EP4116795A1 - Clutch operation effort reactive force generator - Google Patents
Clutch operation effort reactive force generator Download PDFInfo
- Publication number
- EP4116795A1 EP4116795A1 EP22174238.0A EP22174238A EP4116795A1 EP 4116795 A1 EP4116795 A1 EP 4116795A1 EP 22174238 A EP22174238 A EP 22174238A EP 4116795 A1 EP4116795 A1 EP 4116795A1
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- European Patent Office
- Prior art keywords
- cam
- cam plate
- reactive force
- movement
- force generator
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- 230000033001 locomotion Effects 0.000 claims abstract description 69
- 239000000463 material Substances 0.000 claims description 5
- 239000011347 resin Substances 0.000 claims description 4
- 229920005989 resin Polymers 0.000 claims description 4
- 238000009434 installation Methods 0.000 abstract description 6
- 230000000994 depressogenic effect Effects 0.000 description 17
- 230000005540 biological transmission Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 6
- 230000003247 decreasing effect Effects 0.000 description 6
- 230000000284 resting effect Effects 0.000 description 6
- 230000007246 mechanism Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
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Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
- G05G1/00—Controlling members, e.g. knobs or handles; Assemblies or arrangements thereof; Indicating position of controlling members
- G05G1/30—Controlling members actuated by foot
- G05G1/46—Means, e.g. links, for connecting the pedal to the controlled unit
Definitions
- a vertical, longitudinal, and lateral directions are based on the orientation of the clutch operation effort reactive force generator installed in a vehicle, such as an automobile.
- the vertical, longitudinal, and lateral directions will also be referred to as a height-wise direction, a front-back direction, and a width-wise direction, respectively.
- the actuator operates or drives the clutch device as a function of the position of the clutch pedal 4 depressed by the driver of the vehicle 1.
- the clutch pedal 4 is mechanically connected to the clutch device.
- the supporting member 10 includes the front bottom wall 10A, the front left side wall 10B, the front right side wall 10C, the rear left side wall 10D, and the rear right side wall 10E.
- the front bottom wall 10A extends in the longitudinal direction of the vehicle 1.
- the front left side wall 10B extends upward from a left end of front bottom wall 10A.
- the front right wall 10C extends upward from a right end of the front bottom wall 10A.
- the rear left side wall 10D extends rearward from a rear end of the front left side wall 10B.
- the rear eight side wall 10E extends rearward from a rear end of the front right side wall 10C.
- the rear surface 10r of the panel attachment 10F is, as clearly illustrated in Fig. 1 , placed in direct contact with the front surface 2f of the dashboard panel 2.
- the rear surface 10r is firmly fastened to the dashboard panel 2 using a plurality of bolts 6 (only one is shown in Fig. 2 ), thereby securing the supporting member 10 to the dashboard panel 2.
- the supporting member 10 as can be seen in Figs. 2 and 3 , has the upper wall 10G.
- the upper wall 10G connects between upper ends of the front left side wall 10B and the front right side wall 10C and extends substantially vertical at an inclined angle relative to the direction A in which the cam plate 13, which will be described later in detail, is moved.
- the cam plate 13a has the joint groove 13a formed therein.
- the joint groove 13a has a font end of the rod 14 joined thereto.
- the pedal bracket 3 is, as can be seen in Fig. 1 , equipped with the rod support 3A to which the rear end of the rod 14 is joined.
- the cam plate 13 has the cam face 13A formed on an upper surface thereof.
- the roller 16B is placed in contact with the cam face 13A.
- the friction member 19 is inclined relative to the direction in which the cam plate 13 moves. Specifically, the friction member 19 is obliquely oriented to have the upper end 19b facing the cam plate 13 in the direction A of movement of the cam plate 13 and the lower end 19c facing away from the cam plate 13 in the direction A of movement of the cam plate 13.
- the friction member 19 is held from moving in a direction of inclination of the upper wall 10G.
- the friction member 19 frictionally contacts the cam follower 16.
- the friction member 19 will also be referred to below as a second friction member.
- the clutch operation effort reactive force generator 5 in this embodiment has the cam face 13A shaped to have the convex cam face 13c which extends from the front end 13f of the cam plate 13 facing the cam follower 16 toward the rear end 13r and protrudes gradually in a direction perpendicular to the direction A of movement of the cam plate 13.
- the clutch operation effort reactive force generator 5 works to produce the reactive force which gradually increases in the early half or first half (i.e., W1 in Fig. 5 ) from start of depression of the clutch pedal 4 to approximately half of the total amount by which the clutch pedal 4 is depressed (i.e., total amount of stroke of the clutch pedal 4), and also produce the reactive force which gradually decreases in the last half or second half (i.e., W2 to W3 in Fig. 5 ) of the depression of the clutch pedal 4.
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- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
- Mechanical Control Devices (AREA)
Abstract
Description
- The present invention generally relates to a clutch operation effort reactive force generator.
- Vehicles are known which are designed to engage or disengage a clutch using an actuator, for example, in a MT (i.e., Manual Transmission) employing a clutch-by-wire system.
- The use of an actuator to operate the clutch will lead to difficulty for a vehicle operator to sense a reactive force which is usually generated as a function of a degree of effort exerted by a vehicle operator directly on a clutch pedal. It is, therefore, necessary to develop the reactive force as a function of the operator's effort on the clutch pedal.
- Pedal actuating mechanism are known which work to generate a simulated reactive force opposing the degree of effort on a clutch pedal using a mechanical spring (see
JP 1996-161069 A - The pedal actuating mechanism, as taught in
JP 1996-161069 A - The pedal actuating mechanism is also equipped with a biasing stopper working to stop exerting an opposing pressure, as produced by the spring, on the actuating pedal when the actuating pedal is depressed and moved over a preset intermediate position.
- PATENT LITERATURE 1:
JP 1996-161069 A - The above type of pedal actuating mechanism, however, has a risk that the biasing stopper may require an undesirable additional installation space.
- The present invention was made in view of the above problem. It is an object of the invention to provide a clutch operation effort reactive force generator which develops a simulated reactive force as a function of the degree of effort exerted by a vehicle operator on a clutch pedal.
- The present invention is to provide a clutch operation effort reactive force generator which works to produce a reactive force as a function of an amount by which a clutch pedal is operated by an operator. The clutch operation effort reactive force generator comprises: (a) a supporting member; (b) a cam follower which includes a cam plate and a contacting portion, the cam plate having a cam face and being disposed to be movable on the supporting member, the contacting portion being arranged to make contact with the cam face; and (c) a biasing member which is arranged between the cam follower and the cam plate and works to produce a biasing force to urge the cam follower and the cam plate away from each other in a direction of movement of the cam plate. The movement of the cam plate causes a location of the contact between the contacting portion and the cam face to be changed to move the cam follower in the direction of movement of the cam plate.
- The above structure enables the clutch operation effort reactive force generator to be reduced in size thereof, minimizes the volume of space for installation of the clutch operation effort reactive force generator, and is capable of developing a simulated reactive force as a function of an amount by which the clutch pedal is moved by the operator.
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Fig. 1 is a cross sectional view which illustrates a clutch operation effort reactive force generator according to an embodiment of the invention which is attached to a dashboard panel. -
Fig. 2 is a perspective view which illustrates a clutch operation effort reactive force generator according to an embodiment of the invention. -
Fig. 3 is a left side view of a clutch operation effort reactive force generator according to an embodiment of the invention. -
Fig. 4 is a longitudinal sectional view of a cam plate installed in a clutch operation effort reactive force generator according to an embodiment of the invention. -
Fig. 5 is a view which represents a relation of a reactive force to an amount of stroke of a clutch pedal between depression and release of the clutch pedal in a clutch operation effort reactive force generator according to an embodiment of the invention. - A clutch operation effort reactive force generator according to an embodiment of the invention is designed to produce a reactive force as a function of an amount by which a clutch pedal is operated by an operator. The clutch operation effort reactive force generator comprises: (a) a supporting member; (b) a cam follower which includes a cam plate and a contacting portion, the cam plate having a cam face and being disposed to be movable on the supporting member, the contacting portion being arranged to make contact with the cam face; and (c) a biasing member which is arranged between the cam follower and the cam plate and works to produce a biasing force to urge the cam follower and the cam plate away from each other in a direction of movement of the cam plate. The movement of the cam plate causes a location of the contact between the contacting portion and the cam face to be changed to move the cam follower in the direction of movement of the cam plate.
- The above structure enables the clutch operation effort reactive force generator to be reduced in size thereof, minimizes the volume of space for installation of the clutch operation effort reactive force generator, and is capable of developing a simulated reactive force as a function of an amount by which the clutch pedal is moved by the operator.
- A clutch operation effort reactive force generator according to an embodiment of the invention will be described below with reference to the drawings.
Figs. 1 to 5 are views which illustrates the clutch operation effort reactive force generator in the embodiment. - In
Figs. 1 to 4 , a vertical, longitudinal, and lateral directions are based on the orientation of the clutch operation effort reactive force generator installed in a vehicle, such as an automobile. The vertical, longitudinal, and lateral directions will also be referred to as a height-wise direction, a front-back direction, and a width-wise direction, respectively. - The structure will first be described. In
Fig. 1 , the vehicle 1 is equipped with thedashboard panel 2. Theengine compartment 2A in which an engine or a transmission, not shown, are mounted is arranged in front of thedashboard panel 2. Thepassenger compartment 2B occupied by a driver and passengers is located in back of thedashboard panel 2. - The
pedal bracket 3 is mounted on thedashboard panel 2. Thepedal bracket 3 has disposed thereon theclutch pedal 4 which is swingable in the longitudinal direction of the vehicle 1. - The transmission in this embodiment is implemented by a MT (Manual Transmission) and works to engage or disengage a clutch device, not shown, using an actuator.
- The actuator operates or drives the clutch device as a function of the position of the
clutch pedal 4 depressed by the driver of the vehicle 1. Theclutch pedal 4 is mechanically connected to the clutch device. - The vehicle 1 is equipped with the clutch operation effort
reactive force generator 5. The clutch operation effortreactive force generator 5 works to produce an imitation of a reactive force, in other words, a counterforce which is expected to be actually developed as a function of the amount by which theclutch pedal 4 is operated or depressed by the driver of the vehicle 1 (i.e., pedal-exerted load). - Referring to
Figs. 2 and3 , the clutch operation effortreactive force generator 5 includes the supportingmember 10. The supportingmember 10 is secured to thedashboard panel 2. Specifically, thedashboard panel 2 has formed therein a through-hole, not shown, through which the supportingmember 10 passes to have a front portion disposed inside theengine compartment 2A and a rear portion disposed inside thepassenger compartment 2B. - The supporting
member 10 includes thefront bottom wall 10A, the frontleft side wall 10B, the frontright side wall 10C, the rearleft side wall 10D, and the rearright side wall 10E. Thefront bottom wall 10A extends in the longitudinal direction of the vehicle 1. The frontleft side wall 10B extends upward from a left end offront bottom wall 10A. The frontright wall 10C extends upward from a right end of thefront bottom wall 10A. The rearleft side wall 10D extends rearward from a rear end of the frontleft side wall 10B. The rear eightside wall 10E extends rearward from a rear end of the frontright side wall 10C. - The front
left side wall 10B and the frontright side wall 10C face each other in the lateral direction (i.e., the width-wise direction of the vehicle 1) and are shaped to be bilaterally symmetrical. The rearleft side wall 10D and the rearright side wall 10E face each other in the lateral direction and are shaped to be bilaterally symmetrical. - Although not illustrated, the rear
right side wall 10E is located on the right side of the rearleft side wall 10D, in other words, behind the rearleft side wall 10D, as viewed inFig. 3 . - The supporting
member 10 is, as illustrated inFig. 2 , equipped with thepanel attachment 10F. Thepanel attachment 10F is arranged on connections between the rear ends of the frontleft side wall 10B and the frontright side wall 10C and the front ends of the rearleft side wall 10D and the rearright side wall 10E. - Specifically, the supporting
member 10 has the frontleft side wall 10B and the frontright side wall 10C arranged in front of thepanel attachment 10F and also has the rearleft side wall 10D and the rearright side wall 10E in back of thepanel attachment 10F. - The
panel attachment 10F has formed therein the through-hole 10h extending through a thickness of thepanel attachment 10F. Thecoil spring 17 functioning as a biasing member, as will be described later in detail, extends through the through-hole 10h. - The
rear surface 10r of thepanel attachment 10F is, as clearly illustrated inFig. 1 , placed in direct contact with thefront surface 2f of thedashboard panel 2. Therear surface 10r is firmly fastened to thedashboard panel 2 using a plurality of bolts 6 (only one is shown inFig. 2 ), thereby securing the supportingmember 10 to thedashboard panel 2. - The supporting
member 10, as can be seen inFigs. 2 and3 , has theupper wall 10G. Theupper wall 10G connects between upper ends of the frontleft side wall 10B and the frontright side wall 10C and extends substantially vertical at an inclined angle relative to the direction A in which thecam plate 13, which will be described later in detail, is moved. - Specifically, the
upper wall 10G is obliquely inclined relative to the direction A of the movement of thecam plate 13, in other words, extends forward from an upper end thereof obliquely downward to a lower end thereof. - The
cam plate 13 is, as clearly illustrated inFig. 4 , disposed in the supportingmember 10. Thecam plate 13 is movable in the longitudinal direction relative to the supportingmember 10. - The
cam plate 13a has thejoint groove 13a formed therein. Thejoint groove 13a has a font end of therod 14 joined thereto. Thepedal bracket 3 is, as can be seen inFig. 1 , equipped with therod support 3A to which the rear end of therod 14 is joined. - With the above arrangements, swing motion of the
clutch pedal 4 relative to thepedal bracket 3 in the longitudinal direction causes thecam plate 13 to be moved with the aid of therod 14. - Specifically, the
cam plate 13 is moved or thrust forward by therod 14 upon depression of theclutch pedal 4. When the depression of theclutch pedal 4 is released, theclutch pedal 4 is drawn by therod 14 backward, so that it is returned back to a resting position thereof. - The
cam plate 13 formed therein theelongated hole 13b extending in the longitudinal direction. Thepin 15 is disposed in theelongated hole 13b. Thepin 15 has a left end and a right end joined to the rearleft side wall 10D and the rearright side wall 10E, respectively. - The
elongated hole 13b is shaped to have a vertical dimension which is slightly larger than the diameter of thepin 15, thereby ensuring the stability in longitudinal smooth movement of thecam plate 13 relative to the supportingmember 10 without oscillating in the vertical direction. - The supporting
member 10 is equipped with thecam follower 16. Thecam follower 16 is movable along theupper wall 10G. - The
cam follower 16 includes thecam follower body 16A, theroller shaft 16a firmly secured to thecam follower body 16A, and theroller 16B retained by theroller shaft 16a to be rotatable. Theroller 16B works as a rotating member and will also be referred to below as a contacting portion. - The
cam plate 13 has the cam face 13A formed on an upper surface thereof. Theroller 16B is placed in contact with thecam face 13A. - The cam face 13A extends substantially in the direction A of movement of the
cam plate 13. The direction A is identical with the longitudinal direction of the vehicle 1. The direction A of movement of thecam plate 13 is also identical with a direction in which theaxis line 14a of therod 14 extends. - The cam face 13A includes the
convex cam face 13c. Thecam plate 13 has a length with thefront end 13f and therear end 13r which are opposed to each other in the direction A of movement of thecam plate 13. Thefront end 13f is located closer to thecam follower 16 than therear end 13r is. Theconvex cam surface 13c extends from thefront end 13f toward therear end 13r and gradually protrudes in a direction perpendicular to the direction A of movement of thecam plate 13. - The cam face 13A also includes the first S-shaped
cam face 13d and the second S-shapedcam face 13e. The first S-shapedcam face 13d extends from the top 13t of theconvex cam face 13c toward therear end 13r of thecam plate 13 and is gently curved downward from the top 13t in a direction substantially perpendicular to the direction A of movement of thecam plate 13. The second S-shapedcam face 13e extends from the lowest point or bottom 13p of the first S-shapedcam face 13d toward therear end 13r of thecam plate 13 and is gently curved upward from the bottom 13p in a direction perpendicular to the direction A of movement of thecam plate 13. A combination of the first S-shapedcam face 13d and the second S-shapedcam face 13e will also be referred to below as a concave cam face which is recessed gradually in a direction (i.e., inward direction) perpendicular to the direction A. - The
front end 13f of thecam plate 13 will also be referred to below as a first end of thecam plate 13, while therear end 13r will also be referred to below as a second end of thecam plate 13 opposed to the first end in a direction of movement of thecam plate 13. - When the
clutch pedal 4 is not depressed, so that it is located at an initial or resting position (i.e., a fully engaged clutch position), theroller 16B is located to be lower than the top 13t of theconvex cam face 13c and higher than the bottom 13p of the first S-shapedcam face 13d. The bottom 13p is the deepest portion of the first S-shapedcam face 13d. - The longitudinal movement of the
cam plate 13 upon depression of theclutch pedal 4 causes a location of contact between theroller 16B and the cam face 13A to change. - The
coil spring 17 is disposed between thecam follower 16 and thecam plate 13. Thecoil spring 17 has a front end placed in contact with thecam follower body 16A and a rear end placed in contact with the spring-bearingportion 13B provided on a rear end portion of thecam plate 13. - The
coil spring 17 is made of a double-coil spring including theouter coil spring 17A and theinner coil spring 17B disposed inside theouter coil spring 17A. - The
coil spring 17 produces a biasing pressure to urge thecam follower 16 and thecam plate 13 away from each other in the direction A of movement of thecam plate 13. - The clutch operation effort
reactive force generator 5 works to change an amount by which thecoil spring 17 is compressed as a function of a location of contact of theroller 16B with thecam face 13A during longitudinal movement of thecam plate 13 when theclutch pedal 4 is being depressed or released back to the resting position, thereby developing a simulated reactive force opposing the movement of theclutch pedal 4 and exerting it on theclutch pedal 4. - The supporting
member 10 includes theresinous friction members friction member 18 is disposed between thefront bottom wall 10A of the supportingmember 10 and thecam plate 13. - The
friction member 18 has thefitting protrusions 18a formed on a surface thereof which faces thefront bottom wall 10A of thefriction member 18. Thefront bottom wall 10A has formed therein thefitting grooves 10a in which thefitting protrusions 18a are fit. - With the above arrangements, the
friction member 18 is held from moving in the longitudinal direction in which thefront bottom wall 10A extends. Thefriction member 18 frictionally contacts thecam plate 13 when thecam plate 13 is moved in the longitudinal direction. Thefriction member 18 will also be referred to below as a first friction member. - The
friction member 19 is disposed between theupper wall 10G of the supportingmember 10 and thecam follower body 16A. - The
friction member 19 is inclined relative to the direction in which thecam plate 13 moves. Specifically, thefriction member 19 is obliquely oriented to have theupper end 19b facing thecam plate 13 in the direction A of movement of thecam plate 13 and thelower end 19c facing away from thecam plate 13 in the direction A of movement of thecam plate 13. - The
friction member 19 has thefitting protrusions 19a formed on a surface thereof which faces theupper wall 10G. Theupper wall 10G has formed in an inner wall thereof thefitting grooves 19b in which thefitting protrusions 19a are fit. - With the above arrangements, the
friction member 19 is held from moving in a direction of inclination of theupper wall 10G. When thecam follower 16 moves in the direction of inclination, thefriction member 19 frictionally contacts thecam follower 16. Thefriction member 19 will also be referred to below as a second friction member. - The
cover member 20 is arranged in front of the supportingmember 10. Thecover member 20 is, as clearly illustrated inFig. 1 , arranged away from thedashboard panel 2 within theengine compartment 2A and covers the supportingmember 10 from outside it. - The vehicle 1 is equipped with a position sensor, not shown, which detects a position of the
clutch pedal 4, in other words, an amount by which theclutch pedal 4 is operated. The position sensor works to detect a depressed position of theclutch pedal 4, i.e., an amount by which thecam plate 13 is moved and output a signal indicative thereof to a controller, not shown. - The controller analyzes the output from the position sensor to control an operation of the actuator to engage or disengage the clutch device.
- The operation of the clutch operation effort
reactive force generator 5 will be described below. - When the driver of the vehicle 1 does not depress the
clutch pedal 4, the clutch device is engaged. Theroller 16B of thecam follower 16 is riding on a portion of thecam face 13A of thecam plate 13 which is close to thefront end 13f. - When the driver is depressed from the resting position to disengage the clutch device, it causes the
cam plate 13 to be moved forward by therod 14 in frictional contact with thefriction member 18, thereby compressing thecoil spring 17. - The forward movement of the
cam plate 13 causes theroller 16B to rotate on theconvex cam face 13c of thecam face 13A, so that thecam follower 16 is moved obliquely upward in the rearward direction. Simultaneously, thecam follower body 16A moves toward therod 14 in the direction A of movement of thecam plate 13 in frictional contact with thefriction member 19 - When the
cam plate 13 is further moved forward, so that theroller 16B rides on the top 13t of theconvex cam face 13c, it causes thecam follower 16 to be located closest to therod 14 in the direction A of movement of thecam plate 13. In other words, the distance between thelower end 19c of thefriction member 19 of the supportingmember 10 and thecam follower 16 is maximized in the direction A of movement of thecam plate 13. - Consequently, the movement of the
roller 16B from a portion of thecam face 13A close to thefront end 13f of thecam plate 13 until theroller 16B arrives at or contacts the top 13t of theconvex cam face 13c causes an amount by which thecoil spring 17 is compressed to be increased by the distance thecam follower 16 travels toward therod 14. - When the
roller 16B is moving along theconvex cam face 13c, a reactive force which is produced by thecoil spring 17 and, as demonstrated by W1 inFig. 5 , gradually increased in level as a function of the amount by which theclutch pedal 4 is depressed, i.e., an amount of stroke of theclutch pedal 4 is applied to theclutch pedal 4 as a counter pressure. - When the
cam plate 13 is further moved forward, theroller 16B travels from the top 13t of theconvex cam face 13c to the bottom 13p of the first S-shapedcam face 13d in contact with the first S-shapedcam face 13d, in other words, theroller 16B moves downward along the first S-shapedcam face 13d. - When the
roller 16B moves along the first S-shapedcam face 13d, it causes thecam follower 16 to move obliquely downward, forward along thefriction member 19 away from therod 14 in the direction A of movement of thecam plate 13, thereby decreasing the amount by which thecoil spring 17 is compressed. - Consequently, a reactive force which is produced by the
coil spring 17 and, as demonstrated by W2 inFig. 5 , gradually decreased in level as a function of the amount by which theclutch pedal 4 is depressed, i.e., an amount of stroke of theclutch pedal 4 is applied to theclutch pedal 4 as a counter pressure. - When the
cam plate 13 is further moved forward, theroller 16B travels upward from the bottom 13p of the first S-shapedcam face 13d in contact with the second S-shapedcam face 13e, thereby causing thecam follower 16 to move obliquely upward, rearward toward therod 14 in the direction A of movement of thecam plate 13, thereby increasing the amount by which thecoil spring 17 is compressed. - Consequently, a reactive force which is produced by the
coil spring 17 and, as demonstrated by W3 inFig. 5 , gradually increased in level as a function of the amount by which theclutch pedal 4 is depressed, i.e., an amount of stroke of theclutch pedal 4 is applied to theclutch pedal 4 as a counter pressure. - After the
clutch pedal 4 is depressed until the clutch device is disengaged, and then a shift operation of the transmission is been completed, the release of theclutch pedal 4 will cause the pressure exerted by the driver on theclutch pedal 4 to be lower than that applied to theclutch pedal 4 during the depression of theclutch pedal 4. - The release of the
clutch pedal 4 causes thecam plate 13 to be urged by thecoil spring 17, so that it is moved backward along with therod 14. - When the
cam plate 13 is urged by thecoil spring 17 backward, it causes theroller 16B to move from the first S-shapedcam face 13d to theconvex cam face 13c in contact therewith. Thecam follower 16 is, therefore, moved in the direction A of movement of thecam plate 13 with a change in location of contact of theroller 16B with the first S-shapedcam face 13d or theconvex cam face 13c. - The above movement of the
cam follower 16 regulates the amount of compression of thecoil spring 17, which develops a mechanical pressure as a function of the amount of compression of thecoil spring 17 and exerts it to theclutch pedal 4 as a simulated counter force. - When the
clutch pedal 4 is being returned back to the resting position, a reactive force which is, as can be seen inFig. 5 , lower in level than that developed when theclutch pedal 4 is being depressed is exerted on theclutch pedal 4. - Specifically, when the
clutch pedal 4 is depressed, friction which resists the depression of theclutch pedal 4 is developed between thefriction member 18 and thecam plate 13 and between thefriction member 19 and thecam follower 16. The degree of such friction is increased with an increase in amount of compression of thecoil spring 17. - Alternatively, when the
clutch pedal 4 is released, so that it is returned back to the resting position, friction which resists the backward movement of theclutch pedal 4, in other words, which is oriented opposite the direction in which theclutch pedal 4 is depressed is developed between thefriction member 18 and thecam plate 13 and between thefriction member 19 and thecam follower 16. The degree of such friction is decreased with a decrease in amount by which thecoil spring 17 is compressed. - The degree of effort exerted on the
clutch pedal 4 when theclutch pedal 4 is released by the driver of the vehicle 1 is usually lower than that when theclutch pedal 4 is depressed by the driver, thus, as represented inFig. 5 , resulting in hysteresis of the reactive force acting on theclutch pedal 4. - The above hysteresis causes the clutch operation effort
reactive force generator 5 to produce a higher degree of reactive force during the depression of theclutch pedal 4 and a lower degree of reactive force during the release of theclutch pedal 4. - The clutch operation effort
reactive force generator 5 in this embodiment is, as described above, equipped with the supportingmember 10, the cam face 13A, thecam plate 13 which is arranged in the supportingmember 10 to be movable, and thecam follower 16 which is movable in the supporting member. Thecam follower 16 is equipped with theroller 16B which is arranged in contact with thecam face 13A. - The clutch operation effort
reactive force generator 5 is also equipped with thecoil spring 17 which is disposed between thecam follower 16 and thecam plate 13 and generates a biasing force which urges thecam follower 16 and thecam plate 13 away from each other in the direction A in which thecam plate 13 is moved. The movement of thecam plate 13 results in a change in location of contact between theroller 16B and the cam face 13A to move thecam follower 16 in the direction A of the movement of thecam plate 13. - Accordingly, when the
clutch pedal 4 is operated, the clutch operation effortreactive force generator 5 works to change the amount by which thecoil spring 17 is compressed as a function of the distance by which thecam plate 13, i.e., thecam follower 16 is moved and apply, to theclutch pedal 4, a reactive force which resists the operation of theclutch pedal 4 and is developed as a function of the amount of the compression of thecoil spring 17. - The configuration of the
cam face 13A of thecam plate 13 may be changed to control the distance by which thecam follower 16 moves in the direction A of movement of thecam plate 13, thereby regulating the degree of reactive force produced by thecoil spring 17 to a desired level. - As apparent from the above discussion, the clutch operation effort
reactive force generator 5 is capable of creating a simulated reactive force as a function of the amount by which theclutch pedal 4 is operated by the driver of the vehicle 1 and providing the driver with a comfortable feeling of operation of theclutch pedal 4. - The
cam plate 13 is shaped to have thecam face 13A. Thecam follower 16 is equipped with theroller 16B riding directly on thecam face 13A. This eliminates the need for an additional biasing mechanism required in the prior art structure, thereby enabling the clutch operation effortreactive force generator 5 to be reduced in size thereof, which leads to a decreased volume of space for installation of the clutch operation effortreactive force generator 5. - The supporting
member 10, thecam plate 13, thecam follower 16, and thecoil spring 17 constitute the clutch operation effortreactive force generator 5, thereby simplifying the structure of the clutch operation effortreactive force generator 5. Theclutch pedal 4 is joined to thecam plate 13 through therod 14, thereby facilitating transmission of the simulated reactive force from the clutch operation effortreactive force generator 5 to theclutch pedal 4. - The above arrangements eliminate the need for designing the
clutch pedal 4 especially for the clutch operation effortreactive force generator 5 or shaping thedashboard panel 2 especially for the clutch operation effortreactive force generator 5, which minimizes the cost for production of the vehicle 1. - The clutch operation effort
reactive force generator 5 in this embodiment has thecam face 13A shaped to have theconvex cam face 13c which extends from thefront end 13f of thecam plate 13 facing thecam follower 16 toward therear end 13r and protrudes gradually in a direction perpendicular to the direction A of movement of thecam plate 13. - The cam face 13A also has the first S-shaped
cam face 13d which extends from the top 13t of theconvex cam face 13c toward therear end 13r of thecam plate 13 and is curved gently downward from the top 13t in a direction perpendicular to the direction A of movement of thecam plate 13. - With the above arrangements, the
roller 16B makes contact with theconvex cam face 13c upon start of depression of theclutch pedal 4, thereby producing the reactive force whose level, as demonstrated inFig. 5 , increases gradually. - The
roller 16B is also moved from theconvex cam face 13c to the first S-shapedcam face 13d in contact therewith, thereby gradually decreasing the degree of reactive force acting on theclutch pedal 4. - Accordingly, the clutch operation effort
reactive force generator 5 works to produce the reactive force which gradually increases in the early half or first half (i.e., W1 inFig. 5 ) from start of depression of theclutch pedal 4 to approximately half of the total amount by which theclutch pedal 4 is depressed (i.e., total amount of stroke of the clutch pedal 4), and also produce the reactive force which gradually decreases in the last half or second half (i.e., W2 to W3 inFig. 5 ) of the depression of theclutch pedal 4. - The driver of the vehicle 1, therefore, feels a strong resistance to the movement of the
clutch pedal 4 in the first half of the depression of theclutch pedal 4 and then feels a decreased degree of resistance to the movement of theclutch pedal 4 in the second half of the depression of theclutch pedal 4. - When the
clutch pedal 4 is released, the clutch operation effortreactive force generator 5 also works to produce a first level of reactive force in the first half of the release of theclutch pedal 4. The first level of reactive force is lower than that during the second half of the depression of theclutch pedal 4. The enables the driver of the vehicle 1 to physically feel the sense of release of theclutch pedal 4. - The clutch operation effort
reactive force generator 5 in this embodiment also has the supportingmember 10 equipped with thefriction member 18 and thefriction member 19. - The
friction member 18 is disposed between the supportingmember 10 and thecam plate 13 and makes frictional contact with thecam plate 13 during movement of thecam plate 13. - The
friction member 19 is arranged between the supportingmember 10 and thecam follower 16 and makes frictional contact with thecam follower 16 during movement of thecam follower 16. - The frictional contact between the
friction member 18 and thecam plate 13 and between thefriction member 19 and thecam follower 16 results in hysteresis of the reactive force acting on theclutch pedal 4 between the depression and the release of theclutch pedal 4. - The clutch operation effort
reactive force generator 5 in this embodiment has thefriction member 19 inclined relative to the direction A of movement of thecam plate 13 to have theupper end 19b facing thecam plate 13 and thelower end 19c facing away from thecam plate 13. - With the above arrangements, when the
roller 16B of thecam follower 16 slides on theconvex cam face 13c and the first S-shapedcam face 13d, it causes thecam follower 16 to be moved upward along theupper wall 10G and simultaneously travel in the direction A of movement of thecam plate 13. - The upward movement of the
cam follower 16 results in inclination of thecoil spring 17 relative to the direction A of movement of thecam plate 13. The inclination of thecoil spring 17 during the movement of thecam plate 13 may, however, be minimized by increasing the inclination of thefriction member 19 relative to the direction A of movement of thecam plate 13, thereby achieving a smooth movement of theclutch pedal 4 and ensuring the durability of thecoil spring 17. - The inclination of the
friction member 19 relative to the direction A of movement of thecam plate 13 also avoids an increase in dimension of the supportingmember 10 in a direction perpendicular to the direction A of movement of thecam plate 13, thereby enabling the clutch operation effortreactive force generator 5 to be reduced in size thereof. - The inclination of the
friction member 19 relative to the direction A of movement of thecam plate 13 also results in an increased level of pressure acting on a surface-to-surface contact between thecam follower 16 and thefriction member 19, thereby increasing the hysteresis of the reactive force between the depression and release of theclutch pedal 4. - The development of the hysteresis between the depression and release of the
clutch pedal 4 requires increasing the pressure exerted on surface-to-surface contacts between thefriction member 18 and thecam plate 13 and between thefriction member 19 and thecam follower 16 and also achieving frictional sliding motion of thecam plate 13 and thecam follower 16 on thefriction members - However, in case of use of metal as material of the
friction members friction member 18 and thecam plate 13 and between thefriction member 19 and thecam follower 16 will result in mechanical wear thereof due to roughness of the surfaces of thefriction members cam plate 13 and thecam follower 16 during movement thereof. - The clutch operation effort
reactive force generator 5 in this embodiment has thefriction member 18 and thefriction member 19 made from resin material. - The resin material usually has a smooth or slick surface, is excellent in wear resistance, and has an even coefficient of friction. The use of resin material, thus, minimizes the mechanical wear of the surfaces of the
friction members 18 contacting thecam plate 13 and thecam follower 16, respectively, as compared with metallic material. - It is, therefore, possible to keep the reactive force resisting the operation of the
clutch pedal 4 at a constant level, which provides the stability for the driver to feel a suitable level of reactive force opposing the movement of theclutch pedal 4 over an extended period of time. - The clutch operation effort
reactive force generator 5 has thecam follower 16 equipped with theroller 16B arranged to be rotatable in contact with thecam face 13A. - The above structure minimizes the mechanical wear of the
cam face 13A of thecam plate 13, thereby improving the durability of thecam plate 13 and keeping the level of the reactive force resisting the movement of theclutch pedal 4 at a constant level. This enables the driver of the vehicle 1 to feel a suitable level of the reactive force for a long period of time. - The clutch operation effort
reactive force generator 5 has thecam plate 13 connected to theclutch pedal 4 through therod 14, but however, thecam plate 13 may alternatively be joined directly to theclutch pedal 4. - While the present invention has been disclosed in terms of the preferred embodiment in order to facilitate better understanding thereof, it should be appreciated that the invention can be embodied in various ways without departing from the principle of the invention. Therefore, the invention should be understood to include all possible equivalents or modifications to the shown embodiment which can be embodied without departing from the principle of the invention as set forth in the appended claims.
Claims (6)
- A clutch operation effort reactive force generator (5) which works to produce a reactive force as a function of an amount by which a clutch pedal (4) is operated by an operator, comprising:a supporting member (10);a cam follower (16) which includes a cam plate (13) and a contacting portion (16B), the cam plate (13) having a cam face (13A) and being disposed to be movable on the supporting member (10), the contacting portion (16B) being arranged to make contact with the cam face (13A); anda biasing member (17) which is arranged between the cam follower (16) and the cam plate (13) and works to produce a biasing force to urge the cam follower (16) and the cam plate (13) away from each other in a direction of movement of the cam plate (13), characterized in thatthe movement of the cam plate (13) causes a location of the contact between the contacting portion (16B) and the cam face (13A) to be changed to move the cam follower (16) in the direction of movement of the cam plate (13).
- The clutch operation effort reactive force generator as claimed in claim 1, wherein the cam face (13A) includes a convex cam face (13c) and a concave cam face (13d, 13e), the convex cam face (13c) extending from a first end portion (13f) of the cam plate (13) which is located close to the cam follower (16) toward a second end portion (13r) of the cam plate (13) facing away from the cam follower (16) in the direction of movement of the cam plate (13), the convex cam face (13c) gradually protruding in a direction perpendicular to the direction of movement of the cam plate (13), the concave cam face (13d, 13e) extending from a top of the convex cam face (13c) toward the second end portion of the cam plate (13) in the direction of movement of the cam plate (13), the concave cam face (13d, 13e) gradually recessed in a direction perpendicular to the direction of movement of the cam plate (13).
- The clutch operation effort reactive force generator as claimed in claim 1 or 2, wherein the supporting member includes a first friction member (18) and a second friction member (19), the first friction member (18) being disposed between the supporting member (10) and the cam plate (13), the second friction member (19) being disposed between the supporting member (10) and the cam follower (16),the first friction member (18) makes frictional contact with the cam plate (13) during movement of the cam plate (13), andthe second friction member (19) makes frictional contact with the cam follower (16) during movement of the cam follower (16).
- The clutch operation effort reactive force generator as claimed in claim 3, wherein the second friction member (19) is inclined relative to the direction of movement of the cam plate (13) to have an upper end (19b) which faces the cam plate (13) in the direction of movement of the cam plate (13).
- The clutch operation effort reactive force generator as claimed in claim 3 or 4, wherein the first friction member (18) and the second friction member (19) are made from resin material.
- The clutch operation effort reactive force generator as claimed in any one of claims 1 to 5, wherein the contacting portion (16B) is made of a roller which is rotatable in contact with the cam face (13A).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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JP2021113537A JP2023009890A (en) | 2021-07-08 | 2021-07-08 | Clutch operation reaction force generator |
Publications (2)
Publication Number | Publication Date |
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EP4116795A1 true EP4116795A1 (en) | 2023-01-11 |
EP4116795B1 EP4116795B1 (en) | 2024-03-06 |
Family
ID=81749321
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP22174238.0A Active EP4116795B1 (en) | 2021-07-08 | 2022-05-19 | Clutch operation effort reactive force generator |
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EP (1) | EP4116795B1 (en) |
JP (1) | JP2023009890A (en) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2991862A (en) * | 1959-06-19 | 1961-07-11 | Int Harvester Co | Foot operated control mechanism for plurality of clutch assemblies |
JPH08161069A (en) | 1994-12-02 | 1996-06-21 | Toyota Motor Corp | Operation pedal device |
CA2296612A1 (en) * | 1999-01-20 | 2000-07-20 | Joe Talarico | A clutch actuator assembly |
US6837356B2 (en) * | 2001-02-02 | 2005-01-04 | Mannesmann Sachs Ag | Clutch release arrangement |
US20050252334A1 (en) * | 2004-05-14 | 2005-11-17 | Vadym Podkopayev | Pedal assembly |
EP3547070A1 (en) * | 2018-03-30 | 2019-10-02 | Valeo Embrayages | System for generating force for control pedal |
-
2021
- 2021-07-08 JP JP2021113537A patent/JP2023009890A/en active Pending
-
2022
- 2022-05-19 EP EP22174238.0A patent/EP4116795B1/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2991862A (en) * | 1959-06-19 | 1961-07-11 | Int Harvester Co | Foot operated control mechanism for plurality of clutch assemblies |
JPH08161069A (en) | 1994-12-02 | 1996-06-21 | Toyota Motor Corp | Operation pedal device |
CA2296612A1 (en) * | 1999-01-20 | 2000-07-20 | Joe Talarico | A clutch actuator assembly |
US6837356B2 (en) * | 2001-02-02 | 2005-01-04 | Mannesmann Sachs Ag | Clutch release arrangement |
US20050252334A1 (en) * | 2004-05-14 | 2005-11-17 | Vadym Podkopayev | Pedal assembly |
EP3547070A1 (en) * | 2018-03-30 | 2019-10-02 | Valeo Embrayages | System for generating force for control pedal |
Also Published As
Publication number | Publication date |
---|---|
JP2023009890A (en) | 2023-01-20 |
EP4116795B1 (en) | 2024-03-06 |
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