KR20180003440A - Transmission device of working machine and transmission device of paddy field working machine - Google Patents

Abstract

The present invention relates to a transmission device of a working machine. Specifically, the transmission device comprises: a main case unit; a working case unit; a working clutch; and a rotating member. According to the present invention, the transmission device can be installed in a driving vehicle capable of travelling a pavement, and can enable miniaturization of the transmission device.

Description

TECHNICAL FIELD [0001] The present invention relates to a power transmission apparatus for a working machine and a power transmission apparatus for a power reception work machine,

The present invention relates to an automatic transmission comprising a main body portion for outputting transmission power to a traveling driving system and a working case portion for outputting a transmission power to a working device, To a power transmission apparatus of a working machine in which a work clutch capable of interrupting power transmission to a drive shaft is incorporated.

The present invention also relates to a power transmission apparatus for an electric power receiving machine having a working apparatus such as a seedling implanting apparatus for planting seedlings on a ground surface or a direct wave apparatus for spraying seeds on a ground surface.

The present invention also relates to a power transmission apparatus for an electric power receiving machine having a working apparatus such as a seedling implanting apparatus for planting seedlings on a ground surface or a direct wave apparatus for spraying seeds on a ground surface.

In the case of installing the work clutch, in the conventional structure, the engagement position of the drive-side rotational member and the driven-side rotational member, the engagement position of the clutch operating member with respect to the driven-side rotational member, (Refer to Patent Document 1).

On the other hand, in an electric power receiving machine having a working device of a wave form such as a seedling implanting device or a direct wave device, there is provided a takeoff power take-out structure for supplying the power of the engine mounted on the running vehicle to the fertilizing device. An example of the water receiving machine having such a structure is one having the structure described in the following [1].

[1] A transmission mechanism of a traveling drive system and a transmission mechanism between a stock company are incorporated in a mission case, and a fertility drive case is disposed in a rear portion of the mission case. A driving transmission shaft for driving rear wheels protruding rearward from the transmission case extends rearwardly through the inertia drive case so that the driving force can be diverted toward the driving device in the middle of the driving vehicle axis 2).

On the other hand, in an electric power receiving machine provided with a working device of a wave form such as a seedling planting machine or a direct wave machine, the power of the engine mounted on the traveling airframe is supplied to the seedling planting machine or the direct- Structure. An example of the water receiving machine having such a structure is one having the structure described in the following [2].

[2] Inside the mission case, a transmission portion for a traveling portion of a traveling driving system and a transmission portion for a first and second stocks for a seedling-implanting device are built in. The power transmitted from the traveling portion transmission portion is output to the front wheels and the rear wheels via the output shaft and the transmission chain and the power shifted in the first and second weekly transmission portions is output to the seedling plant through the power take-off shaft. In the first and second weekly shifting portions, a plurality of gear pairs are used, and a pair of gears of interest is selected in a gearshift key (patent document, clutch body) provided in each shifting portion so that multi-stage inter- (See Patent Document 3).

Japanese Patent Application Laid-Open No. 2008-173087 (paragraphs [0038], [0039], Figs. 5 and 7) Japanese Patent Application Laid-Open No. 2015-223110 (paragraphs "0086", "0092", "0094", FIGS. 9, 13, 14) Japanese Patent Application Laid-Open No. 2008-289399 (paragraphs "0032", "0036", "0038", "0050", FIGS. 3, 4, 6)

In the power transmission apparatus of the working machine described in Patent Document 1, a space corresponding to the sum of the axial length of the drive-side rotational member, the axial length of the driven-side rotational member, and the axial length of the pressing spring And there is room for improvement in that it is difficult to downsize the power transmission apparatus.

The present invention contemplates the arrangement structure of the driving side rotating member, the driven side rotating member, the clutch operating member, and the urging spring in the working case part, thereby further reducing the size of the working case part.

On the other hand, in the water receiving machine described in Patent Document 2, a fertilizing drive case is provided separately from the mission case. Therefore, it is advantageous in that the mission case itself can be prevented from becoming larger in size as compared with the case in which the inertia drive mechanism is incorporated in the mission case. However, in addition to the transmission mechanism of the traveling driving system, there is also room for improvement in that the transmission case is further equipped with a weekly transmission mechanism, which makes it difficult to further miniaturize the transmission case.

In addition, if the fertilization drive case is provided separately from the mission case, the fertilization operation case having the specification not including the fertilization apparatus is removed, and only the fertilization operation case with the fertilization apparatus having the fertilization apparatus is equipped It is advantageous in that it is easy to obtain the structure according to the specification of the water-receiving machine.

However, if the mission case and the fertilizing drive case are constituted by separate cases separate from each other, there is a convenience in easily diversifying specifications, while a bearing structure or a seal structure is required in each case, The number of parts is likely to increase. Further, in the connecting positions of the cases, the opposing wall surfaces of the connecting portions are connected to each other to have a double wall structure, which may increase the overall weight, and there is room for improvement in these points.

It is an object of the present invention to provide a transmission case in which the transmission case is made easy to diversify the specification of the receiving case and the main part of the transmission case is downsized, And to avoid the increase.

On the other hand, in the power receiving machine described in Patent Document 3, the structures of the engaging portions in the respective gear pairs are almost the same in the engaging portions of the gear pairs of the respective gear positions and the shift key . Thus, engagement of the shift key with respect to each gear pair can achieve a similar engagement state even when any of a plurality of gear pairs is selected as the engagement object.

However, each pair of gears, which is a shift gear, has a structure in which the gear diameters are variously set according to the gear ratio, and the transmission torque is also different for each gear position. Due to this, the gear pair set to be small even if the transmission torque is small, and the gear pair to which the transmission torque is set large, have different required strengths depending on the required torque.

However, in the structure described in Patent Document 3, since the engaging margins of all the gear pairs with respect to the shift key are set to be the same, the gears of all the gear pairs and the shift keys If the engagement margin is designed to be large, the following problems may occur. That is, in the gear pair of the speed change stage in which the assumed transmission torque is small, the engaging engagement margin of the transmission gear is structured to be excessively larger than necessary.

Therefore, when the engagement margin of the transmission gear on the small diameter side of the pair of gears is made large, the transmission gear itself tends to be hardened to secure the engagement margin. When the diameter of the transmission gear on the small diameter side is large, the diameter of the transmission gear on the large diameter side engaged with the diameter of the transmission gear necessarily becomes large, and the whole gear pair is likely to be increased in size.

The present invention aims to reduce the size of the transmission by making the engaging margins at the engagement positions of the gear pairs of the respective speed change stages by the plurality of gear pairs and the transmission gears in accordance with the transmission torque for each gear pair .

The transmission device of the working machine according to the present invention is characterized in that it comprises a main case portion having a transmission mechanism for shifting the input engine power and outputting a transmission power to the travel drive system, A work case including a work system transmission mechanism and outputting a shift power to a work device is provided, and the work case portion includes a work drive shaft for transmitting a shift power by the work system transmission mechanism to the work device, And a work clutch capable of interrupting transmission of power from the transmission mechanism to the work drive shaft is incorporated in the power transmission mechanism. The work clutch includes: a drive side rotating member that receives power from the work system transmission mechanism on the upper side in the power transmission direction; And is externally fitted to the working drive shaft at a lower side in the power transmission direction than the driving side rotating member, The integrally rotatably supported on the drive shaft work with the species also comprising a driving side rotating member,

Wherein the driven-side rotational member and the driven-side rotational member are provided with engaging portions capable of transmitting power in the engaging state on the respective opposed surfaces, and that the driven-side rotational member And a pressing spring which is configured to be movable in the axial direction of the working drive shaft so as to be able to move in the far direction and which presses and urges the driven side rotating member toward the driving side rotating member is installed outside the working driving shaft, And the clutch operating member is engaged with the engaging portion formed on the outer peripheral side of the driven-side rotating member to engage with the engaging portion formed on the outer peripheral side of the driven- Side rotating member to the side away from the driving-side rotating member And possibly the configuration, the pressure spring, which is greater than the clutch-operating handle and the engaging portion wherein the engaging parts of the equipment in the inward side in the radial direction of the longitudinal side rotary member.

According to the present invention, the abutment position of the urging spring with respect to the driven-side rotatable member is provided on the inner side in the radial direction with respect to the engaging portion without being restricted by the position of the engaging portion between the clutch operating member and the engaging portion 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 rotating member while using the pressing spring of a required length.

In the present invention, a spring receiving portion is formed on a surface of the driven side rotating member opposite to the side where the engaging portion is formed, and the spring receiving portion is provided with a spring It is preferable that the engaging portion is provided at a position near the opposed surface side where the engaging portion is formed.

According to the present invention, since the spring receiving portion is provided in the vicinity of the opposite surface side where the engaging portion is formed, as compared with the engaging portion between the clutch operating member and the engaging portion in the axial direction of the working drive shaft, The driven-side rotatable member and the urging spring are overlapped with each other, so that the internal space of the work case can be reliably shortened.

In the present invention, the urging spring is mounted between the spring receiving portion and the fixed portion on the inner surface side of the work case portion, and further on the other end side than the one end side in the axial direction of the working drive shaft It is preferable to form a large cone.

With this configuration, it is difficult for the pressing spring to be deformed such as to be bent in a direction crossing in the elongating and contracting direction, and it is easy to exert the spring force properly.

In the present invention, the pressing spring is formed such that the winding diameter of the driven side rotating member on the side supported by the spring receiving portion is larger than the winding diameter on the opposite side, and the winding diameter on the opposite side is larger than the winding diameter It is preferable that the inner circumferential surface is set so as to abut the outer peripheral surface of the working drive shaft.

By providing this configuration, by setting the winding diameter of the side supported by the spring receiving portion to be large, and the winding diameter on the opposite side to be small so as to abut the outer peripheral surface of the working drive shaft, It is easy to mount it stably.

In the present invention, the clutch operating member includes: an operating pin penetrating the working case portion and being operated around a rotating axis in a direction crossing the axis of the working drive shaft; And an operation guide member for positioning the operation plate in the direction along the rotation axis is provided in the work case portion.

With this configuration, it is possible to reliably restrict the escaping from the work case portion without impairing the operability of the clutch operating member.

In the present invention, it is preferable that the operation guide member includes a guide portion capable of permitting operation of the operation plate about the rotation axis in a range corresponding to the on-off operation range of the work clutch.

By providing this configuration, the operating range of the clutch operating member can be recognized appropriately by means of regulating the escape of the clutch operating member from the working case portion, and the operability can be improved with a simple structure.

In the present invention, the working drive shaft includes: an output transmission shaft integrally rotating with the driven-side rotating member; and a transmission shaft having an output shaft, which is externally fitted to the output shaft and rotates relative to the output shaft, Wherein a portion of the normal shaft body located on the upper side in the most forward direction is inserted into the inner circumference side of the communication boss of the outputting bevel gear located in the main casing portion, The inner circumferential side passageway of the normal shaft member at the position where the main shaft portion and the double shaft structure portion are connected to each other.

With this configuration, the space on the inner circumferential side of the transmission boss of the output bevel gear in the main case portion, the inner circumferential side passage of the normal shaft body, and the double shaft structure portion of the output transmission shaft and the normal shaft are effectively utilized, So that the lubricating oil can be guided to the working case portion side.

In the present invention, it is preferable that the normal shaft member is divided into a plurality of portions in the axial direction of the output transmission shaft member, and a member rotating together with the normal shaft member is fitted to each of the divided normal shaft members.

By using this configuration, even when an output electric transmission shaft having a long axial length is used, proper lubrication can be performed by using the gap between the normal shaft bodies present in the middle.

The power transmission apparatus of the present invention includes a main speed change mechanism for shifting the input engine power and a sub speed change mechanism for shifting the power transmitted from the main speed change mechanism to a plurality of levels and outputting the power to the traveling driving system Wherein the main casing unit includes a main casing unit and a main casing unit for transmitting the power output from the main casing unit to the seedling planting apparatus or the seeding apparatus, And the main case part and the refrigerator case part are integrally connected and fixed to the main case part, and the main case part and the refrigerator case part are formed by sealing the opening parts, In this state, the inner spaces are communicated with each other.

According to the present invention, there is provided a seedling grafting apparatus that includes a type-based gear-shifting mechanism and a tabletting work case unit that transmits power to a seedling-seeding apparatus or a seeding apparatus, and a main case unit that is equipped with a main- It is composed separately. Thereby, the main casing portion, which is the main portion of the transmission case, can be miniaturized, and various types of specifications of the type-based shifting mechanism to be combined can be selected, and it is advantageous in that it is easy to obtain a variety of specification- .

Further, the main case portion and the food waste working case portion are connected in such a state that the respective internal spaces are communicated with each other in a closed state in which the openings formed at the connection portions of the main body portion and the food waste working case portion are joined.

Therefore, although the case portions themselves are individually formed, they are configured as a closed case in which the inner space communicates with each other in a coupled state. Thereby, it is advantageous in that it is possible to avoid that the wall portions facing each other at the connection portions are double-structured, such that the weight is increased, or the shaft support structure or the sealing portions are unnecessarily required, .

In the present invention, there is provided a branch case portion for incorporating therein a branch transmission mechanism for branching the power output from the main case portion to the powder supply device, wherein the branch case portion is formed separately from the main case portion, And the main case part and the branch case part are connected and fixed to the main case part in a closed state in which the openings formed at the connection parts of the main case part and the branch case part are joined to each other, Is appropriate.

According to the present invention, the branch case portion for incorporating the branch transmission mechanism and for branching the power output from the main case portion to the powder supply device is used as the main case portion equipped with the main speed change mechanism and the auxiliary speed change mechanism for outputting power to the drive & It is composed separately from department. Thereby, the main casing portion, which is the main portion of the mission case, can be miniaturized, and various kinds of specifications of the combined branch transmission mechanisms can be selected, which makes it easy to obtain a variety of specifications.

The main case portion and the branch case portion are connected in a state in which the respective internal spaces are communicated with each other in a closed state in which the openings formed in the connection portions of the main case portion and the branch case portion are joined. Therefore, although the case portions themselves are individually formed, they are configured as a closed case in which the inner space communicates with each other in a coupled state. As a result, it is possible to avoid that the wall portions opposed to each other at the connection portions are double-structured, such as when fully individual cases are connected to each other, and the weight is increased, or the shaft supporting structure or the sealing portion is unnecessarily required.

In the present invention, it is preferable that the above-described type-based shifting mechanism includes a shift operating shaft extending between the internal space of the refrigerating operation case portion and the internal space of the main casing portion, It is preferable that a slide operation range associated with shifting operation of the shift gear is set over the inner space of the refrigerator case and the inner space of the main case portion.

With this configuration, the internal space of the main case portion can also be used as a slide operation range accompanying shift operation of the shift gear. As a result, it is possible to reduce the volume of the space to be set in the internal space of the refrigerator operation case portion in the slide operation range accompanying the shifting operation of the shift gear, and to miniaturize the refrigerator operation case portion.

In the present invention, the branch case portion includes: an input side cylindrical portion that is fitted to a traveling transmission shaft of a traveling driving system extending from the main case portion and that supports the traveling electric motor shaft; And an output side cylindrical portion that is fitted outside the extended branch drive shaft and supports the branch drive shaft, the input side cylindrical portion is connected to the main case portion, the output side cylindrical portion is integrally formed with the input side cylindrical portion, It is preferable that a branch output bevel gear is provided in the input side tubular portion near the main case portion.

By providing this configuration, the space of the input side cylindrical portion on the side farther from the main case portion than the branch drive shaft can be set smaller than that in the case where the branch output drive bevel gear is disposed farther from the main case portion than the branch drive shaft. The overall size of the branch case part can be reduced.

In the present invention, a bevel gear for branch input which is engaged with the bevel gear for branch output is supported by the branch drive shaft, the bevel gear for branch output is supported by the drive coaxial shaft, It is preferable that a positioning section for regulating the movement of the bevel gear for branching output to the side opposite to the side where the bevel gear for branch input exists is provided.

With this configuration, the branch case portion can be housed in the main case portion in a state in which the branch output bevel gear is supported by the driving transmission shaft, so that the assembling and disassembling operation of the branch case portion can be easily performed.

In the present invention, it is preferable that the opening of the branch case portion formed at the opposed portion to the main case portion has an inner diameter capable of inserting the branch output bevel gear supported by the traveling transmission shaft.

With this configuration, since the bevel gear for branching output can be carried from the opening of the branch case portion while being supported by the drive transmission shaft, the assembly and disassembly operation of the branch output case bevel gear and the drive transmission shaft is performed It will be 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 branch case portion is provided with an insertion limit position And it is preferable that the drive transmission shaft is supported at a position where it abuts on the input side end of the branch drive shaft.

With this configuration, it is easy to position the end position of the input side of the branch drive shaft relative to the branch case portion.

In the present invention, the auxiliary speed-change mechanism includes a pair of high-speed gears suitable for running on the road, over an upper shift shaft located on the upper side in the power transmission direction and a lower side shifted shaft located on the lower side in the power transmission direction And a shift member disposed between the pair of gears on the lower transmission shaft, wherein the shift member is positioned in the axial direction of the lower transmission shaft, And an engaging portion that is movably supported and protrudes in the direction in which the lower gear located at the lower side in the power transmission direction among the gear pairs is projected, Wherein each of the engaging recesses is engaged with the engaging teeth of the shift member, In the high-speed gear pair suitable for the running of the engagement recess of the lower gear portion in suitable if the shaft support hole and leading the image of the lower gear to be externally engaged in the lower speed shaft.

With 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 engaging concave portion can be positioned at a small diameter close to the shaft diameter of the lower transmission shaft, and the lower gear of 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 the high speed gear pair.

Further, by engaging with the shaft support hole of the lower gear, it is easy to make the shape of the engagement concave portion simple.

In the present invention, there is provided an axle case to which the driving force of the traveling driving system is transmitted. The axle case includes a pair of bevel gears on the upper side of the electric motor located on the upper side of the transmission shaft along the up- The pair of bevel gears located on the lower side of the electric motor and the pair of bevel gears are decelerated and the reduction ratio in the lower pair of bevel gears is set to be larger than the pair of bevel gears on the upper side of the electric motor.

With this configuration, both the upper and lower sides of the transmission shaft in the axle case are decelerated and the reduction ratio in the pair of bevel gears on the lower motor side is larger than that on the upper side of the electric motor, both on the upper and lower sides of the transmission shaft. As a result, the reduction ratio at the portion near the final output point on the lower side of the electric motor is made as large as possible, and the torque reduction on the upstream side can be effectively performed.

The transmission device of the present invention is characterized in that a type-of-gear-type transmission mechanism for shifting the engine power and transmitting the engine power to the seedling-implanting device or the seeding device is incorporated in the food- And a shifting operation body for selecting one of the pair of gears to transmit the power, wherein the pair of gears are arranged in a state of being normally engaged with the input-side transmission shaft of the transmission- Wherein the shift operating body includes a shift key portion that is capable of selectively engaging and disengaging any of the transmission gears constituting the pair of gears to be engaged with each other, The engagement margin of the portion is set such that, among the plurality of gear pairs, Is set to be larger as the gear pair with a shorter sowing pitch is selected.

According to the present invention, as a pair of gears in which a weekly pitch by a seedling planting apparatus or a seeding pitch by a seeding apparatus is set shorter is selected from among a plurality of gear pairs, the engagement margin of the transmission gear portion with respect to the transmission gear Is set to be larger.

That is, taking into account that a larger transmission torque is required for a gear pair in which a weekly pitch by a seedling plant or a sowing pitch by a seeding apparatus is set shorter, a gear pair of a portion where the week pitch or sowing pitch is shortened, The engaging engagement margin is larger than the engaging engagement margin of the gear pair and the shift key at the portion where the pitch pitch or sowing pitch is long. As a result, the engaging engagement margin of the gear pair and the shift key of each gear range is made to be a size corresponding to the transmission torque of each gear pair, and the engaging engagement margin of the gear pair in the region where the pitch pitch or sowing pitch is long By omitting the waste portion, it is possible to cure the resin as much as possible, and the overall structure can be made compact.

In the present invention, a plurality of sets of intervals in the axial direction of the input side transmission shaft or the output side transmission shaft are provided between the transmission gears disposed at positions adjacent to each other in the axial direction of the input side transmission shaft or the output side transmission shaft. And the distance between the collar is set so that the position of the gear pair in which the week pitch by the seedling plant or the sowing pitch by the seeding apparatus is set to be short is set to be smaller than the interval between the gears of the transmission gear portion It is preferable that the amount of engagement is set to be wide.

According to the present invention, it is possible to change the weekly pitch by the seedling planting apparatus or the seeding pitch by the seeding apparatus by using a collar for setting the interval between the electric gears and changing the interval between the colors.

By changing the width of the intervals between the colors, the amount of engagement of the shift key portions that enter between the colors with respect to the transmission gear in the gear pair also changes. Therefore, It is possible to obtain a structure capable of changing the engagement amount of the shift key portion with respect to the transmission gear.

In the present invention, the intervals between the electric gears in the axial direction of the input-side transmission shaft or the output-side transmission shaft are set to be shorter than the intervals between the electric gears existing in the places where the intervals between the collars are widened, It is preferable that the intervals between the electric gears at the positions where the intervals of the electric motors are narrowed are narrowed.

According to the present invention, a plurality of gear pairs are disposed along the axial direction of the input side transmission shaft or the output side transmission shaft. As for the interval between the teeth of the transmission gears constituting the gear pair at the positions adjacent to each other in the axial direction, the interval between the teeth of the transmission gears existing at the positions where the intervals between the collars are widened is smaller than the interval between the teeth of the transmission gears The distance between the teeth of the transmission gears existing in the places is narrowed.

As a result, it is possible to make the distance between the teeth of the transmission gears small in the portion where the transmission torque is small and the interval of the collars to be narrowed to further compact the type separating mechanism, Consists of.

In the present invention, the speed-change operating body is configured to slide the shift-key portion and the shift-key portion thereof in the axial direction of the input-side transmission shaft or the output-side transmission shaft to engage the engagement portion And a slide operation portion for selecting and operating the engagement position, wherein the shift key portion has a connection portion to the slide operation portion as a swinging point, and engages with the transmission gear, which crosses the slide operation direction by the slide operation portion It is suitable if it is constituted so as to be able to oscillate in the direction.

With this configuration, it is possible to provide a shift operating body that has a sliding operation portion for selecting an engagement position with respect to the transmission gear as a shifting operation body, and a transmission portion that is connected to the slide operation portion as a swinging point, By using the shift key configured to swing in the engaging direction with the gear, the engaging depth by the shift key can be appropriately set for each gear pair. The support portion of the slide operation portion in the transmission case equipped with this shift operating body may be provided with a sealing structure capable of coping with a simple slide operation that does not have to correspond to a complicated swing operation of the slide operation portion. Therefore, it is easy to adopt a relatively simple structure as the seal structure.

In the present invention, the speed change operating body is provided with a resilient pressing mechanism for pressing the transmission key portion against the transmission gear side of the engagement object, and the pressure compression point by the resilient pressing mechanism includes a plurality of gears Wherein the pair of gears is set at a position spaced apart from the swinging point with respect to the pair of gears and the pairing pitches set by the seedling implanting apparatus or the sowing apparatus by the seeding apparatus are set shorter than the pairing positions, It is suitable if it is located apart from near the pivot point side.

With this configuration, since there is provided the elastic pressing mechanism that presses the shift key portion against the transmission gear of the engagement object, the engaging depth of the shift key with respect to the pair of gears It can be adjusted automatically.

The pressing position of pressing with the elastic pressing mechanism is set at a position spaced apart from the pivot point of the plurality of gear pairs and the pitch of the sowing by the seeding apparatus or the sowing pitch by the sowing apparatus is set shorter, The pressing force by the elastic pressing mechanism acts more strongly as the gear pair in which the week pitch or the sowing pitch is set shorter by the action of the lever is located apart from the vicinity of the rocking point side from the pressing position by the elastic pressing mechanism.

Therefore, even when a large torque is applied to the engagement portion of the gear pair and the shift key, the possibility that the shift key is simply released from the engagement portion with the gear pair is reduced.

Fig. 1 is a left side view of the passive type reed unit.
2 is a diagram showing a power transmission system.
3 is a developed cross-sectional view of the main case portion in the mission case.
Fig. 4 is a vertical cross-sectional view of the case casing in the mission case. Fig.
5 is a cross-sectional view of the branch case portion in the horizontal direction in the mission case.
6 is a perspective view showing the connection state between the main casing portion and the branch casing portion.
7 is an explanatory view showing a meshing portion of the shift member and the lower gear in the negative speed change mechanism.
8 is a plan view showing a manipulation tool of the grabbing clutch.
Fig. 9 is an exploded perspective view showing the manipulation tool of the grabber clutch. Fig.
10 is a cross-sectional view of the axle case on the front wheel side in the vertical direction.
11 is a left side view of the passive type reed unit.
12 is a diagram showing a power transmission system.
13 is a developed sectional view of the main case portion in the mission case.
14 is an explanatory view showing a meshing portion of the shift member and the lower gear in the negative speed change mechanism.
15 is a perspective view showing the connection state of the main casing portion with the main casing portion and the branch casing portion.
16 is a cross-sectional view of the main casing in the vertical direction in the mission case.
17 is an enlarged cross-sectional view of the type-2 switching mechanism in the vertical case in the daytime case.
18 is a plan view showing an operating portion of the gear type shifting mechanism.
Fig. 19 is a plan view showing an operating tool of the grabbing clutch. Fig.
20 is an exploded perspective view showing an operating port of the transfer clutch.
21 is a sectional view in the horizontal direction of the branch case portion in the mission case.
22 is an explanatory view showing a pattern display section in the lever guide section for the inter-day shift.
23 is an explanatory diagram showing a pattern display section of the lever guide section according to another embodiment.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

The front-rear direction and the left-right direction in the description of this embodiment are described as follows unless otherwise specified. That is, the advancing direction (see the arrow F in Figs. 1 and 2) of the working machine (traveling body 1) such as the passenger-type reverberating machine to which the present invention is applied is "forward" (See arrows B in Figs. 1 and 2) is "after", and a direction (see arrow R in Figs. 2 and 3) corresponding to the right side with reference to the forward posture in the front- Right ", similarly, the direction corresponding to the left side (see the arrow L in Figs. 2 and 3) is " left ".

[Overall configuration]

Fig. 1 is an example of application of a transmission device of a working machine according to the present invention. Fig. 1 is a schematic diagram of a planting apparatus for planting seedlings on the ground or a working apparatus (planting apparatus) such as a direct- And the left side of the passenger type rearing machine as an example of one water receiving machine is shown.

This passenger-type reverberation machine is provided with a pair of left and right steering operations and a driveable front wheel 11F and a pair of right and left driveable rear wheels 11R as a travel drive device below the base frame 10, And a self-propelled traveling body 1 that is powered by an engine E mounted on the vehicle body 10 and on which the front wheel 11F and the rear wheel 11R are driven.

The traveling base 1 is provided with a driving unit 13 in which the engine E is incorporated in the front part of the vehicle on the operation floor 14. [ A seat having a steering handle 15 and a driver's seat 12 for steering the front wheel 11F on the driving floor 14 in the front and rear central portion of the traveling base 1 at the rear side of the driving portion 13 And an operation unit is provided.

On the rear side of the driver's seat 12, a fertilizer 9 (equivalent to a powder supply device) is mounted. The fertilizer unit 9 feeds the fertilizer stored in the fertilizer tank 90 by a predetermined amount from a feeder not shown and feeds the feeder 91 To be supplied to the package. A seedling transplanting apparatus 2 is supported on a rear side of the traveling base 1 via a link mechanism 25 having a hydraulic cylinder 26 for ascending and descending operation.

In the passenger-type rearing unit constructed as described above, seedling transplanting work such as rice is carried out on the packaging by the seedling transplanting apparatus 2.

On the front part of the traveling base 1, a reserve board 17 of a preliminary seedling is disposed on both left and right sides of the driving unit 13 with a distance in the left-right direction so as to be movable back and forth. A seedling transplanting apparatus 2 is supported on a rear portion of the traveling base 1 via a link mechanism 25 having a hydraulic cylinder 26 for ascending and descending operation so as to be able to ascend and descend.

In the passenger-type rearing unit constructed as described above, seedling transplanting work such as rice is carried out on the packaging by the seedling transplanting apparatus 2.

The implanted seedling implanted device 2 is of a four-bowl type and comprises a transmission case 21, a graft case 22 rotatably supported on the right and left lateral sides of the rear portion of the transmission case 21, A pair of grafting arms 23 (grappling claw driving mechanism), a ground float 24 provided at both ends of the case 22, and a kind of stacking table 20 on which seedlings are stacked. The transplanting case 22 is rotated and driven by the transplanting arm 23 to take out the seedlings alternately from the lower part of the loading table 20 It is configured to transplant on the field surface.

A front portion of the base frame 10 of the traveling base 1 is fixedly connected to a transmission case M which supports the front wheel 11F and a rear portion of the base frame 10, And an axle case 19 equipped with right and left front wheels 11R are supported. The front frame 10F extends forward from the transmission case M and the engine E is laterally mounted on the front frame 10F.

As shown in Figs. 2 and 3, on both right and left sides of the transmission case M, the axle case 16 extends to the left and right outer sides, and left and right front wheels 11F and 11F are provided.

The axle case 19 of the rear wheel 11R is elastically supported under the pair of left and right front and rear frames 10A and 10A so as to be vertically movable separately from each other via a suspension spring 18, Respectively.

[Power transmission system]

The power transmission structure in the transmission case M to which the power of the engine E is transmitted will be described.

The power of the engine E inputted to the mission case M is transmitted to the rear wheels 11R and 11R in the mission case M by a traveling driving system for driving the front wheels 11F and the rear wheels 11R, A working device driving system for driving a seeding device 2 or a seeding device (not shown), and a fertility drive system for driving the fertilizer device 9 are output.

The transmission case M includes a main case portion 3 in which the auxiliary transmission mechanism 3A of the traveling driving system and the like are housed and a main casing portion 4 disposed on the rear side of the main casing portion 3 (Corresponding to a refrigerator operation case portion) and a case portion 5 are provided.

The main casing section 4 includes a main transmission mechanism 4A for shifting the power output from the main casing section 3 to the seedling plant 2 and transmitting the power to the seedling plant 2, And the branch case portion 5 incorporates a branch transmission mechanism 5A for branching and transmitting the power output from the main case portion 3 to the fertilizer 9. [

The power of the engine E is transmitted to the pump shaft 60a of the hydrostatic stepless transmission 6 mounted on the outer wall of the main casing 3 in the transmission case M and the hydrostatic stepless speed change From the motor shaft 61a of the device 6 to the inside of the case body 30 in the main case portion 3. [ That is, the hydrostatic stepless transmission 6 is used as an endless main transmission, and the power output from the main transmission is further shifted in the transmission case M.

[Driving driving system]

First, the transmission structure of the travel driving system will be described.

2, the power of the engine E is transmitted to the pump shaft 60a, which is the transmission input shaft of the hydrostatic stepless speed changer 6, via the belt transmission mechanism 62 and is transmitted to the hydraulic pump 60, Is rotationally driven.

The motor shaft 61a serving as the speed change output shaft of the hydrostatic stepless speed change unit 6 is connected to the first speed change shaft 31 (corresponding to the upshift shaft) in the case body 30 of the main case portion 3 And the first speed change shaft 31 is rotationally driven as the motor 61 rotates.

3, the first speed-change shaft 31 is provided with an upper low-speed gear 31a and an upper high-speed gear 31b of the traveling driving system that are integrally rotatable, And the output gear 31c are integrally rotated.

An end portion of the first speed change shaft 31 on the opposite side to the side connected to the motor shaft 61a is connected to a shaft portion (not shown) protruding outside the case body 30 through the side wall 30b of the case body 30 Boss portion 33b of the extension shaft 33 provided with the guide portion 33a. The extension shaft 33 is provided with an implantation transmission gear 33c on the outer circumferential portion of the delivery boss portion 33b and has a shaft portion 33a projecting outwardly of the case body 30 through the side wall 30b, And an external gear 36a is rotatably supported.

The output gear 31c for decelerating transmission and the transfer gear 33c are engaged with a relay gear 32f which is rotatably and loosely fitted to the second speed change shaft 32 to be described later.

And a second speed change shaft 32 (corresponding to the lower speed change shaft) having an axis parallel to the first speed change shaft 31 is supported by the case body 30. A lower side low speed gear 32a (corresponding to a lower gear) meshing with the upper side low speed gear 31a and a lower side high speed gear 32b (corresponding to a lower side gear) (Corresponding to the lower gear) is pivotally supported on the second speed change shaft 32 so as to be relatively rotatable.

A pair of gears of the upper side low speed gear 31a and the lower side low speed gear 32a and a pair of the gears of the upper side high speed gear 31b and the lower side high speed gear 32b and a pair of gears of the second speed change shaft 32 And a shift member 34 that is pivotally supported by the shift member 34. The sub-

The combination of the upper side low speed gear 31a and the lower side low speed gear 32a is a pair of gears for low speed suitable for work traveling and the combination of the upper side high speed gear 31b and the lower side high speed gear 32b Is a high-speed gear pair suitable for a vehicle.

The shift member 34 is spline-fitted to the second speed change shaft 32 and is supported so as to be able to rotate integrally with the second speed change shaft 32 and to be slidable in the axial direction of the second speed change shaft 32 have. The lower side low speed gear 32a and the lower side high speed gear 32b located on the lower side in the power transmission direction are present on both right and left side surfaces of the shift member 34 opposed to the respective gear pairs on the left and right sides And engaging teeth 34a and 34b protruding toward both right and left directions are provided.

The lower side low speed gear 32a and the lower side high speed gear 32b at positions opposite to the shift member 34 are respectively engaged with the engagement teeth 34a and 34b of the shift member 34 The engaging concave portions 32c and 32d are formed.

The engagement teeth 34a on the side of the engagement teeth 34a and 34b of the shift member 34 opposed to the low speed low speed gear 32a having a large diameter are arranged in the vicinity of the outer peripheral edge of the shift member 34, Is formed at a position spaced apart from the outer peripheral surface of the shaft (32). The engagement teeth 34b on the side opposite to the lower high-speed gear 32b having a smaller diameter on the opposite side are formed in the vicinity of the inner peripheral edge of the shift member 34 at a position close to the outer peripheral surface of the second transmission shaft 32 .

The engaging concave portion 32c formed in the lower side low gear 32a of the engaging concave portions 32c and 32d can be engaged with the engaging teeth 34a on the side of the shift member 34, And is formed at a position spaced apart from the outer circumferential surface of the second speed change shaft (32). The meshing concave portion 32d formed in the lower high gear 32b is formed into a shape capable of engaging with the engaging teeth 34b on the side of the shift member 34 at a position facing the meshing concave portion 32d. As shown in Fig.

As shown in Fig. 7, the engaging concave portion 32d formed in the lower high gear 32b is formed by a shaft supporting hole 32e of the lower high gear 32b that is fitted to the second speed change shaft 32 And is formed in a communicated shape. Thus, the engaging concave portion 32d formed in the lower high gear 32b is formed so as to be as close to the outer peripheral surface of the second speed change shaft 32 as possible.

The shift member 34 includes an operation plate 34c that supports the shift member 34 while holding the shift member 34 and an operation rod 34d that is integrally fixed to the operation plate 34c, 30 from the outside.

The position where the operating rod 34d is pressed into the case body 30 most is the position where the shift member 34 selects the pair of gears for low speed suitable for the traveling of the work, Is a position selected by the shift member 34 for a high-speed gear pair suitable for running on the road. The neutral position is a state in which the shift member 34 is in an intermediate position in which no gear pair is selected.

The power transmitted to the second speed change shaft 32 through the shift member 34 is transmitted to the front wheel output gear 35b via the interlock gear 35a fixed to the second speed change shaft 32. [ The front wheel output gear 35b is splined to the outer peripheral portion of the right end side of the cylindrical member 35c fitted externally so as to be rotatable relative to the front wheel drive shaft 63. [ The left end side of the cylinder member 35c is integrally rotatably connected to the differential gear case 70 via the boss portion of the rear wheel output bevel gear 35d which is 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 cylinder member 35c. As a result, as the differential gear case 70 rotates, the left and right front wheel drive shafts 63 are rotationally driven. As the rear wheel output bevel gear 35d rotates, the rear wheel input bevel gear 64a And the rear wheel output shaft 64 (corresponding to the drive transmission shaft) are rotationally driven.

At the right end of the boss portion of the front wheel output gear 35b, a claw portion 71a for locking the differential gear is provided. A sliding claw portion 71b for a differential gear lock engageable with and detachable from the claw portion 71a for locking the differential gear is formed on the left end of the sliding barrel 71 which is fitted to the front wheel drive shaft 63 have. The sliding claw portion 71b for the differential gear lock is engaged and disengaged by the turning operation of the differential gear lock operation pin 72 provided through the case body 30. [ That is, the sliding barrel 71 is moved along the axial direction of the front wheel drive shaft 63 by the rotation operation of the differential gear lock operation pin 72, and the differential gear lock claw portions 71a ).

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

[Work machine driving system]

Apart from the above-described travel driving system, a working device driving system for transmitting the power to the seedling-implanting device 2 of the working type working device will be described.

The power to the seedling plant 2 is transmitted to the seedling plant 2 through the intermittent transmission mechanism 4A and the graft clutch 8 (corresponding to the work clutch) in the main body portion 4 provided in the rear portion of the main casing portion 3 And is taken out from the output transmission shaft 42 extending from the main casing 4 to the rear side and is transmitted to the rear seedling plant 2.

As shown in Figs. 4 and 6, the inter-day case section 4 includes a daytime case body 40 that is formed separately from the case body 30 of the main case section 3. As shown in Fig. The main body case 40 is integrally connected and fixed to the main case part 3 via a connecting bolt or the like (not shown). The main casing unit 4 and the main casing unit 3 are connected to each other in a state in which the openings 40a and 30a formed at the connection points of the main casing unit 3 and the main casing unit 3 are connected to each other, .

The power transmission from the main casing 3 to the main casing 4 is carried out by a combination of the working system transmission coaxial 37 provided on the left and right side walls 30b and 30b of the case main body 30, A bevel gear 37a fixed to the bevel gear 37 and an output bevel gear 38 meshing with the bevel gear 37a.

The working outer rotor 36 is provided on the shaft portion of the work transmission coaxial shaft 37 projecting outwardly of the case body 30 from the case body 30 of the extension shaft 33, Is engaged with the first external gear (36a) provided on a shaft portion projecting to the outside of the first shaft (30), whereby power transmission is performed.

4, a long working drive shaft 41 (corresponding to the speed change operation shaft) extending in the front-rear direction is disposed on the front and rear sides of the case portion 4 in the main body portion 4.

The working drive shaft 41 has an output transmission shaft 42 to which the transmission shaft 27 to the rear seedling plant 2 is connected and a power transmission shaft 42 which is connected to the front end side portion of the output transmission shaft 42, And a front secondary shaft member 43 (corresponding to a normal shaft member) in which the upper side power is transmitted in the motor-driven direction.

The front auxiliary shaft member 43 on the upper side of the electric motor is positioned such that its front end portion is intruded into the case body 30 of the main case unit 3. [ A spline portion is formed at a portion located on the uppermost position in the forward direction of the front portion of the front auxiliary shaft member 43. The spline portion of the output bevel gear 38 located in the main case portion 3 has a spline portion Respectively.

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, (43) are also supported.

The ball bearing 38a provided on the side of the case body 30 is provided with a portion of the front auxiliary shaft member 43 which is slightly larger in diameter than the portion inserted into the output bevel gear 38, . Further, on the rear end side of the inner race of the ball bearing 38a, the larger-diameter portion of the front secondary shaft member 43 abuts against the front side, and position regulation to the front side is performed.

The front auxiliary shaft member 43 is formed with a small diameter hole 43b communicating with the inner space of the main case unit 3 on the front side of the large diameter hole 43a into which the output transmission shaft 42 is inserted The small-diameter hole 43b and the large-diameter hole 43a of the front secondary shaft member 43 are connected to the inner peripheral side of the main casing 3 and the inner casing of the main casing 4, It is a passage.

An intermediate cylindrical member 44 (corresponding to a normal shaft member) and a rear cylindrical member 45 (corresponding to a normal shaft member) are formed in the outer peripheral portion of the output transmission shaft 42 at the rear side of the position where the front auxiliary shaft member 43 exists. ) Is externally fitted so as to be relatively rotatable.

A torque limiter 46 is provided between the rear end of the intermediate cylindrical member 44 and the front end of the rear cylindrical member 45.

A clutch 8 is provided between the rear end of the rear cylinder body 45 and the output transmission shaft body 42 on the rear side of the rear cylinder body 45. [

The intermediate transmission body 44 and the rear transmission body 45 exist in the outer peripheral portion of the output transmission transmission body 42 so as to be rotatable relative to each other, And is in the inner circumferential side passage of the shaft body 43, it is easy to perform the lubrication in the daytime casing portion 4 satisfactorily.

That is, the lubricating oil existing in the inner space of the main case 3 flows through the inner circumference side of the transmission boss gear 38 and flows into the front auxiliary shaft member (as shown by the broken- 43 and the intermediate cylindrical member 44 and between the intermediate cylindrical member 44 and the rear cylindrical member 45 and between the rear cylindrical member 45 and the output transmission shaft member 42 on the rear side, It is possible to lubricate satisfactorily while using the centrifugal force accompanying the rotation of the member rotating on the drive shaft 41. [

The front auxiliary shaft member 43 has a splined portion 43c formed at the outer peripheral portion thereof and a shift gear 47 fitted to the splined portion 43c is integrally rotatably and slidably mounted.

The shift gear 47 is provided with a first tooth portion 47a and a second tooth portion 47b having an approximate diameter that is slightly different in the number of teeth and one of the teeth portions 47a and 47b is alternatively provided with a driven gear 47c So as to be able to be moved in the axial direction of the front auxiliary shaft member 43. [

As shown in Fig. 4, the shift range of the shift gear 47 is a state in which both the first tooth portion 47a and the second tooth portion 47b are located in the main casing portion 4, So that the front portion or a part of the front portion 47a of the main casing portion 3 can be shifted to a state of being displaced from the main casing portion 4 and located in the inner space of the main casing portion 3 The range is set.

In the case casing 4, there is provided a speed change shaft 48 which is disposed in parallel with the working drive shaft 41. And the follower side gear 47c is integrally rotatably mounted on the transmission shaft 48. [

The transmission shaft 48 is provided with a plurality of (three in the figure) transmission gears 44a fixed to the intermediate cylindrical member 44 on the output transmission shaft 42 side and a plurality of Each of the speed change gears 48a is loosely fitted. The shifting gears 48a and 48a which are always in the engaged state and the shifting rod 48b which is slidably operated in the transmission shaft 48 and the positioning mechanism 48c which uses the detent mechanism always engage So that the combination of the shift gears 44a and 48a in the state of being in the engaged state can be alternatively selected.

The first shift portion 4B that uses the shift gear 47 and the driven gear 47c and the second shift portion 46 that selectively allows the combination of the shift gears 44a and 48a, The section 4C constitutes a weekly transmission mechanism 4A.

The inter-day shift operating member 100 in the inter-day transmission mechanism 4A is configured as shown in Figs. 4 and 6. Fig.

That is, the lower end of the operating shaft 101 passing through the upper wall portion of the case portion 4 is fixed to the lower end of the main shaft portion 4 by the engagement pin 102 which is fitted between the first and second teeth portions 47a and 47b And a plate-like operating body 103 is provided at the upper end of the operating shaft 101 located outside the upper wall portion.

The engaging pin 102 existing at the eccentric position shifts the shift gear 47 in the axial direction of the work drive shaft 41 by manipulating the plate operating body 103 to rotate around the axis of the operation shaft 101 . The position of the plate-like operating body 103 around the axis is positioned by the ball detent mechanism 104.

The torque limiter 46 includes a support plate 46a fixed to the rear end of the intermediate cylindrical member 44, a presser plate 46b which abuts against the support plate 46a, and a presser plate 46b toward the support plate 46a And a coil spring 46c for pressurizing and pressing.

The transfer clutch 8 is constructed as follows.

A driving-side rotary member 80 (hereinafter, referred to as " driving-side rotary member ") of the working drive shaft 41, which engages with the outer peripheral side spline of the rear normal body 45 to integrally rotate with the rear normal body 45, ).

The power transmission shaft 42 is engaged with a spline portion 42a formed on the outer circumferential surface of the output transmission shaft 42 so as to engage with the output transmission shaft 42 And a driven side rotary member 81 movable in position in the axial direction of the output electric drive shaft member 42 are provided.

The driven side rotational member 81 is urged toward the drive side rotational member 80 by the urging spring 82 and is urged toward the driven side rotational member 80 and the driven side rotational member 81, Engagement portions 80a and 81a capable of transmitting power in the engaged state are formed on the opposite surfaces.

The urging spring 82 has a spring receiving portion 81b formed on the side opposite to the side where the engaging portion 81a of the driven side rotary member 81 is formed and a spring receiving portion 81b formed on the inner side of the main casing portion 4 And is disposed between the fixing portions. The inner end of the inner race 49a of the ball bearing 49 for supporting the output transmission shaft 42 is used as the fixing portion on the inner surface side of the case portion 4, There is no.

The shape of the urging spring 82 is such that the winding diameter at the end on the side where the urging spring 82 abuts against the spring receiving portion 81b in the axial direction of the working drive shaft 41 is smaller than the winding diameter of the inner race 49a And is formed into a conical shape larger than the winding diameter.

The winding diameter of the compression spring 82 on the side contacting the inner end of the inner race 49a is about the same as or slightly larger than the outer diameter of the output transmission shaft 42 fitted to the outside. Therefore, the inner end of the inner race 49a of the ball bearing 49 for supporting the output transmission shaft 42 can be used to position the end portion thereof, without requiring any positioning means.

4, the driven-side rotational member 81 is spaced apart from the drive-side rotational member 80 against the urging force of the urging spring 82 by a clutch operating member 83 abutting on the outer peripheral portion And the engaging portion 81c is engaged with the outer periphery of the clutch operating member 83. As shown in Fig.

The clutch operating member 83 is provided with an operating pin 84 passing through the upper wall portion of the main casing portion 4 and is engaged with the lower end portion of the operating pin 84, And an operating portion 84a for moving the driven-side rotating member 81 in the axial direction of the output transmission shaft 42 is formed in association with the rotation of the operating pin 84. [

The clutch operating member 83 is a member for operating the portion of the operating pin 84 exposed outside the main casing portion 4 out of the operating pin 84 operated around the rotating axis p1 in the direction crossing the axis of the working drive shaft 41 An operation plate 85 is provided at the shaft end of the pin 84 to rotate the operation pin 84. [ An operation guide member 86 for guiding a pivoting operation of the operation plate 85 around the rotation axis p1 while supporting a part of the operation plate 85 from above and below is provided, (4).

The operating pin 84 is regulated by the operating plate 85 to move the position in the direction along the rotating axis p1 and the operating range around the rotating axis p1 is controlled by the operating plate 85 And is regulated by the abutment of the operation guide member 86.

The position of the spring receiving portion 81b of the driven side rotational member 81 is set such that the position of the engaging portion 81c of the driven side rotational member 81 at the lower end portion of the operating pin 84 Of the driven side rotational member 81 and the engaging portion 81c of the driven side rotational member 81 in the axial direction of the working drive shaft 41 and the inward side in the radial direction of the driven side rotational member 81, (81a) is formed.

The spring receiving portion 81b is located on the inner side in the radial direction from the engaging portion of the engaging portion 81c of the operating pin 84 and the driven side rotary member 81, Is concave so as to be close to the side on which it is present. This prevents the axial length of the work drive shaft 41 of the urging spring 82 from being restricted by the position of the operation pin 84 in the axial direction of the work drive shaft 41, 4 can be made compact.

[Fertility drive system]

A driving system for driving a driving force for diverting the driving force to the driving device 9 from the traveling driving system described above is constituted as follows.

6, the branch case portion 5, which is formed separately from the main case portion 3, is connected and fixed to the rear side of the main case portion 3 via a mounting bolt or the like (not shown) have.

The main case portion 3 and the branch case portion 5 are communicated with each other in the closed state in which the openings 30a and 50a formed at the connection portions of the main case portion 3 and the branch case portion 5 are bonded to each other.

5, the branched case portion 5 includes an input side cylindrical portion 50A that supports the rear wheel output shaft 64 extending rearward from the main case portion 3, And an output side cylindrical portion 50B that is fitted to the branch transmission shaft 51 extending in the direction of the axis and supports the branch transmission shaft 51. [ The input side cylindrical portion 50A and the output side cylindrical portion 50B are formed of an integral body having a common internal space.

The bevel gear 52 for transmitting the power from the rear wheel output shaft 64 to the branch transmission shaft 51 is provided in the input side cylindrical portion 50A and is connected to a bevel gear 53 (corresponding to the bevel gear for branch input) are provided in the output side trading portion 50B.

The bevel gear 52 for branching output is provided in the input side cylindrical portion 50A closer to the main case portion 3 than the branch transmission shaft 51. [

A rear wheel output shaft 64 provided at the front end of the rear wheel input bevel gear 64a meshing with the rear wheel output bevel gear 35d is connected to the rear wheel output shaft 64 via a ball And the rear end portion is supported by a ball bearing 54 provided near the rear end portion of the branch case portion 5. As shown in Fig.

The rear wheel output shaft 64 is provided with a stepped portion 64C (corresponding to the positioning portion) at a midway position in the axial direction thereof. The front portion of the rear wheel output shaft 64, which corresponds to the upper side in the motor- Diameter shaft portion 64A and the rear side corresponding to the lower side in the rolling direction than the stepped portion 64C is formed by the 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. A spline portion 64D is formed at a portion near the step portion 64C of the small diameter shaft portion 64B And the branch output bevel gear 52 is splined to the spline portion 64D.

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

Therefore, when the rear wheel output shaft 64 is housed in the branch case portion 5, it can be housed in the branch case portion 5 in a state in which the branch output bevel gear 52 is previously supported on the rear wheel output shaft 64 , It is possible to facilitate the assembly and disassembly.

The branching transmission shaft 51 equipped at the input side end with the application bevel gear 53 engaged with the branch output bevel gear 52 supported by the rear wheel output shaft 64 is disposed in a posture orthogonal to the rear wheel output shaft 64 Respectively. The input side end portion can be inserted and extracted from the output side opening portion 50b formed in the output side cylindrical portion 50B of the branch case portion 5. The output side end portion is configured to extend outward from the output side opening portion 50b of the output side normal portion 50B And is supported in a protruded state.

An interlocking shaft (not shown) to the threading device 9 is connected to the projecting portion of the branching transmission shaft 51 protruding outward from the output side opening 50b.

The branch transmission shaft 51 is a portion corresponding to the insertion limit position to the output side normal section 50B and the end of the input side abuts against the rear wheel output shaft 64. [ That is, when the branch transmission shaft 51 is inserted into the output side cylindrical portion 50B until reaching the insertion limit position from the output side opening 50b, the input side cylindrical portion 50A of the rear output shaft 64. In this case,

The exciting bevel gear 53 is supported so as to be rotatable relative to the branching transmission shaft 51. The branching transmission shaft 51 and the application bevel gear 53 are rotatably supported by a friction clutch 55 (Not shown).

The friction clutch 55 is provided with a normal shift member 56 splined to a spline portion formed on the outer peripheral surface of the branch transmission shaft 51. [ A pawl portion 56a formed on the opposing surface of the normal shift member 56 with respect to the application bevel gear 53 and a hook portion 56b formed on the side of the application bevel gear 53 facing the normal shift member 56 The engaging concave portion 53a is engaged and detached so that the rotation of the application bevel gear 53 can be switched to the branch transmission shaft 51 and the transmission can be switched off.

The shift member 56 is normally urged by the coil spring 57 toward the application bevel gear 53 so that the normally shift member 56 is displaced from the application bevel gear 53 The clutch operating shaft 58 is provided so as to penetrate through the output side sun gear 50B.

[Axle case]

10, a transmission shaft 65 along the vertical direction is provided on the axle case 16 to which the driving force is transmitted from the front wheel drive shaft 63, and the transmission shaft 65 is disposed on the upper side of the transmission shaft 65 An upper bevel gear pair 66 on the upper side of the electric motor and a lower pair of bevel gears 67 on the lower electric side positioned on the lower side of the transmission shaft 65 are provided.

Each of these bevel gear pairs 66 and 67 is deceleratedly driven. The reduction ratio of the lower bevel gear pair 67 on the lower side of the electric motor is set to be larger than that of the upper bevel gear pair 66 on the electric upper side.

Although not shown, the axle case 19 that transmits the driving force to the rear wheel 11R is also provided with a transmission shaft 65 which is obliquely rearwardly downwardly directed from the upper side. The upper and lower sides of the transmission shaft 65 also have the same structure as that of the upper bevel gear pair 66 and the lower bevel gear pair 67 on the side of the front wheel 11F, A large configuration is adopted.

[Other Embodiment 1]

In the above-described embodiment, the case portion 4 is shown as the working case portion, but the present invention is not limited thereto. For example, when the working machine is used in a planter equipped with a direct-wave device, the working case part becomes a working case part for changing the interval of wave intervals by the direct-wave device.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 2]

In the above embodiment, the fertilizer device 9 is used as the powder-supplying device, but the invention is not limited thereto.

For example, it may be possible to supply medicines such as herbicides and insect repellents.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 3]

In the above embodiment, the technique applied to the clutch clutch 8 as the work clutch is shown, but the present invention is not limited thereto. For example, although not shown, the friction clutch 55 may have the same structure as that of the clutch clutch 8 as the above-described work clutch.

Other configurations may be the same as those of the above-described embodiment.

[Other Embodiment 4]

In the above-described embodiment, a structure having three front shafts 43, an intermediate cylindrical member 44, and a rear cylindrical member 45 is illustrated as a typical shaft member, but the present invention is not limited to this structure.

For example, it may be a structure using only a front auxiliary shaft member 43 as a shaft member, or a structure using a combination of more normal members.

Other configurations may be the same as those of the above-described embodiment.

[Other Embodiment 5]

In the above-described embodiment, the rice hatchery having the daytime housing part 4 as the refrigerator working case part is shown, but the present invention is not limited thereto. For example, when used in a planter equipped with a direct wave device, the tabletop operation case portion is a work case portion for changing the interval of wavefront caused by the direct wave device.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 6]

In the above embodiment, the fertilizer device 9 is used as the powder-supplying device, but the invention is not limited thereto.

For example, it may be possible to supply medicines such as herbicides and insect repellents.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 7]

In the above embodiment, the refrigerator has a structure in which both the refrigerator case and the branch case are provided and the refrigerator can be detached from the opening 40a or 50a. However, only the refrigerator case may be detached from the opening 40a It may be done.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 8]

The engagement recess portions 32c and 32d of the lower high gear 32b in the high speed gear pair suitable for running on the road in the negative side shifting mechanism 3A are engaged with the shaft support holes 32e The following shape is exemplified, but this shape is not necessarily required.

For example, although the shaft supporting hole 32e is a perfect round hole and the engaging concave portions 32c and 32d are close to the shaft supporting hole 32e, an independent recessed portion shape other than the shaft supporting hole 32e .

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 9]

Hereinafter, another embodiment of the present invention will be described with reference to the drawings.

[Overall configuration]

Fig. 11 is a schematic view showing an example of a water-receiving working machine having a working machine such as a planting machine for planting seedlings on a ground surface or a direct wave machine for spraying rice seed on the ground. .

This passenger-type reverberation machine is provided with a pair of left and right steering operations and a driveable front wheel 1011F and a pair of right and left driveable rear wheels 1011R below the base frame 1010, And a self-propelled traveling body 1001 that is powered by an engine E100 mounted on the engine 1010 and in which the front wheel 1011F and the rear wheel 1011R are driven.

The traveling base 1001 is provided with a driving unit 1013 in which the engine E100 is incorporated in the front portion of the vehicle on the operation floor 1014. A driver's seat 1012 and a steering handle 1015 for steering the front wheel 1011F on the driving floor 1014 in the front-rear direction central portion of the traveling body 1001 at the rear side of the driving portion 1013, .

On the rear side of the driver's seat 1012, a fertilizer 1009 (equivalent to a powder supply device) is mounted. The fertilizer apparatus 1009 feeds the fertilizer stored in the fertilizer tank 1090 by a predetermined amount from a feeding apparatus not shown and feeds the fertilizer to the seeder 1091 equipped to the seedling transplanting apparatus 1002 through a feeding route not shown, To be supplied to the package. A seedling implanter 1002 is supported on a rear side of the traveling base 1001 via a link mechanism 1025 having a hydraulic cylinder 1026 for lifting and lowering operation.

In the passenger-type rearing unit constructed as described above, the seedling transplanting apparatus 1002 performs the seedling transplanting operation of seedling such as rice.

On the front portion of the traveling base 1001, the reserve seedling bearing rack 1017 is disposed on both left and right sides of the driving portion 1013 at a distance in the left-right direction so as to be movable back and forth. A seedling transplanting apparatus 1002 is supported on a rear portion of the traveling base 1001 via a link mechanism 1025 having a hydraulic cylinder 1026 for an elevating operation so as to be able to move up and down.

In the passenger-type rearing unit constructed as described above, the seedling transplanting apparatus 1002 performs the seedling transplanting operation of seedling such as rice.

The seedling-plant transplanting apparatus 1002 is constituted by a four-bowl type, and includes a transmission case 1021, a graft case 1022 rotatably supported on the right and left lateral sides of the rear portion of the transmission case 1021, A pair of grafting arms 1023 (a grafting claw driving mechanism), a ground float 1024, and a seedling rack 1020 on which seedlings are placed, both provided at both ends of the case 1022. [ The transplanting case 1022 is driven to rotate and the transplanting arm 1023 is taken out from the lower part of the seedling rack 1020 in turn to take out the seedlings, It is configured to be implanted on the floor.

A front portion of the base frame 1010 of the traveling base 1001 is fixedly connected to a transmission case M100 which supports the front wheel 1011F and a rear portion of the base frame 1010 And an axle case 1019 equipped with left and right front wheels 1011R. The front frame 1010F extends forward from the transmission case M100 and the engine E100 is mounted transversely to the front frame 1010F.

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

The axle case 1019 of the rear wheel 1011R is elastically supported under the pair of left and right front and rear frames 1010A and 1010A so as to be vertically movable separately via suspension springs 1018, Is installed.

[Power transmission system]

The power transmission structure in the transmission case M100 to which the power of the engine E100 is transmitted will be described.

The power of the engine E100 inputted to the transmission case M100 is transmitted to the front wheels 1011F and 1011R in the transmission case M100 through a driving driving system for driving the front wheels 1011F and the rear wheels 1011R, A working apparatus driving system for driving the seeding apparatus 1002 or a seeding apparatus (not shown), and a fertility driving system for driving the fertilizing apparatus 1009. [

The transmission case M100 includes a main case portion 1003 incorporating the auxiliary transmission mechanism 1003A of the traveling driving system and a main casing portion 1004 disposed on the rear side of the main casing portion 1003 (Corresponding to the case portion) and a branched case portion 1005.

The weekly case unit 1004 includes a weekly transmission mechanism 1007 (equivalent to a type shifting mechanism) that shifts the power output from the main case unit 1003 to the seedling implanter 1002, The unit 1005 includes a branch transmission mechanism 1005A that branches the power output from the main case unit 1003 to the propulsion system 1009. [

The power of the engine E100 is transmitted to the pump shaft 1060a of the hydrostatic stepless transmission unit 1006 mounted on the outer wall of the main casing unit 1003 in the transmission case M100, Is input from the motor shaft 1061a of the apparatus 1006 to the inside of the case body 1030 in the main case portion 1003. [ That is, the hydrostatic stepless speed changer 1006 is used as an endless main speed changing device, and the power output from the main speed changing device is further shifted in the transmission case M100.

[Travel driving system]

First, the transmission structure of the travel driving system will be described.

12, the power of the engine E100 is transmitted to the pump shaft 1060a, which is the transmission input shaft of the hydrostatic stepless speed changer 1006, via the belt transmission mechanism 1062 and is connected to the hydraulic pump 1060, Is rotationally driven.

The motor shaft 1061a serving as the shift output shaft of the hydrostatic stepless speed change unit 1006 is connected to the first speed change shaft 1031 (corresponding to the upper shift shaft) in the case body 1030 of the main case portion 1003 , And the first shift shaft 1031 is rotationally driven in accordance with the rotation of the motor 1061. As shown in Fig.

As shown in Fig. 13, the first speed change shaft 1031 is provided with an upper low gear 1031a and an upper high gear 1031b of the traveling drive system to be rotated integrally with each other. Further, And the gear 1031c are integrally rotated.

An end portion of the first transmission shaft 1031 opposite to the side connected to the motor shaft 1061a is provided with a shaft portion 1033a which protrudes outside the case body 1030 through the side wall 1030b of the case body 1030 Is inserted into the barrel boss portion 1033b of the extension shaft 1033 provided with the pivot portion 1033 and is pivotally supported so as to be relatively rotatable. The extension shaft 1033 is provided with an implantation transmission gear 1033c on the outer periphery of the communication boss portion 1033b and has a shaft portion 1033a projecting outwardly of the case body 1030 through the side wall 1030b, And an external gear 1036a is rotatably supported.

The output gear 1031c for decelerating transmission and the transfer gear 1033c are engaged with a relay gear 1032f which is rotatably and loosely fitted to the second speed change shaft 1032 to be described later.

A second transmission shift shaft 1032 (corresponding to a lower shift shaft) having an axis parallel to the first transmission shaft 1031 is supported on the case body 1030. A lower side low speed gear 1032a (corresponding to the lower gear) meshed with the upper side low speed gear 1031a and a lower side high speed gear 1032b (corresponding to the lower side gear) are engaged with the second speed change shaft 1032 (Corresponding to the lower gear) is pivotally supported on the second transmission shaft 1032 so as to be relatively rotatable.

The gear pair of the upper low gear 1031a and the lower low gear 1032a and the gear pair of the upper high gear 1031b and the lower high gear 1032b and the second shift shaft 1032 between these gear pairs, And a shift member 1034 that is pivotally supported on the shift member 1034A.

The combination of the upper and lower low gears 1031a and 1032a is a pair of low speed gears suitable for work traveling and a combination of the upper gear 1031b and the lower high gear 1032b It is a suitable high-speed gear pair.

The shift member 1034 is splined to the second transmission shaft 1032 and supported so as to be able to rotate integrally with the second transmission shaft 1032 and to be slidable in the axial direction of the second transmission shaft 1032 . On both right and left side surfaces of the shift member 1034 opposed to the respective gear pairs on the left and right sides, the lower side low speed gear 1032a and the lower side high speed gear 1032b, which are located on the lower side in the power transmission direction, And engaging teeth 1034a and 1034b protruding toward both directions are provided.

Each of the lower side low speed gear 1032a and the lower side high speed gear 1032b at positions opposed to the shift member 1034 is engaged with the engaging teeth 1034a and 1034b of the shift member 1034 The engaging concave portions 1032c and 1032d are formed.

The engagement teeth 1034a on the side of the engagement teeth 1034a and 1034b of the shift member 1034 which face the lower speed lower gear 1032a having a larger diameter are arranged in the vicinity of the outer peripheral edge of the shift member 1034, Is formed at a position spaced apart from the outer peripheral surface of the base 1032. The engagement tooth 1034b on the side opposite to the lower high gear 1032b having a smaller diameter on the opposite side is formed at a position close to the outer peripheral surface of the second shift shaft 1032 near the inner peripheral edge of the shift member 1034 .

The engaging concave portion 1032c formed in the lower side lower gear 1032a of the engaging concave portions 1032c and 1032d has a shape capable of engaging with the engaging teeth 1034a on the side of the shift member 1034 And is formed at a position spaced apart from the outer peripheral surface of the second transmission shaft 1032. The engaging concave portion 1032d formed in the lower side high gear 1032b has a shape that allows engagement with the engaging teeth 1034b on the side of the shift member 1034 at a position facing the engaging concave portion 1032d. As shown in Fig.

As shown in Fig. 14, the engaging concave portion 1032d formed in the lower high gear 1032b has a shaft supporting hole 1032e of the lower high gear 1032b that is fitted to the second speed change shaft 1032, And is formed in a communicated shape. Thus, the engagement concave portion 1032d formed in the lower high gear 1032b is formed so as to approach the outer peripheral surface of the second transmission shaft 1032 to the limit.

The shift member 1034 is fixed to the case body 1030 using the operation plate 1034c that supports the shift member 1034 while holding the shift member 1034 and an operation rod 1034d that is fixed integrally with the operation plate 1034c. As shown in Fig.

The position at which the operation rod 1034d is pressed into the case body 1030 most is the position selected by the shift member 1034 for the low speed gear pair suitable for the work travel and the operation rod 1034d is located at the position closest to the case body 1030, Is a position selected by the shift member 1034 for a high-speed gear pair suitable for running on the road. The state in which the shift member 1034 is present at an intermediate position in which no gear pair is selected is the neutral position.

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

Therefore, 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 cylinder member 1035c. As the differential gear case 1066 rotates, the left and right front wheel drive shafts 1063 are rotationally driven. As the rear wheel output bevel gear 1035d rotates, the rear wheel input bevel gear 1064a And the rear wheel output shaft 1064 (corresponding to the drive transmission shaft) are rotationally driven.

At the right end of the boss portion of the front wheel output gear 1035b, a claw portion 1067a for locking the differential gear is provided. A sliding claw portion 1067b for a differential gear lock which can be engaged with and disconnected from the claw portion 1067a for locking the differential gear is formed on the left end of the sliding cylinder 1067 which is fitted to the front wheel drive shaft 1063 have. The sliding claw portion 1067b for the differential gear lock is engaged and disengaged by the turning operation of the differential gear lock operation pin 1068 provided through the case body 1030. [ That is, the sliding cylinder 1067 moves along the axial direction of the front wheel drive shaft 1063 by the rotation operation of the differential gear lock operation pin 1068, and the differential gear lock claw portions 1067a ).

Differential gear device 1065 locks the differential gear lock state in which the sliding claw portion 1067b for the differential gear lock engages with the claw portion 1067a for the differential gear lock.

[Work device drive system]

Apart from the above-described travel driving system, a working device driving system for transmitting power to the seedling-implanting device 1002 of the working type working device will be described.

The power to the seedling plant 1002 is transmitted to the seedling plant 1002 through the intermittent transmission mechanism 1007 and the graft clutch 1008 (corresponding to the work clutch) in the main body casing portion 1004 provided at the rear portion of the main casing portion 1003 And is taken out from the output transmission shaft body 1042 extending from the main body portion 1004 to the rear side, and is transmitted to the rear seedling plant 1002.

As shown in Figs. 15 and 16, the daytime case portion 1004 includes a daytime case body 1040 which is formed separately from the case body 1030 of the main case portion 1003. The main body case 1040 is integrally fixed to the main case part 1003 through a connecting bolt or the like (not shown). The main casing portion 1003 and the main casing portion 1003 are connected to each other in a sealed state in which the openings 1040a and 1030a formed at the connection portions of the main casing portion 1004 and the main casing portion 1003 are connected to each other, .

The power transmission from the main case portion 1003 to the main casing portion 1004 is carried out by a combination of the working system transmission coaxial shaft 1037 provided on the left and right side walls 1030b and 1030b of the case main body 1030, A bevel gear 1037a fixed to the bevel gear 1037 and an output bevel gear 1038 engaged with the bevel gear 1037a.

The second external gear 1036b provided on the shaft portion of the working-table coaxial shaft 1037 protruding outside the case body 1030 is connected to the case body 1030 of the extension shaft 1033, Is engaged with the first external gear 1036a provided on a shaft portion projecting to the outside of the housing 1030, whereby power transmission is performed.

16, a long working drive shaft 1041 (corresponding to a shift operation shaft) extending in the front-rear direction is disposed in front of and behind the main casing portion 1004 in the main casing portion 1004.

The working drive shaft 1041 is provided with an output transmission shaft 1042 to which a transmission shaft 1027 to the rear seedling plant 1002 is connected, And is constituted of a partial double shaft structure by a normal shaft body 1043 to which power on the upper side in the motor direction is transmitted.

The front end portion of the normal shaft member 1043 located on the upper side of the electric motor is disposed in a state of intruding into the case main body 1030 of the main case member 1003. The spline portion is inserted into the spline portion on the inner circumferential side of the output bevel gear 1038 located in the main case portion 1003, .

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 so that the normal shaft body 1043 inserted into the inner peripheral side, .

The ball bearing 1038a provided on the case body 1030 side is internally supported by a portion of the shaft body 1043 which is slightly larger in diameter than the portion of the shaft body 1043 inserted in the output bevel gear 1038 have. Further, on the rear end side of the inner race in the ball bearing 1038a, the larger-diameter portion of the normal shaft member 1043 is in contact with the other. As a result, the position of the shaft member 1043 in the forward direction is regulated.

The shaft body 1043 is formed with a small diameter hole 1043b communicating with the inner space of the main case unit 1003 on the front side of the large diameter hole 1043a into which the output electric power transmitting body 1042 is inserted. The small diameter hole 1043b and the large diameter hole 1043a of the normal shaft member 1043 are the inner circumferential passage communicating the inner space of the main case portion 1003 and the inner space of the case portion 1004 .

The intermediate cylindrical member 1044 and the rear cylindrical member 1045 are externally fitted to the outer peripheral portion of the output transmission shaft member 1042 on the rear side of the position where the shaft member 1043 is present.

A torque limiter 1046 is provided between the rear end of the intermediate cylindrical member 1044 and the front end of the rear cylindrical member 1045.

A transfer clutch 1008 is provided between the rear end of the rear cylinder body 1045 and the output transmission shaft body 1042 on the rear side of the rear cylinder body 1045. [

In this manner, the intermediate cylindrical member 1044 and the rear cylindrical member 1045 exist in the outer peripheral portion of the output transmission shaft member 1042 in a state where the output shaft member 1042 is fitted to the outer peripheral portion of the output shaft member 1042 in a relatively rotatable manner, 1043, it is easy to perform the lubrication in the daytime case portion 1004 satisfactorily.

Namely, the lubricating oil existing in the inner space of the main case portion 1003 flows through the inner circumferential side of the transmission boss gear 1038, and as shown by the broken line arrow in Fig. 16, And the power transmission shaft 1042 is rotated between the intermediate cylindrical body 1044 and between the intermediate 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, It is possible to lubricate satisfactorily while using the centrifugal force accompanying the rotation of the member.

[Interval transmission mechanism]

The inter-day shift mechanism 1007 will be described.

The inter-week shift mechanism 1007 includes a first transmission portion 1007A located on the upper side of the electric motor and a second transmission portion 1007B located on the lower side of the first transmission portion 1007A. In the first speed change section 1007A, the high and low two-speed shifting is performed, and the second speed change section 1007B is shifted in the high, middle and low three speeds so that the shifting is performed by six speed shift stages in total .

The first transmission portion 1007A is fixed to the front end portion of a shift shaft 1047 provided on the normal shaft member 1043 of the working drive shaft 1041 and the transmission shaft 1048 located parallel to the working drive shaft 1041 And a driven follower gear 1048a is provided.

Usually, the shaft member 1043 has a spline portion 1043c formed on the outer peripheral portion thereof, and a shift gear 1047 fitted to the spline portion 1043c is integrally rotatably and slidably mounted. The shift gear 1047 is provided with a first tooth portion 1047a and a second tooth portion 1047b of an approximate diameter that are slightly different in the number of teeth and one of the teeth portions 1047a and 1047b is alternatively provided on the driven gear 1048a And is positionally changeable along the axial direction of the shaft member 1043 so as to be engageable.

16, the shift range of the shift gear 1047 is set such that the first shift position 1047a and the second shift position 1047b are shifted to the second shift position in which the first gear portion 1047a and the second gear portion 1047b are located in the main body casing portion 1004, All or a part of the one tooth portion 1047a is configured to be capable of switching the shift operation position to the first shift position in which it is discharged from the main casing portion 1004 and located in the inner space of the main casing portion 1003 . The operation range by the daytime shift operating member 1100 is set so that the shift gear 1047 can move over the first shift position and the second shift position.

The shift gear 1047 is provided with a gap between the first tooth portion 1047a and the second tooth portion 1047b at which a latching pin 1102 of a later-described shifting operation member 1100 can be inserted .

The shift gear 1047 is provided with a boss portion 1047c protruding forward from the first tooth portion 1047a and extending toward the rear side of the second tooth portion 1047b toward the boss portion 1047c The equivalent part is not installed. In other words, the shift gear 1047 is provided with the boss portion 1047c only on the side of the front end portion of the end portion in the front-rear direction. The protruding length of the boss portion 1047c is set so as to prevent the shift gear 1047 from being assembled in the backward direction with respect to the shaft member 1043 in the normal direction.

That is, even if the first tooth portion 1047a is operated to the engaging side with the driven gear 1048a when the shift gear 1047 is assembled in the reverse direction with respect to the normal shaft member 1043, The end of the portion 1047c abuts against the front end 1044a of the intermediate cylindrical member 1044 and the first tooth portion 1047a can not be moved to the engagement position with the driven gear 1048a.

Since the protruding length of the boss portion 1047c is set as described above, the provision of the boss portion 1047c at only one end portion serves as a means for preventing assembly of the shift gear 1047 in the reverse direction.

In the case casing 1004, a speed change shaft 1048 (corresponding to an input side driving shaft) is disposed parallel to the working drive shaft 1041. The second transmission portion 1007B is provided over the transmission shaft 1048 and the output transmission shaft 1042 of the working drive shaft 1041. [

The second transmission portion 1007B includes a plurality of (three in the figure) transmission gears 1049 (corresponding to transmission gears) supported on the transmission shaft 1048 at the lower side of the driven side gear 1048a, (Three in the figure) fixed to the intermediate cylindrical body 1044 (corresponding to the output side transmission shaft) which is fitted to the output transmission shaft body 1042 at all times in a state of being always engaged with the transmission gear 1049 And a pair of driven gears 1044b (corresponding to transmission gears).

The transmission gear 1049 supported on the transmission shaft 1048 is loosely inserted into the transmission shaft 1048 so as to be relatively rotatable.

A plurality of speed change gears 1049 are provided between the plurality of speed change gears 1049 and the plurality of driven type speed change gears 1044b which are in the normally engaged state by the speed change operation body 1070 which is slid within the speed change shaft 1048, Is selected, the transmission power is transmitted to the output transmission shaft body 1042 through the gear pair.

That is, with respect to the driven gear 1044b engaged with the speed change gear 1049 selected by the speed change operating body 1070, the rotation of the speed change shaft 1048 is transmitted to the speed change gear 1049, And is transmitted as a shift power in accordance with the gear ratio of the transmission gear 1044b.

The shift operating body 1070 includes a shift key portion 1071 having a latching protrusion 1071a configured to be engageable with and detachable from a latching concave portion 1049a formed on the inner peripheral side of each shift gear 1049, , The position of the engagement protrusion 1071a of the shift key portion 1071 is slid in the axial direction of the transmission shaft 1048 to select the engagement position for the shift gear 1049 to be engaged, And a slide operation portion 1072 for sliding movement.

And a resilient pressing mechanism 1073 for pressing the engaging projection 1071a of the transmission key portion 1071 against the engaging concave portion 1049a on the inner peripheral side of the transmission gear 1049 to be engaged.

16 and 17, the shift key portion 1071 and the slide manipulation portion 1072 are provided in the outer peripheral groove 1072a formed in the front end portion of the slide manipulation portion 1072 and at the rear end of the transmission key portion 1071 Side projecting piece 1071b is engaged and inserted.

Accordingly, as the slide operating portion 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 a state in which the slide operation portion 1072 is press-fitted into the case body 1040 most recently. The engagement protrusion 1071a of the shift key portion 1071 is engaged with the engaging concave portion 1049a of the shift gear 1049 on the foremost end among the plurality of shift gears 1049 to engage with the engagement portion 1048 to the shift gear 1049 on the foremost stage side.

The state in which the shift gear 1049 on the forefront side is selected is a low speed transmission position for transmitting the rotation of the transmission shaft 1048 in the second transmission portion 1007B to the output transmission shaft 1042 side at the lowest speed.

The forwardmost shift gear 1049 located at the low speed transmission position is constituted by an eccentric gear and engages with the driven gear 1044b on the foremost end side on the side of the intermediate cylindrical member 1044 similarly composed of eccentric gears .

The driving speed of the grafting arm 1023 in the seedling implanting apparatus 1002 with respect to the traveling speed becomes the slowest and the week pitch is the longest in the second speed changing section 1007B Loses. At this time, the drive torque of the speed change gear 1049 by the speed change shaft 1048 may be the smallest.

Further, in the transmission state at the low speed transmission position, the rotation of the transmission shaft 1048 is transmitted to the intermediate transmission body 1044 side in the transmission state to the subordinate speed. This is so that the driving speed of the grafting arm 1023 becomes the slowest, so that it is possible to avoid as much as possible that the hooks during grafting become dragged in the mud of the rice field. In other words, the driving speed of the range in which the hooks are present in the mud is partially accelerated so that the hooks can quickly get out of the mud, out of the drive rotary locus of the grafting arm 1023.

The state shown in Fig. 17 shows a state in which the slide operation portion 1072 is drawn out to the outside of the case body 1040 most recently. The engaging projection 1071a of the shift key portion 1071 is engaged with the engaging concave portion 1049a of the shift gear 1049 on the rearm end side of the plurality of speed change gears 1049, To the shift gear 1049 on the rearmost side.

The state where the shift gear 1049 on the rearmost end side is selected is a high-speed drive position in which the rotation of the transmission shaft 1048 in the second transmission portion 1007B is transmitted at the highest speed to the output transmission shaft 1042 side. The driving speed of the grafting arm 1023 in the seedling implanting apparatus 1002 relative to the traveling speed is relatively fast and the weekly pitch is the shortest in the second speed changing portion 1007B . At this time, the drive torque of the speed change gear 1049 by the speed change shaft 1048 becomes the largest.

Although not shown, the intermediate position between the state in which the slide operation portion 1072 is pressed into the inside of the case main body 1040 in the longest time and the state in which the slide operation portion 1072 is drawn out most is the middle speed transmission position.

The engaging projection 1071a of the shift key portion 1071 is engaged with the engaging concave portion 1049a of the speed change gear 1049 existing at the intermediate position among the plurality of speed change gears 1049 , And transmits the rotational power of the transmission shaft 1048 to the intermediate position shifting gear 1049. The driving speed of the grafting arm 1023 in the seedling transplanting apparatus 1002 with respect to the traveling speed becomes a middle speed and the weekly pitch becomes an intermediate length. At this time, the drive torque of the speed change gear 1049 by the speed change 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 recessed portion 1071c formed at a plurality of positions in the longitudinal direction of the shift key portion 1071. [ The steel ball 1073b is pressed against the concave portion 1071c of the shift key portion 1071 so that the engagement protrusion 1071a protruded from the side opposite to the concave portion 1071c is engaged with the shift gear 1049 And is pressed by the engagement concave portion 1049a on the inner circumference side of the engaging concave portion 1049a. The coil spring 1073a, the steel ball 1073b and the concave portion 1071c are provided to constitute the elastic pressing mechanism 1073. [

The shift key portion 1071 is a swinging point at which the outer peripheral groove 1072a and the rear end side protruding piece 1071b are engaged with each other at the connection point between the shift key portion 1071 and the slide operation portion 1072, It is possible to swing toward the engaging concave portion 1049a on the inner peripheral side of the shift gear 1049 in the pushing and pressing direction by the mechanism 1073, that is, in the direction intersecting the slide operation direction by the slide operation portion 1072 .

The pushing-pushing position by the elastic pressing mechanism 1073 is provided at a position spaced apart from the pivotal point of the plurality of gear pairs in the second speed change portion 1007B. Therefore, the pressing force by the elastic pressing mechanism 1073 acts more strongly as the gear pair in which the week pitch is set shorter by the action of the lever.

The intermediate gear at the intermediate position and the intermediate gear at the rearmost end of the transmission gear 1049 in the second transmission portion 1007B are respectively sandwiched by the collar 1074 from both sides. The low-speed gear of the foremost end side is provided so as to be fitted in a part of the collar 1074 and the transmission shaft 1048. [

As shown in Fig. 17, the intervals a1001, a1002, and a1003 between the collars 1074 are set so that the position where the pair of gears with the weekly pitch set by the seedling plant 1002 is short, The engagement amount of the shift key portion 1071 is set to be wide.

That is, as shown in Figs. 16 and 17, the latching protrusion 1071a is formed in a mountain-like shape having a tapered shape. Accordingly, when the intervals a1001, a1002, and a1003 between the collars 1074 are wide, the engaging concave portion 1049a of the speed change gear 1049 is engaged with the engaging concave portion 1049a deeply so that the engaging engagement margin becomes large. The engaging engagement margin with respect to the engaging concave portion 1049a of the gear 1049 is reduced.

The width of the gear portion 1049b of the shift gear 1049 in the second speed change portion 1007B at the portion engaged with the driven type speed change gear 1044b is set to the same width, A bulging portion 1049c dotted at a plurality of places in the circumferential direction is formed. The projecting amount of the swelling portion 1049c is different for each of the shift gears 1049. [

That is, as shown in Fig. 17, the low-speed gear of the foremost portion is formed with a swelling portion 1049c having a small projection amount on the hub surface on the rear side, and the medium speed gear of the intermediate position is formed on the hub surface on the rear side with a swelling portion (Not shown). In the high-speed gear of the rearmost portion, swelling portions 1049c and 1049c are protruded from the hub surfaces on the front and rear sides in both forward and backward directions.

The width of the teeth 1049b of the transmission gear 1049 and the width in the forward and backward directions including the swelling portion 1049c are set to be a width that coincides with the intervals a1001, a1002, and a1003 of the aforementioned collars 1074 .

As a result, the intervals b1001 and b1002 between the teeth 1049b of the transmission gear 1049 are set so that the intervals a1001, a1002 and a1003 between the collars 1074 are widened, The intervals b1002 between the teeth 1049b of the transmission gear 1049 at the positions where the intervals a1001, a1002 and a1003 between the collars 1074 are narrowed are smaller than the interval b1001 between the gears 1049b Is set.

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

As shown in Figs. 15 and 16, the second shift lever 1075 is rotatably connected to the rear end portion of the slide operating portion 1072 of the speed change operating body 1070. As shown in Fig. The lower portion of this second shift lever 1075 is connected to the slide operating portion 1072 and an intermediate portion in the up and down direction is supported by a lever support portion 1076 provided on the upper portion of the main body case 1040.

Thus, at a portion of the lever body of the second shift lever 1075 which is relatively rotatably supported by the lever support portion 1076, the center of the lever body portion at the intermediate position along the vertical direction of the second shift lever 1075 So that the second shift lever 1075 is pivoted about the pivot center line y1001 indicating the pivot center.

Therefore, by sliding the second shift lever 1075 around the swing center line y1001, the slide operation portion 1072 of the speed change operating body 1070 slides along the axial direction of the speed change shaft 1048 .

The lever support portion 1076 supports the intermediate portion in the vertical direction of the second shift lever 1075 so as to be relatively rotatable. However, while the movement of the intermediate portion in the longitudinal direction is regulated, A pair of upper and lower concave pivot portions 1076a formed in a U-shape in plan view. Thus, by allowing the intermediate portion in the vertical direction of the second shift lever 1075 to move in a predetermined range in the left and right direction, the second shift lever 1075 can be shifted in the vertical direction The oscillating center line y1001 is also moved in a predetermined range in the lateral direction.

That is, by supporting the rocking center line y1001 in a positional shiftable state within a predetermined range in the left and right direction, it is possible to move the slide operation portion 1072 linearly, without interfering with the backward movement of the slide operation portion 1072, So that operation can be performed.

The inter-day shift operating member 1100 in the inter-day transmission mechanism 1007 is configured as shown in Figs. 15, 16, and 18.

That is, the lower end of the operating shaft 1101 passing through the upper wall portion of the main casing portion 1004 is fixed with a locking pin 1102 which is fitted between the first and second teeth 1047a and 1047b And a plate-like operating body 1103 is provided at an upper end of an operating shaft 1101 located outside the upper wall portion.

The engaging pin 1102 existing at the eccentric position moves the shift gear 1047 in the axial direction of the operation drive shaft 1041 by rotating the plate actuating member 1103 around the axis of the operation shaft 1101 . The position of the plate-like operating body 1103 around the axis is positioned by the ball detent mechanism 1104.

The inter-day shift operating member 1100 for operating the first transmission portion 1007A of the inter-day transmission mechanism 1007 is not limited to the structure shown in Fig. 22 And is linked to the first shift lever 1077.

The upper end portion of the first shift lever 1077 is provided in a state of being positioned in a T-shaped guide groove 1111 of a lever guide portion 1110 provided on the operation floor portion 1014 of the traveling base 1001 . The upper end of the first shift lever 1077 is located in the right and left guide grooves 1111 in the figure and is guided by the guide groove 1111 so that any one of the two positions of the first shift position and the second shift position So that the position can be changed.

The upper end portion of the second shift lever 1075 for operating the second speed change portion 1007B is also formed in the guide groove 1111 of the lever guide portion 1110 in the forward and backward guide grooves 1111 And guided by the guide groove 1111 so that the position can be changed so as to be able to select one of three positions, namely, the low-speed shift position, the medium-speed shift position and the high-speed shift position.

In the lever guide portion 1110, pattern display portions 1112 are provided on both left and right sides of a T-shaped guide groove 1111, in which numerical values indicative of a week pitch are described.

22, there is a character pattern of " 14 " supporting the week pitch 14 cm above the left side in the figure. In order to set the pitch 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 at the right side of the character pattern of the frontmost "14" Position. In this state, since 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, Set the pitch to the tightest 14 cm.

When the first shift lever 1077 is operated toward the right end of the guide groove 1111 and is operated to the forward position of the character pattern 16 from this state, the first shift lever 1077 is switched to the second shift position And is switched to the low speed side. Therefore, if the position of the second shift lever 1075 is not changed, the week pitch is set to 16 cm.

When the position of the second shift lever 1075 is positioned on the left side of the character pattern 21 from this state, the week pitch is set to 21 cm, and if the position is positioned on the left side of the character pattern " 28 " Is set to 28 cm.

When the first shift lever 1077 is positioned at the left end of the guide groove 1111 and the same operation is performed, the position of the second shift lever 1075 is positioned on the right side of the character pattern " 18 "Quot; is set to 18 cm, and is positioned on the right side of the character pattern " 24 ", the weekly pitch is set to 24 cm.

That is, the shift gear 1047 is switched to the first shift position and the second shift position by the left and right movement of the first shift lever 1077, and the character pattern group on the left side of the guide groove 1111 and the character pattern group on the right side And the desired character pattern can be selected from the group of character patterns by the movement of the second shift lever 1075 in the forward and backward directions.

Therefore, it is easy to set the weekly pitch by the operating positions of the first shift lever 1077 and the second shift lever 1075 in a state where there is little erroneous operation by eyes.

The guide groove 1111 of the lever guide portion 1110 is constituted by a through hole formed in the operation part floor 1014 of the traveling base 1001. Fig. 22 is an explanatory view seen from a plane showing the pattern display section 1112 in the lever guide section 1110. Fig. The first shift lever 1077 and the second shift lever 1075 in the guide groove 1111 are provided so as not to protrude above the upper surface of the operation part floor 1014 and are normally provided on the operation part floor 1014 ) In the state of being covered with a mat, so that the mat can be operated by turning it if necessary.

The power shifted by the intermeshing transmission mechanism 1007 is transmitted from the intermediate body 1044 to the torque limiter 1046. [

The torque limiter 1046 includes a plate 1046a on the disk fixed to the rear end of the intermediate cylindrical member 1044, a pressure plate 1046b which is brought into contact with the plate 1046a and a pressure plate 1046b which is located on the side of the plate 1046a And a coil spring 1046c for pressurizing and pressing against the coil spring 1046c. Through this torque limiter 1046, the shift power by the inter-speed transmission mechanism 1007 is transmitted to the clutch 1008. [

[Transmission clutch]

The transfer clutch 1008 is configured as follows.

A driving side rotating member 1080 in the form of a disk integrally rotatable with the rear normal body 1045 by engaging with the outer side spline of the rear normal body 1045 is integrally formed with the rear end of the rear normal body 1045 of the working driving shaft 1041, Respectively.

The output transmission shaft 1042 is engaged with a spline portion 1042a formed on the outer circumferential surface of the output transmission shaft 1042 so as to engage with the output transmission shaft 1042 And a driven side rotary member 1081 movable in position in the axial direction of the integral rotation and output transmission shaft 1042 are provided.

The driven side rotational member 1081 is pressed by the urging spring 1082 toward the side of the drive side rotational member 1080 so that the drive side rotational member 1080 and the driven side rotational member 1081 Engagement portions 1080a and 1081a capable of transmitting power with each other being engaged with each other are formed on the opposite surface.

The urging spring 1082 has a spring receiving portion 1081b formed on a surface of the driven side rotary member 1081 opposite to the side where the engaging portion 1081a is formed and a spring receiving portion 1081b formed on the inner surface side of the main casing portion 1004 And is installed between the fixing portions. Although the inner end of the inner race 1040c of the ball bearing 1040b supporting the output transmission shaft 1042 is used as the fixing portion on the inner surface side of the case portion 1004 in this case, There is no.

The shape of the urging spring 1082 is such that the winding diameter at the end of the urging spring 1082 on the side of abutting against the spring receiving portion 1081b in the axial direction of the working drive shaft 1041 is larger than that of the inner side of the inner race 1040c And is formed in a conical shape larger than the winding diameter.

The winding diameter of the compression spring 1082 on the side contacting the inner end of the inner race 1040c is equal to or slightly larger than the outer diameter of the output transmission shaft member 1042 fitted to the outside. Therefore, it is possible to position the end position of the inner race 1040c of the ball bearing 1040b supporting the output transmission shaft 1042 by using the inner end of the inner race 1040c without particularly requiring a positioning means.

16, the driven-side rotational member 1081 is separated from the drive-side rotational member 1080 by the clutch operating member 1083 abutting on the outer peripheral portion against the urging force of the urging spring 1082 And the engagement portion 1081c is engaged with the outer circumferential portion of the clutch operation member 1083. As shown in Fig.

The clutch operating member 1083 is provided with an operating pin 1084 that penetrates the upper wall portion of the case portion 1004 and is provided at the lower end portion of the operating pin 1084 with the engagement portion 1084 of the driven- An operating portion 1084a for moving the driven side rotating member 1081 in the axial direction of the output transmission shaft 1042 is formed in association with the operation of the operating pin 1084 when the operating pin 1084 is rotated.

The clutch operating member 1083 is disposed on the operating pin 1084 of the operating pin 1084 which is exposed to the outside of the main casing portion 1004 among the operating pins 1084 operated around the rotating axis p1001 in the direction crossing the axis of the working driving shaft 1041 An operation plate 1085 for rotating the operation pin 1084 is provided at the shaft end of the operation plate 1084. An operation guide member 1086 for guiding a pivoting operation of the operation plate 1085 around the rotation axis p1001 is supported on the upper surface of the inter- (1004).

Thereby, the operation pin 1084 is regulated by the operation plate 1085 to move the position in the direction along the rotation axis p1001, and the operation range around the rotation axis p1001 is moved to the operation plate 1085 And is regulated by the abutment of the operation guide member 1086.

The position of the spring accommodating portion 1081b of the driven side rotatable member 1081 is set to the position where the engaging portion 1081c of the driven side rotatable member 1081 is engaged with the engagement portion 1081c at the lower end of the operating pin 1084 Side rotating member 1081 and the engaging portion 1081c of the driven-side rotating member 1081 with respect to the axial direction of the working drive shaft 1041 as compared with the engaging portion with the engaging portion 1081c of the driven- 1081a are formed.

As described above, the spring receiving portion 1081b is the inner side in the radial direction than the engaging portion of the engaging portion 1081c of the operating pin 1084 and the driven-side rotating member 1081, and the engaging portion 1081a, Is concave so as to be close to the side on which it is present. This makes it possible to avoid that the axial length of the working drive shaft 1041 of the urging spring 1082 is restricted by the position of the operating pin 1084 in the axial direction of the working drive shaft 1041, It is possible to reduce the size of the display device 1004.

[Fertility drive system]

A drive system for driving a drive force for branching the drive force from the above-described travel drive system to the drive system 1009 is constructed as follows.

21, a branch case portion 1005, which is formed separately from the main case portion 1003, is connected and fixed to the rear side of the main case portion 1003 through a mounting bolt or the like (not shown) have.

The main case portion 1003 and the branch case portion 1005 are communicated with each other in an airtight state in which the openings 1030a and 1050a formed at the connection portions of the main case portion 1003 and the branch case portion 1005 are joined.

21, the branched case portion 1005 includes an input side cylindrical portion 1050A that supports the rear wheel output shaft 1064 extending rearward from the main case portion 1003, and an input side cylindrical portion 1050B that extends in the direction crossing the rear wheel output shaft 1064 And an output side cylindrical portion 1050B that is externally fitted to the branch transmission shaft 1051 extending to the branch transmission shaft 1051 and supports the branch transmission shaft 1051. [ The input side cylindrical portion 1050A and the output side cylindrical portion 1050B are formed of an integral body having a common internal space.

The bevel gear 1052 for transmitting the power from the rear wheel output shaft 1064 to the branching transmission shaft 1051 is provided in the input side cylindrical portion 1050A and a bevel gear 1052 for engaging with the bevel gear 1052 for branching output 1053 (corresponding to a bevel gear for branch input) is provided in the output side cylindrical portion 1050B.

The bevel gear 1052 for branching output is provided in the input side cylindrical portion 1050A closer to the main case portion 1003 than the branch transmission shaft 1051. [

A rear wheel output shaft 1064 provided at the front end of the rear wheel input bevel gear 1064a meshing with the rear wheel output bevel gear 1035d is connected to the rear wheel output shaft 1064 via a ball And the rear end portion is supported by a ball bearing 1054 provided near the rear end portion of the branch case portion 1005. [

The rear wheel output shaft 1064 is provided with a step portion 1064C (corresponding to the positioning portion) at a position midway in the axial direction thereof. The front portion of the rear wheel output shaft 1064, Diameter shaft portion 1064A and the rear side corresponding to the lower side in the rolling direction than the stepped portion 1064C is formed in the small diameter shaft portion 1064B.

The stepped portion 1064C is formed near the boundary between the main case portion 1003 and the branched case portion 1005 and a spline portion 1064D is formed at a portion near the step portion 1064C of the small diameter shaft portion 1064B And the branch output bevel gear 1052 is splined to the spline portion 1064D.

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

Therefore, when the rear wheel output shaft 1064 is housed in the branched case portion 1005, it can be housed in the branched case portion 1005 with the bevel gear 1052 for branch output held in advance on the rear wheel output shaft 1064 , It is possible to facilitate the assembly and disassembly.

The branching transmission shaft 1051 provided at the input side end of the bevel gear 1053 for meshing with the bevel gear 1052 supported by the rear wheel output shaft 1064 is disposed in a posture orthogonal to the rear wheel output shaft 1064 Respectively. The input side end portion can be inserted and extracted from the output side opening portion 1050b formed in the output side normal portion 1050B of the branch case portion 1005. The output side end portion is configured to extend outward from the output side opening portion 1050b of the output side normal portion 1050B And is supported in a protruded state.

An interlocking shaft (not shown) to the propeller unit 1009 is connected to a protruding portion of the branching transmission shaft 1051 protruding outward from the output side opening 1050b.

The branching transmission shaft 1051 is a portion corresponding to the insertion limit position to the output side cylindrical portion 1050B and the input side end abuts the rear wheel output shaft 1064. [ That is, when the branch transmission shaft 1051 is inserted into the output side cylindrical portion 1050B until reaching the insertion limit position from the output side opening 1050b, the input side tubular portion 1050B is positioned so that the input side end portion thereof abuts on the rear wheel output shaft 1064 1050A of the rear output shaft 1064 of the rear wheel.

The application bevel gear 1053 is supported so as to be relatively rotatable with respect to the branching transmission shaft 1051. The branching transmission shaft 1051 and the application bevel gear 1053 are rotatably supported by a friction clutch 1055 And is detachably detachable through the through holes.

The friction clutch 1055 is provided with a normal shift member 1056 which is splined to a spline portion formed on the outer peripheral surface of the branching transmission shaft 1051. The pawl portion 1056a formed on the opposing face of the normal shift member 1056 to the application bevel gear 1053 and the engagement portion 1056a on the side of the application bevel gear 1053 facing the normal shift member 1056 The engaging concave portion 1053a is engaged and disengaged to switch the rotation of the bevel gear 1053 to the diverging transmission shaft 1051 and to switch the transmission to the disengaged state.

The shift member 1056 is normally urged toward the application bevel gear 1053 by the coil spring 1057 and the normally shift member 1056 is moved away from the application bevel gear 1053 against this pressing force The clutch operating shaft 1058 is provided so as to penetrate through the output side cylindrical portion 1050B.

[Other Embodiment 10]

In the above-described embodiment, a rice hatching machine having a daytime housing part 1004 as a refrigerator working case part is shown, but the present invention is not limited thereto. For example, when used in a planter equipped with a direct wave device, the tabletop operation case portion is a work case portion for changing the interval of wavefront caused by the direct wave device.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 11]

In the above embodiment, the fertilizer device 1009 is used as the powder supply device, but the invention is not limited thereto.

For example, it may be possible to supply medicines such as herbicides and insect repellents.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 12]

In the above-described embodiment, the pattern display portion 1112 of the lever guide portion 1110 has a structure in which the T-shaped guide groove 1111 is arranged on the left and right, but the present invention is not limited to this structure.

For example, as shown in FIG. 23 (a), the guide groove 1111 may be arranged on the front side and the lateral side of the L-shaped guide groove 1111, or may be arranged in a cross- 1111 in the front, rear, left, and right directions.

Other configurations may adopt the same configurations as those of the above-described embodiments.

[Other Embodiment 13]

In the above-described embodiment, the speed change operation body 1070 of the inter-speed transmission mechanism 1007 is provided on the side of the transmission shaft 1048 arranged as an axis corresponding to the input side transmission shaft, The power transmission is selectively transmitted to the driven type transmission gear 1044b fixed to the driven gear 1044. However, the present invention is not limited to this structure.

For example, a fixed transmission gear is provided on the side of the transmission shaft 1048 disposed as an axis corresponding to the input side transmission shaft, and a transmission gear that is relatively rotatable relative to the intermediate transmission body 1044 provided as an output side transmission shaft is provided , And the transmission operating member 1070 may be configured to select a relatively rotatable transmission gear on the side of the intermediate cylindrical member 1044.

Other configurations may adopt the same configurations as those of the above-described embodiments.

The present invention is not limited to the passenger-type transplanter for four-row grafting, but may be applied to various types of working machines such as a working machine, a water-receiving machine, a tiller or a tractor, Device.

1: running gas
2: seedling transplanting device (working device)
3: Main case part
3A: Auxiliary transmission mechanism
4A: Work system transmission mechanism (transmission mechanism)
4: seeding case part (work case part)
5: Branch case section
5A: Branch transmission mechanism
6: Main transmission mechanism
8: Work Clutch
16: Axle case
30a: opening
31: Upper transmission shaft
32: Lower speed change shaft
32a, 32b: Lower gear
32c, 32d: engaging recesses
32e: Shaft support hole
34: Shift member
34a, 34b:
40a: opening
41: Shifting operation shaft (work drive shaft)
42: Output power shaft
43:
47: Shift gear
50a: opening
50A:
50B:
51:
52: Bevel gear for branch output
53: Bevel gear for branch input
64: Driving transmission shaft
64C:
65:
66: Bevel gear pair
67: Bevel gear pair
80:
80a:
81: driven side rotary member
81a:
81b: spring receiving portion
81c:
82: pressing spring
83: clutch operating member
84: Operation pin
85: Operation plate
86: Operation guide member
p1: Rotational axis
1001:
1002: seedling transplanting device (working device)
1004:
1007: Inter-weekly transmission mechanism (planetary transmission mechanism)
1041: Shift operation shaft
1044: intermediate cylindrical member (output side driving shaft)
1044b: a driven type shift gear (transmission gear)
1047: Shift gear
1048: Shifting axis (input side driving shaft)
1049: Transmission gear (transmission gear)
1049b:
1070:
1071: Shift key portion
1072:
1073: Elastic pressing device
1074: Color

Claims (22)

A main casing unit having a transmission mechanism for shifting the input engine power and outputting transmission power to the traveling driving system,
A work case unit including a work system transmission mechanism for shifting the engine power input via the main case unit and outputting a shift power to the work equipment,
Wherein the work case portion is provided with a work drive shaft for transmitting a shift power by the work system transmission mechanism to the work device and a work clutch capable of interrupting power transmission from the work system transmission mechanism to the work drive shaft,
Wherein the work clutch includes a drive side rotating member that receives power from the work system transmission mechanism at an upper side in a power transmitting direction and a driving side rotating member that is externally fitted to the working driving shaft at a lower side in a power transmitting direction than the driving side rotating member, And a driven side rotating member supported so as to be rotatable integrally with the working drive shaft,
Wherein the driven-side rotational member and the driven-side rotational member are provided with engaging portions capable of transmitting power in the engaging state on the respective opposed surfaces, and that the driven-side rotational member And is movable in the direction of the axis of the working drive shaft,
And a pressing spring for press-urging the driven-side rotational member toward the driven-side rotational member is provided outside the working drive shaft, and the driven-side rotational member is spaced apart from the driven-side rotational member against the urging force of the urging spring A clutch operating member operable to be operated by a driver is provided,
Wherein the clutch operating member is engaged with a engaging portion formed on an outer peripheral side of the driven side rotational member and operable to move the driven side rotational member away from the drive side rotational member,
Wherein the urging spring is provided on the inner side in the radial direction of the driven-side rotational member with respect to the engaged position of the clutch operating member and the engaging portion. 2. The hydraulic control apparatus according to claim 1, wherein a spring receiving portion is formed on a surface of the driven side rotational member opposite to the side where the engaging portion is formed, and the spring receiving portion is provided in the axial direction of the working drive shaft, Wherein the engaging portion is provided at a position near the opposed surface side where the engaging portion is formed. The work machine as set forth in claim 2, wherein the urging spring is mounted between the spring receiving portion and the fixed portion on the inner surface side of the work case portion, and is provided on the other end side of the working drive shaft in the axial direction Wherein the cone is formed in a conical shape having a large winding diameter. 4. The spool according to claim 3, wherein the compression spring is formed such that the winding diameter of the driven side rotational member on the side supported by the spring receiving portion is larger than the winding diameter on the opposite side, Is set so as to abut the outer peripheral surface of the working drive shaft. The clutch operation device according to any one of claims 1 to 4, wherein the clutch operation member includes: an operation pin penetrating the operation case portion and being operated around a rotation axis in a direction crossing the axis of the operation drive shaft; And an operating plate provided at an axial end portion of the operating pin at a portion exposed to the outside,
Wherein the operation case member is provided with an operation guide member for positioning in the direction along the rotation axis of the operation plate. 6. The work machine according to claim 5, wherein the operation guide member includes a guide portion capable of permitting operation of the operation plate about the rotation axis in a range corresponding to an on-off operation range of the work clutch Lt; / RTI > The power transmission device according to any one of claims 1 to 4, wherein the working drive shaft includes: an output transmission shaft integrally rotating with the driven side rotary member; And a double shaft structure part formed by a normal shaft body to which a power on the upper side in the electric motor direction is transmitted,
A portion of the normal shaft body located at the uppermost position in the motor-driven direction is inserted into the inner circumferential side of the communication boss of the output bevel gear located in the main casing portion, and the inner peripheral side of the normal shaft body Wherein the passage connects the inside of the main case part and the part of the double shaft structure. The power transmission apparatus according to claim 7, wherein said normal shaft member is divided into a plurality of portions in the axial direction of said output transmission shaft member, and a member that rotates together with said ordinary shaft member is mounted on each of the divided normal shaft members . A main case unit for providing a main speed change mechanism for shifting the input engine power and a sub speed change mechanism for shifting the power transmitted from the main speed change mechanism to a driving driving system,
And a tabletop working case having a type separating mechanism for shifting the power output from the main case part to a seedling or seeding device,
The refrigerator case is formed separately from the main case part and integrally fixed to the main case part,
Wherein the main case part and the cooking utensil case part are communicated with each other in an airtight state in which openings formed at connection points of the main body case and the cooking utensil case part are joined to each other. 10. The apparatus according to claim 9, further comprising a branch case portion which incorporates a branch transmission mechanism and branches the power output from the main case portion to the powder supply device,
The branch case portion is formed separately from the main case portion and is integrally connected and fixed to the main case portion,
Wherein the main case part and the branch case part are communicated with each other in an airtight state in which openings formed at connection points of the main case part and the branch case part are joined to each other. 11. The automatic transmission according to any one of claims 9 to 10, wherein the type-based shifting mechanism includes a shift operating shaft extending between the internal space of the refrigerating and working case portion and the internal space of the main casing portion and capable of sliding along the axial direction of the shift operating shaft And a shift gear supported on the shift operating shaft,
Wherein a slide operation range accompanying shift operation of the shift gear is set over an internal space of the refrigerator case and an internal space of the main case portion. The power steering apparatus according to claim 10, wherein the branch case portion includes an input side cylindrical portion that is fitted to a traveling transmission shaft of a traveling driving system extending from the main case portion and that supports the traveling electric power shaft,
And an output side cylindrical portion that is externally fitted on a branch drive shaft extending in a direction intersecting the traveling transmission shaft and supports the branch drive shaft,
The input side tubular portion is connected to the main case portion, the output side tubular portion is formed integrally with the input side tubular portion,
And a branch output bevel gear is provided in the input side cylindrical portion on the side closer to the main case portion than the branch drive shaft. 13. The automatic transmission according to claim 12, characterized in that a bevel gear for engaging with the bevel gear for branching output is supported by the branch drive shaft,
Wherein the branch output bevel gear is supported by the driving transmission shaft,
Wherein the traveling transmission shaft is provided with a positioning portion for regulating the movement of the bevel gear for branching output on a side opposite to the side where the bevel gear for the branch input exists. 14. The automatic transmission according to claim 12 or 13, wherein the opening of the branch case portion formed at an opposed portion to the main case portion has an inner diameter capable of inserting the branch output bevel gear supported by the traveling- , The power transmission device of the hydraulic power plant. An apparatus according to claim 12 or 13, wherein an end of the input side of the branch drive shaft is insertable and withdrawable with respect to an output side opening formed in the branch case portion,
Wherein the branch case portion is provided with a drive transmission shaft which is a portion corresponding to an insertion limit position of an end portion on an input side of the branch drive shaft and in which the drive transmission shaft is supported at a position abutting the end portion on the input side of the branch drive shaft Device. The transmission according to any one of claims 9, 10, 12, and 13, wherein the auxiliary transmission mechanism includes: an upper shift shaft located on the upper side in the power transmission direction; A gear pair for high speed suitable for running on the road and a pair of gears for low speed suitable for running on the work are provided on the lower transmission shaft along the lower transmission shaft, Respectively,
Wherein the shift member is provided with an engaging portion supported so as to be positionally movable in the axial direction of the lower transmission shaft and protruding in a direction in which the lower gear located at the lower side in the power transmission direction among the gear pairs,
Each of the lower gears positioned opposite to both sides of the shift member is provided with an engaging recess portion engaging with the engaging portion of the shift member,
Wherein the engaging concave portion of the lower gear of the pair of high speed gears suitable for running on a road surface of the engaging concave portion has a shape extending from a shaft supporting hole of the lower gear that is fitted to the lower side shifting shaft Transmission device. The vehicle according to any one of claims 9, 10, 12, and 13, further comprising: an axle case to which power of the driving and driving system is transmitted,
The axle case is provided with a pair of bevel gears on the upper side of the electric motor and a pair of lower electric bevel gears on the lower side of the transmission shaft located on the upper side of the transmission shaft along the vertical direction, And the reduction ratio of the pair of bevel gears on the lower electric side is set to be larger than the pair of bevel gears on the upper side of the electric motor. A type-based gear transmission mechanism for shifting the engine power and transferring the engine power to a seedling planting apparatus or a seeding apparatus is incorporated in the gardening work case unit,
The type-based shifting mechanism includes a plurality of gear pairs arranged in a state of always engaged with an input side transmission shaft on the upper side of the electric motor and an output side transmission shaft on the lower side of the electric motor, and a pair of gears The speed change operation body,
Wherein the shift operating body includes a shift key portion that is capable of selectively engaging and disengaging any one of the transmission gears constituting the gear pair as an engagement object,
Wherein the gear engagement margin of the transmission gear portion with respect to the transmission gear of the engagement object is selected such that the gear pair having the week pitch by the seedling plant or the seeding pitch by the seeding apparatus set shorter is selected among the plurality of gear pairs The power transmission mechanism of the waterproofing machine. 19. The automatic transmission according to claim 18, wherein an interval in the axial direction of the input side transmission shaft or the output side transmission shaft is set between the transmission gears disposed at positions adjacent to each other in the axial direction of the input side transmission shaft or the output side transmission shaft A plurality of colors are arranged,
The distance between the collar is set such that the amount of engagement of the shift key portion with respect to the transmission gear is increased as the week interval by the seedling planting apparatus or the portion where the gear pair with the seeding pitch set by the seeding apparatus is set shorter A power transmission device for a water-powered machine, set at wide intervals. The transmission according to claim 19, wherein the interval between the teeth of the transmission gears in the axial direction of the input side transmission shaft or the output side transmission shaft is set to a distance between teeth of the transmission gears Wherein the distance between the teeth of the transmission gears at the positions where the intervals between the collars are narrowed is narrower than that between the teeth of the power transmission gears. 21. The shift operating body according to any one of claims 18 to 20, wherein the shift operating body is configured to slide and operate 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, And a slide operation portion for selecting and operating the engagement position for the electric gear to be the object,
Wherein the shift key portion is configured to be swingable in a direction of engagement with the transmission gear which intersects the slide operation direction by the slide operation portion, with a connection point to the slide operation portion as a swinging point, Lt; / RTI > The shift operating body according to claim 21, further comprising: a resilient pressing mechanism for pressing the transmission key portion against the transmission gear side of the engagement object,
Wherein the pressing-pressing portion by the elastic pressing mechanism is set at a position spaced apart from the swinging point with respect to the plurality of gear pairs,
Wherein the pair of gears that sets the week pitch by the seedling implanting apparatus or the sowing pitch by the seeding apparatus is set so as to be smaller than that of the pair of gears Transmission device.

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