JP4260459B2 - Operating force assist device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an operation force assist device, and more particularly to an operation force assist device that is applied to a vehicle that requires clutch operation, such as a four-wheeled vehicle, a two-wheeled vehicle, and an industrial vehicle, and assists the clutch operation.
[0002]
The operation for releasing the clutch is performed by a driver stepping on a clutch pedal in a four-wheeled vehicle, an industrial vehicle, or the like, and in a two-wheeled vehicle, the driver holds a clutch lever. In recent years, with the improvement of the horsepower of the engine, the improvement of the clutch mechanism, etc., a stronger spring member has been incorporated in the clutch mechanism, and a stronger force is required for the operation of releasing the clutch. . For this reason, especially in the case of driving of a vehicle that frequently performs clutch operation or driving for a long time, or in the case of a driver with a weak operating force, the clutch operation has become a burden.
[0003]
[Prior art]
In order to solve this problem, various operation force assist devices for assisting clutch operation have been proposed and put into practical use. One conventional operating force assist device uses the hydraulic pressure of pressurized oil that is forcibly circulated in the engine. However, with this device, it is necessary to provide an extra oil outlet to the engine, and the engine must be modified. Further, when the operating force assist device is installed at a location away from the engine, it is necessary to provide a long pipe for guiding the circulating oil from the engine to the operating force assist device, which complicates the device. As described above, the operating force assist device configured to use the pressurized oil from the engine has a problem that it is difficult to install because the engine needs to be modified and the piping needs to be installed.
[0004]
In view of this, an operation force assist device having a configuration in which a dedicated hydraulic pump is provided and the hydraulic pressure of pressurized oil from the hydraulic pump is used has been proposed.
[0005]
[Patent Document 1]
Japanese Patent No. 2643400 (page 3 and FIG. 4)
[0006]
[Problems to be solved by the invention]
Although the above-described problem can be solved with the operating force assist device provided with this dedicated hydraulic pump, there is a problem in that the hydraulic pump keeps driving at all times, so that power consumption increases and energy saving cannot be achieved.
[0007]
Accordingly, an object of the present invention is to provide an operating force assist device that solves the above-described problems.
[0008]
[Means for Solving the Problems]
  In order to solve the above-mentioned problem, the invention of claim 1 is an operation force assisting device for adding an assist force to an operation force with a medium.
  A cylinder,
A primary piston made of a metal material, provided in the cylinder, to which an operating force is applied;
A portion having an auxiliary force output and a large-diameter piston portion having a cross-sectional area wider than the cross-sectional area of the portion outputting the auxiliary force, and the side having the large-diameter piston portion is the operating force of the primary piston. Is provided in the cylinder so as to face the end opposite to the side to which the pressure is applied, forms a pressurizing chamber between the primary piston and the large-diameter piston portion, and outputs an auxiliary force. A secondary piston made of a metal material;
When the primary piston to which the operating force is applied moves and hits the secondary piston and the primary piston and the secondary piston are electrically connected to each other, it is detected that the primary piston has pressed against the secondary piston. Detection means;
Pump means for applying pressure to the pressurizing chamber,
The pump means starts in response to detection by the detection means.It is supposed to be configured.
[0011]
A strong auxiliary force can be obtained with a simple configuration in which the shape of the secondary piston is appropriately determined.
[0012]
  Claim2The invention of claim1In the operation force assist device described in
  A medium pressure release path and a valve mechanism that opens and closes the medium pressure release path. When the primary piston and the secondary piston are separated, the valve mechanism opens the medium pressure release path and pressurizes the medium pressure release path. A medium pressure releasing means for releasing the medium pressure in the room is further provided.
[0013]
Since the medium pressure release path is opened when the primary piston and the secondary piston are separated, the operating force assist device is restored to the original state before the operation when the operating force applied to the primary piston is released. The operation to perform is performed smoothly.
[0014]
  Claim3The invention according to claim2In the operation force assist device described in
  When the space between the primary piston and the secondary piston becomes narrow, the valve mechanism and the detection means are closed first, and then the detection means performs a detection operation so that there is a gap between the primary piston and the secondary piston. When expanding, the detection means is first in a non-detection state, and then the valve mechanism is opened.
[0015]
Since the valve mechanism is closed when the pump means is started, it is possible to prevent the medium pressure generated by the pump means from escaping outside and being wasted. That is, since the valve mechanism is closed when the pump means is started, the medium pressure generated by the pump means can be applied to the large-diameter piston portion of the secondary piston without any waste.
[0016]
  Claim4The invention of claim 1 to claim 13The operation force assist device according to any one of the above is configured to assist the operation force of the clutch operation unit.
[0017]
It is possible to realize a vehicle that can perform clutch operation with a light operating force.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
  [First embodiment]
  FIG. 1 shows an operating force assist device 10 according to a first embodiment of the present invention. The operating force assist device 10 includes a device main body 11, an electric motor 70, a hydraulic pump 80, an oil tank 90, and a motor drive circuit 100. The operation force assist device 10 is unitized and generalized. It is easy to attach to a vehicle or the like. The operating force assist device 10 is independent of the vehicle engine (both not shown), and the clutch pedal 110 or the clutch lever 111 and the clutch device are seen in an appropriate place of the vehicle, that is, the transmission path of the operating force. Used at a location between 120 and 120. Since the operating force assist device 10 is unitized and small, it can be mounted on a two-wheeled vehicle. As will be described later, the operating force assist device 10 is a motor when the clutch pedal 110 or the clutch lever 111 is operated.70Starts and hydraulic pump80Is driven to generate hydraulic pressure, and the main body 11 is operated by this hydraulic pressure to assist the operating force of the clutch pedal 110 or the clutch lever 111, so that the clutch device 120 is disengaged. The clutch device 120 has a general configuration including a clutch plate 122 fixed to an engine-side shaft 121, a clutch plate 124 fixed to a wheel-side shaft 123, and a clutch release cylinder mechanism 125.
[0019]
The apparatus main body 11 includes a main cylinder 12, an output cylinder 20, a primary piston 30, a secondary piston 40, a seal valve body 50, and a piston switch contact component 60.
[0020]
The main cylinder 12 is made of an electrically conductive metal material, has a cylinder portion 13 for a primary piston on the X2 side, and a cylinder portion 14 for a first piston portion of a secondary piston on the X1 side. The inner diameter of the cylinder portion 13 is D1, and the inner diameter of the cylinder portion 14 is D2. D1 is approximately ½ of D2. Reference numeral 15 denotes a step portion between the inside of the cylinder portion 13 and the inside of the cylinder portion 14. The cylinder portion 13 has a hydraulic relief hole 16 formed at a substantially central portion thereof, the cylinder portion 14 has a hydraulic pressure supply hole 17 near the step portion 15, and oil holes 18 and 19 formed at a substantially central portion thereof. is there. Anodized surface treatment is applied to the inner diameter portions of the cylinder portions 13 and 14 for electrical insulation and sliding protection.
[0021]
The output cylinder 20 is made of an electrically conductive metal material, and includes a cylinder portion 21 for a second piston portion for a secondary piston, and an output port 22 on the X1 side. An oil residual pressure release hole 23 is formed at a location on the X2 side of the cylinder portion 21. The inner diameter of the cylinder portion 21 is D3. D3 is approximately ½ of the inner diameter D2 of the cylinder portion 14, and boosts the assist force generated by this relationship. The output cylinder 20 is fixed in a state of being fitted into the cylinder portion 14 of the main cylinder 12 and electrically connected to the main cylinder 12.
[0022]
With the apparatus main body 11 attached to the vehicle body, the output cylinder 20 is electrically connected to a part of the vehicle body and grounded.
[0023]
As shown in FIGS. 2 and 3, the primary piston 30 is made of an electrically conductive metal material, has a diameter D <b> 1, has a small-diameter portion 31 at the center, and an end surface on the X <b> 1 side. A T-shaped hydraulic relief through hole 34 is formed to connect between the center of 32 and the peripheral surface of the small diameter portion 31. 34 a is an opening to the end face 32 of the through hole 34. The primary piston 30 has an anodized surface treatment for electrical insulation and sliding protection on the peripheral surface except for the end faces 32 and 33.
[0024]
An annular piston switch contact component 60 is fixed to the end face 32. A push rod receiving member 35 is fixed to the end surface 33. Both the component 60 and the member 35 are made of an electrically conductive metal material. The piston switch contact component 60 protrudes from the end surface 32 by the dimension a. Further, seals 36 and 37 are fitted to the primary piston 30.
[0025]
  The primary piston 30 is fitted in the cylinder portion 13 of the main cylinder 12 and is a stopper ring member.39Dropout is limited by. A cylindrical space 38 is formed around the small diameter portion 31.
[0026]
The through hole 34, the space 38, and the hole 16 form a hydraulic pressure release path 200.
[0027]
As shown in FIGS. 2 and 3, the secondary piston 40 is made of an electrically conductive metal material, has a first piston portion 41 having a diameter D2 on the X2 side, and has a X1 side on the X1 side. It has the 2nd piston part 42 whose diameter is D3. A concave step portion 41 a for forming a first pressurizing chamber 105 described later is formed on the X2 side of the first piston portion 41. A portion between the first piston portion 41 and the second piston portion 42 has a diameter smaller than D3. Seals 43 and 44 are fitted to the piston portions 41 and 42. D2 is substantially twice D3, and the sectional area S2 of the first piston portion 41 is substantially four times the sectional area S3 of the second piston portion 42. This relationship boosts the assist force.
[0028]
A cylindrical portion 45 protrudes from the first piston portion 41 to the X2 side. The diameter of the cylindrical portion 45 is D4, which is slightly shorter than D1. As shown in FIG. 2, a seal valve body 50 is incorporated in the space 46 inside the cylindrical portion 45. The seal valve body 50 has a seal portion 51 on the X2 side. The seal portion 51 is smaller than the inner diameter of the annular piston switch contact component 60 and has a size capable of closing the opening 34a, and is made of rubber or synthetic resin having electrical insulation. The seal valve body 50 is pushed in the X2 direction by the back spring 52 and contacts the stopper portion 47, and the seal portion 51 protrudes from the end face 45a of the cylindrical portion 45 in the X2 direction by the dimension b. The dimension b and the dimension a have a relationship of a <b. (Ba) is slight. Further, the seal valve body 50 and the end face 32 of the primary piston 30 constitute a hydraulic release path valve 210.
[0029]
In the secondary piston 40, the first piston portion 41 is fitted to the cylinder portion 14 of the main cylinder 12, the second piston portion 41 is fitted to the output cylinder 20, and the column portion 45 is loosely fitted to the cylinder portion 13. is doing. A cylindrical space 48 is formed around the cylindrical portion 45. The secondary piston 40 is moved in the X2 direction by the return spring 49 and hits the step portion 15. A first pressurizing chamber 105 is formed by the recessed step portion 41 a and the corner portion of the cylinder portion 14, and a second pressurizing chamber 106 is formed by the second piston portion 42 and the output cylinder 20. Yes. The first pressurizing chamber 105 is a pressurizing chamber in an initial state. The hydraulic pressure supply hole 17 communicates with the first pressurizing chamber 105 in the initial state. When the secondary piston 40 is moved in the X1 direction, the shape of the first pressurizing chamber 105 changes. That is, as shown in FIG. 7A, when the secondary piston 40 is moved in the X1 direction, the first piston portion 41 is separated from the step portion 15, and the chamber 105 and the space 48 communicate with each other. 1 communication pressure chamber 105A.
[0030]
  Inside the cylinder part 13, the end face 32 of the primary piston 30 and the end face of the secondary piston 4045aAnd approach each other. The primary piston 30, the piston switch contact component 60, and the secondary piston 40 constitute a clutch operation detection switch 211. The secondary piston 40 is electrically connected to a part of the vehicle body via the return spring 49 and the output cylinder 20.
[0031]
  Here, the end surface 32 of the primary piston 30 and the end surface of the secondary piston 4045aIs a real distance H between the primary piston 30 and the secondary piston 40.
[0032]
Here, the operation of the detection switch 211 and the hydraulic pressure release path valve 210 when the actual distance H is changed will be described.
[0033]
  As shown by line I in FIG. 4A, when the primary piston 30 approaches the secondary piston 40 and changes in the direction in which the actual distance H is shortened, the opening 34a becomes the seal portion 51 when the actual distance H becomes the dimension b. Is closed and the hydraulic pressure release path valve 210 is closed (see FIG. 4B), and when the actual distance H is further shortened to the dimension a, the hydraulic pressure release path valve 210 remains closed (FIG. 4). (See (B)), piston switch contact part 60 and end face45a is contacted, the detection switch 211 is closed (see FIG. 4C), and the motor 70 is started (see FIG. 4D).
[0034]
When the motor 70 is started, the hydraulic pump 80 is driven, the hydraulic pressure is sent to the first communication pressurizing chamber 105A, and the hydraulic pressure acts on the first piston portion 41 to generate the assist force in the X1 direction.
[0035]
  As shown by line II in FIG. 4A, when the secondary piston 40 moves away from the primary piston 30 and changes in the direction in which the actual distance H becomes longer, first, the piston switch contact component 60 and the end face are changed.45aAnd the detection switch 210 is opened (see FIG. 4C), the motor 70 is stopped (see FIG. 4D), and the hydraulic pressure release path valve 210 is still closed (see FIG. 4D). (See FIG. 4B). When the secondary piston 40 is further moved in the X1 direction and the actual distance H exceeds the dimension b, the seal portion 51 is separated from the end face 32 and the hydraulic pressure release path valve 210 is opened (see FIG. 4B), and the opening 34a. Is opened and the hydraulic pressure release path 200 is opened.
[0036]
When the hydraulic pressure release path 200 is opened, the hydraulic pressure in the first communication pressurizing chamber 105 </ b> A is released to the outside through the hydraulic pressure release path 200, and the secondary piston 40 is generated in the second pressurizing chamber 106. This time, it is moved in the X2 direction by the hydraulic pressure and the return spring 49.
[0037]
Accordingly, the relative positions of the primary piston 30 and the secondary piston 40 are maintained so that the actual distance H remains within a limited small range between the dimension a and the approximate dimension b.
[0038]
In FIG. 1, the motor 70 is normally stopped, and when it is started, the hydraulic pump 80 is driven. The motor driving circuit 100 is provided with its terminal 101 electrically connected to a push rod 112 made of a metal rod. When the potential of the terminal 101 becomes the ground potential, the motor 70 is started and the potential of the terminal 101 is set. When the voltage changes from the ground potential to the non-ground potential, the motor 70 is stopped. The motor drive circuit 100 is provided with an adjustment unit 102 that adjusts the degree of increase in rotation when the motor 70 is started. For example, for a female driver with a weak depression, the duty ratio of the motor drive signal sent from the motor drive circuit 100 to the motor 70 is adjusted by operating the adjustment unit 102 so that the actual operation time of the motor 70 is lengthened. . This increases the assist force.
[0039]
The push rod 112 is in contact with the receiving member 35 and is moved in the X1 direction when the clutch pedal 110 or the clutch lever 111 is operated to push the primary piston 30 in the X1 direction.
[0040]
The hydraulic pump 80 is provided in the middle of a pipe 81 that connects the hole 19 and the hole 17. A check valve 82 is provided between the hydraulic pump 80 and the hole 17. The oil tank 90 is provided in the middle of the pipe 91 that connects the hole 16 and the hole 18. A filter 92 is provided between the oil tank 90 and the hole 18. The pipe 91 and the pipe 81 communicate with each other through the hole 18, the internal space of the cylinder portion 14, and the hole 19. The oil is used not only for generating assist force but also for lubricating the inside of the cylinder part 14 and for lubricating the inside of the cylinder part 13.
[0041]
Next, the operation force assist operation of the operation force assist device 10 having the above-described configuration when the driver depresses the clutch pedal 110 to release the clutch device 120 will be described.
[0042]
Before the clutch pedal 110 is depressed, the operating force assist device 10 and the clutch device 120 are in the state shown in FIGS. 1, 2, and 6A.
[0043]
(1) When the clutch pedal 110 is depressed normally
FIG. 5 shows the operating state of the operating force assist device 10 and the operating state of the clutch device 120 when the clutch pedal 110 is normally depressed deeply.
[0044]
When the driver normally depresses the clutch pedal 110, the primary piston 30 is pushed through the push rod 112 and moved in the X1 direction at once. The secondary piston 40 is pushed by the primary piston 30 and at the same time in the X1 direction by the assist force. The clutch release cylinder mechanism 125 is operated by the hydraulic pressure from the second pressurizing chamber 106 and the clutch device 120 is disconnected.
[0045]
FIGS. 6A to 6C and FIGS. 7A and 7B are views for explaining the operation of the operation force assist device 10.
[0046]
  When the driver depresses the clutch pedal 110, the primary piston 30 is pushed through the push rod 112 and moved in the X1 direction. First, as shown in FIG. 6B, the opening 34a is blocked by the seal portion 51. Then, the hydraulic pressure release path valve 210 is closed, and then, as shown in FIG.45a, The detection switch 211 is closed and the motor 70 is started. Also, the piston switch contact part 60 has an end face.45aBy pressing the secondary piston 40 starts moving in the X1 direction, and as shown in FIG. 7A, the first piston portion 41 moves away from the step portion 15, and the first pressurizing chamber 105, the space 48, Are communicated, and the first pressurizing chamber 105 becomes the first communicating pressurizing chamber 105A.
[0047]
When the motor 70 is started, the hydraulic pump 80 is driven, oil is fed into the first communication pressurizing chamber 105A through the hydraulic pressure supply hole 17, and the hydraulic pressure P acts on the first piston portion 41, and the secondary piston. 40 generates an assist force AF as an assist force in the X1 direction. Therefore, after that, the secondary piston 40 reaches the final position shown in FIG. 7B in the X1 direction by the force (F + AF) obtained by adding the assist force AF to the force (depression force) F by the operation of depressing the clutch pedal 110. Pressed.
[0048]
As shown in FIG. 5, the clutch release cylinder mechanism 125 is operated by the hydraulic pressure generated in the second pressurizing chamber 106 as the secondary piston 40 moves in the X1 direction, and the clutch plate 124 is separated from the clutch plate 122. The clutch is disengaged.
[0049]
Therefore, the operation for the driver to depress the clutch pedal 110 when disengaging the clutch is light.
[0050]
When the clutch pedal 110 is depressed, the drag force increases accordingly, and the depression force F changes as shown by line III in FIG. The assist force AF changes so as to increase as the stroke increases as shown by line IV. A line V is a force output from the apparatus main body 11, that is, a force obtained by adding the assist force AF to the stepping force F. The ratio of the depression force F to the assist force AF, F1: AF1, and F2: AF2 in each stroke are substantially the same. Therefore, the driver feels heavy enough to depress the clutch pedal 110, and there is no sense of incongruity.
[0051]
  The hydraulic pressure P generated in the first communication pressurizing chamber 105A also acts to push back the primary piston 30 in the X2 direction. But,(1)The cross-sectional area of the primary piston 30 is as narrow as about 1/4 of the cross-sectional area S2 of the first piston portion 41, and the piston switch contact component 60 is the end face.45aWhen the hydraulic pressure P is pressed against the primary piston 30, the force acting on the primary piston 30 becomes approximately ¼, and when the hydraulic pressure P further increases, the secondary piston 40 slightly moves in the X1 direction immediately and is used for the hydraulic pressure release path. The valve 210 is opened to release excess hydraulic pressure to the oil tank 90;(2)The oil pressure P is gradually generated,(3)Since the primary piston 30 is not stopped but moved in the X1 direction like the secondary piston 40, the driver does not feel kickback.
[0052]
When the driver releases his / her foot from the clutch pedal 110 after performing the gear shift operation, as shown in FIG. 9A, the primary piston 30 is slightly moved in the X2 direction by the hydraulic pressure P in the first communication pressurizing chamber 105A. Then, the hydraulic pressure release path valve 210 is opened, and the hydraulic pressure release path 200 is opened. Further, the secondary piston 40 starts to move in the X2 direction by the hydraulic pressure generated in the second pressurizing chamber 106 and the back spring 52.
[0053]
While the secondary piston 40 and the primary piston 30 return the oil in the first communication pressurizing chamber 105A to the oil tank 90 through the hydraulic pressure release path 200 while the actual distance H is maintained at the distance of the above-described dimension b, The initial state shown in FIG. 9B is restored.
[0054]
When the secondary piston 40 is returned to the initial state, the clutch is completely connected.
[0055]
While the gear shift operation is performed with the clutch pedal 110 fully depressed, the secondary piston 40 has an actual distance H with respect to the primary piston 30 as shown in FIGS. It is maintained at a distance of approximately the above dimension b.
[0056]
Here, a case where the motor 70 and the hydraulic pump 80 are not driven due to a failure will be described. In this case, although the assist force AF is not generated, the secondary piston 40 is moved by being pushed by the primary piston 30, the clutch device 120 is normally operated, and fail-safe is achieved.
[0057]
(2) About the case where the clutch pedal 110 is slowly depressed halfway so as to be a half clutch and held in that position.
FIG. 10 shows the operating state of the operating force assist device 10 and the operating state of the clutch device 120 when the clutch pedal 110 is depressed halfway and held in that position. The clutch device 120 is in a half-clutch state.
[0058]
FIGS. 11A to 11C show states when the clutch pedal 110 is slowly depressed.
[0059]
  When the driver slowly depresses the clutch pedal 110, the primary piston 30 is moved in the X1 direction via the push rod 112, the secondary piston 40 is pushed and moved in the X1 direction, as shown in FIG. 11A. , The opening 34a is closed by the seal 51, the hydraulic pressure release valve 210 is closed, and the piston switch contact component 60 is connected to the end face.45a, The detection switch 211 is closed, the motor 70 is started, and the hydraulic pump 80 is driven. When the hydraulic pump 80 is driven, hydraulic pressure is generated in the first communication pressurizing chamber 105A and acts on the first piston portion 41, and the secondary piston 40 is moved in the X1 direction, and FIG. As shown. The hydraulic pressure acting on the piston portion 41 becomes an assist force. End face45aIs separated from the piston switch contact component 60, the detection switch 211 is opened, the motor 70 is stopped, and the hydraulic pump 80 is stopped. The stop of the hydraulic pump 80 is delayed due to the inertial rotation of the motor 70, etc., and the secondary piston 40 has an end face.45aIs slightly moved after the piston switch contact part 60 is separated, the seal portion 51 is separated from the end face 32, the hydraulic pressure release path valve 210 is opened, the hydraulic pressure release path 200 is opened, and the excessive assist force is released.
[0060]
  During this time, the primary piston 30 continues to move slowly in the X1 direction. While causing the oil in the first communication pressurizing chamber 105A to flow out from the hydraulic pressure release path 200, the primary piston 30 moves in the X1 direction, the end face 32 hits the seal portion 51, and the hydraulic pressure release path valve 210 is closed. As shown in FIG. Furthermore, the piston switch contact part 60 is an end face.45a, The detection switch 211 is closed, the motor 70 is started, the hydraulic pump 80 is driven, and an assist force is generated.
[0061]
In the process in which the driver slowly depresses the clutch pedal 110, the above-described operation is repeated, and the secondary piston 40 is applied with the assist force and maintains the state close to the primary piston 30, while the X1 Moved in the direction.
[0062]
FIGS. 12A to 12C show the operating state of the operating force assist device 10 when the clutch pedal 110 is held at an intermediate position.
When the clutch pedal 110 is held at an intermediate position, it is assumed that the hydraulic pressure release path valve 210 is closed and the detection switch 211 is closed as shown in FIG.
[0063]
  The motor 70 is started, the hydraulic pump 80 is driven, the hydraulic pressure is generated in the first communication pressurizing chamber 105A, acts on the first piston portion 41, and the secondary piston 40 is moved in the X1 direction. End face45aIs separated from the piston switch contact part 60, the detection switch 211 is opened, the motor 70 is stopped, and the hydraulic pump 80 is stopped. However, the stop of the hydraulic pump 80 is delayed due to inertial rotation of the motor 70, etc.45a12 moves slightly from the piston switch contact part 60, and as shown in FIG. 12B, the seal 51 is separated from the end face 32, the hydraulic pressure release path valve 210 is opened, and the hydraulic pressure release path 200 is opened. It will be in the state. Subsequently, the secondary piston 40 is moved in the X2 direction by the hydraulic pressure generated in the second pressurizing chamber 106 and the back spring 52 while causing the oil in the first communication pressurizing chamber 105A to flow out from the hydraulic pressure release path 200. Then, the end face 32 comes into contact with the seal portion 51 and the hydraulic pressure release path valve 210 is closed, resulting in a state shown in FIG. When the hydraulic pressure release path valve 210 is closed, the movement of the secondary piston 40 in the X2 direction is stopped.
[0064]
That is, the secondary piston 40 is maintained at the position of the above-described dimension b with respect to the primary piston 30, and the clutch device 120 is stably maintained in a half-clutch state.
[0065]
Even when the clutch pedal 110 is normally depressed, as shown in FIGS. 12A to 12C, the secondary piston 40 is the primary piston while the gear shift operation is performed in the depressed state. The actual distance H with respect to 30 is maintained at the distance of the above-described dimension b.
[0066]
When the driver releases his / her foot from the clutch pedal 110, the apparatus main body 11 is restored to the initial state in the same manner as described above.
[0067]
[Second Embodiment]
FIG. 13 shows an operating force assist device 10A according to a second embodiment of the present invention. The operating force assist device 10A is different from the operating force assist device 10 shown in FIG.
[0068]
The apparatus main body 11A has a structure in which the seal valve body 50 is incorporated on the X1 side of the primary piston 30A and the secondary piston 40A has a T-shaped hydraulic pressure relief hole 34A.
[0069]
This operating force assist device 10A requires only one pipe between the oil tank 90 and the apparatus main body 11A.
[0070]
The operation force assist devices 10 and 10A can be applied to an operation mechanism unit other than the clutch mechanism. Moreover, it can be provided not only in the vehicle but also in a construction machine equipped with an engine.
[0071]
【The invention's effect】
  As described above, the invention according to claim 1In an operating force assist device for adding an auxiliary force with a medium pressure to an operating force; a cylinder; a primary piston made of a metal material provided in the cylinder to which the operating force is applied; and a portion for outputting the auxiliary force And a side having the large-diameter piston portion having a cross-sectional area wider than the cross-sectional area of the portion for outputting the auxiliary force, and the side having the large-diameter piston portion is the side of the primary piston to which the operating force is applied. A secondary made of a metallic material that is provided in the cylinder so as to face the opposite end, forms a pressure chamber between the primary piston and the large-diameter piston portion, and outputs an auxiliary force. The primary piston to which the operating force is applied moves and hits the secondary piston, and the primary piston and the secondary piston are electrically Detecting means for detecting that the primary piston has pressed against the secondary piston due to electrical conduction; and pump means for applying pressure to the pressurizing chamber, and in response to detection by the detecting means Since the pump means is configured to start, power consumption can be suppressed as compared with a configuration in which the pump means is constantly driven, and a strong auxiliary force is provided with a simple structure that appropriately determines the shape of the secondary piston. Can be obtained.
[0073]
  Claim2Since the invention according to the above configuration further includes a medium pressure releasing means for releasing the medium pressure in the pressure chamber when the primary piston and the secondary piston are separated, the operating force applied to the primary piston When the operation is canceled, the operation force assist device can be smoothly restored to the original state before the operation.
  Claim3In the invention according to the present invention, when the space between the primary piston and the secondary piston becomes narrow, the valve mechanism is closed first, and then the detection means performs a detection operation so that the space between the primary piston and the secondary piston When the pressure spreads, the detection means is first in a non-detection state, and then the valve mechanism is opened. Therefore, when the pump means is started, the valve mechanism is closed, so that the medium pressure generated by the pump means escapes to the outside. Can be prevented. That is, since the valve mechanism is closed when the pump means is started, the medium pressure generated by the pump means can be applied to the large-diameter piston portion of the secondary piston without any waste, and thus the auxiliary force is efficiently obtained. I can do it.
[0074]
  Claim4The invention according to claim 1 to claim 13The operation force assist device according to any one of the above is configured so as to assist the operation force of the clutch operation unit, so that the vehicle can perform the clutch operation with a light operation force. Can be realized.
[Brief description of the drawings]
FIG. 1 is a view showing an operating force assist device according to a first embodiment of the present invention together with a clutch device.
2 is an enlarged view of a part of the apparatus main body in FIG.
FIG. 3 is a view showing a primary piston and a secondary piston facing each other.
FIG. 4 is a diagram for explaining operations of a valve, a switch, and a motor when an actual distance is changed.
FIG. 5 is a diagram showing an operating state of the operating force assist device and the clutch device when the clutch pedal is normally depressed.
FIG. 6 is a diagram showing an operating state of the operating force assist device when the clutch pedal is normally depressed.
FIG. 7 is a diagram showing an operation state of the operation force assist device following FIG. 6 (C).
FIG. 8 is a diagram showing a relationship between a clutch pedal depression stroke and generated assist force.
FIG. 9 is a diagram illustrating the operation of the operation force assist device when the depression of the clutch pedal is released.
FIG. 10 is a diagram showing the operating state of the operating force assist device and the clutch device when the clutch pedal is slowly depressed halfway and held in that position.
FIG. 11 is a diagram showing an operating state of the operating force assist device and the clutch device in the process of slowly depressing the clutch pedal halfway.
FIG. 12 is a diagram showing the operation of the operating force assist device when the clutch pedal is depressed halfway and held in that position.
FIG. 13 is a view showing an operating force assist device according to a second embodiment of the present invention together with a clutch device.
[Explanation of symbols]
10, 10A operation force assist device
11, 11A device body
12, 12A main cylinder
20 Output cylinder
30 Primary piston
34 Hydraulic relief through hole
40 Secondary piston
50 Seal valve body
60 Piston switch contact parts
70 Electric motor
80 Hydraulic pump
90 oil tank
100 Motor drive circuit
105 First pressurizing chamber
105A First communication pressurizing chamber
106 Second pressurizing chamber
110 Clutch pedal
111 Clutch lever
120 Clutch device
200 Hydraulic release path
210 Hydraulic release path valve
211 Clutch operation detection switch

Claims (4)

In an operation force assist device that adds an auxiliary force with medium pressure to the operation force,
A cylinder,
A primary piston made of a metal material , provided in the cylinder, to which an operating force is applied;
A portion having an auxiliary force output and a large-diameter piston portion having a cross-sectional area wider than the cross-sectional area of the portion outputting the auxiliary force, and the side having the large-diameter piston portion is the operating force of the primary piston. Is provided in the cylinder so as to face the end opposite to the side to which the pressure is applied, forms a pressurizing chamber between the primary piston and the large-diameter piston portion, and outputs an auxiliary force. A secondary piston made of a metal material ;
When the primary piston to which the operating force is applied moves and hits the secondary piston and the primary piston and the secondary piston are electrically connected, it is detected that the primary piston has pressed against the secondary piston. Detection means;
Pump means for applying pressure to the pressurizing chamber,
An operating force assisting device characterized in that the pump means is started in response to detection by the detecting means. The operation force assist device according to claim 1 ,
A medium pressure release path and a valve mechanism that opens and closes the medium pressure release path. When the primary piston and the secondary piston are separated, the valve mechanism opens the medium pressure release path and pressurizes the medium pressure release path. An operating force assisting device characterized by further comprising a medium pressure releasing means for releasing the medium pressure in the room. The operating force assist device according to claim 2 ,
When the space between the primary piston and the secondary piston becomes narrow, the valve mechanism and the detection means first close the valve mechanism, and then the detection means performs a detection operation, and the space between the primary piston and the secondary piston is An operating force assisting device having a configuration in which, when expanding, the detecting means is first in a non-detecting state and then the valve mechanism is opened. A vehicle comprising the operation force assist device according to any one of claims 1 to 3 so as to assist an operation force of a clutch operation unit.

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