JP2011042279A - Shift switching device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shift switching device capable of shortening a time from an output of a switching command requiring switching from one side to the other to the completion of the shift operation, and capable of reducing the size and the cost of an actuator device. <P>SOLUTION: A control means 70 for controlling the drive of a second shift member 10 and a regulation means 30 by a drive source 3 displaces the second shift member 10 to a standby position by the drive of the drive source 3 before a command for moving a first shift member 11 to a movement end position is output to the drive source 3, accumulates a force for moving the first shift member 11 from the standby position to the movement end position in an accumulating spring 18, and releases the regulation of the first shift member 11 by the drive source 3 when the command for moving the first shift member 11 to the movement end position is output to the drive source 3 and allows the actuation of the accumulating spring 18. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a shift switching device, and in particular, switching between two-wheel drive and four-wheel drive in a four-wheel drive vehicle, switching between a high speed and a low speed of a gear ratio of a power transmission path from a sub-transmission to a drive shaft, etc. The present invention relates to a suitable shift switching device.

  Conventionally, for example, in a part-time four-wheel drive vehicle, two-wheel high-speed drive (hereinafter referred to as “2WDH”), four-wheel high-speed drive (hereinafter referred to as “4WDH”), and four-wheel low-speed drive (hereinafter referred to as “four-wheel drive”). There is a shift transmission configured to perform switching of “4WDL” by a single actuator device (see, for example, Patent Document 1).

  The conventional shift transmission apparatus described in Patent Document 1 includes a transfer device and an actuator device. This transfer device includes a drum cam that meshes the first ring gear with the 2WD / 4WD switching clutch gear and meshes the second ring gear with the high-speed gear or the low-speed gear. First and second shift forks are connected to the first and second ring gears, respectively. On the other hand, the actuator device incorporates a speed reduction mechanism by gear means for transmitting the rotation output of the motor to the output shaft, and a drum cam is connected to the output shaft.

  A switching groove for 2WD and 4WD and a switching groove for 4WDH and 4WDL are formed on the outer peripheral surface of the drum cam. The first shift fork is locked in the 2WD / 4WD switching groove, and the first ring gear meshed with the 2WD / 4WD switching clutch gear by the rotating drum cam moves linearly along the axial direction. Driven by. A second shift fork is locked in one 4WDH / 4WDL switching groove, and a second ring gear meshing with either the high speed gear or the low speed gear by the rotating drum cam is linear along the axial direction. Driven to move.

JP 2002-295664 A

  By connecting a speed reduction mechanism or an amplification mechanism to the motor, it is possible to amplify the torque generated by the motor and increase the switching load from 2WDH to 4WDH or from 4WDH to 4WDL. However, for example, if the reduction ratio of the speed reduction mechanism is increased in order to increase the switching load, the switching speed is reduced, and the switching time from when the switching command is output to the actuator device until the shift operation is completed is increased. As a result, the size of the actuator device is determined depending on the relationship between the switching load necessary for the shift operation and the switching time, resulting in a problem that the degree of freedom in design is reduced.

  In the conventional shift transmission device described in Patent Document 1, one actuator device is used, but the switching load and the switching time necessary for the shift operation are determined by the output torque of the actuator device. If the switching load is increased and the switching time is increased, the size of the actuator device becomes large, making it difficult to reduce the size of the actuator device, and the actuator device is also expensive.

  The present invention has been made to solve the above-described conventional problems, and its specific purpose is to set the time from when a switching command for requesting switching from one to the other is output until the shift operation is completed. Provided is a shift switching device that can be shortened and can reduce the size and cost of an actuator device.

The object of the present invention can be achieved by each invention described in claims [1] to [6] of the present application.
[1] The present invention includes a first shift member that moves between first and second positions;
When the first shift member is in the first position, it is in a standby position corresponding to the second position, and when the first shift member is in the second position, the first position And when the second shift member is in the first or second standby position, the first shift member is moved to the first and second positions. A storage means for storing the moving force to be moved between, and a control means for restricting the movement of the first shift member based on the moving force and for releasing the restriction when the storage means stores the moving force. And a drive source for moving the first shift member and the second shift member, and a control means for controlling the drive source, wherein the control means moves the first shift member to the first shift member. From position to the second position or from the second position When the movement command to move the device to the first position is input, the restriction by the restriction means is released by driving the drive source, and the first shift member is moved to the first position by the moving force of the accumulation means. The shift switching device is characterized by being moved to the second position or the first position.
[2] In the invention described in [1] above, the accumulating means is an accumulator spring provided between the first shift member and the second shift member, and the restricting means A drum cam for converting the rotational motion of the drive source into a linear motion, wherein the drum cam is formed with a first cam groove and a second cam groove independently in an axial direction; A first prohibited area for prohibiting movement of the first shift member and a first allowed area for allowing movement of the first shift member are formed, and the second cam groove corresponds to the first prohibited area. A second permissible region for allowing the movement of the second shift member, and a second forbidden region for prohibiting the movement of the second shift member corresponding to the first permissible region. The shift member is engaged with the first prohibited region, and the second And the second shift member is moved to the standby position by driving the drive source to compress the accumulator spring to accumulate the moving force, The drive source is driven to engage the first shift member from the first forbidden area to the first permissible area and to engage the second shift member from the second permissible area to the second forbidden area. The first shift member is moved to the second position or the first position by the urging force of the compressed accumulating spring.
[3] In the invention described in [2] above, the first cam groove is formed between a pair of the first forbidden areas arranged in the circumferential direction between the pair of the first forbidden areas arranged in the axial direction. The second cam groove includes an end of the second permissible region extending in a circumferential direction between a pair of the second forbidden regions extending in the circumferential direction. It is characterized by a meandering concave groove connected.
[4] In the invention described in [1] or [2] above, the first shift member is a shift fork for switching between two-wheel drive and four-wheel drive, and the second shift member is The shift rod is a shift rod for moving the shift fork.
[5] In the invention described in [1] or [2] above, the first shift member is a shift fork for switching between at least a high speed stage and a low speed stage, and the second shift member is It is a shift rod for moving the shift fork.
[6] In the invention described in [1] or [2], the drive source includes a motor that can rotate forward and backward.

  According to the present invention, the time from when the command to move the shift means to the movement end position from one to the other is output to the drive source without depending on the output torque of the drive source until the shift operation is completed. In addition, the drive source can be reduced in size and cost.

It is sectional drawing which shows roughly the example of 1 structure of the shift switching apparatus which is typical 1st Embodiment based on this invention. FIG. 2 is a development view schematically showing a drum cam in FIG. 1. It is a flowchart which shows an example of the content switched to 2 wheel drive and 4 wheel drive. It is sectional drawing which shows roughly the example of 1 structure of the shift switching apparatus which concerns on 2nd Embodiment. (A) is a development view schematically showing the drum cam in FIG. 4, and (b) is a development view schematically showing a modification of the drum cam in (a). (A)-(c) is explanatory drawing which shows typically the example of 1 structure of the shift switching apparatus which concerns on 3rd Embodiment. It is sectional drawing which shows roughly the example of 1 structure of the shift switching apparatus which concerns on 4th Embodiment. (A) And (b) is explanatory drawing for demonstrating operation | movement of the shift switching apparatus shown in FIG.

[First Embodiment]
(Configuration of shift switching device)
In FIG. 1, reference numeral 1 shown as a whole is the shift switching device in the first embodiment. The shift switching device 1 according to the illustrated example is applied to, for example, switching to two-wheel drive / four-wheel drive (2WD / 4WD) in a part-time four-wheel drive vehicle based on the FR (front engine, rear drive) system. The transfer device 2 and the actuator device 3 are provided.

(Configuration of transfer device)
As shown in FIG. 1, the transfer device 2 includes a main shaft 6 that transmits engine driving force input to an input shaft (not shown) in a case including a front case 4 and a rear case 5. The transfer device 2 further includes a 4WD gear (clutch gear) 7 spline-fitted on the outer periphery of the main shaft 6, a 2WD gear (sprocket teeth) 8 formed on the outer periphery of the main shaft 6 so as to be relatively rotatable, and 2WD. A sleeve clutch 9 that meshes with the 2WD gear 8 when selected, and meshes with both the 4WD and 2WD gears 7 and 8 when 4WD is selected, and a cylindrical drum cam 30 are provided. Two shift means including the shift rod 10 and the shift fork 11 are engaged with each of the first and second cam grooves 31 and 32 formed independently on the outer peripheral surface of the drum cam 30.

  As shown in FIG. 1, the shift rod 10 switches the shift fork 11 between a 4WD position and a 2WD position, and is supported between the front case 4 and the rear case 5 so as to be able to reciprocate. A cylindrical shift bracket 12 is fixed to the shift rod 10 by a spring pin 13. On the outer periphery of the shift bracket 12, a cylindrical boss portion 11a formed on the shaft portion of the shift fork 11 is externally supported so as to reciprocate in the axial direction. A pair of upper and lower cutout slits 11b and 11b are formed in the axial direction at the opening end of the boss portion 11a on the front case 4 side. In the cutout slits 11 b and 11 b, the tip of the spring pin 13 protrudes and restricts the movement of the shift fork 11 about the axis relative to the shift rod 10.

  As shown in FIG. 1, one shift fork 11 performs gear switching between the 4WD gear 7 and the 2WD gear 8 and is engaged with the sleeve clutch 9. The cylindrical portion of the boss portion 11a of the shift fork 11 includes a small diameter cylindrical portion 11c on the front case 4 side and a large diameter cylindrical portion 11d on the rear case 5 side. A pair of collar members 14 and 15 having an annular shape are fitted on both sides in the axial direction of the large-diameter cylindrical portion 11d.

  As shown in FIG. 1, the collar member 15 on the front case 4 side is locked to an annular support surface formed between the small diameter cylindrical portion 11c and the large diameter cylindrical portion 11d. The movement of the axis direction to is regulated. One rear case 5 side collar member 14 is locked to a snap ring 16 fitted to the large-diameter cylindrical portion 11d and to a snap ring 17 fitted to the outer periphery of the shift rod 10, The movement in the axial direction toward the rear case 5 is restricted.

  A spring 18 is interposed in the annular space formed between the shift rod 10, the shift fork 11, and the collar members 14 and 15, as shown in FIG. With such a structure, a force accumulation mechanism by a spring that temporarily stores the elasticity of the spring 18 that compresses regardless of whether the relative movement direction of the shift rod 10 and the shift fork 11 is normal or reverse, and transmits the stored stress to the sleeve clutch 9 Is configured. Instead of the spring 18, for example, a spring mechanism such as a disc spring or a leaf spring, or a fluid pressure mechanism such as a cylinder can be used.

  As a motion conversion mechanism that converts the rotational motion of the actuator device 3 into a linear motion, a drum cam 30 is used as shown in FIG. The first cam groove 31 of the drum cam 30 is engaged with a fork drive pin 11e protruding from the boss portion 11a of the shift fork 11 for switching between 2WD and 4WD. Is linearly moved in the axial direction.

  As shown in FIG. 1, the shift bracket 12 of the shift rod 10 is engaged with the second cam groove 32 for switching between the 4WD position and the 2WD position. In the illustrated example, the shift bracket 12 is provided with an arm 12a projecting from the axial direction toward the drum cam. A rod drive pin 12b, which is arranged offset by a desired distance with respect to the end face of the shift bracket, is engaged with the second cam groove 32 at the tip of the arm portion 12a, and the shift rod 10 is linear in the axial direction. It is supposed to move.

(Configuration of actuator device)
As shown in FIG. 1, the actuator device 3 rotates the drum cam 30 connected to the output shaft 21 via the drive rod 22 to move the shift rod 10 linearly in the axial direction. A motor 20 built in the housing is provided, and a reduction mechanism using gear means (not shown) for reducing the rotational output of the motor 20 and transmitting it to the output shaft 21. In the actuator device 3, the control unit 70 receives a signal to rotate the drive rod 22 in the forward / reverse direction, and the motor 20 rotates the drive rod 22 in the forward / reverse direction.

  The actuator device 3 is not particularly limited as long as the rotation output of the motor 20 is decelerated and the rotation output is transmitted to the output shaft 21 side. As another example of the drive source, for example, an electromagnetic SOL or a mechanical lever can be applied. Note that the components of the shift switching device 1 configured as described above are not different from the conventional ones in the basic configuration. Therefore, it is needless to say that the present invention is not limited to the illustrated example.

(Drum cam configuration)
Referring to FIG. 2, the first cam groove 31 of the drum cam 30 having the features of the first embodiment includes a 2WD stop region A ₁ B ₁ having a 2WD shift completion position (movement end position) A ₁ , and A 4WD stop area C ₁ D ₁ having a 4WD shift completion position (movement end position) C ₁ is formed in two stages, and between the 2WD stop area A ₁ B ₁ and the 4WD stop area C ₁ D ₁ , 2WD · Each of the 4WD switching region B ₁ C ₁ and the 4WD / 2WD switching region D ₁ A ₁ is formed in an annular concave groove connecting the end portions. The 2WD / 4WD switching area B ₁ C ₁ and the 4WD / 2WD switching area D ₁ A ₁ are movement permission areas in which the shift fork 11 is allowed to move in the axial direction. The other 2WD stop areas A ₁ B ₁ and 4WD stop area C ₁ D ₁ are movement prohibited areas that restrict the movement of the shift fork 11 in the axial direction.

As shown in FIG. 2, the first cam groove 31 uses the 2WD stop area A ₁ B ₁ and the 2WD / 4WD switching area B ₁ C ₁ as the forward path as the first movement restricting means when the drum cam 30 rotates forward. In the reverse rotation of the drum cam 30, the 4WD stop area C ₁ D ₁ and the 4WD / 2WD switching area D ₁ A ₁ are used as the return path as the second movement restricting means, and the fork drive pin 11e is moved forward and backward.

As shown in FIG. 2, the 2WD stop area A ₁ B ₁ is linearly formed along the circumferential direction from the 2WD shift completion position A ₁ to the start end (4WD standby position) B _{1 of the} 2WD / 4WD switching area B ₁ C _1. It is set to extend. The 2WD / 4WD switching region B ₁ C ₁ is set to extend incline along the circumferential direction from the 4WD standby position B ₁ to the 4WD shift completion position C ₁ .

As shown in FIG. 2, the 4WD stop area C ₁ D ₁ is a 2WD stop area A ₁ B from the 4WD shift completion position C ₁ toward the start end (2WD standby position) D _{1 of the} 4WD / 2WD switching area D ₁ A _{1. 1} is set so as to extend in a straight line parallel to ₁ . 4WD · 2WD switching region _D 1 _{A 1} is set so as to extend with a 2WD standby position _{D 1} 2WD shift completion position _{A 1} to 2WD · 4WD switching region _B 1 _{C 1} and the same inclination angle (inclined cam face) .

In the first cam groove 31, as shown in FIG. 2, the width between the 2WD shift completion position A ₁ and the 4WD shift completion position C ₁ is the shift stroke of the shift fork 11. To move the shift fork 11, the 2WD standby position _{D 1} to the 2WD shift completion position _{A 1,} or well from 4WD standby position _{B 1} simply by rotating the drum cam 30 to 4WD shift completion position _{C 1,} the drum cam 30 A small rotation angle is sufficient.

On the other hand, as shown in FIG. 2, the second cam groove 32 of the drum cam 30 has a 2WD drive stop position A ₂ and a 4WD drive stop position C ₂ formed in two stages, and a 2WD drive stop area A ₂ D _2. (D ₂ A ₂ ) and 4WD drive stop region B ₂ C ₂ (C ₂ B ₂ ), and 2WD drive stop region A ₂ D ₂ (D ₂ A ₂ ) and 4WD drive stop region B ₂ C ₂ ( C ₂ B ₂ ) is formed in a meandering concave groove as a switching drive region D ₂ B ₂ (B ₂ D ₂ ). The 2WD drive stop area A ₂ D ₂ is set to extend linearly along the circumferential direction corresponding to the 4WD / 2WD switching area D ₁ A _{2 of} the first cam groove 31. The 4WD drive stop region B ₂ C ₂ is set so as to extend linearly along the circumferential direction corresponding to the 2WD • 4WD switching region B ₁ C _{1 of} the first cam groove 31. The second cam groove 32 is a reciprocating path when the drum cam 30 rotates forward and backward, and is configured to advance and retract the rod drive pin 12b.

As shown in FIG. 2, the second cam groove 32 is driven to switch between the 2WD drive stop area A ₂ D ₂ (D ₂ A ₂ ) and the 4WD drive stop area B ₂ C ₂ (C ₂ B ₂ ). In the range of region D ₂ B ₂ (B ₂ D ₂ ), a cam slope that is displaced by the shift stroke is provided. When the rod drive pin 12b moves on this cam slope, the fork drive pin 11e is on the 2WD stop region A ₁ B ₁ and the 4WD stop region C ₁ D ₁ of the first cam groove 31 and cannot move in the axial direction. One of the collar members 14 and 15 compresses the spring 18. By prohibiting the movement of the fork drive pin 11e in the 2WD standby position D ₁ and 4WD standby position B ₁ of the first cam groove 31, the state (pre-winding state of the energy accumulated in the spring 18 for the next shift ).

(Operation of shift switching device)
The configuration having another characteristic part of the shift switching device 1 according to the illustrated example is that the shift is performed on the drive transmission path from the motor 20 to the sleeve clutch 9 before the command to move the sleeve clutch 9 to the movement end position is output. A force accumulation mechanism that stores in the spring 18 a necessary force to move the fork 11 to the standby position and move the shift fork 11 from the standby position to the movement end position, and the drum cam 30 that regulates the operation of the force accumulation mechanism. And a shift restricting mechanism. The power accumulation mechanism and the shift restriction mechanism are capable of accumulating (pre-winding) regardless of whether the engine is stopped, the engine is restarted, the vehicle is running 2WD, the vehicle is running 4WD, or the vehicle is temporarily stopped. State) is always maintained.

In the illustrated example, a switching command signal is output to the actuator device 3 and is shifted to the movement end position of either the 2WD shift completion position A ₁ or the 4WD shift completion position C ₁ in the first cam groove 31 of the drum cam 30. Before moving the fork 11, by moving the rod drive pin 12b of the shift rod 10 on the switching drive region D ₂ B ₂ (B ₂ D ₂ ) of the second cam groove 32 by rotational driving of the motor 20, displacing the fork drive pin 11e of 2WD standby position _{D 1} or 4WD standby position _{B 1} on the shift fork 11 of the first cam groove 31. Thus, the shift fork 11 is set aside the force required to move from the 4WD standby position _{B 1} 4WD shift completion position _{C 1,} or from 2WD standby position _{D 1} to 2WD shift completion position _{A 1} to the accumulating mechanism.

When the shift fork 11 is moved to either the 2WD shift completion position A ₁ or the 4WD shift completion position C ₁ , the 2WD shift is performed from the 2WD standby position D ₁ of the first cam groove 31 by the rotational drive of the motor 20. to completion position _{a 1,} or move the fork drive pin 11e of the shift fork 11 from the 4WD standby position _{B 1} to 4WD shift completion position _{C 1,} to release the axial regulation. Thus, the sleeve clutch 9 is switched by the switching force stored in the power storage mechanism.

(Drum cam operation)
Table 1 shows the relationship between the shift position of the drum cam 30 and the switching mode of the shift rod 10 and the shift fork 11. Here, the shift positions A to D shown in Table 1 are the cam positions A _{1 to} D ₁ of the first cam groove 31 of the drum cam 30 and the cam positions A _{2 to} D _{2 of} the second cam groove 32 shown in FIG. Each corresponds.

(Wait for switching to 2WD-4WD)
Referring to FIG. 3, FIG. 3 illustrates a procedure for switching to 2WD and 4WD. Until the fork drive pin 11e reaches 4WD shift completion position _{C 1,} the sleeve clutch 9 of the shift fork 11 is in the 2WD state not engaged with the 4WD gear 7 (step S1 shown in FIG. 3, the shift shown in Table 1 Position A). When this is in the 2WD state, is forward rotated clockwise the output shaft 21 and the drive rod 22 within a range extending from 2WD shift completion position _{A 1} to the 4WD standby position _{B 1} (S2 in Fig. 3). Then, the rod drive pin 12b is switched from 2WD drive stop region _A 2 _{D 2} of the second cam groove 32 via the inclined cam face of the driving region _D 2 _{B 2} to move to the 4WD driving standby position _{B 2,} the shift rod 10 is Move to the right in FIG. On the other hand, since the fork drive pin 11e is displaced on the 2WD stop region A ₁ B ₁ , the shift fork 11 is prohibited from moving. From the above, the shift rod 10, the spring 18 is compressed by the 4WD driving standby position _{B 2} of the second cam groove 32, by the restoring force of the compressed spring 18 (biasing force), the shift fork 11 4WD shift completion position C accumulated force while urged ₁ side is stopped at the 4WD standby position B ₁ in (pre winding state) (S3 in FIG. 3, the shift position of the above table 1 B).

(Completion of shift to 2WD-4WD)
When switch switched from 2WD to 4WD command is output to the actuator unit 3 (in FIG. 3 S4), the output shaft 21 and the drive rod 22 from the 4WD standby position _{B 1} of the first cam groove 31 to the 4WD shift completion position _{C 1} It is forwardly rotated clockwise in the range extending to rotate the drum cam 30 from 4WD standby position _{B 1} to 4WD shift completion position _{C 1} (S5 in FIG. 3). Rod drive pin 12b is displaced from the 4WD driving standby position _{B 2} of the second cam groove 32 in the 4WD drive stop position _{C 2.} On the other hand, when the sleeve clutch 9 of the shift fork 11 is synchronized with the 4WD gear 7, the fork drive pin 11 e is moved via the 4WD drive stop region B ₁ C ₁ of the first cam groove 31 by the restoring force of the spring 18. since becomes, the shift fork 11 that has been in a standby state at the 4WD standby position _{B 1} represents Waru switched from 4WD standby position _{B 1} instantly 4WD shift completion position _{C 1} (S6 in FIG. 3).

  When the sleeve clutch 9 moves to the 4WD gear 7 side, the sleeve clutch 9 rotates synchronously with the 4WD gear 7 and the 2WD gear 8, so that the power of the rotating main shaft 6 is the 2WD gear 8 and the sleeve. It is transmitted to the chain and front shaft (not shown) meshed with the 4WD gear 7 via the clutch 9 and the 4WD gear 7, and is switched from 2WD to 4WD for rotation (S7 in FIG. 3, shift position in Table 1 above) C).

(Standby for switching to 4WD-2WD)
When the fork drive pin 11e is electrically detected by position switch is a rotary position detecting means that turn from 4WD shift completion position C ₁ of the first cam groove 31, 4WD shift the output shaft 21 and the drive rod 22 It is reversely rotated counterclockwise in a range extending from the completion position _{C 1} to 2WD standby position _{D 1} (S8 in FIG. 3). Then, the rod drive pin 12b moves from the 4WD drive stop area C ₂ B _{2 of} the second cam groove 32 to the 2WD drive standby position D ₂ via the cam slope of the switching drive area B ₂ D ₂ , and the shift rod 10 , Move leftward in FIG. On the other hand, since the fork drive pin 11e is displaced on the 4WD stop region C ₁ D _{1 of} the first cam groove 31, the shift fork 11 is prohibited from moving. From the above, the shift rod 10 stands in accumulated force while compressing the spring 18 (pre-winding state) in 2WD driving standby position D _2, shift fork 11, 2WD shift completion position by the restoring force of the compressed spring 18 in the waiting state of being urged a ₁ side stops the 2WD standby position _{D 1} (S9, the shift position of the above table 1 D in FIG. 3).

(Shift to 4WD-2WD completed)
From 4WD when switching command switch to 2WD is output to the actuator unit 3 (in FIG. 3 S10), the output shaft 21 and the drive rod 22 from the 2WD standby position _{D 1} of the first cam groove 31 to the 2WD shift completion position _{A 1} It is reversely rotated in a range extending to rotate the drum cam 30 from 2WD standby position _{D 1} of the first cam groove 31 to the 2WD shift completion position _{a 1} (S11 in FIG. 3). Rod drive pin 12b is displaced from 2WD driving standby position _{D 2} in 2WD driving stop position _{A 2.} On the other hand, the sleeve clutch 9 of the shift fork 11 by the restoring force of the spring 18 is removed from the 4WD gear 7, to move the fork drive pin 11e from 2WD standby position _{D 1} of the first cam groove 31 to the 2WD shift completion position _{A 1} since thus, the shift fork 11 that has been in a stopped state in 2WD standby position _{D 1} is switched to 2WD shift completion position _{a 1} instantly from 2WD standby position _{D 1} by the restoring force of the spring 18 (S12 in FIG. 3, Shift position A) in Table 1 above.

When the fork drive pin 11e is electrically detected by position switch that turn from 2WD shift completion position _{A 1} of the first cam groove 31, the output shaft 21 and the drive rod 22 4WD from 2WD shift completion position _{A 1} positive rotation at a range extending to the standby position B _1. Then, the rod drive pin 12b moves from the 2WD drive stop area A ₂ D ₂ of the second cam groove 32 to the 4WD drive standby position B ₂ through the cam slope of the switching drive area D ₂ B ₂ , so the 4WD drive standby position It waits in accumulated force while compressing the spring 18 (pre-winding state) at B _2. On the other hand, since the fork drive pin 11e is displaced on the 2WD stop region D ₁ B ₁ of the first cam groove 31, the movement of the shift fork 11 and the sleeve clutch 9 is prohibited, and 4WD is generated by the restoring force of the compressed spring 18. in accumulated force while urging the shift completion position _{C 1} side stops the 4WD standby position _{B 1} (S13 in FIG. 3, S1 to S3, the shift position of the above table 1 B). By repeating the above operation, a shift operation from 2WD to 4WD or from 4WD to 2WD is effectively performed.

(Effects of the first embodiment)
According to the shift switching device 1 according to the first embodiment configured as described above, the following effects are obtained.
(1) and 2WD stopping area _A 1 _{B 1} from 2WD shift completion position _{A 1} of the first cam groove 31 to the 4WD standby position _{B 1,} 2WD standby position _{D 1} from 4WD shift completion position _{C 1} of the first cam groove 31 Up to the 4WD stop region C ₁ D ₁ until the shift fork 11 switching command is output to the actuator device 3, energy for moving the shift fork 11 is stored in the spring 18. . Therefore, the time from when the switching command for requesting switching from one to the other is output until the shift operation is completed (shift time of the shift fork 11) is not affected by the output torque of the motor 20, and is the first. Only a slight rotational displacement of the 4WD / 2WD switching area D ₁ A ₁ or 2WD / 4WD switching area B ₁ C ₁ of the cam groove 31 and the release time of the spring 18 are required.
(2) Since the release time of the spring 18 is negligibly short, the shift time of the shift fork 11 is the 4WD / 2WD switching region D ₁ A ₁ or the 2WD / 4WD switching region B ₁ C of the first cam groove 31. can be determined by the _first rotation angle and the rotation speed and the result, without depending on the driving force of the actuator device as in the conventional shift switching device, it is possible to shorten the shifting time of the shift fork 11.
(3) The rotation angle of the 2WD / 4WD switching region B ₁ C ₁ or the 4WD / 2WD switching region D ₁ A ₁ of the first cam groove 31 is, for example, ₁ with respect to the rotation angle of the entire shift stroke of the shift fork 11. When set to / 5, the rotational speed of the output shaft 21 of the actuator device 3 required for the shift can be reduced to 1/5. When the shift time is set to be the same as that of the conventional device, the gear ratio in the actuator device 3 can be increased by a factor of 5, and the output torque of the motor 20 alone can be reduced to 1/5.
(4) As described above, the actuator device 3 and the motor 20 can be reduced in size and cost.

[Second Embodiment]
The shift switching device 1 configured as described above can be effectively applied to the auxiliary transmission mechanism 40 having at least a low speed stage and a high speed stage.

  Referring to FIG. 4, FIG. 4 schematically shows a sub-transmission using the shift switching device according to the first embodiment. In addition, the same member name and code | symbol are attached | subjected to the member substantially the same as the said 1st Embodiment. Therefore, a detailed description of substantially the same members as those in the first embodiment is omitted.

(Sub-transmission configuration)
In FIG. 4, reference numeral 23 shown as a whole schematically shows an auxiliary transmission mechanism that switches the driving force of the engine input to the input shaft 24 between the high speed stage H and the low speed stage L. The auxiliary transmission 23 is applied to switching to a high speed position and a low speed position in a part-time four-wheel drive vehicle based on the FR system, for example, and is coaxial with the planetary gear mechanism 25 and the planetary gear mechanism 25. The slide gear 26 is provided.

  As shown in FIG. 4, the planetary gear mechanism 25 includes a high speed gear (sun gear) 27 formed on the outer periphery of the input shaft 24 and a low speed gear (pinion) arranged concentrically on the outer periphery of the sun gear 27. Gear) 28 and a ring gear 29 arranged concentrically on the outer periphery of a sun gear 27 that meshes with the pinion gear 28. In the high speed state, the slide gear 26 and the high speed gear 27 mesh with each other, whereby the rotational driving force of the input shaft 24 is transmitted to the main shaft 6 as a high speed rotational driving force. On the other hand, in the low speed state, the slide gear 26 is detached from the high speed gear 27, so that the rotational driving force of the input shaft 24 is formed as a low speed rotational driving force from the input shaft 24 to the shaft 28a of the low speed gear 28. It is transmitted to the main shaft 6 via the gear 28b.

  As shown in FIG. 4, the fork drive pin 11 e of the shift fork 11 that switches between the high speed stage H and the low speed stage L is engaged with the first cam groove 31 of the drum cam 30. A rod drive pin 12b is engaged with the second cam groove 32 of the drum cam 30 for switching between a high speed drive position and a low speed drive position. A slide gear 26 engaged with either the high speed gear 27 or the low speed gear 28 is linearly moved in the axial direction by the shift fork 11. When switching between the high speed stage H and the low speed stage L, it is switched to the neutral N as an intermediate position.

  The components of the auxiliary transmission mechanism 23 configured as described above are not different from the conventional ones in the basic configuration. Therefore, it is not limited to the illustrated example. Even in the second embodiment, the shift fork 11 is set to the standby position before the command for moving the slide gear 26 to the movement end position is output on the drive transmission path from the motor 20 to the slide gear 26. Displacement of the shift fork 11 from the standby position to the movement end position is stored in the spring 18 and a shift restricting mechanism by the drum cam 30 that restricts the operation of the force storing mechanism. It has a feature. As in the first embodiment, the power storage mechanism and the shift restriction mechanism always maintain the power storage state.

(Drum cam configuration)
Referring to FIG. 5 (a), FIG. 5 (a) is a developed view of the drum cam 30 for speed position switching in which the first cam groove 31 and the second cam groove 32 of two systems are independently drilled. Has been shown. In the switching between 2WD and 4WD in the first embodiment, the switching load applied when the shift fork 11 is pulled out from each position of the 2WD position or the 4WD position is applied by the spring force. In this embodiment, the switching load when the shift fork 11 is pulled out from each position of the high speed position and the low speed position is applied by the driving force of the actuator device 3, and the switching destination is switched from the neutral position N between the high speed position and the low speed position. The switching load when entering the position is applied by the spring force.

  The stroke of the spring force may be a distance obtained by adding the distance of the gear meshing region of either the slide gear 26 and the high speed gear 27 or the low speed gear 28 to the distance of the neutral region. The spring force is preferably set larger than the required switching load.

The first cam groove 31 of the drum cam 30 according to the illustrated example has a high speed / low speed switching area (movement permission area) having a high speed area (movement prohibited area) A ₃ B ₃ and a high / low speed neutral position C ₃ when the drum cam 30 is rotated forward. B ₃ D ₃ is the forward path which is the first movement restricting means, and in the reverse rotation of the drum cam 30, a low speed switching area (movement permission area) having a low speed area (movement prohibition area) D ₃ E ₃ and a low speed high speed neutral position F ₃ ) E ₃ A ₃ is a return path as the second movement restricting means, and is formed in an annular concave groove so as to reciprocate the fork drive pin 11e.

As shown in FIG. 5A, the high speed region A ₃ B ₃ of the first cam groove 31 is set to extend linearly along the circumferential direction. The high / low speed switching region B ₃ C ₃ is set to extend from the end of the high speed region A ₃ B ₃ (high / low speed switching standby position B ₃ ) to the high / low speed neutral position C ₃ . The high / low speed neutral region C ₃ D ₃ is set to extend linearly from the high / low speed neutral position C ₃ to the low speed position (shift completion position) D ₃ along the axial direction.

As shown in FIG. 5A, the low speed region D ₃ E ₃ of the first cam groove 31 is set to extend linearly along the circumferential direction in parallel with the high speed region A ₃ B ₃ . The low and high speed switching area E ₃ F ₃ extends from the end of the low speed area D ₃ E ₃ (low high speed switching standby position E ₃ ) to the low and high speed neutral position F ₃ with the same inclination angle as the high and low speed switching area B ₃ C _3. Is set to The low and high speed neutral region F ₃ A ₃ is linearly formed from the low and high speed neutral position F ₃ to the high speed position A _{3 in} parallel with the high and low speed neutral region C ₃ D ₃ .

On the other hand, as shown in FIG. 5A, the second cam groove 32 of the drum cam 30 has a high-speed drive position (shift completion position) A ₄ (F ₄ ), a speed switching standby position B ₄ (E ₄ ), The low speed drive position (shift completion position) C ₄ (D ₄ ) is formed in three stages. A speed switching area (movement permission area) A ₄ B ₄ (E ₄ F ₄ ) between a high-speed drive position A ₄ (F ₄ ) and a speed switching standby position B ₄ (E ₄ ), and a speed switching standby position B ₄ ( E ₄ ) and a speed switching area (movement permission area) B ₄ C ₄ (D ₄ E ₄ ) between the low-speed drive position C ₄ (D ₄ ) and the circumferential direction extend with the same inclination angle. It is formed as follows.

(Drum cam operation)
Table 2 shows the relationship between the shift position of the drum cam 30 and the switching mode of the shift rod 10 and the shift fork 11. Here, the shift positions A to F shown in Table 2 are the cam positions A _{3 to} F ₃ of the first cam groove 31 and the cam positions A _{4 to} F _{4 of} the second cam groove 32 shown in FIG. Each corresponds.

(Low speed switching standby)
Fork drive pin 11e is to reach the low speed position D ₃ from the high-low speed switching waiting position B ₃ through the high and low speed neutral position C ₃ of the first cam groove 31, shift fork 11 is in a high speed state meshing with the sun gear 27 ( Shift position A) shown in Table 2 above. When the fork drive pin 11e is displaced to the high speed position _{A 3} from high- and low-speed switching waiting position _{B 3} of the first cam groove 31, the rod drive pin 12b, the second cam speed switching area _A 4 _{B 4} of the cam groove 32 since moving the inclined surface, is stopped at the speed switching waiting position B ₄ in accumulated force while urging to the low-speed drive position D ₄ side (pre-winding state) by the restoring force of the compressed spring 18 (table 2 Shift position B) shown in FIG.

(Low speed switching completed)
When switching instruction switches to low-speed driving of the high-speed driving is output to the actuator unit 3, the positive range to reach the output shaft 21 and the drive rod 22 from the high and low speed switching waiting position B ₃ of the first cam groove 31 to the low speed position D ₃ rotate, high and low speed switching fork drive pin 11e that has been in a stopped state at the standby position B ₃ is a high-low speed switching waiting position B ₃ of the first cam groove 31 by rotation of the motor 20 through the high and low speed neutral position C ₃ It moved to the low speed position _{D 3.}

One rod drive pin 12b, so the speed switching waiting position B ₄ of the second cam groove 32 via the low-speed driving region moves to the low-speed drive position D _4, the shift rod 10 moves rightward in FIG. 4 However, unlike the 2WD-4WD switching in the first embodiment, the cam slope of the speed switching region B ₄ C ₄ of the second cam groove 32 is the high / low speed switching region B ₃ C of the first cam groove 31. _The rod drive pin 12 b is moved at the same inclination angle as ₃ . Therefore, the fork drive pin 11e is moved to the high-low speed neutral position C ₃ in a state of holding the shift force accumulated in the spring 18 is force accumulating mechanism.

When the fork drive pin 11e is moved to the high and low speed neutral position C ₃ of the first cam groove 31, the engagement of the slide gear 26 of the shift fork 11 that shift movement becomes unloaded state deviates, restoration of compressed spring 18 the force moves immediately fork drive pin 11e to the low speed position D ₃ of the first cam groove 31, completing the movement of the shift fork 11 (shift position C and D shown in table 2).

(High-speed switching standby)
Fork drive pin 11e is switched to the low speed position D ₃ of the first cam groove 31, the electrically detected by position switch that shifted completed, the output shaft 21 and the drive rod 22 of the first cam groove 31 slow reversely rotated within a range extending from the position D ₃ to the low-high-speed switching standby position E _3. Rod drive pin 12b moves to the second speed switching standby position E ₄ from the low-speed drive position D ₄ through the inclined cam face of the speed switching region D ₄ E ₄ of the cam groove 32. Shift rod 10, so moves leftward in FIG. 4, and waits with accumulated force while compressing the spring 18 in the standby position E ₄ The speed switching (pre winding state). One fork drive pin 11e from being displaced on the standby position E ₃ from the low speed position D ₃ low fast switching of the first cam groove 31, prohibits the movement of the slide gear 26 of the shift fork 11, the compressed spring 18 of stops in the standby state of urging the high speed position a ₃ side of the first cam groove 31 by the restoring force to the low-high speed switching standby position E ₃ (shift position E shown in table 2).

(High-speed switching completed)
When switching instruction switching to high-speed drive from a low-speed driving is output to the actuator unit 3, the reverse range throughout the output shaft 21 and the drive rod 22 from the low high speed switching standby position E ₃ of the first cam groove 31 to the high speed position A ₃ The drum cam 30 is rotated from the low-high speed switching standby position E ₃ of the first cam groove 31 to the high speed position A ₃ . Unlike switching of 2WD-4WD in the first embodiment, the rod drive pin 12b through the inclined cam face of the speed switching area _E 4 _{F 4} from speed switching standby position _{E 4} of the second cam groove 32 slow move to drive position _{a 4.} The cam inclined surface of the speed switching area E ₄ F ₄ of the second cam groove 32 moves the rod driving pin 12 b at the same inclination angle as the low-speed switching area E ₃ F _{3 of} the first cam groove 31, so that the fork driving pin 11e is moved to the lower high-speed neutral position F ₃ in a state of holding the shift force accumulated in the spring 18 is force accumulating mechanism.

Fork drive pin 11e that has been in a stopped state at low fast neutral position F ₃ is, deviates from the sun gear 27, the restoring force of the spring 18, to move the fork drive pin 11e to the high speed position A ₃ of the first cam groove 31 since becomes immediately low fast neutral position F ₃ switched to the high speed position a ₃ from (shift position shown in table 2 F and a) by the restoring force of the spring 18.

(Low speed switching standby)
When the fork drive pin 11e is electrically detected by position switch that turn from the high speed position A ₃ of the first cam groove 31, the high speed position A ₃ of the first cam groove 31 of the output shaft 21 and the drive rod 22 from high and low speed switching is rotated in a range extending to the standby position B _3, to rotate the drum cam 30 from the high speed position a ₃ to the high-low speed switching waiting position B _3. Rod drive pin 12b is moved to the standby position B ₄ switching speed through the cam slope region A ₄ B ₄ switching speed from the high speed drive position A ₄ of the second cam groove 32. Fork drive pin 11e of fast position A ₃ was stopped in the first cam groove 31, by the rotation of the motor 20 is displaced from the high speed position A ₃ in high and low speed neutral position B ₃ (shift position shown in Table 2 B). By repeating the above operation, a shift operation from high speed drive to low speed drive or from low speed drive to high speed drive is effectively performed.

(Effect of the second embodiment)
According to the shift switching device 1 according to the second embodiment configured as described above, the following effects can be obtained.
(1) The high / low speed switching region B ₃ D ₃ from the high / low speed neutral position B ₃ to the low speed position D ₃ of the first cam groove 31 and the low / high speed switching standby position E _{3 of} the first cam groove 31 to the high speed position A ₃ In the low and high speed switching region E ₃ A ₃ until the shift fork 11 switching command is output to the actuator device 3, energy for moving the shift fork 11 is stored in the spring 18. . Therefore, the shift time of the shift fork 11 can be determined by the rotation angle and the rotation speed of the low-speed neutral region F ₃ A _{3 of} the first cam groove 31 or the high-low speed neutral region C ₃ D ₃ .
(2) When the gear ratio in the actuator device 3 is set to double, the output torque of the motor 20 alone can be halved. As a result, the motor 20 can be reduced in size and cost.
(3) From the above, as in the first embodiment, it is not necessary to depend on the driving force of the actuator device as in the conventional shift switching device, and the shift time of the shift fork 11 can be shortened. Thus, the actuator device 3 can be reduced in size and cost.

(Modification of drum cam)
Referring to FIG. 5B, FIG. 5B schematically shows a modified example of the drum cam 30 according to the second embodiment. In addition, the same member name and code | symbol are attached | subjected to the member substantially the same as the said 2nd Embodiment. Therefore, the detailed description regarding the substantially same member as the said 2nd Embodiment is abbreviate | omitted.

In the second embodiment, the switching load when the shift fork 11 is pulled out from each of the high speed position A ₃ and the low speed position D ₃ of the first cam groove 31 is applied by the driving force of the actuator device 3. In this modification, the first embodiment has been described in which a switching load is applied by a spring force when entering the switching destination position from the neutral position N between the high speed position A ₃ and the low speed position D ₃ . Similarly to the switching of 2WD-4WD in the embodiment, the switching load when the shift fork 11 is pulled out from each of the high speed position A ₃ and the low speed position D ₃ of the first cam groove 31 is applied by the spring force.

  According to FIG.5 (b), the stroke of the spring force of an energy storage mechanism is set longer than the stroke of the spring force of the said 2nd Embodiment. Even in this modification, the spring force is set so that the shift operation from the high-speed drive to the low-speed drive or from the low-speed drive to the high-speed drive can be performed effectively, as in the second embodiment. is doing.

[Third Embodiment]
With reference to FIGS. 6A to 6C, these drawings schematically show one configuration example of the shift switching device 1 according to the third embodiment. In the first and second embodiments, the shift switching device 1 including the motion conversion mechanism that can convert the rotational motion of the drum cam 30 into a linear motion is illustrated. However, in the third embodiment, The second embodiment is different from the first and second embodiments in that the shift switching device 1 including a motion conversion mechanism capable of converting the rotational motion of the shaft into the rotational motion is illustrated.

(Configuration of motion conversion mechanism)
In FIG. 6A to FIG. 6C, the regulating member 41 that is slidably supported by the support member 40 is provided in parallel along the axial direction of the input rotation shaft 42 and the output rotation shaft 46. First and second springs 43 and 44 are interposed on both sides in the axial direction of the restricting member 41, and the elasticity of the springs 43 and 44 compresses even if the drive rotation direction of a motor (not shown) is normal or reverse. Is temporarily stored, and a force storage mechanism is configured by a spring that transmits the stored stress to the regulating member 41.

  As shown in FIGS. 6A and 6B, a cam groove 45 for moving the regulating member 41 forward and backward along the axial direction is formed on a part of the outer periphery of the input rotation shaft 42. The cam groove 45 extends between the first and second rotation restricting regions (movement prohibition regions) 45a and 45b extending linearly along the axial direction so as to incline along the circumferential direction. Two switching regions (movement permission regions) 45c and 45d are formed in annular concave grooves so as to connect the end portions thereof.

  The cam groove 45 has a first movement restricting means in a range from the start end (first shift completion position) of the first switching region 45c to the end of the second rotation restricting region 45b during forward rotation (clockwise) of the motor. In the reverse rotation of the motor, the range from the start end (second shift completion position) of the second switching area 45d to the end of the first rotation restriction area 45a is the return path as the second movement restriction means. The input rotation shaft 42 and the output rotation shaft 46 are configured to rotate forward and backward.

  As shown in FIGS. 6A and 6C, the input rotation shaft 42 and the output rotation shaft 46 are arranged on the same axis so as not to be relatively rotatable. An annular first ring collar 47 that engages and disengages with the regulating member 41 is formed on the outer periphery of the output rotation shaft 46. On the outer peripheral end face of the ring collar 47, there are formed first and second locking holes 47a and 47b that are cut out in a rectangular shape with a phase difference of 45 degrees. A second ring collar 48 corresponding to the first ring collar 47 is formed on the outer periphery of the other portion of the input rotation shaft 42. The ring collars 47 and 48 hold both ends of a spring 49 interposed on the outer periphery of the input rotary shaft 42.

(Operation of motion conversion mechanism)
Now, as shown in FIGS. 6A and 6B, the input rotating shaft 42 is moved from the first locking hole 47a of the first ring collar 47 to the second locking hole 47b by the forward rotation of the motor. When the clockwise rotation is performed in the clockwise direction, the first engagement pin 41a of the regulating member 41 is moved in the first switching region 45c of the cam groove 45 of the input rotation shaft 42 along with the forward rotation of the input rotation shaft 42. Move from the start to the end. Then, before the second engagement pin 41b of the restricting member 41 is disengaged from the locking hole 47a of the ring collar 47 in the output rotation shaft 46 toward the output rotation shaft 46 against the elasticity of the first spring 43. The forward rotation of the motor is temporarily stopped. The first engaging pin 41a of the restricting member 41 temporarily stops at the end of the first switching region 45c of the cam groove 45 (standby state).

  When the motor is further driven in the forward rotation direction, the first engaging pin 41a of the restricting member 41 moves from the end of the first switching region 45c of the cam groove 45 to the second rotation restricting region 45b. The second engaging pin 41 b of the restricting member 41 is separated from the first locking hole 47 a of the ring collar 47 of the output rotating shaft 46 toward the output rotating shaft 46, and the output rotating shaft 46 is connected to the input rotating shaft 42. To rotate forward. The second locking hole 47b of the ring collar 47 of the output rotating shaft 46 reaches a position where the second engaging pin 41b of the restricting member 41 is fitted (the end of the second rotation restricting region 45b). Then, the regulating member 41 immediately moves to the input rotating shaft 42 side by the restoring force of the first spring 43 acting on the regulating member 41. The second locking hole 47 b of the ring collar 47 of the output rotation shaft 46 engages with the second engagement pin 41 b of the regulating member 41.

  When the input rotation shaft 42 rotates in the counterclockwise direction due to the reverse rotation of the motor, the first engagement pin 41a of the restricting member 41 is rotated in the second rotation of the cam groove 45 along with the reverse rotation of the input rotation shaft 42. The restriction region 45d moves from the start end to the end. Then, the second engaging pin 41b of the restricting member 41 is disengaged from the second locking hole 47b of the ring collar 47 of the output rotating shaft 46 toward the input rotating shaft 42 against the elasticity of the second spring 44. Before starting, the reverse rotation of the motor is temporarily stopped. The first engaging pin 41a of the regulating member 41 temporarily stops at the end of the second switching region 45d of the cam groove 45 (standby state).

  When the motor is further driven in the reverse rotation direction, the first engagement pin 41a of the restricting member 41 moves from the terminal end of the second switching region 45d of the cam groove 45 to the first rotation restricting region 45a. The second engaging pin 41 b of the restricting member 41 is detached from the second locking hole 47 b of the ring collar 47 of the output rotating shaft 46 toward the input rotating shaft 42, and the output rotating shaft 46 is brought together with the input rotating shaft 42. Reverse rotation. The first locking hole 47a of the ring collar 47 of the output rotating shaft 46 reaches a position where it fits with the second engaging pin 41b of the restricting member 41 (the end of the first rotation restricting region 45a). Due to the return force of the second spring 44 acting on the restricting member 41, the restricting member 41 instantaneously moves to the output rotating shaft 46 side. The first locking hole 47 a of the ring collar 47 of the output rotation shaft 46 engages with the second engagement pin 41 b of the regulating member 41. By repeating the above operation, a shift operation for converting the rotational motion of the input rotational shaft 42 into the rotational motion of the output rotational shaft 46 is effectively performed.

(Effect of the third embodiment)
According to the shift switching device 1 according to the third embodiment configured as described above, the pinion that inputs the reciprocating rotational motion of the output rotating shaft that is rotated forward and backward by the motor, and the pinion is converted into a linear motion. The present invention can be effectively used for various mechanisms such as a rack and pinion mechanism including a rack, a gear mechanism such as a reduction gear, a clutch mechanism, or a shift rod for switching between 2WD and 4WD.

[Fourth Embodiment]
FIG. 7, FIG. 8A, and FIG. 8B schematically show one configuration example of the shift switching device 1 according to the fourth embodiment. In addition, the same member name and code | symbol are attached | subjected to the member substantially the same as the said 1st Embodiment. Therefore, a detailed description of substantially the same members as those in the first embodiment is omitted.

  In these drawings, the difference from the first embodiment is that the drum cam 30 is excluded and the rotational movement of the output shaft 21 of the actuator device 3 is performed on the switching load transmission path from the motor 20 to the sleeve clutch 9. The rack and pinion mechanism that converts the rotational motion of the input pinion 60 into the linear motion of the rack 61 and the restriction mechanism by the stopper lever 62 that restricts the operation of the rack and pinion mechanism are provided.

  In FIG. 7, the shift switching device 1 according to the fourth embodiment includes, for example, a two-wheel drive / four-wheel drive (2WD / 4WD) in a part-time four-wheel drive vehicle based on an FF (front engine, front drive) system. The transfer device 2 and the actuator device 3 are provided.

(Configuration of transfer device)
As shown in FIG. 7, a clutch gear 64, a hub 65, a counter gear 66, and a hypoid gear 67 are coaxially attached to the outer periphery of the main shaft 6 of the transfer device 2. The boss portion 11 a of the shift fork 11 is externally supported by the shift rod 10 so as to be slidable through a force accumulation mechanism using a spring 18. The sleeve clutch 9 of the shift fork 11 meshes with the 2WD clutch gear 64 when 2WD is selected, and meshes with both the 2WD clutch gear 64 and the 4WD hub 65 when 4WD is selected.

  A rack 61 for converting the rotational motion of the pinion 60 supported by the output shaft 21 of the actuator device 3 into a linear motion is formed along the axial direction on the shaft portion on the 4WD switching side of the shift rod 10. A stopper pin 63 projects from the outer peripheral surface of the boss portion 11 a of one shift fork 11. The stopper pin 63 is configured such that the tip of a stopper lever 62 pivotally supported by a holding member (not shown) via a lever support shaft 62 a is engaged with and disengaged from the shift pin 10. The movement in the axial direction is restricted.

  As shown in FIGS. 8A and 8B, the base end portion of the stopper lever 62 is pressed by the protruding piece 60a protruding in the radial direction of the pinion shaft of the pinion 60, so that the rotation of the protruding piece 60a is performed. By the movement, the stopper lever 62 swings against the urging force of the return spring 68 around the lever support shaft 62a.

  Even in the fourth embodiment, the shift fork 11 is set to the standby position before the command for moving the sleeve clutch 9 to the movement end position is output on the drive transmission path from the motor 20 to the sleeve clutch 9. A displacement accumulating mechanism for storing in the spring 18 a force necessary to move the shift fork 11 from the standby position to the movement end position, and a shift restricting mechanism by the stopper lever 62 for restricting the operation of the accumulating mechanism; Has a characteristic part. The power storage mechanism and the shift regulation mechanism are configured to always maintain the power storage state, as in the above embodiments.

(4WD switching standby)
Next, the operation of the shift switching device 1 in the fourth embodiment will be described with reference to FIG. 7, FIG. 8 (a), and FIG. 8 (b). Now, when it is electrically detected by the position switch that the shift fork 11 has been switched to the 2WD position, the motor 20 rotates forward in the counterclockwise direction. The rotational driving force is transmitted to the rack 61 of the shift rod 10 via the pinion 60. The motor 20 temporarily stops before the projecting piece 60a of the pinion shaft engages with the stopper lever 62. Accordingly, the shift rod 10 is moved to the 4WD side, which is the right direction in FIG. 7, against the elasticity of the spring 18. Since the stopper pin 63 of the shift fork 11 is locked to the 2WD side support surface at the tip of the stopper lever 62, the shift fork 11 is in the 2WD position side in the accumulating state (pre-winding state) biased toward the 4WD position side. Waiting to

(4WD shift completed)
When a switching command for switching from 2WD to 4WD is output to the actuator device 3, the output shaft 21 is rotationally driven in the forward rotation direction until it reaches a range exceeding the half circumferential surface including the protruding piece 60a of the pinion shaft. The rotational driving force is transmitted to the rack 61 of the shift rod 10 via the pinion 60 as shown in FIG. The base end portion of the stopper lever 62 is pressed by the protruding piece 60a of the pinion shaft. The stopper lever 62 swings around the lever support shaft 62a, and the engagement between the stopper lever 62 and the stopper pin 63 is released.

  When the engagement between the stopper lever 62 and the stopper pin 63 is released, the restoring force of the compressed spring 18 moves the shift fork 11, so that the shift fork 11 that has been stopped at the 2WD standby position is used. Immediately switches from the 2WD standby position to the 4WD position. When the pressing of the base end portion of the stopper lever 62 by the pinion shaft protruding piece 60a is released, the stopper pin 63 of the shift fork 11 is on the 4WD side of the tip of the stopper lever 62 as shown by a two-dot chain line in FIG. The motor 20 is stopped by being locked to the support surface.

(2WD switching standby)
When it is electrically detected by the position switch that the shift fork 11 has been switched to the 4WD position, the output shaft 21 is rotationally driven in the reverse rotation direction (clockwise direction). The rotational driving force is transmitted to the rack 61 of the shift rod 10 through the pinion 60, and moves the shift rod 10 to the 2WD side, which is the left direction in FIG. Since the stopper pin 63 of the shift fork 11 is locked to the 4WD side support surface at the tip of the stopper lever 62, the shift fork 11 waits at the 4WD standby position in the accumulating state (pre-winding state) biased toward the 2WD position. To do. By repeating the above operations before 4WD switching and before 2WD switching, a shift operation from 2WD to 4WD or from 4WD to 2WD is effectively performed.

(Effect of the fourth embodiment)
According to the shift switching device 1 according to the fourth embodiment configured as described above, the degree of freedom in design of the actuator device 3 is improved as in the effects of the first and second embodiments. be able to.

  As is apparent from the above description, the present invention is not limited to the above-described embodiments, modifications, and illustrated examples, and various design changes can be made within the scope described in each claim. In the above embodiment, the case where the shift switching device of the present invention is applied to the transfer switching mechanism of an FF type or FR type four-wheel drive vehicle has been described, but the present invention is not limited to this. Of course, for example, the shift switching device of the present invention can be effectively used on various drive transmission paths such as a four-wheel vehicle for rough terrain (ATV) and a differential switching mechanism.

DESCRIPTION OF SYMBOLS 1 Shift switching device 2 Transfer device 3 Actuator device 4 Front case 5 Rear case 6 Main shaft 7 4WD gear (clutch gear)
8 2WD gear (sprocket teeth)
9 Sleeve clutch 10 Shift rod 11 Shift fork 11a Boss part 11b Notch slit 11c Small diameter cylindrical part 11d Large diameter cylindrical part 11e Fork drive pin 12 Shift bracket 12a Arm part 12b Rod drive pin 13 Spring pins 14, 15 Color members 16, 17 Snap Rings 18, 43, 44, 49 Spring 20 Motor 21 Output shaft 22 Drive rod 23 Sub-transmission mechanism 24 Input shaft 25 Planetary gear mechanism 26 Slide gear 27 High-speed gear 28 Low-speed gear 28a Pinion gear shaft 28b Spline gear 29 Ring gear 30 Drum cam 31 First cam groove 32 Second cam groove 40 Support member 41 Restriction member 42 Input rotation shaft 45 Cam grooves 45a and 45b Rotation restriction regions 45c and 45d Switching region 46 Output rotation shafts 47 and 48 Ring collars 47a and 4 b engaging holes 41a, 41b engage the pin 60 the pinion 60a projecting piece 61 rack 62 stopper lever 62a lever pivots 63 stopper pin 64 clutch gear 65 hub 66 counter gear 67 Hypoid gear 68 return spring 70 control unit _A 1 2WD shift completion position ( Movement end position)
A ₁ B ₁ 2WD stop area (movement prohibited area)
B ₁ 4WD standby position B ₁ C ₁ 2WD / 4WD switching area (movement permission area)
B ₁ D ₁ 4WD stop area (movement prohibited area)
C ₁ 4WD shift completion position (movement end position)
C ₁ D ₁ 4WD stop area (movement prohibited area)
D ₁ 2WD standby position D ₁ A ₁ 4WD / 2WD switching area (movement permission area)
D ₁ B ₁ 2WD stop area (movement prohibited area)
A ₂ 2WD drive stop position A ₂ D ₂ (D ₂ A ₂ ) 2WD drive stop area B ₂ 4WD drive standby position B ₂ C ₂ (C ₂ B ₂ ) 4WD drive stop area C ₂ 4WD drive stop position D ₂ 2WD drive Standby position D ₂ B ₂ (B ₂ D ₂ ) Switching drive area A ₃ High speed position A ₃ B ₃ High speed area B ₃ High / low speed switching standby position B ₃ C ₃ High / low speed switching area C ₃ High / low speed neutral position C ₃ D ₃ High / low speed neutral region D ₃ Low speed position D ₃ E ₃ Low speed region E ₃ Low high speed switching standby position F ₃ A ₃ High low speed neutral region F ₃ Low high speed neutral position E ₃ F ₃ Low high speed switching region A ₄ High speed drive position B ₄ (E ₄ ) Speed switching standby position A ₄ B ₄ (E ₄ F ₄ ) Speed switching area B ₄ C ₄ (D ₄ E ₄ ) Speed switching area B ₄ E ₄ (E ₄ B ₄ ) Speed switching area D ₄ Low speed Drive position

Claims (6)

A first shift member that moves between first and second positions;
When the first shift member is in the first position, it is in a standby position corresponding to the second position, and when the first shift member is in the second position, the first position A second shift member in a standby position corresponding to
Accumulating means for accumulating a moving force for moving the first shift member between the first and second positions when the second shift member is in the first or second standby position;
When the accumulating means accumulates the moving force, the restricting means for restricting the movement of the first shift member based on the moving force and the restricting means, and
A drive source for moving the first shift member and the second shift member;
Control means for controlling the drive source,
The control means receives the movement command for moving the first shift member from the first position to the second position or from the second position to the first position. The shift switching device is characterized in that the restriction by the restricting means is released by driving and the first shift member is moved to the second position or the first position by the moving force of the accumulating means. . The accumulating means is an accumulating spring provided between the first shift member and the second shift member,
The restricting means has a drum cam that converts a rotational motion of the drive source into a linear motion,
In the drum cam, a first cam groove and a second cam groove are formed independently in the axial direction,
In the first cam groove, a first forbidden area for prohibiting movement of the first shift member and a first permissible area for allowing movement of the first shift member are formed,
The second cam groove has a second permissible area that allows movement of the second shift member corresponding to the first forbidden area, and a second permissible area of the second shift member corresponding to the first permissible area. A second prohibited area is formed to prohibit movement;
The first shift member is engaged with the first forbidden area, the second shift member is engaged with the second allowable area, and the second shift member is moved to the standby state by driving the drive source. Compress the accumulator spring by moving it to a position to accumulate the moving force,
The drive source is driven to engage the first shift member from the first prohibition region to the first permissible region, and the second shift member is engaged from the second permissible region to the second prohibition region. 2. The shift switching device according to claim 1, wherein the first shift member is moved to the second position or the first position by an urging force of the compressed accumulation spring. The first cam groove is an annular concave groove connecting end portions of the pair of first allowable regions arranged in the circumferential direction between the pair of first prohibited regions arranged in the axial direction,
The second cam groove is a meandering concave groove in which an end portion of the second permissible region extending obliquely in the circumferential direction is connected between a pair of second prohibited regions extending in the circumferential direction. The shift switching device according to claim 2. The first shift member is a shift fork for switching between two-wheel drive and four-wheel drive;
The shift switching device according to claim 1 or 2, wherein the second shift member is a shift rod for moving the shift fork. The first shift member is a shift fork for switching between at least a high speed stage and a low speed stage;
The shift switching device according to claim 1 or 2, wherein the second shift member is a shift rod for moving the shift fork.   The shift switching device according to claim 1, wherein the drive source includes a motor that can rotate forward and reverse.

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