the magnetic circuit, and a magnetic attraction force is directly generated between the joint component and the movable magnetic body 60. Since the magnetic frame 68 fixed to the member (not shown) and the magnetic circuit in the joint are magnetically coupled via the radial gap having excellent dimensional stability, the joint and the magnetic frame 68 are Even if the positional relationship between and in the axial direction fluctuates to some extent, fluctuations in the magnetic attraction force acting on the movable magnetic body 60 can be suppressed, and delicate control can be performed by the current flowing in the solenoid coil.

Therefore, not only the discontinuous switching control such as ON / OFF but also the continuous variable control most suitable for the vehicle can be performed. Further, since the magnetic frame 68 covers the joint body and the radial gap portion is formed on the joint outer diameter portion, the length of the joint can be shortened.
Further, at least one of the magnetic poles of the N pole and the S pole of the magnetic frame 68 forms a magnetic circuit without interposing a nonmagnetic member in the radial gap portion, so that the magnetic resistance is further improved. Can be reduced, solenoid coil 70
It is possible to reduce the size and the price. Further, it is possible to reduce power consumption.

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

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

Reference numeral 88 is a cam having the same shape as that shown in FIG. 2, and includes a thrust needle 90 and a bearing 9.
It is rotatably supported with respect to the housing 82 and the input shaft 80 via the shaft 2. Reference numeral 94 is a rotor that is spline-fitted to the input shaft 80, and has a plurality of plunger chambers 96 formed along the circumferential direction. Similar to the first embodiment, the number of plunger chambers 96 is determined by a predetermined relationship based on the number Nc of cam peaks provided on the cam surface 89 of the cam 88, and for five cam peaks. 9 plunger chambers 96
Are formed at equal intervals.

A plunger 98 is housed in each of the plunger chambers 96 so as to be movable back and forth through a return spring 100, and suction and discharge holes 102 are formed in the bottoms of the plunger chambers 96. 104 is a housing 8
2 is a rotary valve fitted and fixed to the inner side of the suction port 2, and a plurality of suction ports 106 and the discharge port 1 are provided on the surface facing the suction / discharge hole 102, as in the first embodiment.
08 are alternately formed, the suction port 106 communicates with the low pressure suction passage 110, and the discharge port 108 communicates with the high pressure chamber 112. Then, the rotor 94 and the rotary valve 1
04 relatively moves and the plunger 98 moves back and forth along the cam peak and the cam trough of the cam 88, so that the suction / discharge stroke operation is performed between each suction / discharge hole 102 and the suction port 106 and the discharge port 108.

Reference numeral 114 is a retainer, and the bearing 11
6 is rotatably supported by the input shaft 80 via 6,
By contacting the back surface of the rotary valve 104,
The high pressure chamber 112 is sealed and integrated with the rotary valve 104. Reference numeral 118 denotes an accumulator piston provided in a sealed state between the inside of the third portion 82c of the housing 82 and the retainer 114, and between the retainer 120 fixed to the end of the third portion 82c. By the intervening return spring 122, it is always elastically biased to the left side 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 movable in a direction parallel to the central axis Q. Rotary valve 104
And is biased away from the first positioning member 126. 126 is the first portion 82a of the housing 82.
An annular first positioning member made of a magnetic material fixed to the inside of the second positioning member 128 is a second positioning member fixed to the inside of the third portion 82c, and the movable magnetic member 124 can move back and forth. Specifies the stroke range. Incidentally, FIG.
As shown in, when the movable magnetic body 124 reaches the most retracted position where it abuts the second positioning member 128,
The gap between the positioning member 126 and the movable magnetic body 124 is designed to be an air gap Z having a predetermined gap L1.

Reference numeral 130 denotes a spool fixedly attached to the movable magnetic body 124 and operating integrally therewith, and its tip is inserted into a spool insertion hole communicating with the high pressure chamber 112 formed in the rotary valve 104. Further, an annular groove 132 is formed in the peripheral end portion of the first spool 130,
The opening / closing between the high pressure chamber 112 and the low pressure suction passage 126 is switched and controlled according to the position where the spool 130 moves back and forth together with the movable magnetic body 124.

Reference numeral 134 denotes a relief valve movably supported at the other end of the movable magnetic body 124 so that the movable magnetic body 124 is urged toward the rotary valve 104 by a relief spring 136 interposed between the movable magnetic body 124 and the movable magnetic body 124. It moves back and forth as the body 124 moves back and forth. In addition, a communication groove 138 is formed on the side surface of the relief valve 134 so as to connect a discharge side of an orifice 140 described later and a piston chamber 139 of the low pressure accumulator piston 118.

Reference numeral 140 is an orifice communicating with the high pressure chamber 112, and opening / closing control is performed according to the forward / backward movement position of the relief valve 134. 142 is a magnetic frame made of a ferromagnetic material fixed to a fixing member (not shown) on the outside of the housing, and has extremely narrow air gaps X and Y in the first portion 82a and the third portion 82c of the housing. It is provided in a non-contact manner.

Reference numeral 144 is a solenoid coil wound around the magnetic frame 142. As shown in FIG. 13, the gap between the tip 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 have a predetermined value L2. The relationship between the gap distance 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 body 124 comes to the most retracted position (hereinafter referred to as the first control position), the annular groove 132 of the spool 130.
Is located in the rotary valve 104, the high pressure chamber 112
And the suction passage 110 are cut off, and at the same time, the orifice 140
Becomes 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 the 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 between the high pressure chamber 112 and the suction passage 110. To communicate. In this state, the hydraulic pressure in the high pressure chamber 112 is equal to the suction passage 110.
It will be in a free state, which will be described later.

Further, the movable magnetic body 124 contacts the first positioning member 126 at the most forward position 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). When it moves to a position (hereinafter, referred to as a third control position), the relief spring 136 contracts and the tip of the relief valve 134 keeps closing the orifice 140, while the annular groove 132 of the spool 130 and the high pressure chamber 112. Since it moves forward to a position where it does not communicate, the high pressure chamber 112 and the suction passage 110 are disconnected. In this state,
Since the hydraulic pressure in the high-pressure chamber 112 is not released, the lock state will be described later.

The relief valve 134 is the orifice 1
When the opening / closing operation of the valve 40 is performed, the balance between the hydraulic pressure of the high pressure chamber 112 and the spring force f2 of the relief spring 136 exerts a function as a poppet valve to smoothly perform the opening / closing operation. Then, when the current is not 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 magnet, 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 magnetic gaps X, Y, and Z are used to magnetize. A path is formed, whereby a 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 (that is, f1 <F1 <
f1 + f2) is generated to move the movable magnetic body 124 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, the first portion 82a and the third portion 82c of the housing 82, the first positioning member 126, the 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 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 is moved 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 140, and in the free state the characteristic shown in the characteristic B of FIG. In the locked state, the characteristic shown in the characteristic C of FIG. 12 is obtained. Further, since the magnetic resistance due to the air gap is reduced, the movable magnetic body 124 can be efficiently driven, 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, while the cam 88 of the hydraulic pump shown in FIG.
In 4, the cam is formed integrally with the housing.
Further, the retainer 114 of FIG. 13 has a different shape 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 that is a first portion of a housing that is rotatably supported by an input shaft 150 via a shaft 4, and is formed at a side end of the first portion 152. .. Reference numeral 158 denotes a second portion of the housing made of a magnetic material, 160 denotes a third portion of the housing made of a non-magnetic material, and 162 denotes a fourth portion of the housing made of a magnetic material. The four parts are continuously provided and integrated by a connecting screw or welding (not shown).

A cam surface 164 similar to the cam shown in FIG. 2 is formed inside the first portion 152, and, for example, five cam peaks and five cam valleys are alternately formed. 166 is
It is a rotor that is spline-fitted to the input shaft 150, and has a plurality of plunger chambers 168 formed along the circumferential direction. Similar to the first embodiment, the number of plunger chambers 168 is determined by a predetermined relationship based on the number Nc of cam peaks provided on the cam surface 164, and is 9 for five cam peaks.
Plunger chambers 168 are formed at equal intervals.

The plunger 170 is housed in each plunger chamber 168 so as to be movable back and forth via a return spring 172, 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,
Similar to the first embodiment, the suction / discharge hole 17
4, a plurality of suction ports 178 and discharge ports 180 are alternately formed. The suction ports 178 communicate with the low pressure suction passages 182, and the discharge ports 180 are connected to the high pressure chambers 18.
It communicates with 4. Then, the rotor 166 and the rotary valve 176 rotate relative to each other, and the plunger 170 moves back and forth along the cam peaks and the cam troughs of the cam surface 164, so that each intake / discharge hole 174 and the intake port 178 and the discharge port 180 are connected. The operation of the intake and discharge stroke is performed.

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

Reference numeral 198 denotes an annular movable magnetic body made of a ferromagnetic material, which is disposed inside the third portion 162 and is movable in a direction parallel to the central axis Q. The return spring is not shown. By rotary valve 1
Biased away from 76. Reference numeral 200 denotes an annular positioning member made of a magnetic material, which is fixed to the side end of the second portion 158 of the housing. The distance between the movable magnetic material 198 and the retainer 194 sets the stroke of the movable magnetic material 198. The stroke L1 is set in the same way as in the second embodiment shown in FIG.
When 98 comes to the most retracted position where it abuts on 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 fixedly attached to the movable magnetic body 198 and operates integrally with the spool. The tip of the spool 202 is inserted into a spool insertion hole communicating with the high pressure chamber 184 formed in the rotary valve 176. Furthermore, the spool 202
An annular groove 204 is formed at the peripheral end portion of the control valve, and the opening / closing between the high pressure chamber 184 and the low pressure suction passage 182 is switched and controlled in accordance with the position where the spool 202 moves back and forth together with the movable magnetic body 198.

Reference numeral 206 denotes a relief valve movably supported by the other end of the movable magnetic body 198 so as to be urged toward the rotary valve 176 by a relief spring (not shown) interposed between the movable magnetic body 198 and the movable magnetic body 198. While moving, the movable magnetic body 198 moves back and forth as it moves back and forth. or,
A communication groove 208 is formed on a side surface of the relief valve 206 to connect a discharge side of an orifice 210, which will be described later, and a low-pressure housing inner chamber.

An orifice 210 communicates with the high-pressure chamber 184, and opening / closing control is performed according to the forward / backward movement position of the relief valve 206. Reference numeral 212 is a magnetic frame made of a ferromagnetic material fixed to a fixing member (not shown) on the outside of the housing, and has extremely narrow air gaps X and Y in the second portion 158 and the fourth portion 162 of the housing. It is provided in a non-contact manner.

Reference numeral 214 is 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 member 198 is at the most retracted position is designed to have a predetermined value L2, and the positioning is performed as described above. The relationship between the gap distance 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 reaches the most retracted position (hereinafter referred to as the first control position), the annular groove 204 of the spool 202 is formed.
Is located in the rotary valve 176, the high pressure chamber 184
And the suction passage 182 are blocked, and at the same time, the orifice 210
Becomes 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 the distance L2 against 1 (hereinafter referred to as the second control position), the relief valve 2
The front end of 06 blocks the orifice 210, and at the same time, the annular groove 204 of the spool 202 is closed by the high pressure chamber 184 and the suction passage 18.
Communicate between the two. In this state, the hydraulic pressure of the high pressure chamber 184 is lost in the suction passage 182, so that the free state described later is obtained.

Further, against the spring force f1 + f2 (the spring force of the relief spring is f2) of the return spring and the relief spring (not shown), the movable magnetic body 198 comes into contact with the positioning member 200 at the most forward position. When the relief valve 20 is moved to the position (hereinafter, referred to as a third control position), the relief spring contracts and the relief valve 20
The tip of 6 remains blocked with the orifice 210,
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 high pressure chamber 184 and the suction passage 182 are blocked. In this state, the high pressure chamber 184
Since the internal hydraulic pressure is not released, the lock state will be described later.

The relief valve 206 is the orifice 2
When opening and closing 10, the balance between the hydraulic pressure of the high pressure chamber 184 and the spring force f1 of the relief spring exerts a function as a poppet valve, and the opening and closing operation is performed smoothly. Then, if the current is not supplied to the solenoid coil 214, the movable magnetic body 198 can be set to 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 a 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 through Z, and thereby a magnetic force F1 (that is, f1 <F1 <f1 + f2) that is 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 is generated, and the movable magnetism is generated. The body 198 is moved to the second control position.

In order to move the movable magnetic body 198 to the third control position, the solenoid coil 214 has 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 portion 158 and fourth portion 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, which makes the magnetic force F2 stronger than the spring force f1 + f2 of the return spring and the relief spring (that is, f1 + f2 <
F2) is generated 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 in the characteristic C of FIG. 12 is obtained. Further, since the magnetic resistance due to the air gap is reduced, the movable magnetic body 198 can be efficiently driven, the size of the solenoid coil can be reduced, and the power consumption can be reduced.

[0072]

As described above, according to the present invention, the joint constituent member is a part of the magnetic circuit, and the magnetic attraction force is directly generated between the joint constituent member and the movable magnetic body. Since the magnetic frame fixed to the non-rotating third member and the magnetic circuit in the joint are magnetically coupled through the radial gap having excellent dimensional stability, the joint and the magnetic frame are not connected to each other. Even if the positional relationship in the axial direction changes a little, it is possible to suppress the change in the magnetic attraction force acting on the movable magnetic body, and it is possible to perform delicate control by the current flowing through the solenoid coil.

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

[Brief description of drawings]

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

FIG. 2 is a perspective view showing the 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 of plungers.

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

FIG. 7 is an explanatory diagram showing 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 the operation during torque transmission.

FIG. 9 is a cross-sectional view showing a cam and a plunger portion developed in a straight line in order to further explain an operation at the time of transmitting torque.

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

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

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

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

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

FIG. 15 is an explanatory diagram for explaining a problem of the conventional technique.

[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; suction / discharge hole 34; rotary Valve 34a; Cutout 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; Second spool 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; Howe 86,156; Spline joint 88; Cam 89,164; Cam surface 94,166; Rotor 96,168; Plunger chamber 98,170; Plunger 100,172; Return spring 102,174; Suction / discharge hole 104,176; Rotary. Suction ports 108, 180; Discharge ports 110, 182; Suction passages 112, 184; High pressure chambers 114, 186; Retainers 118, 192; Accumulator pistons 124, 198; Movable magnetic bodies 130, 202; Spools 132, 182. 204; annular groove 125; return spring 126, 128, 200; positioning member 134, 206; relief valve 138, 208; communication groove 139; piston chamber 136; relief spring 140, 210; orifice 142, 21 2; magnetic frame 144, 214; solenoid coil 152, 158, 160, 162; first to first housing
Fourth portion 190; fixing member X, Y, Z; air gap

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[Procedure amendment]

[Submission date] July 17, 1992

[Procedure Amendment 1]

[Document name to be corrected] Drawing

[Name of item to be corrected] Fig. 4

[Correction method] Change

[Correction content]

[Figure 4]

Claims (2)

[Claims] 1. A hydraulic pump provided on first and second rotary shafts which are relatively rotatable, and driven by differential rotation of the first and second rotary shafts, and pressure oil of the hydraulic pump is controlled. Control valve and an actuator that operates the control valve in response to an external signal, and hydraulic power for transmitting torque according to the rotational speed difference between the first and second rotating shafts and the external control signal. In the transmission joint, it is fixed to a non-rotating third member, is held in a concentric and non-contact state with the joint, and through a radial gap between the joint and the member constituting the actuator. A magnetic frame that is magnetically coupled, a solenoid coil that is provided integrally with the magnetic frame, and a joint component that forms a magnetic path with the magnetic frame and that moves in the joint in the axial direction. It is stored as much as possible And the control valve, which is magnetically coupled to the joint component via an axial gap and generates an axial magnetic attraction force with the joint component when the solenoid coil is energized. And a non-magnetic member that is a part of a container that holds the oil tightness while preventing a short circuit of the magnetic circuit in the joint, and electrically and mechanically from the outside of the joint. A hydraulic power transmission joint, which controls the control valve in a non-contact manner. 2. The hydraulic power transmission joint according to claim 1, wherein at least one of the N-pole and S-pole magnetic poles of the magnetic frame does not have a non-magnetic member interposed in the radial gap portion. A hydraulic power transmission joint characterized by forming a magnetic circuit.