JP2618725B2 - Operation mechanism of power take-off device for specially equipped vehicles - Google Patents

Description

The present invention relates to an operation mechanism of a power take-off device in a specially-equipped vehicle, and more specifically, to the power transmitted from an engine transmission to a rear wheel via a propeller shaft. Separately, when taking out the power for the hydraulic actuator that enables various operations of specially equipped vehicles from the transmission, it is possible to engage and disengage the rotating gear and the gear that meshes with it and transmit it to the hydraulic pump for the hydraulic actuator. The present invention relates to an operation mechanism in a power take-out device capable of connecting and disconnecting motive power.

[Conventional technology]

Specially equipped vehicles include a dump truck having a tilting carrier at the rear of the vehicle body, and are equipped with a hydraulic actuator for tilting the carrier. The hydraulic pump that supplies hydraulic oil to the actuator is driven by the engine power that is being driven while the vehicle is stopped. In this case, the power taken out of the transmission can be transmitted or interrupted to the take-out shaft through several gears and by changing the meshing state of the gears. The rotation of the hydraulic pump is driven. For example, JP-A-57-58513 and JP-A-51-12662
Japanese Patent Publication No. 8 and other publications describe a power take-out device capable of taking out power for various operations in addition to the power transmitted from the transmission to the rear wheels.

By the way, it has been easy to separate the power described above from the transmission, but if a specially equipped vehicle is equipped with a transmission having an automatic transmission function, the power take-out operation becomes complicated. In conclusion, the operation procedure is as follows: when the vehicle is stopped, the range switching lever located in the D range is put in the P range, and when the engine power is supplied to the hydraulic pump,
The range change lever is returned to the D range once, and the shifter that can interlock the gears for transmitting the power is moved while continuously depressing the brake pedal in this state. And
The range switching lever is switched from the D range to the N or P range while releasing the brake pedal.

On the other hand, when stopping power take-off, while depressing the brake pedal, switch the range switching lever in the N or P range to the D range, disengage the shifter and each gear, and loosen the depression of the brake pedal,
Move the range switching lever to the N or P range again.

As described above, when extracting power for various operations from an engine equipped with an automatic transmission or stopping the extraction, it is necessary to frequently operate a brake pedal and a range switching lever, which is extremely complicated and cumbersome. There is a problem. At this time, if the brake pedal is depressed erroneously, a trouble may occur, and attention is required in operation. In addition, during the operation of extracting power, there is a connection between the rotating gear and the stopped gear and the release of the connection, but at that time, the gear may ring and the tooth surface may be damaged. Is strongly desired.

[Problems to be solved by the invention]

In order to solve the above-mentioned drawbacks, the present applicant has proposed a power take-out device which does not require a complicated switching operation in Japanese Patent Laying-Open No. 2-266149. As shown in FIG. 5 (c), this device transmits power from the power take-out gear 11 which is constantly rotating by transmitting engine power to a power transmission gear 15 which drives a hydraulic pump. An annular gear 14 provided on its inner surface with a fitted conical surface 14b that can be fitted to and detached from an output conical surface 15b formed on the transmission gear 15, and a shifter 16 that is movable so as to be able to mesh with any of the gears at the same time. Power can be taken out by a simple operation even in the case of a vehicle equipped with an automatic transmission. At this time, the state of engagement of the shifter with each gear can be changed by manual operation remotely from the driver's seat or the like.

That is, the shifter 16 is initially engaged only with the power take-off gear 11, and the displacement of the operation rod (not shown) causes
When the shifter 16 shown in FIG. 5A is moved in the direction of the arrow X via the recess 16b, the shift internal teeth 16a of the shifter 16 are shifted.
Are meshed with the transmission external teeth 14a of the ring gear 14, and also mesh with the input external teeth 15a of the power transmission gear 15, so that the shifter 16
The power is taken out in a state in which the power take-out gear 11, the ring gear 14, and the power transmission gear 15 mesh with each other (see FIG. 5 (c)). At this time, the power take-out gear 11, i.e., the shifter 16 and the power transmission gear 15 are engaged by the fitting operation between the fitted conical surface 14 b of the ring gear 14 and the output conical surface 15 b of the power transmission gear 15.
Synchronization of rotation with 15 is obtained.

By the way, when the operating rod having no self-displacement absorbing force for moving the shifter 16 is displaced by the electric motor driven at a constant rotation speed, the shifter 16 is moved as shown by the line Q in FIG. 6 (c). It is moved at a constant speed. Returning to the apparatus of FIG. 5 (c), the shifter 16 is always rotating because it is in mesh with the power take-off gear 11, but since the ring gear 14 is in a state capable of idle rotation, the shifter 16 is ring-shaped. It is easy to completely mesh with the gear 14 [see the point S on the dashed line in FIG. 6 (d)]. The operating force acting on the operating rod during this time changes as shown by a two-dot chain line point S in FIG. 6 (c). During the engagement between the shifter 16 and the ring gear 14, the shifter 16 slightly moves the ring gear 14 toward the power transmission gear 15, so that the ring gear
The fitted conical surface 14b of the power transmission gear 15 is closely but not completely adhered to the output conical surface 15b of the power transmission gear 15. Therefore, the power transmission gear
Reference numeral 15 denotes the rotation of the ring gear 14, which starts to rotate up to a point S indicated by a two-dot chain line in FIG. 6 (d).

After this state, the operating rod is displaced at a constant speed, so that the shifter 16 further moves toward the power transmission gear 15. It takes time T ₁ (see FIGS. 6 (c) and (d)) to start engaging with the power transmission gear 15;
And, by achieving complete meshing between the shifter 16 and the ring gear 14, the force of the shifter 16 pressing the ring gear 14 toward the power transmission gear 15 is sharply reduced, and the fitted cone of the ring gear 14 is reduced. Since the adhesive force between the surface 14b and the output conical surface 15b of the power transmission gear 15 is weakened, the power transmission gear 15
During this period, as shown in FIG. 6 (d), from point S to point U, decreases significantly. When the shifter 16 starts to mesh with the power transmission gear 15 and the meshing is completed,
The power transmission gear 15 rotates at a speed _R0 that matches the driving force of the shifter 16, that is, the power take-off gear 11, and the power drives a hydraulic pump or the like.

In such an operation, the number of rotations of the power transmission gear 15 that has begun to rotate is greatly reduced from Ra to _RL shown in FIG. 6D because the shifter 16 engages with the ring gear 14. This is because long the the time T ₁ of the up start meshing with the power transmission gear 15 after completing. Therefore, in order for the shifter 16 to mesh with the power transmission gear 15 from the first time to a predetermined rotation speed, it is necessary to increase the speed by Rc shown in FIG. 6 (d). As a result, the shifter 16 and the power transmission gear 15
Too much difference in the number of rotations between the shifter 16 and the synchronizing shift becomes severe, noise such as gear noise and switching noise occurs between the shifter 16 and the power transmission gear 15, and in some cases, damage to the tooth surface. Invitation and other problems remain. This occurs more violently as the rotational speed of the shifter 16 to which the power from the engine is transmitted increases, and as the load applied to the power transmission gear 15 increases.

This is because, when the displacement of the operating rod for moving the shifter 16 is manually performed, when the engagement reaction force between the shifter 16 and the power transmission gear 15 is increased, the displacement of the operating rod is It doesn't happen if you slow down the speed. However, if the operation rod is to be displaced by the electric motor in order to eliminate the inconvenience of the manual operation, the operation rod will be moved at a uniform speed (see line Q in FIG. 6 (c)), Even if there is a large meshing reaction force when the shifter 16 meshes with the power transmission gear 15, it is not possible to perform a slow meshing operation to reduce it,
This results in gear noise and the like.

Incidentally, Japanese Utility Model Laid-Open No. 59-113520 discloses that a shifter moving member, which is usually fixedly mounted on a reciprocatingly displaceable operation rod, is mounted on the operation rod so as to be relatively displaceable, and a plurality of coil springs are arranged between the two. Described manual transmission. According to such a structure, the movement of the shifter moving member can be adjusted to be different from the displacement of the operation rod by the compression of the spring. That is,
Unlike the above described FIG. 6 (c), the shifter can be operated in the same manner as the movement along the solid line in FIG. 6 (a) which will be described later. However, since the displacement adjusting mechanism is provided in the casing of the power take-out device, there is a drawback that the interior of the casing must be significantly modified when applied to an existing power take-out device.

The present invention has been made in view of the above-described problems, and has as its object to provide a specially-equipped vehicle equipped with a transmission having an automatic speed change function, and to take out a power for performing various operations, a very simple range switching operation. Therefore, even if the gears can be connected and disconnected smoothly, even if the operating rod is displaced by the electric motor driven at a constant rotation speed, the shift speed of the shifter is adjusted according to the displacement of the operating force applied to the shifter, and the shifter That the rotation of the power transmission gear can be reduced quickly until it balances the driving force of the power take-off gear, and this occurs when the shifter and the power transmission gear mesh. Noise and damage to the tooth surface, as well as a structure that can be easily applied to existing power take-off devices. Improvement of the device is to provide an operating mechanism of the power take-off in a specially equipped that realizes that it is possible to be operated mechanism is achieved easily.

[Means for solving the problem]

INDUSTRIAL APPLICABILITY The present invention is applied to a power take-out device of a specially-equipped vehicle in which power for a hydraulic actuator that enables various operations by equipment of the vehicle is taken out of an engine that is operating while the vehicle is stopped.

The feature is that, with reference to FIGS. 1 and 2, a power take-out gear 11 is fixed to the input shaft 2 that transmits the power of the engine 3 taken out of the transmission 4 and is constantly rotating, A concentric and same-diameter annular gear 14 movably mounted on the input shaft 2 in the vicinity of the power take-off gear 11.
A shifter 16 movable in the input axis direction so as to be able to mesh with any of the gears simultaneously, and an operating rod 7 displaced to move the shifter 16; The inner surface of the ring gear 14 is formed with a fitted conical surface 14b extending toward the power take-out gear 15 while the power transmission gear 15 is formed with an output conical surface 15b capable of being fitted and detached from the fitted conical surface 14b. In the power take-out device having a mechanism, when the shifter 16 is moved to mesh with the ring gear 14 and the power transmission gear 15, an electric force that applies an operation force in a pulling direction to displace the operation rod 7 at a constant speed. The motor 9 is provided.

When the operating rod 7 is pulled by the electric motor 9, it accumulates energy while absorbing the displacement of the operating rod 7 from the point of receiving the meshing reaction force equal to or more than a predetermined value and shifts
The displacement of the operating rod 7 is directly transmitted after the limit of the accumulated power, and the shifter 16 meshes with the ring gear 14,
When the shifter 16 completely meshes with the ring gear 14, when the meshing reaction force acting on the operating rod 7 is sharply reduced, the accumulated force is released to the operating rod 7 displaced at a constant speed, and the operation is started. The variable length buffer type energy storage means 10 for increasing the displacement of the rod 7 is interposed in the operation rod 7 at a portion existing outside the casing 1A of the power take-out device 1.

As a result, the time until the shifter 16 starts meshing with the power transmission gear 15 after the shifter 16 completes meshing with the ring gear 14 is shortened, and during this time, the synchronous rotation speed of the power transmission gear 15 is suppressed from being significantly reduced. Is to be able to do it.

The variable-length buffer type energy storage means 10 (see FIG. 3 (a)) has a cylinder 10d, a piston 10a and a piston rod 10b, and applies an operating force in the pulling direction to the piston rod 10b. Connect motor 9 to cylinder 10d
It is preferable that a compression spring 10c is interposed on the piston rod 10b side.

As shown in FIG. 4, the variable length buffer type energy storage means 10 includes a cylinder 10d, a piston 10a, and a piston rod.
An electric motor 9 having a piston rod 10b and applying an operating force in the pulling direction to the piston rod 10b side may be connected, and the compressed gas 10e may be sealed in the piston rod 10b side in the cylinder 10d.

[Action]

Power from the engine is supplied to a power take-off gear 11 fixed to the input shaft 2 of the power take-out device 1 via a transmission.
It is transmitted to. The shifter 16 is meshed only with the power take-off gear 11, and the shifter 16 is also rotating. When the electric motor 9 is driven in this state, the operating force in the pulling direction is transmitted to the operating rod 7 and the variable-length buffer type energy storage means 10 (see FIG. 3A). The shifter 16 starts to move by the displacement of the operating rod 7, and receives the operating force to
Starts to mesh with the ring gear 14. The operating force increases during the meshing, but when receiving a meshing reaction force equal to or greater than a predetermined value, the variable-length buffer type energy storage means 10 starts accumulating while absorbing the displacement of the operating rod 7 and shifter 16. Suppress movement.

When the variable-length buffer type energy storage means 10 reaches the energy storage limit,
Thereafter, the displacement of the operating rod 7 is directly transmitted to the shifter 16, the shifter 16 moves following the displacement of the operating rod 7, and the shifter 16 is completely meshed with the ring gear 14.
That is, the time until the engagement between the shifter 16 and the ring gear 14 is completed is extended by the variable-length buffer type energy storage means 10.

During this meshing, the shifter 16 slightly moves the ring gear 14 toward the power transmission gear 15, so that the fitted conical surface 14b of the ring gear 14 is not completely on the output cone surface 15b of the power transmission gear 15. Is adhered. Therefore, the power transmission gear 15 starts to rotate with the rotation of the ring gear 14.

After this state, the operation rod 7 is displaced at a constant speed,
The shifter 16 further moves toward the pressing force transmission gear 15.
However, after the shifter 16 is completely meshed with the ring gear 14, a pushing force for meshing is not required, and the shifter 16 does not push the ring gear 14 toward the power transmission gear 15. Therefore, the meshing reaction force acting on the operating rod 7 decreases sharply after meshing with the ring gear 14 is completed. As a result, the variable length buffer type energy storage means 10
Is released, and the operating rod 7 displaced at a constant speed is accelerated. That is, the pulling force of the operating rod 7 and the force accumulated in the variable length buffer type energy storage means 10 act synergistically on the shifter 16, and the shifter 16 moves to the power transmission gear 15 in a short time. The time T ₂ [see FIG. 6 (a)] until the engagement with the power transmission gear 15 starts is short.

Achieving complete engagement between the shifter 16 and the ring gear 14 reduces the force by which the shifter 16 presses the ring gear 14 toward the power transmission gear 15 so that the fitted conical surface 14b of the ring gear 14 The contact force between the power transmission gear 15 and the output conical surface 15b of the power transmission gear 15 is weakened, and the rotation of the power transmission gear 15 that is being rotated starts to fall. However, short contact is weakening time and T _2, the smaller the rotation speed decrease of the power transmission gear 15 occurring between them. That is, the shift in the synchronous speed between the shifter 16 and the power transmission gear 15 is reduced. Therefore, the subsequent engagement of the shifter 16 and the power transmission gear 15 is smoothly performed, and noise and damage to the tooth surface due to the engagement are prevented.

When the shifter 16 starts to mesh with the power transmission gear 15 and the meshing is completed, the power transmission gear 15 is shifted to the shifter 16.
That is, it rotates at a speed R ₀ (see FIG. 6 (b)) balanced with the driving force of the power take-off gear 11, and the power drives the hydraulic pump and the like.

As the above-mentioned variable length buffer type energy storage means 10, a cylinder 10
If the compression spring 10c is interposed on the piston rod 10b side in d, when the operating rod 7 receives a predetermined or more meshing reaction force, the compression spring 10c starts to be reduced,
The displacement of the operating rod 7 is absorbed by the compression spring 10c. During the absorption of the displacement, the variable length buffer type energy storage means 10
Restrains the shifter 16 from moving, while the compression spring 10
Energy is stored by the contraction deformation of c. The point at which the compression spring 10c is completely contracted is the storage limit, and the subsequent displacement of the operating rod 7 is directly transmitted to the shifter 16.

When the shifter 16 meshes with the ring gear 14, the meshing reaction force is generated, but after completely meshing, the meshing reaction force hardly disappears.
The force accumulated in 10c is released and is added to the force displacing the operating rod 7.

Instead of the compression action of the spring, the compression action of air can be used. In that case, the compressed gas 10e may be sealed in the piston rod side 10b in the cylinder 10d (see FIG. 4).

〔The invention's effect〕

According to the present invention, the time until the shifter completely meshes with the ring gear is lengthened by the displacement absorption of the operating rod by the variable-length buffer type energy storage means, while the shifter completely meshes with the ring gear. Until the engagement with the rear power transmission gear starts, the displacement of the operating rod is accelerated by the release of the force accumulated in the variable length buffer type energy storage means, and the engagement of the shifter and the power transmission gear is quickly started. If the time from when the shifter completely meshes with the ring gear until it begins to mesh with the power transmission gear is short, the degree of rotation of the power transmission gear that has been rotating with the ring gear will also decrease, and the shifter will be moved to the power transmission gear. , It is possible to reduce the synchronization deviation when meshing with. Therefore, the generation of gear noise and switching noise at the time of the meshing is reduced, and damage to the tooth surface is prevented. Furthermore, since the above-mentioned variable-length buffer type energy storage means is provided on the operation rod outside the casing of the power take-off device, the electric motor employed to eliminate the trouble of manual operation is constant. Even if the power take-off device is driven at such a rotational speed, the structure according to the present invention can be easily adopted later in such a ready-made power take-out device. In such a case, it is possible to avoid as much as possible a complicated remodeling operation of the ready-made device and a complicated structure, and it is possible to exhibit the above-described effects.

〔Example〕

Hereinafter, the present invention will be described in detail with reference to the drawings. The power take-off device 1 shown in FIG. 1 has an input shaft 2 connected to a transmission 4 for transmitting the power of an engine 3, and a take-out shaft 6 for taking out the drive power of a hydraulic pump 5 that rotates a hydraulic actuator by its rotation. Have been. Then, an operation rod 7 that is displaced to take out power from the input shaft 2 to the take-out shaft 6 or to stop taking out power.
Is connected to an electric motor 9 for eliminating the trouble of manually operating the operation rod 7 via a bell crank 8, and the operation rod 7 is operated by a mechanical operation according to a remote command from a vehicle room or the like. Can be displaced at a constant speed.

The operating rod 7 is composed of a front rod 7A and a rear rod 7B.
A variable-length shock-absorbing storage means 10 having a built-in piston 10a, piston rod 10b and compression spring 10c is interposed between both parts located outside (see FIG. 1). The front rod 7A is connected to the base of the cylinder 10d, and the rear rod 7B is connected to the piston rod 10b.

FIG. 2 is a cross-sectional view of a main part of the power take-out device 1, in a casing 1A of which there is a power take-out gear 11 having external teeth 11a, which is supported by two bearings 2a, 2b via a spline 11b. Attached to the input shaft 2. On the input shaft 2, an intermediate gear 12 is provided movably via a needle bearing 12a, adjacent to the power take-off gear 11, and an take-out gear fixed to the take-out shaft 6 supported by two bearings 6a, 6b. 13 is engaged. Between the power take-out gear 11 and the intermediate gear 12, there is provided an annular gear 14 having transmission external teeth 14a having the same concentricity and the same diameter as the power take-out gear 11, and the same gear specifications are provided on the side thereof. The power transmission gear 15 formed with the input external teeth 15a is disposed. The shift internal teeth 16a meshing with the power take-out gear 11, the ring gear 14, and the power transmission gear 15
And a cylindrical shifter 16 that can move in the axial direction of the input shaft 2 is provided. In order to move the shifter 16, a front rod 7A including a fitting member 17 indicated by a two-dot chain line engaged with a concave portion 16b formed on the outer periphery.
Also, its tip is stored.

The casing 1A is provided with a portion through which the input shaft 2 penetrates and a take-out shaft 6.
A cover member 1a for covering the other end of the input shaft 2 and a cover member 1b for covering one end of the input shaft 2, the interior of which is a sealed space, and a pipe or the like for lubricating the above-mentioned gear group. Zu] are arranged.

As described above, the power take-off gear 11 is provided with the external teeth 11a meshing with the shift internal teeth 16a of the shifter 16, and the input shaft 2 always rotates as long as the engine 3 is operated. ing. If the shifter 16 is moved as indicated by the two-dot chain line, the shifter 16 meshes only with the power take-out gear 11 and constantly rotates.

The inner surface of the ring gear 14 is formed with a conical surface 14b that extends toward the power transmission gear 15, and the width of the outer transmission tooth 14a is viewed in a plan view at the end on the power take-out gear 11 side. The shape is gradually narrowed down so as to form a substantially triangular shape. On the other hand, the shift inner teeth 16a of the shifter 16 are also cut off in a triangular shape on the side facing the ring gear 14, so that the shifter 16
When the gear is moved to the ring gear 16 side, care is taken so that the rotating shift internal teeth 16a mesh with the non-rotating ring gear 14 so that the initial engagement is smooth.

In the small diameter portion of the power transmission gear 15, an output conical surface 15b that can be fitted and detached from the fitted conical surface 14b of the ring gear 14 is engaged,
The tooth width of the large-diameter input external teeth 15a is gradually cut off so as to be substantially triangular in plan view at the end on the ring gear 14 side. Therefore, when the shift internal teeth 16a cut into a triangular shape are moved to the power transmission gear 15, the rotating shifter 16 can smoothly engage with the slowly rotating power transmission gear 15 at the beginning. It has become.
The ring gear 14 is made of a brass material or the like that is different from other steel gears, so that the fitted conical surface 14b is easily brought into close contact with the output conical surface 15b. In addition, the mating conical surface
Serrations 14c are formed on the surface of 14b, and the output conical surface 15
The frictional force generated at the time of close contact with b can be further enhanced.

The above-mentioned power transmission gear 15 is provided with internal teeth 15c, which are meshed with engaging external teeth 12c provided on a small-diameter boss portion 12b of the intermediate gear 12, which protrudes toward the power transmission gear 15. As a result, the power transmission gear 15 has a structure integrated with the intermediate gear 12 for rotating the take-out shaft 6. The power transmission gear 15 and the intermediate gear 12 may be integrated in advance.

FIG. 3 (a) shows an example of a variable-length buffer type energy storage means 10 interposed between the operating rod 7 and an electric motor 9 (see FIG. 1) driven at a constant rotational speed.
When the shifter 16 meshes with the ring gear 14 when the shifter 16 meshes with the ring gear 14 by pulling 7B in the direction of the arrow X, the compression spring 10c contracts from the point of receiving a meshing reaction force exceeding a predetermined value, and stores energy while absorbing the displacement of the rear rod 7B. It is supposed to. During that time, the displacement of the front rod 7A is interrupted, and the movement of the shifter 16 is suppressed. When the compression spring 10c contracts as shown in FIG. 3 (b) and reaches the storage limit, thereafter, the displacement of the rear rod 7B is directly transmitted to the front rod 7A, and the movement of the shifter 16 can be resumed. Then, the shifter 16 meshes with the ring gear 14 by this movement, and when the meshing reaction force acting on the operating rod 7 sharply decreases for the reason described later, the compression spring 10c moves the operating rod 7 displaced at a constant speed. The storage power is released, and the displacement of the operation rod 7 can be increased.

In FIG. 2, when the operating rod 7 is pulled to the illustrated position, the shifter 16 has been moved to the power transmission gear 15 as shown by a solid line, and the front end 7a of the operating rod 7 is formed in the casing 1A. Ball-shaped blocking member, which is positioned slightly in the recessed hole 1c and is urged by the spring 18.
If the fitting 19 is fitted into the first ring groove 7b and no force is applied to the operating rod 7, the fitting member 17 is kept at that position.
On the other hand, when the operating rod 7 is pushed in by the reverse rotation of the electric motor 9, the front end 7a is set to a position deep into the recessed hole 1c, the blocking member 19 is fitted into the second ring groove 7c, and the shifter 16 is As shown by, the power take-off gear 11 stays at a position where it meshes only.

According to the power take-out device 1 having such a configuration, the hydraulic pump 5 that supplies hydraulic oil to the actuators for various operations mounted on the specially-equipped vehicle can be driven by the power taken out of the transmission 4. At the time of power take-out, the displacement of the operating rod 7 by the electric motor driven at a constant rotation speed is adjusted by the operation of the variable-length buffer type energy storage means 10, so that the engagement between the shifter 16 and the power transmission gear 15 is smooth. Done in The temporal change in the operation of the operation mechanism will be described with reference to FIGS. 6 (a) and 6 (b) in which FIGS. 6 (c) and 6 (d) are overlapped.

After the vehicle is stopped, the range switching lever of the automatic transmission is set to the P range, the power from the engine 3 in the idling state is transmitted to the input shaft 2 via the transmission 4, and the power take-out gear 11 is It rotates (see line A in FIG. 6 (b)). At this time, the shifter 16 is engaged only with the power take-off gear 11 as shown in FIG. 5 (a), and the shifter 16 is also rotating.

When the electric motor 9 is started by a command operation in the vehicle cabin, a pulling direction operation force indicated by an arrow X acts on the operation rod 7 via the bell crank 8, and the operation force is controlled via the variable length buffer type energy storage means 10. The rod 7A is displaced. By the displacement, the shifter
16 is moved toward the ring gear 14 as shown by the two-dot chain line in FIG. 5 (a) [see line B in FIG. 6 (a)]. No large force is required until the shifter 16 reaches the transmission external teeth 14a of the ring gear 14, and the electric motor 9 gradually increases the operation force in the pulling direction during the movement [FIG. 6 (a)]. The blocking member 19 fitted in the second ring groove 7c (see FIG. 2) retreats against the elastic force of the spring 18, and the engagement of the blocking member 19 is released. You.

The shifter 16 starts to mesh with the ring gear 14, and the ring gear 14
Starts rotation [see the arrow D in FIG. 6 (b)]. The rotating shift internal teeth 16a do not immediately mesh with the transmission external teeth 14a of the ring gear 14, and the triangular-pointed shift internal teeth 16a are not rotated.
The shifter 16 moves toward the ring gear 14 so that the rear end of the transmission external tooth 14a also has a triangular-shaped rear end. Therefore, a force sufficient for the transmission external teeth 14a to push the shift internal teeth 16a apart is provided by the shifter via the operating rod 7.
Conveyed to 16. This pushing force acts on the front rod 7A as a meshing reaction force between the transmission external teeth 14a and the shift internal teeth 16a.

The meshing reaction force increases as the meshing between the shift internal teeth 16a and the transmission external teeth 14a progresses. However, before the meshing reaction force increases, the variable-length buffer type energy storage means
10 compression springs 10c are used for piston 10a and cylinder 10d
Begins to shrink between the rear end walls. During this time, the operating force gradually increases (see the arrow E in FIG. 6 (a)), but the displacement of the rear rod 7B, which is displaced by the pulling force at a constant speed, is absorbed. During this time, since the pulling force of the rear rod 7B is not transmitted to the front rod 7A, the shifter 16 does not move (see the line F in FIG. 6 (a)).

Although the state in which the shifter 16 and the ring gear 14 are not sufficiently engaged with each other continues, the rotation of the ring gear 14 is gradually increased [see the line G in FIG. 6 (b)]. ]. During this time, the ring gear 14 is pushed toward the power transmission gear 15, and the fitted conical surface 14 b is intimately, but not completely, adhered to the output conical surface 15 b of the power transmission gear 15. Therefore, the power transmission gear 15 which has not been rotated also starts to rotate (see the line H in FIG. 6 (b)). When the compression spring 10c contracts due to the displacement of the rear rod 7B without reaching sufficient engagement between the shift internal teeth 16a and the transmission external teeth 14a and reaches the energy storage limit,
Thereafter, the displacement of the rear rod 7B is directly transmitted to the front rod 7A (see the line I in FIG. 6 (a)). Therefore, at that time, the shifter 16 starts moving again, and the shifter 16 is deeply meshed with the ring gear 14. Meanwhile shift internal teeth
The frictional force between the transmission external teeth 14a and the transmission external teeth 14a peaks (see the arrow J in FIG. 6 (a)), and finally the tooth side surfaces of the shift internal teeth 16a and the transmission external teeth 14a completely face each other. The meshing state is established (see the arrow K in FIGS. 6 (a) and 6 (b)). During this time, the fitted conical surface 14b becomes the output conical surface 15b.
Therefore, the rotation of the power transmission gear 15 is further increased in speed.

However, when the engagement between the shifter 16 and the ring gear 14 is completed, the pushing force of the shifter 16 on the ring gear 14 sharply decreases at the opposing surfaces of the two teeth, and the operating force of the shifter 16 decreases. 6 (see line L in FIG. 6A)]. At the same time, the close contact between the fitted conical surface 14b and the output conical surface 15b is loosened, so that the force for rotating the power transmission gear 15 decreases,
The rotation starts to decelerate (see the line M in FIG. 6B). By reducing the meshing reaction force acting on the shifter 16, the compression spring 10c reduced in the variable length buffer type energy storage means 10 is restored, and its energy is released. This force is added to the pulling force acting on the operating rod 7 by the electric motor 9, and the operating force is reinforced (see the line N in FIG. 6 (a)).

A large force generated by a combination of the two forces acts on the shifter 16, and as shown in FIG. 5 (b), after the shifter 16 and the ring gear 14 are completely meshed, the power transmission gear 15 The time T ₂ [see FIG. 6 (a)] until the start of engagement with the input external teeth 15a of FIG.
T ₁ (see FIG. 6 (c)). When the shifter 16 starts to mesh with the input external teeth 15a (see the arrow V in FIGS. 6A and 6B), the power transmission gear 15
6 (b).
Part reference] is, the power transmission gear 15 for a short time T ₂ which is above
Rotation only drops to R _M. That is, the amount of decrease in the number of rotations is as small as Rb, and the shifter 16
The synchronization deviation at the time of starting to mesh with Rd is significantly smaller than Rc described with reference to FIG. 6 (d). Therefore,
The engagement between the shift internal teeth 16a and the input external teeth 15a is made smooth, and the time required for the shifter 16 to completely mesh with the power transmission gear 15 (see FIG. 5 (c)) is slightly shorter. At this time, generation of gear noise and switching noise is significantly reduced. The impact at the start of the engagement between the shift internal teeth 16a and the input external teeth 15a is reduced, and the tooth surface is not damaged.

When the operation of the hydraulic pump is stopped, the electric motor 9 is rotated in the reverse direction, and a pushing force is applied to the operation rod 7. Since the compression spring 10c has already been restored, the piston 1
0a is in contact with the front end wall of the cylinder 10d and the rear rod 7
The displacement of B is immediately transmitted to the front rod 7A. Therefore, the shifter 16 meshing and rotating at the same speed is easily disengaged from the power transmission gear 15, and the return movement of the shifter 16 causes the fitted conical surface 14b to be far from the output conical surface 15b. It is easily disengaged from the rotating ring gear 14 and is returned to the state of engagement with only the power take-off gear 11. Compression spring 10c in variable length buffer type energy storage means 10
Remains in the cylinder 10d, and when the electric motor 9 is rotated forward again, the above-described power take-out operation can be performed.

In the above description, an example in which a spring cylinder is used as the variable-length buffer type energy storage means 10 has been described. However, as shown in FIG. 4, a compressed gas 10e may be filled instead of the spring 10c. If the gas pressure is increased in advance, the displacement of the rear rod 7B can be transmitted to the front rod 7A until a predetermined compression is applied, and when the pressure is reached, the compression spring 10c is contracted. Similarly begin to contract, front rod 7
When the meshing reaction force acting on A suddenly decreases, the compressive force is released through the piston 10a which moves while being kept airtight by the piston ring 10f, and exerts the speed increasing function in synergy with the displacement operation of the operating rod 7. be able to. Note that a suction / discharge port 10g is provided in the piston side chamber in order to smoothly move the piston 10a.

As described in detail above, the time required for the shifter 16 to complete the engagement with the ring gear 14 compared to the conventional power take-off device is calculated from T ₃ (see FIGS. 6 (c) and (d)). T ₄ (see FIGS. 6 (a) and 6 (b)) is intentionally prolonged to make the initial rotation time of the power transmission gear 15 longer. After the meshing between the shifter 16 and the ring gear 14 is completed, the speed of the shifter 16 is increased by causing the operating rod 7 having a constant displacement speed to release the accumulated power of the variable length buffer type energy storage means 10. The time T ₁ (see FIGS. 6 (c) and 6 (d)) until the start of meshing with the power transmission gear 15 is shortened to time T ₂ (see FIGS. 6 (a) and 6 (b)). The time during which the adhesion between the fitted conical surface 14b and the output conical surface 15b is reduced is reduced so that the accompanying rotation speed of the power transmission gear 15 is not significantly reduced. As a result, the total time from the start of the electric motor 9 to the engagement of the shifter 16 with the power transmission gear 15 and the rotation of the extraction gear 13 for transmitting power to a hydraulic pump or the like is the same or slightly shorter. Regardless, the power transmission gear 15 can be driven smoothly without any gear noise or the like.

Such a variable-length buffer type energy storage means 10 can be provided between the two divided bodies outside the casing of the power take-out device by dividing the operation lever 7 and modifying the operation lever in the existing power take-out device. A self-displacement absorbing function can be easily provided. Therefore, when the shifter is moved via the operation rod by the electric motor rotating at a constant speed, which is usually adopted to eliminate the trouble of the manual operation, the shifter is applied to the operation as described above in the ready-made device. The shift speed of the shifter is adjusted according to the change in the operating force, and the reduction in the number of rotations of the power transmission gear for synchronizing with the shifter is suppressed, whereby the rotation of the power transmission gear is reduced to the driving force of the power take-out gear. Raise quickly until balanced,
It is possible to prevent noise and damage to the tooth surface generated when the shifter and the power transmission gear mesh with each other.

In the above, a specially-equipped vehicle equipped with an automatic transmission has been described. However, the present invention can be applied to a vehicle equipped with a transmission having no such automatic transmission function.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram of an operation mechanism for operating the power take-out device of the present invention, FIG. 2 is a sectional view of a main part of the power take-out device, and FIG.
(A) and (b) are explanatory views of the configuration and operation of a spring cylinder which is a variable-length buffer type energy storage device, and FIG. 4 is an operation explanatory diagram of a compressed gas cylinder which is a different variable-length buffer type energy storage device. FIGS. 5 (a) to 5 (c) are explanatory diagrams of the meshing operation of the shifter, the ring gear and the power transmission gear, and FIGS. 6 (a) and 6 (b) are temporal changes in the operation mechanism of the present invention. 6 (c) and 6 (d) are graphs illustrating the temporal change in operation of the conventional operating mechanism. DESCRIPTION OF SYMBOLS 1 ... Power extraction device, 1A ... Casing, 2 ... Input shaft, 3 ... Engine, 4 ... Transmission, 7 ...
... operating rod, 9 ... electric motor, 10 ... variable length buffer type energy storage means, 10a ... piston, 10b ... piston rod, 10c ... compression spring, 10d ... cylinder, 10e ...
… Compressed gas, 11… power take-out gear, 14 …… ring gear, 14
a: transmission external teeth, 14b: conical surface to be fitted, 15: power transmission gear, 15a: input external teeth, 15b: output conical surface, 16: shifter, 16a: shift internal teeth.

Claims (3)

(57) [Claims] A power take-out gear is fixed to an input shaft that transmits engine power taken out of a transmission and is constantly rotating, and is mounted movably on the input shaft in proximity to the power take-out gear. An annular gear and a power transmission gear having a core and the same diameter are arranged, and a shifter movable in the input shaft direction so as to be able to mesh with any of the gears simultaneously, and an operating rod displaced to move the shifter The ring gear has an inner surface formed with a fitted conical surface extending toward the power take-out gear, while the power transmission gear has an output conical surface fitted and detached from the fitted conical surface. In the power take-out device for a specially equipped vehicle having a synchronized mechanism, when the shifter is moved to mesh with the ring gear and the power transmission gear, an operating force in a pulling direction is generated. An electric motor that displaces the operation rod at a constant speed by using the electric rod. When the operation rod is pulled by the electric motor, the electric rod stores the displacement of the operation rod while absorbing the displacement of the operation rod from a point at which a predetermined or more meshing reaction force is received. By suppressing the movement of the shifter while applying force, the displacement of the operating rod is directly transmitted after the storage limit, and the shifter meshes with the ring gear, and the shifter completely meshes with the ring gear,
At the time when the meshing reaction force acting on the operating rod suddenly decreases, the variable-length buffer type energy storing means for releasing the above-mentioned accumulated power to the operating rod displaced at a constant speed and increasing the displacement of the operating rod, It is interposed in the operation rod of the portion outside the casing of the power take-off device, and after the shifter completes meshing with the ring gear, shortens the time until it starts meshing with the power transmission gear,
An operating mechanism for a power take-out device in a specially equipped vehicle, wherein the synchronous rotation speed of the power transmission gear can be suppressed from being significantly reduced during this time. 2. The variable-length buffer type energy storage means has a cylinder, a piston, and a piston rod, and the piston rod side is connected to the electric motor for applying an operation force in a pulling direction. The compression spring is interposed on the piston rod side.
The operation mechanism of the power take-out device in the specially equipped vehicle described in the above. 3. The variable-length buffer type energy storage means has a cylinder, a piston, and a piston rod, and the electric motor for applying an operation force in a pulling direction is connected to the piston rod side thereof. The operating mechanism of a power take-out device in a specially equipped vehicle according to claim 1, wherein a compressed gas is sealed in the rod side.