KR20020074941A - Semi-auto shift gears for used vehicle clutch apparatus - Google Patents

Abstract

PURPOSE: A clutch-operating unit for a semi-auto transmission vehicle is provided to make control of a clutch easier than before, to simplify the structure, and to reduce the cost. CONSTITUTION: A clutch-operating unit(100) for a semi-auto transmission vehicle comprises partition plates(110a,11b); plural connecting rods(120) connecting the partition plates opposed; a hydraulic cylinder(130) for supplying hydraulic pressure to a clutch booster(20) of a clutch unit(10) and shutting off a clutch(12); a booster(140) for boosting the supplied hydraulic pressure; a hydraulic control valve(150) for controlling the hydraulic pressure supplied from a hydraulic power unit in the direction of shut off and connection of the clutch in controlling the clutch; a hydraulic control lever(160) for converting flow of hydraulic pressure in the hydraulic control valve to the booster and the atmosphere side; control units(170,172,174) for controlling the direction of the hydraulic control lever; and an elastic spring(180) giving the power toward the direction restoring a booster piston(142) and a piston(132) of the hydraulic cylinder. Therefore, control of the clutch is easily performed and the cost is reduced.

Description

Semi-auto shift gears for used vehicle clutch apparatus

The present invention relates to a clutch operation device for a semi-automatic shifting vehicle, and more particularly, to allow a flexible adjustment of the power transmission of the clutch, as well as to operate a semi-automatic shifting clutch for smooth operation in a semi-clutch state. Relates to a device.

In general, the use of a conventional manual transmission to reduce the transmission cost and fuel cost, while the semi-automatic transmission that does not need to step on the clutch pedal, such as an automatic transmission has been gradually expanded.

On the other hand, the above-mentioned clutch Clutch refers to a mechanical element having a function of transmitting or interrupting power by mechanical contact from the driving side on the concentric shaft to the driven side. Such a clutch is installed between the engine and the transmission.

The above-mentioned clutch performs a power transmission function for transmitting the engine's rotational force to the transmission and a power cut function for temporarily shutting off the power flow between the engine and the transmission when necessary, enabling a smooth and vibration-free oscillation, It protects the overdrive power train from overload, as well as reduces the rotational vibration of the engine with the flywheel. The following describes a typical automotive clutch system.

1 is a cross-sectional view showing a conventional clutch device for a vehicle.

As shown in FIG. 1, the conventional clutch device 10 for a vehicle includes a clutch pedal 14 for regulating the clutch 12, a master cylinder 16 transmitting a force of the clutch pedal 14, and a master cylinder ( 16 is boosted by the pneumatic pump 18 for supplying air pressure through the valve hole 18a opened by hydraulic pressure, the clutch booster 20 for boosting the air pressure supplied from the pneumatic pump 18, and the clutch booster 20. It consists of a release cylinder 22 which operates the clutch 12 by pressure and a shift lever 24 which is hinged and connects the release cylinder 22 and the clutch 12. At this time, the push rod 22a of the release cylinder 22 has a return force by the return spring 26.

In the conventional clutch device for automobiles configured as described above, when the driver presses the clutch pedal 14, the piston 16a of the master cylinder 16 is actuated by the force to generate oil pressure, and the generated oil pressure is a valve hole. By opening 18a, the air pressure generated by the pneumatic pump 18 flows into the clutch booster 20 through the valve hole 18a. At this time, the air pressure generated by the pneumatic pump 18 is introduced into the clutch booster 20 via the pneumatic induction pipe 18b, and the introduced air pressure moves the clutch booster piston 20a to move the release cylinder 22. The push rod 22a is moved, and by the movement of the push rod 22a, the shift lever 24 separates the clutch disc of the clutch 12 from the drive plate of the engine and cuts off power transmitted to the flywheel.

However, the manual clutch device as described above has a problem in that an overwhelming force occurs in the ankle or knee when the vehicle is driven for a long time because the driver has to give a greater force than the small vehicle when the driver presses the clutch pedal.

In addition, even in small vehicles, in order to prevent the vehicle from turning off during long periods of congestion and slowness, or when driving in the city, in the half-clutch section when the clutch pedal is released, the accelerator pedal must be pressed while the foot pedal is finely moved. There is a problem that it is easy to get tired and get tired easily.

In addition, in order to flexibly maintain the operation of the clutch pedal, complicated components are required as described above.

Moreover, when the left foot is unnaturally disabled, there is a problem in that the vehicle equipped with the manual clutch cannot be driven at all.

On the other hand, in some cases, a semi-automatic system such as a semi-auto is installed in an existing vehicle. The semi-automatic system is simpler in structure and inexpensive compared to a full automatic system, but more complicated and expensive than a manual vehicle. Has a problem.

The present invention has been devised to solve the problems described above, and the clutch operating device for a semi-automatic variable speed vehicle which can be easily mounted on an existing vehicle to control the clutch relatively easily compared to the conventional operation of the clutch pedal. The purpose is to provide. In particular, the present invention provides a convenience in use by operating the clutch using the clutch pedal, as well as operable by hand.

Another object of the present invention is to facilitate the operation of the state of the van clutch so that the engine is not turned off or the vehicle is snoozed even if the foot on the clutch pedal is quickly released in the half clutch section.

Still another object of the present invention is to enable the operation of the clutch pedal as well as the electronic control operation unit so that the disabled can easily operate the clutch.

In addition, an object of the present invention is to facilitate installation and removal by connecting the completed clutch operating device to the existing clutch device.

In addition, the present invention provides an improved function as a semi-automatic system than the conventional semi auto as well as the above-described objects, as well as providing a device having a simpler structure and a lower cost than the conventional semi auto.

1 is a cross-sectional view showing a conventional clutch system for a vehicle.

Figure 2 is a perspective view showing a clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 3 is a state diagram showing the connection of the clutch device for a semi-automatic variable speed vehicle according to the present invention and the automobile clutch device.

Figure 4a is a side view showing a clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 4b is a cross-sectional view showing the hydraulic control lever and the hydraulic control valve of the clutch operation device for a semi-automatic variable speed vehicle according to Figure 4a.

Figure 5a is a side view showing a rotating state of the hydraulic control lever at the time of clutch blocking (power off) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 5b is a cross-sectional view showing the operating state of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 5a.

Figure 5c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve at the time of clutch shutoff (power off) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 5d is a cross-sectional view showing the operating state of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 5c.

Figure 6a is a side view showing a rotating state of the hydraulic control lever in the semi-clutch state of the clutch operating device for a semi-automatic variable speed vehicle according to the present invention.

Figure 6b is a cross-sectional view showing the operation of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 6a.

Figure 6c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve in the semi-clutch state of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 6d is a cross-sectional view showing the operation of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 6c.

Figure 7a is a side view showing a rotating state of the hydraulic control lever when the clutch connection (power transmission) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 7b is a cross-sectional view showing the operation of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 7a.

Figure 7c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve when the clutch connection (power transmission) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention.

Figure 7d is a cross-sectional view showing the operation of the hydraulic control lever and the hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to Figure 7c.

*** Explanation of symbols for the main parts of the drawing ***

100. Clutch Actuator for Semi-Auto Transmission

110a, 110b. 120. Connecting rod

130. Hydraulic Cylinder 132. Piston

134. Piston Rod 138. Hydraulic Transmission Line

140. Booster 142. Booster Piston

144. Booster Piston Rod 150. Hydraulic Control Valve

151. Valve Body 151a. Upper side pressure chamber

151b. Lower pressure chamber 151c. Communicator

151b-1. Hydraulic 151a-1. Supply hole

151a-2, 152a-1. Spring support 151b-2, 152-2. Sealing Ring Fixture

152. Upper Cap 152a. Lower cap

153a, 153. Sealing ring 154. Upper valve body

154a. Lower valve body 155, 155a, 174, 180. Elastic spring

156. Upper valve body pusher 156a. Lower valve body push rod

157. Pushing plate 160. Hydraulic control lever

170. Magnet switch 172. Cable

190. Hydraulic lever adjustment

192a. Hydraulic control lever rotation range limited groove

192. Adjusting screw

The present invention configured to achieve the above object is as follows. That is, in the clutch device for automobiles which consists of the master cylinder which transmits the force of a clutch pedal, the clutch booster which boosts the pressure generated by the master cylinder, and the shift lever which clamps a clutch by the action of a clutch booster, the plate shape of predetermined size is carried out. Diaphragms formed to be arranged on both sides of a predetermined distance; A plurality of connecting rods for opposing the diaphragms on both sides; A hydraulic cylinder installed at one side of the diaphragm and having a piston installed therein, and supplying the generated hydraulic pressure to the clutch booster to block the clutch; A booster installed at the rear end of the other side plate and including a booster piston connected to the piston of the hydraulic cylinder, while boosting the supplied hydraulic pressure to operate the hydraulic cylinder through the booster piston; It is installed on the connection part of the piston of the hydraulic cylinder and the booster piston so that it can be moved at the same time as the distance moved in the forward and backward movement direction of the piston and supplies the hydraulic pressure supplied from the hydraulic source to the booster when the clutch is blocked, while the booster is connected when the clutch is connected. Hydraulic control valve for controlling the hydraulic pressure to discharge the hydraulic pressure supplied to the atmosphere; A hydraulic control lever rotatably installed in place of the hydraulic control valve so as to switch the flow of hydraulic pressure in the hydraulic control valve to the booster and the atmospheric side through rotation by an external force; Hydraulic control lever control means for controlling rotation of the hydraulic control lever in the direction when the clutch is shut off and connected so that the flow of hydraulic pressure in the hydraulic control valve can be switched to the booster and the atmospheric side; And an elastic spring supported between the hydraulic control valve and the hydraulic cylinder so that the force acts in the direction to always restore the booster piston and the piston of the hydraulic cylinder, and the booster travels as much as the rotational movement distance of the hydraulic control lever when the clutch is interrupted. The hydraulic control valve is moved in the same direction by the action of the spring and the elastic spring so that the hydraulic pressure of the hydraulic control valve does not flow to the booster and the atmosphere after the clutch is interrupted. By the action of the control lever control means, the hydraulic control lever is rotated in the reverse direction by the middle part when the clutch is blocked and connected, and the hydraulic control valve is moved by the rotational distance of the hydraulic control lever in the same direction. Anti-clutch phase to make this booster and neutral state do not flow to the atmosphere It is the one to keep.

On the other hand, the means for adjusting the piston moving distance of the hydraulic cylinder by adjusting the position of the hydraulic control lever is further provided, the above-mentioned piston moving distance adjusting means of the hydraulic cylinder is capable of moving back and forth on the upper connection rod of the plurality of connecting rods On the other hand, the hydraulic control lever position adjustment piece is provided in the upper and lower through-form is provided with a hydraulic control lever rotation range restriction groove of the long groove to limit the rotation range of the hydraulic control lever; And it can be made of the adjusting piece adjusting screw for moving the hydraulic adjusting lever position adjusting piece back and forth through the rotation, while the screw is coupled to the hydraulic adjusting lever position adjusting piece through the screw connection to the place where the booster is fixed fixed. After moving the hydraulic control lever position adjusting piece by rotating the adjusting screw, place the hydraulic control lever in the direction when the clutch is connected. By moving the hydraulic control valve to the moving position of the hydraulic control lever through the hydraulic flow to change the piston position of the hydraulic cylinder to adjust the piston movement distance of the hydraulic cylinder.

The hydraulic pressure generated in the above-described master cylinder of the automobile clutch device may be supplied to the clutch booster through the hydraulic cylinder to control the clutch so that the master cylinder of the automobile clutch device and the hydraulic cylinder may be connected to the hydraulic transmission pipe. The configuration of the hydraulic transmission tube is to supply the pressure generated by the pedal force of the clutch pedal to the clutch booster through the master cylinder and the hydraulic cylinder to control the clutch by the clutch pedal.

In the above-described configuration, the pressure control valve of the hydraulic control valve is formed in the form of the outer side of each of the upper and lower sides to communicate with each other through communication holes, while the lower pressure chamber is formed with an inlet hole through which hydraulic pressure flows from the hydraulic source. A valve body having a supply hole for supplying hydraulic pressure to the booster; The upper and lower caps are screwed to each of the upper and lower pressure chambers, and screwed to the upper pressure chamber, the upper and lower caps having through-holes formed to penetrate up and down; A sealing ring supported at each of an inner end of the through hole of the upper cap and a lower end of the communication hole, which is an upper end of the lower pressure chamber; It is installed in each pressure chamber so that the outer circumferential surface is in close contact with each sealing ring to close the lower part of the through-hole and the communication hole of the upper cap, but the one installed in the upper-side pressure chamber penetrates the center vertically, and the lower side is formed. Installed in the pressure chamber includes a conical upper and lower valve body formed with a seat groove at the front end of the center; An elastic spring for supporting the upper and lower valve bodies in each of the pressure chambers so that the elastic force acts in a direction in contact with the sealing ring at all times; While contacting the outer circumference of the front end face of the upper valve body through the through hole of the upper cap, the outer end is formed to protrude outward of the upper cap to press the upper valve body by rotation in the direction when the hydraulic control lever is connected to the clutch. Upper valve body pressing rod; One end penetrates the through-hole of the upper valve body through the hollow of the upper valve body push rod and is coupled to the seat groove of the lower valve body, while the other end protrudes outwardly than the upper valve body push bar to shut off the clutch of the hydraulic control lever. A lower valve element pressing rod that presses the lower valve element by rotation in the direction; And a pressing plate coupled to the upper position of the valve body to be rotatably hinged to be pressed by rotation in the direction when the hydraulic control lever is connected to the clutch to press the upper valve body pressing rod.

The above-mentioned hydraulic control lever is hinged to a certain range of rotation in place of the upper valve body of the pressing plate, and rotates in the direction when the clutch is closed, presses the lower valve body pressing rod, and rotates in the direction when the clutch is connected, the upper valve body It can be configured to press the upper valve element pressing rod through the pressing plate.

And, the lower portion of the above-described hydraulic control lever may be further provided with a pressing piece for pressing the upper valve body pressing plate during rotation in the direction of the clutch connection of the hydraulic control lever.

In the above-described configuration, a sealing ring fixing part associated with the sealing ring may be formed at each of the lower end of the communication hole, which is the upper end of the through hole inner end of the upper cap and the lower side pressure chamber, so that the sealing ring may be supported.

The inner side of the upper pressure chamber lower end and the lower cap described above may be formed with a spring support for supporting one end of the elastic spring to support the elastic spring.

On the other hand, the hydraulic control lever control means of the above configuration is provided in place of the hydraulic control valve magnet switch for rotating the hydraulic control lever in the direction of pressing the lower valve body pressing rod; One end is connected to the hydraulic control lever, the other end is connected to the accelerator pedal side of the vehicle for rotating the hydraulic control lever in the direction of pressing the upper valve body pressing rod by the pedal force of the accelerator pedal; And the hydraulic control lever elastically connected to the connection portion of the accelerator pedal side of the cable to be elastically deformed when the hydraulic control lever is rotated in the direction when the clutch is blocked, and the hydraulic control lever rotated in the direction when the clutch is blocked by the elastic force of the half clutch. It can be made to include an elastic spring to reverse the state.

The cable described above is in a loose state when the accelerator pedal is not fully depressed when the position of the hydraulic control lever is fully rotated in the direction of connecting the clutch, and the position of the hydraulic control lever is moved in the direction when the clutch is blocked, thus the position of the half clutch state. After reaching the state it may be made of a length that is tightened.

And, the elastic spring on the cable side is the position of the hydraulic control lever when the position of the hydraulic control lever is in the half-clutch state when the position of the hydraulic control lever is moved in the direction when the clutch is shut off when the cable is loose. Elasticity is increased until it reaches the position when the clutch is completely blocked, while hydraulic pressure is rotated in the direction of clutch disconnection through the restoring force of the elastic spring on the cable side when the Marknet switch is off. The lever is rotated back to the state of the half clutch so as to become the state of the half clutch.

Hereinafter, a clutch operating device for a semi-automatic variable speed vehicle according to a preferred embodiment of the present invention will be described in detail.

Figure 2 is a perspective view showing a clutch operation apparatus for a semi-automatic shift vehicle according to the present invention, Figure 3 is a state diagram showing the connection of the clutch operation apparatus for a semi-automatic variable speed vehicle according to the present invention and the automobile clutch device, Figure 4a is a present invention Figure 4b is a side view showing the clutch operation device for a semi-automatic shifting vehicle according to the present invention, Figure 4b is a cross-sectional view showing a hydraulic control lever and a hydraulic control valve of the clutch operation device for a semi-automatic shifting vehicle according to Figure 4a.

As illustrated in FIGS. 2 to 4 b, the clutch operating device 100 for a semi-automatic variable speed vehicle according to the present invention connects diaphragms 110a and 110b and diaphragms 110a and 110b arranged at both sides of a predetermined distance to face each other. A plurality of connecting rods 120, a hydraulic cylinder 130 to block the clutch by supplying the generated hydraulic pressure to the clutch booster 20 of the clutch device 10, a booster 140 for boosting the supplied hydraulic pressure, clutch 12 ), The hydraulic control valve 150 for controlling the hydraulic pressure supplied from the hydraulic source in the direction of interruption and connection of the clutch 12 (during the interruption and transmission of power), and the hydraulic control valve 150 through rotation by external force. Hydraulic control lever 160 for switching the flow of hydraulic pressure in the booster 140 and the atmosphere side, means for controlling the direction of the hydraulic control lever 160 (170, 172, 174) and the booster piston 142 and the hydraulic cylinder The force is small in the direction to always return the piston 132 of 130 It is made by including an elastic spring 180.

The clutch operating device 100 for a semi-automatic variable speed vehicle of the present invention configured as described above is adapted to the action of the booster 140 and the elastic spring 180 by the rotational movement distance of the hydraulic control lever 160 when the clutch 12 is interrupted. After the hydraulic control valve 150 is moved in the same direction and the clutch 12 is interrupted, the hydraulic pressure of the hydraulic control valve 150 does not flow to the booster 140 and the atmosphere, while the clutch 12 When the clutch 12 is shut off, the hydraulic pressure adjusting lever 160 is controlled by the action of the hydraulic control lever control means so that the hydraulic pressure adjusting lever 160 rotates in the reverse direction by the middle portion of the clutch 12 when the clutch 12 is blocked and connected. The valve 150 is moved by the rotational distance of the hydraulic control lever 160 in the same direction so that the hydraulic pressure of the hydraulic control valve 150 is in a neutral state that does not flow into the booster 140 and the atmosphere so as to maintain a half-clutch state. It is.

Referring to the configuration of the clutch operation device 100 for a semi-automatic variable speed vehicle according to the present invention as described above in detail. First, the diaphragms 110a and 110b are for fixing and installing the hydraulic cylinder 130 and the booster 140 to be described later. The diaphragms 110a and 110b are formed in a plate shape in a rectangular shape so as to face opposite sides of a predetermined distance. do.

As described above, the connecting rod 120 connects diaphragms 110a and 110b arranged opposite to each other at a predetermined distance, and the connecting rod 120 connects corners of the diaphragms 110a and 110b, respectively. Therefore, as described above, by connecting the corner portions of the diaphragm 110a, 110b through the connecting rod 120, a rectangular parallelepiped form is formed.

Hydraulic cylinder 130 is to supply the generated hydraulic pressure to the booster 20 of the clutch device 10 to clamp the clutch 12, this hydraulic cylinder 130 is installed on the front plate (110a) front side Is fixed. At this time, a piston 132 is installed inside the hydraulic cylinder 130 described above, and the piston rod 134 is connected to the piston 132 so as to be movable back and forth through the diaphragm 110a on the front side.

On the other hand, the hydraulic cylinder 130 is provided with a hydraulic supply pipe (130a) for supplying the generated hydraulic pressure to the clutch booster 20 of the clutch device 10, this hydraulic supply pipe (130a) is the front end of the hydraulic cylinder (130) From the hydraulic supply path 17 of the clutch device 10.

In addition, the hydraulic cylinder 130 is provided with an oil inlet 136 for receiving oil from the oil tank 16b provided in the master cylinder 16 of the clutch device 10, and this oil inlet 136 Is connected to the master cylinder 16 of the clutch device 10 via a hydraulic transmission pipe (138).

As described above, the hydraulic transmission pipe 138 has a function of supplying oil into the hydraulic cylinder 130 from the oil tank 16b provided in the master cylinder 16 of the clutch device 10, as well as the clutch. By the pedal force of the clutch pedal 14 of the device 10 is to function to be supplied to the clutch booster 20 through the hydraulic cylinder 130 generated in the master cylinder 16.

That is, the hydraulic transmission pipe 138 connecting the master cylinder 16 and the hydraulic cylinder 130 of the clutch device 10 described above intermittently clamps the clutch 12 through the clutch pedal 14 of the clutch device 10. That means you can do it.

Booster 140 is to operate the hydraulic cylinder 130 by boosting the supplied hydraulic pressure, the booster 140 is installed and fixed to the rear of the rear side plate (110b). At this time, a booster piston 142 is installed inside the booster 140 described above, and the booster piston rod 144 is installed to the booster piston 142 so as to be movable back and forth through the diaphragm 110b on the rear side. do.

The booster piston rod 144 described above is located on the same center line as the piston rod 134 of the hydraulic cylinder 130 described above. The above-described booster piston rod 144 and the piston rod 134 of the hydraulic cylinder 130 are connected by the hydraulic control valve 150 to be described later from the inner side between the two diaphragms 110a and 110b to boost the pressure in the booster 140. The hydraulic pressure can be transmitted to the hydraulic cylinder 130 through the booster piston rod 144 and the piston rod 134 of the hydraulic cylinder 130.

On the other hand, one side of the above-described booster 140 allows the hydraulic pressure from the hydraulic control valve 150 to be described later to be supplied into the booster 140, while the hydraulic pressure discharged from the booster 140 to the hydraulic control valve 150 A hydraulic pipe 146 is installed to be discharged to the outside air through.

Therefore, when the hydraulic pressure generated from the hydraulic control valve 150 to be described later is supplied to the booster 140, the hydraulic pressure introduced into the booster 140 is boosted by the booster 140 to operate the booster piston 142, By the operation of the booster piston 142, the booster piston rod 144 moves the piston rod 134 on the hydraulic cylinder 130 side so that hydraulic pressure is generated in the hydraulic cylinder 130. The hydraulic pressure generated in the hydraulic cylinder 130 as described above is transmitted to the hydraulic pressure supply path 17 of the clutch device 10 through the hydraulic pressure supply pipe 130a described above.

The hydraulic control valve 150 supplies the hydraulic pressure supplied from the hydraulic source to the booster 140 when the clutch 12 is blocked, while discharging the hydraulic pressure supplied to the booster 140 when the clutch 12 is connected to the atmosphere. By adjusting the hydraulic pressure, as shown in Figures 4a and 4b.

The hydraulic control valve 150 as described above is connected to the piston 132 and the booster piston 142 of the hydraulic cylinder 130 so as to be moved at the same time by the distance moved in the forward and backward direction of the piston (132, 142). Is installed on.

In more detail, the hydraulic control valve 150 is a piston rod 134 of the hydraulic cylinder 130 and a booster piston rod 144 of the booster 140 installed to be moved back and forth through the diaphragm 110a and 110b. Installed between). Therefore, it can be seen that the aforementioned oil control valve 150 is simultaneously moved in the same direction by the moving distance of the booster piston 142.

According to the configuration as described above it can be seen that the hydraulic control lever 150 is supported by the piston rod 134 of the hydraulic cylinder 130 and the booster piston rod 144 of the booster 140.

On the other hand, look at the configuration of the above-described hydraulic control valve 150 as follows. That is, the hydraulic control valve 150 of the semi-automatic variable speed vehicle clutch operation apparatus 100 according to the present invention is a valve body formed with upper and lower pressure chambers 151a and 151b as shown in FIGS. 4A and 4B. 151, upper and lower caps 152 and 152a screwed into the upper and lower pressure chambers 151a and 151b, sealing rings 153 and 153a, upper and lower valve bodies 154 and 154a, and elastic springs. 155, 155a, the upper valve body pressing rod 156, the lower valve body pressing rod 156a, and the pressing plate 157.

In the above-described configuration, the valve body 151 forms the exterior of the hydraulic control valve 150. The valve body 151 has pressure chambers 151a and 151b of the space in the form of an outer side of the upper and lower portions thereof. These upper and lower pressure chambers 151a and 151b communicate with each other through communication holes 151c formed smaller than the diameters of the upper and lower pressure chambers 151a and 151b. That is, the upper and lower pressure chambers 151a and 151b are formed on the upper and lower surfaces of the valve body 151, respectively, but the upper pressure chamber 151a is open at the upper side and the lower pressure chamber 151b. ) Is formed in the form of the lower side open.

In the above-described configuration, a spring support part 151a-2 for supporting the elastic spring 155 to be described later is formed on the lower end of the upper pressure chamber 151a, that is, on the interface with the upper end of the communication hole 151c, and the lower pressure chamber The sealing ring fixing part 151b-2 for fixing the sealing ring 153a to be described later is formed on the upper end of the 151b, that is, on the interface with the lower end of the communication hole 151c.

Meanwhile, an inlet hole 151b-1 through which hydraulic pressure flows from a hydraulic source (not shown) is formed in the lower pressure chamber 151b of the valve body 151 described above, and the hydraulic pressure is provided in the upper pressure chamber 151a. A supply hole 151a-1 for supplying hydraulic pressure introduced through the inlet hole 151b-1 from the source to the booster 140 is formed.

Therefore, the hydraulic pressure flows from the hydraulic pressure source into the lower pressure chamber 151b through the inlet hole 151b-1, and the hydraulic pressure introduced into the lower pressure chamber 151b passes through the communication hole 151c and the upper pressure chamber. After flowing into 151a, it can be seen that it is supplied to the booster 140 through the supply hole 151a-1.

The upper and lower caps 152 and 152a are for closing the upper and lower pressure chambers 151a and 151b of the valve body 151. The upper and lower caps 152 and 152a are upper and lower pressure chambers. It is screwed on the outer side of 151a, 151b. Thus, by screwing the upper and lower caps 152 and 152a into the upper and lower pressure chambers 151a and 151b, the upper and lower pressure chambers 151a and 151b form a closed space.

In the above-described configuration, the upper cap 152 is formed with a through hole 152-1 penetrating up and down the center thereof, and an inner end of the through hole 152-1, that is, a lower surface of the upper cap 152. A sealing ring fixing part 152-2 for fixing the sealing ring 153 to be described later is formed around the bottom surface of the through hole 152-1 on the side surface. The lower cap 152a is provided with a spring support 152a-1 for supporting the elastic spring 155a which will be described later.

The sealing rings 153 and 153a have a lower end surface of the through hole 152-1 of the upper cap 152, a front end surface of the upper valve body 154 to be described later, and a lower end of the communication hole 151c and a lower valve body 154a line. The sealing rings 153 and 153a are made of a rubber material to seal between end faces so that hydraulic pressure is not leaked.

As described above, the sealing rings 153 and 153a have the sealing ring fixing part 152-2 and the lower portion formed around the lower surface of the through hole 152-1 on the inner side, which is the lower surface of the upper cap 152, as described above. It is fixed on the sealing ring fixing part 151b-2 formed on the upper end of the side pressure chamber 151b, that is, on the interface with the lower end of the communication hole 151c.

The upper and lower valve bodies 154 and 154a are for blocking or blocking the hydraulic pressure in the upper and lower hydraulic chambers 151a and 151b. The upper and lower valve bodies 154 and 154a respectively have sealing rings 153. , 153a are provided in the upper and lower pressure chambers 151a and 151b so as to be in close contact with the outer circumferential surface thereof. At this time, the upper and lower valve body (154, 154a) is in contact with the sealing ring (153, 153a) the upper side is made of a conical shape, the lower portion of the elastic spring (155, 155a) to be described later is fastened to the outer peripheral surface elastic spring Spring support jaws 154-1 and 154a-1 are formed to be supported by 155 and 155a.

The upper and lower valve bodies 154 and 154a configured as described above are supported by the elastic springs 155 and 155a which will be described later in the upper and lower pressure chambers 151a and 151b, respectively. The through hole 152-1 and the communication hole 151c of the cap 152 are closed. Therefore, the upper valve body 154 opens and closes the through hole 152-1 of the upper cap 152 in the upper hydraulic chamber 151a, and the lower valve body 154a is in the lower hydraulic chamber 151b. It can be seen that the opening and closing of the communication hole (151c).

On the other hand, the above-described upper valve body 154 is formed with a through hole 154-2 penetrating the upper and lower portions of the central portion thereof so that the lower valve body pressing rod 156a, which will be described later, penetrates the lower valve body 154a. A seat groove 154a-2 is formed at the front end of the center, and the lower end of the lower valve body pressing rod 156a penetrating the through hole 154-2 of the upper valve body 154 is seated.

The elastic springs 155 and 155a are for elastically supporting the respective valve bodies 154 and 154a in the respective pressure chambers 151a and 151b. Each of the elastic springs 155 and 155a has an upper pressure It is supported by the lower end of the seal 151a and the inner surface of the lower cap 152a.

That is, the elastic spring 155 installed in the upper pressure chamber 151a has a lower end in the spring support part 151a-2 formed on the lower end of the upper pressure chamber 151a, that is, on the interface with the communication hole 151c. In this supported state, the upper side is fastened to the lower outer peripheral surface of the upper valve body 154 provided in the upper pressure chamber 151a to elastically support the upper valve body 154, and to the lower pressure chamber 151b. The installed elastic spring 155a has a lower end supported by a spring support 152a-1 formed on the inner side of the lower cap 152a, and the upper side thereof has a lower valve body installed in the lower pressure chamber 151b. It is fastened to the outer peripheral surface of the lower side of 154a, and elastically supports the lower valve body 154a.

In other words, each of the elastic springs 155 and 155a installed as described above has a spring support portion 154-1 of the upper valve body 154 and a spring support portion of the upper pressure chamber 151a as shown in FIG. 4B. An elastic spring 155 of the upper pressure chamber 151a is installed between the 151a-2, and the spring support jaw 154a-1 of the lower valve body 154a and the spring support of the lower cap 152a ( An elastic spring 155a of the lower pressure chamber 151b is installed between 152a-1.

The upper valve element pressing rod 156 is for opening the through hole 152-1 of the upper cap 152 by pressing the upper valve element 154. The upper valve element pressing rod 156 is the upper cap 152. It is installed to contact the outer periphery of the front end surface of the upper valve body 154 through the through hole 152-1. At this time, the upper valve body pressing rod 156 is formed in the form of a hollow tube, the upper end of the upper valve body pressing rod 156 is formed in a length that can protrude to the outside of the upper cap 152 as shown in Figure 4b do.

Booster 140 by moving the upper valve body 154 to the lower side through the pressing operation of the upper valve body pressing rod 156 installed as described above to open the through-hole 152-1 of the upper cap 152. The hydraulic pressure introduced into the outside air is discharged to the outside air between the inner wall of the through hole 152-1 of the upper cap 152 and the outer circumferential surface of the upper valve body pressing rod 156. At this time, since the lower end of the upper valve body pressing rod 156 is in surface contact with the circumferential surface of the front end surface of the upper valve body 154, the hydraulic pressure is not discharged to the outside air through the upper valve body pressing rod 156.

The pressing operation of the upper valve body pressing bar 156 as described above is made as the hydraulic control lever 160, which will be described later, rotates in the direction when the clutch 12 is connected (power transmission).

The lower valve element pressing rod 156a presses the lower valve element 154a to open the communication hole 151c so that the hydraulic pressure introduced from the hydraulic source into the lower oil pressure chamber 151b passes through the communication hole 151c. The lower valve body pressing rod 156a has one end penetrating the through-hole 154-2 of the upper valve body 154 through the hollow of the upper valve body pressing rod 156. It is installed so that it may be seated in the seat groove 154a-2 of the lower valve body 154a. At this time, the upper end of the lower valve body pressing rod 156a is formed to a length that can protrude to the outside of the upper valve body pressing rod 156, as shown in FIG.

The lower valve body 154a is moved to the lower side through the pressing operation of the lower valve body pressing rod 156a installed as described above, so that the communication hole 151c is opened, thereby flowing into the lower hydraulic chamber 151b. The hydraulic pressure enters the upper hydraulic chamber 151a through the communication hole 151c.

The pressing operation of the lower valve body pressing rod 156a as described above is performed as the hydraulic control lever 160 to be described later rotates in the direction when the clutch 12 is blocked (when power is blocked).

The pressing plate 157 is pushed by the lower side of one side of the hydraulic control lever 160 as the hydraulic control lever 160 to be described later rotates in the direction when the clutch 12 is connected (power transmission), the upper valve body pressing rod described above The pressing plate 157 is provided so that the pressing plate 157 is coupled to a hinge 157b at an appropriate position in the valve body 151 of the upper side of the upper valve body pressing rod 156 so as to rotate in a predetermined range. At this time, the through-hole 157a is formed in place of the pressing plate 157 so that the lower valve side pressing rod 156a can move up and down.

The pressing operation of the pressing plate 157 installed as described above is made as the hydraulic control lever 160, which will be described later, rotates in the direction when the clutch 12 is connected (at the time of power transmission).

The hydraulic control valve 150 configured as described above allows the hydraulic pressure introduced from the hydraulic source through the opening of the communication hole 151c to be supplied into the booster 140 to block the clutch 12 of the clutch device 10 (power On the other hand, the hydraulic pressure supplied into the booster 140 is discharged to the outside air through the opening of the through hole 152-1 formed in the upper cap 152 to connect the clutch 12 of the clutch device 10 ( Power transmission).

On the other hand, the hydraulic pressure of the above-described hydraulic control valve 150 is the flow is switched by the hydraulic control lever 160, the hydraulic control lever 160 for switching the hydraulic flow of the hydraulic control valve 150 is a hydraulic control valve ( Hinge 164 is coupled to the valve body 151 in place of 150 is installed to be rotatable. At this time, the pressing piece 162 for pressing the pressing plate 157 is provided at the lower portion in the rotational direction when the clutch 12 is connected to the clutch 12 of the hydraulic control lever 160.

When the hydraulic control lever 160 having the configuration as described above is rotated in the direction when the clutch 12 of the clutch device 10 is blocked (when the power is blocked), the hydraulic pressure is adjusted around the hinge 164 as shown in FIG. 4B. The right end of the lever 160 presses the lower valve element pressing rod 156a to move the lower valve element 154a to the lower side to open the communication hole 151c. At this time, the upper valve body 154 is in a state of closing the through hole 152-1 of the upper cap 152.

Therefore, the hydraulic pressure introduced from the hydraulic source into the lower hydraulic chamber 151b is introduced into the upper hydraulic chamber 151a through the communication hole 151c and is supplied to the booster 140 through the hydraulic tube 146. When the hydraulic pressure is supplied to the booster 140 as described above, the boost pressure is transmitted to the clutch booster 20 of the clutch device 10 by the boosting action of the booster 140, and the clutch 12 is blocked. . In other words, the power being transmitted is cut off.

On the other hand, when the above-mentioned hydraulic control lever 160 is rotated in the direction (power transmission) when the clutch 12 of the clutch device 10 is connected (hydraulic transmission) as shown in Figure 4b the hydraulic control lever 160 around the hinge 164 The left end of the pressurizes the upper valve element pressing rod 156 to move the upper valve element 154 to the lower side to open the through hole 152-1 of the upper cap 152. At this time, the lower valve body pressing rod 156a is returned to its original position by the restoring force of the elastic spring 155a installed in the lower pressure chamber 151b, and the communication hole 151c is closed by the lower valve body 154a.

Therefore, the booster piston 142 is retracted by the restoring force of the elastic spring 180 of the clutch operating device 100 to be described later, by disappearing the pressure supplied to the booster 140 to operate the hydraulic cylinder 130 through the elevated pressure. Accordingly, the hydraulic pressure introduced into the booster 140 is introduced into the upper hydraulic chamber 151a through the hydraulic pipe 146 and discharged to the outside air through the through hole 152-1 of the upper cap 152 that is opened. . By this action, the clutch 12 of the clutch device 100 is connected. That is, power is transmitted.

Hydraulic control lever control means (170, 172, 174) is to rotate the hydraulic control lever 160 in the direction of the clutch block 10 of the clutch device 10 when the clutch block and connection (power off and transfer), this hydraulic control lever control The means (170, 172, 174) is a magnet switch 170 for rotating the hydraulic control valve 150 in the direction of pressing the lower valve body pressing rod (156a), one end is connected to the hydraulic control lever 160 and the other end of the vehicle Accel of the cable 172 and the cable 172 is connected to the accelerator pedal (not shown) of the side to rotate the hydraulic control lever 160 in the direction of pressing the upper valve body pressing rod 156 by the pedal force of the accelerator pedal When the hydraulic control lever 160 is rotated in the direction when the clutch 12 is blocked, it is elastically connected to the pedal side connection part, and is elastically deformed while the hydraulic control rotated in the direction when the clutch 12 is blocked by the elastic force. Reverse the lever 160 in the state of half clutch The charge consists of an elastic spring 174.

In the hydraulic control lever control means (170, 172, 174) configured as described above, the magnet switch 170 is installed and fixed by the fixing piece 176 in place of the valve body 151, the magnet switch 170 is It is connected to one end of the hydraulic control valve 150 through the connecting rod (170-1). At this time, the above-described magnet switch 170 only rotates the hydraulic control lever 150 in the direction of the clutch 12 when the clutch 12 is blocked (when the power is cut off), and the hydraulic control lever 150 rotates in the reverse direction. It does not work. That is, even if the force of the magnet switch 170 acting in the rotational direction when the hydraulic control lever 150 is blocked (when power is interrupted) of the clutch 12 disappears, the magnet switch 170 maintains the hydraulic control lever 160. The state is maintained as long as no external force is applied without rotating in the reverse direction.

Therefore, if the force of the magnet switch 170 continues to operate in the rotational direction when the hydraulic control lever 150 is interrupted (when the power is interrupted), the hydraulic pressure control lever 150 cannot be rotated in the reverse direction. .

On the other hand, when the force of the magnet switch 170 acting in the rotational direction when the hydraulic control lever 150 is blocked (when the power is blocked) when the clutch 12 is interrupted, the external force for rotating the hydraulic control lever 150 in the reverse direction is It stays in that state unless it works.

On the other hand, the magnet switch 170 as described above is electrically connected to the magnet switch operating portion (not shown) installed in the indoor location of the vehicle, especially the gear shifting lever (not shown), the on / off of the magnet switch operating portion Controlled by (On / Off) control. That is, when the magnet switch operating part is turned on, the hydraulic control lever 160 is rotated by the magnet switch 170 in the direction when the clutch 12 is blocked (when power is transmitted), while the magnet switch operating part is turned off ( In the case of off, the hydraulic pressure control lever 160 is operated in the reverse direction when the clutch 12 is shut off (power cut off), that is, the external force to rotate in the direction when the clutch 12 is connected (when power is being transferred). The rotated state of the control lever 160 is maintained.

The cable 172 is for rotating the hydraulic control lever 160 rotated in the direction when the clutch 12 is blocked (when power is interrupted) in the direction when the clutch 12 is connected (when power is transmitted). One end of 172 is connected to the hydraulic control lever 160, the other end is connected to the accelerator pedal (not shown) side of the car when the hydraulic control lever 160 is connected to the clutch 12 by the pedal force of the accelerator pedal ( Rotation of the upper valve body pressing rod 156.

The elastic spring 174 of the hydraulic control lever control means is for reversely rotating the hydraulic control lever 160, which is completely rotated in the direction of the clutch 12, in a half-clutch state, and the elastic spring 174 is a cable. 172 is elastically connected to the accelerator pedal side connection portion. That is, the elastic spring 174 is elastically deformed when the hydraulic control lever 160 is rotated in the direction of the clutch 12 when the clutch 12 is blocked (when the power is blocked), and then when the hydraulic control lever 160 is blocked by the clutch 12 ( When the force to rotate in the direction of power interruption) disappears (magnet switch 170 is off), the hydraulic control lever 160 is connected to the clutch 12 (at the time of power transmission) as much as it is elastic through its restoring force. In reverse direction to bring the clutch 12 into the anti-clutch state.

On the other hand, the entire length of the cable 172 including the elastic spring 174 of the non-elastic state without pressing the accelerator pedal is connected to the position of the hydraulic control lever 160 from the side of the accelerator pedal to be connected. It consists of a length that reaches the position of the half-clutch state, which is the middle part of the state completely rotated in the direction (when power transmission) and the state completely rotated in the direction of the clutch 12 (blocking power) when the clutch 12 is shut off. The elastic spring 174 is configured to be elastic in the liver in a state in which the position of the 160 is completely rotated from the half-clutch state when the clutch 12 is cut off (power cut off).

Therefore, the cable 172 described above is in a loose state when the accelerator pedal is not pressed when the position of the hydraulic control lever 160 is fully rotated in the direction of the clutch 12 connection, whereas the hydraulic control lever 160 is The position is moved in the direction when the clutch 12 is interrupted and becomes taut after the state in which the position of the half clutch state is reached.

By the above-described configuration, the elastic spring 174 on the cable 172 side clutches the position of the hydraulic control lever 160 when the cable 172 is loose and the ON signal of the marknet switch 170 is on. When moving in the direction of interruption (power interruption) of (12), from the state where the position of the hydraulic control lever 160 reaches the position of the half clutch state, when the clutch 12 is completely blocked (at the time of power interruption) When it is elastic and stretches until it reaches a position, the clutch 12 is blocked by the restoring force of the elastic spring 174 on the cable 172 side when the mark net switch 170 is off. The hydraulic control lever 160 rotated in the direction is reversely rotated in the state of the half clutch as the elastic spring 174 is elastic, so that the state becomes the half clutch.

The elastic spring 180 of the clutch operating device 100 for a semi-automatic variable speed vehicle according to the present invention returns the booster piston 142 to the booster 140 when the clutch 12 is connected (power transmission) through its restoring force. To discharge the hydraulic pressure to the outside, the elastic spring 180 is supported between the hydraulic control valve 150 and the hydraulic cylinder 130 to boost the booster piston 142 and the piston 132 of the hydraulic cylinder 130 The force acts in the direction of constant repositioning.

In the elastic spring 180 installed as described above, the communication hole 151c is closed by the lower valve body 154a by the rotation of the hydraulic control lever 160 in the direction of the clutch 12 connection (power transmission), When the upper valve element pressing rod 156 opens the through hole 152-1 of the upper cap 152 by the operation of pressing the upper valve element 154, the hydraulic pressure supplied to the booster 140 disappears. The elasticity is restored by the restoring force. At this time, the booster piston 142, the hydraulic control valve 150 and the piston 132 of the hydraulic cylinder 130 moved in the direction of the clutch 12 is blocked (power off) by the restoring force of the elastic spring 180. This clutch 12 is moved in the direction at the time of connection (power sawing).

On the other hand, the semi-automatic shift vehicle clutch operation apparatus 100 according to the present invention is further provided with a means for adjusting the movement distance of the piston 132 of the hydraulic cylinder 130 by adjusting the position of the hydraulic control lever 160, this The piston movement distance adjusting means of the hydraulic cylinder is coupled to the front and rear movement on the upper connection rod 120 of the plurality of connection rods 120, while being formed in the upper and lower through the appropriate position to rotate the hydraulic control lever 160 Hydraulic control lever of the long groove so that the range can be limited by the rotation range restriction groove (190a) is provided through the screw connection to the place of the diaphragm (110b) where the hydraulic control lever position adjustment piece 190 and the booster 140 is installed and fixed The screw is coupled to the hydraulic control lever position adjusting piece 190, while consisting of the adjusting piece adjusting screw 192 for moving the hydraulic control lever position adjusting piece 190 back and forth through the rotation.

The piston 132 moving distance adjusting means of the hydraulic cylinder 130 configured as described above moves the hydraulic adjusting lever position adjusting piece 190 through the rotation of the adjusting piece adjusting screw 192, and then the moved hydraulic adjusting lever. The hydraulic flow of the hydraulic control valve 150 is positioned by positioning the hydraulic control lever 160 in the direction of connecting the clutch 12 which is one end of the hydraulic control lever rotation range limiting groove 190a of the position adjusting piece 190 (when power is transmitted). By changing the position of the piston 132 of the hydraulic cylinder 130 by moving the hydraulic control valve 150 to the moving position of the hydraulic control lever 160 to adjust the moving distance of the piston 132 of the hydraulic cylinder 130 To help.

An example of adjusting the moving distance of the piston 132 through the moving distance adjusting means of the piston 132 of the hydraulic cylinder 130 described above is as follows. First, the position of the hydraulic control lever 160 is completely rotated in the direction (when the power transmission) when the clutch 12, which is one end of the hydraulic control lever rotation range restriction groove 190a of the hydraulic control lever position adjustment piece 190 is connected. Suppose that, if the hydraulic control lever position adjusting piece 190 is slightly moved in the direction of the hydraulic cylinder 130 by rotating the adjusting piece adjusting screw 192, as much as the moved position of the hydraulic control lever position adjusting piece 190 The hydraulic control lever 160 rotates in the direction of the hydraulic cylinder 130, that is, the direction when the clutch 12 is blocked, thereby pressing the lower valve body pressing rod 156a to lower the valve body 154a downward. By moving the communication hole (151c) is opened by the rotation range of the hydraulic control lever 160.

As described above, when the communication hole 151c is opened by the rotation range of the hydraulic control lever 160, the upper hydraulic chamber 151a through the communication hole 151c in which the hydraulic pressure introduced from the hydraulic source into the lower hydraulic chamber 151b is opened. ) Is supplied to the booster 140 through the hydraulic pipe 146. Accordingly, the booster piston 142 is moved as much as the hydraulic pressure supplied to the booster 140, and the piston 132 in the hydraulic cylinder 130 is also moved by the movement of the booster piston 142 to move the piston 132. Shorter distance.

As described above, after the movement distance of the piston 132 is adjusted, the hydraulic control lever 160 is returned to its original position so that the force for pressing the lower valve body pressing rod 156a disappears so that the lower valve body 154a communicates with the communication hole 151c. To close.

When the piston 132 of the hydraulic cylinder 130, the movement distance adjusting means is configured as described above, each vehicle is different according to its type, when the clutch operating device 100 for a semi-automatic variable speed vehicle according to the present invention is installed in a vehicle. This is to adjust the pressure for clamping the clutch 12 of the clutch device 10.

Hereinafter, the state of the clutch automatic operation device 100 for the semi-automatic transmission vehicle having the above-described configuration when the clutch 12 is blocked (when the power is shut off), the half clutch state and the state when the clutch 12 is connected (when the power is transmitted) The operation of the hydraulic control valve 150 and the inlet control lever 160 will be described in detail.

Figure 5a is a side view showing the rotation state of the hydraulic control lever when the clutch is blocked (power off) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention, Figure 5b is a hydraulic control of the clutch operation device for a semi-automatic variable speed vehicle according to Figure 5a Figure 5c is a cross-sectional view showing the operating state of the lever and the hydraulic control valve, Figure 5c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve when the clutch is shut off (power off) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention. 5D is a cross-sectional view illustrating an operation state of a hydraulic control lever and a hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to FIG. 5C.

First, the state illustrated in FIGS. 5A to 5D shows a state of the clutch 12 of the semi-automatic shift vehicle clutch operating device 100 according to the present invention when the clutch 12 is blocked (when power is interrupted), as shown in FIG. 4A. Likewise, the hydraulic control lever 160 is completely rotated in the direction when the clutch 12 is connected (when power is transmitted) (as shown in FIG. 4A, the hydraulic control lever rotation range limiting groove 190a of the hydraulic control lever position adjusting piece 190 is shown. In the state where the hydraulic control lever 160 is completely rotated to the left end, and the cable 172 is stretched without pressing the accelerator pedal, the magnet switch 170 is turned on as shown in FIGS. 5A and 5B. When the hydraulic control lever 160 is completely rotated in the direction when the clutch 12 is cut off (power cut off) by the operation, the elastic spring 174 on the cable 172 side is elastically deformed and the cable 172 is Tension, the lower valve element pressing rod 15 by the hydraulic control lever 160 6a) is pressed and the lower valve body 154a is moved to the lower side to open the communication hole 151c.

As described above, when the communication hole 151c is opened, the hydraulic pressure introduced from the hydraulic source into the lower pressure chamber 151b flows into the upper pressure chamber 151a through the communication hole 151c, and the upper pressure chamber ( The hydraulic pressure introduced into the 151a is supplied to the booster 140 through the hydraulic pipe 146 and boosted by the booster 140.

On the other hand, the pressure boosted by the booster 140 pushes the booster piston 142, and accordingly the boost pressure is increased by the hydraulic cylinder (the piston rod 134 on the booster piston rod 144 and the hydraulic cylinder 130 side). The piston 132 of the 130 is advanced so that hydraulic pressure is generated in the hydraulic cylinder 130.

As described above, the pressure generated in the hydraulic cylinder 130 is supplied through the hydraulic supply path 17 (see FIG. 3) of the clutch device 10 through the hydraulic supply pipe 130a to open the valve hole 18a. The air pressure generated by the pump 18 is introduced into the clutch booster 20 through the valve hole 18a through the air pressure induction pipe 18b, and the introduced air pressure moves the clutch booster piston 20a to release the cylinder ( The push rod 22a of 22 is moved, and the shift of the push rod 22a causes the shift lever 24 to separate the clutch disk of the clutch 12 from the drive plate of the engine, thereby interrupting the power transmitted to the flywheel. . That is, the clutch 12 is cut off.

On the other hand, when the pressure boosted by the booster 140 in the above-described description pushes the booster piston 142 and the booster piston rod 144 is moved, the hydraulic control valve 150 is also moved by the moving distance of the booster piston 142. The posture of the hydraulic control lever 160 is moved and the hydraulic pressure of the hydraulic control lever position adjusting piece 190 as shown in FIG. 5D when the clutch 12 is blocked (when the power is blocked) as shown in FIGS. 5C and 5D. The hydraulic control lever 160 is moved to the right end of the lever rotation range limiting groove 190a, so that the lower valve body pressing rod 156a is not pressed. Accordingly, the hydraulic pressure in the hydraulic control valve 150 does not flow.

Figure 6a is a side view showing the rotation state of the hydraulic control lever in the semi-clutch state of the clutch operation device for semi-automatic variable speed vehicle according to the present invention, Figure 6b is a hydraulic control lever and hydraulic control of the clutch operation device for a semi-automatic variable speed vehicle according to Figure 6a. Figure 6c is a cross-sectional view showing the action state of the valve, Figure 6c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve in the semi-clutch state of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention, Figure 6d according to Figure 6c This is a cross-sectional view showing the working condition of the hydraulic control lever and the hydraulic control valve of the semi-automatic clutch operating device for a vehicle.

6A to 6D show a semi-clutch state of the clutch 12 through the clutch operating device 100 for the semi-automatic variable speed vehicle according to the present invention, and the booster piston 142 as shown in FIGS. 5C and 5D. The hydraulic control valve 150 is also moved as much as the moving distance of) so that the hydraulic control lever 160 does not press the lower valve body pressing rod 156a, that is, when the clutch 12 is blocked (when power is blocked). In the state (state in which the hydraulic control lever 160 is completely moved to the right end of the hydraulic control lever rotation range limiting groove 190a of the hydraulic control lever position adjusting piece 190 as shown in FIG. 5D), in FIGS. 6A and 6B. When the mark net switch 170 is off (Off) so that the force pulling the hydraulic control lever 160 in the direction of clutch disconnection (power off) disappears, the hydraulic control lever 160 blocks the clutch 12 Elastic edge when fully rotated in the clockwise (power off) direction The cable consisting of 172 side elastic spring (174), connects elastically deformed by the clutch 12 by the restoring force of (on a power transmission) to rotate by pulling the hydraulic control lever 160 in the direction.

That is, when the hydraulic control lever 160 is pulled and rotated in the direction when the clutch 12 is connected (power transmission) as much as it is elastically deformed by the restoring force of the elastic spring 174 as described above, the hydraulic control lever 160 6A and 6B, the middle portion of the clutch 12 connection (power transmission) and the clutch 12 blocking (power interruption) (the hydraulic control lever position adjusting piece (in FIGS. 6A and 6B) Hydraulic control lever of the rotating range 190 is limited to the rotational groove (190a) between the right end and the left end middle}.

As described above, when the hydraulic control lever 160 is rotated to an intermediate portion of the clutch 12 when the clutch 12 is connected (power transmission) and when the clutch 12 is blocked (power interruption), the pressure plate by the hydraulic control lever 160 157 is pressed by the rotation range of the hydraulic control lever 160, accordingly, the upper valve body pressing rod 156 presses the upper valve body 154 to move the upper valve body 154 to the lower by the hydraulic control lever. The through hole 152-1 of the upper cap 152 is opened by the rotation range of 160.

When the through hole 152-1 of the upper cap 152 is opened, the hydraulic control valve 150 is driven by a force to restore the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130. Is moved in the direction when the clutch 12 is connected (power transmission), so that the booster piston 142 retracts by the restoring force of the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130. do.

When the above-described booster piston 142 is retracted by the restoring force of the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130, the hydraulic pressure introduced into the booster 140 is the hydraulic pipe 146. Through the through-hole 152-1 of the upper cap 152 is introduced into the upper hydraulic chamber 151a and is discharged to the outside air.

On the other hand, the hydraulic pressure introduced into the booster 140 is the outside air through the through-hole 152-1 of the upper cap 152 by the restoring force of the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130 6C and 6D, when the hydraulic control valve 150 is retracted by the restoring force of the elastic spring 180, the posture of the hydraulic control lever 160 is the clutch 12 as shown in Figs. 6C and 6D. ) Middle part of connection (when power transmission) and clutch 12 (blocking power) (the hydraulic control lever rotation range limiting groove 190a of the hydraulic control lever position adjusting piece 190 in FIGS. 6C and 6D) It moves to the middle between a right end and a left end, and it does not press the upper valve body pressing bar 156. This state is commonly referred to as the anti-clutch state.

That is, the force for interrupting the clutch 12 by the operation as shown in Figs. 5A and 5D disappears about half by the operation as shown in Figs. 6A to 6D, so that the clutch disc (not shown) is driven by the engine. The state is half connected to the plate (not shown), and thus the state becomes the half-clutch state after the operation as in 6a to 6d is performed.

Figure 7a is a side view showing the rotation state of the hydraulic control lever when the clutch connection (power transmission) of the clutch operation device for a semi-automatic variable speed vehicle according to the present invention, Figure 7b is a hydraulic control of the clutch operation device for a semi-automatic variable speed vehicle according to Figure 7a Figure 7c is a cross-sectional view showing the action state of the lever and the hydraulic control valve, Figure 7c is a side view showing the action of the hydraulic control lever according to the movement of the hydraulic control valve when the clutch connection (power transmission) of the clutch operating device for a semi-automatic variable speed vehicle according to the present invention. FIG. 7D is a cross-sectional view illustrating an operation state of a hydraulic control lever and a hydraulic control valve of the clutch operating device for a semi-automatic variable speed vehicle according to FIG. 7C.

7A to 7D show a state when the clutch 12 is connected (power transmission) of the clutch operation device 100 for a semi-automatic variable speed vehicle according to the present invention, as in FIGS. 6C and 6D. When the accelerator pedal (not shown) is pressed in the half-clutch state, the hydraulic control lever 160 is connected to the clutch 12 by the pedal force of the accelerator pedal when the clutch 12 is connected (when the power is transmitted) (the hydraulic pressure is adjusted in FIGS. 7A and 7B). It is rotated in the left end direction} of the hydraulic control lever rotation range limiting groove (190a) of the lever position adjustment piece (190).

As described above, when the hydraulic control lever 160 is rotated in the direction when the clutch 12 is connected (power transmission) by the pedal force of the accelerator pedal, the pressing plate 157 is driven by the hydraulic control lever 160 to the hydraulic control lever 160. ), The upper valve body pressing rod 156 presses the upper valve body 154 to move the upper valve body 154 downward so that the upper cap is rotated by the rotation range of the hydraulic control lever 160. The through hole 152-1 of 152 is opened.

When the through hole 152-1 of the upper cap 152 is opened, the hydraulic control valve 150 is restored by the force to restore the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130. ) Is moved in the direction of the clutch 12 connection (power transmission), so that the booster piston 142 retracts by the restoring force of the elastic spring 180 between the hydraulic control valve 150 and the hydraulic cylinder 130. do.

When the above-described booster piston 142 is retracted by the restoring force of the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130, the hydraulic pressure introduced into the booster 140 is the hydraulic pipe 146. Through the through-hole 152-1 of the upper cap 152 is introduced into the upper hydraulic chamber 151a and is discharged to the outside air.

On the other hand, the hydraulic pressure introduced into the booster 140 is the outside air through the through hole 152-1 of the upper cap 152 by the restoring force of the elastic spring 180 installed between the hydraulic control valve 150 and the hydraulic cylinder 130. 7C and 7D, when the hydraulic control valve 150 is retracted by the restoring force of the elastic spring 180, the posture of the hydraulic control lever 160 is the clutch 12 as shown in Figs. 7C and 7D. ) When connected (in the case of power transmission) is moved to the left end of the hydraulic control lever rotation range limiting groove (190a) of the hydraulic control lever position adjustment piece 190 in Figs. 7c and 7d and the upper valve body push bar (156) ) Is not pressed.

As described above, the clutch disc (not shown) is completely connected to the drive plate (not shown) of the engine, or the clutch disc (not shown) is driven by the drive plate (not shown) of the engine when the clutch disk is not half clutch. Not closer).

Meanwhile, as shown in FIGS. 7A to 7D, the hydraulic control lever 160 is rotated in the direction when the clutch 12 is connected (power transmission) in proportion to the speed and the stepping force of the accelerator pedal, and also the hydraulic pressure control. Since the valve 150 is also moved in the direction when the clutch 12 is connected (power transmission) in proportion to the speed and stepping force of the accelerator pedal, the control of the clutch 12 is easy even on a hill.

The present invention is not limited to the above embodiments, and various modifications can be made within the scope of the technical idea of the present invention.

As described above, according to the present invention, the clutch is easily mounted on an existing vehicle, and thus, the clutch can be controlled relatively easily compared to the conventional operation of the clutch pedal. In particular, the clutch operation device for a semi-automatic variable speed vehicle according to the present invention, as well as the operation of the clutch using the clutch pedal, can be operated by hand to provide convenience in use.

Another effect of the present invention is to facilitate the operation of the state of the van clutch so that even if the foot is stepping on the clutch pedal quickly in the half-clutch section, the engine does not turn off or the vehicle does not snooze. Easy to control

Another effect of the present invention is to be able to operate not only the clutch pedal but also the electronically controlled operation unit is an effect that can be easily operated by the disabled clutch.

In addition, another effect of the present invention has the advantage that it is easy to install and remove by connecting the clutch operation device for a semi-automatic variable speed vehicle to an existing clutch device.

In addition, the present invention can provide an improved function as a semi-automatic system than the conventional semi auto, in addition to the effects described above, and can provide a device having a simpler structure and a lower cost than the conventional semi auto.

Claims (13)

In the clutch device for an automobile comprising a master cylinder for transmitting the force of the clutch pedal, a clutch booster for boosting the pressure generated by the master cylinder, and a shift lever for controlling the clutch by the action of the clutch booster, Plates formed in a plate shape of a predetermined size and arranged on both sides of a predetermined distance; A plurality of connecting rods for opposing the diaphragms on both sides; A hydraulic cylinder installed at the front side of the diaphragm and having a piston installed therein, for supplying the generated hydraulic pressure to the clutch booster to block the clutch; A booster piston installed at a rear end of the other side plate and connected to a piston of the hydraulic cylinder, and boosting hydraulic pressure to operate the hydraulic cylinder through the booster piston; It is installed on the connecting portion of the piston and the booster piston of the hydraulic cylinder so as to be moved at the same time by the distance moved in the forward and backward movement direction of the piston to supply the hydraulic pressure supplied from the hydraulic source to the booster when the clutch is blocked, Hydraulic control valve for controlling the hydraulic pressure by discharging the hydraulic pressure supplied to the booster to the atmosphere when the clutch is connected; A hydraulic control lever rotatably installed in place of the hydraulic control valve to switch the flow of hydraulic pressure in the hydraulic control valve to the booster and the atmospheric side through rotation by an external force; Hydraulic control lever control means for controlling the rotation of the hydraulic control lever in the direction when the clutch is shut off and connected so that the flow of the hydraulic pressure in the hydraulic control valve can be switched to the booster and the atmospheric side; And Supported between the hydraulic control valve and the hydraulic cylinder is made of an elastic spring acting in the direction to force the booster piston and the piston of the hydraulic cylinder at all times to the original position, When the clutch is interrupted, the hydraulic control valve is moved in the same direction by the action of the booster and the elastic spring by the rotational movement distance of the hydraulic control lever. While the clutch does not flow to the atmosphere, after the clutch is blocked, the hydraulic control lever is actuated in the reverse direction by an intermediate portion of the clutch when the clutch is blocked and connected by the action of the hydraulic control lever control means. With the rotation of the hydraulic control valve is moved in the same direction by the rotational distance of the hydraulic control lever so that the hydraulic pressure of the hydraulic control valve to the neutral state does not flow into the booster and the atmosphere to maintain a half clutch state Semi-automatic variable speed clutch clutch device. The clutch operating device of claim 1, further comprising means for adjusting a piston movement distance of the hydraulic cylinder by adjusting the position of the hydraulic control lever. The method of claim 2, wherein the piston movement distance adjusting means of the hydraulic cylinder is coupled to the front and rear movement on the upper connection rod of the plurality of connecting rods, while being formed in the upper and lower through the appropriate position to rotate the hydraulic control lever Hydraulic control lever position adjustment piece equipped with a rotation range restriction groove of the long groove to limit the range; And The booster is screwed to the hydraulic adjustment lever position adjusting piece to penetrate through the screw connection to the place where the installation is fixed, while consisting of the adjusting piece adjusting screw for moving the hydraulic control lever position adjusting piece back and forth through rotation, After moving the hydraulic control lever position adjustment piece through the rotation of the adjustment screw adjustment screw, the hydraulic control lever in the direction of the clutch connection which is one end of the hydraulic control lever rotation range restriction groove of the moved hydraulic control lever position adjustment piece. Position the piston to move the hydraulic control valve to the moving position of the hydraulic control lever through the hydraulic flow of the hydraulic control valve to change the piston position of the hydraulic cylinder to adjust the piston movement distance of the hydraulic cylinder. Semi-automatic clutch actuating device. The hydraulic cylinder of claim 1, wherein the hydraulic pressure generated in the master cylinder of the automotive clutch device is supplied to the clutch booster through the hydraulic cylinder to control the clutch. Clutch operating device for a semi-automatic variable speed vehicle, characterized in that connected to the pipe. The method of claim 4, wherein the hydraulic transmission pipe is to supply the pressure generated by the stepping force of the clutch pedal to the clutch booster through the master cylinder and the hydraulic cylinder so that the clutch pedal can be intermittent by the clutch pedal. Semi-automatic variable speed clutch clutch device. According to claim 1, wherein the hydraulic pressure control valve is formed in the pressure chamber of the space is formed in the form of the outer side in the upper and lower, respectively communicate with each other through the communication hole, while the lower side pressure chamber is supplied with hydraulic pressure from the hydraulic source A valve body having an inlet hole formed therein and an upper side pressure chamber having a supply hole for supplying hydraulic pressure to the booster; Upper and lower caps which are screwed to the upper and lower pressure chambers, and screwed to the upper pressure chamber, the upper and lower caps having through-holes formed therethrough; A sealing ring supported at each of an inner end of the through hole of the upper cap and a lower end of the communication hole which is an upper end of the lower pressure chamber; The outer peripheral surface is in close contact with each of the sealing ring is installed in each of the pressure chamber to close the through hole of the upper cap and the lower portion of the communication hole, but the one installed in the upper pressure chamber through the center vertically through the through hole is formed The lower side pressure chamber is provided with a conical upper and lower valve body having a seat groove formed at the front end of the center; An elastic spring in which the elastic force acts in the direction in which the upper and lower valve bodies are supported in the respective pressure chambers to be in contact with the sealing ring at all times; While contacting the outer circumference of the front end surface of the upper valve body through the through hole of the upper cap, the outer end is formed to protrude outward of the upper cap, the rotation of the hydraulic control lever in the direction of the clutch connection by the A hollow upper valve body pressing rod for pressing the upper valve body; One end passes through a through hole of the upper valve body and is coupled to a seat groove of the lower valve body through the hollow of the upper valve body pressing rod, while the other end protrudes outwardly than the upper valve body pressing rod to adjust the hydraulic pressure. A lower valve element pressing rod that presses the lower valve element by rotation of a lever in a direction when the clutch is blocked; And Semi-automatic shifting characterized in that the hinge is coupled to the upper portion of the valve body rotatably for a certain range and is pressed by rotation in the direction of the clutch connection of the hydraulic control lever to press the upper valve body pressing rod. Automotive clutch actuator. According to claim 6, wherein the hydraulic control lever is hinged to a certain range rotatable in place of the valve body of the upper side of the pressing plate is rotated in the direction of the closing of the clutch to press the lower valve body pressing rod, the clutch And the upper valve body pressing plate is pushed through the upper valve body pressing plate when rotated in the direction of connection. 8. The clutch of claim 7, wherein the lower portion of the hydraulic control lever is further provided with a pressing piece for pressing the upper valve body pressing plate when the hydraulic control lever rotates in the direction of the clutch connection. Device. [9] The semi-automatic shift of claim 8, wherein a sealing ring fixing part associated with the sealing ring is formed at each of the lower end of the communication hole, the inner end of the through hole of the upper cap and the upper end of the lower pressure chamber. Automotive clutch actuator. 10. The clutch actuating device of claim 9, wherein a spring support portion is formed at one end of the upper pressure chamber lower end and the lower cap to support one end of the elastic spring to support the elastic spring. According to any one of claims 1 to 6, wherein the hydraulic control lever control means is installed in place of the hydraulic control valve magnet switch for rotating the hydraulic control lever in the direction of pressing the lower valve body pressing rod; A cable, one end of which is connected to the hydraulic control lever and the other end of which is connected to an accelerator pedal side of the vehicle to rotate the hydraulic control lever in a direction of pushing the upper valve body pressing rod by the pedal force of the accelerator pedal; And The hydraulic control lever is elastically connected to the connection portion of the accelerator pedal side of the cable and is elastically deformed when the hydraulic control lever rotates in the direction when the clutch is blocked, while the hydraulic control lever rotates in the direction when the clutch is blocked by the elastic force. Semi-automatic clutch operating device for a semi-automatic variable speed vehicle characterized in that it comprises an elastic spring to rotate in the state of the half clutch. 12. The method of claim 11, wherein the cable is loose when the position of the hydraulic control lever is not rotated when the accelerator pedal is fully rotated in the direction in which the clutch is connected, while the position of the hydraulic control lever is The clutch operating device for a semi-automatic variable speed vehicle, characterized in that it is made of a length that becomes taut after being moved in the direction of blocking and reaching the position of the semi-clutch state. 12. The method of claim 11, wherein the elastic spring on the cable side is the hydraulic pressure control when the position of the hydraulic pressure control lever in the direction of the closing of the clutch when the On signal of the mark net switch in the loose state of the cable While the position of the lever reaches the position of the half-clutch state, the elastically stretches from the state of reaching the position at the time of complete shutoff of the clutch, while the elastic spring of the cable side of the cable when the OFF signal of the marknet switch The clutch operating device for a semi-automatic variable speed vehicle characterized in that the hydraulic control lever rotated in the direction at the time of blocking the clutch through an elastic force reverses the state of the half clutch so as to be in the half clutch state.