JP7621207B2 - Power transmission mechanism for working machine and walking type management machine - Google Patents

Description

The present invention relates to the technology of the power transmission mechanism of a work machine and a walk-behind cultivator.

Conventionally, technology for the power transmission mechanism of a work machine has been publicly known. For example, it is as described in Patent Document 1.

The differential lock device (power transmission mechanism) described in Patent Document 1 includes a pawl clutch and a fork. The pawl clutch is slidably mounted on the axle. The pawl clutch is configured to be able to mesh with a clutch engagement portion formed on the input sprocket. The fork can move the pawl clutch closer to or farther from the clutch engagement portion in response to the operation of the operating tool. By bringing the pawl clutch closer to the clutch engagement portion, the fork can engage the pawl clutch and the clutch engagement portion to prohibit differential motion. In addition, by moving the pawl clutch away from the clutch engagement portion, the fork can release the engagement and allow differential motion.

However, in the differential lock device of Patent Document 1, depending on the relative circumferential positional relationship between the claw clutch and the clutch engagement portion, when the claw clutch is brought close to each other, the end face of the claw clutch may come into contact with the end face of the clutch engagement portion, resulting in poor meshing and excessive load being applied to the forks.

JP 2011-63224 A

The present invention was made in consideration of the above-mentioned circumstances, and the problem it aims to solve is to provide a power transmission mechanism for a work machine and a walk-behind type cultivator that can prevent excessive load from being applied to the moving mechanism for moving the rotating member.

The problem that the present invention aims to solve is as described above, and the means for solving this problem will be explained next.

That is, in claim 1, the present invention provides a work power switching member that can switch between a power transmission state in which power can be transmitted to a work device and a power interruption state in which power cannot be transmitted to the work device by moving in a predetermined direction, a moving mechanism that can move the first rotating member or the second rotating member in a direction in which the first rotating member and the second rotating member approach or move away from each other, and a moving mechanism that is provided on the first rotating member so as to be able to advance and retreat toward the second rotating member, and that can move the first rotating member and the second rotating member together by engaging with the engaged portion. the moving mechanism comprises an engaging member that renders the first rotating member or the second rotating member physically rotatable, and a biasing member that biases the engaging member toward the second rotating member, the moving mechanism comprises a movable member that can move the first rotating member or the second rotating member and the working power switching member together, the movable member comprises a supported part that is supported so as to be movable along the predetermined direction, a first engaging part that can engage with the first rotating member or the second rotating member, and a second engaging part that can engage with the working power switching member, and the supported part, the first engaging part, and the second engaging part are formed by a single member .

In claim 2, the first rotating member is rotatable on the same axis as the rotation axis of the second rotating member, and the engaging member is movable in a direction parallel to the rotation axis.

In claim 3, the engaging member is formed in a cylindrical shape with its axis oriented in the direction of advancement and retreat.

In claim 4, either the first rotating member or the second rotating member is provided in a differential device that allows differential movement of the wheels, and the moving mechanism is capable of switching between a differential prohibition state in which the differential device prohibits differential movement of the wheels by moving the first rotating member or the second rotating member in one direction to engage the engaging member with the engaged portion, and a differential permission state in which the differential device allows differential movement of the wheels by moving the first rotating member or the second rotating member in the other direction to release the engagement between the engaging member and the engaged portion.

In claim 5, the moving mechanism is capable of switching the first rotating member or the second rotating member to the differential prohibited state and switching the working power switching member to the power transmission state by moving the first rotating member or the second rotating member, and the working power switching member in the one direction, and is capable of switching the first rotating member or the second rotating member to the differential permitted state and switching the working power switching member to the power interruption state by moving the first rotating member or the second rotating member, and the working power switching member in the other direction .

In claim 6, when the moving mechanism moves the first rotating member or the second rotating member, and the work power switching member in one direction, it is possible to engage the engaging member with the engaged portion before switching the work power switching member to the power transmission state .

According to a seventh aspect of the present invention, there is provided a power transmission mechanism for a work machine according to any one of the first to sixth aspects .

The effects of the present invention are as follows:

In claim 1, when the two rotating members (the first rotating member and the second rotating member) are moved toward each other, even if the engaging member and the engaged portion are not in mesh with each other, the engaging member retreats and the relative movement of the two rotating members is not impeded. This makes it possible to prevent excessive load from being applied to the moving mechanism for moving the rotating members. In addition, by sharing the mechanism (moving mechanism) for moving the first rotating member or the second rotating member and the work power switching member, the number of parts can be reduced, thereby saving space.

In claim 2, in a power transmission mechanism having a first rotating member and a second rotating member that rotate on the same axis, it is possible to prevent excessive load from being applied to the moving mechanism.

In claim 3, the configuration can be simplified.

In claim 4, it is possible to prevent excessive load from being applied to the moving mechanism when operating the differential device.

In the fifth aspect, the differential device and the working device are linked to each other, thereby improving operability .

According to the sixth aspect of the present invention, even if the working power switching member is in a state in which it cannot be switched to the power transmitting state, the working power switching member can be stably switched from the differential permitted state to the differential prohibited state .

In accordance with the seventh aspect of the present invention, it is possible to prevent an excessive load from being applied to the moving mechanism for moving the rotating member .

FIG. 2 is a side view showing a walk-behind type cultivator according to one embodiment of the working machine of the present invention. FIG. 4 is a front perspective view showing a portion of a shaft and a gear provided in a transmission case. FIG. Also, side view. FIG. 4 is a perspective view showing a configuration for switching whether or not power transmission is enabled. Also, side view. Also, front view. FIG. 1A is a perspective view of a PTO gear; 1A is a perspective view of a PTO shifter, FIG. 1B is a side view of the same, and FIG. FIG. 4 is a schematic cross-sectional view showing a claw portion of a PTO gear and a PTO shifter. 1A is a perspective view of a differential sprocket; 1A is an exploded perspective view showing the advance/retract mechanism, and FIG. 1A is a perspective view of a differential lock shifter, FIG. 1B is a side view of the same, and FIG. FIG. 4 is a schematic cross-sectional view showing a differential sprocket and a reciprocating mechanism. FIG. (a) is a side view of the same, and (b) is a front view of the same. 1A is a schematic cross-sectional view showing a state in which a claw portion of a PTO shifter is close to a claw portion of a PTO gear, and FIG. 1B is a schematic cross-sectional view showing a state in which a differential sprocket and a pin of a reciprocating mechanism are engaged with each other. 1A is a schematic cross-sectional view showing a state in which a PTO gear and a claw portion of a PTO shifter are engaged with each other, and FIG. 1B is a schematic cross-sectional view showing a state in which a differential sprocket and a pin of a reciprocating mechanism are engaged with each other. 1A is a schematic cross-sectional view showing a state before the PTO gear and the claws of the PTO shifter are engaged with each other, and FIG. 1B is a schematic cross-sectional view showing a state in which the teeth of the differential sprocket and the pin of the advance/retract mechanism are in contact with each other. 1A is a schematic cross-sectional view showing a state in which the PTO gear and the claws of the PTO shifter are engaged with each other, and FIG. 11 is a front cross-sectional view showing a state in which a pin of the advancing and retreating mechanism is pressed by a valley portion of a differential sprocket. FIG. FIG. 13 is a front cross-sectional view showing a modified example of the pin.

In the following, with reference to FIG. 1, a walk-behind cultivator 1 according to one embodiment of the working machine of the present invention will be described. In addition, in the following, the traveling direction of the walk-behind cultivator 1 will be described as the forward direction (the direction of the arrow F in the figure), the retreating direction as the rearward direction (the direction of the arrow B in the figure), the left side when the worker looks in the traveling direction as the leftward direction (the direction of the arrow L in the figure), the right side when the worker looks in the traveling direction as the rightward direction (the direction of the arrow R in the figure), the vertically upward direction as the upward direction (the direction of the arrow U in the figure), and the vertically downward direction as the downward direction (the direction of the arrow D in the figure).

The walk-behind cultivator 1 includes a machine frame 2, wheels 3, an engine 4, a fuel tank 5, a bonnet 6, a cover 7, a transmission case 8, a rotary tilling device 9, a clutch mechanism 10, a handle frame 11, a handle connection part 12, and a control handle 13.

The vehicle frame 2 is a member formed by appropriately bending a plate material. The vehicle frame 2 is supported by a pair of left and right wheels 3. The pair of left and right wheels 3 are configured to be able to move differentially by a differential gear 30, which will be described later. The engine 4 is mounted on the vehicle frame 2. The fuel tank 5 is disposed behind the engine 4. The engine 4 and the fuel tank 5 are covered by a bonnet 6. A cover 7 is provided to the side of the engine 4, which covers a clutch mechanism 10 that transmits the power of the engine 4 to a transmission case 8.

The transmission case 8 has a rotating shaft 8a that rotates when power is transmitted from the engine 4, and multiple shafts and gears (see FIG. 2) that transmit power to the rotating shaft 8a and the axle 3a. The rotary tilling device 9 has tilling tines 9a fixed to the rotating shaft 8a, and a tilling cover 9b that covers the upper part of the tilling tines 9a. The clutch mechanism 10 is used to switch between enabling and disabling the transmission of power from the engine 4 to the transmission case 8. The clutch mechanism 10 in this embodiment is assumed to be a so-called belt tension clutch that transmits power by applying tension to a belt wound around a pulley.

A handle frame 11 is disposed above the tilling cover 9b. The handle frame 11 is a frame for supporting a steering handle 13. The handle frame 11 is formed to extend rearward and upward. The steering handle 13 is attached to the rear upper end of the handle frame 11 via a handle connector 12.

The steering handle 13 is for the operator to operate. The steering handle 13 is equipped with an operable main clutch lever 13a and a differential lock lever 13b. The main clutch lever 13a is connected to the clutch mechanism 10 via a cable (not shown). The differential lock lever 13b is connected to the slide mechanism 90 (described later) via a cable 141 (see FIG. 6) etc.

When the main clutch lever 13a of the steering handle 13 of the walk-behind cultivator 1 configured as described above is operated, tension is applied to the belt and the clutch mechanism 10 is activated. This transmits power from the engine 4 to the transmission case 8. This allows the walk-behind cultivator 1 to rotate the wheels 3 and tilling tines 9a to cultivate the field.

In addition, when the operation of the main clutch lever 13a of the walk-behind cultivator 1 is released, tension is no longer applied to the belt and the operation of the clutch mechanism 10 is stopped. This stops the rotation of the wheels 3 and the tilling tines 9a.

In addition, the walk-behind cultivator 1 can switch between differential operation and non-differential operation of the pair of left and right wheels 3 by operating the differential lock lever 13b.

The power transmission mechanism 40 for transmitting power from the engine 4 will be described below with reference to Figures 1 to 4. The power transmission mechanism 40 is provided in the transmission case 8, and can transmit power from the engine 4 to the tilling tines 9a (rotary tilling device 9) and the wheels 3.

Below, we will briefly explain the power transmission from the engine 4 to the tiller tines 9a (rotary tiller 9) with reference to Figures 1 to 3. Note that Figures 2, 3, and Figure 4, which will be described later, show the shafts, gears, etc. provided in the transmission case 8. Also, for the sake of convenience, some gears and shafts are omitted from Figures 2 to 4.

When the engine 4 is driven, the power from the engine 4 is transmitted to the input shaft 21 via the clutch mechanism 10. The power is transmitted to the intermediate shaft 22 via the input gear 21a and the first intermediate gear 22a shown in Figures 2 and 3. The power transmitted to the intermediate shaft 22 is transmitted to the PTO shaft 23 via the PTO gear 50 described below, and is transmitted to the rotating shaft 8a shown in Figure 1 via the chain 23a attached to the PTO shaft 23. In this way, the power from the engine 4 is transmitted to the tilling tines 9a, allowing the tilling tines 9a to rotate.

Below, we will briefly explain the power transmission from the engine 4 to the wheels 3 with reference to Figures 1, 2 and 4.

As described above, the power from the engine 4 shown in FIG. 1 is transmitted from the input shaft 21 to the intermediate shaft 22. The power transmitted to the intermediate shaft 22 is transmitted to the transmission shaft 24 via the second intermediate gear 22b and the transmission gear 24a shown in FIGS. 2 and 4. The power transmitted to the transmission shaft 24 is transmitted to the differential device 30 via the transmission chain 24b attached to the transmission shaft 24.

The differential device 30 enables differential rotation of the wheels 3. The differential device 30 includes a differential sprocket 31, a pinion gear 32, and a side gear 33. The differential sprocket 31 is connected to the transmission shaft 24 via the transmission chain 24b. The pinion gear 32 is supported by the differential sprocket 31 and is configured to be able to rotate integrally with the rotation of the differential sprocket 31 and to be able to rotate (rotate) relative to the differential sprocket 31. The side gear 33 is supported by the axle 3a and meshes with the pinion gear 32.

Power from the engine 4 is transmitted to the differential sprocket 31 of the differential device 30 configured as described above via the transmission chain 24b. The power is then transmitted to a pair of left and right axles 3a via the pinion gear 32 and side gear 33. In this way, the power from the engine 4 is transmitted to a pair of left and right wheels 3, causing the wheels 3 to rotate. In addition, the differential device 30 allows the pinion gear 32 to rotate (spin) relative to the differential sprocket 31 in response to the load on the wheels 3, thereby differentially rotating the wheels 3 and making it easier to turn the walking cultivator 1.

The power transmission mechanism 40 can switch between transmitting power to the tilling tines 9a and differentially by the differential gear 30, using a slide mechanism 90 (described later) or the like. The configuration for switching between transmitting power and not transmitting it is described below.

As shown in Figures 3 and 5, the power transmission mechanism 40 includes a PTO gear 50, a PTO shifter 60, a differential sprocket 31, a forward/reverse mechanism 70, a differential lock shifter 80, and a slide mechanism 90. Note that only the components related to switching between enabling and disabling differential and enabling and disabling power transmission are shown in the figures from Figure 5 onwards.

As shown in Figures 7 to 9, the PTO gear 50 is formed in a generally cylindrical shape with its axis oriented in the left-right direction (parallel to the axis of the PTO shaft 23). The PTO gear 50 is formed in a stepped cylindrical shape with different diameters at the left portion, the middle left-right portions, and the right portion. The PTO gear 50 is supported by the PTO shaft 23 so as to be rotatable relative to the PTO shaft 23. The PTO gear 50 has an opposing surface 51 and a claw portion 52.

The facing surface 51 is the surface that faces the PTO shifter 60. The facing surface 51 is formed on the inside of the PTO gear 50. The facing surface 51 is also formed to face to the right.

The claw portion 52 is a portion that can engage with the PTO shifter 60. As shown in Figs. 9 and 11, the claw portion 52 is formed so as to protrude from the opposing surface 51 to the right (towards the PTO shifter 60). The claw portion 52 is formed in a substantially rectangular parallelepiped shape. A plurality of claw portions 52 (three in this embodiment) are formed at intervals in the circumferential direction of the PTO gear 50.

The PTO shifter 60 shown in Figures 8 and 10 is for switching whether or not power is transmitted to the tilling tines 9a. The PTO shifter 60 can switch whether or not power is transmitted by engaging or disengaging with the PTO gear 50, as described below. The PTO shifter 60 is formed in a generally cylindrical shape with its axis facing left and right. The PTO shifter 60 is formed in a stepped cylindrical shape with the outer diameter of the left and right middle parts being smaller than the outer diameter of both left and right ends. The PTO shifter 60 is formed so that it can enter the PTO gear 50 from the right. The PTO shifter 60 has an opposing surface 61, a claw portion 62, and a step portion 63. Below, the configuration of the PTO shifter 60 will be described based on the state in which the PTO gear 50 and the PTO shifter 60 are not engaged as shown in Figures 5 and 7.

The opposing surface 61 is the surface that faces the opposing surface 51 of the PTO gear 50. Specifically, the opposing surface 61 is the left side surface of the PTO shifter 60.

The claw portion 62 is a portion that can engage with the claw portion 52 of the PTO gear 50. As shown in Figures 10 and 11, the claw portion 62 is formed so as to protrude from the opposing surface 61 toward the left (toward the PTO gear 50). The claw portion 62 is formed in a substantially rectangular parallelepiped shape. A plurality of claw portions 62 (three in this embodiment) are formed at intervals in the circumferential direction of the PTO shifter 60. The intervals between the multiple claw portions 62 are set to be substantially the same as the intervals between the multiple claw portions 52 of the PTO gear 50.

The stepped portion 63 is a portion that engages with the shift fork 150 (see FIG. 8) described later. The stepped portion 63 is formed in the middle of the left and right sides of the PTO shifter 60. The stepped portion 63 is formed so that its outer diameter is smaller than the other portions.

As shown in Figures 5 and 7, the PTO shifter 60 is supported on the right end of the PTO shaft 23. The PTO shifter 60 is configured to be movable relative to the PTO shaft 23 in the left-right direction and to be rotatable integrally with the PTO shaft 23 by being spline-fitted to the PTO shaft 23, etc. The PTO shifter 60 is disposed to the right of the PTO gear 50. The opposing surface 61 of the PTO shifter 60 faces the opposing surface 51 of the PTO gear 50 (see Figure 11).

The PTO shifter 60 configured as described above can switch between transmitting power to the tilling tines 9a and not transmitting power to the tilling tines 9a by moving left and right. Specifically, the PTO shifter 60 approaches the PTO gear 50 by moving leftward from the state shown in Figures 5 and 7, and enters the PTO gear 50. The claw portion 62 of the PTO shifter 60 meshes with the claw portion 52 of the PTO gear 50. Specifically, the claw portion 62 of the PTO shifter 60 is disposed on one side in the circumferential direction of the claw portion 52 of the PTO gear 50 (see Figure 19 (a)).

In this way, the PTO shifter 60 has its own claws 62 abutting (engaging) with the claws 52 of the PTO gear 50, and rotates integrally with the rotation of the PTO gear 50. The PTO shaft 23 rotates integrally with the PTO shifter 60, and power from the engine 4 is transmitted to the tilling tines 9a via the chain 23a. Hereinafter, this state in which power can be transmitted to the tilling tines 9a is referred to as the "power transmission state."

In addition, by moving the PTO shifter 60 to the right, as shown in FIG. 11, the claw portion 62 moves away from the claw portion 52 of the PTO gear 50 and disengages from the claw portion 52. In this way, the power transmission to the tilling tines 9a is cut off. Hereinafter, this state in which power cannot be transmitted to the tilling tines 9a is referred to as the "power cut-off state."

As shown in Figures 7, 8 and 12, the differential sprocket 31 is formed in a generally circular plate shape with its plate surface facing left and right. The differential sprocket 31 is supported by the axle 3a via side gears 33 and is rotatable around the axle 3a as a rotation axis (see Figure 2). The differential sprocket 31 is manufactured, for example, by forging. The differential sprocket 31 has an opposing surface 31a and a through hole 31b.

The facing surface 31a is the surface that faces the differential lock shifter 80. Specifically, the facing surface 31a is the right side surface of the differential sprocket 31.

The through hole 31b shown in FIG. 12 is a hole that penetrates the differential sprocket 31 from left to right. The through hole 31b is formed in a generally circular shape when viewed from the side. Multiple through holes 31b (two in this embodiment) are provided at intervals in the circumferential direction of the differential sprocket 31.

The advance/retract mechanism 70 shown in Figures 5, 7, and 13 advances and retreats with a pin 72, which will be described later. The advance/retract mechanism 70 is provided in each through hole 31b of the differential sprocket 31. The advance/retract mechanism 70 includes a fixed member 71, a pin 72, a circlip 73, and a spring 74.

The fixing member 71 is a generally cylindrical member fixed to the differential sprocket 31. The fixing member 71 is arranged with its axis oriented in the left-right direction. The fixing member 71 is fixed to the through-hole 31b of the differential sprocket 31 by welding. The right end of the fixing member 71 is arranged so as not to protrude to the right (towards the differential lock shifter 80) beyond the opposing surface 31a of the differential sprocket 31. As shown in FIG. 13(b), the fixing member 71 has a small diameter portion 71a and a large diameter portion 71b.

The small diameter portion 71a is a portion of the inner circumferential surface of the fixed member 71 that has a smaller diameter than the other portions. The small diameter portion 71a is formed on the right side of the fixed member 71. The large diameter portion 71b is a portion of the inner circumferential surface of the fixed member 71 excluding the small diameter portion 71a. The large diameter portion 71b is formed so as to extend from the left end portion of the fixed member 71 to the middle portion on the left and right.

The pin 72 is a generally cylindrical member that can engage with the diff-lock shifter 80. The pin 72 is arranged so that its axial direction faces the left-right direction and its flange-shaped head 72a faces left. The head 72a of the pin 72 has an outer diameter that is generally the same as the inner diameter of the large diameter portion 71b of the fixing member 71. The shaft portion 72b of the pin 72 has an outer diameter that is generally the same as the inner diameter of the small diameter portion 71a and is formed so that its axial width (left-right length) is larger than that of the small diameter portion 71a.

The pin 72 configured as described above is inserted into the fixed member 71 from the left side (the side of the large diameter portion 71b). In this way, the head portion 72a of the pin 72 is disposed within the large diameter portion 71b, and the shaft portion 72b is inserted into the small diameter portion 71a, so that the pin 72 is slidable in the left-right direction (the same direction as the axial direction of the pin 72) relative to the fixed member 71.

The circlip 73 is for holding the spring 74, which will be described later. The circlip 73 is fixed to the large diameter portion 71b of the fixing member 71 and is positioned to the left of the pin 72 with a gap between them.

The spring 74 biases the pin 72 to the right. The right end of the spring 74 abuts against the head 72a of the pin 72. The left end of the spring 74 abuts against the circlip 73. The spring 74 is made of a coil spring.

The pin 72 of the advance/retract mechanism 70 configured as described above is positioned in a state in which the head 72a slides to the right end of the large diameter portion 71b due to the biasing force of the spring 74, and the shaft portion 72b protrudes to the right from the small diameter portion 71a. When the pin 72 is pressed to the left, it slides to the left on the fixed member 71 against the biasing force of the spring 74. In this way, the pin 72 can move so as to enter the fixed member 71.

The diff-lock shifter 80 shown in Figures 5 and 7 is used to switch between differential and non-differential driving of the wheels 3. As described below, the diff-lock shifter 80 can switch between differential and non-differential driving by engaging or disengaging with the pin 72 of the forward/reverse mechanism 70. Below, the configuration of the diff-lock shifter 80 will be described based on the state in which the diff-lock shifter 80 and the pin 72 are not engaged as shown in Figures 5 and 7.

As shown in Figures 8 and 14, the diff-lock shifter 80 is formed in a generally plate-like shape with the plate surface facing in the left-right direction. The diff-lock shifter 80 is formed in a generally annular shape when viewed from the side. The diff-lock shifter 80 is manufactured, for example, by forging. The diff-lock shifter 80 has an opposing surface 81, a peak portion 82, a valley portion 83, and a step portion 84.

The opposing surface 81 is the surface that faces the opposing surface 31a of the differential sprocket 31. Specifically, the opposing surface 81 is the left side surface of the differential lock shifter 80.

The peaks 82 are portions that protrude from the opposing surface 81 to the left (towards the differential sprocket 31). The peaks 82 are formed at the radially outer end of the differential lock shifter 80. Multiple peaks 82 (four in this embodiment) are formed at intervals around the circumference of the differential lock shifter 80.

The valley portion 83 is a portion recessed to the right (opposite side from the differential sprocket 31) of the peak portion 82. A plurality of valley portions 83 (four in this embodiment) are formed so as to be continuous with the peak portion 82 in the circumferential direction. As shown in FIG. 15, the valley portion 83 is formed so that the circumferential width (vertical width in FIG. 15) is longer than the outer diameter of the pin 72, and is formed so that the pin 72 can enter inside.

The step portion 84 is the portion that engages with the shift fork 150 (see FIG. 8). The step portion 84 is formed in the middle of the left and right sides of the PTO shifter 60. The step portion 84 is formed so that its outer diameter is smaller than the other portions.

The pin 72 (see FIG. 8, etc.) of the differential sprocket 31 is positioned to face the outer periphery of the differential lock shifter 80. In other words, the pin 72 is positioned to face the peak portion 82 or the valley portion 83.

As shown in Figures 5 and 6, the differential lock shifter 80 is supported by the right axle 3a and is positioned to the right of the differential sprocket 31. Thus, the opposing surface 81 of the differential lock shifter 80 faces the opposing surface 31a of the differential sprocket 31. The valley portion 83 is positioned on the same circumference as the pin 72 (see Figure 15). The differential lock shifter 80 is configured to be movable relative to the axle 3a in the left-right direction and to rotate integrally with the axle 3a by being spline-fitted to the axle 3a, etc. In this way, the differential lock shifter 80 can rotate coaxially with the differential sprocket 31. Furthermore, as shown in Figures 6 and 7, the differential lock shifter 80 is positioned below the front left of the PTO shifter 60.

The differential lock shifter 80 configured as described above can switch between differential and non-differential operation by moving left and right (in a direction parallel to the movement direction of the PTO shifter 60). Specifically, the differential lock shifter 80 moves leftward from the state shown in Figures 5, 7, and 15 to approach the differential sprocket 31. The valley portion 83 of the differential lock shifter 80 engages with the pin 72 of the forward and backward movement mechanism 70 as the pin 72 enters the valley portion 83 (see Figure 19 (b)).

When the valley portion 83 and the pin 72 engage in this way, a rotational force can be transmitted from the pin 72 to the differential lock shifter 80, and the differential lock shifter 80 and the differential sprocket 31 rotate together as the differential sprocket 31 rotates. This causes the pair of left and right axles 3a to rotate together, and differential rotation of the wheels 3 is prohibited. Hereinafter, this state in which differential rotation is prohibited is referred to as the "differential rotation prohibited state."

In addition, by moving the diff-lock shifter 80 to the right, as shown in FIG. 15, the valley portion 83 moves away from the pin 72, and disengages from the pin 72. In this way, differential movement of the wheels 3 is permitted. Hereinafter, this state in which differential movement is permitted is referred to as the "differential permitted state."

The slide mechanism 90 is for operating the PTO shifter 60 and the diff-lock shifter 80. As shown in Figures 5 to 8, the slide mechanism 90 includes a shaft 100, a pin 110, a receiving member 120, a spring 130, a connecting member 140, and a shift fork 150.

The shaft 100 is for supporting the shift fork 150 (described later) so that it can move left and right. The shaft 100 is arranged with its axis oriented left and right. The shaft 100 is supported rotatably by the transmission case 8 (not shown).

The pin 110 is inserted into the middle of the shaft 100 on the left and right. The pin 110 is arranged with its axial direction facing the radial direction of the shaft 100. One end and the other end of the pin 110 in the axial direction are formed to protrude from the outer periphery of the shaft 100.

The receiving member 120 receives the shift fork 150. The receiving member 120 is formed in a generally annular shape with an outer diameter larger than the outer diameter of the shaft 100, and is fitted into a groove (not shown) formed in the shaft 100. The receiving member 120 is disposed to the right of the pin 110 and the shift fork 150. In this way, the receiving member 120 can restrict the rightward movement of the shift fork 150 (receive the shift fork 150).

The spring 130 biases the shift fork 150. The spring 130 is disposed to the left of the pin 110, sandwiching the shift fork 150, and biases the shift fork 150 to the right.

The connection member 140 connects the shaft 100 and the diff-lock lever 13b shown in FIG. 1. The connection member 140 is formed in a generally L-shape with a bent midway point of the plate surface. The connection member 140 is fixed to the right end of the shaft 100. The connection member 140 is connected to the diff-lock lever 13b via a cable 141 and a spring 142 shown in FIG. 6, and is configured to be rotatable in response to the operation of the diff-lock lever 13b. In addition, the connection member 140 can rotate the shaft 100 in response to its own rotation.

The shift fork 150 shown in Figures 8, 16, and 17 is for moving the PTO shifter 60 and the differential lock shifter 80 together. The shift fork 150 is formed in a roughly L-shape when viewed from the side (see Figure 17(b)). The shift fork 150 includes a cylindrical portion 151, a differential connection portion 152, a differential engagement portion 153, a PTO connection portion 154, a PTO engagement portion 155, a first rib 156, and a second rib 157.

The cylindrical portion 151 is a portion formed in a substantially cylindrical shape. The cylindrical portion 151 is formed so that the axis direction faces the left-right direction. The cylindrical portion 151 is formed so that the shaft 100 can be inserted therethrough. The cylindrical portion 151 has a notch 151a.

The notch 151a is formed by cutting out the cylindrical portion 151 from the right. One end face in the circumferential direction of the notch 151a (the upper end face in FIG. 17(b)) is formed to extend in the left-right direction. The other end face in the circumferential direction of the notch 151a (the lower end face in FIG. 17(b)) of the notch 151a is formed to approach the one end face side (upper side) as it moves leftward. Two notches 151a are formed with a gap between them in the circumferential direction.

The differential connection part 152 is a part that connects the cylindrical part 151 and the differential engagement part 153 described below. The differential connection part 152 is formed in a substantially plate shape. The differential connection part 152 is formed so as to extend linearly forward from the cylindrical part 151.

The differential engagement portion 153 is a portion that can engage with the differential lock shifter 80. The differential engagement portion 153 is formed so as to be continuous with the front end portion of the differential connection portion 152. The differential engagement portion 153 is formed in a generally semicircular shape in a side view with the opening facing forward. The differential engagement portion 153 has an abutment portion 153a.

The contact portion 153a is a portion that contacts the differential lock shifter 80. The contact portion 153a is formed to be thicker than other portions. A plurality of contact portions 153a are formed at intervals in the circumferential direction of the differential engagement portion 153. Specifically, the contact portions 153a are formed at two positions (both ends in the circumferential direction of the differential engagement portion 153) that face each other across the center C153 of the differential engagement portion 153, and at one position between the two positions (a position spaced approximately 90 degrees from each end of the differential engagement portion 153). In other words, a total of three contact portions 153a are formed.

The PTO connection part 154 is a part that connects the cylindrical part 151 and the PTO engagement part 155 described later. The PTO connection part 154 is formed in a generally plate shape. The PTO connection part 154 is formed so as to extend upward from the cylindrical part 151 in a side view (see FIG. 17(a)). A first bent part 154a that bends to the right is formed at the bottom of the PTO connection part 154. In addition, a second bent part 154b that bends upward is formed to the right of the first bent part 154a. In this way, the PTO connection part 154 is formed so that the upper end is shifted to the right with respect to the lower end (see FIG. 17(b)).

The PTO engagement portion 155 is a portion that can engage with the PTO shifter 60. The PTO engagement portion 155 is formed so as to be continuous with the upper end of the PTO connection portion 154. The PTO engagement portion 155 is formed in a generally semicircular shape in a side view with an opening facing forward and upward. The PTO engagement portion 155 is formed so as not to overlap with the differential engagement portion 153 in a side view (see FIG. 17(a)). More specifically, the PTO engagement portion 155 is formed rearward and upward of the differential engagement portion 153 in a side view. The angle α formed by the line L2 connecting the center C155 of the PTO engagement portion 155 and the center C151 of the cylindrical portion 151 and the line L1 connecting the center C153 of the differential engagement portion 153 and the center C151 is formed to be 90 degrees or less in a side view. The PTO engagement portion 155 is also formed at a position displaced in the left-right direction with respect to the differential engagement portion 153. More specifically, the PTO engagement portion 155 is formed so that its left-right position is shifted to the right relative to the left-right position of the differential engagement portion 153 (see FIG. 17(b)). The PTO engagement portion 155 has an abutment portion 155a.

The contact portion 155a is a portion that contacts the PTO shifter 60. The contact portion 155a is formed to be thicker than other portions. A plurality of contact portions 155a are formed at intervals in the circumferential direction of the PTO engagement portion 155. Specifically, the contact portions 155a are formed at two positions (both ends in the circumferential direction of the PTO engagement portion 155) that face each other across the center C155 of the PTO engagement portion 155, and at one position between the two positions (a position spaced approximately 90 degrees from each end of the PTO engagement portion 155). In other words, a total of three contact portions 155a are formed.

The first rib 156 and the second rib 157 are portions that reinforce the first bent portion 154a. The first rib 156 and the second rib 157 are formed to span the cylindrical portion 151 and the PTO connection portion 154. The second rib 157 is positioned to the right of the first rib 156, sandwiching the PTO connection portion 154 between them.

As shown in Figs. 5 and 7, the cylindrical portion 151 of the shift fork 150 configured as described above is inserted into the shaft 100 and is supported on the shaft 100 so as to be movable relative to the shaft 100 in the left-right direction. The pin 110 abuts against the notch 151a of the cylindrical portion 151. The differential engagement portion 153 is fitted into the step portion 84 of the differential lock shifter 80. The PTO engagement portion 155 is fitted into the step portion 63 of the PTO shifter 60. In this way, the PTO shifter 60 and the differential lock shifter 80 are engaged with the shift fork 150 so as to be rotatable relative to the shift fork 150 and to be movable integrally in the left-right direction.

The operation of the slide mechanism 90 configured as described above is described below.

The slide mechanism 90 can slide the PTO shifter 60 and the diff-lock shifter 80 together in the left-right direction in response to the forward and backward swinging of the diff-lock lever 13b shown in FIG. 1, thereby switching the state of the PTO shifter 60, etc. The following describes an example in which the diff-lock lever 13b is swung forward.

When the diff-lock lever 13b is swung forward, the connecting member 140 of the slide mechanism 90 shown in FIG. 6 is pulled rearward and upward, and the connecting member 140 and the shaft 100 rotate in the clockwise direction in FIG. 6. With this rotation, the pin 110 rotates in the same direction as the shaft 100 and presses the notch 151a (the inclined portion) of the shift fork 150 shown in FIG. 7. As a result, the rotational motion of the shaft 100 is converted into the linear motion of the shift fork 150, and the shift fork 150 moves leftward against the biasing force of the spring 130.

As the shift fork 150 moves leftward, the PTO shifter 60 and the diff-lock shifter 80 move leftward together with the shift fork 150. This brings the PTO shifter 60 closer to the PTO gear 50. The diff-lock shifter 80 also moves closer to the diff sprocket 31.

In this embodiment, the arrangement of the PTO shifter 60 and the diff-lock shifter 80 and the shape of the claws 62 are appropriately set so that the valleys 83 of the diff-lock shifter 80 reach a position where they engage with the other side (the pins 72 of the forward/reverse mechanism 70) before the claws 62 of the PTO shifter 60. Therefore, when the shift fork 150 moves leftward, as shown in FIG. 18, the pins 72 of the forward/reverse mechanism 70 enter the valleys 83 of the diff-lock shifter 80, and the valleys 83 and the pins 72 engage with each other. In this way, the diff-lock shifter 80 is switched from the differential permission state to the differential prohibition state. At this time, the claws 62 of the PTO shifter 60 are positioned to the right of the claws 52 of the PTO gear 50 (see distance D shown in FIG. 18(a)).

When the shift fork 150 moves further to the left from the state shown in FIG. 18, the claw portion 62 of the PTO shifter 60 reaches a position where it meshes with the claw portion 52 of the PTO gear 50, as shown in FIG. 19. In this way, the claw portion 62 of the PTO shifter 60 engages with the claw portion 52 of the PTO gear 50, and the PTO shifter 60 is switched from the power interruption state to the power transmission state.

As shown in FIG. 20(b), depending on the rotational positions of the differential sprocket 31 and the differential lock shifter 80, the differential lock shifter 80 may be moved to the left with the valleys 83 and the pins 72 misaligned in the circumferential direction. In this case, the peaks 82 approach the pins 72 and come into contact with each other.

When the diff-lock shifter 80 moves further to the left from this state, as shown in FIG. 21, the pin 72 is pressed to the left by the peak 82 and moves to the left against the biasing force of the spring 74. In this way, even if the pin 72 and peak 82 are in contact with each other, the diff-lock shifter 80 can push the pin 72 to the left (move it back), and the movement to the left is not restricted. Therefore, the shift fork 150 can move the diff-lock shifter 80 smoothly even if the pin 72 and peak 82 are facing each other. This makes it possible to prevent excessive load from being applied to the slide mechanism 90 that moves the diff-lock shifter 80.

As shown in FIG. 21(a), the shift fork 150 can cause the claw portion 62 of the PTO shifter 60 to reach a position where it meshes with the claw portion 52 of the PTO gear 50, regardless of whether the pin 72 and the valley portion 83 are engaged. This allows the shift fork 150 to switch the PTO shifter 60 to a power transmission state, regardless of whether the pin 72 and the valley portion 83 are engaged.

In addition, since the PTO gear 50 has a relatively high rotation speed (compared to the differential sprocket 31), even if the end faces of the claws 52 and 62 come into contact with each other, the PTO gear 50 rotates relative to the PTO shifter 60, releasing the contact between the end faces, and the claws 52 and 62 are quickly engaged.

In addition, when a rotational difference occurs between the pair of left and right wheels 3, the differential sprocket 31 and the differential lock shifter 80 rotate relative to each other from the state shown in FIG. 21, and the pin 72 and the valley portion 83 face each other. This releases the pressure on the pin 72 from the peak portion 82, and the pin 72 moves to the right (towards the differential lock shifter 80) due to the biasing force of the spring 74. In this way, the pin 72 and the valley portion 83 engage, and the differential lock shifter 80 is switched to a differential prohibition state (see FIG. 19(b)).

When the differential lock shifter 80 is switched to the differential inhibition state and rotates by the power from the engine 4, the inner surfaces of the peaks 82 and valleys 83 press the pin 72 as shown in FIG. 22. At this time, a force acts on the pin 72 along the circumferential direction of the differential lock shifter 80 from the contact portion between the pin 72 and the inner surfaces of the peaks 82 and valleys 83 (see the arrows in FIG. 22). In this embodiment, the arrangement of the pin 72 and the shapes of the peaks 82 and valleys 83 are appropriately set so that the center C72 of the pin 72 is located in the direction of the force acting on the contact portion (on the extension of the arrow in FIG. 22). With this configuration, when the peaks 82 and valleys 83 press the pin 72, a force acts toward the center C72 of the pin 72, reducing the load on the pin 72.

Here, the shift fork 150 can move the diff-lock shifter 80 to the left and switch to a differential inhibition state by swinging the diff-lock lever 13b forward, and can also move the PTO shifter 60 to the left and switch to a power transmission state. With this configuration, by operating a single operating tool (diff-lock lever 13b), it is possible to easily switch to a state in which tilling work can be performed favorably (a state in which the walk-behind cultivator 1 can easily move in a straight line and the tilling tines 9a can rotate), for example. This improves operability.

When the diff-lock lever 13b shown in FIG. 1 is swung backward, the shaft 100 and the pin 110 rotate in the opposite direction (counterclockwise in FIG. 6) to when it is swung forward. In this case, the shift fork 150 shown in FIGS. 5 and 7 is biased by the spring 130 to move to the right.

The PTO shifter 60 and the diff-lock shifter 80 move together to the right as the shift fork 150 moves to the right. In this way, the PTO shifter 60 and the diff-lock shifter 80 move away from the PTO gear 50 and the diff sprocket 31.

In this way, by swinging the diff-lock lever 13b backward, the shift fork 150 can move the diff-lock shifter 80 to the right to switch to a differential permission state, and move the PTO shifter 60 to the right to switch to a power cut-off state. With this configuration, by operating a single operating tool (diff-lock lever 13b), it is possible to easily switch to a state in which, for example, normal driving and turning can be performed favorably (a state in which the walk-behind cultivator 1 can turn easily and the tiller tines 9a cannot turn). This improves operability.

In addition, the state of the PTO shifter 60 and the diff-lock shifter 80 can be changed simultaneously using a single part (shift fork 150), reducing the number of parts and saving space.

As described above, the power transmission mechanism 40 of the walk-behind cultivator 1 (working machine) according to this embodiment includes the differential sprocket 31 (first rotating member), the differential lock shifter 80 (second rotating member) on which the concave valley portion 83 (engaged portion) is formed, a slide mechanism 90 (moving mechanism) capable of moving the differential lock shifter 80 (the first rotating member or the second rotating member) in a direction (left-right direction) in which the differential sprocket 31 and the differential lock shifter 80 approach or move away from each other, a pin 72 (engagement member) that is provided on the differential sprocket 31 so as to be able to move toward or away from the differential lock shifter 80 and engages with the valley portion 83 to make the differential sprocket 31 and the differential lock shifter 80 rotatable together, and a spring 74 (urging member) that urges the pin 72 toward the differential lock shifter 80.

By configuring it in this way, even if the pin 72 and the valley portion 83 are not in meshing (cannot engage) when the differential sprocket 31 and the differential lock shifter 80 are moved toward each other, the pin 72 retracts and the relative movement between the differential sprocket 31 and the differential lock shifter 80 is not impeded. This makes it possible to prevent excessive load from being applied to the slide mechanism 90.

The differential sprocket 31 can rotate on the same axis as the rotation shaft (axle 3a) of the differential lock shifter 80, and the pin 72 can move back and forth in a direction parallel to the rotation shaft (left and right direction).

By configuring it in this way, it is possible to prevent excessive load from being applied to the slide mechanism 90 in the power transmission mechanism 40, which has a differential sprocket 31 and a differential lock shifter 80 that rotate on the same axis.

The pin 72 is formed in a cylindrical shape with its axis facing in the direction of advancement and retreat (left and right direction).

By configuring it in this way, the configuration can be simplified.

The differential sprocket 31 (either the first rotating member or the second rotating member) is provided in a differential device 30 that allows differential movement of the wheels 3, and the slide mechanism 90 can switch between a differential prohibition state in which the differential device 30 prohibits differential movement of the wheels 3 by moving the differential lock shifter 80 in one direction (leftward) to engage the pin 72 with the valley portion 83, and a differential permission state in which the differential device 30 allows differential movement of the wheels 3 by moving the differential lock shifter 80 in the other direction (rightward) to release the engagement between the pin 72 and the valley portion 83.

This configuration makes it possible to prevent excessive load from being applied to the slide mechanism 90 when operating the differential device 30 (when switching between the differential prohibited state and the differential permitted state).

The power transmission mechanism 40 further includes a PTO shifter 60 (working power switching member) that can be switched between a power transmission state in which power can be transmitted to the rotary tilling device 9 (working device) and a power cut-off state in which power cannot be transmitted to the rotary tilling device 9 by moving in a predetermined direction (left and right direction), and the slide mechanism 90 moves the diff-lock shifter 80 and the PTO shifter 60 together.

In this way, by sharing the same mechanism (slide mechanism 90) for moving the diff-lock shifter 80 and the PTO shifter 60, the number of parts can be reduced, resulting in space savings.

The slide mechanism 90 can switch the diff-lock shifter 80 to the differential prohibition state and the PTO shifter 60 to the power transmission state by moving the diff-lock shifter 80 and the PTO shifter 60 in the one direction (left direction), and can switch the diff-lock shifter 80 to the differential permission state and the PTO shifter 60 to the power interruption state by moving the diff-lock shifter 80 and the PTO shifter 60 in the other direction (right direction).

By linking the differential gear 30 and the rotary tilling device 9 in this way, operability can be improved.

In addition, when the slide mechanism 90 moves the diff-lock shifter 80 and the PTO shifter 60 in one direction (leftward), it is possible for the pin 72 to engage with the valley portion 83 before the PTO shifter 60 is switched to the power transmission state (see FIG. 18).

By configuring it in this way, even when the PTO shifter 60 cannot be switched to a power transmission state (when the end faces of the claws 52 and 62 are in contact with each other), it is possible to stably switch from the differentially permitted state to the differentially prohibited state.

The walk-behind cultivator 1 according to this embodiment is also equipped with the power transmission mechanism 40.

This configuration can prevent excessive load from being applied to the slide mechanism 90.

The walk-behind cultivator 1 according to this embodiment is one embodiment of a working machine.
Moreover, the differential sprocket 31 according to this embodiment is one embodiment of a first rotating member.
Moreover, the valley portion 83 according to this embodiment is one embodiment of the engaged portion.
The diff-lock shifter 80 according to this embodiment is an embodiment of a second rotating member.
Moreover, the slide mechanism 90 according to the present embodiment is one embodiment of a moving mechanism.
Moreover, the pin 72 according to the present embodiment is one embodiment of an engagement member.
Moreover, the spring 74 according to this embodiment is one embodiment of a biasing member.
Moreover, the rotary tilling implement 9 according to this embodiment is one embodiment of a working implement.
The PTO shifter 60 according to this embodiment is an embodiment of a work power switching member.

Although an embodiment of the present invention has been described above, the present invention is not limited to the above configuration, and various modifications are possible within the scope of the invention described in the claims.

For example, the working machine was a walk-behind cultivator 1, but the type of working machine is not limited to this and may be a harvester, a lawnmower, etc.

Movement of the shift fork 150 to the left switches the PTO shifter 60 to the power transmission state and the diff-lock shifter 80 to the differential inhibition state, and movement of the shift fork 150 to the right switches the PTO shifter 60 to the power cut-off state and the diff-lock shifter 80 to the differential permissible state, but the relationship between the movement direction of the shift fork 150 and the switching between the power transmission state, power cut-off state, differential inhibition state, and differential permissible state is not particularly limited.

In addition, the valley portion 83 of the diff-lock shifter 80 engages with the pin 72 of the forward/reverse mechanism 70 before the claw portion 62 of the PTO shifter 60 engages with the PTO gear 50 (see FIG. 18), but the timing at which the valley portion 83 engages with the pin 72 is not particularly limited. For example, the valley portion 83 may engage with the pin 72 at the same timing that the PTO shifter 60 engages with the PTO gear 50.

The positional relationship between the differential engagement portion 153 and the PTO engagement portion 155 of the shift fork 150 is not particularly limited. That is, the differential engagement portion 153 is formed so as not to overlap with the PTO engagement portion 155 in a side view (see FIG. 17(a)), but this is not limited to this and can be changed as desired depending on the arrangement of the differential lock shifter 80 and the PTO shifter 60, etc. Also, the differential engagement portion 153 is formed at a position displaced in the left-right direction relative to the PTO engagement portion 155 (see FIG. 17(b)), but this is not limited to this and can be changed as desired depending on the arrangement of the differential lock shifter 80, etc.

In addition, the angle α between the straight line L1 connecting the differential engagement portion 153 and the cylindrical portion 151 and the straight line L2 connecting the PTO engagement portion 155 and the cylindrical portion 151 is formed to be 90 degrees or less in a side view (see FIG. 17(a)), but is not limited to this and can be any angle.

In addition, the shift fork 150 does not necessarily have to include the first rib 156 and the second rib 157.

In addition, in this embodiment, the differential sprocket 31 and the differential lock shifter 80 are shown as an example of the first rotating member and the second rotating member according to the present invention, but the present invention is not limited to this and can be applied to various rotatable members. In addition, in this embodiment, an example is shown in which the second rotating member (diff lock shifter 80) is moved in a direction toward or away from the first rotating member (diff sprocket 31), but the present invention is not limited to this and it is also possible to configure the first rotating member, or both the first rotating member and the second rotating member, to move.

In addition, in this embodiment, the pin 72 that moves in the direction of the rotation axis (left and right direction) of the differential sprocket 31 is exemplified as an example of an engagement member, but the configuration of the engagement member is not limited to this. The movement direction of the engagement member can be changed as desired as long as it moves toward and away from the second rotating member on which the valley portion 83 (engaged portion) is formed. For example, the pin 72 can be arranged to move toward and away from the radial direction, and configured to engage with the valley portion 83 (engaged portion) arranged on the radial outer or inner side.

In addition, in this embodiment, the differential lock shifter 80 is provided with the valley portion 83, and the differential sprocket 31 is provided with the pin 72, but the member on which the pin 72 and the valley portion 83 are provided is not limited to this. In other words, the pin 72 and the valley portion 83 may be provided on two different rotating members.

In addition, the pin 72 is biased by a coil spring (spring 74), but the biasing member that biases the pin 72 is not limited to a coil spring, and may be another type of spring or an elastic body such as resin.

In addition, two pins 72 (advance/retract mechanism 70) are provided, but the number of pins 72 is not particularly limited and can be changed as desired depending on the shape of the differential sprocket 31, etc.

In addition, although the pin 72 is formed in a generally cylindrical shape, the shape of the pin 72 is not particularly limited and can be changed as desired. FIG. 23 shows a modified version of the pin 72 in which the shape of the pin 72 has been changed. The pin 72 in FIG. 23 is formed in a generally rectangular parallelepiped shape. The pin 72 has a flat portion 72c that fits along the inner side of the valley portion 83. The flat portion 72c of the pin 72 abuts against the inner side of the valley portion 83, thereby engaging with the valley portion 83. With this configuration, the contact area of the pin 72 with the valley portion 83 can be increased (surface contact).

In addition, although four valleys 83 are formed in the diff-lock shifter 80, the number of valleys 83 is not particularly limited and can be set arbitrarily depending on the shape of the diff-lock shifter 80, etc.

In addition, the differential sprocket 31 and the differential lock shifter 80 are manufactured by, for example, forging, but they may also be machined and manufactured by, for example, a lathe or milling machine, and the manufacturing method is not limited.

1. Walk-behind management machine (working machine)
31 Differential sprocket (first rotating member)
40 Power transmission mechanism 72 Pin (engagement member)
74 Spring (biasing member)
80 Diff lock shifter (second rotating member)
83 Valley part (engaged part)
90 Slide mechanism (movement mechanism)

Claims (7)

A first rotating member;
A second rotating member having a concave engaged portion formed thereon;
a work power switching member that can switch between a power transmission state in which power can be transmitted to the work device and a power interruption state in which power cannot be transmitted to the work device by moving in a predetermined direction;
a moving mechanism capable of moving the first rotating member or the second rotating member in a direction in which the first rotating member and the second rotating member approach or move away from each other;
an engaging member provided on the first rotating member so as to be movable toward and away from the second rotating member, and engaging with the engaged portion to make the first rotating member and the second rotating member rotatable together;
a biasing member that biases the engagement member toward the second rotation member;
Equipped with
The moving mechanism includes:
The first rotating member or the second rotating member and the working power switching member are integrally moved by a movable member.
The movable member is
A supported portion that is supported so as to be movable along the predetermined direction;
A first engagement portion engageable with the first rotating member or the second rotating member;
A second engagement portion engageable with the working power switching member;
Equipped with
the supported portion, the first engaging portion, and the second engaging portion are formed of a single member,
Power transmission mechanism for work equipment. The first rotating member is
The second rotating member is rotatable on a same axis as the rotation axis of the second rotating member,
The engaging member is
The movable member can move forward and backward in a direction parallel to the rotation axis.
The power transmission mechanism of a working machine according to claim 1. The engaging member is
It is formed in a cylindrical shape with its axis facing the direction of advancement and retreat.
The power transmission mechanism of a working machine according to claim 1 or 2. Either the first rotating member or the second rotating member is
A differential device is provided to enable differential movement of the wheels.
The moving mechanism includes:
a differential inhibition state in which the first rotating member or the second rotating member is moved in one direction to cause the engaging member to engage with the engaged portion, thereby inhibiting differential motion of the wheels by the differential gear;
a differential allowing state in which the first rotating member or the second rotating member is moved in another direction to release the engagement between the engaging member and the engaged portion, thereby allowing differential motion of the wheels by the differential gear;
It is possible to switch between
The power transmission mechanism of a working machine according to any one of claims 1 to 3. The moving mechanism includes:
By moving the first rotating member or the second rotating member, and the working power switching member in the one direction, it is possible to switch the first rotating member or the second rotating member to the differential prohibition state and switch the working power switching member to the power transmission state,
By moving the first rotating member or the second rotating member and the working power switching member in the other direction, it is possible to switch the first rotating member or the second rotating member to the differential allowing state and switch the working power switching member to the power interrupting state.
The power transmission mechanism for a work machine according to claim 4. The moving mechanism includes:
When the first rotating member or the second rotating member and the working power switching member are moved in the one direction, the engaging member can be engaged with the engaged portion before the working power switching member is switched to the power transmission state.
The power transmission mechanism of a working machine according to claim 5. The power transmission mechanism of the working machine according to any one of claims 1 to 6 is provided.
Walk-behind management machine.

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