JP2015143548A - Clutch switching device and transmission equipped with same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a technique contributing to making compact a clutch switching device and a transmission equipped with the same.SOLUTION: A clutch switching device 10 switching a clutch CL by an axial movement of a slide 14 to which the rotation of a motor 18 is transmitted via a third gear mechanism 16 is configured. At a time of the axial movement of the slider 14, a gear 14c of the slider 14 and a gear 16c of the third gear mechanism 16 sliding relatively to each other are configured as helical gears, respectively. Each helical gear is inclined so that a thrust force generated in response to the engagement of the gear 14c with the gear 16c acts in an opposite direction to a slide resistance force generated between the gear 14c and the gear 16c. This can reduce an output required of the motor 18 for the axial movement of the slider 14, so that the motor 18 can be downsized. As a result, the device 10 can be made compact.

Description

  The present invention relates to a clutch switching device capable of switching a clutch between a connected state and a disconnected state.

  Conventionally, this type of clutch switching device includes a motor, a driven gear that is driven to rotate by the motor, a fixed sleeve that rotatably supports the driven gear, and a driven sleeve that is screw-engaged with the shaft portion of the driven gear. And a clutch that engages and disengages by moving the driven sleeve in the axial direction by rotating the driven gear by rotating the motor is proposed (see, for example, Patent Document 1).

  In this device, the shaft portion of the driven gear, the driven sleeve, and the fixed sleeve are arranged in a nested manner to achieve a compact device. On the other hand, the applicant proposes a configuration that can reduce the number of parts compared to the above-described configuration and can be made compact as a configuration in which the driven gear itself that is rotationally driven by the motor advances and retracts in the axial direction. (See Patent Document 2). As described above, since the clutch switching device is attached to a limited space such as a transmission, it can be considered that downsizing of the clutch switching device is one of important issues. If the device can be miniaturized, the power consumption can be reduced.

JP 2009-281570 A JP 2012-159139 A

  The present invention has been made in view of the above, and an object of the present invention is to provide a technique that contributes to the compactness of a clutch switching device and a transmission including the clutch switching device.

  The clutch switching device of the present invention and the transmission equipped with the same employ the following means in order to achieve the above-described object.

  According to a preferred embodiment of the clutch switching device according to the present invention, a clutch switching device that performs clutch switching is configured. The clutch switching device includes a motor, a gear member that is rotationally driven by the motor, a slider shaft that is fixedly provided, and a slider member. The gear member has a first gear. The slider member has a second gear that meshes with the first gear and is screw-engaged on the slider shaft. The first gear has tooth traces that are inclined with respect to the central axis of the first gear. Further, the second gear has tooth traces inclined with respect to the central axis of the second gear. And it is comprised so that a clutch may be switched by the slider member screwed back and forth on the slider shaft to an axial direction. In the present invention, “inclined with respect to the central axis” means that when the first gear and the second gear are viewed from the front with the central axes of the first gear and the second gear oriented in the vertical direction, A mode in which the tooth trace is inclined to the right or to the left corresponds to this.

  According to the present invention, since the tooth traces of the first gear of the gear member and the second gear of the slider member are inclined with respect to the central axis, the first gear and the second gear are engaged with each other. Thrust force is generated. The thrust force assists the axial movement of the slider member on the slider shaft toward the clutch side and the axial movement toward the side away from the clutch. Thereby, the output of the motor required for moving the slider member in the axial direction can be reduced, and the motor can be miniaturized. As a result, the clutch switching device can be made compact. Furthermore, since the meshing rate is improved compared to the case where the tooth traces of the first gear and the second gear are parallel to the central axis, that is, configured as a spur gear, gear noise can be improved.

  According to the further form of the clutch switching device according to the present invention, the second gear is configured to slide relative to the first gear when the slider member moves in the axial direction. The inclination of the tooth traces in the first gear and the second gear is such that the thrust force generated when the first gear and the second gear mesh with each other is the sliding resistance force generated between the first gear and the second gear. It is configured to act in the opposite direction.

  When the slider member is configured to move in the axial direction, the tooth surface of the second gear provided on the slider member slides against the tooth surface of the first gear provided on the gear member. The driving force required to move the slider member in the axial direction is increased by the sliding resistance force. However, according to the present embodiment, the thrust force generated when the first gear and the second gear mesh with each other acts in the opposite direction to the sliding resistance force generated between the first gear and the second gear. Therefore, an increase in driving force necessary to move the slider member in the axial direction can be suppressed. As a result, the motor can be reduced in size. In addition, it is preferable that the inclination angle of the tooth traces of the first gear and the second gear is in the range of 0 ° to 10 ° with respect to the central axis.

  According to the further form of the clutch switching device according to the present invention, the inclination of the tooth trace in the first gear and the second gear is set to an angle capable of generating a thrust force capable of canceling the sliding resistance force. Yes.

  According to this embodiment, the slider member is configured to cancel the sliding resistance force generated between the first gear and the second gear by the thrust force generated when the first gear and the second gear mesh with each other. It is possible to further suppress an increase in driving force necessary for moving the shaft in the axial direction. As a result, the motor can be further downsized.

  According to the further form of the clutch switching apparatus which concerns on this invention, the urging | biasing member urged | biased in the direction which connects a clutch or the direction which cancels | releases connection of a clutch is provided. The inclination of the tooth traces of the first gear and the second gear is set to an angle that can generate a thrust force that can cancel at least a part of the urging force of the urging member. The “biasing member” in the present invention typically corresponds to a diaphragm spring.

  According to this embodiment, since the thrust force generated by the meshing of the first gear and the second gear cancels at least a part of the urging force of the urging member, it is necessary to move the slider member in the axial direction. The increase in driving force can be further suppressed. As a result, the motor can be further reduced in size.

  According to the further form of the clutch switching device according to the present invention, the third gear that can rotate integrally with the rotating shaft is fixed to the rotating shaft of the motor. The gear member includes a fourth gear that meshes with the third gear, and a support shaft that supports the first gear and the fourth gear so as to be integrally rotatable. The “gear ratio” in the present invention typically corresponds to a reduction ratio in which the rotation of the motor is reduced and transmitted, but preferably includes a speed increase ratio in which the rotation of the motor is increased and transmitted. . In the present invention, “the first gear and the fourth gear can be integrally rotated” typically means that the first gear and the fourth gear are formed separately and then fixedly attached to the rotating shaft. Although the aspect which rotates integrally by (for example, spline fitting or press fit) corresponds, the aspect rotated integrally by integrally forming a 1st gear, a 4th gear, and a rotating shaft is included suitably.

  According to this embodiment, the rotation of the motor is transmitted to the slider member with a gear ratio obtained by multiplying the gear ratio constituted by the third gear and the fourth gear by the gear ratio constituted by the first gear and the second gear. Therefore, the gear ratio from the motor to the slider member can be set large. Therefore, when the “gear ratio” is the reduction ratio, a large driving torque can be obtained, and the motor can be downsized.

  According to a preferred mode of the transmission according to the present invention, a transmission that transmits power from a power source with a changeable gear ratio is configured. The transmission includes a first input shaft to which power from a power source is input, a clutch that connects and disconnects the power shaft of the power source and the first input shaft, and the invention according to any one of the above aspects. A clutch switching device, a second input shaft that is concentrically arranged on the inner periphery of the first input shaft and connected directly to the power shaft, an output shaft, a first input shaft, and an output A first gear mechanism that connects the shaft at a first gear ratio, a second gear mechanism that can connect a second input shaft and an output shaft at a second gear ratio, and a second input shaft by the second gear mechanism; And a switching member that selectively switches the connection state with the output shaft. The slider shaft is disposed concentrically with the first input shaft on the outer periphery of the first input shaft. The “direct connection” in the present invention is defined as a mode in which the second input shaft and the power shaft of the power source rotate integrally, and the second input shaft is spline-fitted or press-fitted to the power shaft of the power source. Or a mode in which the second input shaft and the power shaft of the power source are integrally formed.

  According to the present embodiment, since the clutch switching device of the present invention according to any one of the above-described aspects is mounted, the effect similar to the effect exhibited by the clutch switching device of the present invention, for example, the effect that the device can be made compact can be achieved. There is an effect.

  According to the further form of the transmission according to the present invention, the second gear ratio is set to a gear ratio larger than the first gear ratio. According to this embodiment, power can be transmitted using the second gear mechanism when large power is required, and power can be transmitted using the first gear mechanism when large power is not required. That is, the necessary driving force can be obtained while operating the power source in an efficient operating state. As a result, energy efficiency can be improved.

  ADVANTAGE OF THE INVENTION According to this invention, size reduction of a clutch switching apparatus and a transmission provided with the same can be achieved.

It is a block diagram which shows the outline of a structure of the transmission 1 provided with the clutch switching apparatus 10 which concerns on embodiment of this invention. FIG. 6 is an explanatory diagram showing a state of meshing between a gear 16c of a third gear mechanism 16 and a gear 14c of a slider 14; It is a state figure which shows a mode that the slider 14 was moved to the axial direction in order to connect the clutch CL. It is a state figure which shows a mode that the slider 14 was moved to the axial direction in order to cancel | release connection of the clutch CL.

  Next, the best mode for carrying out the present invention will be described using examples.

  Below, the case where the transmission 1 which mounts the clutch switching apparatus 10 which concerns on embodiment of this invention is applied to an electric vehicle is demonstrated. As shown in FIG. 1, the transmission 1 according to the embodiment includes a clutch CL connected to the rotating shaft 52 of the electric motor 50, an outer input shaft 2 connected to the rotating shaft 52 via the clutch CL, and a rotating shaft 52. The inner input shaft 4 directly connected to the outer input shaft 2, the counter shaft 6 arranged in parallel to the inner input shaft 4, the first gear mechanism 20 connecting the outer input shaft 2 and the counter shaft 6, and the inner A second gear mechanism 30 capable of connecting the input shaft 4 and the counter shaft 6, a synchro mechanism 40 fixedly disposed on the inner input shaft 4, a clutch switching device 10 of the present invention for switching the clutch CL, and A casing 60 for housing. The clutch switching device 10 corresponds to the “clutch switching device” in the present invention, and the transmission 1 is an example of an implementation configuration corresponding to the “transmission device” in the present invention. The electric motor 50 corresponds to the “power source” in the present invention, and the rotating shaft 52 is an example of an implementation configuration corresponding to the “power shaft” in the present invention.

  As shown in FIG. 1, the clutch CL is configured as a dry single-plate clutch including a clutch cover 82, a clutch disk 84, a pressure plate 86, and a diaphragm spring 88. The clutch CL corresponds to the “clutch” in the present invention, and the diaphragm spring 88 is an example of an implementation configuration corresponding to the “biasing member” in the present invention.

  The clutch cover 82 is attached to the outer peripheral surface of the inner input shaft 4 directly connected to the rotation shaft 52 so as to rotate integrally with the rotation shaft 52 of the electric motor 50.

  As shown in FIG. 1, the clutch disk 84 is attached to the outer peripheral surface of the outer input shaft 2 by spline fitting.

  The pressure plate 86 is disposed in the clutch cover 82 so as to rotate integrally with the clutch cover 82, and is configured so that the clutch disk 84 can be sandwiched between the clutch cover 82.

  The diaphragm spring 88 always urges the spring force in a direction in which the pressure plate 86 is separated from the clutch disk 84. That is, the clutch CL is normally configured as a normally open clutch in which the connection between the outer input shaft 2 and the rotating shaft 52 of the electric motor 50 is released.

  As shown in FIG. 1, the outer input shaft 2 is configured as a hollow shaft member, and is rotatably supported by the casing 60 via a ball bearing B1. The outer input shaft 2 is an example of an implementation configuration corresponding to the “first input shaft” in the present invention.

  As shown in FIG. 1, the inner input shaft 4 is fitted into the outer input shaft 2 coaxially. One end of the inner input shaft 4 is spline-fitted inside the rotating shaft 52 of the electric motor 50, and the other end is rotatably supported by the casing 60 via a ball bearing B2. The inner input shaft 4 is an example of an implementation configuration corresponding to the “second input shaft” in the present invention.

  As shown in FIG. 1, the counter shaft 6 is rotatably supported by the casing 60 via ball bearings B3 and B4 arranged at both ends. An output gear OG is integrally formed at the end of the counter shaft 6 near the ball bearing B3. The output gear OG meshes with the ring gear RG of the differential device DF. The counter shaft 6 is an example of an implementation configuration corresponding to the “output shaft” in the present invention.

  As shown in FIG. 1, the first gear mechanism 20 includes a first drive gear 22 provided on the outer input shaft 2 and a first driven gear 24 provided on the counter shaft 6. The first drive gear 22 is integrally formed at one end of the outer input shaft 2 (the end opposite to the side on which the clutch disc 84 is splined). The first driven gear 24 is fixed to the counter shaft 6 by spline press so as to rotate integrally with the counter shaft 6, and is configured to mesh with the first drive gear 22. The first driven gear 24 is disposed adjacent to the output gear OG. The first gear mechanism 20 is an example of an implementation configuration example corresponding to the “first gear mechanism” in the present invention.

  As shown in FIG. 1, the second gear mechanism 30 includes a second drive gear 32 provided on the inner input shaft 4 and a second driven gear 34 provided on the counter shaft 6. The second drive gear 32 is disposed on the inner input shaft 4 via a needle bearing. That is, the second drive gear 32 is configured as an idler gear that can rotate relative to the inner input shaft 4. The second drive gear 32 is integrally provided with a clutch gear 32a that engages with a coupling sleeve 44 described later. The second driven gear 34 is fixed to the counter shaft 6 by spline press so as to rotate integrally with the counter shaft 6, and is configured to mesh with the second drive gear 32. The second gear mechanism 30 is set to a larger gear ratio than the first gear mechanism 20. The 2nd gear mechanism 30 is an example of the implementation structural example corresponding to the "2nd gear mechanism" in this invention.

  As shown in FIG. 1, the synchro mechanism 40 includes a synchro hub 42 that is spline-fitted to the inner input shaft 4, a coupling sleeve 44 that is disposed on the outer peripheral surface of the synchro hub 42, a clutch hub 42, and a clutch gear. And a boke ring 46 disposed between the two members 32a.

  The coupling sleeve 44 is configured to be slidable in the axial direction on the outer peripheral surface of the sync hub 42 by the shift fork F. By operating the coupling sleeve 44 toward the clutch gear 32a by the shift fork F, the coupling sleeve 44 and the clutch gear 32a are engaged. As a result, the second drive gear 32 is fixed to the inner input shaft 4, and the second drive gear 32 rotates integrally with the inner input shaft 4. That is, the rotation of the inner input shaft 4 is transmitted to the counter shaft 6 via the second gear mechanism 30. The synchro mechanism 40 is an example of the implementation structure corresponding to the "switching member" in this invention.

  As shown in FIG. 1, the clutch switching device 10 includes a slider shaft 12, a slider 14 coaxially disposed on the outer peripheral surface of the slider shaft 12, a third gear mechanism 16 connected to the slider 14, and a third gear mechanism 16. And a motor 18 connected to the gear mechanism 16.

  As shown in FIGS. 1 and 2, the slider shaft 12 includes a shaft portion 12 a formed in a hollow shape and a flange portion 12 b projecting in a direction orthogonal to the axial direction. The slider shaft 12 is coaxially disposed on the outer peripheral surface of the outer input shaft 2 and is fixed to the casing 60 by a bolt BLT inserted through the flange portion 12b.

  A male screw is formed on the outer peripheral surface of the shaft portion 12a over the entire axial length of the shaft portion 12a. The male screw is configured as a right screw. The slider shaft 12 is an example of the implementation structure corresponding to the "slider shaft" in this invention.

  As shown in FIGS. 1 and 2, the slider 14 includes a shaft portion 14a formed in a hollow shape, and a disk-shaped portion 14b projecting radially outward from the outer peripheral surface of the shaft portion 14a. ing.

  On the inner peripheral surface of the shaft portion 14a, a female screw that is engaged with a male screw formed on the outer peripheral surface of the shaft portion 12a of the slider shaft 12 is formed. The female screw is configured as a right screw corresponding to the male screw of the slider shaft.

  A gear 14c is formed on the outer peripheral surface of the disc-like portion 14b. As shown in FIG. 2, the gear 14 c is configured as a helical gear whose tooth traces are left-handed. In other words, when the gear 14c is viewed from the front with the central axis CS1 of the gear 14c facing in the vertical direction, the tooth trace has an upward slope with respect to the central axis CS1.

  In the embodiment, the inclination angle of the tooth trace of the gear 14c is set within a range of 0 ° to 10 °. The gear 14c is an example of an implementation configuration corresponding to the “second gear” in the present invention. Further, an aspect in which the tooth trace is a left-handed twist or an aspect in which the tooth trace has an upward slope with respect to the central axis CS1 when the central axis CS1 of the gear 14c is viewed from the front in the vertical direction. This is an example of an implementation configuration corresponding to “having tooth traces inclined with respect to the central axis of the second gear” in the present invention.

  Further, a holding portion 14d for holding the release bearing member RB is formed in the radially inner portion of the disc-like portion 14b. The release bearing RB is in contact with a radially inward portion of the diaphragm spring 88. The slider 14 is an example of an implementation configuration corresponding to the “slider member” in the present invention.

  As shown in FIG. 1, the third gear mechanism 16 includes a support shaft 16a, a gear 16b attached and fixed to the support shaft 16a by a pin P1, and a gear 16c attached and fixed to the support shaft 16a by a pin P2. Is provided. The support shaft 16a corresponds to the “support shaft” in the present invention, the gear 16b corresponds to the “fourth gear” in the present invention, and the gear 16c has an implementation configuration corresponding to the “first gear” in the present invention. It is an example.

  One end of the support shaft 16a is rotatably supported by the casing 60 via a ball bearing B5, and is rotatably supported by the adapter plate AP via a ball bearing B6 at the center. The adapter plate AP is attached and fixed to the casing 60.

  The gear 16b is disposed between the bearing B5 and the bearing B6 on the support shaft 16a. The gear 16c is disposed at the other end of the support shaft 16a (the side opposite to the side supported by the casing 60 via the ball bearing B5) and is configured to mesh with the gear 14c of the slider 14.

  Further, as shown in FIG. 2, the gear 16c is configured as a helical gear having the same twist angle as that of the gear 14c and the reverse twist direction, that is, a right twist. That is, in the gear 16c, when viewed from the front with the central axis CS2 of the gear 16c oriented in the vertical direction, the tooth traces have an upward slope with respect to the central axis CS2.

  In the embodiment, the inclination angle of the tooth trace of the gear 16c is set within a range of 0 ° to 10 ° according to the inclination angle of the tooth trace of the gear 14c. An aspect in which the tooth trace is twisted to the right or an aspect in which the tooth trace has an upward slope with respect to the central axis CS2 when the central axis CS2 of the gear 16c is viewed from the front in the vertical direction. It is an example of the implementation structure corresponding to "having the tooth trace which inclines with respect to the center of a 1st gear" in this invention.

  The gear 16c is formed in a long cylindrical shape having an axial length longer than that of the gear 14c. Thus, the meshing between the gear 16c and the gear 14c is maintained even while the slider 14 moves in the axial direction. The gear diameter of the gear 16c is set smaller than the gear diameter of the gear 16b and the gear 14c of the slider 14.

  As shown in FIG. 1, a pinion gear 18b is fixed to the rotating shaft 18a of the motor 18 by a pin P3. The pinion gear 18 b is configured to mesh with the gear 16 b of the third gear mechanism 16. The gear diameter of the pinion gear 18b is set smaller than the gear diameter of the gear 16b.

  As a result, the rotation of the motor 18 is decelerated at the first reduction ratio i1 configured by the pinion gear 18b and the gear 16b and transmitted to the support shaft 16a of the third gear mechanism 16, and the rotation of the support shaft 16a is further reduced. It is decelerated at a second reduction ratio constituted by the gear 16 c and the gear 14 c and is transmitted to the slider 14. That is, the rotation of the motor 18 can be transmitted to the slider 14 at a reduction ratio i obtained by multiplying the first reduction ratio i1 by the second reduction ratio i2. The pinion gear 18b is an example of an implementation configuration corresponding to the “third gear” in the present invention.

  Thus, by transmitting the rotation of the motor 18 to the slider 14 via the third gear mechanism 16, the reduction ratio i from the motor 18 to the slider 14 can be set large. As a result, a large rotational torque can be applied to the slider 14, so that the motor 18 can be reduced in size.

  Further, compared with a configuration in which the motor 18 and the slider 14 are directly connected, that is, a configuration in which the pinion gear 18b and the gear 14c are directly meshed with each other, a reduction ratio of the same size can be realized in a small space. As a result, the apparatus can be made compact.

  When the clutch CL is connected, the motor 18 is rotationally driven so that the rotary shaft 18a rotates in a clockwise direction when the pinion gear 18a side is viewed from the motor 18 side, and the clutch CL is connected. When releasing the rotation, the rotary shaft 18a is rotationally driven so as to rotate in a counterclockwise direction when the pinion gear 18a side is viewed from the motor 18 side. Hereinafter, for convenience of explanation, a clockwise direction when viewing the pinion gear 18a side from the motor 18 side is referred to as a clockwise direction, and a counterclockwise direction is referred to as a counterclockwise direction.

  Next, the operation of the transmission 1 of the embodiment thus configured, particularly the clutch switching operation of the clutch switching device 10 when switching the clutch CL will be described. FIG. 3 is a state diagram showing a state in which the slider 14 is moved in the axial direction in order to connect the clutch CL, and FIG. 4 shows a state in which the slider 14 is moved in the axial direction in order to release the connection of the clutch CL. FIG. First, a case where the clutch CL is connected will be described.

  When the clutch CL is connected, the motor 18 is rotationally driven by a control device (not shown) so that the rotating shaft 18a rotates clockwise. When the rotating shaft 18a is rotated clockwise, the gear 16b meshing with the pinion gear 18b is rotated counterclockwise. As a result, the gear 16c is rotated counterclockwise together with the support shaft 16a, and the gear 14c engaged with the gear 16c is rotated clockwise. That is, when the motor 18 is driven to rotate so that the rotating shaft 18 a is rotated clockwise, the slider 14 is rotated clockwise via the third gear mechanism 16.

  Since the slider 14 is screw-engaged with the slider shaft 12 on its inner peripheral surface, the slider 14 moves in the axial direction on the slider shaft 12 toward the clutch CL side by clockwise rotation as shown in FIG. . At this time, since the gear 14c of the slider 14 slides with respect to the gear 16c of the third gear mechanism 16, a sliding resistance force is generated between the gear 14c and the gear 16c.

  However, according to the present embodiment, since the tooth traces of the gear 14c and the gear 16c are inclined so that the thrust force in the direction opposite to the sliding resistance force acts, the slider 14 is axially moved. An increase in driving force required for movement can be suppressed. As a result, the motor 18 can be reduced in size.

  In the embodiment, the inclination angle of the tooth traces of the gear 14c and the gear 16c is set within a range of 0 ° to 10 ° in which a thrust force that can cancel the sliding resistance force can be generated. The increase in driving force necessary for moving the slider 14 in the axial direction can be further suppressed, and the motor 18 can be further downsized.

  By such movement of the slider 14 in the axial direction, the radially inner portion of the diaphragm spring 88 connected to the slider 14 via the release bearing RB is pressed toward the clutch disk 84 side. As a result, the clutch disk 84 is pressed by the pressure plate 86 (the state indicated by the two-dot chain line in FIG. 1), that is, the clutch CL is connected.

 When the clutch CL is connected, the rotating shaft 52 of the electric motor 50 and the outer input shaft 2 are connected, and the power of the electric motor 50 is output via the first gear mechanism 20. In this case, the synchro mechanism 40 is controlled so that the second drive gear 32 is in an idle state with respect to the inner input shaft 4.

  Next, a case where the clutch CL is disconnected will be described. When releasing the connection of the clutch CL, basically, an operation reverse to that in the case of connecting the clutch CL described above is performed. In other words, the motor 18 is rotationally driven by a control device (not shown) so that the rotating shaft 18a rotates counterclockwise, whereby the gear 16b meshing with the pinion gear 18a is rotated clockwise.

  Along with this, the gear 16c is rotated clockwise together with the support shaft 16a, and the gear 14c meshing with the gear 16c is rotated counterclockwise. That is, when the motor 18 is rotationally driven so that the rotating shaft 18 a is rotated counterclockwise, the slider 14 is rotated counterclockwise via the third gear mechanism 16.

  Since the slider 14 is screw-engaged with the slider shaft 12 on the inner peripheral surface thereof, the slider 14 is axially moved on the slider shaft 12 away from the clutch CL as shown in FIG. . Also at this time, a sliding resistance force is generated between the gear 14c and the gear 16c due to the sliding of the gear 14c of the slider 14 in the axial direction with respect to the gear 16c of the third gear mechanism 16. Is in the opposite direction to that when the clutch CL is connected.

  On the other hand, even when the slider 14 moves axially on the slider shaft 12 in the direction away from the clutch CL, the thrust force generated by inclining the tooth traces of the gear 14c and the gear 16c is engaged with the gear 14c and the gear 16c. Caused by. The direction of the thrust force is opposite to that in the case where the clutch CL described above is connected.

  That is, a thrust force acts in the direction opposite to the direction of the sliding resistance force generated between the gear 14c and the gear 16c. As a result, even when the slider 14 moves axially on the slider shaft 12 in the direction away from the clutch CL, it is possible to suppress an increase in the driving force required to move the slider 14 in the axial direction.

  As a result, the motor 18 can be reduced in size. In addition, since the inclination angle of the tooth traces of the gear 14c and the gear 16c is set within a range of 0 ° to 10 °, the above-described clutch CL is also connected in that the sliding resistance force can be canceled by the thrust force. This is the same as when

  When the slider 14 moves in the axial direction on the slider shaft 12 away from the clutch CL, the spring force of the diaphragm spring 88 acts in the same direction as the axial movement direction of the slider shaft 14. The output of the motor 18 required to move the motor in the axial direction can be kept small compared to when the clutch CL is connected.

  Due to the axial movement of the slider 14, the radially inner portion of the diaphragm spring 88 connected to the slider 14 via the release bearing RB is pulled in a direction away from the clutch disk 84. As a result, the clutch disk 84 is released from being pressed by the pressure plate 86 (shown by the solid line in FIG. 1), that is, the clutch CL is disconnected.

  When the connection of the clutch CL is released, the connection between the rotating shaft 52 of the electric motor 50 and the outer input shaft 2 is released. In this case, the synchro mechanism 40 is controlled so that the second drive gear 32 is fixed to the inner input shaft 4, and the power of the electric motor 50 is output via the second gear mechanism 30.

  According to the clutch switching device 10 of the embodiment described above, the gear 14c is connected to the gear 16c by configuring the gear 14c of the slider 14 and the gear 16c of the third gear mechanism 16 meshing with the gear 14c as helical gears. Thus, the thrust force that can cancel the sliding resistance force that occurs when sliding is generated, so that the output required for the motor 18 to move the slider 14 in the axial direction can be reduced. As a result, the motor 18 can be reduced in size. As a result, the clutch switching device 10 can be reduced in size. Further, since the gear 14c and the gear 16c are configured as helical gears, gear noise can be improved as compared with the case where the gear 14c and the gear 16c are configured as spur gears.

  Further, according to the clutch switching device 10 of the embodiment, since the rotation of the motor 18 is transmitted to the slider 14 via the third gear mechanism 16, the reduction ratio from the motor to the slider member is set large. Can do. Therefore, since a large driving torque can be obtained, the motor 18 can be downsized.

  In the clutch switching device 10 according to the embodiment, the clutch switching device 10 is applied to the transmission 1 mounted on the electric vehicle including the electric motor 50. It may be applied to a transmission mounted on a hybrid vehicle. In addition, the present invention is not limited to such automobiles, and may be applied to a transmission that is mounted on a moving body such as a vehicle including a vehicle, a ship, or an aircraft, or may be applied to a transmission that is incorporated in a construction facility or the like. It is good also as a form.

  Further, in the clutch switching device 10 of the embodiment, it is applied to the switching of the dry type single plate clutch, but may be applied to the switching of the dry type multi-plate clutch and the wet type multi-plate clutch.

  In the clutch switching device 10 according to the embodiment, the clutch switching device 10 is applied to the transmission 1 including only one clutch CL. However, the clutch switching device 10 may be applied to a twin clutch transmission including two clutches. In this case, two clutches can be switched by one clutch switching device 10, or each clutch can be switched by using two clutch switching devices 10.

  In the clutch switching device 10 according to the embodiment, the clutch switching device 10 is applied to the switching of the normally open type clutch CL. However, the clutch switching device 10 may be applied to a normally closed type clutch. Even in this case, the gear 14c of the slider 14 and the gear 16c of the third gear mechanism 16 have a thrust force generated by the engagement of the gear 14c of the slider 14 and the gear 16c of the third gear mechanism 16 with the gear 14c. What is necessary is just to comprise so that it may become the inclination which acts in the direction opposite to the sliding resistance force produced between the gears 16c.

  In the clutch switching device 10 of the embodiment, as an inclination angle of the tooth traces of the gear 14c and the gear 16c, an angle (0) that can generate a thrust force that can cancel the sliding resistance force generated between the gear 14c and the gear 16c. However, it is possible to generate a thrust force that can cancel at least part of the spring force of the diaphragm spring 88 as the inclination angle of the tooth traces of the gear 14c and the gear 16c. An angle (for example, an angle larger than 10 °) may be set.

  The clutch switching device 10 of the embodiment is applied to the two-stage transmission 1 including the first gear mechanism 20 and the second gear mechanism 30, but may be applied to a transmission having three or more stages. Absent.

  In the clutch switching device 10 of the embodiment, the rotation of the motor 18 is transmitted to the slider 14 via the third gear mechanism 16, but the rotation of the motor 18 may be directly transmitted to the slider 14. In other words, the pinion gear 18b attached and fixed to the rotating shaft 18a of the motor 18 may be engaged with the gear 14c of the slider 14.

  In the clutch switching device 10 of the embodiment, when the clutch CL is connected, the motor 18 is rotationally driven so that the rotating shaft 18a is rotated in the clockwise direction, and when the clutch CL is released. Is configured to be rotationally driven so that the rotary shaft 18a is rotated in the counterclockwise direction, but the motor 18 may be configured to be rotationally driven in the opposite direction. That is, when the clutch CL is connected, the rotary shaft 18a is driven to rotate in the counterclockwise direction, and when the clutch CL is released, the rotary shaft is rotated in the clockwise direction. It is good also as a structure driven rotationally so that 18a may be rotated. In this case, the gear 14c and the gear 16c may be configured as a helical gear having a twisted tooth trace reverse to that of the embodiment. That is, the tooth trace of the gear 14c may be configured to be right-twisted, and the tooth trace of the gear 16c may be configured to be left-twisted.

(Correspondence between each component of the embodiment and each component of the present invention)
This embodiment shows an example for carrying out the present invention. Therefore, the present invention is not limited to the configuration of the present embodiment.

2 Outer input shaft 4 Inner input shaft 6 Counter shaft 10 Clutch switching device 12 Slider shaft 12a Shaft portion 12b Flange portion 14 Slider 14a Shaft portion 14b Disk-shaped portion 14c Gear 14d Holding portion 16 Third gear mechanism 16a Support shaft 16b Gear 16c Gear 18 Motor 18a Rotating shaft 18b Pinion gear 20 First gear mechanism 22 First drive gear 24 First driven gear 30 Second gear mechanism 32 Second drive gear 32a Clutch gear 34 Second driven gear 40 Synchro mechanism 42 Synchro hub 44 Coupling Sleeve 46 Bokeh ring 50 Electric motor 52 Rotating shaft 60 Casing 82 Clutch cover 84 Clutch disc 86 Pressure plate 88 Diaphragm spring CL Clutch B1 Ball bearing B2 Ball bearing B3 Bo Bearings B4 ball bearings B5 ball bearing B6 ball bearing OG output gear DF differential unit RG ring gear F shift fork RB release bearing P1 Pin P2 Pin AP adapter plate P3 pin CS1 central axis CS2 central axis BLT bolt

Claims (8)

A clutch switching device for switching a clutch,
A motor,
A gear member having a first gear and driven to rotate by the motor;
A fixed slider shaft;
A slider member having a second gear meshing with the first gear and screw-engaged on the slider shaft;
With
The first gear has tooth traces inclined with respect to the central axis of the first gear;
The second gear has tooth traces inclined with respect to the central axis of the second gear;
A clutch switching device configured to switch the clutch by the slider member which is screwed back and forth on the slider shaft in the axial direction. The second gear is configured to slide relative to the first gear when the slider member is screwed back and forth on the slider shaft in the axial direction.
The inclination of the tooth traces in the first gear and the second gear is caused by the sliding force generated between the first gear and the second gear due to the thrust force generated by the meshing of the first gear and the second gear. The clutch switching device according to claim 1, wherein the clutch switching device is configured to act in a direction opposite to the dynamic resistance force.   The clutch switching device according to claim 2, wherein the inclination of the tooth traces in the first gear and the second gear is set to an angle at which a thrust force capable of canceling the sliding resistance force can be generated. An urging member that urges the clutch in a direction to connect the clutch or a direction to release the clutch;
4. An inclination of tooth traces of the first gear and the second gear is set to an angle at which a thrust force capable of canceling at least a part of the urging force of the urging member can be generated. The clutch switching device according to any one of the above. A third gear that can rotate integrally with the rotating shaft is fixed to the rotating shaft of the motor.
The said gear member has a 4th gear which meshes with the said 3rd gear, and the support shaft which supports the said 1st gear and the said 4th gear so that integral rotation is possible. The clutch switching device according to item.   The clutch switching device according to any one of claims 1 to 5, wherein an inclination angle of tooth traces of the first gear and the second gear is within a range of 0 ° to 10 ° with respect to the central axis. A transmission that transmits power from a power source with a changeable gear ratio,
A first input shaft to which power from the power source is input;
A clutch that connects and disconnects the power shaft of the power source and the first input shaft;
The clutch switching device according to any one of claims 1 to 6,
A second input shaft disposed concentrically with the first input shaft on the inner periphery of the first input shaft and directly connected to the power shaft;
An output shaft;
A first gear mechanism that connects the first input shaft and the output shaft at a first gear ratio;
A second gear mechanism capable of connecting the second input shaft and the output shaft at a second gear ratio;
A switching member that selectively switches the connection state between the second input shaft and the output shaft by the second gear mechanism;
With
The transmission, wherein the slider shaft is arranged on the outer periphery of the first input shaft concentrically with the first input shaft.   The transmission according to claim 7, wherein the second gear ratio is set to a gear ratio larger than the first gear ratio.

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