WO2017122522A1 - Dispositif de production de charge - Google Patents

Dispositif de production de charge Download PDF

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Publication number
WO2017122522A1
WO2017122522A1 PCT/JP2016/088684 JP2016088684W WO2017122522A1 WO 2017122522 A1 WO2017122522 A1 WO 2017122522A1 JP 2016088684 W JP2016088684 W JP 2016088684W WO 2017122522 A1 WO2017122522 A1 WO 2017122522A1
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WO
WIPO (PCT)
Prior art keywords
load
elastic member
generating device
stroke amount
generator
Prior art date
Application number
PCT/JP2016/088684
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English (en)
Japanese (ja)
Inventor
彰一 山崎
亮祐 永谷
雄輝 汲川
Original Assignee
アイシン精機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン精機株式会社 filed Critical アイシン精機株式会社
Publication of WO2017122522A1 publication Critical patent/WO2017122522A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/02—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for main transmission clutches

Definitions

  • the present invention relates to a load generator that generates a load, and more particularly to a load generator having a high degree of freedom in design of load characteristics.
  • the conventional load generator using a tension compression spring and a disc spring has a problem that the degree of freedom in designing the load characteristics is low because the tension compression spring and the disc spring are merely combined.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a load generator having a high degree of freedom in design of load characteristics.
  • a load generating device of the present invention includes a piston member that is housed in a cylinder and reciprocates in a predetermined stroke direction, and a load generating member that generates a load to be applied to the piston member.
  • a first elastic member having a positive gradient load characteristic and a second elastic member having at least a negative gradient load characteristic, wherein the first elastic member is connected to the second elastic member in a pre-compressed state. Yes.
  • the load generated by the load generating member is applied to the piston member. Since the load generating member is composed of a first elastic member (an elastic member having a positive gradient load characteristic) and a second elastic member (an elastic member having at least a negative gradient load characteristic), the load characteristic of the load generating member is Is a combination of the load characteristics of the first elastic member and the second elastic member. In this case, since the first elastic member is connected to the second elastic member in a pre-compressed state, the load characteristic of the load generating member is obtained when the stroke amount of the piston member is gradually increased from zero.
  • the load characteristic of the first elastic member is shown, and after exceeding the predetermined stroke amount, The load characteristics of the second elastic member are shown. Therefore, by adjusting the amount of pre-compression of the second elastic member, a load having a desired load characteristic can be generated, and the design flexibility of the load characteristic is high.
  • the second elastic member may be constituted by a disc spring.
  • the load characteristics of a disc spring gradually increase when the stroke amount of the piston member is gradually increased from zero, and gradually decrease when the predetermined peak value (maximum value) is exceeded. Increase gradually.
  • the predetermined stroke amount the stroke amount at which the load of the first elastic member becomes equal to the precompression load of the second elastic member
  • the stroke amount of the piston member is gradually increased from zero.
  • the load characteristic of the load generating member reaches a predetermined stroke amount (a stroke amount at which the load of the first elastic member becomes equal to the precompression load of the second elastic member).
  • the load gradually increases (becomes a positive gradient), and after exceeding the predetermined stroke amount, the load gradually decreases (becomes a negative gradient) as the stroke amount increases, and the stroke amount again. As it increases, it gradually increases (becomes a positive slope).
  • load characteristics are similar to the load characteristics of the clutch pedal. In this way, by configuring the second elastic member with a disc spring, it is possible to generate a pseudo load having a load characteristic similar to that of the clutch pedal.
  • the plurality of disc springs may be connected in series or in parallel in the second elastic member.
  • the load characteristic of the second elastic member can be changed by selecting the number of disc springs or the series / parallel. Therefore, the load characteristic of the load generated by the load generating member can be changed.
  • the first elastic member may be disposed inside the second elastic member.
  • the first elastic member can be disposed inside the second elastic member, so that the degree of freedom in design is increased.
  • the load generator of the present invention may include a support member that supports an end portion of the second elastic member.
  • the end of the second elastic member is supported by the support member. Therefore, for example, even if the second elastic member is constituted by a plurality of disc springs, the plurality of disc springs can be appropriately connected.
  • the first elastic member and the second elastic member may be arranged coaxially with a shaft member as a center.
  • the coaxiality of the first elastic member and the second elastic member can be improved by the shaft member.
  • the second elastic member may be constituted by a torsion spring.
  • a plurality of torsion springs may be connected in parallel in the second elastic member.
  • the load characteristic of the second elastic member can be changed by selecting the number of torsion springs. Therefore, the load characteristic of the load generated by the load generating member can be changed.
  • the stroke amount of the second elastic member may be prevented from exceeding a predetermined limit stroke amount.
  • This configuration allows the stopper to prevent the stroke amount of the second elastic member from exceeding the limit stroke and becoming an overstroke.
  • the load generator of the present invention may include an air hole that communicates the air chamber in the cylinder with the outside.
  • the piston member may include a second stopper for preventing the stroke amount of the first elastic member from exceeding a predetermined limit stroke amount.
  • the second stopper can prevent the stroke amount of the first elastic member from exceeding the limit stroke and becoming an overstroke.
  • the load generator of the present invention may be provided with a bleeder for discharging the air in the oil chamber in the cylinder to the outside.
  • the first elastic member and the second elastic member may be connected via a hydraulic pipe.
  • a clutch pedal connected to the first elastic member and the second elastic member via a hydraulic pipe may be provided, and a third elastic member may be provided in the clutch pedal.
  • the load characteristic on the clutch pedal shows a load characteristic in which the load of the third elastic member is further added to the load characteristic added on the clutch pedal by the load generating device.
  • the degree of freedom in designing the load characteristics on the pedal is increased.
  • a load having desired load characteristics can be generated by adjusting the amount of pre-compression of the second elastic member.
  • the automatic clutch system 1 includes an operation mode switching unit 2 that switches between a manual operation mode and an automatic operation mode.
  • the manual operation mode is an operation mode in which the clutch 4 is connected / disconnected based on the pedal operation of the clutch pedal 3
  • the automatic operation mode is an operation mode in which the actuator 6 is operated based on a control signal from the control unit 5. This is an operation mode for connecting and disconnecting.
  • the clutch pedal 3 is provided with a stroke sensor 7 for detecting an operation amount (depression amount) of the pedal operation, and the control unit 5 receives a signal indicating the current depression amount of the clutch pedal 3 from the stroke sensor 7. .
  • the control part 5 may receive the signal which shows the depression amount of the present accelerator pedal from the stroke sensor (not shown) of an accelerator pedal.
  • the operation mode switching unit 2 is schematically shown.
  • the manual operation mode as shown in FIG. 1
  • the depression amount of the clutch pedal 3 is directly transmitted to the clutch 4, and the depression amount is determined. Accordingly, the clutch 4 is connected / disconnected.
  • the automatic operation mode as shown in FIG. 2, a control signal is sent from the control unit 5 to the actuator 6, and the actuator 6 is operated according to the control signal to connect / disconnect the clutch 4.
  • the operation mode switching unit 2 switches between the manual operation mode and the automatic operation mode based on the switching signal from the control unit 5.
  • the operation mode switching unit 2 determines to switch from the automatic operation mode to the manual operation mode. In this case, until the depression amount of the clutch pedal 3 becomes zero, a control signal corresponding to the depression amount is transmitted from the control unit 5 to the actuator 6, and the clutch 4 is connected / disconnected according to the depression amount. . That is, the actuator 6 follows the pedal operation of the clutch pedal 3. When the depression amount of the clutch pedal 3 becomes zero, the operation mode switching unit 2 switches from the automatic operation mode to the manual operation mode.
  • the operation mode switching unit 2 may switch from the automatic operation mode to the manual operation mode when the accelerator pedal is operated in the automatic operation mode.
  • the automatic clutch system 1 includes a load generator 8 that generates a load (pseudo reaction force) corresponding to the operation amount of the pedal operation when the pedal operation of the clutch pedal 3 is performed in the automatic operation mode.
  • the characteristic of the load is the reaction force characteristic (cover reaction force) of the pedal reaction force received from the clutch pedal 3 according to the operation amount of the pedal operation when the pedal operation is performed in the manual operation mode. Characteristic)) (see FIG. 5).
  • FIG. 3 is an explanatory diagram showing a configuration of the load generating device 8 according to the first embodiment.
  • the load generation device 8 includes a cylinder 10, a piston member 11 accommodated in the cylinder 10, and a load generation member 12 that generates a load applied to the piston member 11.
  • the piston member 11 reciprocates in the cylinder 10 in a predetermined stroke direction (vertical direction in FIG. 3).
  • the load generating member 12 includes a tension / compression spring member 13 (coil spring) and a disc spring member 14.
  • the tension / compression spring member 13 and the disc spring member 14 are arranged in series.
  • the disc spring member 14 of the present embodiment includes a single disc spring 15, and the disc spring 15 is pre-compressed.
  • the disc spring member 15 is pre-compressed with 50-100% of the peak load of the disc spring 15 in the initial state. Compression is given.
  • An end 16 on the inner diameter side of the disc spring 15 is supported by a support member 17, and an end 18 on the outer diameter side of the disc spring 15 is supported by a body 19.
  • the tension compression spring member 13 is connected to the disc spring member 14 in a precompressed state.
  • the upper end of the tension / compression spring member 13 is in contact with the piston member 11, and the lower end of the tension / compression spring member 13 is supported by a support member 17. It can be said that the support member 17 also serves as a sheet of the tension / compression spring member 13.
  • the piston member 11 has a columnar main body 110, and an upper end portion of the tension compression spring member 13 is provided at the center of the lower surface (lower surface in FIG. 3) of the main body 110.
  • a convex portion 111 is provided to be locked.
  • the support member 17 has a disc-shaped main body 170, and a convex portion 171 to which the lower end portion of the tension / compression spring member 13 is locked is provided at the center of the upper surface of the main body 170. .
  • a convex portion 172 to which the upper end portion of the disc spring member 14 is locked is provided at the center portion of the lower surface of the main body 170 of the support member 17.
  • a lower end portion of the disc spring member 14 is locked to a stepped portion 190 provided on the body 19.
  • the lower surface of the main body 170 of the support member 17 is a tapered surface.
  • the disc spring 15 may be supported by the cylinder 10 on the inner end 16 of the disc spring 15 in a pre-compressed state.
  • the cylinder 10 also serves as the support member 17.
  • the load generating member 12 of the present embodiment is composed of the tension / compression spring member 13 and the disc spring member 14, the load generating member 12 has a load characteristic as shown in FIG.
  • the load characteristics of the disc spring member 14 are combined.
  • the tension compression spring member 13 has a positive gradient load characteristic
  • the disc spring member 14 has at least a negative gradient load characteristic.
  • the load characteristic of the load generation member 12 gradually increases the stroke amount of the piston member 11 from zero.
  • the load generator 8 of the present embodiment it is possible to generate a load having a desired load characteristic by adjusting the amount of pre-compression of the disc spring member 14, and the design flexibility of the load characteristic. Is expensive.
  • a large precompression to the disc spring 15 and arranging it in series with the tension compression spring an area in which only the tension compression spring is operated can be formed, so that the stroke amount of the disc spring 15 can be greatly reduced.
  • the stress generated in the disc spring 15 can be reduced, the number of the disc springs 15 can be reduced, and the outer diameter (size) of the disc spring 15 can be reduced.
  • the generator 8 can be realized.
  • the load characteristic of the disc spring 15 gradually increases when the stroke amount of the piston member 11 is gradually increased from zero, and gradually decreases when a predetermined peak value (maximum value) is exceeded. Increase gradually. For example, when the predetermined stroke amount (the stroke amount at which the load of the tension compression spring member 13 becomes equal to the precompression load of the disc spring member 14) is set to a value near the peak value, the stroke amount of the piston member 11 is zero. Until the load characteristics of the load generating member 12 reaches a predetermined stroke amount (a stroke amount at which the load of the tension compression spring member 13 becomes equal to the precompression load of the disc spring member 14).
  • the load gradually increases as the stroke amount increases (becomes a positive gradient), and after exceeding the predetermined stroke amount, the load gradually decreases as the stroke amount increases (becomes a negative gradient) Again, it gradually increases (becomes a positive gradient) as the stroke amount increases.
  • load characteristics are similar to the load characteristics of the clutch pedal (see FIG. 5). Therefore, according to the load generator 8 of the present embodiment, it is possible to generate a pseudo load having a load characteristic similar to that of the clutch pedal.
  • FIG. 6 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment.
  • a plurality of disc springs 15 are connected in series.
  • the lower end portion of the disc spring member 14 is locked to a step portion 191 provided at the center portion of the body 19.
  • a plurality of disc springs 15 may be connected in parallel.
  • the lower end portion of the disc spring member 14 is locked to the step portion 190 provided at the end portion of the body 19.
  • the load characteristics of the disc spring member 14 can be changed by selecting the number of disc springs 15 or the series / parallel. Therefore, the load characteristic of the load generated by the load generating member 12 can be changed. Further, by using a plurality of disc springs 15, the outer diameter (size) of the load generating member 12 can be reduced.
  • FIG. 8 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment.
  • a movable cylinder 10 is employed, and a tension / compression spring member 13 is disposed inside a disc spring member 14.
  • a piston member 11 and a sliding pin 20 are accommodated in the movable cylinder 10.
  • the piston member 11 has a columnar main body 110, and the upper end portion of the tension / compression spring member 13 is engaged with the central portion of the lower surface (lower surface in FIG. 8) of the main body 110.
  • the convex part 111 to be stopped is provided.
  • a lower bent portion 100 in which the lower end portion of the tension / compression spring member 13 is locked is formed at the lower portion of the movable cylinder 10.
  • a second convex portion 112 is provided at the center of the lower surface of the convex portion 111 of the piston member 11.
  • the 2nd convex part 112 is comprised so that it can pass through the opening part 101 of the lower part of the movable cylinder 10, when the tension compression spring member 13 is compressed.
  • an upper bent portion 102 in which the upper end portion of the disc spring member 14 is locked is formed at the upper portion of the movable cylinder 10.
  • the lower end of the disc spring member 14 is locked on the bottom surface of the disc spring storage chamber 192 provided in the body 19.
  • the tension / compression spring member 13 can be disposed inside the disc spring member 14, the degree of design freedom is increased. Further, in this case, since “the axial length of the portion that accommodates the disc spring 15” can be overlapped with “the axial length of the movable cylinder 10 + the stroke amount of the movable cylinder 10” in the axial direction, a load is generated. The size of the device 8 can be reduced. Further, since the interference between the disc spring 15 and the tension / compression spring member 13 can be prevented, it is possible to prevent a stroke failure due to an increase in the number of hiss or a catch.
  • FIG. 9 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment.
  • a plurality of disc springs 15 are connected in series, and the end 16 on the inner diameter side of the disc spring 15 is connected to the first support member 21 (inner support).
  • the end 18 on the outer diameter side of the disc spring 15 is supported by the second support member 22 (outer support member).
  • the first support member 21 has a disk-shaped main body 210, and a lower end portion of the disc spring 15 disposed on the upper side of the first support member 21 is at the center of the upper surface of the main body 210.
  • a convex portion 211 to be locked is provided.
  • a convex portion 212 is provided at the center of the lower surface of the main body 210 of the first support member 21 so that the upper end portion of the disc spring 15 disposed below the first support member 21 is locked. ing. As shown in FIGS. 10 and 11, a plurality of disc springs 15 may be connected in parallel.
  • the inner end 16 of the disc spring 15 is supported by the first support member 21, and the outer end 18 of the disc spring 15 is supported by the second support member 22.
  • a plurality of disc springs 15 can be appropriately connected. Further, when a plurality of disc springs 15 are arranged in series, the stroke amount of the disc springs 15 becomes large (the disc springs 15 can be stroked larger than the horizontal state), and the degree of freedom in designing the load characteristics depends. improves. On the other hand, when a plurality of disc springs 15 are arranged in parallel, the disc springs 15 can be prevented from contacting each other (surface contact), and sliding hiss and twisting force can be reduced. In addition, compared with the structure of FIG. 10, the structure of FIG. 11 can reduce a twisting force more.
  • FIG. 12 is an explanatory diagram showing a configuration of the load generating device 8 of the present embodiment.
  • the tension / compression spring member 13 and the disc spring member 14 are arranged coaxially with the shaft member 23 as the center.
  • the shaft member 23 is disposed so as to penetrate the support member 21 (inner support member).
  • the shaft member 23 may be configured integrally with the piston member 11.
  • it can be arranged coaxially with the shaft member 23 as the center.
  • the coaxiality of the tension / compression spring member 13 and the disc spring member 14 can be improved by the shaft member 23.
  • uneven wear due to shaft misalignment can be reduced, so that changes with time in the load characteristics of the load generator 8 can be suppressed.
  • sliding hiss due to interference between the outer diameter of the disc spring 15 and the body 19 can be reduced.
  • FIG. 15 is an explanatory diagram showing a configuration of the load generating device 8 of the present embodiment.
  • the lower surface 24 of the support member 17 (inner support member) of the disc spring 15 serves as a stopper that prevents the disc spring 15 stroke amount from exceeding a predetermined limit stroke amount. It has the function of In other words, when the stroke amount of the disc spring 15 increases and exceeds the predetermined limit stroke amount, the lower surface 24 of the support member 17 (inner support member) comes into contact with the body 19, and the disc spring 15 It is possible to prevent the stroke amount from increasing.
  • the lower surface 24 of the first support member 24 (inner support member) of the disc spring 15 may have a function as a stopper that prevents the disc spring 15 from exceeding a predetermined stroke amount.
  • the disc spring 15 may be brought into direct contact with the body 19 so that the disc spring 15 has a function as a stopper.
  • the stopper can prevent the stroke amount of the disc spring 15 from exceeding the limit stroke and becoming an overstroke. Therefore, the stress generated in the disc spring 15 during the overstroke can be reduced. As a result, the stress generated in the disc spring 15 can be reduced.
  • the diameter (size) can be reduced, and a compact and highly loadable load generator 8 can be realized. Since the tension compression spring is compressed after the disc spring 15 stops, the clutch pedal stroke can be secured.
  • FIG. 18 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment.
  • an air hole 25 communicating with the air chamber in the cylinder 10 is formed.
  • the air hole 25 is formed in the shaft member 23.
  • the air hole 25 may be formed in the body 19 as shown in FIG. 19, or may be formed in the cylinder 10 as shown in FIG.
  • the air (air pressure) in the air chamber in the cylinder 10 can be released to the outside from the air hole 25, and the contraction caused by the temperature change of the air. You can cancel minutes. Therefore, even when the piston member 11 moves or when the temperature of the air changes, the internal pressure of the cylinder 10 does not change, so that no load (unintended load) resulting from the change of the internal pressure of the cylinder 10 occurs.
  • FIG. 21 is an explanatory diagram showing a configuration of the load generator 8 of the present embodiment.
  • the lower surface 26 of the piston member 11 has a function as a stopper (second stopper) that prevents the stroke amount of the tension / compression spring member 13 from exceeding a predetermined limit stroke amount. . That is, when the stroke amount of the tension / compression spring member 13 increases and exceeds the predetermined limit stroke amount, the lower surface 26 of the piston member 11 contacts the upper surface of the support member 21 (inner support member) of the disc spring 15. It is possible to prevent the stroke amount of the tension / compression spring member 13 from increasing further.
  • the second stopper can prevent the stroke amount of the tension / compression spring member 13 from exceeding the limit stroke and becoming an overstroke. Thereby, the damage by adhesion
  • FIG. 22 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment. As shown in FIG. 22, in the present embodiment, a bleeder 27 that discharges the air in the oil chamber in the cylinder 10 to the outside is provided.
  • the air in the cylinder 10 can be released from the bleeder 27.
  • the air can be discharged from the bleeder 27 to the outside, so that load characteristic change (unintended load characteristic change) due to air mixing can be prevented.
  • load characteristic change unintended load characteristic change
  • it is possible to improve mountability and assemblability.
  • FIG. 23 is an explanatory diagram showing a configuration of the load generating device 8 of the present embodiment.
  • the tension / compression spring member 13 and the disc spring member 14 arranged at different places are connected via a hydraulic pipe 28.
  • the tension / compression spring member 13 and the disc spring member 14 are connected in series via the hydraulic pipe 28.
  • the tension / compression spring member 13 and the disc spring member 14 can be arranged at different locations via the hydraulic pipe 28, the degree of freedom in design is increased. In this case, even when a plurality of biston cylinders 10 are employed, a load characteristic equivalent to that of a single piston cylinder 10 can be realized. Mountability can be improved by separating the portion for accommodating the tension compression spring member 13 and the portion for accommodating the disc spring member 14.
  • FIG. 24 is an explanatory diagram showing the configuration of the load generating device 8 of the present embodiment. As shown in FIG. 24, in the present embodiment, the clutch pedal 3 is provided with a third elastic member 32.
  • the load characteristic on the clutch pedal 3 is a load characteristic in which the load of the third elastic member 32 is further added to the load characteristic added on the clutch pedal 3 by the load generator 8. As a result, the degree of freedom in designing the load characteristics on the clutch pedal 3 is increased.
  • the second elastic member is constituted by the disc spring member 14
  • the scope of the present invention is not limited to this.
  • the second elastic member only needs to have at least negative load characteristics.
  • the second elastic member can be constituted by a coil spring 29.
  • the coil spring 29 is configured to have at least negative load characteristics. That is, when the piston member 11 is stroked in the pushing direction (downward direction in FIG. 25), the coil spring 29 is gradually compressed, and the load of the coil spring 29 is gradually increased. Thereafter, when the stroke position of the piston member 11 (position where the coil spring 29 can be compressed most) is exceeded, the coil spring 29 gradually expands as the piston member 11 is pushed in, and the load of the coil spring 29 gradually decreases.
  • the load characteristic of the load generating member 12 is such that the stroke amount of the piston member 11 is zero.
  • the load characteristics of the tension / compression spring member 13 are shown up to a predetermined stroke amount (a stroke amount at which the load of the tension / compression spring member 13 becomes equal to the precompression load of the coil spring 29). After the predetermined stroke amount is exceeded, the load characteristics after the precompression load of the coil spring 29 are connected in series.
  • the second elastic member can be constituted by a torsion spring 30.
  • the torsion spring 30 is configured to have at least negative load characteristics. That is, when the piston member 11 is stroked in the pushing direction (downward in FIG. 26), the torsion spring 30 is gradually compressed, and the load of the torsion spring 30 gradually increases. Thereafter, when the stroke position of the piston member 11 (position where the torsion spring 30 is reversed) is exceeded, the torsion spring 30 gradually expands as the piston member 11 is pushed in, and the load of the torsion spring 30 gradually decreases.
  • the load characteristic of the load generating member 12 makes the stroke amount of the piston member 11 zero.
  • the load characteristic of the tension compression spring member 13 is shown up to a predetermined stroke amount (a stroke amount at which the load of the tension compression spring member 13 becomes equal to the precompression load of the torsion spring 30). After the predetermined stroke amount is exceeded, the load characteristic after the precompression load of the torsion spring 30 is displayed in a load characteristic connected in series.
  • the second elastic member can be composed of a rubber member 31.
  • the rubber member 31 is configured to have at least negative load characteristics. That is, when the piston member 11 is stroked in the pushing direction (downward direction in FIG. 27), the rubber member 31 is gradually compressed, and the load on the rubber member 31 is gradually increased. Thereafter, when the stroke position of the piston member 11 (position where the stretched rubber member 31 yields) is exceeded, the rubber member 31 gradually expands as the piston member 11 is pushed in, and the load on the rubber member 31 gradually decreases.
  • the load characteristic of the load generating member 12 is such that the stroke amount of the piston member 11 is zero.
  • the load characteristic of the tension compression spring member 13 is shown up to a predetermined stroke amount (a stroke amount at which the load of the tension compression spring member 13 becomes equal to the precompression load of the rubber member 31). After the predetermined stroke amount is exceeded, the load characteristic after the precompression load of the rubber member 31 is displayed in series.
  • the load generating device has an effect that the degree of freedom in design of load characteristics is high, and is useful for being applied to an automatic clutch system for a vehicle.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
  • Springs (AREA)

Abstract

L'invention concerne un dispositif de production de charge comprenant : un élément piston qui est stocké dans un cylindre et qui se déplace en va-et-vient dans une direction de course prédéfinie ; et un élément de production de charge qui produit une charge à appliquer sur l'élément piston. L'élément de production de charge comprend un élément ressort de traction/compression et un élément ressort à disque, l'élément ressort de traction/compression étant relié à une partie ressort à disque pré-comprimé.
PCT/JP2016/088684 2016-01-15 2016-12-26 Dispositif de production de charge WO2017122522A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-005801 2016-01-15
JP2016005801A JP2017124775A (ja) 2016-01-15 2016-01-15 荷重発生装置

Publications (1)

Publication Number Publication Date
WO2017122522A1 true WO2017122522A1 (fr) 2017-07-20

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Application Number Title Priority Date Filing Date
PCT/JP2016/088684 WO2017122522A1 (fr) 2016-01-15 2016-12-26 Dispositif de production de charge

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JP (1) JP2017124775A (fr)
WO (1) WO2017122522A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6259330U (fr) * 1985-10-02 1987-04-13
JPH0559041U (ja) * 1992-01-16 1993-08-03 三菱自動車工業株式会社 クラッチ制御装置
US20140230429A1 (en) * 2013-02-20 2014-08-21 Mando Corporation Pedal simulator for active brake system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6259330U (fr) * 1985-10-02 1987-04-13
JPH0559041U (ja) * 1992-01-16 1993-08-03 三菱自動車工業株式会社 クラッチ制御装置
US20140230429A1 (en) * 2013-02-20 2014-08-21 Mando Corporation Pedal simulator for active brake system

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