WO2018220918A1

WO2018220918A1 - Load generation device

Info

Publication number: WO2018220918A1
Application number: PCT/JP2018/007157
Authority: WO
Inventors: 雄輝汲川; 中村　祐一郎; 大志須山; 亮祐永谷
Original assignee: アイシン精機株式会社
Priority date: 2017-05-31
Filing date: 2018-02-27
Publication date: 2018-12-06
Also published as: JP2018205884A

Abstract

[Problem] To provide a load generation device having improved performance with respect to existing problems. [Solution] This load generation device is provided with: a first movable member which slides inside a first cylinder according to an operating force of a clutch pedal; a first load generation part disposed inside the first cylinder and including a first load generation spring; a second movable member which slides inside a second cylinder according to the operating force; and a second load generation part disposed inside the second cylinder and including a second load generation spring, wherein a load is generated on the clutch pedal by sliding the first and second movable members in series and thereby stretching/contracting the first and second load generation springs in conjunction with a rotation assist spring that is locked in a different position than a rotation shaft of the clutch pedal and inverts the operating force during rotation.

Description

Load generator

The technology disclosed in the present application relates to a load generator that generates a load (reaction force) on a clutch pedal.

Instead of an operation on the clutch pedal, a vehicle that employs a system in which the load generator generates a load (reaction force) on the clutch pedal while the actuator controls the load on the clutch to execute connection / disconnection of the clutch. Conventionally known.

The load generator disclosed in Patent Document 1 includes a piston that engages with a cylinder, a spring that is disposed between the piston and the end of the cylinder, and a piston that is formed on the piston and gradually increases from the tip toward the center. The cam part which has an outer diameter which reduces gradually toward a rear end from a part, and the cylindrical member provided facing the cam part in a cylinder are included.

The cylindrical member formed of an elastic material has an opening for receiving the cam portion, and a plurality of elastic pieces divided by a plurality of slits extending along the axial direction adjacent to the opening. In response to depression of the clutch, the piston slides toward the end of the cylinder against the biasing force of the spring. In parallel with this, the cam portion pressed by the piston enters the inside of the cylindrical member from the opening against the urging force of the plurality of elastic pieces trying to maintain the original shape. While the leading end to the center of the cam portion enters the inside of the cylindrical member, the cam portion receives a biasing force that gradually increases from a plurality of elastic pieces, and the remaining portion of the cam portion is inside the cylindrical member. During the intrusion, the cam portion receives a biasing force that gradually decreases from the plurality of elastic pieces. Thereby, the load generator disclosed in Patent Document 1 generates a reaction force (load) against the clutch by combining the urging force caused by the spring and the urging force caused by the plurality of elastic pieces. The entire contents of Patent Document 1 are incorporated herein by reference.

German Patent Application Publication No. 102014425996

However, in the load generator described in Patent Document 1, since the friction coefficient of the cam portion that slides with respect to the cylindrical member has a large influence on the load characteristics, the cam can be stabilized to stabilize the friction coefficient. Costs resulting from surface treatment, heat treatment, and the like on the part occur. In addition, with repeated use of the load generating device, the cam portion may wear, and the originally intended load characteristics may not be obtained. Furthermore, since there is a possibility that the cam portion may become a source of abnormal noise by sliding with respect to the cylindrical member, there is a possibility that the navigation environment in the vehicle interior is deteriorated.

Therefore, the present application provides a load generator having improved performance with respect to the conventional problems according to various embodiments.

A load generator according to an aspect includes a first cylinder, a first moving member that slides in the first cylinder in response to an operation force of a clutch pedal, and the first moving member that engages with the first moving member. A first load generating portion having a first load generating spring disposed in a pre-compressed manner in the cylinder; a second cylinder; and a second moving member that slides in the second cylinder in response to the operating force. And a second load generating spring that is engaged with the second moving member and is pre-compressed in the second cylinder, and a rotation of the clutch pedal. The first moving member and the second moving member are slid in series in cooperation with a rotation assist spring that is locked at a position different from the axis and reverses the operation force during rotation. Extending or contracting at least one of the first load generating spring and the second load generating spring And by those which generate a load against the clutch pedal.

It is a schematic diagram which shows the structural example of the load generator which concerns on one Embodiment. It is a figure which shows the specific example of the characteristic of the load given to a clutch pedal by the load generator shown in FIG. FIG. 3 is a schematic diagram for conceptually explaining load characteristics shown in FIG. 2. It is a schematic diagram which shows the structural example of the load generator which concerns on another embodiment. It is a schematic diagram which shows the structural example of the load generator which concerns on another embodiment. It is a schematic diagram which shows the structural example of the load generator which concerns on another embodiment.

Hereinafter, various embodiments will be described with reference to the accompanying drawings. In addition, the same referential mark is attached | subjected to the same component in drawing. It should also be noted that components represented in one drawing may be omitted in another drawing for convenience of explanation. Furthermore, it should be noted that the attached drawings are not necessarily drawn to scale.

1. Configuration of Load Generating Device A load generating device according to an embodiment is mounted on a vehicle adopting a system in which an actuator controls a load on a clutch to execute connection / disconnection of the clutch instead of an operation by a driver on a clutch pedal. Is. The load generator according to the present embodiment generates a load (reaction force) on the clutch pedal.

FIG. 1 is a schematic diagram illustrating a configuration example of a load generator according to an embodiment. As shown in FIG. 1, the load generating device 10 extends from one end 102 to the other end 104 and rotates around a central axis 106, and is provided so as to be rotatable with respect to the rotating member 100. The sliding member 200, the master cylinder 300 engaged with the sliding member 200, the load generating unit 400 connected to the master cylinder 300, and the rotating member 100 are provided so as to be rotatable (rotating). And a torsion spring 700 (as one mode of the assist spring). Further, the load generator 10 can optionally include a reservoir tank 800 coupled to the master cylinder 300.

1-1. Rotating member 100
The rotating member 100 extends from one end 102 to the other end 104, and can be formed as a rod-shaped member with a metal such as iron, steel, an aluminum alloy, or a titanium alloy. A clutch pedal C is fixed to one end 102 of the rotating member 100. A combination of the rotating member 100 and the clutch pedal C can be understood as a “clutch pedal”.

Between the one end 102 and the other end 104 of the rotating member 100 (in the vicinity of the other end 104 of the rotating member 100 in the example shown in FIG. 1), a direction orthogonal to the extending direction of the rotating member 100 (on the paper surface). A central axis 106 extending in the depth direction) is formed. The first wall surface W ₁ of the vehicle, bearing unit 2 for rotatably supported by inserting the pivot member 110 is provided. Thereby, the rotation member 100 rotates in the forward direction (X ₁ ) around the central axis 106 supported rotatably by the bearing portion 2 (forward rotation) or in the reverse direction (X ₂ ) ( Can be reversed). Specifically, when the clutch pedal C is stepped on by a driver (not shown), the rotating member 100 rotates (forward) around the central axis 106 in the forward direction (X ₁ ). Later, when the clutch pedal C is released by the driver, the clutch pedal C can be rotated (reversely rotated) in the reverse direction (X ₂ ) around the central axis 106. As described above, since the combination of the rotating member 100 and the clutch pedal C can be understood as a “clutch pedal”, the central axis 106 can also be understood as the central axis of the clutch pedal. Is possible.

A torsion spring 700 is rotatably provided at the other end 104 of the rotating member 100. In order to realize such a connection, for example, a central axis (not shown) extending in a direction orthogonal to the extending direction of the rotating member 100 is provided at the other end 104 of the rotating member 100, and the torsion spring 700 is provided. It is possible to provide a bearing portion (not shown) that is inserted into the central axis of the other end 704 and is supported rotatably. Alternatively, the other end 704 of the torsion spring 700 is provided with a central axis (not shown) extending in a direction orthogonal to the extending direction of the rotating member 100, and the central axis applied to the other end 104 of the rotating member 100 is inserted. It is also possible to provide a bearing portion (not shown) that is rotatably supported.

The sliding member 200 is rotatably provided at the connecting portion 108 between the one end 102 of the rotating member 100 and the central shaft 106. In order to realize such a connection, for example, a connecting shaft 108 of the rotating member 100 is provided with a central axis (not shown) extending in a direction orthogonal to the extending direction of the rotating member 100, and the sliding member A bearing portion (not shown) that is rotatably supported by inserting a central axis applied to one end 202 of 200 can be provided. Alternatively, a central axis (not shown) extending in a direction orthogonal to the extending direction of the rotating member 100 is provided at one end 202 of the sliding member 200, and the central axis applied to the connecting portion 108 of the rotating member 100 is inserted. It is also possible to provide a bearing portion (not shown) that is rotatably supported.

1-2. Sliding member 200
The sliding member 200 extends from one end 202 to the other end 204, and can be formed as a rod-shaped member with a metal such as iron, steel, an aluminum alloy, or a titanium alloy. As described above, the one end 202 of the sliding member 200 is provided so as to be rotatable with respect to the connecting portion 108 of the rotating member 100. As the rotating member 100 rotates, the sliding member 200 moves in the direction intersecting the extending direction of the rotating member 100 (in the example shown in FIG. 1, for example, the extending direction of the master cylinder 300). Slide relative to the cylinder 300.

1-3. Master cylinder 300
The master cylinder 300 extends from one end 302 to the other end 304, and can be formed as a cylindrical member from a metal such as iron, steel, an aluminum alloy, or a titanium alloy. The master cylinder 300 has a cylindrical storage region 306 that stores hydraulic oil or the like inside.

The master cylinder 300 has a through hole 308 that communicates with the outside at one end 302 and receives the other end 204 of the sliding member 200. The master cylinder 300 has a columnar piston 310 coupled to the other end 204 of the sliding member 200 in the accommodation region 306. The piston 310 can be formed as a cylindrical member with a metal such as iron, steel, an aluminum alloy, or a titanium alloy.

The master cylinder 300 has an output port 312 that communicates with the first pipe 4 at the other end 304.

When the rotating member 100 is rotated in the forward direction (X ₁ ) around the central axis 106 (forward rotation) as the clutch pedal C is depressed by the driver, the sliding pressed by the rotating member 100 The member 200 moves toward the other end 304 of the master cylinder 300. Along with this, the piston 310 fixed to the other end 204 of the sliding member 200 slides toward the other end 304 of the master cylinder 300, so that the hydraulic oil stored in the storage region 306 is supplied to the output port 312 and The load is pressed toward the load generating unit 400 via the first pipe 4. Thereafter, when the clutch pedal C is released by the driver, the piston 310 slides toward the one end 302 of the master cylinder 300 by receiving a load from the load generating unit 400 via the hydraulic oil. Along with this, the sliding member 200 fixed to the piston 310 moves in a direction away from the other end 304 of the master cylinder 300. Since the rotating member 100 pressed by the sliding member 200 rotates (reverses) around the central axis 106 in the reverse direction (X ₂ ), the clutch pedal C returns to the original position.

1-4. Load generator 400
The load generating unit 400 includes a plurality of load generating units (two load generating units in the present embodiment). Specifically, the load generation unit 400 includes a first load generation unit 500 and a second load generation unit 600.

Roughly speaking, the first load generating unit 500 is disposed inside the first cylinder 510 facing the one end 502 of the first cylinder 510 and the first cylinder 510 extending from the one end 502 to the other end 504. A cylindrical first piston (first moving member) 520, and a first spring (first load generating spring) 530 that engages with the first piston 520 and is disposed inside the first cylinder 510. .

Roughly speaking, the second load generating part 600 extends from one end 602 to the other end 604 and is connected between the first cylinder 510 and the second cylinder 610 integrally formed with the first cylinder 510. A cylindrical second piston (second moving member) 620 disposed with the first spring 530 interposed therebetween, and a second spring (second assembly) disposed between the second piston 620 and the other end 604 of the second cylinder 610. 2 load generating springs) 630.

1-5. First load generator 500
An input port (first through hole) 506 communicating with both the first pipe 4 and the inside of the first cylinder 510 is formed at one end 502 of the first cylinder 510.

A plurality of annular grooves (two

grooves

522 and 524 in the example shown in FIG. 1) extending along the circumferential direction are formed on the outer periphery of the first piston 520. A cup (sealing) 526 and a cup (sealing) 528 are attached to the groove 522 and the groove 524, respectively, for preventing hydraulic oil from entering. A first convex portion 529 protruding from the surface of the first piston 520 facing the second piston 620 is formed.

The first spring 530 is disposed between the first piston 520 and the second piston 620 in a pre-compressed state (in a previously contracted state). Specifically, the first spring 530 is inserted (engaged) with the first protrusion 529 of the first piston 520 at one end 532, and the second protrusion described later is formed at the other end 534 on the second piston 620. By inserting (engaging) the portion 622, the portion 622 is disposed between the first piston 520 and the second piston 620. Accordingly, the first piston 520 is urged in the direction away from the second piston 620 by the first spring 530.

The first pre-compression amount (pre-compressed / contracted amount) of the first spring 530 and the first spring constant are set by the first spring 530 arranged pre-compressed as shown in FIG. Is set so as to contract when receiving a force (operation force of the clutch pedal) equal to or higher than a first threshold value from the first piston 520 pressed by the hydraulic oil supplied via the valve.

1-6. Second load generator 600
In one embodiment, second cylinder 610 is formed to have an inner diameter that is larger than the inner diameter of first cylinder 510. The second cylinder 610 has a protrusion (stepped portion) 606 formed on the inner wall near one end 602 thereof. The protruding portion 606 may extend, for example, in an annular shape. The protrusion 606 functions to contact the surface of the second piston 620 facing the first piston 520 and to restrict the sliding of the second piston 620 toward the first piston 520.

The second cylinder 610 has a columnar wall member 612 provided opposite to the second piston 620 in the vicinity of the other end 604. The wall member 612 is fixed by a snap ring 614 attached to the inner wall near the other end 604 of the second cylinder 610. A third convex portion 616 protruding from the surface of the wall member 612 facing the second piston 620 is formed.

The surface of the second piston 620 facing the first piston 520 is formed with a second convex portion 622 protruding from the surface. The second convex portion 622 is inserted into the other end 534 of the first spring 530 as described above. As a result, the second piston 620 is biased in a direction away from the first piston 520 by the first spring 530.

The surface of the second piston 620 that faces the second spring 630 or the wall member 612 is formed with a fourth convex portion 624 that protrudes from the surface.

The second spring 630 is disposed between the second piston 620 and the wall member 612 in a pre-compressed state (in a contracted state in advance). Specifically, the second spring 630 has one end 632 inserted (engaged) with the fourth convex portion 624 of the second piston 620 and the other end 634 inserted with the third convex portion 616 of the wall member 612 (engagement). By combining, the second piston 620 and the wall member 612 are disposed. As a result, the second piston 620 is biased in a direction away from the wall member 612 by the second spring 630.

The second pre-compression amount (pre-compressed / contracted amount) of the second spring 630 and the second spring constant are determined by the second spring 630 disposed in a pre-compressed manner as shown in FIG. Is set so as to contract when receiving a force (operation force of the clutch pedal) equal to or greater than a second threshold. This second threshold value is larger than the first threshold value described above.

According to the load generator 400 having the above-described configuration, the first piston 520 is pressed by the hydraulic oil supplied via the first pipe 4 as the clutch pedal C is depressed by the driver. When the force received from the first threshold value reaches and exceeds the first threshold value, the first spring 530 disposed in the first cylinder 510 by being pre-compressed further contracts. In this state, the first spring 530 presses the second piston 620 and thus the second spring 630 in a direction toward the wall member 612. However, when the force received by the second spring 630 from the second piston 620 is less than the second threshold value, the second spring 630 disposed in the second cylinder 610 by being pre-compressed does not further contract. Thereafter, when the clutch pedal C is further depressed by the driver, the force received by the second spring 630 from the second piston 620 reaches the second threshold value and exceeds the second threshold value. The second spring 630 disposed in a compressed state further contracts.

1-7. Torsion spring 700
The torsion spring 700 can be used as one mode of a rotation assist spring that generates a load on the clutch pedal C in cooperation with the first load generation unit 500 and the second load generation unit 600.

The torsion spring 700 extends from one end 702 to the other end 704 and can be formed of a linear elastic material. The torsion spring 700 includes a winding portion 706 that is wound a plurality of times between one end 702 and the other end 704 and extends annularly.

One end 702 of the torsion spring 700 is provided rotatably relative to the second wall _{W 2} of the vehicle. To achieve such a connection, among the one end 702 and the second wall W ₂ of the torsion spring 700 has either one (the paper-depth extending in a direction) central axis (not shown), the other It is possible to have a bearing portion (not shown) through which the central shaft is inserted and rotatably supported.

The other end 704 of the torsion spring 700 is provided so as to be rotatable with respect to the other end 104 of the rotating member 100 as described above. In order to realize such a connection, as described above, one of the other end 704 of the torsion spring 700 and the other end 104 of the rotating member 100 has a central axis (extending in the depth direction on the paper surface) (see FIG. And a bearing portion (not shown) that rotatably supports the other center shaft.

The torsion spring 700 functions to press the other end 104 of the rotation member 100 so as to resist or assist the rotation of the rotation member 100 according to the rotation of the rotation member 100.

Specifically, if a virtual line connecting one end 702 of the torsion spring 700 and the central axis 106 of the rotating member 100 is defined as a reference line L, the other end 704 of the torsion spring 700 is as shown in FIG. When the reference line L is sandwiched between the winding part 706 (at the position on the left side of the drawing with respect to the reference line L), that is, the other end 704 is pressed by the sliding member 200 when viewed from the reference line L. The torsion spring 700 resists rotation (forward rotation) in the forward direction (X ₁ ) of the rotation member 100 (in other words, rotation). The other end 104 of the rotating member 100 is pressed such that the moving member 100 assists in the rotation (reverse rotation) of the moving member 100 in the reverse direction (X ₂ ).

On the other hand, by the torsion spring 700 is rotated in the Y ₁ direction shown in FIG. 1 around the end 702, in the position of the winding portion 706 and the same side and the other end 704 of the torsion spring 700 is viewed from the reference line L ( In other words, the position where the other end 704 is displaced in the direction opposite to the direction in which the sliding member 200 is pressed when viewed from the reference line L (the right direction on the paper). The torsion spring 700 assists in the rotation (forward rotation) of the rotation member 100 in the forward direction (X ₁ ) (in other words, the rotation of the rotation member 100 in the reverse direction (X ₂ )). The other end 104 of the rotating member 100 is pressed so as to resist (reverse rotation).

1-8. Reservoir tank 800 (optional)
The reservoir tank 800 and the second pipe 6) used therewith are selectively used as an option.

The 1st piping 4 which connects the master cylinder 300 and the load generator 400 (the 1st load generator 500) and conveys hydraulic fluid has the possibility of retaining air in the inside with use. is there. When such an operation of extracting air from the first pipe 4 is performed, not only air but also hydraulic oil may be discharged from the first pipe 4. A reservoir tank 800 can be provided to replenish hydraulic oil to the master cylinder 300 when the hydraulic oil is insufficient.

The reservoir tank 800 stores hydraulic oil in the storage area 802. The reservoir tank 800 and the master cylinder 300 are connected by the second pipe 6. The second pipe 6 is attached to the reservoir tank 800 and the master cylinder 300 so as to communicate with the storage area 802 of the reservoir tank 800 and the storage area 306 of the master cylinder 300.

2. Operation of the load generator 10 First, a state in which the clutch pedal C is not depressed at all by the driver is shown in FIG. In this state, paying attention to the first load generating unit 500, the upper surface of the first piston 520 is adjacent to one end 502 of the first cylinder 510 because the first spring 530 is pre-compressed and disposed. Further, when focusing on the second load generating unit 600, the second spring 630 is disposed in a pre-compressed manner, so that a surface of the second piston 620 facing the first piston 520 is formed on the second cylinder 610. It is in contact with the protrusion 606. Further, focusing on the torsion spring 700, the other end 704 of the torsion spring 700 is located on the left side of the reference line L in the drawing.

When the clutch pedal C is depressed by the driver, the rotating member 100 rotates forward around the central axis 106. Accordingly, the sliding member 200 moves toward the other end 304 of the master cylinder 300, so that the piston 310 slides toward the other end 304 of the master cylinder 300 in the accommodation region 306 of the master cylinder 300. As a result, the hydraulic oil stored in the storage region 306 is pressed by the piston 310 and supplied to the input port 506 of the first load generating unit 500 via the first pipe 4.

In the first load generating unit 500, the first piston 520 is pressed in the direction toward the second piston 620 by the hydraulic oil supplied to the input port 506. At this time, it is assumed that the force received by the first spring 530 from the first piston 520 is not less than the first threshold and less than the second threshold. If it does so, the 1st spring 530 arrange | positioned by pre-compression will shrink | contract further by receiving the force beyond a 1st threshold value. Thereby, the first piston 520 slides in a direction approaching the second piston 620.

In the second load generation unit 600, the second piston 620 is pressed in the direction toward the wall member 612 by the first spring 530. Here, since the force received by the second spring 630 from the second piston 630 is less than the second threshold value, the second piston 620 has a surface facing the first piston 520 abutted against the protrusion 606 of the second cylinder 610. It does not slide so as to maintain the contacted state and approach the wall member 612.

On the other hand, paying attention to the torsion spring 700, the torsion spring 700 rotates around the one end 702 in the Y ₁ direction by pressing the other end 704 against the other end 104 of the rotation member 100. Here, the other end 704 of the torsion spring 700 is still located on the left side of the drawing from the reference line L. In this state, the torsion spring 700 receives a force that brings the one end 702 and the other end 704 closer from the other end 104 of the rotating member 100. The torsion spring 700 that has received such force tends to deform so as to return to its original shape (the one end 702 and the other end 704 are separated). As a result, the torsion spring 700 presses the other end 704 of the rotating member 100 so as to resist forward rotation of the rotating member 100 (helping reverse rotation).

Thereafter, when the clutch pedal C is continuously depressed by the driver, operations similar to those described above are performed in the master cylinder 300, the first load generating unit 500, the second load generating unit 600, and the torsion spring 700.

As described above, when the clutch pedal C is continuously depressed by the driver, the force received by the second spring 630 from the second piston 620 eventually reaches the second threshold value. Then, the second spring 630 that has been pre-compressed is further contracted. Thus, the second piston 620 slides in a direction approaching the wall member 612 against the biasing force from the second spring 630 (at this time, the first piston 520 and the second piston 620 are connected in series. It can be said that it is sliding.)

The torsion spring 700 presses the other end 704 from the other end 104 of the rotating member 100 at almost the same timing as when the second spring 630 receives a force equal to or greater than the second threshold and starts to contract further. by being, by continued to rotate in the Y ₁ direction around the end 702), the other end 704 of the torsion spring 700 located in the plane on the left side of the reference line L, beyond the reference line L , Located on the right side of the reference line L on the paper surface. Even in this state, the torsion spring 700 receives a force from the other end 104 of the rotating member 100 to bring the one end 702 and the other end 704 closer to each other. The torsion spring 700 receiving such a force tends to deform so as to return to its original shape (the one end 702 and the other end 704 are separated). Thereby, the torsion spring 700 presses the other end 704 of the rotating member 100 so as to assist the forward rotation of the rotating member 100 (resist the reverse rotation).

Thereafter, when the clutch pedal C is continuously depressed by the driver, the first spring 530 of the first load generating unit 500 and the second spring 630 of the second load generating unit 600 continue to contract, as described above. The torsion spring 700 is deformed so as to separate the one end 702 and the other end 704 in order to return to the original shape, and thereby the other end of the rotating member 100 is assisted to forward rotation of the rotating member 100. Continue pressing 104.

After this, when the clutch pedal C is released from the driver, the first spring 530 of the first load generating unit 500 and the second spring 630 of the second load generating unit 600 both expand, and FIG. Return to the state shown. Accordingly, the hydraulic oil pressed by the first piston 520 flows into the storage area 306 of the master cylinder 300 via the input port 506, the first pipe 4, and the output port 312. The piston 310 pressed by the hydraulic oil slides in a direction toward the one end 302 of the master cylinder 300. The sliding member 200 pressed by the piston 310 moves in a direction away from the master cylinder 300.

Rotating member 100 which is pressed by the sliding member 200, the _{X 2} direction to rotate (reverse) about a central axis 106. Along with the rotation member 100 rotates, the torsion spring 700, and rotates Y ₂ direction about one end 702, returns to the state shown in FIG. Even during the torsion spring 700 is rotated in this manner in the Y ₂ direction, when the other end 704 of the torsion spring 700 is positioned on paper right side of the reference line L, the torsion spring 700, the rotary member resist 100 _{X 2} direction rotation (reverse rotation), when the other end 704 of the torsion spring 700 is positioned on paper left side of the reference line L, the torsion spring 700, _{X 2} direction of the rotating member 100 There is no change in that it helps the rotation (reverse rotation).

3. Load Characteristics of Load Generating Device 10 FIG. 2 is a diagram showing a specific example (one example) of the characteristics of the load applied to the clutch pedal by the load generating device shown in FIG. FIG. 2 shows how much load or reaction force (unit [N]) is applied to the clutch pedal in association with the amount of depression of the clutch pedal, that is, the pedal stroke (unit [mm]). Are shown for each of the forward path (solid line) and the backward path (one-dot chain line).

In the example of the load characteristic shown in FIG. 2, focusing on the forward path, in the section (section A) from the time when the pedal stroke exceeds S1 [mm] to S2 [mm], the load on the clutch pedal is the pedal stroke. It is increasing in proportion to In the section (section B) from when the pedal stroke exceeds S2 [mm] to S3 [mm], the load on the clutch pedal decreases in inverse proportion to the pedal stroke. That is, in this section B, the load characteristic has a negative gradient. Thereafter, in the section (section C) from when the pedal stroke exceeds S3 [mm] to the end, the load on the clutch pedal is slightly increased in proportion to the pedal stroke.

In one embodiment, a half-clutch is obtained at any point in section B that results in a negative slope. As a result, the driver can feel that the half-clutch has been obtained in the section B where the clutch feels lighter than the section A.

Next, focusing on the return path, in the example of the load characteristics shown in FIG. 2, the return path load characteristics are generally similar to the forward load characteristics except that the magnitude of the load is reduced overall. It has become. There is a difference (hysteresis) in the magnitude of the load between the forward load characteristic and the return load characteristic (for example, when the pedal stroke is S2, the load is P2 in the forward load characteristic). On the other hand, in the load characteristic of the return path, the load is P1 (<P2) due to the frictional force caused by the sliding in the master cylinder 300, the first load generating unit 500, the second load generating unit 600, and the like. It is considered a thing.

Next, the reason why the load characteristic shown in FIG. 2 is obtained will be described with reference to FIG. FIG. 3 is a schematic diagram for conceptually explaining the load characteristics shown in FIG. In the load characteristics shown in FIG. 3, the horizontal axis and the vertical axis indicate the pedal stroke and the load, respectively, as in FIG. 2, but for the purpose of schematically showing the concept of the load characteristics, Therefore, it should be noted that the notation of the horizontal axis and the vertical axis is omitted.

As shown in FIG. 3, the first curve (the curve extending from the point P ₁ indicated by the two-dot chain line to the portion indicated by the dotted line via the point P ₂ ) uses only the first spring 530 (that is, An example of load characteristics obtained when the second spring 630 and the torsion spring 700 are not used) is shown. As shown in the first curve, the load on the clutch pedal is proportional (increases) to the pedal stroke.

Furthermore, the second curve (the curve indicated by the two-dot chain line extending from the point P ₁ to the point P ₃ via the point P ₂ ) uses only the first spring 530 and the second spring 630 (that is, torsion). An example of load characteristics obtained when the spring 700 is not used) is shown. As shown in the second curve in the section from the point P ₁ to the point P _2, although the force which the first spring 530 receives from the first piston 520 is in the first threshold value or more, the second spring 630 second Since the force received from the piston 620 is greater than or equal to the first threshold and less than the second threshold, only the first spring 530 contracts (that is, the second spring 630 does not contract).

In the section from the point _{P 2} to the point _{P 3,} the force which the first spring 530 receives from the first piston 520 is smaller than the first threshold value, and the force which the second spring 630 receives from the second piston 620 second Since it is more than a threshold value, both the 1st spring 530 and the 2nd spring 630 contract. In this case, since it can be considered that the first spring 530 and the second spring 630 are combined to form one spring substantially, the first spring 530 and the second spring 630 are combined 1 The spring constants of the two springs are smaller than the spring constant of the first spring 530 alone due to Hooke's law. As a result, the gradient in the section from the point P ₂ to the point P ₃ is smaller than the gradient in the section from the point P ₁ to the point P ₂ .

Furthermore, when the third curve (the curve indicated by the alternate long and short dash line extending from the point Q ₁ to the point Q ₃ via the point Q ₂ ) is used only with the torsion spring 700 (ie, the first spring 530 and the second spring 630). An example of the load characteristic obtained when (when is not used) is shown. As shown in the third curve in the section from the point Q ₁ to the point Q _2, present in the position of the other end 704 of the torsion spring 700, to a certain position and the reference line L of the paper on the left side of the reference line L Therefore, the torsion spring 700 presses the other end 104 of the rotating member 100 so as to resist forward rotation of the rotating member 100. In this section, the load on the clutch pedal decreases according to the pedal stroke.

In the section from the point Q ₂ to the point Q ₃ , the other end 704 of the torsion spring 700 exists at a certain position on the right side of the drawing with respect to the reference line L to the reference line L. The other end 104 of the rotating member 100 is pressed so as to assist the forward rotation of the moving member 100. As a result, in this section, the load on the clutch pedal decreases in the negative region as the pedal stroke increases.

By adding the load characteristic shown as the second curve and the load characteristic shown as the third curve, the load characteristic obtained when all of the first spring 530, the second spring 630 and the torsion spring 700 are used in combination. (The load characteristic indicated by the fourth curve shown by the solid line extending from the point P ₀ to the point P ₄ via the point P ₂ , that is, the load characteristic shown in FIG. 2) is obtained.

As can be seen from a comparison between FIG. 2 and FIG. 3, the first spring 530 and the second spring connected in series in the section from the point P ₂ to the point P ₃ in the second curve of FIG. 3. by both 630 contracts simultaneously, a small gradient is obtained than the gradient in the section from the point P ₁ to point P _2. Further, with respect to the load characteristics shown in the second curve, by adding the load characteristic of the torsion spring 700 to provide a negative slope in the third from the point Q ₂ to which was shown in the curve to the point Q ₃ sections, final Specifically, a load characteristic having a negative gradient (in section B) as shown in FIG. 2 is obtained.

4). 1st modification In embodiment shown in FIG. 1, the case where the structure which formed the 1st load generation part 500 and the 2nd load generation part 600 integrally was employ | adopted was demonstrated. Instead, in another embodiment, as described below, a configuration in which the first load generation unit 500 and the second load generation unit 600 are formed as separate bodies may be employed.

FIG. 4 is a schematic diagram showing a configuration example of a load generator according to another embodiment. 4 will be described by focusing attention only on the configuration different from that shown in FIG. 1, and the same configuration as that shown in FIG. 1 among the configurations shown in FIG. 4 will be described in detail. Omitted.

4 includes a load generator 2000 instead of the load generator 400 shown in FIG. The load generating unit 2000 includes a first load generating unit 1000 and a second load generating unit 1500 that are formed separately from each other.

Furthermore, the load generator 20 includes a third pipe 7, a fourth pipe 8, and a fifth pipe 9 instead of the first pipe 4 shown in FIG. One end of the third pipe 7 is connected to the output port 312 of the master cylinder 300, and the other end of the third pipe 7 is connected to both one end of the fourth pipe 8 and one end of the fifth pipe 9. The other end of the fourth pipe 8 is connected to the first load generator 1000, and the other end of the fifth pipe 9 is connected to the second load generator 1500.

4-1. First load generator 1000
Roughly speaking, the first load generating unit 1000 is disposed inside the first cylinder 1100 facing the one end 1102 of the cylindrical first cylinder 1100 extending from one end 1102 to the other end 1104 and the first cylinder 1100. A cylindrical first piston 1200, and a first spring 1300 disposed between the first piston 1200 and the other end 1104 of the first cylinder 1100.

An input port (first through hole) 1106 that communicates with both the fourth pipe 8 and the first cylinder 1100 is formed at one end 1102 of the first cylinder 1100. The first cylinder 1100 has a columnar wall member 1110 provided to face the first piston 1200 in the vicinity of the other end 1104. The wall member 1110 may be attached to the first cylinder 1100 using a snap ring 1112. A first convex portion 1114 that protrudes from the surface of the wall member 1110 that faces the first piston 1200 is formed.

As with the first piston 520 shown in FIG. 1, a cup (sealing) for preventing intrusion of hydraulic oil can be provided on the outer periphery of the first piston 1200. This point is the same as described above. Therefore, detailed description thereof is omitted.

The surface of the first piston 1200 that faces the wall member 1110 is formed with a second protrusion 1202 that protrudes from the surface.

The first spring 1300 is pre-compressed (in a contracted state) between the first piston 1200 and the wall member 1110. Specifically, the first spring 1300 has one end 1302 inserted (engaged) with the second convex portion 1202 of the first piston 1200 and the other end 1304 formed with the first convex portion 1114 formed on the wall member 1110. By being inserted (engaged), it is disposed between the first piston 1200 and the wall member 1110. Accordingly, the first piston 1200 is urged in the direction away from the wall member 1110 by the first spring 1300.

The first precompression amount (precompression / contraction amount) of the first spring 1300 and the first spring constant are determined by the first spring 1300 arranged in a precompressed manner as shown in FIG. Is set so as to contract when receiving a force (operation force of the clutch pedal) equal to or higher than a first threshold value from the first piston 1200 pressed by the hydraulic oil supplied via the valve.

4-2. Second load generation unit 1500
Roughly speaking, the second load generating unit 1500 is disposed inside the second cylinder 1600 so as to face the cylindrical second cylinder 1600 extending from one end 1502 to the other end 1504 and the one end 1502 of the second cylinder 1600. A cylindrical second piston 1700, and a second spring 1800 disposed between the second piston 1700 and the other end 1504 of the second cylinder 1600.

An input port (second through hole) 1506 communicating with both the fifth pipe 9 and the second cylinder 1600 is formed at one end 1502 of the second cylinder 1600. The second cylinder 1600 has a columnar wall member 1610 provided to face the second piston 1700 in the vicinity of the other end 1504. The wall member 1610 can be attached to the second cylinder 1600 using a snap ring 1612. A first convex portion 1614 protruding from the surface of the wall member 1610 facing the second piston 1700 is formed.

The outer periphery of the second piston 1700 may be provided with a cup (sealing) for preventing hydraulic oil from entering similarly to the first piston 520 shown in FIG. 1, but this is the same as described above. Therefore, detailed description thereof is omitted.

2nd convex part 1702 which protrudes from the surface is formed in the surface facing the wall member 1610 of the 2nd piston 1700.

The second spring 1800 is disposed in a pre-compressed state (in a contracted state in advance) between the second piston 1700 and the wall member 1610. Specifically, the second spring 1800 has one end 1802 inserted (engaged) with the second convex portion 1702 of the second piston 1700 and the other end 1804 with the first convex portion 1614 formed on the wall member 1610. By being inserted (engaged), it is disposed between the second piston 1700 and the wall member 1610. As a result, the second piston 1700 is biased in a direction away from the wall member 1610 by the second spring 1800.

The second pre-compression amount (the amount compressed / contracted in advance) and the second spring constant of the second spring 1800 are set so that the second spring 1800 arranged pre-compressed as shown in FIG. Is set so as to contract when receiving a force (operation force of the clutch pedal) equal to or greater than a second threshold value from the second piston 1700 pressed by the hydraulic oil supplied via the valve.

As an alternative, as shown in FIG. 4, the second piston 1700 is provided with a protrusion 1704 protruding from the outer periphery thereof, and the second cylinder 1600 protrudes from the inner wall (step). 1616 may be provided. In this case, the second piston 1700 can be restricted from sliding in the direction toward the one end 1502 of the second cylinder 1600 by the protrusion 1704 coming into contact with the protrusion 1616 of the second cylinder 1600.

4-3. The operation

load generator

20 of the load generator 20 is different from the load generator 10 shown in FIG. 1 only in that the first load generator 1000 and the second load generator 1500 are configured as separate bodies. . However, when the first spring 1300 pre-compressed and disposed in the first cylinder 1100 of the first load generator 1000 receives a force greater than or equal to the first threshold value from the first piston 1200, the load generator 20 further When the second spring 1800 that contracts and is pre-compressed and disposed in the second cylinder 1600 of the second load generating unit 1500 receives a force greater than a second threshold value (greater than the first threshold value) from the second piston 1700. 1 (the first piston 1200 and the second piston 1700 can slide in series), and has the same configuration as the load generator 10 shown in FIG. Therefore, the load generator 20 operates in the same manner as the load generator 10 described above with reference to FIG.

According to the load generation device 20 described above, the first load generation unit 1000 and the second load generation unit 1500 are formed as separate bodies, which is required as compared with the load generation device 10 shown in FIG. The axial lengths of the cylinders (that is, the first cylinder 1100 and the second cylinder 1600) can be shortened. In general, due to the fact that the workability of a cylinder with a long shaft length is poor, the workability of the cylinder required for the load generator 20 is higher than that of the cylinder required for the load generator 10. Improved. Such an advantage becomes even more remarkable when three or more load generating parts are used.

Further, according to the load generator 20, by forming a plurality of load generators as separate bodies, even if any one of the plurality of load generators fails, the failed load generator Only the part can be exchanged for a new one.

5). Second Modification In the embodiment shown in FIG. 1, a case has been described in which a configuration in which transmission of a load between the clutch pedal C and the load generation unit 400 is realized via hydraulic oil is employed. Instead, in another embodiment, as described below, a configuration that realizes transmission of a load between the clutch pedal C and the load generation unit without using hydraulic oil may be employed.

FIG. 5 is a schematic diagram showing a configuration example of a load generator according to still another embodiment. Only the configuration different from that shown in FIG. 1 will be described in the configuration shown in FIG. 5, and the same configuration as that shown in FIG. 1 will be described in detail for the configuration shown in FIG. Omitted.

5 includes a load generation unit 3000 in place of the load generation unit 400 illustrated in FIG. The load generating unit 3000 is different from the load generating unit 400 shown in FIG. 1 mainly in that it has a through hole 3010 instead of the input port 506.

A through hole (first through hole) 3010 that receives the sliding member 200 (the other end 204 thereof) and allows contact with the first piston 520 is formed at one end 502 of the first cylinder 510 of the first load generating unit 500. Has been.

The first piston 520 comes into contact with the other end 204 on the surface facing the other end 204 of the sliding member 200. The first piston 520 can also have a recess 520C on the surface facing the other end 204 of the sliding member 200 to receive the other end 204 and properly engage with the other end 204 (FIG. 5). A recess 520C is shown).

The first piston 520 receives a force from the rotating member 100 via the sliding member 200 connected to the rotating member 100 according to the rotation of the rotating member 100. More specifically, when the clutch pedal C is depressed by the driver, as described above, the rotating member 100, the X ₁ direction to rotate (forward) about the central axis 106. Along with this, the sliding member 200 moves in a direction approaching the load generating unit 3000. Thereby, the first piston 520 is pressed in a direction toward the second piston 620.

In the embodiment illustrated in FIG. 5, since no hydraulic oil is used, the first piston 520 does not need to have a cup (sealing) on the outer periphery (and need to have a groove for mounting such a cup). Needless to say.

In the load generating device 30 having the above-described configuration (substantially similar to the load generating device 10 shown in FIG. 1), the first pre-compression amount (pre-compressed / contracted amount) of the first spring 530 and the first 1 spring constant is a force (the clutch pedal operating force) that is greater than or equal to a first threshold value from the first piston 520 pressed by the sliding member 200 when the first spring 530 arranged pre-compressed as shown in FIG. ) Is set to contract when receiving. Similarly, the second pre-compression amount (the amount to be pre-compressed / contracted) of the second spring 630 and the second spring constant are determined by the second spring 630 disposed by pre-compression as shown in FIG. It is set so that it contracts when receiving a force (operation force of the clutch pedal) equal to or greater than the second threshold value from the two pistons 620. This second threshold value is larger than the first threshold value described above. Therefore, the load generator 30 operates in the same manner as the load generator 10 described above with reference to FIG. 1 (note that the first piston 520 and the second piston 620 can slide in series).

6). Third Modification In the embodiment described with reference to FIGS. 1, 4, and 5, the case where a torsion spring is used as one aspect of the rotation assist spring has been described. In another embodiment, the rotation assist unit shown in FIG. 6 can be used as another aspect of the rotation assist spring.

FIG. 6 is a schematic diagram showing a configuration example of a load generator according to still another embodiment. 6 will be described by focusing attention only on the configuration different from that shown in FIG. 1, and the same configuration as that shown in FIG. 1 among the configurations shown in FIG. 6 will be described in detail. Omitted.

A rotation assist unit 4000 extending from one end 4000a to the other end 4000b shown in FIG. 6 is provided to be opposed to the first support member 4100 having a generally cylindrical shape as a whole, and to be substantially circular as a whole. A second support member 4200 having a columnar shape, and a fourth spring (which is disposed between the first support member 4100 and the second support member 4200 and fixed to the first support member 4100 and the second support member 4200 ( Winding part) 4300.

Turning assist unit 4000, around 4000a (central axis extending in the plane on the depth direction) central shaft provided at an end portion of the fixing member 4400 having a wall surface W ₂ which is fixed to the example substantially triangular cross-section of the vehicle It is provided rotatably. The rotation assist unit 4000 is provided so as to be rotatable around a central axis (a central axis extending in the depth direction on the paper surface) 4000b provided at the other end 104 of the rotation member 100.

The first support member 4100 has a fifth convex portion 4120 on the surface facing the second support member 4200. The first support member 4100 has a bearing portion 4110 that pivotally supports the central shaft 4000b on a surface opposite to the second support member 4200.

The second support member 4200 has a sixth convex portion 4220 on the surface facing the first support member 4100. The second support member 4200 has a bearing portion 4210 that pivotally supports the central shaft 4000a on the surface opposite to the first support member 4100.

The fourth spring 4300 is provided between the first support member 4100 and the second support member 4200 with the fifth protrusion 4120 inserted through one end and the sixth protrusion 4220 inserted through the other end. As a result, the fourth spring 4300 biases the first support member 4100 away from the second support member 4200.

As shown in FIG. 6, the rotation assist unit 4000 having the above-described configuration has the other end 4000 b as viewed from the reference line L (a reference line connecting the one end 4000 a and the central axis 106 of the rotation member 100). Is in a position displaced in the pressing direction (left direction on the paper surface), resists rotation (forward rotation) of the rotation member 100 in the forward direction (X ₁ ) (in other words, rotation member 100). The other end 104 of the rotating member 100 is pressed so as to assist in the rotation (reverse rotation) in the opposite direction (X ₂ ). Such an operation is common to the operation of the torsion spring 700 described with reference to FIG.

On the other hand, the other end 4000b is the direction opposite to the direction in which the sliding member 200 is pressed when viewed from the reference line L (the reference line connecting the one end 4000a and the central axis 106 of the rotating member 100) (the right direction on the paper). When it is in the position displaced, it assists in the rotation (forward rotation) of the rotation member 100 in the forward direction (X ₁ ) (in other words, the rotation of the rotation member 100 in the reverse direction (X ₂ ) ( The other end 104 of the rotating member 100 is pressed so as to resist the reverse rotation). Such an operation is common to the operation of the torsion spring 700 described with reference to FIG.

Here, as an example, a case where the second support member 4200 of the rotation assist unit 4000 supports the center shaft 4000a and the first support member 4100 of the rotation assist unit 4000 supports the center shaft 4000b will be described. However, the end portion of the fixing member 4400 may support the central shaft 4000a, or the other end 104 of the rotating member 100 may support the central shaft 4000b.

The rotation assist unit 4000 has been described focusing on the case where it is used in the configuration shown in FIG. 1, but the rotation assist unit 4000 is also referred to FIG. 1 in the configuration shown in FIGS. 4 and 5. It can be used as an operation similar to that described above.

7). Other Modifications In the embodiment described with reference to FIGS. 1, 4, and 6, as an example, an example in which a cylinder included in a load generation unit is formed to extend in the vertical direction has been described. However, in another embodiment, the cylinder included in the load generation unit may be formed to extend in an arbitrary direction (for example, the horizontal direction).

In the embodiment described with reference to FIGS. 1, 4, 5, and 6, as a most preferable example, the diameter of the second cylinder included in the second load generation unit is included in the first load generation unit. An example in which the diameter is larger than the diameter of one cylinder has been described. However, in another embodiment, the diameter of the second cylinder included in the second load generation unit may be formed smaller than the diameter of the first cylinder included in the first load generation unit, or the diameter of the first cylinder. And substantially the same. However, even in such a case, the pre-compressed first spring further contracts when receiving a force greater than or equal to the first threshold value from the first piston, and the pre-compression Both of the conditions that the second spring arranged in this way further contracts when subjected to a force greater than a second threshold (greater than the first threshold) from the second piston need to be satisfied. The material, length, diameter, and the like for each of the first spring and the second spring can be designed so that these conditions are satisfied.

In the embodiment described with reference to FIGS. 1, 4, 5, and 6, as a most preferable example, the plurality of load generation units include two load generation units, a first load generation unit and a second load generation unit. The example formed by the above has been described. However, the plurality of load generation units may include N (N is a natural number of 2 or more) load generation units. Even in this case, the condition that the N-th spring arranged in a pre-compression state further contracts when receiving a force greater than the N-th threshold value greater than the (N-1) -th threshold value from the N-th piston. Need to be met.

In this regard, in the embodiment shown in FIG. 1, when three load generating portions are used, for example, the following advantages arise. In the section C in the load characteristic shown in FIG. 2, when the combination of the first spring, the second spring, and the third spring is viewed as one spring, the spring constant is reduced by Hook's law (gradient in the load characteristic). Becomes smaller). Then, in the load characteristic obtained by adding the load characteristic due to these three springs and the load characteristic due to the torsion spring, in section C, the load on the clutch pedal decreases (for example, slightly) according to the pedal stroke. It will be a thing. Thereby, the design freedom degree of a load characteristic can be improved.

7). Effects The load generating devices according to the various embodiments described above do not use a member having a friction coefficient that greatly affects the load characteristics with respect to the clutch pedal in each load generating unit, torsion spring, and the like. Thereby, the load generators according to the various embodiments described above can eliminate the need for extra processing such as surface treatment and heat treatment required to stabilize the friction coefficient of such members, Therefore, the cost resulting from such processing can be suppressed.

Furthermore, the load generating apparatus according to the various embodiments described above uses a member that does not maintain the originally intended load characteristics due to wear with use in each load generating portion, torsion spring, and the like. is not. Thereby, the load generator which concerns on various embodiment mentioned above can generate | occur | produce the load which has the characteristic originally intended over a longer period.

Furthermore, the load characteristics according to the various embodiments described above do not use a member that may become a generation source of abnormal noise due to sliding in each load generation section and torsion spring. Thereby, the load characteristic which concerns on various embodiment mentioned above can keep the navigation environment in a vehicle interior favorable.

As described above, according to various embodiments, it is possible to provide a load generator having improved performance with respect to the above-described conventional problems.

8). Various Embodiments A load generator according to a first aspect includes a first cylinder, a first moving member that slides in the first cylinder in response to an operation force of a clutch pedal, and the first moving member. In addition, a first load generating portion having a first load generating spring disposed in a pre-compressed manner in the first cylinder, a second cylinder, and a slide in the second cylinder according to the operating force. A second load generating portion having a second moving member that moves, and a second load generating spring that is engaged with the second moving member and is pre-compressed in the second cylinder. The first moving member and the second moving member are connected in series in cooperation with a rotation assist spring that is locked at a position different from the rotation axis of the clutch pedal and reverses the operation force during rotation. At least one of the first load generating spring and the second load generating spring. By stretching towards those which generate a load against the clutch pedal.

According to this aspect, the load obtained by combining the load obtained by the plurality of sliding control springs sliding inside the cylinder and the load obtained by the rotation assist spring is applied to the clutch pedal, thereby providing a manual. A load similar to a load on a clutch pedal used in a transmission type vehicle can be generated.

Further, according to this aspect, there is no need to use a member having a friction coefficient that greatly affects the load characteristics with respect to the clutch pedal. As a result, unnecessary processing such as surface treatment and heat treatment required to stabilize the friction coefficient of such a member can be eliminated, and thus the costs resulting from such treatment can be suppressed. .

Furthermore, according to this aspect, there is no need to use a member that cannot maintain the originally intended load characteristics due to wear with use. As a result, a load having the originally intended characteristics can be generated over a longer period.

Furthermore, according to this aspect, there is no need to use a member that may be a source of abnormal noise due to sliding. Thereby, the navigation environment in the passenger compartment can be kept good.

In the load generator according to a second aspect, in the first aspect, the first cylinder and the second cylinder communicate with each other, and the first load generation spring includes the first moving member and the second movement. The first moving member is extended between the first load generating spring and the first load generating spring according to the operation force transmitted through the hydraulic oil, and the second load generating spring is the first load generating spring. The second moving member is disposed so as to sandwich the second moving member between the load generating spring, and the second cylinder abuts on a surface of the second moving member facing the first moving member, so that the second moving member A protrusion for restricting sliding toward the first moving member;

According to this aspect, it is possible to provide a load generating device having a configuration in which a load generated by the rotation of the clutch pedal is transmitted by hydraulic oil and a plurality of load generating springs are arranged in the same cylinder.

The load generator according to a third aspect is the load generator according to the first aspect, wherein the first cylinder and the second cylinder are formed as separate bodies, and the first moving member is transmitted via hydraulic oil. The first load generating spring is expanded and contracted according to the operated force, and the second moving member is expanded and contracted according to the operating force transmitted through the hydraulic oil.

According to this aspect, it is possible to provide a load generating device having a configuration in which a load generated by the rotation of the clutch pedal is transmitted by hydraulic oil, and a load generating spring unique to the cylinder is arranged in each cylinder.

In the load generator according to a fourth aspect, in the first aspect, the first cylinder and the second cylinder communicate with each other, and the first load generation spring includes the first moving member and the second movement. The first moving member is disposed between the first moving member and the first load according to the operating force transmitted via the sliding member disposed between the first moving member and the clutch pedal. The generating spring is extended and contracted, and the second load generating spring is disposed so as to sandwich the second moving member between the second load generating spring and the second cylinder, and the second cylinder is the first moving member of the second moving member. A protrusion that abuts against a surface facing the first moving member and restricts sliding of the second moving member toward the first moving member;

According to this aspect, it is possible to provide a load generating device having a configuration in which a load generated by the rotation of the clutch pedal is transmitted without using hydraulic oil and a plurality of load generating springs are arranged in the same cylinder.

The load generator according to a fifth aspect is the load generator according to any one of the first aspect to the fourth aspect, wherein the first load generation spring contracts by receiving the operation force equal to or greater than a first threshold, The second load generating spring contracts by receiving the operation force that is greater than or equal to a second threshold value that is greater than the first threshold value.

The load generator according to a sixth aspect is the load generator according to any one of the first to fifth aspects, wherein the rotation assist spring is disposed at an end of the clutch pedal at the other end of the rotation assist spring. A first support member that is pivotably provided; a second support member that is pivotally provided on a wall of a vehicle at one end of the rotation assist spring; and the first support member and the second support member. And a spring disposed therebetween.

In the load generator according to a seventh aspect, in any one of the first aspect to the fifth aspect, the rotation assist spring is a torsion spring having a winding portion between one end and the other end. There,
The other end is rotatably provided at an end of the clutch pedal, and the one end is rotatably provided on a vehicle wall.

In the load generator according to an eighth aspect, in the sixth aspect or the seventh aspect, the end portion of the clutch pedal includes the rotation shaft of the clutch pedal and the one end of the rotation assist spring. The clutch pedal is pressed by the rotation assist spring so that the end of the clutch pedal is directed to the one side, and the clutch pedal is When the end portion is located on the side opposite to the one side as viewed from the reference line, the clutch pedal is configured so that the end portion of the clutch pedal faces the opposite side. It is pressed by.

According to this aspect, the rotation assist spring can operate so as to resist or assist the rotation of the clutch pedal in accordance with the rotation of the clutch pedal.

According to various embodiments, it is possible to provide a load generator having improved performance with respect to conventional problems.

This application is based on Japanese Patent Application No. 2017-107882 filed May 31, 2017 entitled “Load Generating Device”, and enjoys the benefit of the priority right from this Japanese Patent Application. Is. The entire contents of this Japanese patent application are incorporated herein by reference.

C Clutch pedal L Reference line 4 1st piping 6 2nd piping 7 3rd piping 8 4th piping 9

5th piping

10, 20, 30 Load generating device 100 Rotating member 102 One end of the rotating member 104 Other than rotating member End 106 Center axis of rotating member 108 Connecting portion of rotating member 200 Sliding member 202 One end of sliding member 204 Other end of sliding

member

400, 2000, 3000

Load generating portion

506, 1106 Input port (first through hole )
500, 1000 1st

load generation part

600, 1500 2nd

load generation part

606, 1616 Protrusion part (step part)
510, 1100

First cylinder

610, 1600

Second cylinder

520, 1200 First piston (first moving member)
620, 1700 Second piston (second moving member)
530, 1300 First spring (first load generating spring)
630, 1800 Second spring (second load generating spring)
700 Torsion spring (rotation assist spring)
702 One end of torsion spring 704 Other end of torsion spring 706 Torsion spring winding portion 1506 Input port (second through hole)
3010 Through hole (first through hole)
4000 Rotation assist unit (Rotation assist spring)
4000a One end of rotation assist spring (center axis)
4000b The other end (center axis) of the rotation assist spring
4100 1st support member 4110 Bearing part 4120 5th convex part 4200 2nd support member 4210 Bearing part 4220 6th convex part 4300 4th spring (winding part)
4400 Fixing member

Claims

A first cylinder, a first moving member that slides in the first cylinder in response to an operating force of the clutch pedal, and a precompressed arrangement in the first cylinder that engages with the first moving member. A first load generating portion having a first load generating spring;
A second cylinder, a second moving member that slides in the second cylinder in response to the operating force, and a second moving member that is engaged with the second moving member and pre-compressed in the second cylinder. A second load generating portion having two load generating springs;
Comprising
The first moving member and the second moving member are connected in series in cooperation with a rotation assist spring that is locked at a position different from the rotation axis of the clutch pedal and reverses the operation force during rotation. A load generating device that generates a load on the clutch pedal by sliding and expanding and contracting at least one of the first load generating spring and the second load generating spring.
The first cylinder and the second cylinder communicate with each other;
The first load generating spring is disposed between the first moving member and the second moving member,
The first moving member expands and contracts the first load generating spring according to the operation force transmitted through the hydraulic oil,
The second load generating spring is disposed so as to sandwich the second moving member between the first load generating spring and the second load generating spring.
The said 2nd cylinder has a projection part which contact | abuts the surface which faces the said 1st moving member of the said 2nd moving member, and controls the sliding toward the said 1st moving member of the said 2nd moving member. The load generator according to 1.
The first cylinder and the second cylinder are formed as separate bodies,
The first moving member expands and contracts the first load generating spring according to the operation force transmitted through the hydraulic oil,
2. The load generating device according to claim 1, wherein the second moving member expands and contracts the second load generating spring according to the operation force transmitted through the hydraulic oil.
The first cylinder and the second cylinder communicate with each other;
The first load generating spring is disposed between the first moving member and the second moving member,
The first moving member expands and contracts the first load generating spring according to the operation force transmitted through a sliding member disposed between the first moving member and the clutch pedal.
The second load generating spring is disposed so as to sandwich the second moving member between the first load generating spring and the second load generating spring.
The said 2nd cylinder has a projection part which contact | abuts the surface which faces the said 1st moving member of the said 2nd moving member, and controls the sliding toward the said 1st moving member of the said 2nd moving member. The load generator according to 1.
The first load generating spring contracts by receiving the operation force equal to or greater than a first threshold value,
5. The load generation device according to claim 1, wherein the second load generation spring contracts by receiving the operation force that is greater than or equal to a second threshold value that is greater than the first threshold value.
The rotation assist spring rotates at the other end of the rotation assist spring at the end of the clutch pedal, and rotates at the vehicle wall at one end of the rotation assist spring. The load according to any one of claims 1 to 5, further comprising: a second support member provided freely, and a spring disposed between the first support member and the second support member. Generator.
The rotation assist spring is a torsion spring having a winding portion between one end and the other end,
The load generation according to any one of claims 1 to 5, wherein the other end is rotatably provided at an end portion of the clutch pedal, and the one end is rotatably provided on a wall portion of a vehicle. apparatus.
When the end portion of the clutch pedal is located on one side when viewed from a reference line connecting the rotating shaft of the clutch pedal and the one end of the rotation assist spring, the clutch pedal is Pressed by the rotation assist spring so that the end portion is directed to the one side,
When the end portion of the clutch pedal is located on the side opposite to the one side as viewed from the reference line, the clutch pedal is arranged so that the end portion of the clutch pedal faces the opposite side. The load generator according to claim 6 or 7, wherein the load generator is pressed by the rotation assist spring.