KR20230142383A - Transmission device of paddy field working machine - Google Patents

Abstract

The arrangement structure of the driving side rotating member, the driven side rotating member, the clutch operating member, and the compression spring is studied to miniaturize the work case portion. In addition, the transmission case is structured to facilitate diversification of the specifications of the faucet work machine, to miniaturize the main parts of the transmission case, and to avoid an increase in the number of parts and weight of the entire transmission case. do. In addition, the size of the engagement margin at the engagement point between the gear pair and the shift key at each shift stage of the plurality of gear pairs is set to a size in accordance with the transmission torque for each gear pair, thereby attempting to miniaturize the transmission device.
The work clutch 8 in the work case portion 4 is provided with a driving side rotating member 80, a driven side rotating member 81, and a compression spring 82, and is provided on the outer peripheral side of the driven side rotating member 81. A clutch operating member (83) is engaged with the engaging portion (81c) and is capable of operating the driven side rotating member (81) to a side away from the driving side rotating member (80) by resisting the pressing spring (82). , the compression spring 82 is installed on the inward side in the radial direction from the engaging portion of the clutch operating member 83 and the engaging portion 81c. In addition, a seeding work case portion 4 is provided with a built-in seeding system transmission mechanism that changes and transmits the power output from the main case portion 3 to the seedling transplant device or the seeding device, and the seeding work case portion 4 , It is constructed separately from the main case portion 3, and is integrally connected and fixed to the main case portion 3, and the main case portion 3 and the seeding operation case portion 4 are connected to each other. In a sealed state where the openings formed at the connection points are joined to each other, the respective internal spaces are in communication with each other. In addition, it is provided with a plurality of gear pairs arranged in a constantly engaged state and a shift operation body 1070 that selects one of the gear pairs, and the shift operation body 1070 is an electric gear constituting the gear pair. It is provided with a shift key portion 1071 that can be alternatively coupled to and detachable from any one of the electric gears as a locking target, and the locking engagement margin of the shift key portion 1071 with respect to the locking target electric gear is a plurality of gears. Among the pairs, the gear pair with a shorter weekly pitch or seeding pitch is configured to become larger as it is selected.

Description

Electric device of faucet work machine {TRANSMISSION DEVICE OF PADDY FIELD WORKING MACHINE}

In the present invention, a traveling body capable of driving and moving on a pavement is provided with a main case portion that outputs shifting power to a traveling drive system and a working case portion that outputs shifting power to a working device, and the working case portion is provided with a working case portion from a working shifting mechanism. It relates to a power transmission device for a work machine that has a built-in work clutch that can control power transmission to the drive shaft.

In addition, the present invention relates to a power transmission device for a water-hydraulic work machine equipped with a traveling body capable of traveling across a field and a working device such as a seedling transplant device for transplanting seedlings to the ground or a direct seeding device for sowing rice seeds to the ground.

In addition, the present invention relates to a power transmission device for a water-hydraulic work machine equipped with a traveling body capable of traveling across a field and a working device such as a seedling transplant device for transplanting seedlings to the ground or a direct seeding device for sowing rice seeds to the ground.

In installing the work clutch, in the conventional structure, the engaging portion of the driving side rotating member and the driven rotating member, the engaging portion of the clutch operation member with respect to the driven rotating member, and the pressing spring are located at the working case portion. They were arranged in order in the axial direction of the output shaft inside (see Patent Document 1).

On the other hand, a power receiving work machine equipped with a work device of the seeding system, such as a seedling transplant device or a direct seeding device, is provided with a fertilizing power extraction structure for supplying the power of the engine mounted on the traveling body to the fertilizing device. As an example of a water faucet work machine having this structure, there is one having the structure described in [1] below.

[1] The transmission mechanism of the traveling drive system and the main transmission mechanism are built into the inside of the transmission case, and the fertilization drive case is disposed at the rear of the transmission case. In addition, the traveling transmission shaft for the rear wheel drive that protrudes rearward from the transmission case extends rearwardly through the fertilization drive case, and is capable of branching and transmitting the driving force toward the fertilization device in the middle of the traveling transmission shaft (patent document) 2).

On the other hand, in a power receiving work machine equipped with a work device of a type seeding system, such as a seedling transplanter or a direct seeding device, the power of the engine mounted on the traveling body is taken out to supply power to the seedling transplanting device or a direct seeding device separately from the traveling drive system. It has a structure. As an example of a water faucet work machine having this structure, there is one having the structure described in [2] below.

[2] Inside the transmission case, a traveling unit transmission unit of the traveling drive system and a transmission unit between the first and second mains for the seedling transplant device are built in. The power shifted from the travel unit transmission unit is output to the front and rear wheels via the output shaft and transmission chain, and the power shifted from the first and second main transmission units is output to the seedling transplant device via the power extraction shaft. In the first and second day shift units, a plurality of gear pairs are used, and the target gear pair is selected with a shift key (clutch body in the patent document) provided in each shift unit, so that multi-stage day shift can be performed. It is composed (see Patent Document 3).

Japanese Patent Laid-Open No. 2008-173087 (paragraph numbers “0038” and “0039”, see Figs. 5 and 7) Japanese Patent Publication No. 2015-223110 (paragraph numbers “0086”, “0092”, “0094”, see Figs. 9, 13, and 14) Japanese Patent Laid-Open No. 2008-289399 (paragraph numbers “0032”, “0036”, “0038”, “0050”, see Figs. 3, 4, and 6)

In the transmission device of the work machine described in Patent Document 1, a space corresponding to the sum of the axial length of the driving side rotating member, the axial length of the driven side rotating member, and the axial length of the compression spring is provided to the output shaft in the work case portion. There is room for improvement in that it is difficult to miniaturize the electric transmission device.

The present invention seeks to further miniaturize the work case section by devising an arrangement structure of the driving side rotation member, the driven side rotation member, the clutch operation member, and the compression spring within the work case section.

On the other hand, the water faucet work machine described in Patent Document 2 is provided with a fertilization drive case separately from the transmission case. Therefore, compared to the case where the fertilization drive mechanism is also built into the mission case, it is useful in that the enlargement of the mission case itself can be avoided. However, since the inside of the transmission case is equipped with a day shift mechanism in addition to the travel drive system shift mechanism, there is room for improvement in that it is difficult to achieve further miniaturization of the mission case.

In addition, if the fertilization drive case is provided separately from the transmission case in this way, the fertilization drive case is removed from the faucet work machine of specifications not equipped with a fertilization device, and the fertilization drive case is installed only on the faucet work machine of specifications provided with a fertilization device. As mentioned above, it is advantageous in that it is easy to obtain a structure according to the specifications of the faucet work machine.

However, if the transmission case and the fertilization drive case are made up of different cases that are independent of each other, it is convenient to diversify the specifications, but each case requires a bearing structure or seal structure inside it. It is easy to cause an increase in the number of parts. In addition, at the connection point between cases, opposing walls are connected to each other at the connection portion to form a double wall structure, so there is a risk that the overall weight will increase, and there is room for improvement in this respect.

The present invention has a structure that makes it easy to diversify the specifications of the transmission case, and miniaturization of the main parts of the transmission case, and also increases the number of parts and weight of the entire transmission case. This is to avoid an increase.

On the other hand, in the water faucet work machine described in Patent Document 3, the structures of the engaging portions of each gear pair at the engaging portions of the gear pair of each shift stage and the shift key are all configured to substantially the same specifications. . Accordingly, the same engaging state is obtained in the engaging engagement of the shift key for each gear pair, even when one of a plurality of gear pairs is selected as the engaging target.

However, each gear pair, which is a gear for shifting, has a structure in which the gear diameter is set in various ways depending on the transmission ratio, and the transmission torque is also different for each shift stage. For this reason, the required strength also differs depending on the required torque for a gear pair whose transmission torque is set to be small and a gear pair whose transmission torque is set to be large.

However, in the structure described in Patent Document 3, the engaging engagement margin of all gear pairs with respect to the shifting key is set to be the same, so that all gear pairs and shifting keys are adjusted according to the gear pair set to transmit the maximum torque. If the jamming margin is designed to be large, the following problems may occur. That is, in a gear pair at a shift stage where the assumed transmission torque is small, the engagement margin of the shift key is structured to be excessively large beyond necessity.

Therefore, when the engaging margin of the electric gear on the smaller diameter side of the gear pair is increased, the electric gear itself tends to have a larger diameter in order to secure the engaging margin. Also, as the diameter of the transmission gear on the small diameter side increases, the diameter of the transmission gear on the large diameter side that meshes with it inevitably increases, and there is a risk that the entire gear pair may become large, and there is room for improvement in this regard.

The present invention aims to miniaturize the transmission device by setting the engagement margin at the engagement point between the gear pair and the shift key at each shift stage of a plurality of gear pairs to a size in accordance with the transmission torque for each gear pair. It is done.

The characteristic of the transmission device of the work machine in the present invention is that it has a main case part that has a shifting mechanism for shifting the input engine power and outputs the shifting power to the traveling drive system, and a main case part that shifts the engine power input through the main case part. A work case unit is provided that has a work-type shifting mechanism built in and outputs shift power to a work device, wherein the work case portion includes a work drive shaft that transmits shift power from the work-type shift mechanism to the work device, and the work case portion. A work clutch capable of interdicting power transmission from the system transmission mechanism to the work drive shaft is built-in, and the work clutch includes a drive-side rotating member to which power from the work system transmission mechanism is transmitted from the upper side in the power transmission direction; A driven-side rotating member is externally fitted to the work drive shaft at a lower side in the power transmission direction than the drive-side rotating member and is rotatably supported integrally with the work drive shaft,

The driving-side rotating member and the driven-side rotating member have engaging portions capable of transmitting power in an engaged state on their respective opposing surfaces, and the driven-side rotating member with respect to the driving-side rotating member is, A compression spring configured to be movable along the axial direction of the work drive shaft and pressurizing the driven side rotation member toward the drive side rotation member is externally fitted to the work drive shaft and resists the compression force of the compression spring. A clutch operating member capable of manipulating the driven-side rotating member to a side away from the driving-side rotating member is installed, and the clutch operating member engages the engaging portion formed on the outer circumferential side of the driven-side rotating member to engage the driven side rotating member. The same-side rotating member is configured to be operable toward a side away from the driving-side rotating member, and the pressing spring is located on an inward side in the radial direction of the driven-side rotating member than the engaging portion of the clutch operating member and the engaging portion. It is equipped.

According to the present invention, the contact position of the compression spring with respect to the driven side rotating member is located on the inner side in the radial direction than the engaging point without being restricted by the presence position of the engaging point of the clutch operation member and the engaging part. Since it can be set, there is an advantage that it is easy to shorten the internal space of the work case portion in the moving direction of the driven side rotation member while using a compression spring of the required length.

In the present invention, a spring accommodating portion is formed on a surface of the driven side rotating member opposite to the side on which the engaging portion is formed, and this spring accommodating portion engages the clutch operating member and the engaging portion in the axial direction of the work drive shaft. It is suitable if it is installed at a location near the opposing surface side where the engaging portion is formed, rather than at a coupling location.

According to the present invention, since the spring receiving portion is installed in the axial direction of the work drive shaft at a location closer to the opposing surface side where the engaging portion is formed than the engaging portion of the clutch operating member and the engaging portion, in the moving direction of the driven rotating member, By overlapping the driven side rotation member and the compression spring, the internal space of the work case portion can be reliably shortened.

In the present invention, the pressing spring is mounted between the spring receiving portion and the fixing portion on the inner surface of the working case portion, and is located on the other end side rather than the one end side in the axial direction of the working drive shaft. It is suitable if it is formed in a conical shape with a large winding diameter.

By providing this configuration, it becomes difficult for the compression spring to be deformed, such as bending in a direction intersecting the expansion/contraction direction, and it is easy to exert the spring force accurately.

In the present invention, the compression spring has a winding diameter on the side supported by the spring receiving portion of the driven side rotation member larger than the winding diameter on the opposite side, and the winding diameter on the opposite side is that of the compression spring. It is suitable if the inner peripheral surface is set to contact the outer peripheral surface of the work drive shaft.

By providing this configuration, the winding diameter on the side supported by the spring receiving portion is increased, and the winding diameter on the opposite side is made small and set to a level that contacts the outer peripheral surface of the work drive shaft, thereby eliminating the need for the addition of a special fixing member for the compression spring. It is easy to install stably.

In the present invention, the clutch operating member includes an operating pin that penetrates the work case portion and is operated around a rotation axis in a direction intersecting the axis of the work drive shaft, and the operating pin in a portion exposed to the outside of the work case portion. It is suitable to have an operating plate installed at the end of the shaft, and to have an operating guide member for positioning in the direction along the rotational axis of the operating plate in the work case portion.

By providing this configuration, escape from the work case portion can be reliably controlled without impairing the operability of the clutch operating member.

In the present invention, the operation guide member is suitable as long as it has a guide portion capable of allowing operation around the rotation axis of the operation plate within a range corresponding to the on-off operation range of the work clutch.

By providing this configuration, the operation range by the clutch operation member can be properly recognized using means for regulating the clutch operation member's escape from the work case portion, and operability can be improved with a simple structure.

In the present invention, the work drive shaft includes an output transmission shaft that rotates integrally with the driven side rotation member, and is externally fitted to the output transmission shaft so that it can rotate relative to the output transmission shaft, so that power in the transmission direction above the output transmission shaft is transmitted. It is provided with a dual shaft structure portion formed by a shaft body, and of the above-mentioned normal shaft body, the portion located most upward in the rolling direction is inserted into the inner circumferential side of the barrel boss of the output bevel gear located in the main case portion, and the portion located most upward in the rolling direction is It is suitable if the inner circumferential passage of the normal shaft body at the portion located in connects the inside of the main case portion and the dual shaft structure portion.

By providing this configuration, the space on the inner circumference side of the cylinder boss of the output bevel gear in the main case portion, the passage on the inner circumference side of the normal shaft body, and the dual shaft structure portion of the output transmission shaft body and the normal shaft body are effectively utilized, Lubricating oil can be guided to the work case side.

In the present invention, it is suitable if the normal shaft body is divided into a plurality of places in the axial direction of the output transmission shaft body, and a member that rotates together with the normal shaft body is mounted on each of the divided normal shaft bodies.

By providing this configuration, even if an output transmission shaft having a long axial length is used, appropriate lubrication can be performed by utilizing the clearance between the normal shafts existing in the middle.

The characteristic of the transmission device of the power receiving work machine in the present invention is that it is equipped with a main transmission mechanism that shifts the input engine power, and a auxiliary transmission mechanism that shifts the power transmitted from the main transmission mechanism into multiple stages and outputs it to the traveling drive system. A main case part is provided, and a planting work case part is provided with a planting system transmission mechanism that changes and transmits the power output from the main case part to a seedling transplant device or a seeding device, and the planting work case part is provided in the main case. It is constructed separately from the main case section and is integrally connected and fixed to the main case section, and the main case section and the type breaking operation case section are sealed by joining openings formed at mutual connection points. In this state, each internal space is connected to each other.

According to the present invention, the planting work case part which has a planting system transmission mechanism built in and transmits power to a seedling transplant device or a seeding device is different from the main case part equipped with a main transmission mechanism or a auxiliary transmission mechanism that outputs power to a traveling drive system. It is configured separately. As a result, the main case part, which is the main part of the transmission case, can be miniaturized, and the specifications of the type wave type transmission mechanism to be combined can be selected from various types, which has the advantage of making it easy to obtain a faucet work machine with a wide variety of specifications. .

Additionally, the main case portion and the cooling operation case portion are connected in a sealed state in which the openings formed at the connection points are joined to each other, and in a state in which the respective internal spaces are in communication with each other.

Accordingly, the case portions themselves are formed individually, but when combined and connected, they are configured as one sealed case with an internal space that communicates. This is also advantageous in that, as in the case of connecting completely individual cases, it is possible to avoid the double structure of the wall surfaces facing each other at the connection point, which increases the weight, and avoids the need for numerous shaft support structures and seal parts. .

In the present invention, a branch case unit is provided with a branch transmission mechanism for branching and transmitting the power output from the main case unit to a powder or grain supply device, and the branch case unit is configured separately from the main case unit, In addition, while being integrally connected and fixed to the main case portion, the main case portion and the branch case portion communicate with each other in a sealed state in which openings formed at connection points are joined to each other. If it is, it is suitable.

According to the present invention, the main case is equipped with a main transmission mechanism or a auxiliary transmission mechanism for outputting power to the traveling drive system, and a branch case unit that has a branch transmission mechanism built in to branch and transmit power output from the main case unit to the powder supply device. It is organized separately from the department. This has the advantage that the main case part, which is the main part of the transmission case, can be miniaturized, and the specifications of the branch transmission mechanism to be combined can be selected from various types, making it easy to obtain a water faucet work machine with a wide variety of specifications.

Additionally, the main case portion and the branch case portion are connected in a sealed state in which the openings formed at the connection points are joined to each other, and in a state in which the respective internal spaces are in communication with each other. Accordingly, the case portions themselves are formed individually, but when combined and connected, they are configured as one sealed case with an internal space that communicates. As a result, it is possible to avoid, as in the case of connecting completely individual cases, the wall portions facing each other at the connection point becoming a double structure, increasing the weight, or requiring numerous shaft support structures or seal parts.

In the present invention, the type wave system shifting mechanism includes a shift operation shaft spanning the inner space of the type wave operation case portion and the inner space of the main case portion, and a shift operation shaft that can be slidably operated along the axis direction of the shift operation shaft. It is suitable if it has a supported shift gear, and the slide operation range accompanying the shifting operation of the shift gear is set over the interior space of the cooling operation case portion and the interior space of the main case portion.

By providing this configuration, the inner space of the main case portion can also be used as a slide operation range accompanying the shifting operation of the shift gear. As a result, the volume of the space to be set within the internal space of the cooling work case portion within the slide operation range accompanying the shifting operation of the shift gear can be reduced, and miniaturization of the planting work case portion can be achieved.

In the present invention, the branch case portion is externally inserted into the traveling transmission shaft of the traveling drive system extending from the main case portion, and is oriented in a direction intersecting the input side normal portion supporting the traveling transmission shaft and the traveling transmission shaft. An output side cylindrical part is externally fitted to an extended branch drive shaft and supports the branch drive shaft, the input side cylindrical part is connected to the main case part, the output side cylindrical part is formed integrally with the input side cylindrical part, and is larger than the branch drive shaft. It is suitable if a bevel gear for branch output is installed in the input side normal part on the side close to the main case part.

By providing this configuration, compared to the case where the bevel gear for branch output is disposed on the side farther from the main case portion than the branch drive shaft, the space of the input side normal portion on the side farther from the main case portion than the branch drive shaft can be set to be small. As a result, miniaturization of the entire branch case portion can be achieved.

In the present invention, the branch input bevel gear meshed with the branch output bevel gear is supported on the branch drive shaft, the branch output bevel gear is supported on the travel transmission shaft, and the travel transmission shaft includes the above It is suitable if a positioning part that regulates the positional movement of the branch output bevel gear to the side opposite to the side where the branch input bevel gear exists is provided.

By providing this configuration, the branch case part can be built into the main case part while the branch output bevel gear is supported on the traveling transmission shaft, so it is easy to assemble and disassemble the branch case part.

In the present invention, it is suitable as long as the opening of the branch case portion formed at a location opposite to the main case portion has an inner diameter through which the branch output bevel gear supported on the traveling transmission shaft can be inserted.

By providing this configuration, the branch output bevel gear can be put in and out from the opening of the branch case portion while being supported on the traveling transmission shaft, so assembly and disassembly work of the branch output bevel gear and the traveling transmission shaft to the branch case portion can be performed. It's easy.

In the present invention, the input side end of the branch drive shaft is configured to be insertable and retractable with respect to the output side opening formed in the branch case portion, and the insertion limit position of the input side end of the branch drive shaft is in the branch case portion. It is a location corresponding to , and it is suitable if the traveling transmission shaft is supported at a position that abuts the end of the input side of the branch drive shaft.

By providing this configuration, it is easy to position the end position of the input side of the branch drive shaft with respect to the branch case portion.

In the present invention, the auxiliary transmission mechanism includes a pair of high-speed gears suitable for road driving, spanning an upper shift shaft located above in the power transmission direction and a lower shift shaft located below in the power transmission direction. A low-speed gear pair suitable for work travel is provided, and a shift member is provided on the lower shift shaft between the gear pairs, and the shift member is located in the axial direction of the lower shift shaft. The lower gear is movably supported and has engaging teeth protruding in the direction of existence of the lower gear located on the lower side in the power transmission direction among each gear pair, and is located opposite to both sides of the shift member. Each of the engaging recesses is formed to engage with the engaging teeth of the shift member, and among the engaging recesses, the engaging recesses of the lower gear in the high-speed gear pair suitable for road driving are the lower shift shaft. It is suitable if it has a shape that connects to the shaft support hole of the lower gear that is externally fitted.

By providing this configuration, the engagement concave portion of the lower gear can be formed simultaneously with the shaft support hole of the lower gear. Therefore, the position of the engaging concave portion can be made to have a small diameter that is as close as possible to the shaft diameter of the lower transmission shaft, and the lower gear in the high-speed gear pair can be formed with a smaller diameter. This is advantageous in that it is easy to increase the reduction ratio in a high-speed gear pair.

Additionally, by being connected to the shaft support hole of the lower gear, the shape of the engaging concave portion is also easy to keep simple.

In the present invention, an axle case through which the power of a traveling drive system is transmitted is provided, and the axle case includes a pair of bevel gears on the upper side of the transmission located on the upper side of the transmission shaft along the vertical direction, and a pair of bevel gears on the lower side of the transmission shaft. It is suitable if a bevel gear pair on the lower side of the transmission is provided, each bevel gear pair is reduced and transmitted, and the reduction ratio of the bevel gear pair on the lower side of the transmission is set to be larger than that of the bevel gear pair on the upper side of the transmission.

By providing this configuration, not only is the speed reduced on both the upper and lower sides of the transmission shaft in the axle case, but also on both upper and lower sides of the transmission shaft, the reduction ratio in the bevel gear pair on the lower side of the transmission is larger than the bevel gear pair on the upper side of the transmission. As a result, the reduction ratio at the area close to the final output point on the lower side of the transmission is made as large as possible, and the torque on the upstream side can be effectively reduced.

The characteristic of the electric transmission device of the electric power work machine in the present invention is that the seeding system shifting mechanism that changes the engine power and transmits it to the seedling transplanting device or the seeding device is built into the planting work case part, and the planting system shifting mechanism is located in the electric upper side. A plurality of gear pairs arranged in a state of constant engagement across the input side transmission shaft and the output side transmission shaft on the lower side of the transmission, and a shift operation body that enables power transmission by selecting one of the gear pairs, The shift operation body is provided with a shift key portion capable of selectively engaging and disengaging any one of the electric gears constituting the gear pair as an engaging object, and the shifting key for the electric gear as an engaging object. The locking engagement margin of the portion is configured to become larger as the gear pair in which the weekly pitch by the seedling transplant device or the seeding pitch by the seeding device is set to be shorter is selected among the plurality of gear pairs.

According to the present invention, among a plurality of gear pairs, the shorter the gear pair that is set to the weekly pitch by the seedling transplant device or the seeding pitch by the seeding device is selected, the engagement margin of the shift key portion for the electric gear to be engaged is increased. It is set to grow.

In other words, considering that a gear pair with a shorter weekly pitch by a seedling transplant device or a seeding pitch by a seeding device requires a larger transmission torque, the gear pair and the shift key at the portion where the weekly pitch or the seeding pitch is shortened are The engagement margin is larger than the engagement margin between the gear pair and the shifting key in the area where the main pitch or seeding pitch is long. As a result, the engagement margin between the gear pair and the shift key at each shift stage is set to a size according to the transmission torque for each gear pair, and the engagement margin for the gear pair in the portion where the main pitch or seeding pitch is long is determined. By omitting waste parts, it becomes possible to reduce the diameter as much as possible, thereby achieving compactness of the overall structure.

In the present invention, a plurality of devices are provided that set a gap in the axis direction of the input transmission shaft or the output transmission shaft between the electric gears disposed at adjacent positions in the axis direction of the input transmission shaft or the output transmission shaft. The collars are arranged, and the gap between the collars is such that the gear pair having a short weekly pitch by the seedling transplant device or a seeding pitch by the seeding device is present, the shift key portion for the electric gear It is suitable if it is set at wide intervals so that the amount of jamming increases.

According to the present invention, the weekly pitch by the seedling transplant device or the seeding pitch by the seeding device can be changed by using the colors for setting the space between the electric gears and changing the space between the colors.

Also, by changing the spacing between the collars, the amount of engagement of the shift key part between the collars with respect to the electric gear in the gear pair also changes, so it is simple to change the spacing between the collars. It is possible to obtain a structure in which it is possible to change the engaging amount of the shift key portion with respect to the electric gear.

In the present invention, the distance between the electric gears in the axial direction of the input-side transmission shaft or the output-side transmission shaft is greater than the distance between the electric gears existing at the location where the distance between the collars is widened. It is suitable if the gap between the electric gears present in the location where the gap is narrowed is narrowed.

According to the present invention, a plurality of gear pairs are arranged along the axis direction of the input-side transmission shaft or the output-side transmission shaft. And, in adjacent positions in the axial direction, the gap between the teeth of the electric gears constituting the gear pair is narrower than the gap between the teeth of the electric gears present at the location where the gap between the collars is widened. The gap between the teeth of the electric gear existing at this location is narrowed.

As a result, along with the gap between the collars, the gap between the teeth of the electric gear in the area where the transmission torque is small is narrowed, further compacting the type wave system shifting mechanism, making it easier to place in the type wave work case section. Consists of.

In the present invention, the shift operation body slides the shift key portion and the shift key portion in the axial direction of the input-side transmission shaft or the output-side transmission shaft, thereby locking the electric gear to be engaged. A slide operation unit for selecting and manipulating an engagement position is provided, wherein the shift key portion has a connection point to the slide operation unit as a swing point, and is engaged with the electric gear that intersects the slide operation direction by the slide operation unit. It is suitable if it is configured to allow oscillating operation in the direction.

By providing this configuration, the shift operation body includes a slide operation unit that selects and operates an engaging position for the electric gear, and a connection point to the slide operation unit as a swing point, and an electric transmission that intersects the direction of the slide operation by the slide operation unit. By using a shifting key configured to be oscillated in the engaging direction with the gear, the engaging depth by the shifting key can be appropriately set for each gear pair. And, the support portion of the slide operating portion in the transmission case equipped with this shift operating body may be provided with a sealed structure that can handle simple slide operations without the need to correspond to performing complex rocking operations of the slide operating portion. Therefore, it is easy to adopt a relatively simple structure as the seal structure.

In the present invention, the shift operating body is provided with an elastic pressing mechanism that presses the shift key portion against the electric gear side to be engaged, and the pressing portion by the elastic pressing mechanism is located at a plurality of the gears. The gear pair is set at a position further away from the swing point than the pair, and the weekly pitch by the seedling transplant device or the seeding pitch by the seeding device is set shorter, the closer the gear pair is to the pressing point by the elastic pressing mechanism. It is suitable if it is located near the shaking point and away from it.

By providing this configuration, an elastic pressing mechanism is provided to press the shift key portion against the electric gear side of the locking target, so that the locking depth of the shift key with respect to the gear pair is increased with the slide operation of the shift operating body. It can be adjusted automatically.

In addition, the pressing point by the elastic pressing mechanism is set at a position further away from the swing point than the plurality of gear pairs, and the shorter the weekly pitch by the seedling transplant device or the seeding pitch by the seeding device is set, the shorter the gear pair is, Since it is located near the swing point side from the pressing point by the elastic pressing mechanism, the pressing action by the elastic pressing mechanism acts more strongly in a gear pair whose main pitch or seeding pitch is set shorter by the action of the lever.

Accordingly, even when a large torque acts on the engaging point between the gear pair and the shifting key, there is a small possibility that the shifting key will easily be released from the engaging position between the gear pair and the shifting key.

Figure 1 is a left side view of a riding-type rice transplanter.
Figure 2 is a diagram showing a power transmission system.
Figure 3 is an exploded cross-sectional view of the main case portion in the mission case.
Figure 4 is a cross-sectional view in the vertical direction of the main case part in the mission case.
Figure 5 is a cross-sectional view in the horizontal direction of the branch case portion in the mission case.
Figure 6 is a perspective view showing the connection state of the main case section and the branch case section with respect to the main case section.
Fig. 7 is an explanatory diagram showing a meshing portion between the shift member and the lower gear in the auxiliary transmission mechanism.
Fig. 8 is a plan view showing the operating tool of the implantable clutch.
Fig. 9 is an exploded perspective view showing the operating tool of the transplant clutch.
Fig. 10 is a cross-sectional view in the vertical direction of the axle case on the front wheel side.
Figure 11 is a left side view of a riding-type rice transplanter.
Figure 12 is a diagram showing the power transmission system.
Figure 13 is an exploded cross-sectional view of the main case portion in the mission case.
Fig. 14 is an explanatory diagram showing the engaging portion between the shift member and the lower gear in the auxiliary transmission mechanism.
Fig. 15 is a perspective view showing the connection state of the main case section and the branch case section with respect to the main case section.
Figure 16 is a cross-sectional view in the vertical direction of the main case part in the mission case.
Fig. 17 is an enlarged cross-sectional view in the vertical direction of the type wave system shifting mechanism in the main case portion.
Fig. 18 is a plan view showing the operating portion of the type wave type shifting mechanism.
Fig. 19 is a plan view showing the operating tool of the implantable clutch.
Fig. 20 is an exploded perspective view showing the operating tool of the transplant clutch.
Fig. 21 is a cross-sectional view in the horizontal direction of the branch case portion in the mission case.
Fig. 22 is an explanatory diagram showing a pattern display portion in the lever guide portion for daytime shifting.
Fig. 23 is an explanatory diagram showing a pattern display portion of the lever guide portion in another embodiment.

Hereinafter, an example of an embodiment of the present invention will be described based on the description of the drawings.

In addition, in the description of this embodiment, the front-back direction and the left-right direction are described as follows, unless otherwise specified. That is, the forward direction (see arrow F in FIGS. 1 and 2) of a work machine (traveling body 1) such as a riding-type rice transplanter to which the present invention is applied is "forward" and backward. The direction of travel (see arrow B in Figs. 1 and 2) is “back,” and the direction corresponding to the right (see arrow R in Figs. 2 and 3) based on the forward posture in the forward and backward directions is “back.” “Right”, and similarly, the direction corresponding to the left (see arrow L in Figs. 2 and 3) is “left”.

[Full configuration]

Figure 1 shows an example of the application of the electric device of the working machine in the present invention, and is provided with working devices such as a seedling transplant device for transplanting seedlings to the ground or a direct seeding device for sowing rice seeds on the ground (seeding system work device). The left side of a riding-type rice transplanter as an example of a one-hand operation machine is shown.

This riding-type rice transplanter is provided with a pair of left and right front wheels 11F that can be steered and driven as a traveling drive device below the body frame 10, and a pair of left and right rear wheels 11R that can be driven, and the body frame 10 It is provided with a self-propelled traveling body 1 in which front wheels 11F and rear wheels 11R are driven by receiving power from an engine E mounted on 10.

In the traveling body 1, a driving unit 13 containing an engine E is provided in the front part of the body on the operating section floor 14. A passenger with a steering handle 15 for steering the front wheels 11F and a driver's seat 12 on the driver's floor 14 in the center of the traveling body 1 in the anteroposterior direction at the rear side of the propulsion unit 13. A driver's unit is provided.

A fertilizing device 9 (equivalent to a granular material supply device) is mounted on the rear portion of the driver's seat 12. The fertilization device 9 supplies the fertilizer stored in the fertilizer tank 90 in a predetermined amount from a feeding device not shown, and equips the seedling transplant device 2 through a supply path not shown. ) and is configured to be supplied in packaging. On the rear side of the traveling body 1, the seedling transplant device 2 is supported so as to be able to be raised and lowered through a link mechanism 25 having a hydraulic cylinder 26 for lifting and lowering operation.

The riding-type rice transplanter configured in this way performs the operation of transplanting seedlings, such as rice, to the field using the seedling transplanting device 2.

In the front part of the traveling body 1, a loading stand 17 for spare seedlings is arranged on both left and right sides of the motor unit 13 at a distance in the left and right directions sufficient to allow forward and backward movement. At the rear of the traveling body 1, the seedling transplant device 2 is supported so as to be able to be raised and lowered through a link mechanism 25 having a hydraulic cylinder 26 for lifting and lowering operation.

The riding-type rice transplanter configured in this way performs the operation of transplanting seedlings, such as rice, to the field using the seedling transplanting device 2.

The seedling transplant device 2 is comprised of a four-piece type, including an electric case 21, a transplant case 22 rotatably supported on the right and left lateral sides of the rear part of the electric case 21, and a transplant case 22. It is provided with a pair of transplanting arms 23 (planting hook drive mechanism) provided at both ends of the case 22, a grounding float 24, and a seedling loading stand 20 on which seedlings are loaded. As the seedling loading stand 20 is driven to reciprocate left and right, the transplanting case 22 is rotated, and the transplanting arms 23 alternately take out the seedlings from the lower part of the seedling loading stand 20. It is designed to be transplanted onto the field.

In the traveling body 1, a transmission case M supporting the front wheel 11F is connected and fixed to the front part of the body frame 10, and at the rear part of the body frame 10, the rear wheel The axle case 19 equipped with (11R) on the left and right is supported. A front frame 10F extends forward from the transmission case M, and an engine E is mounted laterally on this front frame 10F.

As shown in Figs. 2 and 3, axle cases 16 extend outward on both left and right sides of the transmission case M, and left and right front wheels 11F and 11F are installed.

The axle case 19 of the rear wheel 11R is elastically supported on the lower side of the left and right pairs of front and rear frames 10A and 10A so that the left and right can move up and down separately through suspension springs 18, allowing left and right rolling operations. It is installed properly.

[Power transmission system]

The power transmission structure in the mission case (M) through which the power of the engine (E) is transmitted will be described.

The power of the engine E input to the mission case M is a driving drive system for driving the front wheels 11F and the rear wheels 11R, etc. within the mission case M, and a seedling transplant device as a planting system work device. (2) Alternatively, the output is branched to a work device drive system for driving a seeding device (not shown) and a fertilization drive system for driving the fertilization device 9.

The transmission case M includes a main case part 3 that houses the auxiliary transmission mechanism 3A of the traveling drive system, etc., and a main case part 4 (working case) disposed on the rear side of the main case part 3. It is equipped with a case part (equivalent to the type breaking operation case part) and a case part (5).

The main case part 4 is a main shift mechanism 4A (corresponding to a work type shift mechanism and a planting type shift mechanism) that changes and transmits the power output from the main case part 3 to the seedling transplant device 2. The branch case portion 5 includes a branch transmission mechanism 5A that branches and transmits the power output from the main case portion 3 to the fertilization device 9.

The power of the engine E is transmitted to the pump shaft 60a of the hydrostatic continuously variable transmission device 6 mounted on the outer wall of the main case portion 3 in the transmission case M, and the hydrostatic continuously variable transmission It is input from the motor shaft 61a of the device 6 into the inside of the case body 30 in the main case portion 3. That is, the hydrostatic continuously variable transmission 6 is used as a continuously variable main transmission, and the power output from the main transmission is further shifted within the transmission case M.

[Driving drive system]

First, the transmission structure of the traveling drive system will be explained.

As shown in FIG. 2, the power of the engine E is transmitted to the pump shaft 60a, which is the shift input shaft of the hydrostatic continuously variable transmission 6, through the belt transmission mechanism 62 and is supplied to the hydraulic pump 60. is driven to rotate.

The motor shaft 61a, which is the shift output shaft of the hydrostatic continuously variable transmission 6, is connected to the first shift shaft 31 (corresponding to the upper shift shaft) within the case body 30 of the main case portion 3. , are connected in a spline-fitting state, and the first shift shaft 31 is rotationally driven as the motor 61 rotates.

As shown in FIG. 3, the upper low-speed gear 31a of the traveling drive system and the upper high-speed gear 31b of the traveling drive system are equipped to rotate integrally on the first shift shaft 31, and also a gear for deceleration transmission of the work device drive system. The output gear 31c is installed to rotate integrally.

Of this first shifting shaft 31, the end opposite to the side connected to the motor shaft 61a is a shaft portion ( It is inserted into and fitted into the tubular boss portion 33b of the extension shaft 33 provided with 33a) and pivoted to enable relative rotation. The extension shaft 33 is provided with an implanted electric gear 33c on the outer periphery of the barrel boss portion 33b, and has a first shaft portion 33a that penetrates the side wall 30b and protrudes to the outside of the case body 30. The external gear 36a is supported so as to be fully rotatable.

The output gear 31c for reduction transmission and the transplant transmission gear 33c are meshed with a relay gear 32f that is loosely and rotatably fitted to a second shift shaft 32, which will be described later.

A second shift shaft 32 (corresponding to the lower shift shaft), which has an axis parallel to the first shift shaft 31, is axially supported by the case main body 30. This second shift shaft 32 includes a lower low-speed gear 32a (corresponding to the lower gear) meshing with the upper low-speed gear 31a, and a lower high-speed gear 32b meshing with the upper high-speed gear 31b ( (corresponding to the lower gear) is axially supported on the second shift shaft 32 so as to be capable of relative rotation.

A gear pair of the upper low-speed gear 31a and the lower low-speed gear 32a, a gear pair of the upper high-speed gear 31b and the lower high-speed gear 32b, and a second shift shaft 32 between these gear pairs. The auxiliary transmission mechanism 3A is configured by providing a shift member 34 axially supported on ).

Among the gear pairs, the combination of the upper low-speed gear 31a and the lower low-speed gear 32a is a low-speed gear pair suitable for work driving, and the combination of the upper high-speed gear 31b and the lower high-speed gear 32b is a gear pair for road driving. It is a gear pair suitable for high speed.

The shift member 34 is spline-fitted to the second shift shaft 32, is supported so as to be rotatable integrally with the second shift shaft 32, and can slide in the axis direction of the second shift shaft 32. there is. On the left and right sides of the shift member 34 opposing each pair of gears on both left and right sides, there is a lower low speed gear 32a and a lower high speed gear 32b located on the lower side in the power transmission direction among each gear pair. It is provided with engaging teeth 34a and 34b that protrude in both left and right directions.

And, each of the lower low-speed gear 32a and the lower high-speed gear 32b at a position opposite to the shift member 34 has a gear that alternatively engages with the engaging teeth 34a and 34b of the shift member 34. Engaging recesses 32c and 32d are formed.

Among the engaging teeth 34a and 34b of the shift member 34, the engaging tooth 34a on the side opposite to the lower low-speed gear 32a with a large diameter is near the outer peripheral edge of the shift member 34, and performs the second shifting. It is formed at a location spaced apart from the outer peripheral surface of the shaft 32. The engaging teeth 34b on the side opposite to the lower high-speed gear 32b with a small diameter on the opposite side are formed near the inner peripheral edge of the shift member 34 at a location close to the outer peripheral surface of the second shift shaft 32. .

Among the engaging recesses 32c and 32d, the engaging recessed portion 32c formed on the lower low-speed gear 32a is capable of engaging with the engaging teeth 34a on the shift member 34 side at a position opposite to it. In shape, it is formed at a location spaced apart from the outer peripheral surface of the second shift shaft 32. In addition, the engagement concave portion 32d formed in the lower high-speed gear 32b has a shape that can be engaged with the engagement tooth portion 34b on the side of the shift member 34 located opposite to the engagement concave portion 32d, and the second shift shaft 32 It is formed in a location close to the outer circumference of the .

As shown in FIG. 7, the engagement concave portion 32d formed in the lower high-speed gear 32b is formed with the shaft support hole 32e of the lower high-speed gear 32b externally fitted to the second shift shaft 32. It is formed in a connected shape. As a result, the engagement concave portion 32d formed on the lower high-speed gear 32b is formed as close to the outer peripheral surface of the second shift shaft 32 as possible.

The shift member 34 includes a case main body ( 30) is configured to be operable from the outside.

The position at which the operating rod 34d is pressed into the case body 30 is the position where the shift member 34 selects the low-speed gear pair suitable for work travel, and the operating rod 34d is most pressed into the case body 30. The position pulled out to the outside of is the position where the shift member 34 selects the high-speed gear pair suitable for road driving. The state in which the shift member 34 is in an intermediate position where neither gear pair is selected is the neutral position.

The power transmitted to the second shift shaft 32 through the shift member 34 is transmitted to the front wheel output gear 35b through the interlocking gear 35a fixed to the second shift shaft 32. The front wheel output gear 35b is spline-fitted to the outer peripheral portion of the right end side of the cylinder member 35c externally fitted to be rotatable relative to the front wheel drive shaft 63. The left end side of the cylinder member 35c is rotatably connected to the differential gear case 70 through the boss portion of the bevel gear 35d for rear wheel output splined to the outer peripheral portion.

Therefore, when the front wheel output gear 35b is driven, the rear wheel output bevel gear 35d and the differential gear case 70 are rotationally driven through the barrel member 35c. As a result, the left and right front wheel drive shafts 63 are rotationally driven in accordance with the rotation of the differential gear case 70, and the rear wheel input bevel gear 64a meshes with the rotation of the rear wheel output bevel gear 35d. ) and the rear wheel output shaft 64 (equivalent to a driving electric shaft) are driven to rotate.

A claw portion 71a for differential gear locking is provided at the right end of the boss portion of the front wheel output gear 35b. In addition, at the left end of the sliding cylinder 71 externally fitted to the front wheel drive shaft 63, a sliding claw for differential gear locking (71b) is formed, which is detachable from the hook for differential gear locking (71a). there is. This differential gear lock sliding claw portion 71b is engaged and disengaged by rotating the differential gear lock operating pin 72 installed through the case body 30. That is, by rotating the differential gear lock operation pin 72, the sliding barrel 71 moves along the axis direction of the front wheel drive shaft 63, and the differential gear lock claw portion 71a of the front wheel output gear 35b ) for the bond separation operation.

In the differential gear lock state in which the differential gear lock sliding claw portion 71b is engaged with the differential gear lock claw portion 71a, the differential by the differential gear device 7 is locked.

[Work device drive system]

Separately from the above-mentioned traveling drive system, a working device driving system that transmits power to the seedling transplanting device 2 of the planting system working device will be described.

Power to the seedling transplant device 2 is provided through the main transmission mechanism 4A and the transplant clutch 8 (equivalent to a work clutch) in the main case part 4 installed in the rear part of the main case part 3. , is taken out from the output transmission shaft body 42 extending rearwardly from the main case part 4, and is transmitted to the rear seedling transplantation device 2.

As shown in FIGS. 4 and 6, the main case portion 4 is provided with a main case body 40 that is constructed separately from the case body 30 of the main case portion 3. This main case body 40 is integrally connected and fixed to the main case portion 3 through connecting bolts or the like (not shown). Then, the main case part 4 and the main case part 3 are connected in a sealed state in which the openings 40a and 30a formed at the connection points are joined to each other, and the respective internal spaces are in communication with each other. It is done.

Power is transmitted from the main case portion 3 to the main case portion 4 through a work-type transmission shaft 37 installed across the left and right side walls 30b and 30b of the case main body 30, and a work-type transmission shaft. This is done through the bevel gear 37a fixed to (37) and the output bevel gear 38 meshed with the bevel gear 37a.

As the work system transmission shaft 37, a second external gear 36b installed on the axial portion of the work system transmission shaft 37 protrudes outward from the case body 30, and the case main body of the extension shaft 33. It is engaged with the first external gear 36a installed on the shaft portion protruding outward of 30, and power is transmitted thereby.

In the main case part 4, as shown in FIG. 4, a work drive shaft 41 (corresponding to a shift operation shaft) that is long in the front-back direction is arranged across the front and back of the main case part 4.

The work drive shaft 41 is externally fitted to enable relative rotation between the output transmission shaft body 42 to which the transmission shaft 27 is connected to the rear seedling transplant device 2 and the front end portion of the output transmission shaft body 42. It is configured as a double shaft structure with a front normal shaft body 43 (corresponding to a normal shaft body) through which power in the upper direction of the transmission direction is transmitted.

The front normal shaft body 43 on the upper side of the transmission is positioned with its front end protruding into the case body 30 of the main case portion 3. A spline portion is formed on the portion of the front normal shaft 43 located at the uppermost rolling direction, and the spline portion is a spline portion on the inner circumference of the barrel boss of the output bevel gear 38 located within the main case portion 3. It is inserted in .

The output bevel gear 38 is supported on the outer peripheral side of the boss portion by a ball bearing 38a provided on the case body 30 side of the main case portion 3, and is thereby inserted into the inner peripheral side of the front normal shaft body. (43) is also supported.

In addition, in the ball bearing 38a provided on the case main body 30 side, a slightly larger diameter portion rearward than the portion inserted into the output bevel gear 38 among the front normal shaft body 43 is internally inserted. and is supported. In addition, the larger diameter portion of the front normal shaft 43 abuts on the rear end side of the inner race of the ball bearing 38a, thereby regulating the position toward the front side.

The front normal shaft body 43 is formed with a small diameter hole 43b communicating with the internal space of the main case portion 3 on the front side of the large diameter hole 43a into which the output transmission shaft body 42 is inserted. There is a small diameter hole 43b and a large diameter hole 43a of this front normal shaft body 43 on the inner circumferential side communicating with the inner space of the main case portion 3 and the inner space of the main case portion 4. It is a passageway.

On the outer periphery of the output transmission shaft 42 rearward from the location where the front normal shaft 43 exists, an intermediate cylindrical body 44 (corresponding to the normal shaft) and a rear cylindrical body 45 (normal shaft (equivalent to) is externally fitted so that relative rotation is possible.

A torque limiter 46 is installed between the rear end of the middle cylindrical body 44 and the front end of the rear cylindrical body 45.

An implant clutch 8 is provided between the rear end of the rear cylindrical body 45 and the output transmission shaft body 42 on the rear side of the rear cylindrical body 45.

In this way, the middle cylindrical body 44 and the rear cylindrical body 45 exist on the outer periphery of the output transmission shaft body 42 in a state in which they are externally fitted so as to be relatively rotatable, and this output transmission shaft body 42 is connected to the front cylindrical body 42. Since it exists in the passage on the inner circumference side of the shaft body 43, it is easy to perform satisfactory lubrication within the main case portion 4.

That is, the lubricating oil existing in the inner space of the main case portion 3 flows through the inner peripheral side of the barrel boss of the output bevel gear 38, and as shown by the broken arrow in FIG. 4, the front normal shaft body ( 43) and the middle cylindrical body 44, between the middle cylindrical body 44 and the rear cylindrical body 45, and between the rear cylindrical body 45 and the rear output transmission shaft body 42, Good lubrication can be achieved while utilizing the centrifugal force accompanying the rotation of the member rotating on the drive shaft 41.

The front normal shaft body 43 has a spline portion 43c formed on its outer periphery, and a shift gear 47 externally fitted into the spline portion 43c is equipped to rotate and slide integrally.

The shift gear 47 is provided with a first tooth 47a and a second tooth 47b of similar diameters with slightly different numbers of teeth, and either of the teeth 47a, 47b is alternatively a driven gear 47c. ) is configured so that the position can be changed along the axis direction of the front normal shaft body 43 so that it can be engaged with.

As shown in FIG. 4, the movement range of this shift gear 47 is in a state where both the first teeth 47a and the second teeth 47b are located within the main case portion 4, and the first teeth Operation by the daytime shift operation member 100 so that the front part or part of the portion (47a) can be switched to a state where it protrudes from the daytime case part 4 and is located in the internal space of the main case part 3. Setting the range.

Inside the main case portion 4, a shift shaft 48 positioned parallel to the work drive shaft 41 is provided. The driven gear 47c is installed on this shift shaft 48 so that it can rotate integrally.

On the shift shaft 48, a plurality (three in the figure) of shift gears 44a fixed to the intermediate cylindrical body 44 on the output transmission shaft body 42 side are installed in a constant meshing state (3 in the figure). The shift gear 48a (false) is installed in a loosely fitted state. And, these shift gears 44a and 48a, which are in a state of constant engagement, a shift rod 48b that is slidably operated within the shift shaft 48, and a positioning mechanism 48c using a detent mechanism are constantly engaged. A combination of the current shift gears 44a and 48a can be selectively selected.

A second shift that allows selective selection of a combination of the first shift unit (4B) using the shift gear 47 and the driven gear 47c, and the shift gears 44a and 48a that are always engaged. The part 4C constitutes the daytime shifting mechanism 4A.

The day shift operation member 100 in the day shift mechanism 4A is configured as shown in FIGS. 4 and 6.

That is, a locking pin 102 inserted between the first teeth 47a and the second teeth 47b is fixed to the lower end of the operating shaft 101 penetrating the upper wall portion of the main case portion 4. and a plate-shaped operating body 103 is installed at the upper end of the operating shaft 101 located outside the upper wall portion.

By rotating this plate-shaped operating body 103 around the axis of the operation shaft 101, the locking pin 102 present at an eccentric position changes the position of the shift gear 47 in the axis direction of the work drive shaft 41. It is configured to do so. The position of the plate-shaped operating body 103 around the axis is determined by the ball detent mechanism 104.

The torque limiter 46 includes a support plate 46a fixed to the rear end of the intermediate cylindrical body 44, a press plate 46b abutting toward the support plate 46a, and a press plate 46b facing the support plate 46a. It is comprised of a coil spring 46c that pressurizes.

The transplant clutch 8 is configured as follows.

Among the work drive shafts 41, at the rear end of the rear cylindrical body 45, there is a disk-shaped drive side rotation member 80 that engages with the outer circumferential spline of the rear cylindrical body 45 and rotates integrally with the rear cylindrical body 45. ) is installed.

The outer peripheral side of the output transmission shaft body 42 extending rearward than the rear cylindrical body 45 is engaged with the spline portion 42a formed on the outer peripheral surface of the output transmission shaft body 42, so that the output transmission shaft body 42 ) and a driven side rotation member 81 that can rotate integrally and move in position in the axis direction of the output transmission shaft body 42 is provided.

This driven-side rotating member 81 is pressed toward the driving-side rotating member 80 by a compression spring 82, and each of the driving-side rotating member 80 and the driven-side rotating member 81 On the opposing surfaces, engaging portions 80a and 81a, which enable power transmission in a mutually engaged state, are formed.

The compression spring 82 includes a spring receiving portion 81b formed on a surface opposite to the side on which the engaging portion 81a of the driven side rotation member 81 is formed, and a spring receiving portion 81b formed on the inner side of the main case portion 4. It is installed between the fixed parts. As a fixing part on the inner side of the main case part 4, the inner end of the inner race 49a of the ball bearing 49 supporting the output transmission shaft body 42 is used, but it must be in this position. There is no

And, the shape of the compression spring 82 is such that the winding diameter at the end on the side abutting the spring receiving portion 81b in the axial direction of the work drive shaft 41 is on the side abutting against the inner end of the inner race 49a. It is formed in a cone shape that is set larger than the winding diameter.

Among these compression springs 82, the winding diameter of the side that abuts the inner end of the inner race 49a is approximately the same as or slightly larger than the outer diameter of the externally fitted output transmission shaft body 42. Therefore, the end position can be determined using the inner end of the inner race 49a of the ball bearing 49 supporting the output transmission shaft body 42 without requiring any special positioning means.

As shown in FIG. 4, the driven-side rotating member 81 is spaced apart from the driving-side rotating member 80 by resisting the pressing force of the pressing spring 82 by the clutch operating member 83 abutting the outer peripheral part. It is operated sideways, and is provided with an engaging portion 81c on the outer periphery where the clutch operating member 83 engages.

The clutch operating member 83 is provided with an operating pin 84 that penetrates the upper wall portion of the main case portion 4, and the driven side rotation member 81 is engaged with the lower end of the operating pin 84. In contact with the portion 81c, an operation portion 84a is formed that moves the driven side rotation member 81 in the axis direction of the output transmission shaft body 42 in accordance with the rotation operation of the operation pin 84.

The clutch operation member 83 operates the portion exposed to the outside of the main case portion 4 among the operation pins 84 operated around the rotation axis p1 in the direction intersecting the axis of the work drive shaft 41. An operating plate 85 for rotating the operating pin 84 is provided at the axial end of the pin 84. And, an operation guide member 86 that supports a part of the operation plate 85 so as to fit it from above and below and guides the rotation operation of the operation plate 85 around the rotation axis p1 is provided in the main case. It is installed on the outside of part 4.

As a result, the positional movement of the operation pin 84 in the direction along the rotation axis p1 is regulated by the operation plate 85, and the operation range around the rotation axis p1 is controlled by the operation plate 85 and the operation plate 84. It is regulated by the abutment of the operation guide member 86.

The position of the spring receiving portion 81b of the driven rotating member 81 is relative to the engaging portion of the engaging portion 81c of the driven rotating member 81 at the lower end of the operating pin 84. , on the inward side in the radial direction of the driven-side rotary member 81, and in the axial direction of the work drive shaft 41, the engaging portion is larger than the engaging portion of the engaging portion 81c of the driven-side rotating member 81. It is installed at a location near the opposing surface where (81a) is formed.

In this way, the spring receiving portion 81b is on the inner side in the radial direction than the engaging portion between the operating pin 84 and the engaging portion 81c of the driven side rotation member 81, and the engaging portion 81a It has a greatly concave shape close to the side where it exists. As a result, the axial length of the work drive shaft 41 of the compression spring 82 is prevented from being restricted by the position of the operation pin 84 in the axial direction of the work drive shaft 41, and the main case portion ( 4) can achieve compactness.

[fertilization drive system]

From the above-described traveling drive system, the fertilizing device drive system that branches and transmits the driving force to the fertilizing device 9 is configured as follows.

As shown in FIG. 6, on the rear side of the main case part 3, a branch case part 5, which is separate from the main case part 3, is connected and fixed through a mounting bolt or the like (not shown). there is.

The main case portion 3 and the branch case portion 5 are in a sealed state in which the openings 30a and 50a formed at the connection points are joined to each other, and their respective internal spaces are in communication with each other.

As shown in FIG. 5, the branch case portion 5 includes an input side normal portion 50A that supports the rear wheel output shaft 64 extending rearward from the main case portion 3 and an input side normal portion 50A that intersects the rear wheel output shaft 64. It is provided with an output-side normal portion 50B that is externally fitted to a branch transmission shaft 51 extending in the direction and supports the branch transmission shaft 51. The input side normal portion 50A and the output side normal portion 50B are formed as an integrated body with a common internal space.

The branch output bevel gear 52, which transmits power from the rear wheel output shaft 64 to the branch transmission shaft 51, is installed in the input side normal portion 50A, and the fertilization bevel gear meshed with the branch output bevel gear 52 ( 53) (corresponding to a bevel gear for branch input) is installed in the output side normal portion 50B.

The branch output bevel gear 52 is installed in the input side normal part 50A on the side closer to the main case part 3 than the branch transmission shaft 51.

The rear wheel output shaft 64, which has a rear wheel input bevel gear 64a engaged with the rear wheel output bevel gear 35d at the front end, has a ball installed on the front end to the case body 30 of the main case portion 3. It is supported by a bearing 39, and the rear end is supported by a ball bearing 54 installed near the rear end of the branch case portion 5.

This rear wheel output shaft 64 has a step portion 64C (corresponding to a positioning portion) provided at a midway position in the axis direction, and the front portion corresponding to the upper side in the transmission direction is larger than the step portion 64C. It is the diameter shaft portion 64A, and the rear side corresponding to the lower side in the rolling direction than the step portion 64C is formed as a small diameter shaft portion 64B.

The step portion 64C is formed near the boundary between the main case portion 3 and the branch case portion 5, and a spline portion 64D is formed at a portion of the small diameter shaft portion 64B close to the step portion 64C. It is formed, and the bevel gear 52 for branch output is spline-fitted to this spline portion 64D.

The opening portion 50a of the branch case portion 5 formed at a location opposite to the main case portion 3 has an inner diameter through which the bevel gear for branch output 52 supported on the rear wheel output shaft 64 can be inserted.

Therefore, when embedding the rear wheel output shaft 64 in the branch case part 5, it can be built in the branch case part 5 with the bevel gear 52 for branch output supported in advance on the rear wheel output shaft 64. , convenience can be achieved during assembly and disassembly.

The branch transmission shaft 51, which is equipped at the input side end with a fertilizing bevel gear 53 that engages the branch output bevel gear 52 supported on the rear wheel output shaft 64, is in an attitude perpendicular to the rear wheel output shaft 64. It is placed. And, the input side end is configured to be insertable and extractable from the output side opening 50b formed in the output side normal portion 50B of the branch case portion 5, and the output side end is pulled outward from the output side opening 50b of the output side normal portion 50B. It is supported in a protruding state.

A linkage shaft (not shown) to the fertilizing device 9 is connected to the protruding portion of the branch transmission shaft 51 that protrudes outward from the output side opening 50b.

Additionally, the branch transmission shaft 51 is at a location corresponding to the insertion limit position into the output side normal portion 50B, and the input side end abuts the rear wheel output shaft 64. That is, when the branch transmission shaft 51 is inserted from the output side opening 50b into the output side normal portion 50B until it reaches the insertion limit position, the input side end is in a positional relationship in contact with the rear wheel output shaft 64, so that the input side normal portion ( 50A), the position of the rear wheel output shaft 64 is determined.

The bevel gear 53 for fertilization is supported so as to rotate relative to the branch transmission shaft 51, and the branch transmission shaft 51 and the bevel gear 53 for fertilization are connected to a fertilization clutch 55 (equivalent to a work clutch). It is configured so that it can be combined and separated.

The fertilizing clutch 55 is provided with a normal shift member 56 spline-fitted to a spline portion formed on the outer peripheral surface of the branch transmission shaft 51. And, the claw portion 56a formed on the opposing surface of the normal shift member 56 to the bevel gear 53 for fertilization is caught on the side of the bevel gear 53 for fertilization opposed to the normal shift member 56. It is configured to be able to switch between a state in which the rotation of the bevel gear 53 for fertilization is transmitted by the branch transmission shaft 51 and a state in which transmission is interrupted by engaging and disengaging the engaging recessed portion 53a.

Normally, the shift member 56 is pressed toward the bevel gear 53 for fertilization by a coil spring 57, and resists this pressing force to move the normal shift member 56 away from the bevel gear 53 for fertilization. A clutch operating shaft body 58 that operates toward the side is installed penetrating the output side normal portion 50B.

[Axle Case]

As shown in FIG. 10, a transmission shaft 65 along the vertical direction is installed in the axle case 16 through which the driving force is transmitted from the front wheel drive shaft 63, and is located on the upper side of this transmission shaft 65. An upper bevel gear pair 66 on the upper side of the transmission and a lower bevel gear pair 67 on the lower side of the transmission located on the lower side of the transmission shaft 65 are provided.

Each of these bevel gear pairs 66 and 67 is subjected to reduction gear transmission. And, the reduction ratio in the lower bevel gear pair 67 on the lower side of the transmission is set to be larger than that in the upper bevel gear pair 66 on the upper side of the transmission.

Although not shown, in the axle case 19 that transmits the driving force to the rear wheels 11R, a transmission shaft 65 is installed diagonally downward from the upper side. Also, on the upper and lower sides of the transmission shaft 65, the structure is similar to that of the upper bevel gear pair 66 and the lower bevel gear pair 67 on the front wheel 11F side, and the reduction ratio on the lower transmission side is changed. A large configuration is adopted.

[Other Embodiment 1]

In the above embodiment, the main case part 4 is shown as the work case part, but it is not limited to this. For example, when the work machine is used in a seed drill equipped with a direct seeding device, the work case portion becomes a work case portion for changing the seeding spacing by the direct seeding device.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 2]

In the above embodiment, the fertilizing device 9 is used as the powder supply device, but it is not limited to this.

For example, it may be to supply chemicals such as herbicides or insect repellent.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 3]

In the above embodiment, the technology applied to the transplant clutch 8 as a work clutch is shown, but it is not limited to this. For example, although not shown, the fertilizing clutch 55 may be configured to have the same structure as the transplant clutch 8 as the work clutch described above.

For other configurations, the same configuration as the above-described embodiment may be adopted.

[Other Embodiment 4]

In the above embodiment, a structure consisting of three examples of the cylindrical shaft body, the front cylindrical body 43, the middle cylindrical body 44, and the rear cylindrical body 45 is illustrated, but the structure is not limited to this structure.

For example, as a normal shaft body, it may be a structure using only the front normal shaft body 43 or a structure using a combination of more normal shaft bodies.

For other configurations, the same configuration as the above-described embodiment may be adopted.

[Other Embodiment 5]

In the above embodiment, the rice transplanter provided with the main case part 4 as the planting case part is shown, but it is not limited to this. For example, when used in a seed drill equipped with a direct seeding device, the planting work case portion becomes a work case portion for changing the planting spacing by the direct seeding device.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 6]

In the above embodiment, the fertilizing device 9 is used as the powder supply device, but it is not limited to this.

For example, it may be to supply chemicals such as herbicides or insect repellent.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 7]

In the above embodiment, a structure is illustrated in which both the cooling operation case portion and the branch case portion are provided and each can be detached from the openings 40a and 50a. However, only the cooling operation case portion can be detached from the opening 40a. It may be something that allows you to do so.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 8]

In the above embodiment, the meshing recesses 32c and 32d of the lower high-speed gear 32b in the high-speed gear pair suitable for road driving in the auxiliary transmission mechanism 3A are aligned with the shaft support hole 32e. Although it is exemplified that it is formed in a continuous shape, it does not necessarily have to be this shape.

For example, the shaft support hole 32e is a perfectly round hole, and the engaging recesses 32c and 32d are close to the shaft support hole 32e, but have an independent concave shape different from the shaft support hole 32e. It may be formed of .

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 9]

Hereinafter, other embodiments of the present invention will be described based on the description of the drawings.

〔Overall composition〕

In Figure 11, the left side of a riding-type rice transplanter as an example of a water-transplanting machine equipped with a working device (seeding system working device) such as a seedling transplant device for transplanting seedlings to the ground or a direct sowing device for sowing rice seeds to the ground is shown. It is done.

This riding-type rice transplanter is provided with a pair of left and right front wheels 1011F that can be steered and driven as a traveling drive device, and a pair of left and right rear wheels 1011R that can be driven as a travel drive device below the body frame 1010. It is provided with a self-propelled traveling body 1001 in which front wheels 1011F and rear wheels 1011R are driven by receiving power from an engine E100 mounted on 1010.

In the traveling body 1001, a prime mover 1013 containing an engine E100 is provided in the front part of the body on the operating section floor 1014. Ride-on operation with a steering handle 1015 and a driver's seat 1012 for steering the front wheels 1011F on the driver's floor 1014 in the center of the traveling body 1001 in the anteroposterior direction from the rear side of the propulsion unit 1013. Supplies are provided.

A fertilizing device 1009 (equivalent to a granular material supply device) is mounted on the rear portion of the driver's seat 1012. The fertilization device 1009 supplies fertilizer stored in the fertilizer tank 1090 in predetermined amounts from a delivery device not shown, and is equipped with a planting device 1091 in the seedling transplant device 1002 through a supply path not shown. It is configured to be sent to and supplied in packaging. On the rear side of the traveling body 1001, a seedling transplant device 1002 is supported so as to be able to be raised and lowered through a link mechanism 1025 having a hydraulic cylinder 1026 for lifting and lowering operation.

The riding-type rice transplanter configured in this way performs the operation of transplanting seedlings such as rice to the field using the seedling transplanting device 1002.

In the front part of the traveling body 1001, a spare seedling loading stand 1017 is arranged on both left and right sides of the motor unit 1013 at a distance in the left and right directions that can be moved back and forth. At the rear of the traveling body 1001, a seedling transplantation device 1002 is supported so as to be able to be raised and lowered through a link mechanism 1025 having a hydraulic cylinder 1026 for lifting and lowering operation.

The riding-type rice transplanter configured in this way performs the operation of transplanting seedlings such as rice to the field using the seedling transplanting device 1002.

The seedling transplant device 1002 is composed of a four-piece type, including an electric case 1021, a transplant case 1022 rotatably supported on the right and left lateral sides of the rear part of the electric case 1021, and a transplant case 1022. It is equipped with a pair of transplanting arms 1023 (transplanting hook drive mechanism) provided at both ends of the case 1022, a grounding float 1024, and a seedling loading stand 1020 on which seedlings are loaded. As the seedling loading stand 1020 is driven to reciprocate left and right, the transplanting case 1022 is rotated, and the transplanting arms 1023 alternately take out seedlings from the lower part of the seedling loading stand 1020 and plant them. It is designed to be transplanted to the floor.

In the traveling body 1001, a transmission case M100 supporting the front wheel 1011F is connected and fixed to the front part of the body frame 1010, and at the rear part of the body frame 1010, the rear wheel The axle case 1019 equipped with (1011R) on the left and right is supported. A front frame 1010F extends forward from the transmission case M100, and an engine E100 is mounted laterally on this front frame 1010F.

As shown in Figs. 12 and 13, on both left and right sides of the transmission case M100, an axle case 1016 extends outward on both left and right sides, and left and right front wheels 1011F and 1011F are installed.

The axle case 1019 of the rear wheel 1011R is elastically supported on the lower side of the left and right pairs of front and rear frames 1010A and 1010A so that the left and right can move up and down separately through suspension springs 1018, allowing left and right rolling operation. It is installed.

[Power transmission system]

The power transmission structure in the mission case (M100) through which the power of the engine (E100) is transmitted will be described.

*The power of the engine (E100) input to the mission case (M100) is used as a driving drive system to drive the front wheels (1011F) and rear wheels (1011R), etc. within the mission case (M100), and for seedling transplantation as a seeding system work device. The output is branched to a work device drive system for driving the device 1002 or a seeding device (not shown) and a fertilization drive system for driving the fertilization device 1009.

The transmission case (M100) includes a main case part (1003) containing the sub-shift mechanism (1003A) of the traveling drive system, etc., and a main case part (1004) disposed on the rear side of the main case part (1003) (see Equivalent to the case part) and a branch case part 1005.

The main case portion 1004 has a built-in main shift mechanism 1007 (corresponding to a plant-type shift mechanism) that changes and transmits the power output from the main case portion 1003 to the seedling transplant device 1002, and the branch case portion The unit 1005 has a built-in branching mechanism 1005A that branches off the power output from the main case unit 1003 to the fertilizing device 1009.

The power of the engine E100 is transmitted to the pump shaft 1060a of the hydrostatic continuously variable transmission device 1006 mounted on the outer wall of the main case portion 1003 in the transmission case M100, and the hydrostatic continuously variable transmission It is input from the motor shaft 1061a of the device 1006 into the inside of the case body 1030 in the main case portion 1003. That is, the hydrostatic continuously variable transmission device 1006 is used as a continuously variable main transmission device, and the power output from the main transmission device is further shifted within the transmission case M100.

[Driving drive system]

First, the transmission structure of the traveling drive system will be explained.

As shown in FIG. 12, the power of the engine E100 is transmitted to the pump shaft 1060a, which is the shift input shaft of the hydrostatic continuously variable transmission 1006, through the belt transmission mechanism 1062 and is supplied to the hydraulic pump 1060. is driven to rotate.

The motor shaft 1061a, which is the shift output shaft of the hydrostatic continuously variable transmission 1006, is connected to the first shift shaft 1031 (corresponding to the upper shift shaft) within the case body 1030 of the main case portion 1003. , are connected in a spline-fitting state, and the first shift shaft 1031 is rotationally driven as the motor 1061 rotates.

As shown in FIG. 13, the first shift shaft 1031 is equipped so that the upper low-speed gear 1031a of the traveling drive system and the upper high-speed gear 1031b of the travel drive system rotate together, and also the output for the reduction transmission of the work device drive system The gears 1031c are installed to rotate integrally.

The end of the first shifting shaft 1031 opposite to the side connected to the motor shaft 1061a is a shaft portion 1033a that penetrates the side wall 1030b of the case body 1030 and protrudes outward from the case body 1030. ) is inserted into the tubular boss portion 1033b of the extension shaft 1033, and is pivotally supported so as to be relatively rotatable. The extension shaft 1033 is provided with an implanted electric gear 1033c on the outer periphery of the barrel boss portion 1033b, and has a first shaft portion 1033a that penetrates the side wall 1030b and protrudes to the outside of the case body 1030. The external gear 1036a is supported so as to be fully rotatable.

The output gear 1031c for reduction transmission and the transfer gear 1033c are meshed with a relay gear 1032f that is loosely and rotatably fitted to a second shift shaft 1032, which will be described later.

A second shift shaft 1032 (corresponding to the lower shift shaft), which has an axis parallel to the first shift shaft 1031, is axially supported by the case body 1030. This second shift shaft 1032 includes a lower low-speed gear 1032a (corresponding to the lower gear) meshing with the upper low-speed gear 1031a, and a lower high-speed gear 1032b meshing with the upper high-speed gear 1031b ( (corresponding to the lower gear) is axially supported on the second shift shaft 1032 so as to be capable of relative rotation.

The gear pair of the upper low-speed gear 1031a and the lower low-speed gear 1032a, the gear pair of the upper high-speed gear 1031b and the lower high-speed gear 1032b, and the second shift shaft 1032 between these gear pairs. The auxiliary transmission mechanism 1003A is configured by providing a shift member 1034 axially supported.

Among the gear pairs, the combination of the upper low-speed gear 1031a and the lower low-speed gear 1032a is a low-speed gear pair suitable for work driving, and the combination of the upper high-speed gear 1031b and the lower high-speed gear 1032b is suitable for road driving. This is a gear pair suitable for high speed use.

The shift member 1034 is spline-fitted to the second shift shaft 1032, is supported so as to be rotatable integrally with the second shift shaft 1032, and can slide in the axis direction of the second shift shaft 1032. . On the left and right sides of the shift member 1034 opposing each pair of gears on both left and right sides, there is a lower low speed gear 1032a and a lower high speed gear 1032b located on the lower side in the power transmission direction of each gear pair. It is provided with engaging teeth 1034a and 1034b that protrude in both directions.

And, each of the lower low-speed gear 1032a and the lower high-speed gear 1032b at a position opposite to the shift member 1034 has a gear alternatively engaged with the engaging teeth 1034a and 1034b of the shift member 1034. Engagement concave portions 1032c and 1032d are formed.

Among the engaging teeth 1034a and 1034b of the shift member 1034, the engaging tooth 1034a on the side opposite to the lower low-speed gear 1032a with a large diameter is located near the outer peripheral edge of the shift member 1034, and is located on the second shift shaft. It is formed at a location spaced apart from the outer peripheral surface of (1032). The engaging teeth 1034b on the side opposite to the lower high-speed gear 1032b with a small diameter on the opposite side are formed near the inner peripheral edge of the shift member 1034 and close to the outer peripheral surface of the second shifting shaft 1032. .

Among the engaging recessed portions 1032c and 1032d, the engaging recessed portion 1032c formed in the lower low-speed gear 1032a has a shape capable of engaging with the engaging tooth portion 1034a on the shift member 1034 side located opposite to the engaging recessed portion 1032c. It is formed at a location spaced apart from the outer peripheral surface of the second shift shaft 1032. In addition, the engagement concave portion 1032d formed in the lower high-speed gear 1032b has a shape that allows engagement with the engagement tooth portion 1034b on the shift member 1034 side located opposite to the engagement concave portion 1032d, and the second shift shaft 1032 It is formed in a location close to the outer circumference of the .

As shown in FIG. 14, the engagement concave portion 1032d formed in the lower high-speed gear 1032b includes the shaft support hole 1032e of the lower high-speed gear 1032b externally fitted to the second shift shaft 1032. It is formed in a connected shape. As a result, the engagement concave portion 1032d formed in the lower high-speed gear 1032b is formed as close to the outer peripheral surface of the second shift shaft 1032 as possible.

The shift member 1034 uses an operation panel 1034c that supports the shift member 1034 while holding it, and an operation rod 1034d integrally fixed with the operation panel 1034c, and forms a case body 1030. ) is configured to be operable from the outside.

The position at which the operating rod 1034d is pressed into the case body 1030 is the position where the shift member 1034 selects a low-speed gear pair suitable for work travel, and the operating rod 1034d is most pressed into the case body 1030. The position pulled out to the outside of is the position where the shift member 1034 selects the high-speed gear pair suitable for road driving. The neutral position is when the shift member 1034 is in an intermediate position where neither gear pair is selected.

The power transmitted to the second shift shaft 1032 through the shift member 1034 is transmitted to the front wheel output gear 1035b through the interlocking gear 1035a fixed to the second shift shaft 1032. The front wheel output gear 1035b is spline-fitted to the outer peripheral portion of the right end side of the cylinder member 1035c externally fitted so as to be rotatable relative to the front wheel drive shaft 1063. The left end side of the cylinder member 1035c is rotatably connected to the differential gear case 1066 through the boss portion of the rear wheel output bevel gear 1035d spline-fitted to the outer peripheral portion.

Accordingly, when the front wheel output gear 1035b is driven, the rear wheel output bevel gear 1035d and the differential gear case 1066 are rotationally driven through the barrel member 1035c. As a result, the left and right front wheel drive shafts 1063 are rotationally driven with the rotation of the differential gear case 1066, and with the rotation of the rear wheel output bevel gear 1035d, the rear wheel input bevel gear 1064a engages with this. ) and the rear wheel output shaft 1064 (equivalent to a driving electric shaft) are driven to rotate.

A claw portion 1067a for differential gear locking is provided at the right end of the boss portion of the front wheel output gear 1035b. Also, at the left end of the sliding cylinder 1067 externally fitted to the front wheel drive shaft 1063, a sliding hook 1067b for differential gear locking that can be coupled and detached from the differential gear lock hook 1067a is formed. there is. This differential gear lock sliding claw portion 1067b is engaged and disengaged by rotating the differential gear lock operating pin 1068 installed through the case body 1030. That is, by rotating the differential gear lock operation pin 1068, the sliding barrel 1067 moves along the axis direction of the front wheel drive shaft 1063, and the differential gear lock claw portion 1067a of the front wheel output gear 1035b ) for the bond separation operation.

In the differential gear lock state in which the differential gear lock sliding claw portion 1067b is engaged with the differential gear lock claw portion 1067a, the differential by the differential gear device 1065 is locked.

[Working device drive system]

Separately from the above-described traveling drive system, a working device driving system that transmits power to the seedling transplanting device 1002 of the planting system working device will be described.

Power to the seedling transplanting device 1002 is provided through the main shifting mechanism 1007 and the transplanting clutch 1008 (corresponding to a working clutch) in the main case part 1004 installed in the rear part of the main case part 1003. , is taken out from the output transmission shaft body 1042 extending rearwardly from the main case portion 1004, and is delivered to the rear seedling transplantation device 1002.

As shown in FIGS. 15 and 16, the main case portion 1004 is provided with a main case body 1040 that is constructed separately from the case body 1030 of the main case portion 1003. This main case body 1040 is integrally connected and fixed to the main case portion 1003 through connection bolts or the like (not shown). Then, the main case part 1004 and the main case part 1003 are connected in a sealed state where the openings 1040a and 1030a formed at the connection points are joined to each other, and their respective internal spaces are in communication with each other. It is done.

Power is transmitted from the main case portion 1003 to the main case portion 1004 through a work-type transmission shaft 1037 installed across the left and right side walls 1030b and 1030b of the case body 1030, and a work-type transmission shaft. This is done through a bevel gear 1037a fixed to 1037 and an output bevel gear 1038 meshed with the bevel gear 1037a.

As the work system transmission shaft 1037, a second external gear 1036b installed on the axial portion of the work system transmission shaft 1037 protrudes outward from the case body 1030, and the case main body of the extension shaft 1033. It is engaged with the first external gear 1036a installed on the shaft portion protruding outward from 1030, and power is transmitted thereby.

In the main case part 1004, as shown in FIG. 16, a work drive shaft 1041 (corresponding to a shift operation shaft) that is long in the front-back direction is arranged across the front and back of the main case part 1004.

The work drive shaft 1041 is externally fitted to enable relative rotation between the output transmission shaft body 1042 to which the transmission shaft 1027 is connected to the rear seedling transplantation device 1002 and the front end portion of the output transmission shaft body 1042. It is composed of a partial double-axis structure by a normal shaft body 1043 through which power in the upper direction of the transmission direction is transmitted.

The front end of the normal shaft body 1043 located on the upper side of the transmission is disposed in a state that penetrates into the inside of the case body 1030 of the main case portion 1003. A spline portion is formed on the portion located most above the rolling direction of this normal shaft body 1043, and the spline portion is inserted into the spline portion on the inner peripheral side of the barrel boss of the output bevel gear 1038 located within the main case portion 1003. It is done.

The output bevel gear 1038 is supported on the outer peripheral side of the boss portion by a ball bearing 1038a provided on the case body 1030 side of the main case portion 1003, and the normal shaft body 1043 is thereby inserted into the inner peripheral side. is also supported.

In addition, in the ball bearing 1038a provided on the case main body 1030 side, a slightly larger diameter portion of the shaft body 1043 rearward than the portion inserted into the output bevel gear 1038 is fitted and supported. there is. Additionally, the larger diameter part of the shaft body 1043 is usually in contact with the rear end side of the inner race of the ball bearing 1038a. As a result, the position of the shaft body 1043 toward the front side is normally regulated.

Normally, the shaft body 1043 is formed with a small diameter hole 1043b communicating with the internal space of the main case portion 1003 on the front side of the large diameter hole 1043a into which the output transmission shaft body 1042 is inserted. The small-diameter hole 1043b and the large-diameter hole 1043a of this normal shaft body 1043 form an inner circumferential passage that communicates the inner space of the main case portion 1003 and the inner space of the main case portion 1004. .

A middle cylindrical body 1044 and a rear cylindrical body 1045 are externally fitted so as to be relatively rotatable on the outer periphery of the output transmission shaft 1042 rearward of the location where the cylindrical shaft 1043 exists.

A torque limiter 1046 is installed between the rear end of the middle cylindrical body 1044 and the front end of the rear cylindrical body 1045.

An implant clutch 1008 is provided between the rear end of the rear cylindrical body 1045 and the output transmission shaft body 1042 on the rear side of the rear cylindrical body 1045.

In this way, on the outer periphery of the output transmission shaft body 1042, the middle cylindrical body 1044 and the rear cylindrical body 1045 exist in an externally fitted state so as to be relatively rotatable, and this output transmission shaft body 1042 is a normal shaft body ( Since it exists in the inner circumferential passage of 1043), it is easy to achieve satisfactory lubrication within the main case portion 1004.

That is, the lubricating oil existing in the inner space of the main case portion 1003 flows in through the inner peripheral side of the barrel boss of the output bevel gear 1038, and as shown by the broken arrow in FIG. 16, the normal shaft body 1043 and Rotating on the work drive shaft 1041 between the middle cylindrical body 1044, between the middle cylindrical body 1044 and the rear cylindrical body 1045, and between the rear cylindrical body 1045 and the output transmission shaft body 1042 on the rear side. Good lubrication can be achieved while utilizing the centrifugal force accompanying the rotation of the member.

[Weekly shifting mechanism]

The day shift mechanism 1007 will be described.

The day shift mechanism 1007 includes a first shift portion 1007A located above the transmission, and a second shift portion 1007B located below the transmission. The first shift unit 1007A performs two high and low gear shifts, and the second shift unit 1007B performs three high and mid low gear shifts, so that a total of six gear shifts are performed. .

In the first transmission unit 1007A, a shift gear 1047 installed on the normal shaft body 1043 of the work drive shaft 1041 is fixed to the front end of the shift shaft 1048 located parallel to the work drive shaft 1041. A supported driven gear 1048a is provided.

Normally, the shaft body 1043 has a spline portion 1043c formed on its outer periphery, and a shift gear 1047 externally fitted into the spline portion 1043c is equipped to rotate and slide integrally. The shift gear 1047 is provided with a first tooth 1047a and a second tooth 1047b of similar diameters with slightly different numbers of teeth, and either of the teeth 1047a, 1047b is alternatively connected to the driven gear 1048a. To enable engagement, the position is generally configured to be changeable along the axis direction of the shaft body 1043.

As shown in FIG. 16, the movement range of the shift gear 1047 includes a second shifting position where both the first teeth 1047a and the second teeth 1047b are located within the main case portion 1004, and All or part of the 1 tooth portion 1047a is a first shift position protruding from the main case portion 1004 and located in the inner space of the main case portion 1003, and is configured to enable the shift operation position to be switched. . The operating range by the day shift operation member 1100 is set so that the shift gear 1047 can be moved between the first shift position and the second shift position.

In addition, the shift gear 1047 forms a gap between the first teeth 1047a and the second teeth 1047b into which the locking pin 1102 of the daytime shift operation member 1100, which will be described later, can be inserted. It is done.

In addition, the shift gear 1047 has a boss portion 1047c that protrudes toward the front side of the first tooth portion 1047a, and has a boss portion 1047c toward the rear side of the second tooth portion 1047b. A significant portion is not installed. That is, the shift gear 1047 has a boss portion 1047c provided only on the front end side, which is one of the front and rear ends thereof. The protruding length of this boss portion 1047c is usually set to prevent the shift gear 1047 from being assembled in the reverse direction in the front-back direction with respect to the shaft body 1043.

That is, when the shift gear 1047 is assembled in the reverse direction in the front-back direction with respect to the normal shaft body 1043, even if the first tooth 1047a is operated to the engaging side with the driven gear 1048a, the boss of the shift gear 1047 The end of the portion 1047c is in contact with the front end 1044a of the intermediate cylindrical body 1044, and the first tooth 1047a cannot be moved to the engaging position with the driven gear 1048a.

In this way, since the protruding length of the boss portion 1047c is set, the fact that the boss portion 1047c is provided only at one end serves as a means of preventing assembly of the shift gear 1047 in the reverse direction.

In the main case portion 1004, a shift shaft 1048 (corresponding to the input side transmission shaft) positioned parallel to the work drive shaft 1041 is provided. A second transmission portion 1007B is provided across this transmission shaft 1048 and the output transmission shaft body 1042 of the work drive shaft 1041.

The second transmission unit 1007B includes a plurality of (three in the figure) transmission gears 1049 (corresponding to electric gears) supported on the transmission shaft 1048 on the lower side of the transmission than the driven gear 1048a. and a plurality (three pieces in the drawing) fixed to the intermediate cylindrical body 1044 (corresponding to the output-side transmission shaft) externally fitted to the output transmission shaft body 1042 in a state of constant engagement with the transmission gear 1049. It is provided with a gear pair by a driven transmission gear 1044b (equivalent to an electric gear).

The shift gear 1049 supported on the shift shaft 1048 is installed in a loosely inserted state so that it can rotate relative to the shift shaft 1048.

Between the plurality of shift gears 1049 and the plurality of driven shift gears 1044b in this always engaged state, the plurality of shift gears 1049 are operated by a shift operation body 1070 that is slidably operated within the shift shaft 1048. ) is selected, the shifting power is transmitted to the output transmission shaft body 1042 through the gear pair.

That is, with respect to the driven shift gear 1044b in a state of engagement with the shift gear 1049 selected by the shift operation body 1070, the rotation of the shift shaft 1048 is driven by the shift gear 1049 in a state of mesh with each other. It is transmitted as shifting power according to the gear ratio of the shifting gear 1044b.

The shift operating body 1070 includes a shift key portion 1071 having a locking protrusion 1071a configured to be disengaged from a locking recess 1049a formed on the inner peripheral side of each shift gear 1049; , the position of the locking protrusion 1071a of the shift key portion 1071 is slid in the direction of the axis of the shift shaft 1048, and the locking position for the shift gear 1049 that is the target of locking is selected. It is provided with a slide operation unit 1072 that operates.

In addition, it is provided with an elastic pressing mechanism 1073 that presses the locking protrusion 1071a of the shift key portion 1071 against the locking recess 1049a on the inner peripheral side of the shift gear 1049 to be locked.

As shown in FIGS. 16 and 17, the shift key portion 1071 and the slide operation portion 1072 are located at the rear end of the shift key portion 1071 in the outer peripheral groove 1072a formed at the front end of the slide operation portion 1072. The side protrusions 1071b are connected by being inserted.

Therefore, as the slide operation unit 1072 is pushed and pulled back and forth in the axial direction, the shift key portion 1071 also moves back and forth in the same direction.

The state shown in FIG. 16 shows the state in which the slide operation portion 1072 is pressed into the inner case main body 1040. In this state, the locking protrusion 1071a of the shift key portion 1071 is engaged with the locking recess 1049a of the shift gear 1049 on the frontmost side among the plurality of shift gears 1049, and the shift shaft ( The rotational power of 1048 is transmitted to the shifting gear 1049 on the frontmost side.

The state in which the shift gear 1049 on the front-most side is selected is a low-speed transmission position in which the rotation of the shift shaft 1048 is transmitted from the second shift portion 1007B to the output transmission shaft body 1042 at the lowest speed.

The shifting gear 1049 on the frontmost side that exists at the low-speed transmission position is comprised of an eccentric gear, and is meshed with the driven shift gear 1044b on the frontmost side on the side of the intermediate cylindrical body 1044, which is also comprised of an eccentric gear. .

In the transmission state at this low-speed transmission position, the drive speed of the transplant arm 1023 in the seedling transplant device 1002 relative to the travel speed is the lowest, and the weekly pitch is the longest in the second transmission unit 1007B. Lose. At this time, the driving torque of the shift gear 1049 by the shift shaft 1048 may be the smallest.

Additionally, in the transmission state at this low-speed transmission position, the rotation of the shift shaft 1048 is transmitted to the intermediate cylindrical body 1044 side in the transmission state at an uneven speed. This is because the driving speed of the transplanting arm 1023 is the lowest, so as to avoid as much as possible the hook being dragged in the mud on the bottom of the rice field during transplanting. That is, in the driving rotation trajectory of the grafting arm 1023, the driving speed of the range where the hook is in the mud is partially increased to enable the hook to quickly escape from the mud.

The state shown in FIG. 17 shows a state in which the slide operation unit 1072 is pulled out to the outside of the main case body 1040. In this state, the locking protrusion 1071a of the shift key portion 1071 is engaged with the locking recess 1049a of the last shift gear 1049 among the plurality of shift gears 1049, and the shift shaft 1048 ) of the rotational power is transmitted to the shift gear 1049 on the last end.

The state in which this last-stage shift gear 1049 is selected is a high-speed transmission position in which the rotation of the shift shaft 1048 is transmitted from the second shift portion 1007B to the output transmission shaft body 1042 at the highest speed. In the transmission state at this high-speed transmission position, the drive speed of the transplant arm 1023 in the seedling transplant device 1002 relative to the travel speed becomes relatively fast, and the weekly pitch becomes shortest in the second transmission portion 1007B. . At this time, the driving torque of the shift gear 1049 by the shift shaft 1048 becomes the largest.

Although not shown, the intermediate position between the state in which the slide operating portion 1072 is most pressed into the inside of the case main body 1040 and the state in which it is pulled out most outward is the medium-speed transmission position.

In this middle-speed transmission position, the locking protrusion 1071a of the shift key portion 1071 is engaged with the locking recess 1049a of the shift gear 1049 located in the middle position among the plurality of shift gears 1049. , the rotational power of the shift shaft 1048 is transmitted to the shift gear 1049 in the intermediate position. In the transmission state at the medium-speed transmission position, the drive speed of the transplanting arm 1023 in the seedling transplantation device 1002 relative to the travel speed becomes a medium speed, and the main pitch also becomes a medium length. At this time, the driving torque of the shift gear 1049 by the shift shaft 1048 also becomes a medium size.

The elastic pressing mechanism 1073 presses the steel ball 1073b pressed by the coil spring 1073a against the concave portions 1071c formed at a plurality of locations in the longitudinal direction of the shift key portion 1071. When the steel ball 1073b is pressed against the recessed portion 1071c of this shifting key portion 1071, the locking protrusion 1071a protruding on the opposite side from the recessed portion 1071c is formed to cause the shifting gear 1049 to be engaged. ) is pressed against the engaging recess 1049a on the inner circumference side. By providing these coil springs 1073a, steel balls 1073b, and concave portions 1071c, an elastic pressing mechanism 1073 is formed.

The shift key portion 1071 uses as a swing point the engaging portion of the outer peripheral groove 1072a and the rear end protrusion piece 1071b, which is the connection portion between the shift key portion 1071 and the slide operation unit 1072, and provides elastic compression. A swing operation is possible toward the engaging recess 1049a on the inner circumferential side of the shifting gear 1049 in the pressing direction by the mechanism 1073, that is, in a direction intersecting the slide operation direction by the slide operation unit 1072. It is composed of:

In addition, the pressing point by the elastic pressing mechanism 1073 is provided at a position further away from the swing point than the plurality of gear pairs in the second transmission unit 1007B. Therefore, the shorter the gear pair whose main pitch is set by the action of the lever, the stronger the pressing action by the elastic pressing mechanism 1073 is.

Among the shift gears 1049 in the second transmission unit 1007B, the high-speed gear at the last stage and the middle-speed gear at the intermediate position are each sandwiched from both sides by collars 1074. And, the low-speed gear on the front-most side is installed in a state where it is sandwiched between the collar 1074 and a part of the shift shaft 1048.

As shown in FIG. 17 , the spacing (a1001, a1002, a1003) between the collars 1074 is the location where the gear pair whose weekly pitch by the seedling transplant device 1002 is set to be short exists, the closer the shift gear 1049 is. ) is set at wide intervals so that the amount of engagement of the shift key portion 1071 for ) increases.

That is, the locking protrusion 1071a is formed in a mountain shape with a tapered tip, as shown in FIGS. 16 and 17 . Therefore, if the spacing (a1001, a1002, a1003) between the collars 1074 is wide, they are deeply engaged with the engaging concave portion 1049a of the shifting gear 1049, and the engaging margin increases, and conversely, if it is shallow, the shifting gear 1049 is engaged deeply. The engaging margin for the engaging concave portion 1049a of the gear 1049 becomes smaller.

The front-to-back widths of the teeth 1049b of the portion that engages with the driven shift gear 1044b of the shift gear 1049 in the second shift portion 1007B are all set to the same width, but each shift gear 1049 On the hub surface of , bulging portions 1049c are formed scattered at a plurality of locations in the circumferential direction. The protrusion amount of this bulging portion 1049c is different for each transmission gear 1049.

That is, as shown in FIG. 17, the low-speed gear in the frontmost position has a bulge 1049c with a small protrusion on the rear hub surface, and the medium-speed gear in the middle position has a bulge 1049c with a large protrusion on the rear hub surface. (1049c) is formed. And, in the rearmost high-speed gear, bulges 1049c and 1049c are formed to protrude from the hub surfaces on both front and rear sides in both front and rear directions.

As a result, the width of the teeth 1049b of the shifting gear 1049 and the front-back width including the bulge 1049c are set to a width that matches the distances a1001, a1002, and a1003 between the collars 1074 described above. It is done.

As a result, the spacing (b1001, b1002) between the teeth 1049b of the shifting gear 1049 is the tooth of the shifting gear 1049 existing at the location where the spacing (a1001, a1002, a1003) between the collars 1074 is widened. So that the gap (b1002) between the teeth 1049b of the shifting gear 1049 existing at the location where the gap (a1001, a1002, a1003) between the collars 1074 is narrowed is smaller than the gap (b1001) between the collars (1049b). It is set.

The shift operation body 1070 is slid in the axial direction of the shift shaft 1048 by operating the second shift lever 1075.

As shown in FIGS. 15 and 16 , a second shift lever 1075 is connected to the rear end of the slide operation portion 1072 of the shift operation body 1070 so as to be capable of relative rotation. The lower end of the second shift lever 1075 is connected to the slide operation portion 1072, and the middle portion in the vertical direction is supported by a lever support portion 1076 provided at the upper part of the main case main body 1040.

As a result, in the portion of the lever body of the second shift lever 1075 supported so as to be relatively rotatable by the lever support portion 1076, the center of the lever body portion at the middle position along the vertical direction of the second shift lever 1075 This becomes the actual center of rotation, and the second shift lever 1075 is operated to rock around the rotation center line y1001 indicating this center of rotation.

Therefore, by swinging the second shift lever 1075 around the swing center line y1001, the slide operation portion 1072 of the shift operation body 1070 is configured to slide along the axis direction of the shift shaft 1048. It is done.

The lever support portion 1076 described above supports the middle portion of the second shift lever 1075 so as to be relatively rotatable, but the movement of this middle portion in the forward and backward directions is regulated, and the positional movement in the left and right directions is within a predetermined range. It is provided with a pair of upper and lower recessed pivot parts 1076a formed in a U-shape in plan view so as to allow it within. In this way, by allowing the middle portion in the vertical direction of the second shift lever 1075 to move within a predetermined range in the left and right directions, the center portion coincides with the axis of the middle portion in the vertical direction of the second shift lever 1075. The swing center line (y1001) also moves in position within a predetermined range in the left and right directions.

That is, the swing center line (y1001) is also supported in a state where its position can be moved within a predetermined range in the left and right directions, so that the swing of the second shift lever 1075 does not interfere with the forward and backward movement of the linearly moving slide operation unit 1072. It is configured so that operations can be performed.

The day shift operation member 1100 of the day shift mechanism 1007 is configured as shown in FIGS. 15, 16, and 18.

That is, a locking pin 1102 that is inserted between the first teeth 1047a and the second teeth 1047b is fixed to the lower end of the operating shaft 1101 that penetrates the upper wall portion of the main case portion 1004. , a plate-shaped operating body 1103 is installed at the upper end of the operating shaft 1101 located outside the upper wall portion.

By rotating this plate-shaped operating body 1103 around the axis of the operation shaft 1101, the locking pin 1102 present at an eccentric position changes the position of the shift gear 1047 in the axis direction of the work drive shaft 1041. It is configured to do so. The position of the plate-shaped operating body 1103 around the axis is determined by the ball detent mechanism 1104.

The daytime shift operation member 1100 that operates the first shift unit 1007A of the daytime shift mechanism 1007 has a plate-shaped operating body 1103 shown in FIG. 22, although description of the intermediate linkage mechanism is omitted. It is linked to the first shift lever 1077.

The upper end of the first shift lever 1077 is installed in the T-shaped guide groove 1111 of the lever guide portion 1110 installed on the operating section floor 1014 of the traveling body 1001. . The upper end of the first shift lever 1077 is located in the guide groove 1111 in the left and right lateral directions in the figure, and is guided by the guide groove 1111 and is shifted to one of two positions, the first shift position and the second shift position. It is configured so that it can be selected and its location can be changed.

In addition, the upper part of the second shift lever 1075 that operates the second shift unit 1007B is also located within the guide groove 1111 in the front-back direction along the front-back direction among the guide grooves 1111 of the lever guide section 1110. It is positioned and guided by the guide groove 1111, and is configured to change its position so that any of the three positions of the low-speed shift position, the middle-speed shift position, and the high-speed shift position can be selected.

In the lever guide unit 1110, pattern display units 1112 on which numerical values representing the weekly pitch are written are provided on both left and right sides of the T-shaped guide groove 1111.

In the figure shown in FIG. 22, a character pattern of "14" supporting a weekly pitch of 14 cm exists in the upper left corner of the figure. In order to set this weekly pitch of 14 cm, the first shift lever 1077 is positioned at the left end of the guide groove 1111, and the second shift lever 1075 is positioned next to the right of the character pattern of “14” at the forefront. Just place it. In this state, the first shift lever 1077 is operated from the first shift position to the high-speed side, and the second shift lever 1075 is also operated to the high-speed shift position, so the implantation device side is driven at the highest speed, Set the pitch to the densest 14cm.

From this state, when the first shift lever 1077 is operated toward the right end of the guide groove 1111 and operated to the forward position of the character pattern “16”, the first shift lever 1077 switches to the second shift position. and the state is switched to the low speed side. Therefore, if the position of the second shift lever 1075 does not change, the weekly pitch is set to 16 cm.

Additionally, from this state, if the position of the second shift lever 1075 is located next to the left of the character pattern “21”, the weekly pitch is set to 21 cm, and if the position of the second shift lever 1075 is located next to the left of the character pattern “28”, the weekly pitch is set to 21 cm. is set to 28cm.

If the same operation is performed with the first shift lever 1077 positioned at the left end of the guide groove 1111, the position of the second shift lever 1075 is located next to the right of the character pattern “18”, and the weekly pitch is set to 18 cm, and when placed next to the right of the character pattern “24”, the weekly pitch is set to 24 cm.

That is, by moving the first shift lever 1077 to the left and right, the shift gear 1047 is switched between the first shift position and the second shift position, and the character pattern group on the left and the right side of the guide groove 1111 are switched. It is possible to select a group and select a target character pattern from each group of character patterns by moving the second shift lever 1075 in the forward and backward directions.

Therefore, it is easy to set the weekly pitch by operating positions of the first shift lever 1077 and the second shift lever 1075 with less visual error.

The guide groove 1111 of the lever guide unit 1110 is formed by a through hole formed in the operating unit floor 1014 of the traveling body 1001. Fig. 22 is an explanatory diagram viewed from the plane showing the pattern display portion 1112 in the lever guide portion 1110. The first shift lever 1077 and the second shift lever 1075 in the guide groove 1111 are installed in a state that does not protrude upward from the upper surface of the operating section floor 1014, and are normally installed on the operating section floor 1014. ) It is covered with a mat on top, so the mat can be rolled up and manipulated as needed.

The power shifted by the day shift mechanism 1007 is transmitted from the intermediate cylindrical body 1044 to the torque limiter 1046.

The torque limiter 1046 includes a disk-shaped support plate 1046a fixed to the rear end of the intermediate cylindrical body 1044, a press plate 1046b abutting toward the support plate 1046a, and the press plate 1046b on the support plate 1046a side. It is comprised of a coil spring 1046c that presses and presses toward the coil spring 1046c. The shifting power from the weekly shifting mechanism 1007 is transmitted to the transplant clutch 1008 via this torque limiter 1046.

[Transplant Clutch]

The transplant clutch 1008 is configured as follows.

At the rear end of the rear cylindrical body 1045 of the work drive shaft 1041, there is a disk-shaped drive side rotation member 1080 that engages with the outer circumferential spline of the rear cylindrical body 1045 and rotates integrally with the rear cylindrical body 1045. is installed.

The outer peripheral side of the output transmission shaft body 1042 extending rearward than the rear cylindrical body 1045 is engaged with the spline portion 1042a formed on the outer peripheral surface of the output transmission shaft body 1042, and the output transmission shaft body 1042 ) and a driven side rotation member 1081 that can rotate integrally and move in position in the axis direction of the output transmission shaft body 1042 is provided.

This driven-side rotating member 1081 is pressed toward the driving-side rotating member 1080 by a compression spring 1082, and each of the driving-side rotating member 1080 and the driven-side rotating member 1081 On the opposing surfaces, engaging portions 1080a and 1081a that enable power transmission in a mutually engaged state are formed.

The compression spring 1082 includes a spring receiving portion 1081b formed on a surface opposite to the side on which the engaging portion 1081a of the driven side rotation member 1081 is formed, and a spring receiving portion 1081b formed on the inner side of the main case portion 1004. It is installed between the fixed parts. As a fixing part on the inner side of this main case part 1004, the inner end of the inner race 1040c of the ball bearing 1040b supporting the output transmission shaft body 1042 is used, but it must be in this position. There is no

And, the shape of the compression spring 1082 is such that the winding diameter at the end on the side abutting the spring receiving portion 1081b in the axial direction of the work drive shaft 1041 is the winding diameter on the side abutting against the inner end of the inner race 1040c. It is formed in a truncated cone shape set larger than the winding diameter.

The winding diameter of the compression spring 1082 on the side that abuts the inner end of the inner race 1040c is approximately the same as or slightly larger than the outer diameter of the externally fitted output transmission shaft body 1042. Therefore, the end position can be determined using the inner end of the inner race 1040c of the ball bearing 1040b supporting the output transmission shaft body 1042 without requiring any special positioning means.

As shown in FIG. 16, the driven-side rotating member 1081 is spaced apart from the driving-side rotating member 1080 by resisting the pressing force of the pressing spring 1082 by the clutch operating member 1083 abutting the outer periphery. It is operated sideways, and is provided with an engaging portion 1081c on the outer periphery where the clutch operating member 1083 engages.

The clutch operating member 1083 is provided with an operating pin 1084 that penetrates the upper wall portion of the main case portion 1004, and at the lower end of the operating pin 1084, an engaging portion of the driven side rotation member 1081 is provided. In contact with 1081c, an operation portion 1084a is formed that moves the driven side rotation member 1081 in the axis direction of the output transmission shaft body 1042 in accordance with the rotation operation of the operation pin 1084.

The clutch operating member 1083 is an operating pin ( An operating plate 1085 for rotating the operating pin 1084 is provided at the end of the shaft 1084. And, an operation guide member 1086 that supports the part of the operation plate 1085 so as to fit it from above and below and guides the rotation operation of the operation plate 1085 around the rotation axis p1001 is provided in the main case portion. It is installed outside (1004).

As a result, the positional movement of the operation pin 1084 in the direction along the rotation axis p1001 is regulated by the operation plate 1085, and the operation range around the rotation axis p1001 is controlled by the operation plate 1085 and the operation plate 1084. It is regulated by the abutment of the operation guide member 1086.

The position of the spring receiving portion 1081b of the driven rotating member 1081 is relative to the engaging portion 1081c of the driven rotating member 1081 at the lower end of the operating pin 1084. , on the inner side in the radial direction of the driven side rotary member 1081, and in the axial direction of the work drive shaft 1041, the engaging portion ( It is installed near the opposing surface where 1081a) is formed.

In this way, the spring receiving portion 1081b is on the inner side in the radial direction than the engaging portion between the operating pin 1084 and the engaging portion 1081c of the driven side rotation member 1081, and the engaging portion 1081a It has a greatly concave shape close to the side where it exists. Thereby, it is possible to avoid that the axial length of the working drive shaft 1041 of the pressing spring 1082 is restricted by the position of the operation pin 1084 in the axial direction of the working driving shaft 1041, and the main case part (1004) can be compacted.

[fertilization drive system]

From the above-described traveling drive system, the fertilizing device drive system that branches and transmits the driving force to the fertilizing device 1009 is configured as follows.

As shown in FIG. 21, on the rear side of the main case portion 1003, a branch case portion 1005, which is separate from the main case portion 1003, is connected and fixed through an installation bolt or the like (not shown). there is.

The main case portion 1003 and the branch case portion 1005 are in a sealed state where the openings 1030a and 1050a formed at the connection points are joined to each other, and their respective internal spaces are in communication with each other.

As shown in FIG. 21, the branch case portion 1005 intersects the input side normal portion 1050A supporting the rear wheel output shaft 1064 extending rearward from the main case portion 1003 and the rear wheel output shaft 1064. It is provided with an output-side normal portion 1050B that is externally fitted to the branch transmission shaft 1051 extending to and supports the branch transmission shaft 1051. The input side normal portion 1050A and the output side normal portion 1050B are composed of an integrated body with a common internal space.

The branch output bevel gear 1052, which transmits power from the rear wheel output shaft 1064 to the branch transmission shaft 1051, is installed in the input side normal portion 1050A, and the fertilization bevel gear meshed with the branch output bevel gear 1052 ( 1053) (corresponding to a bevel gear for branch input) is installed in the output side normal portion 1050B.

The bevel gear 1052 for branch output is installed in the input side normal part 1050A on the side closer to the main case part 1003 than the branch transmission shaft 1051.

The rear wheel output shaft 1064, which has a rear wheel input bevel gear 1064a engaged with the rear wheel output bevel gear 1035d at the front end, has a ball installed on the front end to the case body 1030 of the main case portion 1003. It is supported by a bearing 1039, and the rear end is supported by a ball bearing 1054 installed near the rear end of the branch case portion 1005.

This rear wheel output shaft 1064 has a step portion 1064C (corresponding to a positioning portion) formed at a midway position in the axis direction, and the front portion corresponding to the upper side in the transmission direction is larger than the step portion 1064C. The small diameter shaft portion 1064B is the diameter shaft portion 1064A, and a rear side corresponding to the lower side in the rolling direction than the step portion 1064C is formed in the small diameter shaft portion 1064B.

The step portion 1064C is formed near the boundary between the main case portion 1003 and the branch case portion 1005, and a spline portion 1064D is formed at a portion of the small diameter shaft portion 1064B close to the step portion 1064C. It is formed, and a bevel gear 1052 for branch output is spline-fitted to this spline portion 1064D.

The opening 1050a of the branch case portion 1005 formed at a location opposite the main case portion 1003 has an inner diameter through which the branch output bevel gear 1052 supported on the rear wheel output shaft 1064 can be inserted.

Therefore, when embedding the rear wheel output shaft 1064 in the branch case part 1005, the bevel gear 1052 for branch output can be supported in advance on the rear wheel output shaft 1064, and then it can be embedded in the branch case part 1005. , convenience can be achieved during assembly and disassembly.

The branch transmission shaft 1051, which is equipped at the input side end with a fertilization bevel gear 1053 that engages the branch output bevel gear 1052 supported on the rear wheel output shaft 1064, is in an attitude perpendicular to the rear wheel output shaft 1064. It is placed. And, the input side end is configured to be insertable and extractable from the output side opening 1050b formed in the output side normal portion 1050B of the branch case portion 1005, and the output side end is drawn outward from the output side opening 1050b of the output side normal portion 1050B. It is supported in a protruding state.

A linkage shaft (not shown) to the fertilizing device 1009 is connected to the protruding portion of the branch transmission shaft 1051 that protrudes outward from the output side opening 1050b.

Additionally, the branch transmission shaft 1051 is at a location corresponding to the insertion limit position into the output side normal portion 1050B, and the input side end abuts the rear wheel output shaft 1064. That is, when the branch transmission shaft 1051 is inserted from the output side opening 1050b into the output side normal portion 1050B until it reaches the insertion limit position, the input side end is in a positional relationship in contact with the rear wheel output shaft 1064, so that the input side normal portion ( The position of the rear wheel output shaft 1064 with respect to 1050A) is determined.

The bevel gear 1053 for fertilization is supported to rotate relative to the branch transmission shaft 1051, and the branch transmission shaft 1051 and the bevel gear 1053 for fertilization are connected to a fertilization clutch 1055 (equivalent to a work clutch). ) is configured to enable separation through bonding.

The fertilizing clutch 1055 is provided with a normal shift member 1056 spline-fitted to a spline portion formed on the outer peripheral surface of the branch transmission shaft 1051. And, the claw portion 1056a formed on the opposing surface of the normal shift member 1056 to the bevel gear 1053 for fertilization is caught on the side of the bevel gear 1053 for fertilization opposed to the normal shift member 1056. It is configured so that the rotation of the fertilizing bevel gear 1053 can be switched between a state in which the rotation of the fertilizing bevel gear 1053 is transmitted to the branch transmission shaft 1051 and a state in which transmission is interrupted by engaging and disengaging the engaging recessed portion 1053a.

The normal shift member 1056 is pressed toward the bevel gear 1053 for fertilization by a coil spring 1057, and resists this pressing force to move the normal shift member 1056 away from the bevel gear 1053 for fertilization. A clutch operation shaft body 1058 that operates toward the side is installed penetrating the output side normal portion 1050B.

[Other Embodiment 10]

In the above embodiment, the rice transplanter provided with the main case part 1004 as the planting case part is shown, but it is not limited to this. For example, when used in a seed drill equipped with a direct seeding device, the planting work case portion becomes a work case portion for changing the planting spacing by the direct seeding device.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 11]

In the above embodiment, the fertilizing device 1009 is used as the powder supply device, but it is not limited to this.

For example, it may be to supply chemicals such as herbicides or insect repellent.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 12]

In the above-described embodiment, the pattern display portion 1112 in the lever guide portion 1110 is illustrated as having a structure disposed on the left and right sides of the T-shaped guide groove 1111, but it is not limited to this structure.

For example, as shown in Figure 23 (a), it is disposed on the front and lateral sides of the L-shaped guide groove 1111, or as shown in Figure 23 (b), a cross-shaped guide groove ( 1111) can be adopted with an appropriate structure, such as arranging them front, rear, left, and right.

The other configuration may be the same as that of the above-described embodiment.

[Other Embodiment 13]

In the above-described embodiment, the shift operating body 1070 of the day shift mechanism 1007 is installed on the side of the shift shaft 1048 arranged as an axis corresponding to the input side transmission shaft, and the intermediate cylindrical body installed as the output side transmission shaft. Although a structure in which power is selectively transmitted to the fixed driven transmission gear 1044b is illustrated in 1044, the structure is not limited to this structure.

For example, a fixed electric gear is installed on the shift shaft 1048 arranged as an axis corresponding to the input-side transmission shaft, and an electric gear capable of relative rotation is installed on the intermediate cylindrical body 1044 installed as the output-side transmission shaft. , it may be configured so that the relatively rotatable electric gear on the side of the intermediate cylindrical body 1044 is selected by the shift operation body 1070.

The other configuration may be the same as that of the above-described embodiment.

The present invention is not limited to a riding-type rice transplanter for 4-row transplanting, but is also applicable to a small number of plants of 3 or less, or a work machine employing a seedling transplanter or direct seeding device of 5 or more plants, a hand-operated work machine, or an electric power plant for various work machines such as a cultivator or tractor. Applicable to devices.

1: Running body
2: Seedling transplant device (working device)
3: Main case part
3A: Sub-transmission mechanism
4A: Work type shifting mechanism (type wave type shifting mechanism)
4: Seeding case part (work case part)
5: Branch case part
5A: Branch electric mechanism
6: Main transmission mechanism
8: Working clutch
16: Axle case
30a: opening
31: upper shifting shaft
32: Lower shifting shaft
32a, 32b: lower gear
32c, 32d: Engagement recess
32e: shaft support hole
34: Shift member
34a, 34b: Engaging teeth
40a: opening
41: Shift operation shaft (work drive shaft)
42: Output electric shaft body
43: Front normal shaft body
47: shift gear
50a: opening
50A: Input side barrel shape
50B: Output side barrel-shaped portion
51: branch drive shaft
52: Bevel gear for branch output
53: Bevel gear for branch input
64: Transmission shaft for driving
64C: Positioning unit
65: transmission shaft
66: Bevel gear pair
67: Bevel gear pair
80: Drive side rotation member
80a: engaging portion
81: Followed side rotation member
81a: engaging portion
81b: spring receiving portion
81c: Locking joint
82: compression spring
83: Clutch operation member
84: operation pin
85: operating plate
86: Operation guide member
p1: rotation axis
1001: Running aircraft
1002: Seedling transplant device (working device)
1004: Cooling work case part
1007: Day shift mechanism (day shift mechanism)
1041: Shift operation shaft
1044: Middle cylindrical body (output side transmission shaft)
1044b: Driven shifting gear (electric gear)
1047: shift gear
1048: Shift shaft (input side transmission shaft)
1049: Shift gear (electric gear)
1049b: Ilbu
1070: Shift operation body
1071: Shift key part
1072: Slide control unit
1073: Elastic compression device
1074: collar

Claims (5)

A sowing system transmission mechanism that changes the engine power and transmits it to the seedling transplant device or sowing device is built into the sowing work case portion,
The type wave system transmission mechanism includes a plurality of gear pairs arranged in a state of constant engagement across the input side transmission shaft on the upper side of the transmission and the output side transmission shaft on the lower side of the transmission, and enables power transmission by selecting any one gear pair among the gear pairs. It is provided with a shift operation body that allows,
The shift operation body is provided with a shift key portion that can be alternatively engaged and disengaged with one of the electric gears constituting the gear pair as an engaging object,
The locking engagement margin of the shift key portion with respect to the electric gear to be engaged is selected from among the plurality of gear pairs, the gear pair having a short weekly pitch by the seedling transplant device or a short seeding pitch by the seeding device. The electric device of a faucet work machine that is configured to become larger as it becomes larger. The method according to claim 1, wherein a gap in the axis direction of the input transmission shaft or the output transmission shaft is set between the electric gears disposed at adjacent positions in the axis direction of the input transmission shaft or the output transmission shaft. Multiple colors are arranged,
The spacing between the collars is such that the amount of engagement of the shift key portion with respect to the electric gear increases at a location where the gear pair having a short weekly pitch by the seedling transplant device or a seeding pitch by the seeding device is present. The electric device of the faucet machine, set at wide intervals. The method according to claim 2, wherein the gap between the teeth of the electric gear in the axial direction of the input-side transmission shaft or the output-side transmission shaft is the distance between the teeth of the electric gear present at a location where the gap between the collars is widened. Furthermore, the electric device of a water faucet work machine, wherein the interval between the teeth of the electric gear existing at the location where the interval between the collars is narrowed is narrowed. The method according to any one of claims 1 to 3, wherein the shift operation body slides the shift key portion and the shift key portion in the axis direction of the input side transmission shaft or the output side transmission shaft, thereby engaging the shift key portion. Equipped with a slide operation unit that selects and operates an engaging position for the target electric gear,
The shift key portion is configured to be swing-operable in an engaging direction with the electric gear that intersects the slide operation direction by the slide operation unit, with the connection point to the slide operation unit as a swing point. of powertrain. The method according to claim 4, wherein the shift operating body is provided with an elastic pressing mechanism that presses and presses the shift key portion against the electric gear side to be engaged,
The pressing point by this elastic pressing mechanism is set at a position further away from the swing point than the plurality of gear pairs,
The shorter the gear pair in which the main pitch by the seedling transplantation device or the seeding pitch by the seeding device is set, the more the gear pair is located near the swing point side from the pressing point by the elastic pressing mechanism. Electric gear.