JPS60260742A - Servo valve - Google Patents

Abstract

PURPOSE:To easily manufacture a servo valve by assembling the servo valve and then adjusting each of restricting members which are screwed to both ends of said casing, whereby having the operating characteristics of the forward stoke and the reverse stroke of an input rod correspond to each other in a simple manner. CONSTITUTION:In a servo valve which is suitable for use in a speed-change operating multiplying device, a pair of float valves 124 and 125 which are pressed to be separated in the opposite directions by the action of a return spring 126 is included inside a casing 123. A pair of valve lifters 129 and 130 which are pressed to be separated in the opposite directions by return springs 131 and 132 are disposed outside of the float valves 124 and 125, respectively. A cap 141 acting as a restricting member which restricts the reverse stroke of an input rod 136 selectively operating the valve lifters 129 and 130 and an output rod 135 acting as another restricting member which restricts the reverse stroke of one 130 of said lifters 129 and 130 are screwed up to both ends of the casing 123. An adjusting nut 144 is also screwed up to the input rod 136.

Description

[Detailed Description of the Invention] a. Industrial Application Field The present invention relates to a servo valve used in a booster for operating a transmission, etc., and in particular, it is capable of adjusting the stroke amount of an input lot required for opening and closing pulp. Regarding servo valves.

b. Prior art This type of conventional servo valve has a structure in which it is integrated and housed within an output generating part such as a power piston or an output transmitting part such as a piston rond, and due to structural constraints, the input rond cannot be controlled. A device equipped with an adjustment device for adjusting the stroke amount has not yet been realized. Therefore, in order to reduce variations in the stroke amount of the input rond, high machining accuracy is required for each component of the pulp, and as a result, the manufacturing cost of the servo pulp has increased.

C0 Object of the Invention The present invention was developed in view of the above circumstances, and its object is to provide a servo valve that can easily adjust the stroke amount of the input rond.

d. Example An example in which the present invention is applied to a booster for operating a transmission will be described below with reference to the drawings.

First, Fig. 1 shows the transmission*operation mechanism, in which 2 is the transmission, 5 is the change lever, 7 is the clutch, 101 is the body frame, 102 is the pressure source, 103
is a pressure tank, 104 is a valve unit (servo valve), and lO5 is a power cylinder. car body frame 10
As shown in FIGS. 1 and 2, a pair of upper and lower brackets 106 and 107 are attached to the bracket 1, and both upper and lower ends of a rotating shaft 108 are rotatably supported by the pair of brackets 06 and 107. There is. This rotation shaft 108 has a lever 1
09 and 110 are fixed respectively, and the lever 1
One end 109a of 09 is connected to one end of the valve unit 104 by a link rod 111. The other end 109b of the lever 109 is connected to a shift lever 113 of the transmission 2 via a link rod 112.

The other end of the valve unit 104 is connected to the change lever 5 by a link rod 117 as shown in FIG. On the other hand, the cylinder portion 105a of the power cylinder 105
is supported by a suitable fixed part 120 of the vehicle by a pin 118 and a placket 119, and the cylinder part 105a is horizontally rotatable about the pin 118.

Further, the piston rod 105b of the power cylinder 105 is connected to the tip of the lever 110, and the piston rod 105b of the power cylinder 105 is connected to the tip of the lever 110.
5 is driven, the rotation shaft 108 and the lever 109 .
110 are configured to rotate together.

In this way, the booster for operating the transmission is operated by the valve unit 10.
4 and the power cylinder 105 are configured separately, and these are connected to the change lever 5 or the shift lever of the transmission 2 via link rods 111, 112 and 117.
113, the above valve unit 104
Furthermore, the degree of freedom in design regarding the location of the power cylinder 105 is greatly improved, and as will be described later, the structure is extremely simple compared to a conventional booster in which a valve unit and a power cylinder are integrated. Furthermore, it is not necessary to form a mounting portion for the booster on the transmission side, and the output transmission mechanism of the booster and its peripheral structure can be extremely simplified.

The lever 109, 110 has four connecting holes 114a to 114a along its longitudinal direction as shown in FIGS. 2 and 3.
114d and 115a to 115d are formed, respectively.

In FIGS. 2 and 3, the link rod 111 and the piston rod 105b are connected to the connecting holes 114a and 115a on the distal end side by pins 121 and 122, respectively, but the link rod 111 and the piston rod 105b are connected by other connections. It can also be connected to the holes 114b to 114b to 115d, and by changing the connection position in this way, it is possible to easily change the boost ratio of the booster.

The details of this adjustment of the boost ratio will be described later.

The valve lifter 104 has a cylindrical casing 123 as shown in FIGS. 4 to 6.

A pair of left and right idler valves 124 and 125 are accommodated in this casing 123, and the pair of idler valves 124 and 125 are connected to a return spring 1 disposed between the idler valves 124 and 125.
26, they are energized in directions away from each other.

A casing 1 is provided on the outside of the pair of idle valves 124 and 125.
A pair of left and right valve seats 127 and 128 are provided integrally with 23, and a pair of idle valves 124 and 125 are normally operated by a return spring 126.
They are pressed against the valve seats 127 and 128, respectively, with a force of .

A pair of left and right valve lifters 129 and 130 are also provided on the outside of the pair of floating valves 124 and 125. The pair of valve lifters 129 and 130 are biased in directions away from each other by a pair of return springs 131 and 132, and normally the tips of the valve lifters 129 and 130 are separated from the idler valves 124 and 125 as shown in FIG. is seperated.

An insertion hole 133 is formed at one end of the casing 123 of the valve unit 104. This insertion hole 1334- is for inserting the aforementioned valve mechanism into the casing 123 when assembling the valve unit 104.
After inserting the valve mechanism, the end cover 134 is screwed on. This end cover 134 further includes an output rod 1.
35 (third regulating member) is screwed together, and this output lot 1
35 is connected to one end 109a of the lever 109 via a link rod 111.

An input rod 136 is inserted into the valve unit 104, and the tip end 136a of the input rod 136 is inserted into the support hole 13 formed at the end 135b of the output rod 135.
7 in a slidable manner. In addition, output rod 13
A locking nut 145 is screwed into the threaded portion 135a of No. 5.

A stopper ring 138 sandwiched between the valve lifter 130 and the end of the output rod 135 is slidably inserted into the tip 136a of the input rod 136. This stopper ring 138 restricts the backward movement position of the valve lifter 130 while in contact with the end 135b of the output rod 135, and also transmits the pulling force in the direction indicated by the arrow in FIG. 4 of the input rod 136 to the valve lifter 130. belongs to. A retaining ring 139 is fitted to the tip of the input rod 136, so that the pulling force of the input rod 136 is transmitted to the stopper ring 138 by the retaining ring 139.

On the other hand, a cap 141 (first regulating member) is screwed onto the outer periphery of the other end of the casing 123 of the valve unit 104, and an input rod 136 protrudes from the cap 141. The protruding end of the input rod 136 is connected to the change lever 5 via a link rod 117.

A first stopper portion 14 is provided on the inner surface of the cap 141.
2 is formed, and when the input rod 136 is pulled in the direction indicated by the arrow in FIG. Therefore, by adjusting the screwing amount of the camp 141, the pull stroke C2 of the input rod 136 or the valve lifter 1 can be adjusted.
30 forward strokes can be adjusted.

A nut 146 to prevent loosening is screwed into the threaded portion 123a into which the camp 141 is screwed. A second stopper portion 143 is formed on the outer surface of the cap 141, and when the input iron 136 is pushed in the direction of arrow a in FIG.
An adjusting nut 144 (second regulating member) screwed onto the input rod 136 comes into contact with the second stopper portion 143 . Therefore, by adjusting the screwing position of the adjusting nut 144, the bush stroke C2 of the input iron 136 or the forward stroke of the valve lifter 129 can be adjusted.

Therefore, the bushing stroke C3 and the pull stroke C1 can be easily made equal, which alleviates the high machining precision of individual parts required for conventional boosters, and ensures stable operation at all times. In addition, even with respect to dimensional variations due to wear of parts, etc., the dimensions can be corrected by the adjustment function of the cap 141 and the adjusting diagonal eye 44, which is advantageous in terms of the durability of the device.

Air pressure from the pressure tank 103 is constantly introduced into the valve chamber 150 of the valve unit 104 in which the pair of floating valves 124 and 125 are housed through an air tube 152 connected to a pressure supply port 151 of the casing 123.

Further, the outer circumferential space of the valve lifter 129 is
As shown in FIG. 2, the air tube 154 (first communication path) connected to the bushing side output hole 153 of No. 3 communicates with the bushing side input hole 148 of the power cylinder 105. Further, the outer peripheral space of the valve lifter 130 is connected to the power cylinder 10 by an air tube 156 (second communication path) connected to the pull side output hole 155 of the casing.
It communicates with the pull side manual hole 149 of No. 5.

7- And the input lot 136 is indicated by arrow a in FIGS. 2 and 4.
When pushed in the direction, the floating valve 124 is lifted and the valve chamber 1
The air pressure inside 50 is discharged from the bush side output hole 153, and is further transmitted to the power cylinder 1 via the air tube 154.
05, and is configured to move the piston rod 105b of the power cylinder 105 in the direction of arrow C in FIG. On the other hand, when the input iron 136 is pulled in the direction of the arrow in FIG.
Furthermore, the power cylinder 2to is connected via the air tube 156.
5, and is configured to move the piston rod 105b of the power cylinder 105 in the direction of arrow d in FIG.

Exhaust passages 157 and 158 are formed in the inner peripheries of the valve lifters 129 and 130, respectively. Exhaust passage 157
The exhaust passage 15B communicates with an exhaust port 159 provided in the casing 123, and the exhaust passage 15B communicates with an exhaust port 160 provided in the end cover 134. When the operating force of the change lever 5 is released, the pair of idle valves 124 and 125 return to the state shown in FIG.
60 to be discharged to the outside.

Next, the cent state of the valve lifters 129 and 130 will be explained in more detail. The rear end of the valve lifter 129 normally comes into contact with the stopper step 164 of the casing 123 by the setting force of the return spring 131 as shown in FIG. A predetermined stroke S is formed. Further, the rear end of the valve lifter 130 comes into contact with the stopper ring 138 by the setting force of the return spring 132, and in this state, a predetermined stroke S2 is formed between the tip of the valve lifter 130 and the floating valve 125. This strike S2
can be adjusted by the amount by which the output rod 135 is screwed into the end cover 134, and the stroke S1 and the stroke S are equal, and the valve lifters 129 and 13
It is adjusted so that there is no wobbling at 0. The return springs 131 and 132 are of exactly the same type, and are constructed so that the forces pushing and pulling the input rod 136 are exactly the same.

The booster for operating the transmission is constructed as described above, and when the link rod 117 is pushed in the direction of the arrow a in FIGS. 2 and 4 by operating the change lever 5, the input lot 1
36 pressing step portions 165 press the rear end portion of the valve lifter 129. Therefore, the valve lifter 129 moves forward against the return spring 131 as shown in FIG. 5, and lifts the idle valve 124 at its tip against the return spring 126. As a result, the entrance of the exhaust passage 157 of the valve lifter 129 is closed by the floating valve 124 and the valve seat 127 is opened, and the air pressure in the valve chamber 150 is transferred to the power cylinder 105 through the bush side output hole 153 and the air tube 154.
is introduced into the rear cylinder of the piston 105c, and moves the piston rod l05b in the direction of arrow C in FIG. When piston rod 105b moves in the direction of arrow C, lever 109, 110 and pivot shaft 108 rotate clockwise in FIG. 2, pulling link rod 112 in the direction of arrow e. As a result, the shift lever 113 of the transmission 2 rotates clockwise in FIG. 1, and a predetermined gear shift is performed.

At this time, the operating force acting on the shift lever 113 is
It can be changed by the connection position of the link rod 111 or the piston rod 105b with respect to 09.110, and the boost ratio can be easily changed depending on the vehicle type. That is, as shown in FIG. 3, the push force of the link rod 111 or 117 is P3, the push force of the piston rod 105b is P2, the pull force of the link rod 112 is P9, and the rotation axis 108 is If the distance to the center is 11, the distance from the connecting position of the piston rod 105b to the center of the rotating shaft 108 is 42, and the distance from the connecting position of the link rod 112 to the center of the rotating shaft 108 is 18, then 4 g is obtained. By increasing A, P8 can be increased, and for example, the boost ratio can be changed in three stages as shown in FIG. Also, since pt<p, the influence of P8 by the magnitude of 7!1 is relatively small, so even if the boost ratio is the same as before or increased, l is reduced. By doing so, the amount of operation of the change lever 5 can be reduced.

Next, by operating the change lever 5, the link rod 1
17 in the direction of the arrow in FIGS. 2 and 4, the retaining ring 139 attached to the tip 136a of the inlet 136 presses against the stopper ring 138,
This stopper ring 138 presses the rear end of the pulp lifter 130. Therefore, the valve lifter 130 moves forward against the return spring 132 as shown in FIG. The inlet of the valve is closed by the floating valve 125, and the valve seat 127 is opened, and the air pressure in the valve chamber 150 is introduced into the cylinder in front of the piston 105c of the power cylinder 105 through the pull-side output hole 155 and the air tube 156. The piston rod 105b is moved in the direction of the arrow d in FIG.
rotates counterclockwise in FIG. 2, pushing the link rod 112 in the direction of arrow f. As a result, the shift lever of transmission 2
113 is rotated counterclockwise in FIG. 1 to effect a predetermined gear shift. Note that the operating force acting on the shift lever 113 is the same as when pressing the link rod 117 described above.

The push and pull forces of the input lot 136 are generated by the return spring 1
It is calculated by adding the pressure that the valve lifter 129 or 130 receives to the sum of the repulsive forces of the return spring 126, 131 or the return spring 126, 132, but in the booster according to the present invention, the stroke amount of the valve lifter 129, 130 is The push force and pull force of the input rod 136 have been successfully made equal by making them equal by the cap 144 and the cap 141, and by employing exactly the same spring as the return spring 13L 132. In other words, in conventional boosters, an output generating part such as a piston is arranged around the valve mechanism, so air pressure cannot be directly supplied to the valve chamber 150 of the valve mechanism. A pipe was inserted in the axial direction, and air pressure was supplied through this pipe. However, when air pressure is supplied through such a pipe, an error occurs in the push force and pull force of the input lot due to the pressure acting on the pipe itself.

For this reason, in conventional boosters, the push force and pull force of the input rod 136 are balanced by using different return springs for the left and right valve lifters.

For this reason, the design of the booster became extremely complicated, and parts management was also difficult. However, the booster according to the present invention does not require any of the above-described complicated configurations, and can extremely easily adjust the balance between the push force and pull force of the input iron 136.

Next, when the operating force of the change lever 5 is released, the pair of valve lifters 129 and 130 and the pair of idle valves 124
, 125 return springs 131, 132 and 12, respectively.
6, as shown in FIG.
It is discharged to the outside through 59° 160, and the driving of the power cylinder 105 is stopped.

Although one embodiment of the present invention has been described above in which the present invention is applied to a booster for operating a transmission, the present invention is not limited to this and can be applied to servo valves of various pressure equipment. Furthermore, the present invention is not limited to the above embodiments, and can be modified in various ways.

For example, in the above embodiment, the boost ratio was changed depending on the mounting position of the link rod 111 or the piston rod 105b with respect to the lever 109, 110.
09.110 can be modified in various ways, and the lever 109
A lever in which the levers 109 and 110 are integrated may be used, or it is also possible to separately arrange the levers 109 and 110 at arbitrary positions on the shift force transmission path. Also lever 109.1
By forming a long hole in 10, the lever ratio can be adjusted steplessly and the boost ratio can be changed continuously.

f6 Effects of the Invention As described above, the present invention includes a first regulating member for regulating the stroke amount in the backward movement direction of the input rond at one end of the casing of the servo valve, and an input rond protruding from the cap. A third regulating member is screwed together with a second regulating member that regulates the stroke amount in the forward direction of the input rod, and a third regulating member that regulates the backward movement position of at least one of the pair of valve lifters.
Since the third regulating member is screwed to the other end of the casing, after assembling the servo valve, the pair of valve lifters in the non-operating state of the servo valve can be adjusted by adjusting the third regulating member. can be made equal to each other, and by adjusting the first and second regulating members respectively, the stroke amount in the forward direction and the stroke amount in the backward direction of the input iron can be made equal to a predetermined stroke amount. As a result, the operating characteristics in the forward and backward directions of the input rond can be easily matched. Therefore, the strict processing precision conventionally required for each component of the servo valve can be alleviated, and the cost of the servo valve can be reduced. In addition, since the operating characteristics of the input iron can be improved, the operation of the servo valve can be stabilized, and dimensional changes due to wear of each part can be prevented by adjusting the above-mentioned regulating member. Supplement 15- It is possible to improve the durability of the servo valve significantly.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, in which Fig. 1 is a schematic configuration diagram of a transmission operating mechanism, Fig. 2 is a perspective view of a booster for operating the transmission, and 3rd FEJ is a boosting ratio. A plan view of the variable mechanism, FIG. 4 is a vertical cross-sectional view of the valve unit when not in operation, FIG. 5 is a vertical cross-sectional view of the valve unit during push operation, and FIG. 6 is a vertical cross-sectional view of the valve unit during pull operation. , FIG. 7 is a graph showing how the boost ratio is changed. 2...Transmission, 5...Change lever, 101.
...Vehicle body frame, 102...Pressure source, 103...
Pressure tank, 104... Valve unit (servo valve), 105
...Power cylinder, 123...Valve unit casing, 124, 1
25... Idle valve, 129.130... Valve lifter, 135... Output Rondo (third regulating member), 13
6...Input lot, 138...Stopper ring, 1
41... Cap (first regulating member), 16-142... First stopper section, 143... Second stopper section, 144... Adjusting nut (second regulating member)
, 150...valve chamber. W Ward's Tomi Tentoku Kaisho GO-260742 (8) Procedural amendment stamp button 1. Display of the case 1982 Patent Application No. 114237 2, Name of the invention Servo Valve 3, Person making the amendment Relationship to the case Name of the patent applicant Jidosha Kiki Co., Ltd. 4, Agent 107 (and 2 others) 5, Amendment Subject of “Detailed Description of the Invention” column of the specification,
and drawings. Contents of the amendment (1) “Valve seat 127” on page 13, line 6 of the specification has been changed to “valve seat 1”.
28” is corrected. (2) Figures 2 and 4 are corrected as shown in red on the attached sheet. 6. Contents of amendment as attached.

Claims (1)

[Claims] A valve chamber into which fluid pressure is introduced from a predetermined external pressure source is formed in the cylindrical casing, and a pair of idler valves are disposed within the valve chamber so as to be openable and closable. , a pair of pulp lifters that selectively open the pair of floating valves to discharge the fluid pressure from a predetermined output hole are disposed in a reciprocating manner, and the pair of valve lifters are selectively moved in the casing. An input rond that is moved to selectively open the pair of idle valves is inserted so as to be reciprocally movable, and a first regulating member that regulates a stroke amount of the input rond in a backward direction is provided at one end of the casing. At the same time, a second regulating member protruding from the cap and regulating the forward stroke amount of the operating rond is screwed onto the input rond, and at least one of the pair of valve lifters is moved in a backward direction. A servo valve characterized in that a third regulating member for regulating the position is screwed onto the other end of the casing.