Shift device

Abstract

To provide a shift device that can suppress rattling noise in the oscillating slider-crank mechanism. [Solution] The shift device 10 includes a motor 26 and a swing slider crank mechanism 30 that decelerates the rotation of the motor 26, and selectively switches the operating state of the parking lock device 70 to either a locked state or an unlocked state, in which (a) the swing slider crank mechanism 30 includes a short lever 32 and a long lever 40, and (b) when the swing slider crank mechanism 30 is in a non-P range state, the operating state of the parking lock device 70 is switched to an unlocked state, and play is suppressed to reduce the relative movement between the short lever 32 and the long lever 40 in order to suppress rattling noise between the short lever 32 and the long lever 40.

Description

Technical Field

[0001] The present invention relates to a shift device that selectively switches the operating state of a parking lock device to either one of a locked state and an unlocked state, and includes a motor and an oscillating slider crank mechanism that decelerates the rotation of the motor.

Background Art

[0002] Shift devices that selectively switch the operating state of a parking lock device to either one of a locked state and an unlocked state are known. For example, the one described in Patent Document 1 is such a device. The "locked state" refers to a state in which the parking lock device blocks rotation of a parking gear that rotates in conjunction with a pair of drive wheels. On the other hand, the "unlocked state" refers to a state in which the locked state of the parking lock device is released, and rotation of the parking gear that rotates in conjunction with the pair of drive wheels is permitted.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of Invention

Problems to be Solved by the Invention

[0004] Patent Document 1 discloses a shift device provided with an oscillating slider crank mechanism. The oscillating slider crank mechanism includes a short lever provided with a pin that makes a rotational motion, and a long lever that is provided with a substantially rectangular long hole for retaining the pin and that oscillates. To enable the long lever of the oscillating slider crank mechanism to oscillate, a play, which is a gap of a predetermined amount, is required between the inner wall surface of the long hole and the outer peripheral surface of the pin. For example, in a state where the shift device is controlled so that the parking lock device is in the unlocked state, vibration input to the shift device from the outside acts on the play of the oscillating slider crank mechanism, which may cause a rattle noise.

[0005] The present invention was made against the above circumstances, and its objective is to provide a shift device that can suppress rattling noise in the oscillating slider-crank mechanism. [Means for solving the problem]

[0006] The gist of the present invention is a shift device comprising a motor and a swing slider crank mechanism for decelerating the rotation of the motor, which selectively switches the operating state of a parking lock device to either a locked state or an unlocked state, wherein (a) the swing slider crank mechanism comprises a short lever and a long lever, and (b) when the swing slider crank mechanism is in a predetermined state, the operating state of the parking lock device is switched to the unlocked state, and a predetermined tightening is performed to suppress the relative movement between the short lever and the long lever in order to suppress rattling noise between them. [Effects of the Invention]

[0007] According to the shift device of the present invention, (a) the oscillating slider crank mechanism is equipped with a short lever and a long lever, and (b) when the oscillating slider crank mechanism is in a predetermined state, the operating state of the parking lock device is switched to the unlocked state, and a predetermined adjustment is made to suppress the relative movement between the short lever and the long lever in order to suppress rattling noise between the short lever and the long lever. As a result, when the operating state of the parking lock device is switched to the unlocked state, a predetermined adjustment is made to suppress the relative movement between the short lever and the long lever. As a result, even if vibration is input to the shift device from the outside, rattling noise caused by play in the oscillating slider crank mechanism is suppressed. [Brief explanation of the drawing]

[0008] [Figure 1] This is a schematic diagram of a vehicle equipped with a shift device that includes a swing slider-crank mechanism according to Embodiment 1. [Figure 2]Figure 1 is an explanatory diagram of the parking lock device. [Figure 3] Figure 1 is an explanatory diagram of the oscillating slider crank mechanism. [Figure 4] This is an explanatory diagram of the oscillating slider-crank mechanism according to Example 2. [Figure 5] This is an explanatory diagram of the oscillating slider-crank mechanism according to Example 3. [Figure 6] This is an explanatory diagram of the oscillating slider-crank mechanism according to Embodiment 4. [Figure 7] This is an explanatory diagram of the oscillating slider-crank mechanism according to Examples 5 and 6. [Modes for carrying out the invention]

[0009] Hereinafter, each embodiment of the present invention will be described in detail with reference to the drawings. In each embodiment, the drawings have been simplified or modified as appropriate, and the dimensional ratios and shapes of each part are not necessarily depicted accurately. Furthermore, in each embodiment, if the configuration is substantially the same as that of a prior embodiment, the explanation will focus on the differences, and parts that are substantially common in function with those of a prior embodiment will be denoted by the same reference numerals, and their explanation will be omitted as appropriate. [Examples]

[0010] Figure 1 is a schematic diagram of a vehicle 100 equipped with a shift device 10 having a swing slider-crank mechanism 30 (hereinafter simply referred to as "crank mechanism 30") according to Embodiment 1. The shift device 10 is a shift-by-wire system. The shift device 10 comprises a motor 26, a crank mechanism 30, and an electronic control device 90. The motor 26 and the crank mechanism 30 constitute an actuator 20. The shift device 10 is mounted on the vehicle 100 and is a device that switches the shift range of the vehicle 100. The operation of selecting the shift range of the vehicle 100 is performed, for example, by the driver's operation of a well-known shift lever. The shift device 10 switches the shift range by the rotation of the motor 26. The shift range represents the state of power transmission from the power source for driving the vehicle 100 (e.g., engine or drive motor) to a pair of drive wheels. For example, the shift device 10 switches the shift range from one of the P range and non-P range to the other. The P range is a parking range in which the vehicle 100 is in a neutral state and the pair of drive wheels are mechanically fixed so that they cannot rotate. Non-P ranges are other shift ranges other than the P range, such as the reverse driving range which allows the vehicle 100 to move in reverse, the neutral range which puts the vehicle in a neutral state in which power transmission from the driving power source to the pair of drive wheels is cut off, and the forward driving range which allows the vehicle 100 to move forward.

[0011] Motor 26 is, for example, a well-known DC motor. Motor 26 is a motor that generates a reluctance torque Trel [N·m] in a non-driving state. For example, it is a permanent magnet type DC commutator motor. Reluctance torque Trel is a well-known torque that attempts to rotate the rotor of motor 26 so that magnetic field lines penetrate the shortest distance, and is a torque that is generated by the same principle as cogging torque. The rotation of motor 26 is output from the motor output shaft 48, which is the output shaft of motor 26, and then from the crank mechanism 30, starting from the motor 26 side. The crank output shaft 48 is the output shaft of actuator 20. The crank output shaft 48 is connected to the manual shaft 72 in a way that prevents relative rotation (see Figure 2). The rotation of the crank output shaft 48 switches the operating state of the parking lock device 70 and switches the shift range. Details of the crank mechanism 30 will be described later.

[0012] The electronic control unit 90 is composed of, for example, a so-called microcomputer and performs signal processing according to a pre-stored program. The electronic control unit 90 switches the shift range by controlling the rotation of the motor 26. The electronic control unit 90 receives various signals based on values ​​detected by various sensors (for example, a rotation angle sensor 92, a vehicle speed sensor 94, an accelerator pedal position sensor 96, an acceleration sensor 98, etc.) (for example, the motor rotation angle θmt [deg] representing the rotational position of the motor output shaft 28, the vehicle speed V [km / h], the accelerator pedal position θacc [%] representing the amount of accelerator operation by the driver, and the longitudinal acceleration Ax [m / s] of the vehicle 100). 2 ] and lateral acceleration Ay[m / s² 2 The following are inputs: [etc.]. The electronic control unit 90 outputs a motor control signal Smt to the motor 26 to control the rotation of the motor 26.

[0013] Figure 2 is an explanatory diagram of the parking lock device 70 shown in Figure 1. The parking lock device 70 includes a manual shaft 72, a parking gear 76, a parking lock pole 78, a parking rod 82, and a taper member 86. The parking lock device 70 is a well-known device that blocks the rotation of a pair of drive wheels connected to the parking gear 76 by making the parking gear 76 non-rotatable when the driver operates the vehicle 100 to set the shift range to the P range. Figure 2 shows a state where the operating state of the parking lock device 70 is the locked state. In the locked state, when the manual shaft 72 is rotated in the direction of arrow A, one end of the parking rod 82 is moved in the direction of arrow B, and the movement of the taper member 86 causes the claw portion 80 of the parking lock pole 78 to be moved in the direction of arrow C. As a result, the operating state of the parking lock device 70 is switched to the unlocked state. In the unlocked state, when the manual shaft 72 is rotated in the direction opposite to arrow A, one end of the parking rod 82 is moved in the direction opposite to arrow B, and the movement of the taper member 86 causes the claw portion 80 to be moved in the direction opposite to arrow C. As a result, the operating state of the parking gear 76 is switched to the locked state. For example, when the driver operates to set the shift range to a non-P range, the rotation of the motor 26 rotates the manual shaft 72, and the parking lock device 70 is switched to the unlocked state. The shift device 10 is a device that selectively switches the operating state of the parking lock device 70 to either one of the locked state and the unlocked state.

[0014] Figure 3 is an explanatory diagram of the crank mechanism 30 shown in Figure 1. Figure 3 (the same applies to Figures 4 to 7 described later) is a view of the crank mechanism 30 as viewed in the direction of arrow X shown in Figure 2.

[0015] The crank mechanism 30 includes a short lever 32 and a long lever 40.

[0016] One end of the main body 34 of the short lever 32 is fixed to the motor output shaft 28 so as not to rotate relative to it. The rotational centerlines of the motor output shaft 28 and the short lever 32 are the first axis C1. The other end of the main body 34 is provided with a cylindrical pin 36 extending in the direction of the first axis C1. The pin 36 rotates along a trajectory on the arc of a circle C1f centered on the first axis C1. One end of the main body 42 of the long lever 40 is fixed to the crank output shaft 48 so as not to rotate relative to it. The rotational centerlines of the crank output shaft 48 and the long lever 40 are the second axis C2. The other end of the main body 42 is provided with a roughly rectangular elongated hole 44 extending in the longitudinal direction of the main body 42. The pin 36 is slidable within the elongated hole 44. There is some play G between the inner wall surface 44i of the elongated hole 44 and the outer circumferential surface 36o of the pin 36. The play G includes the circumferential gap centered on the second axis C2. The inner wall surface 44i and the outer circumferential surface 36o are surfaces that face each other in the vertical plane of the first axis C1. The long lever 40 functions as a reduction device that slows down the rotation of the short lever 32.

[0017] Here, the direction indicated by the short lever 32 in the radial direction centered on the first axis C1 will be referred to as "indication direction Dr1". The direction indicated by the long lever 40 in the radial direction centered on the second axis C2 will be referred to as "indication direction Dr2". "Indication direction Dr1" and "indication direction Dr2" correspond to the "predetermined indication direction of the short lever" and the "predetermined indication direction of the long lever" in this invention, respectively. As shown in Figure 3(a), the indication direction Dr1 when indication direction Dr1 and indication direction Dr2 are in the same direction will be referred to as "reference direction Dr0". In Figure 3 (and similarly in Figures 4 to 7 described later), the rotation angle of the main body 34 of the short lever 32 will be referred to as "rotation angle θ", and the rotation angle of the main body 42 of the long lever 40 will be referred to as "rotation angle φ". For rotation angles θ and φ, the angle in the counterclockwise direction from the reference direction Dr0, i.e., the non-P range state side, is considered positive, and the angle in the clockwise direction is considered negative. The rotation angle of the indicator direction Dr1 relative to the indicator direction Dr2 is called the intersection angle ψ [deg]. The intersection angle ψ is defined as the angle in the counterclockwise direction of the indicator direction Dr1 relative to the indicator direction Dr2 being positive, and the angle in the clockwise direction being negative. When the indicator direction Dr1 and the indicator direction Dr2 are in the same direction, the intersection angle ψ is 0 degrees, and the length from the first axis C1 to the center of the pin 36 is L1 [m], and the length from the second axis C2 to the first axis C1 is L2 [m].

[0018] Fig. 3(a) shows a state where the intersection angle ψ is 0 degrees. Fig. 3(b) shows a state where the indication direction Dr2 has rotated counterclockwise to the maximum extent, the intersection angle ψ is 90 degrees, the rotation angle φ [deg] is defined as the maximum rotation angle φmax, and the rotation angle θ [deg] is defined as the right-angle intersection rotation angle θr1. Fig. 3(c) shows a state where the short lever 32 has further rotated counterclockwise from the state of Fig. 3(b), the intersection angle ψ exceeds 90 degrees, the rotation angle φ is defined as the return position rotation angle φ1 (0<φ1<φmax), and the rotation angle θ is defined as the maximum rotation angle θmax (180>θmax>θr1). Fig. 3(c) shows the non-P range state of the crank mechanism 30. The crank mechanism 30 enters the non-P range state, for example, when the rotation angle φ is within a predetermined angle range including the return position rotation angle φ1. The "non-P range state" refers to the state of the shift device 10 that puts the parking lock device 70 in the unlocked state, that is, the state of the crank mechanism 30. In the crank mechanism 30, the elongated hole 44 and the pin 36 are engaged such that the absolute value of the intersection angle ψ exceeds 90 degrees. Note that the non-P range state corresponds to the "predetermined state" in the present invention.

[0019] Although not shown in Fig. 3, in a state where the short lever 32 rotates clockwise and the intersection angle ψ is -90 degrees, the rotation angle φ is defined as the minimum rotation angle φmin, and the rotation angle θ is defined as the right-angle intersection rotation angle θr2. Fig. 3(d) shows a state where the indication direction Dr2 has rotated clockwise to the maximum extent, and then the short lever 32 has further rotated clockwise, the rotation angle φ is defined as the return position rotation angle φ2 (0>φ2>φmin), and the rotation angle θ is defined as the minimum rotation angle θmin (-180<θmin<θr2). Fig. 3(d) shows the P range state of the crank mechanism 30. The crank mechanism 30 enters the P range state when the rotation angle φ is within a predetermined angle range including the return position rotation angle φ2. The "P range state" refers to the state of the shift device 10 that puts the parking lock device 70 in the locked state, that is, the state of the crank mechanism 30.

[0020] The crank mechanism 30 is provided with a compression coil spring 50 that biases the main body 42, as shown in Figures 3(b) and 3(c). One end 50a of the compression coil spring 50 is connected to a non-rotating member 68, and the other end 50b contacts the main body 42 in Figures 3(b) and 3(c), biasing the long lever 40 to rotate clockwise. In Figure 3(c), the intersection angle ψ exceeds 90 degrees and is less than 180 degrees, and the biasing force F[N] of the compression coil spring 50 presses the inner wall surface 44i against the outer circumferential surface 36o in a clockwise direction, thereby eliminating the play G[m]. An intersection angle ψ of less than 180 degrees is equivalent to the short lever 32 being unable to rotate 360 ​​degrees. This play elimination suppresses relative movement between the short lever 32 and the long lever 40 and corresponds to the "predetermined elimination" in the present invention. The biasing force F is a torque that rotates the short lever 32 counterclockwise. The biasing force F is set to a size that allows the motor 26 to rotate the short lever 32 against the biasing force F, and also to reduce play in order to suppress rattling noise. "Rattling noise" refers to the collision sound generated when the outer surface 36o and the inner wall surface 44i collide with each other in the rattle G. The compression coil spring 50 corresponds to the "biasing member" in this invention. In Figure 3(d), the crank mechanism 30 is provided with a compression coil spring 52 that contacts the main body 42 and biases the long lever 40 to rotate counterclockwise. Similarly, in Figure 3(d), the biasing force F of the compression coil spring 52 presses the inner wall surface 44i against the outer surface 36o in a counterclockwise direction, thereby reducing play.

[0021] In this embodiment, (a) the crank mechanism 30 is equipped with a short lever 32 and a long lever 40, and (b) when the crank mechanism 30 is in a non-P range state, the parking lock device 70 is switched to an unlocked state, and the play is eliminated by the biasing force F of the compression coil spring 50. In this way, since the play is eliminated when the parking lock device 70 is switched to an unlocked state, even if vibration is input to the shift device 10 from the outside, the rattling noise caused by the play G of the crank mechanism 30 is suppressed. [Examples]

[0022] Figure 4 is an explanatory diagram of the oscillating slider crank mechanism 130 according to Embodiment 2 (hereinafter simply referred to as "crank mechanism 130"). The crank mechanism 130 has substantially the same configuration as the crank mechanism 30 according to Embodiment 1 described above, but the main difference is that a tension coil spring 56 is provided instead of compression coil springs 50 and 52.

[0023] Figure 4(a) shows the state where the intersection angle ψ is 0 degrees. Figure 4(b) shows the state where both the indicator direction Dr1 and the indicator direction Dr2 are rotated to their maximum extent in the counterclockwise direction, and the crank mechanism 130 is in a non-P range state. The crank mechanism 130 is in a non-P range state when the rotation angle φ is within a predetermined angular range that includes the maximum rotation angle φmax.

[0024] In the crank mechanism 130, the elongated hole 44 and the pin 36 are locked together so that the absolute value of the intersection angle ψ does not exceed 180 degrees. In this embodiment, the maximum rotation angle θmax is 90 degrees. The tension coil spring 56 has, for example, one end 56a connected to the crank output shaft 48 so as to be rotatable relative to it, and the other end 56b connected to the pin 36 so as to be rotatable relative to it. As a result, when the intersection angle ψ exceeds 0 degrees and is less than 180 degrees (0 < ψ < 180), the biasing force F of the tension coil spring 56 biases the main body 34 to rotate counterclockwise via the pin 36. The tension coil spring 56 corresponds to the "biasing member" in this invention.

[0025] In the P range state of the crank mechanism 130, the biasing force F of the tension coil spring 56 biases the main body 34 to rotate clockwise via the pin 36. In this embodiment, the rotational trajectory of the pin 36 is outward, on the semicircular arc opposite to the second axis C2 in circle C1f.

[0026] In this embodiment, when the crank mechanism 130 is in a non-P range state, the parking lock device 70 is switched to an unlocked state, and the play is eliminated by the biasing force F of the tension coil spring 56. As a result, as in the above-described embodiment 1, the generation of rattling noise in the crank mechanism 130 is suppressed. Furthermore, the number of biasing member parts can be reduced compared to embodiment 1. [Examples]

[0027] Figure 5 is an explanatory diagram of the oscillating slider crank mechanism 230 according to Embodiment 3 (hereinafter simply referred to as "crank mechanism 230"). The crank mechanism 230 has substantially the same configuration as the crank mechanism 30 according to Embodiment 1 described above, but the main difference is that a torsion coil spring 58 is provided instead of the compression coil springs 50 and 52.

[0028] Figure 5(a) shows the state where the intersection angle ψ is 0 degrees. Figure 5(b) shows the state where the indicator direction Dr2 has rotated to its maximum extent counterclockwise, and the intersection angle ψ is 90 degrees, with the rotation angle φ being the maximum rotation angle φmax and the rotation angle θ being the right-angle intersection rotation angle θr1. Figure 5(c) shows the state where the short lever 32 has rotated further counterclockwise from the state in Figure 5(b), and the intersection angle ψ exceeds 90 degrees, with the long lever 40 and short lever 32 in the same state as in Figure 3(c). In the crank mechanism 230, the elongated hole 44 and the pin 36 are locked so that the absolute value of the intersection angle ψ exceeds 90 degrees. Although not shown in Figure 5, when the short lever 32 rotates clockwise and the intersection angle ψ becomes -90 degrees, the rotation angle φ is the minimum rotation angle φmin and the rotation angle θ is the right-angle intersection rotation angle θr2. Figure 5(d) shows the state after the indicator direction Dr2 has rotated to its maximum extent clockwise, and the short lever 32 has rotated further clockwise, with the long lever 40 and short lever 32 in the same state as in Figure 3(d).

[0029] The crank mechanism 230 is provided with a torsion coil spring 58. One end 58a of the torsion coil spring 58 is connected to a non-rotating member 68, and the other end 58b is connected between the second axis C2 and the elongated hole 44 of the long lever 40. For example, in Figure 5(a), the torsion coil spring 58 does not bias the long lever 40. In Figures 5(b) and 5(c), the torsion coil spring 58 biases the main body 42 of the long lever 40 to rotate clockwise. In Figure 5(d), the torsion coil spring 58 biases the main body 42 to rotate counterclockwise. The torsion coil spring 58 corresponds to the "biasing member" in this invention.

[0030] In Figure 5(c), the same play reduction procedure as in Figure 3(c) is performed. In Figure 5(d), the same play reduction procedure as in Figure 3(d) is performed.

[0031] In this embodiment, when the crank mechanism 230 is not in the P range, the parking lock device 70 is switched to the unlocked state, and the play is eliminated by the biasing force F of the torsion coil spring 58. As a result, as in the above-described embodiment 1, the generation of rattling noise in the crank mechanism 230 is suppressed. In addition, the number of parts of the biasing member can be reduced compared to embodiment 1. [Examples]

[0032] Figure 6 is an explanatory diagram of the oscillating slider crank mechanism 330 according to Embodiment 4 (hereinafter simply referred to as "crank mechanism 330"). The crank mechanism 330 has substantially the same configuration as the crank mechanism 130 according to Embodiment 2 described above, but the main difference is that at least one of the elastic members 60, 62, 64, and 66 is provided instead of the tension coil spring 56.

[0033] Figure 6(a) shows the state where the intersection angle ψ is 0 degrees. Figure 6(b) shows the state where both the indicator direction Dr1 and the indicator direction Dr2 are rotated to their maximum extent in the counterclockwise direction, which is the non-P range state of the crank mechanism 330.

[0034] In the crank mechanism 330, the elongated hole 44 and the pin 36 are locked together so that the absolute value of the intersection angle ψ does not exceed 180 degrees. Figures 6(i) to (iv) are cross-sectional views along the cutting line SS shown in Figure 6(b).

[0035] In Figure 6(i), a cylindrical pin 36 extending in the direction of the first axis C1 is fixed to the main body 34. In Figure 6(ii), the pin 36 has a cylindrical shaft portion inserted through the main body 34 and movable in the direction of the first axis C1, and a cylindrical flange portion fitted to the end of the shaft portion on the side of the elongated hole 44. In Figure 6(iii), the pin 36 has a cylindrical shaft portion extending in the direction of the first axis C1 and fixed to the main body 34, and a cylindrical flange portion inserted into the elongated hole 44 side of the shaft portion and movable in the direction of the first axis C1. In Figure 6(iv), the pin 36 has a cylindrical shaft portion extending in the direction of the first axis C1 and fixed to the main body 34, and a cylindrical flange portion fitted to the end of the shaft portion on the side of the elongated hole 44. In Figures 6(ii) to (iv), the outer surface 36o is the outer surface of the flange portion facing the inner wall surface 44i.

[0036] In Figures 6(i) to (iv), at least one of the outer circumferential surface 36o and the inner wall surface 44i is tapered. When the outer circumferential surface 36o is tapered, the outer diameter increases the further it is from the main body 42 in the direction of the first axis C1. When the inner wall surface 44i is tapered, the inner diameter decreases the further it is from the main body 34 in the direction of the first axis C1. In Figures 6(i) to (iv), the maximum outer diameter of the pin 36 is greater than the minimum inner diameter of the elongated hole 44.

[0037] The elastic members 60, 62, 64, and 66 are all positioned so that when the crank mechanism 330 is in a non-P range state, a biasing force F acts on one of the outer circumferential surface 36o and the inner wall surface 44i from one to the other in the direction of the first axis C1. The elastic members 60, 62, 64, and 66 are, for example, disc springs. The elastic members 60, 62, 64, and 66 are provided with, for example, hemispherical projections. The elastic members 60, 62, 64, and 66 each correspond to the "biasing members" in the present invention.

[0038] As shown in Figure 6(i), the elastic member 60 biases the tapered inner wall surface 44i to press against the corner of the outer circumferential surface 36o on the main body portion 42 side.

[0039] As shown in Figure 6(ii), the elastic member 62 biases the outer peripheral surface of the flange of the tapered pin 36 against the corner on the main body 34 side of the inner wall surface 44i. In Figure 6(a), the lower surface of the pin 36 (= the surface of the flange of the pin 36 on the main body 34 side, the same applies hereafter) is separated from the main body 34 by a distance d1 [m]. In Figure 6(b), the lower surface of the pin 36 is separated from the main body 34 by a distance d2 (>d1) [m]. When the state is switched from Figure 6(a) to Figure 6(b), the elastic member 62 is inserted between the lower surface of the pin 36 and the main body 34 such that the spherical surface of its hemispherical projection enters through the gap of distance d1.

[0040] As shown in Figure 6(iii), the elastic member 64 biases the corner of the outer circumferential surface of the flange of the pin 36 on the main body portion 42 side to press against the tapered inner wall surface 44i. When the state is switched from Figure 6(a) to Figure 6(b), the elastic member 64 is inserted between the lower surface of the pin 36 and the main body portion 34 such that the spherical surface of its hemispherical projection enters through a gap of distance d1.

[0041] As shown in Figure 6(iv), the elastic member 66 biases the outer circumferential surface of the flange portion of the tapered pin 36 against the tapered inner wall surface 44i.

[0042] The biasing force F of these elastic members 60, 62, 64, and 66 in the direction of the first axis C1 suppresses the relative movement of the long lever 40 and the short lever 32 by frictional force. The biasing force F of the elastic members 60, 62, 64, and 66 suppresses the relative movement between the short lever 32 and the long lever 40, and corresponds to the "predetermined engagement" in the present invention. The frictional force is set to a magnitude that allows the motor 26 to rotate the short lever 32 against the frictional force, and that prevents relative movement between the long lever 40 and the short lever 32 even with external vibrations. Although the explanation is omitted, similarly, when the crank mechanism 330 is in the P range state, a predetermined engagement is performed to suppress the relative movement between the short lever 32 and the long lever 40.

[0043] According to this embodiment, when the crank mechanism 330 is in a non-P range state, the parking lock device 70 is switched to an unlocked state, and relative movement between the short lever 32 and the long lever 40 is suppressed by a biasing force F from at least one of the elastic members 60, 62, 64, and 66. As a result, rattling noises in the crank mechanism 330 are suppressed, similar to Embodiment 2. [Examples]

[0044] Figure 7 is an explanatory diagram of the oscillating slider-crank mechanism 430 according to Embodiment 5 (hereinafter simply referred to as "crank mechanism 430"). The reference numerals in parentheses in Figure 7 refer to Embodiment 6, which will be described later. The crank mechanism 430 has substantially the same configuration as the crank mechanism 130 according to Embodiment 2 described above, but the main difference is that it does not have a tension coil spring 56.

[0045] Figure 7(a) shows the state where the intersection angle ψ is 0 degrees. Figure 7(b) shows the state where both the indicator direction Dr1 and the indicator direction Dr2 are rotated to their maximum extent in the counterclockwise direction, which is the non-P range state of the crank mechanism 430.

[0046] In the crank mechanism 430, the elongated hole 44 and the pin 36 are locked together so that the absolute value of the intersection angle ψ does not exceed 180 degrees. Preferably, the maximum absolute value of the intersection angle ψ in the crank mechanism 530 is near 90 degrees.

[0047] When the crank mechanism 430 is switched to a non-P range state, the motor 26 rotates the short lever 32 counterclockwise until the crank mechanism 430 is in a non-P range state. Preferably, the motor 26 is deactivated when its rotation angle φ is just before it reaches its maximum rotation angle φmax. At this time, the rotation of the motor 26 is stopped at a position where the play is eliminated by the reluctance torque Trell. When the motor 26 is deactivated, the play is eliminated by the reluctance torque Trell of the motor 26. The reluctance torque Trell is set to a size that allows for play elimination.

[0048] According to this embodiment, (a) when the rotation angle θ is at its maximum rotation angle θmax, the intersection angle ψ is less than 180 degrees, and (b) when the crank mechanism 430 is in a non-P range state, the parking lock device 70 is switched to an unlocked state, and the play is eliminated by the biasing force F of the reluctance torque Trel. As a result, rattling noise is suppressed in the crank mechanism 430 without the need for a biasing member. [Examples]

[0049] The oscillating slider crank mechanism 530 according to Embodiment 6 (hereinafter simply referred to as "crank mechanism 530") has substantially the same configuration as the crank mechanism 430 according to Embodiment 5 described above, but the main difference is that when the crank mechanism 530 is in a non-P range state, the motor 26 outputs a backlash-reducing torque Tgata [N·m] which is a torque that reduces backlash G.

[0050] When the crank mechanism 530 is switched to a non-P range state, the motor 26 outputs a backlash reduction torque Tgata, and the backlash is reduced by this backlash reduction torque Tgata. The "backlash reduction torque Tgata" is the torque required to reduce backlash G in order to suppress rattling noise, converted into a torque value in the motor 26, and is a predetermined torque that is experimentally or design-wise determined in advance. The backlash reduction torque Tgata corresponds to the "predetermined torque" in this invention.

[0051] The play-reducing torque Tgata may always be output when the crank mechanism 530 is not in the P range, or it may only be output when certain conditions are met under which it is assumed that rattling noise may occur due to external vibration. The predetermined conditions are, for example, that the vehicle speed V is greater than or equal to a predetermined vehicle speed value V_jdg, and the vehicle acceleration α{for example (Ax 2 +Ay 2 ) 1 / 2 At least one of the following conditions is met: the acceleration value α_jdg is greater than or equal to a predetermined acceleration value α_jdg, and the torque change ΔTr [N·m / s], which is the rate of change of the drive torque Tr [N·m] per unit time, is greater than or equal to a predetermined change value ΔTr_jdg. The drive torque Tr is calculated, for example, by applying the actual accelerator opening θacc and vehicle speed V to the relationship between a predetermined accelerator opening θacc and vehicle speed V and the required drive torque Trdem [N·m], which is the drive torque Tr required for the vehicle 100. The drive torque Tr of the vehicle 100 is determined based on the required drive torque Trdem. The output torque of the power source for driving is controlled to become the drive torque Tr of this vehicle 100. The predetermined vehicle speed value V_jdg, the predetermined acceleration value α_jdg, and the predetermined change value ΔTr_jdg are predetermined judgment values ​​that are experimentally or design-wise predetermined, where external vibrations may cause rattling noises in the crank mechanism 530.

[0052] According to this embodiment, (a) when the rotation angle θ is at its maximum rotation angle θmax, the intersection angle ψ is less than 180 degrees, and (b) when the crank mechanism 530 is in a non-P range state, the parking lock device 70 is switched to an unlocked state, and a backlash-reducing torque Tgata is output from the motor 26 to reduce backlash. As a result, the generation of rattling noise in the crank mechanism 530 is suppressed without the need for a biasing member.

[0053] The above-described examples are embodiments of the present invention, and the present invention can be implemented in various modified and improved forms based on the knowledge of those skilled in the art, without departing from its spirit.

[0054] The elastic members 60, 62, 64, and 66 in the aforementioned Embodiment 4 are illustrative examples, and the present invention is not limited to these embodiments. In short, when the crank mechanism 330 is in a non-P range state, it is sufficient that an elastic member is provided at a position where a biasing force F acts from one of the outer peripheral surface 36o and the inner wall surface 44i to the other in the direction of the first axis C1.

[0055] In the above-described embodiments 1 to 4, if the crank mechanisms 30, 130, 230, and 330 are in a non-P range state, and the rotation of the short lever 32 is maintained by the reluctance torque Trel or the frictional force of the elastic members 60, 62, 64, and 66, then the crank mechanisms 30, 130, 230, and 330 may be configured to allow the short lever 32 to rotate 360 ​​degrees. For example, if the short lever 32 can rotate 360 ​​degrees and the rotational path of the pin 36 is outward, then the reduction ratio of the crank mechanisms 30, 130, 230, and 330 is increased compared to the case where it is not, and the ratio of the output torque of the crank output shaft 48 to the output torque of the motor 26 is decreased. For example, when the direction of indication Dr1 is the same as the reference direction Dr0, the reduction ratio of the crank mechanisms 30, 130, 230, and 330 is increased by {(L1+L2) / (L1-L2)} times compared to when the direction of indication Dr1 is opposite to the reference direction Dr0. In other words, the ratio of the output torque of the crank output shaft 48 to the output torque of the motor 26 is reduced by {(L1-L2) / (L1+L2)} times.

[0056] In the aforementioned embodiments 1, 2, 3, 4, and 6, the intersection angle ψ was less than 180 degrees. In such embodiments, the motor 26 may not generate reluctance torque (Trel) when not in operation.

[0057] In the aforementioned embodiments 1 to 6, predetermined tightening was performed even when the crank mechanism 30, etc., was in the P range state. However, it is also possible to perform predetermined tightening only when the crank mechanism 30, etc., is not in the P range state. This is because when the crank mechanism is in the P range state, there is a lower risk of rattling noise being generated due to external vibrations compared to when it is not in the P range state.

[0058] In the above-described embodiments 1 to 6, for example, a reduction gear separate from the crank mechanism 30, etc. may be provided in the power transmission path between the motor 26 and the crank mechanism 30, 130, 230, 330, 430, 530 (hereinafter simply referred to as "crank mechanism 30, etc.") or in the power transmission path between the crank mechanism 30, etc. and the parking lock device 70. [Explanation of Symbols]

[0059] 10: Shift device, 26: Motor, 30, 130, 230, 330, 430, 530: Swivel slider crank mechanism, 32: Short lever, 40: Long lever, 50: Compression coil spring (biasing member), 56: Tension coil spring (biasing member), 58: Torsion coil spring (biasing member), 60, 62, 64, 66: Elastic member (biasing member), 70: Parking lock device, Dr1: Indication direction (predetermined indication direction of the short lever), Dr2: Indication direction (predetermined indication direction of the long lever), Trel: Reluctance torque, Tgata: Play reduction torque (predetermined torque), ψ: Crossing angle

Claims

1. A shift device comprising a motor and a swing slider-crank mechanism for reducing the rotation of the motor, which selectively switches the operating state of the parking lock device between a locked state and an unlocked state, The aforementioned oscillating slider crank mechanism comprises a short lever and a long lever, When the oscillating slider crank mechanism is in a predetermined state, the operating state of the parking lock device is switched to the unlocked state, and a predetermined tightening is performed to suppress the relative movement between the short lever and the long lever in order to suppress rattling noise between them. A shift device characterized by the following features.

2. The biasing force of the biasing member causes the predetermined packing to occur. The shift device according to feature 1.

3. When the short lever is rotated to its maximum extent, the intersection angle between the predetermined direction of the short lever and the predetermined direction of the long lever exceeds 90 degrees and is less than 180 degrees. The shift device according to feature 2.

4. When the short lever is rotated to its maximum extent, the intersection angle between the predetermined direction of the short lever and the predetermined direction of the long lever is less than 180 degrees. The motor generates reluctance torque when not in operation. The motor stops rotating when the predetermined filling position is reached by the reluctance torque. The shift device according to feature 1.

5. When the short lever is rotated to its maximum extent, the intersection angle between the predetermined direction of the short lever and the predetermined direction of the long lever is less than 180 degrees. The predetermined torque is output from the motor, thereby performing the predetermined tightening. The shift device according to feature 1.

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