JP2001227641A - Shift operation assistor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a shift operation assistor miniaturized and reduced in cost with simple structure. SOLUTION: A power cylinder part 2 has a piston 5, a piston rod 6 and a cylinder body 10. A control valve 3 has an operating spool part 7 constituted by arranging valve spools 71a, 71b opposedly and interposing a pin 76, plates 73a, 73b and a spacer between them. The pin 7 is connected to a change lever 9. The valve spools 71a, 71b abut on the plates 73a, 73b with air pressure supplied from a compressed air source to air chambers 25a, 25b, and hold a neutral position during non-operation. When the pin 76 moves in one direction, high pressure air is led into a working pressure chamber 26 on that side, while low pressure air is led into the other to make the cylinder body 10 follow the displacement of the pin 76.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change operation booster mounted on a vehicle such as an automobile, and more particularly to an improvement thereof.

[0002]

2. Description of the Related Art In conventional vehicles, particularly buses and trucks having a large transmission, an actuator that uses fluid pressure (particularly air pressure) is incorporated in a gear shift operation booster, and a smooth gear shift is performed with a light operating force of a change lever. You can operate it.

[0003] This type of speed change operation booster usually includes a power cylinder portion, a control valve mechanism portion, and an operation rod whose end is connected to a change lever side. The power cylinder section includes a cylinder body, a piston slidably disposed within the cylinder body, and a piston for dividing the cylinder body into two pressure chambers; A hollow piston rod connected to the shift lever side of the transmission.
The control valve mechanism is disposed in the hollow piston rod, and is opened and closed by the operation rod slidably disposed in the piston rod.

[0004] High-pressure air is supplied to one of the pressure chambers and low-pressure air is supplied to the other of the pressure chambers via the valve mechanism by a relative displacement between the operation rod and the piston rod by operating the change lever. And, together with the piston, the piston rod is made to follow the displacement caused by the operation of the operating rod, so that the light operating force of the change lever is boosted to rotate the shift lever of the transmission. Is operated.

[0005] However, the conventional speed change operation booster has the following problems. (A) Since the housing of the booster and the shift lever of the transmission are separate structures, the structure is complicated and large.

(B) Since the operating points of the operating force (output) to the shift lever of the transmission of the booster and the shift command operating force (input) from the change lever are the same, (I) The operation stroke of the change lever cannot be changed. Therefore, the operability is poor. (Ii) There is no degree of freedom in mounting the booster to the transmission, and the vehicle mountability is poor.

(C) Further, since the power cylinder and the control valve of the booster are integrated, the operation stroke of the speed change operation lever cannot be changed as described above. Therefore, the operability is poor. (Ii) There is no degree of freedom in mounting the booster to the transmission, and the vehicle mountability is poor.

For this reason, as shown in FIG. 6, the shift command operating force transmitted from the shift command operating means via the shift command operating force transmitting means is boosted to shift the shift lever 1 of the transmission.
In order to solve the above-mentioned problem, the speed change operation booster 101 operated at 04 is configured as follows.

A cylinder main body 110 of the power cylinder 102 of the speed change operation booster 101 is integrally formed with or disposed on the shift lever 104, and is slidably disposed within the cylinder main body 110. Piston 1
The output shaft end 05 is fixed to the main body of the transmission or a vehicle body to which the transmission main body is fixed via a piston rod 106 so that the output shaft end does not move in the rotation direction of the shift lever 104. I have.

The shift operation booster 101 supplies and discharges high-pressure air to and from two pressure chambers 111a and 111b divided by a piston 105 in the cylinder body 110 based on the shift command operation force. The control valve 103 includes a shift command operating force transmitting unit, or the shift command operating force transmitting unit and the shift lever 1.
04 or one of the shift levers 104.

Further, the positions of the cylinder main body 110 and the control valve 103 are different from each other in the radial direction, the circumferential direction, or the axial direction of the rotation of the shift lever 104.

With such a configuration, for example, high-pressure air is supplied to the pressure chamber 111a and another pressure chamber 111a is supplied to the pressure chamber 111a.
b, low-pressure air is introduced into the power cylinder 10
The second cylinder body 110 moves with respect to the transmission body, and the shift lever 104 rotates to perform a shift operation.

Further, the position where the command operation force from the change lever acts on the shift lever 104 can be changed to the position where the power cylinder 102 acts. Further, the control valve 103 for controlling the operating pressure of the high-pressure air of the power cylinder 102 according to a command operation stroke of the change lever is provided between the change lever and the shift lever 104 of the transmission. ing.

[0014]

However, even such a conventional speed change operation booster has the following problems. (A) In order to secure the non-operation neutral position of the valve spool 107, the spring receiving member 12 is attached to the end of the valve spool 107.
The arrangement of the springs 130 and 9a, 129b complicates the structure and increases the size of the control valve 103. (b) Since it is constituted by one valve spool 107, for example, when the valve on one pressure chamber 111a side is operated, the valve on the opposite side also moves. In this case, in particular, it is necessary to prevent the supply valve 127b on the opposite side from being opened, and accordingly, the length of the valve sleeve 107 becomes longer, the overall length of the control valve 103 becomes longer, and the supply valve 127b becomes longer.
a, 127b have a problem in durability. (c) Since the control valve 103 is configured by inserting two valve sleeves 108 from both sides of one valve spool 107, if the concentricity of the two valve sleeves 108 is poor, the valve spool 107 moves. It may be worse.

The present invention has been made in view of the above circumstances, and has as its object to provide a speed change operation booster that has a simple structure, can reduce the size of the device itself, and can reduce the cost.

[0016]

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above-mentioned problem, and operates a shift lever of a transmission by boosting a shift command operating force from a shift command operating means. In the speed change operation booster, the speed change operation booster includes a cylinder body, a piston slidably disposed in the cylinder body, and dividing the inside of the cylinder body into two pressure chambers; A power cylinder portion comprising a piston rod whose end is fixed to the transmission body side, a pair of control means which are individually configured and arranged so as to face each other so that their axes overlap each other, A pressing member that is interposed between the pair of control means and is connected to the shift command operation means and operates the pair of control means, and a control valve including a valve body including the pair of control means therein. Prepared, said The Linda main body and the valve main body are integrally formed or arranged on a shift lever of a transmission, and the control means is actuated by the pressing member, so that one of the pressure chambers is provided through the valve main body. High pressure air,
The transmission is operated by introducing low-pressure air into the other of the pressure chambers and causing the cylinder body to follow the displacement of the pressing member.

In the above construction, the control valve includes a pair of control means, a pair of valve spools disposed so as to face each other such that their axes overlap each other, and a stopper for regulating a minimum separation distance between the valve spools. The control valve may be configured as a spool valve control valve including a pair of valve sleeves in which the pair of valve spools are slidably disposed.

The spool valve type control valve includes a supply valve provided outside each of the pair of valve spools in the axial direction and an exhaust valve provided inside the supply valve. The valve body is provided outside a portion corresponding to each of the supply valves. An air chamber respectively communicating with a compressed air source, an exhaust chamber communicating with the atmosphere inside a portion corresponding to each of the exhaust valves, and a power source corresponding to a portion between the supply valve and the exhaust valve. An operating pressure chamber communicating with each of the two pressure chambers of the cylinder portion is provided, and the neutral position of the valve spool during non-operation can be maintained by the air pressure of the air chamber.

The valve spool may be made of resin.

In the above configuration, the control valve includes the pair of control means, a pair of valve seat members disposed so as to face each other such that their axes overlap each other, and a first valve provided on each of the valve seats of the valve seat members. A pair of valve members biased in a direction to be seated by a spring, a pair of valve lifters biased in a direction away from the pair of valve members by a second spring, and a minimum separation distance between the valve lifters. The control valve can be configured as a one-valve, two-seat control valve including a stopper.

In the one-valve, two-seat control valve, a supply valve is constituted by a valve seat of the valve seat member and the valve member, and an exhaust passage is formed by an exhaust passage opening at an end face of the valve lifter and the valve member. An air chamber communicating with a compressed air source on the outside in the axial direction from the valve member, and an exhaust chamber communicating with the atmosphere while communicating with the exhaust valve through an inner diameter hole of the valve lifter between the pair of valve lifters; An operating pressure chamber may be provided between the valve lifter and the valve seat member to communicate with the two pressure chambers of the power cylinder unit.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a speed change operation booster according to the present invention will be described with reference to the drawings. FIGS. 1 to 5 show a shift operation booster according to a first embodiment of the present invention, and FIGS. 6 to 8 show a shift operation booster according to a second embodiment. First, a shift operation booster 1 according to a first embodiment of the present invention will be described with reference to FIGS.

A schematic configuration of the speed change operation booster 1 will be described with reference to FIG. As shown in the figure, the speed change operation booster 1 includes a power cylinder unit 2, a control valve 3, and a shift valve of a transmission T integrally formed with the power cylinder unit 2 and one end of which has a shift shaft Ta and a main body Tb. The shift lever 4 is connected to the shaft Ta.

The power cylinder section 2 includes a piston 5,
It has a piston rod 6 and a cylinder body 10. The piston 5 is connected to a main body T of the transmission T via a piston rod 6.
It is fixed to the b side. In addition, the control valve 3 includes an operation unit 7
(A pair of control means). The operation unit 7 is connected to a change lever 9 via a link mechanism 8. The shift lever 4 has one end connected to a shift shaft Ta of the transmission T. In the first embodiment, the operation unit 7 is provided with a valve spool 71 as described later.
a, 71b and valve sleeves 72a, 72b,
In the second embodiment, valve lifters 81a, 81
b, valve seat members 82a and 82b, and valve members 83a and 83b. That is, the control valve 3 of the first embodiment is a spool valve type, and the second embodiment is a one-valve two-seat type.

When the operation unit 7 is displaced by operating the change lever 9, the compressed air is supplied to and discharged from the power cylinder unit 2 by the operation of the control valve 3 to which the compressed air is supplied. The shift lever 4 is operated while following the displacement of the operation unit 7 via the cylinder body 10 of the transmission T to rotate the shift shaft Ta of the transmission T.

Next, the components of the speed change operation booster will be described with reference to FIGS. As shown in FIG. 2, a cylinder 10a is formed in the cylinder body 10 of the power cylinder unit 2. The cylinder 10a is divided into a pressure chamber (A) 11a and a pressure chamber (B) 11b by a piston 5 slidably disposed inside. A piston rod 6 as an output shaft, which is slidably penetrated through the cylinder body 10, is fixed to the piston 5. A control valve 3 is disposed above the power cylinder unit 2 (on the side of the shift shaft Ta of the transmission T) such that its spool axis is parallel to the cylinder axis of the power cylinder unit 2.

As shown in FIG. 2 or FIG. 4, a valve hole is formed in the valve main body 20 of the control valve 3, and the operation portion 7 is disposed in the valve hole. In this operation unit 7, valve spools 71a and 71b each having a small diameter at both ends and having two steps are supported slidably while each end and each large diameter portion are guided by valve sleeves 72a and 72b. I have. The valve spools 71a and 71b have the same shape, and are arranged to face each other such that the respective spool axes overlap with each other. This concentricity need not be high precision.

As shown in FIG. 2, FIG. 4 or FIG. 5, plates 73a, 73 are provided between valve spools 71a, 71b.
3b and a U-shaped spacer 74 (stopper) are provided. The plates 73a and 73b are provided with holes larger than the small diameter portions of the valve spools 71a and 71b, respectively, and at the assembly stage, the valve spools 71a and 71b
Are respectively inserted. By this insertion, each end face of the large diameter portion of the valve spools 71a, 71b is
a and 73b are in contact with the outer surfaces, respectively. Spacer 74
Is inserted between the plates 73a and 73b to keep the distance between the plates 73a and 73b constant.
Therefore, the valve gap is stabilized, and the durability of the valve is improved.

As shown in FIG. 2 or FIG. 4, after inserting the valve spools 71a and 71b, they are sealed with a plug 75 using a ring-shaped seat member having a small seat diameter. The plug 75 is further fixed by the cover 29 of the power cylinder unit 2, thereby preventing the plug 75 from being removed.

As shown in FIG. 4, an exhaust chamber 21 is provided at the position where the plate 73 is disposed. The exhaust chamber 21 communicates with the atmosphere through an exhaust port 22 provided in the valve body 20. I have. The exhaust port 22 is covered with a shielding plate 23 so that water or the like does not enter.

As shown in FIG. 2, the valve body 20 at both ends of the operating portion 7 is connected to the side end of the shift lever 4 through an air passage 24 formed inside the shift lever 4. Air chamber (A) 25 communicating with the connected compressed air source
a, an air chamber (B) 25b is formed.

As shown in FIG. 2 or FIG.
Compressed air is supplied and discharged between the air chamber (A) 25a and the air chamber (B) 25b and the exhaust chamber 21 by the operation of the operation unit 7, and the power cylinder Pressure chamber (A) 11a and pressure chamber (B) 1 of part 2
Working pressure chamber (A) 26a, working pressure chamber (B) communicating with 1b
26b are respectively formed.

On both sides of the valve spools 71a and 71b of the operating portion 7 of the control valve 3, two large-diameter and small-diameter stages are formed, and a small-diameter portion includes a ring-shaped seat member having a small seat diameter. The valve (A) 27a and the supply valve (B) 27b are provided with an exhaust valve (A) 28a and an exhaust valve (B) 2 having a large-diameter ring-shaped seat member in the large-diameter portion.
8b are provided respectively.

That is, between the air chamber (A) 25a and the working chamber (A) 26a, a supply valve (A) 27a which is closed when not operating is provided with the working chamber (A) 26a and the exhaust chamber. 21 and an exhaust valve (A) 28a which is open when not in operation.
A non-operating closed supply valve (B) 27b is provided between the air chamber (B) 25b and the working chamber (B) 26b between the working chamber (B) 26b and the exhaust chamber 21. Is formed with an exhaust valve (B) 28b which is open when not in operation.

Air chamber (A) 25a, air chamber (B) 25b
Are connected to a compressed air source (not shown) via the air passage 24 (see FIG. 2), so that the compressed air acts on the small-diameter side ends of the valve spools 71a and 71b. For this reason, the valve spools 71a and 71b are urged in a direction in which they contact the plate 73. Therefore,
The inactive neutral positions of the valve spools 71a and 71b are held.

As shown in FIG. 2, FIG. 4 or FIG. 5, the valve spools 71a, 71b are held at the inactive neutral position by the air pressure of the air pressure chamber (A) 25a or the air chamber (B) 25b and the plate 73. Between the pins 76 (pressing member)
Are arranged so as to be sandwiched. This pin 76
It is sandwiched between the valve spools 71a and 71b with a small gap. As described above, since the spool can be almost directly positioned with respect to the valve sleeves 72a and 72b, the supply valve (A) 27a, the supply valve (B) 27b, the exhaust valve (A) 28a, and the exhaust valve ( B) 28
The valve clearance of b becomes more accurate.

In the exhaust chamber 21 formed in the valve body 20 corresponding to the pin 76 between the valve spools 71a and 71b, as shown in FIG.
6, an input transmission member 40 guided by being sandwiched and guided by a U-shaped guide member 41 and a guide cover 42 is provided, and a link is provided from the change lever 9 via the input transmission member 40. An input operated via the mechanism 8 is transmitted to the operation unit 7 (see FIG. 1). Also, as shown in FIG. 4 or FIG.
The base of the input transmission member boot 43 is sandwiched and fixed between the press-formed mounting plate 44 and the guide cover 42. With this mounting structure, the structure for holding the boot 43 can be simplified.

As shown in FIG. 3, the end 6a of the piston rod 6 of the power cylinder 2 is provided with two bearing members 15a and 15b which are swingably fixed, and a screw whose length is adjustable. The transmission main body (or the transmission main body) is rotated via a rotation lever 16 having a mechanism such that the lever rotation center point is located on the swinging neutral axis 17 of the shift shaft Ta of the transmission T. (Fixed vehicle body) Tb.

Next, the operation of the speed change operation booster 1 will be described with reference to FIGS. The control valve 3 is
In the inoperative position shown in FIG. 2, the air from the source of compressed air is
The air chamber (A) 25a and the air chamber (B) 2 of the valve body 20
5b, and the pressure chamber (A) 11a and the pressure chamber (B) 11b of the power cylinder unit 2 are connected via the exhaust valve (A) 28a, the exhaust valve (B) 28b, and the exhaust chamber 21, Open to the atmosphere and inactive.

When the change lever 9 is operated and the input transmission member 40 moves the operation spool 71b rightward in FIG. 2 via the pin 76, first, the exhaust valve (B) 28b is closed, Next, the supply valve (B) 27b is opened. Then, the air supplied to the air chamber (B) 25b is introduced into the pressure chamber (B) 11b of the power cylinder unit 2 through the supply valve (B) 27b and the working pressure chamber (B) 26b. Then, the air pressure tries to push the piston 5 to the left. However, the piston 5 has the end 6a of the piston rod 6 at the rotation lever rotation center point via the rotation lever 16. Since the piston 5 is fixed to the transmission main body Tb, the piston 5 does not move in the axial direction of the power cylinder section 2 but is moved by the introduced air pressure to the cylinder main body 10b.
Moves to the right in FIG.

At this time, the pressure chamber (A) 11a of the power cylinder unit 2 has a small volume, but the air in the pressure chamber (A) 11a is exhausted by the exhaust valve (A) 28a and the exhaust chamber 21. And the air is exhausted to the atmosphere through the exhaust port 22, so that no pressure is generated in the pressure chamber (A) 11a.
(At this time, the supply valve (A) 27a is closed and the exhaust valve (A) 28a remains open.)

The cylinder body 1 of the power cylinder unit 2
When 0 moves rightward, the valve body 20 of the control valve 3 moves in the direction of closing the supply valve (B) 27b and opening the exhaust valve (B) 28b with respect to the valve spool 71b. The valve spool 7 operated by a lever 9
The valve body 20 rotates so as to follow the stroke of 1b, and the supply valve (B) 27b and the exhaust valve (B)
28b are both kept closed. The shift shaft Ta is rotated by the rotation of the cylinder body 10 of the power cylinder portion 2 and the shift lever 4, so that the shift operation of the transmission T is performed.

Since the air pressure introduced into the working chamber (B) 26b and the air pressure in the air chamber (B) 25b act on the valve spool 71b so as to press leftward, the acting force is reduced. It acts as a reaction force to the operation input via the pin 76.

The cylinder body 1 of the power cylinder section 2
With the rotation of 0, the axial direction of the cylinder portion 2 is inclined, and accordingly, the axial direction of the piston 5 is also inclined. At this time,
The rotating lever 16 slidably connected to the end 6a of the piston rod 6 of the piston 5 is provided with a transmission body Tb.
The piston 5 rotates about the rotation center point of the lever, so that the position of the piston 5 with respect to the transmission main body Tb is the same as that at the time of non-operation, and the position of the piston 5 in the axial direction of the power cylinder portion 2 is In response to the tilt, it just turns.

When the shift operation of the transmission T is completed and the hand is released from the change lever 9 in the shift position, the operation input to the valve spool 71b becomes 0 (zero).
Therefore, the valve spool 71b is returned to a position where it comes into contact with the plate 73 by the action force of the air pressure of the working chamber (B) 26b and the air chamber (B) 25b, returns to the inoperative position, and returns to the supply valve ( B) 27b is in the closed position, and the exhaust valve (B) 28b is in the open position. Then, the air that has been introduced into the pressure chamber (B) 11b of the power cylinder unit 2 is exhausted by the exhaust valve (B) 28b, the exhaust chamber 21, and the exhaust port 22.
, The transmission T is kept in the shift position because no force acts to return the transmission T to the neutral position.

Next, in order to return the transmission T to the neutral position, when the valve spool 71a is moved leftward through the pin 76 by operating the change lever 9,
The exhaust valve (A) 28a is closed, and the supply valve (A) 27a is open. Then, the air chamber (A) 25a of the valve body 20
Is introduced into the power cylinder unit 2 via the supply valve (A) 27a and the working pressure chamber (A) 26a.
Into the pressure chamber (A) 11a of the cylinder body 1
0 rotates to the left and returns to the neutral position. Even when the change lever 9 is operated from the neutral position to move the valve spool 71a to the left via the input transmission member 40, the same operation as described above is performed.

In FIG. 2, the operation stroke of the control valve 3 to the input transmission member 40 is different from the stroke of the power cylinder portion 2 by the transmission of the power cylinder portion 2 and the input transmission member 40 to the transmission. It can be changed in proportion to the ratio of the respective distances L1 and L2 of T from the shift axis Ta. That is, according to FIG.
The operation stroke of the input transmission member 40 is L2 / L1 with respect to the stroke of the power cylinder unit 2,
Can be smaller.

In this embodiment, the position of the input transmission member 40 acting on the shift lever 4 and the position of the power cylinder portion 2 acting on the shift lever 4 are different. If the respective distances L1 and L2 of the portion 2 and the input transmission member 40 from the shift shaft Ta of the transmission T are equal, the respective operating positions on the shift lever 4 are set to the same position. Can be.

The guide member 41 and the guide cover 42
May be formed of a material having lubricity, a material having a low friction coefficient μ, a material having a high hardness, or the like. With this configuration, the sliding resistance of the input transmission member 40 can be reduced with a simple structure, so that the change lever operating force can be transmitted reliably and accurately. Further, the valve spool 71a,
71b may be formed of resin for weight reduction and cost reduction.

Next, a speed change operation booster according to a second embodiment of the present invention will be described with reference to FIGS.
In the description of the shift operation booster 1 of the present embodiment, the same members as those of the shift operation booster 1 of the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted.

FIG. 6 shows the components of the speed change operation booster 1.
This will be described with reference to FIGS. As shown in FIG. 6, the cylinder 1 is provided in the cylinder body 10 of the power cylinder section 2 '.
0a is formed. This cylinder 10a is provided with a pressure chamber (A) by a piston 5 slidably disposed inside.
11a and a pressure chamber (B) 11b. A piston rod 6 as an output shaft, which is slidably penetrated through the cylinder body 10, is fixed to the piston 5. The neutral position of the piston 5 is maintained by the detent mechanism 8.
6. A control valve 3 'is disposed above the power cylinder 2' (on the shift shaft Ta side of the transmission T) so that its axis is parallel to the cylinder axis of the power cylinder 2 '.

As shown in FIG. 6 or 7, a valve hole is formed in the valve main body 20 of the control valve 3 ', and the operating portion 7 (see FIG. 1) is disposed in the valve hole. I have. In the operation section 7 in the present embodiment, valve lifters 81a and 81b each having a small diameter at both ends and having a two-step diameter are slidably supported while their large diameter portions are guided by valve seat members 82a and 82b. . The valve lifters 81a, 81
“b” has the same shape, and is arranged to face each other such that the respective axes overlap each other. This concentricity need not be high precision.

As shown in FIG. 6, FIG. 7, or FIG. 8, plates 73a, 73b are provided between the valve lifters 81a, 81b.
b and a U-shaped spacer 74 (stopper) are provided. The plates 73a and 73b are provided with holes larger than the small-diameter portions of the valve lifters 81a and 81b, respectively. In the assembling stage, the valve lifters 81a and 81b are respectively formed in the holes from outside. Inserted. With this insertion, the valve lifter 81a,
Each end surface of the large diameter portion of 81b abuts on the outer surface of each of the plates 73a and 73b. Spacer 74 is plate 7
3a, 73b, between the plate 73a,
The distance 73b is kept constant. Therefore, the valve gap is stabilized, and the durability of the valve is improved.

The valve lifters 81a, 81b are provided with exhaust holes 81c (exhaust passages) extending in the axial direction.
The exhaust hole 81c is open to the exhaust chamber 21 provided at the position where the plate 73 is provided. The exhaust chamber 21 communicates with the atmosphere via an exhaust port 22 provided in the valve body 20.

As shown in FIG. 6, FIG. 7 or FIG. 8, the end surfaces of the large diameter portions of the valve lifters 81a and 81b and the valve seat member 82
Springs 84a, 84b (second springs) are interposed in contact with the valve seats 82c (valve seats) facing outward in the axial direction of the a, 82b. Therefore, the valve lifters 81a and 81b are pressed against the plates 73a and 73b by the urging forces of the springs 84a and 84b.

When the valve lifters 81a and 81b move against the urging forces of the springs 84a and 84b, the small diameter portions of the valve lifters 81a and 81b are moved to the valve seat members 82a and 82b.
The vehicle travels through the valve seat 82c of FIG.

The valve members 83a and 83b are disposed on the opposite sides of the valve holes of the valve body 20 with the valve seats 82c of the valve lifters 81a and 81b and the valve seat members 82a and 82b interposed therebetween, and springs 85a and 85b ( The first spring (the first spring) abuts the end surface in contact with the valve seat 82c. A spring 84a is provided on the valve lifters 81a and 81b.
When only the urging force 84b is acting, the valve lifters 81a and 81b are separated from the valve members 83a and 83b (the inoperative neutral position). Valve lifters 81a, 81
b moves in a direction against the biasing force of the springs 84a and 84b, the valve lifters 81a and 81b
a, 83b, whereby the valve members 83a, 83b are pressed.
b moves away from the biasing force of the springs 85a and 85b and leaves. When the valve lifters 81a and 81b are returned to their original positions, the valve members 83a and 83b are also returned to their original positions and seated (non-operation neutral position). in this way,
The valve lifters 81a and 81b include valve members 83a and 83b.
Activate There is a gap between the outer surfaces of the valve members 83a and 83b and the inner surfaces of the valve seat members 82a and 82b, so that the valve members 83a and 83b move smoothly. A pin 76 (pressing member) is disposed between the valve lifters 81a and 81b so as to be held therebetween. The pin 76 is supported by the input transmission member 40 as in the first embodiment, and when the input transmission member 40 is stroked by operating a change lever, the pin 76 is moved to the valve lifter 81.
a, 81b are moved.

As shown in FIG. 6 or 7, after the valve lifters 81a, 81b and the valve members 83a, 83b are inserted, they are sealed with a plug 75. This plug 75 is further fixed by the cover 29 of the power cylinder unit 2.
This prevents the plug 75 from being removed.

As shown in FIG. 6, the valve body 20 at both ends of the operating portion 7 is connected to the side end of the shift lever 4 through an air passage 24 formed inside the shift lever 4. Air chamber (A) 25 communicating with the connected compressed air source
a, an air chamber (B) 25b is formed. Other structures are the same as those of the first embodiment.

Next, the operation of the speed change operation booster 1 will be described with reference to FIGS. The control valve 3 is
In the inoperative position shown in FIG. 6, the air from the compressed air source is:
The air chamber (A) 25a and the air chamber (B) 2 of the valve body 20
5b, and the pressure chamber (A) 11a and the pressure chamber (B) 11b of the power cylinder unit 2 are opened to the atmosphere through the exhaust holes 81c and the exhaust chamber 21 of the valve lifters 81a and 81b. Is inactive.

When the change lever 9 is operated and the input transmission member 40 moves the valve lifter 81b rightward in FIG. 6 via the pin 76, first, the valve lifter 81b presses the valve member 83b to release the valve. The member 83b is moved rightward, and thereby is separated. Valve member 83a,
When the valve 83b is unseated, the exhaust hole 81c of the valve lifter 81b is closed by the valve member 83b, so that the communication between the pressure chamber (B) 11b and the exhaust chamber 21 is cut off. On the other hand, the pressure chamber (B) 11b is
The air supplied to the air chamber (B) 25b is introduced into the pressure chamber (B) 11b of the power cylinder unit 2 'through the space between the valve seat 82c and the valve member 83b of the valve seat member 82b. You. That is, the valve member 83b and the valve lifter 81b
Is a working pressure chamber communicating with each pressure chamber of the power cylinder. Then, the air pressure tries to push the piston 5 to the left. However, the piston 5 has the end 6a of the piston rod 6 at the rotation lever rotation center point via the rotation lever 16. Since the piston 5 is fixed to the transmission body Tb, the piston 5 does not move in the axial direction of the power cylinder portion 2 ', and the cylinder body 10 moves rightward in FIG. 6 by the introduced air pressure.

At this time, the pressure chamber (A) 11a of the power cylinder section 2 'has a small volume, but the air in the pressure chamber (A) 11a is exhausted by the exhaust hole 81c, the exhaust chamber 21, and the exhaust chamber. As it is discharged to the atmosphere through the mouth 22,
No pressure is generated in the pressure chamber (A) 11a. In addition,
At this time, the valve member 83a is connected to the valve seat 8 of the valve seat member 82a.
Since the air chamber (A) 25a remains seated, the air supplied to the air chamber (A) 25a is not supplied to the pressure chamber (A) 11a.

When the cylinder body 10 of the power cylinder unit 2 'moves rightward, the valve body 20 of the control valve 3' shuts off the air supply to the pressure chamber (B) 11b with respect to the valve lifter 81b. , The valve body 20 rotates so as to follow the stroke of the valve lifter 81b by the operation from the change lever 9, and the air supply to the pressure chamber (B) 11b and the pressure chamber (B) ) 1
1b is kept in a state where neither air is discharged. The shift shaft Ta is rotated by the rotation of the cylinder body 10 of the power cylinder portion 2 and the shift lever 4, so that the shift operation of the transmission T is performed.

The air pressure introduced into the working chamber (B) 26b and the air pressure in the air chamber (B) 25b act on the valve lifter 81b so as to press to the left. It acts as a reaction force to an operation input via the pin 76.

With the rotation of the cylinder body 10 of the power cylinder portion 2 ', the axial direction of the cylinder portion 2' is tilted,
Accordingly, the axial direction of the piston 5 is also inclined. At this time, the rotation lever 16 pivotally connected to the end 6a of the piston rod 6 of the piston 5 rotates about the lever rotation center point attached to the transmission body Tb. The position of the piston 5 with respect to the transmission body Tb is the same as in the non-operation state, and at that position, the power cylinder 2 simply rotates in accordance with the axial inclination of the power cylinder 2.

When the shift operation of the transmission T is completed and the hand is released from the change lever 9 in the shift position, the operation input to the valve lift 81b becomes 0 (zero). 81b is the working chamber (B)
The pressure chamber 26B and the air chamber (B) 25b are returned to the position where they come into contact with the plate 73 by the air pressure of the air pressure, return to the inactive position, and the air supply to the pressure chamber (B) 11b is cut off. B) Air is discharged from 11b, and the air introduced into the pressure chamber (B) 11b of the power cylinder unit 2 is discharged from the exhaust hole 81b.
c, the exhaust gas is exhausted to the atmosphere via the exhaust chamber 21 and the exhaust port 22, but is held at the shift position because no force acts to return the transmission T to the neutral position.

Next, when the transmission T is returned to the neutral position, the valve lifter 81a is moved to the left through the pin 76 by operating the change lever 9, and the valve lifter 81a presses the valve member 83a. The valve member 83a is moved to the left, and thereby the user separates. Therefore, the air introduced into the air chamber (A) 25a of the valve body 20 passes between the valve seat 82c of the valve seat member 82a and the valve member 83a, and passes through the pressure chamber ( A) After being introduced into 11a, the cylinder body 10 rotates to the left and returns to the neutral position. By operating the change lever 9 from the neutral position, the valve lift 81a is controlled via the input transmission member 40.
Even when is moved to the left, the same operation is performed as described above.

[0068]

According to the present invention, there is provided a gear shift operation booster for boosting a gear shift command operating force from a gear shift command operating means to operate a shift lever of a transmission.
The speed change operation booster includes a cylinder body, a piston slidably disposed in the cylinder body, and a piston for dividing the inside of the cylinder body into two pressure chambers, and
A power cylinder portion having a piston rod whose end is fixed to the transmission body side; a pair of control means which are separately configured and arranged so as to face each other so that the shafts overlap each other; A pressing member interposed between the means and connected to the speed change command operating means for operating the pair of control means, and a control valve including a valve body containing the pair of control means, The cylinder main body and the valve main body are integrally formed or arranged on a shift lever of a transmission, and the control means is operated by the pressing member, so that the cylinder is connected to one of the pressure chambers via the valve main body. The high-pressure air is introduced into the other of the pressure chambers by introducing low-pressure air, and the transmission is operated by causing the cylinder body to follow the displacement of the pressing member. Shorten It durability can be improved it is also manufacturing cost can be reduced.

The control valve includes a pair of control means, a pair of valve spools disposed so as to face each other so that their axes overlap each other, a stopper for regulating a minimum separation distance between the valve spools, and a pair of the control means. When the control valve is configured as a spool valve control valve including a pair of valve sleeves slidably disposed therein, the structure of the control valve, particularly, the entire structure is simplified or simplified. In addition, there is no need to consider the concentricity of the valve sleeve, and the cost can be reduced. At the same time, the length of the valve sleeve can be reduced, and the size of the device can be reduced.

The spool valve control valve is provided with a supply valve on the outside of each of the pair of valve spools in the axial direction, and an exhaust valve on the inside thereof, and the valve body is provided on the outside of a portion corresponding to each of the supply valves. An air chamber respectively communicating with a compressed air source, an exhaust chamber communicating with the atmosphere inside a portion corresponding to each of the exhaust valves, and a power source corresponding to a portion between the supply valve and the exhaust valve. When an operating pressure chamber communicating with each of the two pressure chambers of the cylinder portion is provided, and the neutral position of the valve spool when not operated is maintained by the air pressure of the air chamber, particularly, the return spring of the valve spool is provided. Can be eliminated, the number of components can be reduced, the configuration can be simplified, and downsizing and cost reduction can be further promoted.

When the valve spool is made of resin, the weight of the apparatus can be reduced and the cost can be further reduced.

In the control valve, the pair of control means is seated by a first spring on a pair of valve seat members disposed so as to face each other such that their axes overlap with each other, and a respective valve seat of the valve seat member. A pair of valve members biased in the direction of
A one-valve, two-seat control valve comprising a pair of valve lifters urged in a direction away from the pair of valve members by a spring, and a stopper for regulating a minimum separation distance between the valve lifters. In addition, the structure of the control valve, in particular, the entire structure is simplified or simplified, and it is not necessary to consider the concentricity of the valve lifter, so that the cost can be reduced. At the same time, the size of the device can be reduced.

In the one-valve, two-seat control valve, a supply valve is constituted by a valve seat of the valve seat member and the valve member, and an exhaust passage is formed by an exhaust passage opening at an end face of the valve lifter and the valve member. An air chamber communicating with a compressed air source on the outside in the axial direction from the valve member, and an exhaust chamber communicating with the atmosphere while communicating with the exhaust valve through an inner diameter hole of the valve lifter between the pair of valve lifters; When the operating pressure chambers respectively communicating with the two pressure chambers of the power cylinder portion are provided between the valve lifter and the valve seat member, the configuration is made up of one valve, so that the configuration can be simplified. Since the valve itself does not slide with the adjacent parts, the durability can be improved.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram when a speed change operation booster of the present invention is mounted on a transmission.

FIG. 2 is a longitudinal sectional view showing a structure of a speed change operation booster according to the first embodiment of the present invention.

FIG. 3 is a bottom view of FIG. 2;

FIG. 4 is a longitudinal sectional view showing a structure of the speed change operation booster of FIG. 2 in a plane orthogonal to a section of the same figure.

FIG. 5 is a partial sectional view taken along line VV in FIG. 4;

FIG. 6 is a longitudinal sectional view showing a structure of a speed change operation booster according to a second embodiment of the present invention.

7 is a longitudinal sectional view showing a structure of the speed change operation booster of FIG. 6 in a plane orthogonal to a section of the same figure.

FIG. 8 is a partial sectional view taken along line VIII-VIII in FIG. 7;

FIG. 9 is a longitudinal sectional view showing the structure of a conventional speed change operation booster.

10 is a longitudinal sectional view showing a structure of the speed change operation booster of FIG. 9 in a plane orthogonal to the section of the same figure.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Transmission operation booster 2, 2 'Power cylinder part 3, 3' Control valve 4 Shift lever 5 Piston 6 Piston rod 6a End part 7 Operation part 8 Link mechanism 9 Change lever 10 Cylinder main body 11a Pressure chamber (A) 11b Pressure Chamber (B) 15a, 15b Bearing member 16 Rotating lever 17 Oscillating neutral axis 20 Valve body 21 Exhaust chamber 22 Exhaust port 23 Shielding plate 24 Air passage 25a Air chamber (A) 25b Air chamber (B) 26a Working pressure chamber ( A) 26b Working pressure chamber (B) 27a Supply valve (A) 27b Supply valve (B) 28a Exhaust valve (A) 28b Exhaust valve (B) 29 Cover 40 Input transmission member 41 Guide member 42 Guide cover 43 Boot 44 Mounting plate 71a, 71b Valve spool 72a, 72b Valve sleeve 73a, 73b Plate 74 Spacer 75 Plug 76 Pin 81a, 81b Valve lifter 81c Exhaust hole 82a, 82b Valve seat member 82c Valve seat 83a, 83b Valve member 84a, 84b, 85a, 85b Spring 86 Detent mechanism T Transmission Ta Shift shaft Tb Transmission body L1, L2 Distance

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3D040 AA22 AB02 AC17 AC33 AC42 AD01 AF08 AF24 3J067 AA02 AB13 AB14 AC01 BA56 DA03 DA07 DA52 DB03 DB14 FB63 FB83 GA04

Claims (6)

[Claims] 1. A gear shift operation booster for operating a shift lever of a transmission by boosting a gear shift command operating force from a gear shift command operating means, comprising: a cylinder main body; A piston slidably disposed in the body to partition the inside of the cylinder body into two pressure chambers, and the piston is attached;
A power cylinder portion having a piston rod whose end is fixed to the transmission body side; a pair of control means which are separately configured and arranged so as to face each other so that the shafts overlap each other; A pressure member interposed between the means, and connected to the shift command operation means, for actuating the pair of control means, and a control valve including a valve body having the pair of control means provided therein; The cylinder main body and the valve main body are integrally formed or arranged on a shift lever of a transmission, and the control means is operated by the pressing member, so that the cylinder is connected to one of the pressure chambers via the valve main body. A transmission operation booster, wherein the transmission is operated such that high-pressure air is introduced into the other of the pressure chambers and low-pressure air is introduced so that the cylinder body follows the displacement of the pressing member. 2. The control valve, wherein the pair of control means includes:
A pair of valve spools disposed to face each other such that their axes overlap, a stopper for regulating a minimum separation distance between the valve spools, and a pair of valves in which the pair of valve spools are slidably disposed. 2. A spool valve type control valve comprising a sleeve.
2. The speed change operation booster according to claim 1. 3. A control valve according to claim 1, wherein said spool valve type control valve is provided with a supply valve on the outside of each of said pair of valve spools in the axial direction, and an exhaust valve on the inside thereof, and said valve body has a portion corresponding to each of said supply valves. An air chamber communicating with the compressed air source on the outside, an exhaust chamber communicating with the atmosphere inside a portion corresponding to each of the exhaust valves, and a portion corresponding between the supply valve and the exhaust valve, 2 of the power cylinder part
An operating pressure chamber communicating with each of the two pressure chambers is provided,
3. The speed change operation booster according to claim 2, wherein the neutral position of the valve spool at the time of non-operation is maintained by the air pressure of the air chamber. 4. The speed change operation booster according to claim 2, wherein the valve spool is made of resin. 5. The control valve, wherein the pair of control means includes:
A pair of valve seat members disposed so as to face each other such that their axes overlap each other, a pair of valve members biased in a direction in which the respective valve seats of the valve seat members are seated by a first spring; A one-valve, two-seat control valve comprising a pair of valve lifters biased in a direction away from the pair of valve members by a spring, and a stopper for regulating a minimum separation distance between the valve lifters. The speed change operation booster according to claim 1. 6. The one-valve, two-seat control valve comprises a supply valve formed by a valve seat of the valve seat member and the valve member, and an exhaust valve formed by an exhaust passage opening at an end face of the valve lifter and the valve member. An air chamber communicating with a compressed air source outside the valve member in the axial direction, and an exhaust chamber communicating between the pair of valve lifters and the atmosphere through an inner diameter hole of the valve lifter. 6. The speed change operation booster according to claim 5, wherein an operating pressure chamber is provided between the valve lifter and the valve seat member to communicate with two pressure chambers of the power cylinder unit.