WO2004065812A1 - パワーアシストクラッチシステム、パワーアシストクラッチシステムの制御方法、およびパワーアシストクラッチシステムの制御プログラム - Google Patents
パワーアシストクラッチシステム、パワーアシストクラッチシステムの制御方法、およびパワーアシストクラッチシステムの制御プログラム Download PDFInfo
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- WO2004065812A1 WO2004065812A1 PCT/JP2004/000302 JP2004000302W WO2004065812A1 WO 2004065812 A1 WO2004065812 A1 WO 2004065812A1 JP 2004000302 W JP2004000302 W JP 2004000302W WO 2004065812 A1 WO2004065812 A1 WO 2004065812A1
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- Prior art keywords
- clutch
- force
- load
- assist
- unit
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/04—Control by fluid pressure providing power assistance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2540/00—Input parameters relating to occupants
- B60W2540/14—Clutch pedal position
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/12—Motorcycles, Trikes; Quads; Scooters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/11—Application
- F16D2500/1107—Vehicles
- F16D2500/1117—Motorcycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3023—Force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3026—Stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/314—Signal inputs from the user
- F16D2500/31406—Signal inputs from the user input from pedals
- F16D2500/31413—Clutch pedal position
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/314—Signal inputs from the user
- F16D2500/3146—Signal inputs from the user input from levers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/70404—Force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/706—Strategy of control
- F16D2500/70668—Signal filtering
Definitions
- the present invention relates to a power assist clutch system, a control method of a power assist clutch system, and a control of a power assist clutch system for assisting a clutch engagement / disengagement operation by an operating force transmitted from a clutch operation unit in an automatic vehicle.
- a power assist clutch system for assisting a clutch engagement / disengagement operation by an operating force transmitted from a clutch operation unit in an automatic vehicle.
- the assist force from the assist force generating means acts in reverse with respect to the movement of the driven member (member that operates for the clutch release) interlocked with the change in the operating speed of the clutch lever, and the resistance is reduced.
- the rate at which the output from the assisting force generating means is transmitted to the driven member as the assisting force changes greatly, whereby the assisting force that should be given at a certain clutch lever operating position is reduced. It changed, and the driver sometimes felt uncomfortable with the operability of the clutch lever. Disclosure of the invention
- An object of the present invention is to provide a power assist clutch system, a power assist clutch system control method, and a power assist clutch system control program that enable smooth control.
- a first aspect of the present invention is a clutch, a driving force transmitting member that transmits driving force to the clutch, and a clutch operation that is connected to the clutch via the driving force transmitting member.
- a power assist clutch system in which an assist force for assisting the on-off operation of the clutch by the operating force transmitted from the clutch operating portion is applied to the driving force transmitting member in the motor vehicle including the driving force transmitting member.
- a detection unit that detects an operation force for operating the clutch operation unit; a control unit that outputs a control signal that controls the assist force based on the operation force detected by the detection unit; An assisting force generator that generates the assisting force according to the output control signal, and synthesizes the operating force and the assisting force transmitted through the driving force transmitting member. And gist that and a driving force generation unit generating drive force for operating the clutch According to a second aspect of the present invention, there is provided a clutch, a driving force transmitting member for transmitting a driving force to the clutch, and a clutch operating unit connected to the clutch via the driving force transmitting member.
- a control method of a power assist clutch system for applying, to the driving force transmitting member, an assisting force for assisting an on-off operation of the clutch by an operating force transmitted from the clutch operating portion,
- a third aspect of the present invention is an automobile including a clutch, a driving force transmitting member that transmits driving force to the clutch, and a clutch operation unit connected to the clutch via the driving force transmitting member.
- a control program for controlling a power assist clutch system for applying an assisting force for assisting the on-off operation of the clutch by the operating force transmitted from the clutch operating portion to the driving force transmitting member.
- the gist of the present invention is to make a computer function as a control unit that outputs a control signal for controlling the assist force based on the operation force detected by a detection unit that detects the operation force.
- a “computer” refers to a CPU (Central Processing Unit) having arithmetic and control functions and a memory such as a RAM (Random Access Memory) for electronically storing programs and arithmetic results. Means at least an electronic device.
- CPU Central Processing Unit
- RAM Random Access Memory
- FIG. 1 is a block diagram illustrating a configuration of a power assist clutch system according to a first embodiment of the present invention.
- FIG. 2 is a block diagram showing a configuration of a load detection device that is a detection unit of the power assist clutch system according to the second embodiment of the present invention.
- FIG. 3 is an explanatory diagram showing a mounting structure of a sensor unit of the power assist clutch system according to the first embodiment of the present invention.
- FIG. 4 is a partial cross-sectional view showing the configuration of the sensor unit in FIG.
- FIG. 5 is a cross-sectional view taken along line VV of FIG.
- FIG. 6 is a partial cross-sectional view showing another configuration of the sensor unit of the power assist clutch system according to the first embodiment of the present invention.
- FIG. 7 is an explanatory diagram showing load characteristics of a clutch lever.
- FIG. 8 is an explanatory diagram showing a schematic configuration of a power assist clutch system according to the first embodiment of the present invention.
- FIG. 9 is a partial cross-sectional view illustrating a configuration of a main part of a clutch part of a motorcycle including a cam-type release mechanism.
- FIG. 0 is an explanatory diagram showing another schematic configuration of the power assist clutch system according to the first embodiment of the present invention.
- FIG. 11 is a schematic diagram in the direction of arrow B in FIG.
- FIG. 12 is a partial cross-sectional view showing a configuration of a main part of a clutch unit of a motorcycle having a rack 'and' pinion type release mechanism.
- FIG. 13 is a flowchart showing a processing content of a control method of the power assist clutch system according to the second embodiment of the present invention.
- FIG. 14 is a partial cross-sectional view showing a configuration of a sensor unit of the power assist clutch system according to the second embodiment of the present invention.
- FIG. 15 is a cross-sectional view taken along the line XV—XV in the direction of arrow C in FIG.
- FIG. 16 is an explanatory diagram showing a schematic configuration of a power assist clutch system according to a third embodiment of the present invention.
- FIG. 7 is a partial cross-sectional view showing the configuration of the sensor unit in FIG.
- FIG. 18 is a sectional view taken along the line XVIII-XVIII in the direction of arrow D in FIG.
- FIG. 9 is a partial cross-sectional view showing another configuration of the sensor unit of the power assist clutch system according to the third embodiment of the present invention.
- FIG. 20 is a partial cross-sectional view illustrating a configuration of a sensor unit of a power assist clutch system according to a fourth embodiment of the present invention.
- FIG. 21 is a cross-sectional view taken along the XXI-XXI line in a direction indicated by arrows in FIG.
- FIG. 22 is a partial cross-sectional view illustrating a configuration of a sensor unit of a power assist clutch system according to a fifth embodiment of the present invention.
- FIG. 23 is an explanatory diagram showing a schematic configuration of a power assist clutch system according to a fifth embodiment of the present invention.
- FIG. 24 is a partial cross-sectional view illustrating a configuration of a main part of a clutch unit of a motorcycle including a hydraulic release mechanism.
- FIG. 25 is a partial cross-sectional view showing a configuration of a sensor unit of a power assist clutch system according to a sixth embodiment of the present invention.
- FIG. 1 is a block diagram showing a configuration of a power assist clutch system according to a first embodiment of the present invention.
- the power assist clutch system 1 shown in FIG. 1 has an input unit 11 which is a clutch operating unit into which an operating force for operating the clutch by the driver is input, and the driver operates the input unit 11 by operating the clutch.
- a detection unit 13 that monitors an input state and detects a load, a torque, a displacement, and the like; a control unit 15 that is a control unit that generates a control signal based on an output signal of the detection unit 13; (1) (assist force generating section), which is an assist force generating means for generating an assist force according to the control signal from (5), and the operating force input from the input section 11 and the assist drive section ⁇ ⁇ ⁇ ⁇ ⁇ At least a joint portion 19 is provided as driving force generating means (driving force generating portion) for generating the driving force of the clutch in the driven portion 3 by combining the assist force generated in step 7.
- the input unit 11 is particularly connected to the clutch lever.
- a rotary potentiometer Detection of the rotation angle of the clutch lever, the stroke of the wire engaged with the clutch lever using the linear displacement potentiometer, and the rotation torque by a torque sensor are assumed.
- the case of detecting the load when the driver operates the clutch lever will be described in the present embodiment, but other than this, for example, a position sensor that detects a change in the position of the clutch lever in addition to the load may be used.
- the detection unit 13 can be configured by combining them.
- the control unit 15 is composed of an electronic device (hereinafter, referred to as a computer) having a calculation / control function by a CPU (Central Process Unit).
- a control program for controlling the power assist clutch system 1 is electronically stored in a memory (main storage device) such as a random access memory (RAM).
- main storage device such as a random access memory (RAM).
- the control unit 15 having such a configuration outputs a control signal for generating an appropriate assist force in accordance with the operation input state of the clutch lever detected by the detection unit 13 to perform smooth control.
- the power assist clutch system 1 is quickly optimized.
- a fail-safe function can be provided as a backup function in case of step-out or engine lock.
- the joint portion 19 connects the assist drive portion 17 and related parts of the clutch release mechanism in the clutch by wires, cables, link structures, gears, hydraulic or pneumatic piping, or the like.
- the detection unit 13, the control unit 15, and the assist drive unit # 7 are more preferably units that can be commonly used regardless of the vehicle type.
- FIG. 2 is a block diagram illustrating a configuration of a load detection device according to an embodiment when the detection unit 13 detects a load.
- the load detection device ⁇ ⁇ 11 as the detection unit 13 shown in the figure is configured as a differential amplifier circuit that amplifies and outputs the difference between the signals output from the pair of load sensors 23A and 23B. Have been.
- the load detection device 1 1 1 includes an oscillation circuit 21 that oscillates an AC signal and applies a voltage to the circuit, two load sensors 23 A and 23 B that detect an external load, Current detectors 25A and 25B, which consist of detection resistors that measure the output signal from each load sensor from the difference from the reference voltage, from a die, etc. to rectify and smooth the output signal Rectifier circuits 27A and 27B, and an amplifying unit 29 composed of an operational amplifier or the like for extracting a difference between output signals from the load sensors and amplifying the difference.
- the current detection section 25 A (25 B, hereinafter referred to in parentheses) and the rectifier circuit 27 A (27 B) output signals from the load sensor 23 A (23 B).
- the load detecting device 1 1 there is no other than the first signal detector (second signal detector) to be detected.
- the load sensors 23 A and 23 B are collectively referred to as a sensor section 123, and other parts are referred to as a signal detecting section 125. .
- the parts other than the sensor plates 23 are disposed on the same substrate as the control unit # 5.
- the temperature characteristics can be improved and the detection accuracy can be further improved.
- FIG. 3 is an explanatory diagram showing a mounting structure in a case where the sensor unit 123 constituted by using two load sensors is incorporated in the clutch lever 131.
- the clutch lever 31 is rotatably provided on the lever holder 33 around the center of rotation P thereof.
- the clutch lever 31 moves to the maximum stroke. Until it reaches (the direction of the arrow (counterclockwise) in the figure).
- One end of the wire 41 is engaged with the clutch lever 31 and the other end of the wire 41 is engaged with the joint 19.
- the joint 19 is provided on the driven part 3 with the camshaft 62 as a rotation axis as an example.
- the wire 41 engaged with the joint portion 19 via the end portion 415 transmits the assist force from the assist drive portion 17.
- a preload is applied to the rotating shaft by bringing a torsion spring into contact with the rotating shaft, and the roller 41 is tensioned in a predetermined direction by tension without loosening.
- the outer circumference of the wire 41 is covered with a wire tube 43.
- the two tube ends 45 provided at both ends of the wire tube 43 are used to secure the wires on the handle and clutch sides. Parts 47 and 49 are fixed respectively.
- the wire 41 moves a minute distance (about 10 mm to 15 mm) toward the clutch lever 31 (in the direction of the arrow (leftward) in the figure) following the rotation of the clutch lever 31 described above.
- FIG. 4 is a partial cross-sectional view showing a detailed configuration of the sensor section 123 when a magnetostrictive load sensor is used as the load sensor.
- the reference numerals 23 A and 23 B attached to the load sensor are applied to the magnetostrictive load sensor as they are.
- a ferromagnetic material such as iron, nickel, chromium, or ferrite having an inverse magnetostrictive effect that causes a change in magnetic permeability due to strain is used.
- This magnetostrictive load sensor 23 A has a load receiving portion 23 1 A as a magnetostrictive element having a rod shape made of a ferromagnetic material for directly receiving a load, and a load receiving portion 23 1 A around the load receiving portion. It is composed of at least a coil 23 A wound around a bobbin and a ferromagnetic case 23 A accommodating them. Although not shown, the coil 23A is electrically connected to the signal detection section 125 (the oscillation circuit 21 and the current detection section 25A). Also, one end of the load receiving portion 231A projects from the case 235A in order to abut against the load receiving surface. The load receiving portion 23 A is magnetized by the current flowing through the coil 23 A.
- the AC resistance (impedance) of the circuit including the coil 2 3 3 A inductance changes.
- the load can be detected electromagnetically by measuring the voltage change across the coil 233 A due to this impedance change with the signal detection unit 125.
- a holder 52 for fitting a tube end 45 of an outer tube 43 covering a wire 41 penetrating the sensor unit cover 51 is provided. Although not shown in the figure, there is an appropriate clearance around the wire 41 so that it can slide smoothly (the same applies to the following).
- One end of an elastic member 53 such as a spring is in contact with the holder 52, and a predetermined amount of load is applied in advance by fixing the other end with the fixing portion 54.
- the case 23 A of the magnetostrictive load sensor 23 A abuts on a plane opposite to the plane on which the end 41 1 of the wire 41 of the holder 52 abuts.
- the load receiving portion 23 A of the magnetostrictive load sensor 23 A is pressed by the pressing member 55.
- the load value applied to the magnetostrictive load sensor 23 A changes.
- the change in impedance caused by the change in the load value is detected by the signal detection unit 125 described above.
- FIG. 5 which is a cross-sectional view taken along line VV in the direction of arrow A in FIG. 4, another embodiment having the same configuration as the magnetostrictive load sensor 23A described above is provided in the present embodiment.
- a magnetostrictive load sensor 23 B is provided in the sensor part 123.
- the load receiving portion 23 1 B (not shown) of the magnetostrictive load sensor 23 B is previously made the same as the magnetostrictive load sensor 23 A by an elastic member such as a spring similarly to the magnetostrictive load sensor 23 A.
- the load receiving portion 2311B is configured so as not to receive the pressure caused by the operation of the clutch lever 311, and a constant load is always applied.
- the two magnetostrictive load sensors only need to be arranged so as to be symmetrical with respect to the line XX in FIG.
- the center axes OA and OB of the load receiving portions of the two magnetostrictive load sensors 23 A and 23 B pass on the same circle centered on the center axis 0 of the handle 35, for example. It is more preferable to have some symmetry. With such an arrangement, the temperature characteristics can be improved, and the detection accuracy of the load detecting device 111 can be further improved.
- FIG. 6 is a partial cross-sectional view showing a detailed configuration of the sensor unit 123 when an overload prevention mechanism is added.
- FIG. 4 shows the appearance of the magnetostrictive load sensor 23 A, it goes without saying that the specific internal configuration is the same as that shown in FIG.
- a load (preset load) is applied to the magnetostrictive load sensor 23 A in advance by providing a disc spring 56 between the sensor unit cover 51 and the pressing member 55.
- Magnetostrictive load sensor 23 Holder 52 that presses 3 A moves when the load exceeds the preset load, and when it reaches the overload range, holder 52 comes into contact with flange-shaped stopper provided on sensor unit cover 51.
- Protects the magnetostrictive load sensor 23 A by preventing the load more than necessary from being applied to the magnetostrictive load sensor 23 A by contacting 5 7. By providing such an overload prevention mechanism, the durability of the magnetostrictive load sensor 23 A can be improved.
- FIG. 7 is an explanatory diagram showing the relationship between the rotation angle of the clutch lever 31 and the load applied to the clutch lever 31 when the driver operates the clutch lever 31.
- the horizontal axis represents the rotation angle (lever angle) of the clutch lever 31 assuming no operation as zero, while the vertical axis represents the load (lever load) applied to the clutch lever 31. .
- the hysteresis curve 2000 shows the history from when the driver starts operating the clutch lever 31 to when the driver returns to the original position (the position where the lever angle is zero).
- the lever load increases sharply to the maximum load point A near the half-clutch region (0 ⁇ A). That is, the section between O and A is a section where the driver feels that the clutch lever 31 is "heavy".
- the load applied at the maximum stroke point B may be the largest in the entire history.
- the clutch lever 31 in the operation of turning the clutch lever 31 on and off, the load value is relatively larger when the lever angle is raised than when the lever angle is lowered.
- assist force changing means capable of appropriately adjusting the ratio of the assist force to the load when the lever angle is raised and when the lever angle is lowered (assist ratio)
- the clutch lever 31 can be operated. It is possible to generate assist power according to the input situation. In this case, for example, while increasing the assist ratio in the section O ⁇ A where the driver feels the most burden, while reducing the assist ratio in the section B ⁇ C ⁇ 0, the adjustment can be made appropriately. Make settings. Note that it is of course possible to provide such an assist force changing means in the control unit 15.
- the absolute value of the load actually applied to the clutch lever 31 differs depending on the type of vehicle, the displacement, and the like, and also the load value felt by the driver varies. That is, the optimum assist ratio differs depending not only on the vehicle type but also on the driver who actually operates the clutch lever 31. Therefore, it is more preferable that the above-mentioned assist force changing means is provided with a setting mechanism that enables the assist ratio to be changed.
- the assist ratio some values are stored in advance in the memory of the control unit 15 at the time of manufacture, and the driver selects a desired assist ratio from the values and sends the assist ratio to the control unit 15.
- the configuration may be such that input is provided from an input unit provided, or the configuration may be such that the driver can set and input an arbitrary assist ratio.
- the hysteresis curve 200 in FIG. 7 is merely an example, and the load characteristics of the clutch lever 31 differ depending on the vehicle type and the like. However, it is not limited to this embodiment, but in all embodiments according to the present invention, it is possible to adjust or change the above-described assist ratio according to the load characteristics of the clutch lever 31. Not even.
- FIG. 8 is an explanatory diagram showing a schematic configuration of a power assisted clutch system 1 using the sensor section 123 having the above configuration.
- the signal detected by the sensor section 123 is transmitted to the signal detection section 125 and input to the control section 15 as a sensor output signal.
- the control unit 15 outputs a control signal based on the sensor output signal to the assist driving unit 17.
- the assist drive unit 17 generates an assist force according to the control signal.
- the manual operation force from the clutch lever 31 and the assist force from the assist drive unit 17 are separately transmitted to the joint unit 19.
- the joint portion # 9 the operating force transmitted from the clutch lever 31 via the wire 41 and the assist force transmitted from the assist driving portion 17 are combined to transmit the driving force to the driven portion 3.
- the power assist clutch system 1 is shown as a schematic diagram in FIG. 8, the actual wiring between the sensor section 123 and the signal detection section 125 is different from that of the actual wiring. It has been simplified. That is, actually, the wiring from the oscillation circuit 21 and the wiring connected from the two load sensors 23 A and 23 B to the current detection units 25 A and 25 B are provided between them. Needless to say.
- the driven section 3 includes a clutch release mechanism that transmits the driving force from the joint section 19 to the clutch section 70.
- FIG. 8 schematically shows a schematic configuration when a cam-type release mechanism using a cam shaft 62 is used as an example of the clutch release mechanism. Transmission, etc.) are omitted.
- a pull lever also referred to as a clutch release lever
- the pull lever is provided so as to pass through the center of rotation.
- the cam shaft 62 contacts the push rod 71, the push rod 71 is pulled out to transmit the driving force to the clutch part 70.
- FIG. 9 is a partial cross-sectional view illustrating a detailed configuration example of a main part of the clutch unit 70.
- the clutch portion 70 shown in the figure is a multi-plate clutch conventionally used in motorcycle engines in general.
- the push lever penetrates the hollow shaft center of the main shaft 72 by operating the clutch lever 31.
- each of the clutch outer members 75 which are pressed by the elastic force of the clutch spring 74 via the pressure plate 73. Release the frictional engagement between the plate 76 and the disks 78 on the clutch inner 77 side, release the link between the clutch outer 75 and the clutch inner 77, and release the clutch.
- a pull lever 6 1 having a cam shaft 6 2 as a rotation axis is adjacent to the end of the push rod 7 1, and a wire 41 extending from a joint 19 is connected to the pull lever 61.
- the pull lever 61 is rotated about the center axis of the cam shaft 62 by the driving force transmitted from the joint 19 via the wire 41.
- the cam ridge formed on the cam shaft 62 pulls out the push rod 71 and pulls out the pressure plate 73.
- the movement distance of the pressure plate 73 by operating the clutch lever 31 is about 2 mm.
- the half-clutch state occurs when the pressure plate 73 moves at most about 1 mm.
- the rotational driving force transmitted from the crankshaft in the driven part 3 can be intermittently connected to a drive system below the transmission (not shown).
- the clutch unit 70 applied in the present embodiment is not particularly limited to a dry type and a wet type.
- the rotation method of the pull lever 61 when the cam-type release mechanism is used is not necessarily limited to the method described above, and is shown in FIGS. 10 and 11 (schematic diagram in the direction of arrow B in FIG. 10).
- the assist force from the assist drive unit 17 generates the assist force by driving the actuators constituting the assist drive unit ⁇ 7 by the motor.
- the rotational driving force due to the evening is transmitted to the joint part 19 via the assist driving force transmitting shaft 17 1 for transmitting the driving force of the assist force, and transmitted from the clutch lever 31 to the wire 41.
- the joint 19 is rotated in cooperation with the operating force to be applied. Therefore, the assist drive unit 17 is appropriately arranged in the space in the driven unit 3.
- the configuration and operation of the other parts are the same as those described above (see FIG. 8).
- the clutch release mechanism itself is not limited to the cam type, and a clutch release mechanism such as a rack, and pinion type, or a ball spring type may be applied.
- a clutch release mechanism such as a rack, and pinion type, or a ball spring type may be applied.
- the rack-and-pinion type is used, as shown in the partial cross-sectional view of FIG. 12, the pinion gear 6 is operated by operating the joint 19 according to the driving force transmitted through the wire 41. 4 rotates, and the push rod 71 moves toward the outside of the engine to pull out the presser plate 73 and disengage the clutch.
- a control method of the power assist clutch system 1 having the above configuration will be described with reference to a flowchart shown in FIG.
- the control method shown in the figure is the same in each of the embodiments described later.
- the detection unit 13 detects the input value of the operating force from the clutch lever 31 and the control unit 15 determines whether the value of the sensor output signal, which is the detection result, exceeds a predetermined threshold (In step S 1), when it exceeds (YES), the assistance is started (step S 3). If not (NO), the process of step S1 is continued.
- the threshold value is such a value that it can be determined that the driver has operated the vehicle by himself / herself. Further, the input value changes according to the physical quantity detected by the detection unit 13, and is a load value when a load is detected, and an input value corresponding to the load value when a rotation speed or a displacement is detected. Value. Therefore, the threshold value itself is set with a physical quantity corresponding to the detected quantity.
- step S3 the control unit 15 compares the operating speed of the clutch lever 31 by the driver with the driving speed of the actuator in the assist driving unit 17 (step S5). If the drive speed is higher (YES), lower the drive speed (step S7). If the drive speed is lower (NO), the drive speed is lower. A control signal for increasing the driving speed is generated (step S9). This allows The control is performed such that the driving speed of the actuator always follows the operating speed of the clutch lever 31 by the driver.
- the speed is obtained by calculating the displacement of the load sensor ⁇ potential.
- the encoder driving speed can be measured by installing an encoder.
- step S11 it is determined whether or not the stop time is equal to or longer than a predetermined time.
- step S11 if the stop time of the clutch lever 31 is equal to or longer than the predetermined time in step S11 ( ⁇ ES), the assist force is gradually reduced so that the assist force becomes 0 after a predetermined time has elapsed.
- a control signal is generated to decrease the value (step S13). This is a process for preventing accidents from occurring in the factory by continuing assistance when the driver stops the clutch lever 31.
- step S25 If the input value becomes zero in the process of decreasing the assist force (N0 in step S15), the assist is stopped (step S25). On the other hand, if the input value is not zero (YES in step S15), the process proceeds to step S25 when the input value falls below the threshold value (N0 in step S ⁇ 7) and stops the assistance. .
- step S17 If the input value does not fall below the threshold value in step S17 (N0 in step S17), the process proceeds to step S19.
- step S 19 it is determined whether or not to re-input the operating speed of the clutch lever 31 and the driving speed of the actuator, and if the input is to be performed again (YES), the flow returns to step S 5 to return to step S 5. Repeat the process. On the other hand, if re-input is not performed (NO), the assistance is stopped (step S25).
- step S11 If the stop time of the clutch lever 31 has not reached the predetermined time in step S11 (NO), the input value from the clutch lever 31 is compared with the threshold value (step S2 1). If the input value is small (YES in step S21), the process proceeds to step S25 to stop the assistance. On the other hand, if the input value is larger (NO in step S21), the process proceeds to step S23 and In the same manner as in step S23, it is determined whether or not to re-input the operating speed of the clutch lever 31 and the driving speed of the actuator, and if the re-input is to be performed (YES), the process returns to step S5 and is performed. If not (NO), proceed to step S25 to stop the assistance.
- step S25 After stopping the assistance in step S25, as long as the main switch is in the ON state (ON in step S27), the flow returns to step S1 to repeat the above processing.
- step S25 the control processing according to the present embodiment ends.
- the operation load when the load applied to the clutch lever is increased, the operation load can be reduced and the operation speed can be improved by generating the assist force.
- the load when the load is reduced, no assistance is performed or the assistance ratio can be kept low, so that the desired clutch connection state of the driver can be quickly reached, and operability can be improved.
- control method includes the feedback mechanism, control accuracy and reliability can be improved.
- the burden at the time of operating the clutch operating unit is reduced, and quick and smooth control by the generation of the assist force according to the operation input state of the clutch operating unit is achieved. It becomes possible.
- the assist force increases when the input value of the load or the like detected by the detection unit is large, so that the load on the driver can be limited to a certain level or less, and the operability can be improved. Can be obtained.
- the sensor unit can be retrofitted, it can be applied regardless of the vehicle type, and the cost is not required.
- FIG. 14 is a partial cross-sectional view showing a detailed configuration of a sensor unit applied to the power assist clutch system according to the second embodiment of the present invention.
- the sensor unit 223 shown in the figure is built in the clutch lever 31 of the handlebar 35 of the motorcycle similarly to the sensor unit 123 described in the first embodiment (see FIG. 3).
- control is performed by detecting the load applied during operation, but physical quantities other than the load (rotation angle, linear displacement, rotation torque, etc.) may be detected as in the first embodiment. .
- a sensor fixing portion 58 for storing and fixing the two magnetostrictive load sensors 63A and 63B is provided inside the sensor portion 222 shown in Fig. 14.
- the sensor fixing section 58 has a vertically convex cross section in the cross section shown in FIG.
- the upper end of the load receiving portion 63 1 A of the magnetostrictive load sensor 63 A is in contact with the end 4 1 1 of the wire 4 1, and has a configuration capable of directly detecting the load applied to the wire 4 1. are doing. For this reason, the end 4 11 1 shown in FIG. Although a contact portion 411a having a flat surface capable of contacting the upper end portion of the sensor 63A is provided, it is needless to say that the shape shown is merely an example and other shapes may be used. As long as it comes into contact with the upper end of the load receiving portion 631A, it does not vibrate in any way.
- the magnetostrictive load sensor 63 has a cylindrical shape having a hollow portion for passing through the wire 41, and has a load receiving portion 631, which receives a load from the outside, and a load receiving portion 631, which receives a load from the outside. It comprises a coil 633 wound around, a load receiving section 631, and a case 635, which is an accommodating section made of a ferromagnetic material for accommodating the coil 633.
- the coil 633 is housed in a bobbin made of a resin such as nylon, which is disposed around the load receiving portion 631.
- the load receiving portion 631 which is constituted by a rod-shaped magnetostrictive element like the magnetostrictive load sensors 23A and 23B in the second embodiment, has a hollow portion through which the wire 41 penetrates. I have. The wire 41 is inserted in close contact with the inner surface of the hollow portion of the load receiving portion 631.
- Fig. 15 which is a cross-sectional view taken along the line XV-XV in the direction of arrow C in Fig. 14, the circle forming the cross section of the case 635A and the ring of the load receiving portion 631A Has a shape whose centers match each other.
- the cross section of the magnetostrictive load sensor 63A is point-symmetric with respect to the central axis O 'of the wire 41 (the same applies to the magnetostrictive load sensor 63B).
- the number of turns of the coil 633 wound around the load receiving portion 631 generates a magnetic field strength necessary for the magnetic flux to saturate when a predetermined current flows through the coil 633. It is set as follows. The magnetic flux generated by the current flowing through the coil 633 wound in this way is transferred to the ferromagnetic load receiver 631 and the case. Stabilized by 6 3 5 That is, the load receiving portion 631 and the case 635 form a magnetic flux path as a whole.
- the upper end of the magnetostrictive load sensor 63 A where the load receiving portion 63 A of the magnetostrictive load sensor 63 A projects from the case 63 A is connected to the end of the wire 41 as described above.
- the upper end of the load receiving portion 631A is pressed by a preload applied to the end 413 of the wire 41 on the clutch side via a torsion spring.
- the bottom of the case 635B of the magnetostrictive load sensor 63B contacts the sensor fixing portion 58. Since the upper end of the load receiver 6 31 B of the magnetostrictive load sensor 6 3 B is fitted in a gap formed between the convex protrusions of the sensor fixing portion 58, the wire 4 1 B There is no load due to the pressing.
- the clutch lever 31 when the clutch lever 31 is operated, a load is applied only to the magnetostrictive load sensor 63A, and a difference occurs between the currents flowing through the two magnetostrictive load sensors. By amplifying the difference between the current signals by the signal detector 125, the load at the time of operating the clutch lever 31 can be detected.
- the control unit 15 receives a sensor output signal based on the detected load, the control unit 15 executes a calculation for obtaining an optimum assist force in accordance with the sensor output signal, and outputs the calculation result.
- a control signal for generating an assist force based on the control signal is transmitted to the assist driver 17.
- the magnetostrictive load sensors 63A and 63B having a load receiving section are arranged coaxially with the axis (the central axis of the wire 41) to which a load is applied. This enables the load sensor to receive the load applied in the axial direction of the wire 41 uniformly on the same axis, thereby improving the measurement accuracy.
- the magnetostrictive load sensor can be configured with a smaller number of components than in the past, resulting in cost reduction. It is possible to reduce as well.
- the sensor section 223 itself can be laid out in a compact manner, and it is possible to obtain an effect that the design is excellent and the appearance does not have a very unnatural feeling when attached later. As in the first embodiment, it is of course possible to engage the magnetostrictive load sensor 63 according to the present embodiment with the joint 19 side.
- the size of the system can be further reduced by applying a sensor unit including a magnetostrictive load sensor having a hollow load receiving unit to the detecting unit.
- the configuration of the magnetostrictive load sensor applied in the present embodiment is not limited to this.
- the load receiving portion 631 can be fitted to the case 635 so as to reach the bottom surface of the sensor.
- the entire load receiving portion can receive a load without passing through the case, and thus may be more advantageous than the magnetostrictive load sensor 63 in terms of sensitivity and responsiveness.
- the covering portion may be a hard resin such as polyacetal, Teflon (registered trademark) tube, fluororesin, or a non-magnetic material such as SUS304, SUS316 which is austenitic stainless steel.
- a hard resin such as polyacetal, Teflon (registered trademark) tube, fluororesin, or a non-magnetic material such as SUS304, SUS316 which is austenitic stainless steel.
- a reinforcing portion having a flange shape near the boundary between the load receiving portion 631 of the magnetostrictive load sensor 631 and the bottom of the case 635 (not shown).
- the ratio of the thickness of the bottom portion to the outer diameter of the load receiving portion 631 is appropriately adjusted so that the bottom portion of the case 635 does not shear and yield due to the load applied to the load receiving portion 631. Further downsizing can be achieved.
- various shapes such as one or a plurality of stepped shapes, a tapered shape, an R shape, and the like can be applied.
- the load receiving portion and the case can be made of a ferromagnetic material having a porous structure (a structure having porosity and permeability).
- a ferromagnetic material having a porous structure has a smaller average effective diameter and better frequency characteristics than a bulk single substance.
- a metal foam network formed of such a ferromagnetic material as the load receiving portion, a desired sensitivity can be obtained without reducing the outer diameter of the load receiving portion, and the magnetostrictive type can be obtained. This makes it possible to prevent the strength of the load receiving portion from being weakened due to the reduced size and weight of the load sensor.
- the load receiving portion and the case can be produced by molding, a process such as cutting is not required, and cost reduction by mass production can be realized.
- the magnetostrictive load sensor described above has a load receiving portion composed of a single magnetostrictive element having a hollow portion
- the load receiving portion may be made of a ferromagnetic material. It is also possible to comprise a plurality of solid rods. These solid rods are arranged so that the central axis in the longitudinal direction (the height direction of the solid rod) passes on the same circumference, and the central axes are oriented in directions parallel to each other. It constitutes. For this reason, the load receiving portion is fixed between the load receiving portion and the hollow portion by providing a cylindrical portion made of the same material as the above-described covering portion and inscribed in each solid rod.
- the magnetostrictive load sensor used in the present embodiment has a hollow portion into which the wire 41 is inserted, various design changes and the like can be made, and all of them have the same effect. To play.
- FIG. 16 is an explanatory diagram showing a schematic configuration of a power assist clutch system according to a third embodiment of the present invention.
- a sensor unit 3 23 is provided at a position corresponding to the wire fixing unit in the above embodiment. Thus, an increase in the load value due to friction generated between the wire 41 and the outer tube 43 is extracted.
- the power assist clutch system shown in Fig. 16 differs from that shown in Fig. 8 in that the driving force obtained by combining the manual operation force and the assist force at the joint 19 is applied to the pull lever 6 1 It is transmitted through the wire 41 of the book, and the clutch is turned on and off.
- the clutch lever 31 is normally used unlike the above-described embodiment in which the sensor section is built.
- the ends 4 11 and 4 13 of the wire 41 engaged with the clutch lever 31 are engaged with the clutch lever 31 itself and the joint 19, respectively.
- the wire 41 for transmitting the operating force from the clutch lever 31 to the joint portion 19 is appropriately preloaded to tension the wire 41.
- the wire 41 is tensioned by a torsion spring that contacts the rotation shaft of the pull lever 61. Prevents relaxation.
- FIG. 16 is merely an example, and in the present embodiment, it is of course possible to adopt a configuration as shown in FIG. 8 (the pull lever corresponds to the joint portion 19 itself).
- FIG. 17 is an explanatory diagram showing a detailed configuration of the sensor unit 323 when the sensor unit 323 including two load sensors is installed on the handlebar 35 near the clutch lever 31.
- FIG. 17 it is possible to install the sensor section 3 23 at a position corresponding to the wire fixing section on the clutch cable side, but in the following description, the case where the sensor section 3 23 is provided on the handle side will be described.
- the sensor section 3 2 3 detects the load applied to the driver in accordance with the operation of the clutch lever 3 1. More specifically, the sensor section 3 2 3 is connected to the clutch lever 3 1, and the other end is connected to the joint section 1. It has a configuration for detecting an increase in load value due to friction generated between the wire 41 and the outer tube 43 engaged with the driven member 9 (or the driven portion 3).
- FIG. 17 is a partial cross-sectional view showing a detailed configuration of the sensor section 123 when a magnetostrictive load sensor is used as the load sensor.
- the magnetostrictive load sensor used in the present embodiment is the magnetostrictive load sensor 23 having the same configuration as in the first embodiment.
- the sensor section 32 3 is provided with a holder 52 for fitting the tube end 45 of the outer tube 43 covering the wire 41 penetrating the sensor unit cover 51.
- One end of an elastic member 53 such as a spring is in contact with the holder 52, and a predetermined amount of load is applied in advance by fixing the other end with the fixing portion 54.
- the case 23 A of the magnetostrictive load sensor 23 A is in contact with the plane of the holder 52 opposite to the plane in which the tube end 45 is fitted.
- the load receiving portion 23A of the magnetostrictive load sensor 23A is pressed by the pressing member 55.
- the load applied to the magnetostrictive load sensor 23 A changes.
- the impedance change with the change in the load value, c detected by the signal detecting unit 1 2 5 described above Incidentally, the distance 2 3 A magnetostrictive load sensor by the clutch lever 3 1 operation moves under load is most ⁇ mm.
- this embodiment also has the same configuration as the magnetostrictive load sensor 23A.
- Two magnetostrictive load sensors 2 3 B are provided in the sensor section 3 2 3. Similar to the magnetostrictive load sensor 23B in the first embodiment, a constant load is constantly applied to a load receiving portion 2311B (not shown) of the magnetostrictive load sensor 23B. Therefore, when the clutch lever 31 is operated, there is a difference between the loads applied to the magnetostrictive load sensors 23A and 23B. By performing differential amplification in 1 25, it is possible to accurately detect the load applied to the clutch lever 31.
- the two magnetostrictive load sensors 23 A and 23 B are arranged near each other, and the center axes OA and OB of the respective load receiving portions are the same circle centered on the center axis 0 of the handle 35. Passing above. More preferably, the two magnetostrictive load sensors may be arranged so as to be symmetrical with respect to the line X′—X ′ in FIG. With such an arrangement, the temperature characteristics can be improved, and the detection accuracy of the load detecting device 111 can be further improved.
- the power assist clutch system 1 can be appropriately added later.
- FIG. 19 is a partial cross-sectional view showing a detailed configuration of the sensor unit 3 23 when an overload prevention mechanism is added. In this figure, the appearance of the magnetostrictive load sensor 23 A is shown, but the internal configuration is the same as that shown in FIG.
- the basic configuration of the overload prevention mechanism is the same as that described in the first embodiment (see FIG. 6), and thus the description is omitted.
- the reference numerals of the respective parts in FIG. 17 are described using the same reference numerals as the corresponding parts in FIG.
- FIG. 20 is a partial cross-sectional view showing a detailed configuration of a sensor unit applied to the power assist clutch system according to the fourth embodiment of the present invention.
- the sensor section 4 23 shown in the figure is the same as the sensor section 3 2 3 (FIG. 1) described in the third embodiment. 6) is installed in the wire fixing part near the clutch lever 31 of the handlebar 35 of the motorcycle.
- a sensor fixing portion 58 for storing and fixing the two magnetostrictive load sensors 63A and 63B is provided inside the sensor portion 423 shown in FIG.
- the sensor fixing portion 58 has a vertically convex cross section in the cross section shown in FIG.
- the bottom surface of the case of the magnetostrictive load sensor 63 A (the surface on the opposite side when the protruding portion of the load receiving portion is the top surface) and the magnetostrictive load sensor 63 B The upper surfaces are fitted respectively. Since the magnetostrictive load sensors 63A and 63B are the same as those used in the second embodiment, they are denoted by the same reference numerals as in the second embodiment.
- FIG. 21 which is a cross-sectional view taken along the line XXI-XXI in the direction of arrow E in FIG. 20, the circle forming the cross section of the case 635 A and the ring of the load receiving portion 631 A Have the same shape.
- the cross section of the magnetostrictive load sensor 63A is point-symmetric with respect to the central axis 0 'of the wire 41 (the same applies to the magnetostrictive load sensor 63B).
- the load applied to the wire 41 in the axial direction can be detected coaxially, and the upper end of the load receiving portion 631 A can receive even power, thereby improving the measurement accuracy.
- Magnetostrictive load sensor 6 3 A Load receiving part 6 3 1 A protrudes from case 6 35 A A part of magnetostrictive load sensor 6 3 A has wire 4 Tube end made of aluminum etc. to fix the end of 3
- control unit 15 When the control unit 15 receives a sensor output signal based on the detected load, the control unit 15 executes a calculation for obtaining an optimum assist force in accordance with the sensor output signal, and outputs the calculation result.
- a control signal for generating an assist force based on the control signal is transmitted to the assist driver 17.
- the sensor unit 423 described above uses a sensor having the same configuration as the magnetostrictive load sensor 63 in the second embodiment, it is possible to improve measurement accuracy and reduce the size and weight of the entire load detection device. In terms of realization and the like, the same effect as in the second embodiment can be obtained.
- the system can be further reduced in size.
- the same effects as those of the second embodiment can be obtained in realizing a small and lightweight detection device as a whole.
- the configuration of the magnetostrictive load sensor applied in the present embodiment is not limited to the one described above, and various design changes and the like may be made as long as there is a hollow portion into which the wire 41 is inserted.
- the second embodiment is the same as that of the second embodiment in that all of them can achieve the same effect.
- FIG. 22 is a partial cross-sectional view showing a detailed configuration of a sensor unit applied to a power assist clutch system according to a fifth embodiment of the present invention.
- This embodiment In, hydraulic piping (oil hose) is used as the driving force transmission system (power transmission member).
- the sensor section 52 3 shown in FIG. 22 has a hydraulic section 83 with an elastic member 82 such as a spring incorporated therein, and a hollow section made of brass 84 covered with a resin 85. Separated by a removable seal member.
- the first embodiment is provided between a pressing member 86 for pressing and moving the sealing member in accordance with the operation of the clutch lever 31 and a receiving member 87 directly receiving the pressing from the clutch lever 31.
- the signal detecting section 12 is configured by symmetrically arranging the magnetostrictive load sensor 23 B having the same shape as the magnetostrictive load sensor 23 A as in the first embodiment. 5 transmits the sensor output signal obtained by differentially amplifying the difference between the signals from the two magnetostrictive load sensors to the control unit 15.
- the number of parts can be reduced, so that the design is excellent as in the second embodiment, a lightweight compact, and uncomfortable after mounting. It is possible to obtain the effect that it is not necessary to hold the user.
- FIG. 23 is an explanatory diagram illustrating a schematic configuration of a power assisted clutch system configured by using the above-described sensor unit 523.
- the hydraulic pressure generated in the sensor section 5 23 by the operation of the clutch lever 31 is transmitted to the release cylinder 91 of the clutch section 70 via the oil hose 81.
- the hydraulic pressure transmitted to the release cylinder 91 moves the push rod 71 to press the pressure plate in the clutch part 70, and as a result, the on / off operation of the clutch is performed.
- the load value detected by the sensor unit 5 23 is differentially amplified by the signal detection unit 125, and then output to the control unit 15 as a sensor output signal. Is transmitted to the motor unit 173.
- the motor unit 173 is connected to the push rod 71 in the driven part 3, and assists the movement of the push rod 71 by the assist force generated based on the control signal. Occurs. That is, an assist force for clutch release is applied to the push rod 71 that operates for clutch release in accordance with the operation of the clutch lever 31. In this sense, in the case shown in FIG. 23, the release cylinder 91 and the motor unit 173 form a driving force generating means (driving force generating unit) as a whole.
- FIG. 24 is a partial cross-sectional view showing a configuration of a main part of the clutch portion 70 in the hydraulic type.
- the other end of the push rod 71 which is linked to the pressure plate 73 of the clutch part 70 at one end, is connected to the release cylinder 91 to which the oil hose 81 from the clutch lever 31 is connected.
- the piston 9 2 is slid by the oil pressure, and the push rod 7 1 is moved. Press to the side of the clutch part 70.
- the mechanism for transmitting the assist force to the push rod 71 is composed of a module 1 73, a torsion spring coil spring 93 having a low elastic constant provided inside thereof, and a substantially Y
- a case is shown in which the fork member 94 is formed.
- the push rod 71 is formed with a flange portion 95 for receiving an assist force generated by the motor unit 1 73 via the fork member 94.
- a more specific assist force generating mechanism will be described.
- a fall guide for preventing the coil spring 93 from falling is coaxially fixed to the output shaft 97 (not shown).
- a coil spring 93 is arranged so as to surround the outside at an interval from the guide.
- the fork member 94 is swingably supported at one end side (both upper ends of a square) by a shaft 96 fixed to a predetermined vertical position.
- One end of the coil spring 93 is fixed to the output shaft 97 of the motor unit 173 near the base of the falling guide, and the other end of the coil spring 93 is the other end movable side of the fork member 94 (the lower end of the square).
- the intermediate portion of the fork member 94 is in contact with the flange portion 95 of the push rod 71 so as to sandwich the push rod 71.
- control method of the power assist clutch system according to the present embodiment is the same as that in each of the above embodiments (see FIG. 13).
- FIG. 25 is a partial cross-sectional view showing a detailed configuration of a sensor unit applied to the power assist clutch system according to the sixth embodiment of the present invention.
- the sensor unit 6 23 shown in the same figure is symmetrical with respect to the surface where the second magnetostrictive load sensors 23 A and 23 B (having the same configuration as the first embodiment) having the same shape abut against each other. And is provided at an intermediate portion of the wire 41.
- the end portion 4 11 is engaged with the clutch lever 3 1, and the end portion 4 13 is engaged with the driven portion 3 side.
- Two magnetostrictive load sensors 23 A and 23 B are accommodated in the sensor housing part 14 1 so as to be movable in the axial direction of the wire 41, and an elastic member 14 4 such as a spring is provided. A and 144B are biased in opposite directions.
- a pressing member 144 having a flange shape is further provided inside the sensor accommodating portion 141.
- the preset load of the elastic member 144 A is set to be larger than the preset load of the elastic member 144 B (about 10 kg weight). Therefore, the flange-shaped portion of the pressing member 144 is required.
- the end of the portion of the magnetostrictive load sensor 23 A that protrudes at the load receiving portion 23 A of the load sensor abuts and is stationary.
- the end of the load receiving portion 23 1 B of the magnetostrictive load sensor 23 B is supported by an elastic member 144 B so as not to receive a load from outside.
- the upper surface of the case 2 35 A which corresponds to the protruding portion side of the load receiving portion 2 31 A, is fitted and held by a flange-shaped stopper 14 9 integrally formed with the sensor accommodating portion 141.
- the overload is prevented from being applied to the magnetostrictive load sensor 23 A. Therefore, even if a large external load is applied, only a load equal to or less than a certain value acts on the magnetostrictive load sensor 23 A, effectively protecting the magnetostrictive load sensor 23 A and improving its durability. I do.
- FIG. 25 shows a case where the load receiving portion 23 1 A comes into contact with the pressing member 144 to receive a load directly.
- the load receiving portion 23 1 A comes into contact with the pressing member 144 to receive a load directly.
- both ends of the wire 41 and the sensor housing part 141 are connected to the wire bonding parts 144A and 147A. Each is joined by 4 7 B.
- the wire 41 moves to the end 4 1 1 side by the operation of the clutch lever 3 1, and the load applied to the magnetostrictive load sensor 2 3 A Decreases.
- the load applied to the clutch lever 31 can be detected by differentially amplifying the impedance change caused by the decrease in the load by the load detecting device 111 in the same manner as in the above embodiment.
- the sensor accommodating portion 14 ⁇ ⁇ and the pressing member 144 can freely rotate relative to each other, the torsion and bending of the sensor portion 42 4 are appropriately adjusted. As a result, high-precision load detection becomes possible, and wasteful action generated due to engine vibrations and the like can be appropriately released, and the durability of the sensor section 623 itself can be increased.
- the sensor unit 6 23 described above does not need to be fixed at a predetermined place, and can be mounted anywhere between the wires 41, so that there is an advantage that the degree of freedom of layout is high. .
- the sensor part 623 is placed in a position that is hidden inside the motorcycle fairing (cowling). Another major advantage is that it is easy to install and does not require changes to existing parts.
- the power assist clutch system and the control method of the system according to the present invention can be applied to a clutch system of not only a motorcycle but also a four-wheel vehicle.
- a clutch system of not only a motorcycle but also a four-wheel vehicle by appropriately mounting the sensor unit inside the vehicle body behind the clutch pedal (clutch lever) as viewed from the driver's seat, the burden on the driver for operating the clutch can be reduced.
- the present invention can include various embodiments having the same effects as described above.
- Industrial applicability As described above, the present invention can include various embodiments having the same effects as described above.
- the burden of operating the clutch operating unit is reduced, and the quick and smooth operation is achieved by the generation of the assist force according to the operation input state of the clutch operating unit. It is possible to provide a power assist clutch system, a power assist clutch system control method, and a power assist clutch system control program that enable control.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (2)
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JP2005508052A JPWO2004065812A1 (ja) | 2003-01-22 | 2004-01-16 | パワーアシストクラッチシステム、パワーアシストクラッチシステムの制御方法、およびパワーアシストクラッチシステムの制御プログラム |
EP04702828A EP1593869A1 (en) | 2003-01-22 | 2004-01-16 | Power-assisted clutch system, method for controlling power-assisted clutch system, and program for controlling power-assisted clutch system |
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JP2003013439 | 2003-01-22 | ||
JP2003-013439 | 2003-01-22 |
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JP (1) | JPWO2004065812A1 (ja) |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2008081055A (ja) * | 2006-09-28 | 2008-04-10 | Honda Motor Co Ltd | クラッチ装置 |
JP2010215085A (ja) * | 2009-03-16 | 2010-09-30 | Honda Motor Co Ltd | 車両用電子クラッチ制御装置 |
JP2011011659A (ja) * | 2009-07-02 | 2011-01-20 | Honda Motor Co Ltd | ブレーキ装置 |
WO2019032674A1 (en) * | 2017-08-08 | 2019-02-14 | Alivel Infinity Llc | APPARATUS FOR ASSISTING ELECTRONIC CLUTCH |
JP2019183967A (ja) * | 2018-04-10 | 2019-10-24 | 株式会社シマノ | 人力駆動車の回転装置 |
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US7591358B2 (en) | 2006-09-12 | 2009-09-22 | Dean Pick | Hydraulic control system and apparatus for friction clutch |
JP2009276290A (ja) | 2008-05-16 | 2009-11-26 | Yamaha Motor Co Ltd | 磁歪式荷重センサおよびそれを備えた移動体 |
JP5737740B2 (ja) * | 2010-11-24 | 2015-06-17 | Udトラックス株式会社 | 機械式自動変速機のクラッチ切断制御機構 |
CN102996680B (zh) * | 2012-11-29 | 2015-12-02 | 浙江吉利汽车研究院有限公司杭州分公司 | 一种辅助离合器系统 |
FR3011599B1 (fr) * | 2013-10-09 | 2017-12-22 | Valeo Embrayages | Actionneur pour systeme de transmission |
CN107202082B (zh) * | 2017-07-14 | 2019-05-03 | 上海电气电站设备有限公司 | 具备低速保护功能的自动同步离合器低速同步方法 |
US11162546B2 (en) | 2017-10-31 | 2021-11-02 | Honda Motor Co., Ltd. | Clutch control device |
WO2019087511A1 (ja) | 2017-10-31 | 2019-05-09 | 本田技研工業株式会社 | クラッチ制御装置 |
JP6826522B2 (ja) * | 2017-11-27 | 2021-02-03 | 本田技研工業株式会社 | クラッチ制御装置 |
CN108152047B (zh) * | 2017-12-14 | 2019-06-28 | 重庆厚全科技发展有限公司 | 一种摩托车把手夹紧装置 |
CN110057577A (zh) * | 2019-04-23 | 2019-07-26 | 重庆房地产职业学院 | 一种离合器操纵手柄行程测试的实验夹具及测试方法 |
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- 2004-01-16 EP EP04702828A patent/EP1593869A1/en not_active Withdrawn
- 2004-01-16 CN CNA2004800026788A patent/CN1742168A/zh not_active Withdrawn
- 2004-01-16 JP JP2005508052A patent/JPWO2004065812A1/ja active Pending
- 2004-01-16 WO PCT/JP2004/000302 patent/WO2004065812A1/ja not_active Application Discontinuation
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008081055A (ja) * | 2006-09-28 | 2008-04-10 | Honda Motor Co Ltd | クラッチ装置 |
JP2010215085A (ja) * | 2009-03-16 | 2010-09-30 | Honda Motor Co Ltd | 車両用電子クラッチ制御装置 |
JP2011011659A (ja) * | 2009-07-02 | 2011-01-20 | Honda Motor Co Ltd | ブレーキ装置 |
WO2019032674A1 (en) * | 2017-08-08 | 2019-02-14 | Alivel Infinity Llc | APPARATUS FOR ASSISTING ELECTRONIC CLUTCH |
US11021205B2 (en) | 2017-08-08 | 2021-06-01 | Alive! Infinity LLC | Electronic clutch assist apparatus |
JP2019183967A (ja) * | 2018-04-10 | 2019-10-24 | 株式会社シマノ | 人力駆動車の回転装置 |
JP7210154B2 (ja) | 2018-04-10 | 2023-01-23 | 株式会社シマノ | 人力駆動車の回転装置 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2004065812A1 (ja) | 2006-05-18 |
CN1742168A (zh) | 2006-03-01 |
EP1593869A1 (en) | 2005-11-09 |
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