JP2021076155A - Passenger work machine - Google Patents

Abstract

To effectively inhibit leakage of a lubrication oil from a breather device caused by influence of air bubbles contained in the lubrication oil in a transmission gear housing space.SOLUTION: A transmission case 34 includes: a transmission gear housing space S1 in which a gear transmission mechanism 35 is installed; and a separated space S2 partitioned from the transmission gear housing space S1 by a partition wall part 36. A breather device 8 communicating with outside air is provided in the separated space S2. Defoaming means 37 for eliminating air bubbles contained in a lubrication oil passing through a breather introduction passage is disposed on the breather introduction passage which enables the lubrication oil to flow from the transmission gear housing space S1 to the separated space S2.SELECTED DRAWING: Figure 9

Description

The present invention relates to a passenger working machine in which a breather device is provided at a position where the pressure in the transmission gear accommodating space in the transmission case is released to the atmosphere.

As a work machine equipped with the above-mentioned breather device, a transmission gear accommodating space in which a gear transmission mechanism is installed and a separate space formed by recesses partitioned by a partition wall with respect to the transmission gear accommodating space are provided in the transmission case. , Are provided. Then, there is a case in which a breather pipe as a breather device is provided through a breather connecting passage communicating with the other space (see Patent Document 1).

Japanese Unexamined Patent Publication No. 2019-90443 (see paragraphs "0049" and "0054", and drawings "FIG. 1" and "FIG. 6").

According to the above prior art, the breather device is partitioned from the transmission gear accommodation space by passing through another space partitioned by a partition wall with respect to the transmission gear accommodation space and a breather connection passage communicating with the other space. Moreover, it is provided at a remote location that is bent like a crank. Therefore, it is possible to prevent air bubbles generated in the transmission gear accommodating space from directly reaching the breather device, and it is easy to suppress the ejection of the lubricating oil to the outside of the transmission case.
However, although there is an effect of suppressing the partition by the partition wall and the bent path between the transmission gear accommodating space and the location where the breather device exists, the state of spatial communication remains unchanged. Since there is no means for extinguishing the air bubbles, it is difficult to reliably prevent the leakage of the lubricating oil accompanied by the air bubbles from the breather device, and there is room for improvement in this respect.

The present invention is intended to effectively suppress the leakage of the lubricating oil from the breather device due to the influence of air bubbles mixed in the lubricating oil in the transmission gear accommodating space.

The passenger working machine according to the present invention is provided with a transmission gear accommodating space in which a gear transmission mechanism is incorporated and a separate space partitioned by a partition wall with respect to the transmission gear accommodating space in the transmission case. A breather device that communicates with the outside air is provided in another space, and air bubbles contained in the lubricating oil passing through the breather introduction path are provided in the breather introduction path that enables communication of the lubricating oil from the transmission gear accommodating space to the other space. It is characterized in that a defoaming means for eliminating the air is intervened.

According to the present invention, since the defoaming means for eliminating the air bubbles contained in the lubricating oil passing through the breather introduction path is provided, the lubricating oil introduces the air bubbles in the lubricating oil generated in the transmission gear accommodating space. It is easy to disappear in the process of flowing through the road. As a result, by reducing the amount of bubbles in the lubricating oil, there is an advantage that leakage of the lubricating oil from the breather device due to the influence of mixed bubbles can be effectively suppressed.

In the present invention, the defoaming means is preferably a bearing that penetrates the partition wall portion and supports a shaft body extending over the transmission gear accommodating space and the separate space.

According to this configuration, the bearing for supporting the shaft body can be effectively used as a defoaming means for air bubbles in the lubricating oil moving from the transmission gear accommodating space to another space, and the structure can be simplified by using the members as well. While trying, it is possible to suppress the leakage of the lubricating oil from the breather device.

In this configuration, it is preferable that the breather device is connected to the separate space at a position lower than the maximum height position of the transmission gear accommodating space.

According to this configuration, since the breather device is located at a position lower than the transmission case, it is easy to avoid the possibility that the breather device interferes with the installation space of the mounting device located above the transmission case, for example, the driving cabin.

In the present invention, it is preferable that the breather device is provided at the maximum height position in the other space.

According to this configuration, when the pressure rises in another space, the whole in another space can be opened to the atmosphere.

In the present invention, a machine frame, a prime mover mounted and supported on the machine body frame, a traveling device provided below the machine body frame and capable of traveling to the ground based on the power of the prime mover, and work on agricultural products in a field. A work device capable of shifting the power of the prime mover and a transmission for shifting and outputting the power of the prime mover are provided, and the shift device receives the power of the prime mover on the first input shaft to shift the speed and receives the power after the shift. A hydrostatic stepless transmission capable of outputting to the first output shaft and the gear transmission mechanism built in the transmission case are provided, and the gear transmission mechanism is provided with a plurality of power sources based on the first input shaft. A work transmission mechanism capable of transmitting power to the work device via the work drive gear, and a travel transmission mechanism capable of transmitting power based on the first output shaft to the travel device via a plurality of travel drive gears. It is preferable that the work transmission mechanism and the traveling speed change mechanism are vertically distributed in the transmission gear accommodating space of the transmission case.

According to the configuration of the present invention, an internal space is formed by the housing case of the transmission mechanism, and the work transmission mechanism and the traveling speed change mechanism are housed in the internal space. That is, since the work transmission mechanism and the traveling transmission mechanism are housed together in one housing case, compared with the configuration in which the work transmission mechanism and the traveling transmission mechanism are arranged in different spaces. , The transmission mechanism tends to be lightweight and compact. In addition, the work transmission mechanism and the traveling transmission mechanism are arranged vertically, so that the work transmission mechanism and the traveling transmission mechanism are not complicatedly intertwined in the internal space and are assembled in a simple configuration. The labor of the worker in the work and maintenance work is reduced. As a result, a lightweight and compact passenger work machine can be realized even when the power transmission mechanism has a complicated structure.

In the present invention, the work input shaft integrally connected to the work transmission mechanism in the direction of the rotation axis core and the work input shaft projecting from the transmission case to the side opposite to the position of the prime mover. It is preferable that a work output shaft capable of transmitting power to the work device is provided.

According to this configuration, the side where the prime mover is located rather than the housing case is the area where the prime mover and the hydrostatic continuously variable transmission are located, and the peripheral devices and the like are also provided and tend to be a crowded area. .. With this configuration, the work output shaft projects to the side opposite to the side where the prime mover is located, avoiding the crowded area, so it is easy to have a mechanism to transmit power further downstream from the work output shaft. It becomes possible to arrange.

In the present invention, the working device includes a liquid spraying device capable of spraying a liquid on agricultural products in a field, and a spraying pump capable of driving the liquid spraying device is provided above the work output shaft. A pulley around which a transmission belt is wound is provided on each of the output shaft for use and the input shaft of the spraying pump 27, and the protruding tip of the work output shaft is used to power the work device other than the liquid sprayer. It is preferable that a relay shaft capable of transmitting the above is connected.

According to this configuration, the transmission belt is wound around the spraying pump and the working output shaft, and the relay shaft is connected further downstream from the working output shaft. Therefore, the power of the work output shaft is branched into the spray pump and the work output shaft with a simple configuration without providing a dedicated power branching mechanism.

In the present invention, it is preferable that the working input shaft is fitted with an intermediate cylinder shaft capable of transmitting the rotational power of the working input shaft to the working output shaft.

According to this configuration, the double shaft is configured by the configuration in which the intermediate cylinder shaft is externally fitted to the working input shaft. Therefore, the number of shafts used for the plurality of work drive gears is reduced, and the work transmission mechanism becomes more compact.

In the present invention, a drill hole is formed on the outer peripheral surface of the intermediate cylinder shaft, and the intermediate cylinder shaft is provided on the work input shaft and is provided in a bearing supporting the intermediate cylinder shaft through the drill hole. It is preferable that it is configured so that it can be supplied.

According to this configuration, lubricating oil enters through the drilled holes, and an oil film of hydraulic oil is attached between the intermediate cylinder shaft and the work input shaft. Then, by spreading the lubricating oil to the bearing that supports the intermediate cylinder shaft, friction does not occur between the intermediate cylinder shaft and the work input shaft, and the intermediate cylinder shaft and the work input shaft can be smoothly moved to each other. Can rotate.

In the present invention, the passenger working machine is preferably a riding management machine.

According to this configuration, a lightweight and compact passenger management machine can be realized even when the power transmission mechanism has a complicated configuration.

It is a left side view which shows the whole of a passenger work machine. It is a top view which shows the whole of a passenger work machine. It is a top view which shows the transmission system including a transmission. It is a left side view which shows the transmission supported by the fuselage frame. It is a front view which shows the transmission supported by the fuselage frame. It is sectional drawing in the vertical direction along the horizontal direction of a transmission. It is a plane development view which shows the transmission mechanism for traveling of a transmission. It is a plane development view which shows the work transmission mechanism of a transmission. It is sectional drawing in the vertical direction along the front-rear direction of a transmission case.

Hereinafter, an example of the embodiment of the present invention will be described based on the description in the drawings.
Unless otherwise specified, the front-back direction and the left-right direction in the description of the present embodiment are described as follows. That is, in the passenger work machine to which the present invention is applied, the traveling direction on the forward side (see arrow F in FIGS. 1 and 2) is "forward" and the traveling direction on the reverse side (FIGS. 1 and 2) when the traveling machine is working. (See arrow B in FIG. 2) is "rear", the direction corresponding to the right side with respect to the forward-looking posture in the front-back direction (see arrow R in FIG. 2) is "right", and similarly the direction corresponding to the left side (see FIG. 2). (See arrow L) is "left".

[Basic configuration of passenger work machine]
As an example of the passenger work machine according to the present invention, FIGS. 1 to 3 show a boom sprayer with a cabin, that is, a passenger management machine.
The boom sprayer is provided with a traveling machine body 1 having a body frame 10, a pair of left and right front wheels 1F and 1F, and a pair of left and right rear wheels 1R and 1R.
Axle units 11F and 11R are connected to the front and rear parts of the lower part of the fuselage frame 10, and the axle units 11F and 11R extend to the left and right of the fuselage. The front wheels 1F and 1F are rotatably supported on the left and right ends of the axle unit 11F in the front portion, and the rear wheels 1R and 1R are rotatably supported on the left and right ends of the axle unit 11R in the rear portion. The front wheels 1F and 1F and the rear wheels 1R and 1R can rotate around the horizontal axis, respectively.

The left and right ends of each of the front and rear axle units 11F and 11R extend downward. This downwardly extending portion can rotate around the vertical axis. As a result, the front wheels 1F and 1F and the rear wheels 1R and 1R can be steered by four wheels, respectively. In the present embodiment, the "front traveling device" is configured by the combination of the front wheels 1F and 1F and the front axle unit 11F, and the "rear traveling device" is formed by the combination of the rear wheels 1R and 1R and the rear axle unit 11R. It is configured. The front traveling device is provided at the front portion of the airframe frame 10, and the rear traveling device is provided at the rear portion of the airframe frame 10. Further, when the front traveling device and the rear traveling device are collectively referred to as a "traveling device".

On the fuselage frame 10, a driving portion 3 is provided at the front portion, and a boarding portion 4 is provided behind the driving portion 3. The driving unit 3 includes an engine 31 as a power source in a state of being built in the engine bonnet 30. The boarding section 4 includes a cabin 40 in which a driver's seat 41 and a steering wheel 43 for maneuvering operations are incorporated.
The boom unit 20 of the liquid spraying device 2 is connected to the front end of the machine frame 10, and the broad caster 13 (powder granules) capable of spraying powder or granular materials such as chemicals on the rear end of the machine frame 10. (Corresponding to a body spraying device) is connected.

A chemical tank 28 that constitutes the liquid spraying device 2 together with the boom unit 20 is provided on the airframe frame 10 between the cabin 40 and the broad caster 13.
The drug tank 28 is provided adjacent to the rear of the cabin 40. The left and right side portions of the drug tank 28 extend to the left and right side portions in the rear portion of the cabin 40, which are located at the rear portion of the door 40B of the cabin 40 in the side view of the machine body. Therefore, the medicine tank 28 is formed in a U shape in a plan view, and the shape of the medicine tank 28 is formed so as to surround the rear portion of the cabin 40.

〔cabin〕
The cabin 40 is provided behind the engine bonnet 30 and the engine 31, and the cabin 40 is located at the center of the left and right sides of the traveling machine body 1.
A windshield 40A is provided on the front surface of the cabin 40, and a door 40B that can be opened and closed is provided on the left side of the cabin 40. Inside the cabin 40, a boarding space on which the driver can board, that is, a boarding section 4 is formed. The boarding section 4 is provided with a driver's seat 41 and a front panel 42. The driver's seat 41 is provided in the central portion of the traveling machine body 1 and is configured so that the passenger can take a seat. The front panel 42 is provided in the central portion of the traveling machine body 1 and is located in front of the driver's seat 41 and behind the windshield 40A. The engine 31 is provided on the front side of the airframe with respect to the boarding unit 4, and is mounted and supported on the airframe frame 10. In this specification, the "passenger" and the "driver" are mixed, but the "passenger" and the "driver" may be the same person.

The front panel 42 is provided with a steering handle 43 and various operating tools such as a main speed change lever (not shown). The steering handle 43 is provided on the front portion of the boarding unit 4 and is configured to enable maneuvering operations of the front wheels 1F and 1F and the rear wheels 1R and 1R by artificial operation. The forward / backward movement switching operation and the traveling speed change operation of the traveling machine body 1 can be performed by, for example, the operation of the main shift lever or the like, and the boom unit 20 and the broad caster 13 can be operated by various operating tools provided on the front panel 42 or the like. It is possible.

A deck portion 44 is provided on the left side of the fuselage with respect to the door 40B, and the boarding / alighting step 45 extends downward from the rear portion of the deck portion 44 on the lateral outer side of the fuselage. In other words, the boarding / alighting step 45 is provided on the left side of the boarding section 4 and extends downward. Although not described in detail, a sliding mechanism is provided at the front portion of the door 40B, and the door 40B is configured to be slidable in the front-rear direction. The door 40B is configured to be switchable between a closed state in which the left side surface of the boarding unit 4 is closed and an open state in which the left side surface of the boarding unit 4 is opened. When the closed door 40B slides forward, the door 40B is switched to the open state, and when the open door 40B slides backward, the door 40B is switched to the closed state. The passenger can enter the boarding section 4 by climbing the boarding / alighting step 45, standing at the rear of the deck section 44, and opening the door 40B (switching to the open state).

[Liquid sprayer]
The boom unit 20 has a center boom 21 and a pair of left and right side booms 22L and 22R. The boom unit 20 is supported by the front end portion of the airframe frame 10 via the elevating link mechanism 19 and the rolling mechanism 18.
The elevating link mechanism 19 has a first hydraulic cylinder 23 that faces up and down. The first hydraulic cylinder 23 is a single rod type cylinder in which the piston rod is located below the first hydraulic cylinder 23. The elevating link mechanism 19 is configured to be able to move up and down by the expansion and contraction operation of the first hydraulic cylinder 23.

The rolling mechanism 18 is supported by the free end portion of the elevating link mechanism 19, and the center boom 21 and the pair of side booms 22L and 22R are supported by the rolling mechanism 18. The longitudinal direction of the center boom 21 is arranged sideways on the machine body. The left and right side booms 22L and 22R are pivotally supported at both ends in the longitudinal direction of the center boom 21. Second hydraulic cylinders 24L and 24R are provided at the pivotal support points at both ends of the center boom 21 in the longitudinal direction.
The second hydraulic cylinders 24L and 24R are connected to the longitudinal end of the center boom 21 and the left and right side booms 22L and 22R pivotally connected to the end, and these second hydraulic cylinders 24L are connected. The left and right side booms 22L and 22R can be swung by the expansion and contraction operation of 24R.

When the second hydraulic cylinder 24L is extended, the side boom 22L extends laterally to the same direction as the center boom 21. In this case, the side boom 22L extends laterally and laterally from the traveling machine body 1. When the second hydraulic cylinder 24L contracts, the side boom 22L is folded in a state of being inclined backward. Similar to the case of the side boom 22L, the side boom 22R extends laterally when the second hydraulic cylinder 24R extends. Further, when the second hydraulic cylinder 24R contracts, the side boom 22R is folded in a state of being inclined backward. The side booms 22L and 22R are tilted upward, and the free end of the side booms 22L and 22R is located at a position corresponding to the rear end of the traveling machine body 1 in the front-rear direction, and the cabin 40 is located in the vertical direction. It is located below the top edge.

Each of the center boom 21 and the pair of side booms 22L and 22R is provided with a drug supply pipe 25 along the longitudinal direction, and the drug supply pipe 25 is provided with a large number of spray nozzles 26. Further, a spraying pump 27 (see FIG. 1 and the like) is supported below the driver's seat 41 in the machine frame 10. The spraying pump 27 is configured to be able to discharge the liquid drug stored in the drug tank 28 toward the drug supply pipe 25.

When spraying the chemicals, the passenger extends the pair of left and right side booms 22L and 22R sideways to drive the spraying pump 27 based on the power of the engine 31. As a result, the liquid drug stored in the drug tank 28 is sprayed from a large number of spray nozzles 26 through the drug supply pipe 25. The spraying pump 27 is configured to be able to spray drive the boom unit 20 as the liquid spraying device 2. In this state, the traveling machine 1 travels in the field by the rotational drive of the front wheels 1F, 1F and the rear wheels 1R, 1R, and the chemicals are sprayed on the field.

Further, when the chemical is not sprayed, the passenger folds the pair of left and right side booms 22L and 22R in the rearward upward direction. As a result, when the boom sprayer runs on a farm road or is parked in a barn for storage, the possibility that the free end portions of the side booms 22L and 22R come into contact with other objects is reduced.

[Granular material spraying device]
The broadcaster 13 disperses the accommodating hopper 13A for accommodating powders and granules such as chemicals and the powders and granules supplied from the bottom of the accommodating hopper 13A in the circumferential direction and sprays them on the field of the passage trace of the traveling machine 1. It is equipped with a mechanism 13B.
As shown in FIGS. 1 to 4, the accommodating hopper 13A and the spraying mechanism 13B are supported by a support frame body 12 extending rearward from the rear end portion of the machine body frame 10. The housing hopper 13A is formed in a funnel shape with the upper side open.

[Transmission device]
As shown in FIGS. 1 and 3, the transmission 32 is supported at a position corresponding to the lower part of the cabin 40 in the airframe frame 10. The power of the engine 31 is distributed to the front and rear axle units 11F and 11R via the transmission 32, and is transmitted to the front wheels 1F and 1F and the rear wheels 1R and 1R, respectively. That is, the transmission 32 is arranged between the front traveling device and the rear traveling device in the plan view and the side view.
The transmission 32 is located between a pair of left and right mainframes 10A and 10A along the front-rear direction. The main frames 10A and 10A are supported by the airframe frame 10 in a state in which the lower portion does not project above the upper edges of the main frames 10A and 10A and the lower portion projects below the lower edges of the main frames 10A and 10A.
A fuel tank 14 is provided on the right side of the mainframes 10A and 10A, and a battery 17 is provided on the left side of the mainframes 10A and 10A.

The transmission 32 includes a hydrostatic continuously variable transmission 33 having a pair of hydraulic pumps (not shown) and a hydraulic motor (not shown), and a plurality of transmission gear pairs to form a transmission. A transmission case 34, which houses a group 35 (corresponding to a gear transmission mechanism), is provided.
The transmission case 34 shifts the shifting power output from the hydrostatic continuously variable transmission 33 to a predetermined shifting stage by the internal shifting gear group 35 and outputs the shifting power. Specific output targets include a traveling system transmission shaft 15 that transmits power to the front and rear axle units 11F and 11R, a spraying pump 27, and a work system transmission shaft that transmits driving force to the broad caster 13 at the rear of the machine body. It is configured to transmit shifting power to the relay shaft 16.
The hydrostatic continuously variable transmission 33 and the transmission case 34 are connected and fixed in the front-rear direction, and the hydrostatic continuously variable transmission 33 is provided so as to be located on the left front side of the front portion of the transmission 32. ..

[About power transmission structure]
As shown in FIGS. 3 to 5, the transmission 32 is supported by the airframe frame 10 in a state of being located below the airframe frame 10. The airframe frame 10 has a pair of left and right main frames 10A and 10A along the front-rear direction and a horizontal frame 10W. The longitudinal direction of the pair of left and right mainframes 10A and 10A is along the front-rear direction of the machine body. That is, the pair of left and right main frames 10A and 10A extend in the front-rear direction of the machine body. Both ends of the horizontal frame 10W are welded and fixed to the main frames 10A and 10A, respectively, and the horizontal frame 10W is horizontally laid over a pair of left and right main frames 10A and 10A. Although not described in detail, a plurality of horizontal frames 10W are provided along the longitudinal direction of the pair of main frames 10A and 10A. The transmission 32 is supported by the main frame 10A and the horizontal frame 10W.

The transmission 32 includes a hydrostatic continuously variable transmission 33 and a transmission case 34 containing a transmission gear group 35 constituting a transmission. The hydrostatic continuously variable transmission 33 and the transmission case are provided. The 34 is connected and fixed in the front-rear direction. A fuel filler port 34a capable of supplying hydraulic oil is provided at the upper end of the transmission case 34.

The hydrostatic continuously variable transmission 33 is provided with a first input shaft 50, a first output shaft 51, and a speed change operation shaft 52. The first input shaft 50 is a pump shaft, and the first output shaft 51 is a motor shaft. By rotating the speed change operation shaft 52, the angle of the swash plate of the hydraulic pump (not shown) of the hydrostatic continuously variable transmission 33 is changed, and the neutral shift state and the forward shift state are changed. The gear is changed to the reverse gear shifting state. The first input shaft 50 extends to the front side and the rear side of the casing of the hydrostatic continuously variable transmission 33, respectively.
The output shaft of the engine 31 and the front end of the first input shaft 50 of the hydrostatic continuously variable transmission 33 are interlocked and connected by a power transmission belt 53. The power of the engine 31 is input to the hydrostatic continuously variable transmission 33 by the power transmission belt 53.

The transmission case 34 includes a front housing 34U and a rear housing 34V. A space is formed inside the transmission case 34 by coupling the rear end surface of the front housing 34U and the front end surface of the rear housing 34V via an oil seal (not shown). That is, the transmission case 34 has an internal space covered by the front housing 34U and the rear housing 34V. In the internal space of the transmission case 34, an auxiliary transmission mechanism 60 as a "travel transmission mechanism" and a work transmission mechanism 70 as a "work transmission mechanism" are provided (see FIG. 6). The auxiliary transmission mechanism 60 is located in the lower part of the internal space, and the work transmission mechanism 70 is located in the upper part of the internal space. That is, in the internal space, the work transmission mechanism 70 as the work transmission mechanism and the auxiliary transmission mechanism 60 as the traveling transmission mechanism are vertically distributed and arranged.

The auxiliary transmission mechanism 60 is provided with a traveling input shaft 61, and the first output shaft 51 of the hydrostatic continuously variable transmission 33 extends to the rear side of the casing of the hydrostatic continuously variable transmission 33. Then, the traveling input shaft 61 and the first output shaft 51 are connected to each other along the rotation shaft core of the first output shaft 51 so as to be relatively non-rotatable by spline engagement. That is, the traveling input shaft 61 is integrally connected to the first output shaft 51 in the direction of the rotation shaft core. Further, the first input shaft 50 of the hydrostatic continuously variable transmission 33 extends to the rear side of the casing of the hydrostatic continuously variable transmission 33, and the work input shaft 71 is provided in the work speed change mechanism 70. Then, the working input shaft 71 and the first input shaft 50 are connected to each other along the rotation shaft core of the first input shaft 50 so as to be relatively non-rotatable by spline engagement. That is, the work input shaft 71 is integrally connected to the first input shaft 50 in the direction of the rotation shaft core.

The power output from the engine 31 is divided into running power and working power by the first input shaft 50 and the first output shaft 51 in the hydrostatic continuously variable transmission 33. The traveling power is input to the traveling auxiliary transmission mechanism 60, and is output from the auxiliary transmission mechanism 60 toward the front wheels 1F and the rear wheels 1R. The work power is input to the work transmission mechanism 70, and is output from the work transmission mechanism 70 toward the spraying pump 27, the broadcaster 13, and the like.

As shown in FIGS. 3 and 4, a spraying pump 27 is provided above the working output shaft 74. A pulley is provided at the rear end of the work output shaft 74 of the work transmission mechanism 70 in the longitudinal direction, and the transmission belt 27B is wound around this pulley. That is, pulleys are provided on the work output shaft 74 and the input shaft of the spraying pump 27, respectively, and the transmission belt 27B is wound around these pulleys. Then, the working power is transmitted from the working output shaft 74 to the spraying pump 27 via the transmission belt 27B. Further, a relay shaft 16 (corresponding to a work system transmission shaft) having a universal joint is provided at the rear end of the work output shaft 74, and the relay shaft 16 extends back and forth between the pair of mainframes 10A and 10A. The front end of the relay shaft 16 is connected to the rear end of the work output shaft 74 via a universal joint, and the rear end of the relay shaft 16 is connected to the input shaft of the broadcaster 13. In short, a relay shaft 16 capable of transmitting power to a work device other than the liquid spraying device is connected to the protruding tip of the work output shaft 74.

[About the shifting mechanism for running]
As shown in FIGS. 6 and 7, the traveling auxiliary transmission mechanism 60 includes a traveling input shaft 61, a first intermediate shaft 62 as a “traveling transmission shaft”, a second intermediate shaft 63, and a second intermediate shaft 63. The three intermediate shafts 64 and the traveling output shaft 65 are provided. The traveling input shaft 61, the first intermediate shaft 62, the second intermediate shaft 63, the third intermediate shaft 64, and the traveling output shaft 65 are respectively connected to the front housing 34U and the rear housing via ball bearings. Both are supported by 34V. A plurality of traveling drive gears are provided on these shafts, and power is transmitted by the meshing of these traveling drive gears. In addition, although each axis from the traveling input shaft 61 to the traveling output shaft 65 is arranged side by side in FIG. 7, FIG. 7 is shown as a developed view so that each of these axes can be easily seen. In fact, each of these axes is arranged as shown in FIG.

The traveling input shaft 61 is provided with a small diameter gear 61A, and the small diameter gear 61A rotates integrally with the traveling input shaft 61 around the rotation shaft core of the traveling input shaft 61. The small diameter gear 61A cannot rotate relative to the traveling input shaft 61. The first intermediate shaft 62 is provided with a large-diameter gear 62A, and the large-diameter gear 62A rotates integrally with the first intermediate shaft 62 around the center of the rotation shaft of the first intermediate shaft 62. The large diameter gear 62A cannot rotate relative to the first intermediate shaft 62. The small diameter gear 61A and the large diameter gear 62A are included in the traveling drive gear. The small diameter gear 61A and the large diameter gear 62A are engaged with each other, and the diameter of the large diameter gear 62A is larger than the diameter of the small diameter gear 61A. Therefore, the rotation speed based on the traveling power is reduced by the first intermediate shaft 62.

A spline portion is formed on the first intermediate shaft 62, and the shift gear 62B is fitted onto the spline portion. The shift gear 62B rotates integrally with the first intermediate shaft 62 around the center of the rotation shaft of the first intermediate shaft 62. The shift gear 62B cannot rotate relative to the first intermediate shaft 62, and can slide along the rotation axis direction of the first intermediate shaft 62 within the range of the spline portion of the first intermediate shaft 62. The shift gear 62B has a plurality of traveling transmission gears capable of shifting the rotational power of the traveling input shaft 61. That is, the shift gear 62B is provided with three gears, a first gear portion 62c, a second gear portion 62d, and a third gear portion 62e, as a plurality of traveling transmission gears, and the diameters of the respective gears are different. The diameter of the second gear portion 62d is larger than the diameter of the third gear portion 62e, and the diameter of the first gear portion 62c is larger than the diameter of the second gear portion 62d. The first gear 63A is arranged adjacent to each of the small diameter gear 61A and the large diameter gear 62A on the rear side, and interference between the large diameter gear 62A and the shift gear 62B is avoided.

Three gears, a first gear 63A, a second gear 63B, and a third gear 63C, are provided side by side along the rotating shaft core of the second intermediate shaft 63 on the second intermediate shaft 63, and each gear is provided. The diameter of is different.
The diameter of the second gear 63B is smaller than the diameter of the third gear 63C, and the diameter of the first gear 63A is smaller than the diameter of the second gear 63B. The first gear 63A, the second gear 63B, and the third gear 63C each rotate integrally with the second intermediate shaft 63 around the center of the rotation shaft of the second intermediate shaft 63 with respect to the second intermediate shaft 63. Relative rotation is not possible.

The shift gear 62B is slidably operated via the traveling shift fork 62F. The traveling shift fork 62F is configured so that the number of gears on the first intermediate shaft 62 as a traveling transmission gear can be switched. One end of the traveling shift fork 62F projects from the front housing 34U and the rear housing 34V as the housing case to the side opposite to the side where the engine 31 is located, that is, to the rear side of the machine body. By engaging the first gear portion 62c on the large diameter side of the shift gear 62B and the first gear 63A on the small diameter side of the second intermediate shaft 63, the shifting state of the auxiliary transmission mechanism 60 becomes a high-speed shifting state. .. Further, the second gear portion 62d of the shift gear 62B and the second gear 63B of the second intermediate shaft 63 are engaged with each other, so that the shift state of the auxiliary transmission mechanism 60 becomes a medium speed shift state. Further, by engaging the third gear portion 62e on the small diameter side of the shift gear 62B and the third gear 63C on the large diameter side of the second intermediate shaft 63, the shifting state of the auxiliary transmission mechanism 60 is changed to a low speed shifting state. become. The rotation speed of the second intermediate shaft 63 in the low speed shifting state is slower than the rotation speed of the second intermediate shaft 63 in the medium speed shifting state. The rotation speed of the second intermediate shaft 63 in the medium speed shifting state is slower than the rotation speed of the second intermediate shaft 63 in the high speed shifting state. As described above, the three gears of the first gear 63A, the second gear 63B, and the third gear 63C are for traveling on the lower side than the traveling transmission gear among the plurality of traveling drive gears described above. It is a drive gear. The first intermediate shaft 62 as the traveling transmission shaft has a plurality of traveling transmission gears and is configured to be able to transmit power to the traveling drive gear on the lower side.

Of the second intermediate shaft 63, a small diameter gear 63D is provided between the second gear 63B and the third gear 63C, and the small diameter gear 63D is integrated with the second intermediate shaft 63 around the rotating shaft core of the second intermediate shaft 63. It rotates and cannot rotate relative to the second intermediate shaft 63. Further, a large diameter gear 64A is provided on the third intermediate shaft 64, and the large diameter gear 64A rotates integrally with the third intermediate shaft 64 around the center of the rotation shaft of the third intermediate shaft 64 with respect to the third intermediate shaft 64. Relative rotation is not possible. The small diameter gear 63D and the large diameter gear 64A are included in the traveling drive gear. The small diameter gear 63D and the large diameter gear 64A are engaged with each other, and the diameter of the large diameter gear 64A is larger than the diameter of the small diameter gear 63D. Therefore, the rotation speed of the second intermediate shaft 63 is reduced by the third intermediate shaft 64.
A small diameter gear 64B is provided on the third intermediate shaft 64, and the small diameter gear 64B rotates integrally with the third intermediate shaft 64 around the rotation shaft core of the third intermediate shaft 64 and cannot rotate relative to the third intermediate shaft 64. is there.
Further, a large-diameter gear 65A is provided on the traveling output shaft 65, and the large-diameter gear 65A rotates integrally with the traveling output shaft 65 around the center of the rotating shaft of the traveling output shaft 65 with respect to the traveling output shaft 65. Relative rotation is not possible. The small diameter gear 64B and the large diameter gear 65A are included in the traveling drive gear. The small diameter gear 64B and the large diameter gear 65A are engaged with each other, and the diameter of the large diameter gear 65A is larger than the diameter of the small diameter gear 64B. Therefore, the rotation speed of the third intermediate shaft 64 is reduced by the traveling output shaft 65. The traveling output shaft 65 projects outward from the front housing 34U and the rear housing 34V as the housing case, and can transmit the power shifted by the first intermediate shaft 62 as the traveling transmission shaft to the above-mentioned traveling device. It is configured in.

As described above, the traveling power passes through the shifting by the shift gear 62B and the deceleration in the process of power transmission between the traveling input shaft 61, the first intermediate shaft 62, the second intermediate shaft 63, and the third intermediate shaft 64. It is transmitted to the traveling output shaft 65. A traveling system transmission shaft 15 is connected to both ends of the traveling output shaft 65 in the longitudinal direction so as to be relatively non-rotatable by spline engagement along the rotating shaft core of the traveling output shaft 65. Then, the traveling output shaft 65 projects to the front side and the rear side of the transmission 32, and is coupled to the traveling system transmission shaft 15 to extend to the front traveling device and the rear traveling device, respectively.

A multi-plate type friction brake 66 is mounted on the traveling output shaft 65. By setting the friction brake 66 in the engaged state, the rotation of the traveling output shaft 65 can be restrained.

[About the work transmission mechanism]
As shown in FIGS. 6 and 8, the work transmission mechanism 70 is provided with a work input shaft 71, a work clutch shaft 72, an intermediate cylinder shaft 73, and a work output shaft 74. The work input shaft 71, the work clutch shaft 72, the intermediate cylinder shaft 73, and the work output shaft 74 are both held by the front housing 34U and the rear housing 34V via ball bearings 37, respectively. Be supported. A plurality of working drive gears are provided on these shafts, and power is transmitted by the meshing of these working drive gears. In FIG. 8, each axis from the work input shaft 71 to the work output shaft 74 is arranged side by side in the vertical direction, but FIG. 8 is shown as a developed view so that each of these axes can be easily seen. In fact, each of these axes is arranged as shown in FIG.

The work input shaft 71 is provided with a small diameter gear 71A, and the small diameter gear 71A rotates integrally with the work input shaft 71 around the rotation shaft core of the work input shaft 71. The small diameter gear 71A cannot rotate relative to the working input shaft 71. The work clutch shaft 72 is provided with a large diameter gear 72A, and the large diameter gear 72A rotates around the center of the rotation shaft of the work clutch shaft 72. The large-diameter gear 72A is fitted onto the working clutch shaft 72 via the needle bearing 72f and is rotatable relative to the working clutch shaft 72. The small diameter gear 71A and the large diameter gear 72A are included in the working drive gear. The small diameter gear 71A and the large diameter gear 72A are engaged with each other, and the diameter of the large diameter gear 72A is larger than the diameter of the small diameter gear 71A. Therefore, the rotation speed based on the working power is reduced by the working clutch shaft 72. A small diameter gear 72B is provided on the work clutch shaft 72, and the small diameter gear 72B rotates integrally with the work clutch shaft 72 around the center of the rotation shaft of the work clutch shaft 72 and cannot rotate relative to the work clutch shaft 72. is there.

FIG. 13 shows a claw clutch 72C and a work clutch operating fork 72D on the work clutch shaft 72. A spline portion is formed on the working clutch shaft 72, and the claw clutch 72C is fitted onto the spline portion. The claw clutch 72C rotates integrally with the work clutch shaft 72 around the center of the rotation shaft of the work clutch shaft 72. The claw clutch 72C cannot rotate relative to the work clutch shaft 72, and can slide along the rotation axis direction of the work clutch shaft 72 within the range of the spline portion of the work clutch shaft 72. The claw clutch 72C is slidably operated via the working clutch operating fork 72D.

One end of the working clutch operating fork 72D projects from the front housing 34U and the rear housing 34V as the housing case to the side opposite to the side where the engine 31 is located, that is, to the rear side of the machine body. The working clutch operating fork 72D is supported by a support hole 34b of the front housing 34U and a boss hole 34c of the rear housing 34V. The support hole 34b projects toward the rear of the fuselage with respect to the surrounding front wall surface of the front housing 34U. Therefore, the front end portion of the working clutch operating fork 72D is held in a state of being inserted into the support hole 34b regardless of the front and rear slides of the working clutch operating fork 72D. As described above, the working clutch operation fork 72D is supported by the wall on one end side of the housing case and the wall on the other end side of the housing case.

Engaging uneven surfaces are formed on the surfaces of the claw clutch 72C and the large-diameter gear 72A on opposite sides, and these engaging uneven surfaces engage with each other to engage the large-diameter gear 72A and the work clutch shaft 72. And rotate integrally. From this, when the engaging uneven surfaces of the claw clutch 72C and the large diameter gear 72A are engaged with each other, the work power input to the work input shaft 71 is transmitted to the work clutch shaft via the large diameter gear 72A. It is transmitted to 72. In this way, the claw clutch 72C transmits the work power to the transmission lower side shaft after the work clutch shaft 72 and the work power to the transmission lower side shaft after the work clutch shaft 72. It is configured to be switchable between the non-transmission state and the non-transmission state. In other words, the work clutch shaft 72 has a transmission state in which the rotational power of the work input shaft 71 is transmitted to the work output shaft 74 and a non-transmission state in which the rotational power of the work input shaft 71 is not transmitted to the work output shaft 74. It is configured to be switchable between states and. Further, the work clutch operation fork 72D is configured so that the work clutch shaft 72 can be switched between a transmission state and a non-transmission state.

A coil spring 72E fits outside the work clutch shaft 72 between the small diameter gear 72B and the claw clutch 72C of the work clutch shaft 72. The coil spring 72E is urged to slide the claw clutch 72C toward the side where the large diameter gear 72A is located. That is, when the claw clutch 72C is switched to the non-transmission state, the working clutch operating fork 72D is slid against the urging force of the coil spring 72E.

As shown in FIGS. 6 and 8, a large-diameter gear 73A is provided on the intermediate cylinder shaft 73, and the small-diameter gear 72B and the large-diameter gear 73A engage with each other. The diameter of the large diameter gear 73A is larger than the diameter of the small diameter gear 72B. Therefore, the rotation speed of the working clutch shaft 72 is reduced by the intermediate cylinder shaft 73. The small diameter gear 72B and the large diameter gear 73A are included in the working drive gear.

The intermediate cylinder shaft 73 is a shaft capable of transmitting the rotational power of the work input shaft 71 to the work output shaft 74, and the intermediate cylinder shaft 73 is fitted so as to be rotatable relative to the work input shaft 71. .. Although not shown, a pair of needle bearings 71b and 71b are provided at both ends in the longitudinal direction of the region where the intermediate cylinder shaft 73 fits out of the work input shaft 71, and the pair of needle bearings 71b and 71b are the work input shafts. It is integrally configured with 71. Both ends of the intermediate cylinder shaft 73 in the longitudinal direction are supported by a pair of needle bearings 71b, 71b on the working input shaft 71. As a result, the double shaft is formed by the work input shaft 71 and the intermediate cylinder shaft 73. Of the intermediate cylinder shaft 73, two gears, a first gear 73B and a second gear 73C, are provided side by side along the rotation shaft core of the intermediate cylinder shaft 73 on the rear side of the machine body with respect to the large diameter gear 73A. .. The diameter of the first gear 73B is larger than the diameter of the second gear 73C. The large-diameter gear 73A, the first gear 73B, and the second gear 73C each rotate integrally with the intermediate cylinder shaft 73 around the center of the rotation shaft of the intermediate cylinder shaft 73, and cannot rotate relative to the intermediate cylinder shaft 73. Is.

A drill hole 73d is formed on the outer peripheral surface of the intermediate tubular shaft 73. Lubricating oil, that is, hydraulic oil stored in the hydraulic oil storage portion 11C enters through the drill hole 73d, and an oil film of hydraulic oil is attached between the intermediate cylinder shaft 73 and the working input shaft 71. This hydraulic oil also spreads to the pair of needle bearings 71b, 71b in the working input shaft 71. As a result, the intermediate cylinder shaft 73 and the work input shaft 71 can rotate smoothly without friction between the intermediate cylinder shaft 73 and the work input shaft 71. That is, the intermediate cylinder shaft 73 is provided on the work input shaft 71 and is configured to be able to supply lubricating oil to the bearing supporting the intermediate cylinder shaft 73 via the drill hole 73d.

The work output shaft 74 projects from the front housing 34U and the rear housing 34V as the housing case to the side opposite to the side where the engine 31 is located, that is, to the rear side of the machine body, and also powers the spraying pump 27 and the broad caster 13. It is configured to be communicable. A spline portion is formed on the work output shaft 74, and the shift gear 74A is fitted onto the spline portion. The shift gear 74A rotates integrally with the work output shaft 74 around the center of the rotation shaft of the work output shaft 74. The shift gear 74A cannot rotate relative to the work output shaft 74, and can slide along the rotation axis direction of the work output shaft 74 within the range of the spline portion of the work output shaft 74.

The shift gear 74A has a plurality of work transmission gears capable of shifting the rotational power of the work input shaft 71. That is, the shift gear 74A is provided with two gears, a first gear portion 74c and a second gear portion 74d, as a plurality of work transmission gears. The diameter of the first gear portion 74c is smaller than the diameter of the second gear portion 74d. Each of the first gear 73B and the second gear 73C is arranged on the rear side of the large diameter gear 73A, and interference between the large diameter gear 73A and the shift gear 74A is avoided.

The shift gear 74A is slidably operated via the work shift fork 74E. The work shift fork 74E is configured so that the number of gears in the work transmission gear can be switched. One end of the work shift fork 74E projects from the front housing 34U and the rear housing 34V as the housing case to the side opposite to the side where the engine 31 is located, that is, to the rear side of the machine body. By engaging the first gear portion 74c on the small diameter side of the shift gear 74A and the first gear 73B on the large diameter side of the intermediate cylinder shaft 73, the shifting state of the working transmission mechanism 70 becomes a high-speed shifting state. .. Further, by engaging the second gear portion 74d on the large diameter side of the shift gear 74A and the second gear 73C on the small diameter side of the intermediate cylinder shaft 73, the shifting state of the working transmission mechanism 70 is changed to a low speed shifting state. become. The rotation speed of the intermediate cylinder shaft 73 in the low speed shifting state is slower than the rotation speed of the intermediate cylinder shaft 73 in the high speed shifting state.

In this way, the work power is transmitted to the work output shaft 74 through the shift by the shift gear 74A and the deceleration in the process of power transmission between the work input shaft 71, the work clutch shaft 72 and the intermediate cylinder shaft 73. Will be done.

In the rear housing 34V, the second output boss portion 34d is formed at a through portion of the rotating shaft core of the working output shaft 74. The second output boss portion 34d is formed in a tubular shape so that the working output shaft 74 can be inserted, and a ball bearing 75 is arranged at the protruding rear end of the second output boss portion 34d. The rear portion of the working output shaft 74 is supported by the ball bearing 75. Of the rear housing 34V, the second output boss portion 34d projects toward the rear side of the fuselage with respect to the rear surface around the second output boss portion 34d.

[Hydraulic oil storage part of transmission mechanism]
The hydraulic oil is stored in the transmission case 34 of the transmission 32, and the hydraulic oil is used to operate the first hydraulic cylinder 23 and the second hydraulic cylinders 24L and 24R in the boom unit 9. The transmission gear accommodating space S1 is used as a storage space for hydraulic oil. In the present embodiment, the front housing 34U and the rear housing 34V are coupled to form an internal space, and this internal space is used as a transmission gear accommodating space S1 and as a storage space for hydraulic oil. In order to make the transmission gear accommodating space S1 as wide as possible, the gears in each transmission shaft are arranged near the front and rear ends of the transmission case 34.

In the auxiliary transmission mechanism 60, each of the small diameter gear 61A and the large diameter gear 62A is arranged in the front end region of the transmission gear accommodating space S1 and approaches the front wall of the front housing 34U. The first gear 63A is arranged adjacent to the front end region of the transmission gear accommodating space S1 on the rear side of each of the small diameter gear 61A and the large diameter gear 62A.

Each of the small diameter gear 64B and the large diameter gear 65A is arranged in the rear end region of the transmission gear accommodating space S1 and approaches the rear wall of the rear housing 34V. In the rear end region of the transmission gear accommodating space S1, the third gear 63C, the third intermediate shaft 64, and the second gear 63B are arranged in order from the rear side to the front side of the small diameter gear 64B and the large diameter gear 65A, respectively. Be placed.

In the working transmission mechanism 70, each of the small diameter gear 71A and the large diameter gear 72A is arranged in the rear end region of the transmission gear accommodating space S1 and approaches the rear wall of the rear housing 34V. Further, each of the small diameter gear 72B and the large diameter gear 73A is arranged in the front end region of the transmission gear accommodating space S1 and approaches the front wall of the front housing 34U. The first gear 73B is arranged adjacent to the rear end region of the transmission gear accommodating space S1 with respect to the large diameter gear 73A. Further, the second gear 73C is arranged adjacent to the rear end region of the transmission gear accommodating space S1 on the front side of the small diameter gear 71A.

As described above, each of the plurality of traveling drive gears and each of the plurality of working drive gears are one end side and the other end side of the internal space formed by the coupling of the front housing 34U and the rear housing 34V. It is arranged so as to be biased toward each side. That is, the transmission gear accommodating space S1 is secured in a wide volume in the front-rear central region of the internal space in the transmission case 34 by the configuration in which the gears on the respective transmission shafts are distributed and arranged in the front-rear direction.

Further, the reduction ratio between the small diameter gear 61A and the large diameter gear 62A is set large, and the rotation speed of the first intermediate shaft 62 is reduced to half or less of the rotation speed of the traveling input shaft 61. That is, deceleration is performed at the transmission stage between the traveling input shaft 61 and the first intermediate shaft 62 before the shift gear 62B shifts the gear. In other words, the traveling input shaft 61 and the first intermediate shaft 62 as the traveling transmission shaft are each provided with a pre-shift transmission gear as a traveling drive gear that meshes with each other, and serves as a pre-shift transmission gear. A small diameter gear 61A and a large diameter gear 62A are provided. The diameter of the large-diameter gear 62A on the first intermediate shaft 62 as the traveling speed change shaft is formed to be larger than the diameter of the small-diameter gear 61A on the traveling input shaft 61. The gear of the traveling input shaft 61 is only the small diameter gear 61A, and a plurality of gears are provided on the first intermediate shaft 62. Due to the configuration in which the rotation speed of the first intermediate shaft 62 is reduced, the friction between the plurality of gears on the first intermediate shaft 62 and the hydraulic oil is suppressed, the oil temperature of the hydraulic oil rises, and the viscosity of the hydraulic oil accompanying this is suppressed. And is suppressed. As a result, leakage of the hydraulic oil due to a decrease in the viscosity of the hydraulic oil is suppressed in the gap between the cylinder and the piston in the first hydraulic cylinder 23 and the second hydraulic cylinders 24L and 24R.

[Breazer device]
As shown in FIG. 9, the transmission case 34 includes a transmission gear accommodating space S1 in which a transmission gear group 35 or the like having a plurality of transmission gear pairs is installed, and a breather discharge space in which the transmission gears such as the transmission gear group 35 do not exist. S2 (corresponding to another space) is formed in a state of being partitioned by a partition wall portion 36.
A ball bearing 37 (corresponding to a shaft body extending between the transmission gear accommodating space S1 and another space) rotatably and pivotally supported on the partition wall 36 is a work output shaft 74 (corresponding to a shaft body extending between the transmission gear accommodating space S1 and another space) arranged at the uppermost position of the transmission case 34. (Corresponding to a bearing that also serves as a defoaming means) is installed.
As a result, the transmission gear accommodating space S1 and the breather discharge space S2 can communicate with each other via the ball bearing 37. As a result, when the internal pressure in the transmission gear accommodating space S1 increases, the lubricating oil in the transmission gear accommodating space S1 can enter the breather discharge space S2 via the ball bearing 37.

To add an explanation, a mounting hole for mounting the ball bearing 37 is formed in the partition wall portion 36, the ball bearing 37 is press-fitted into the mounting hole, and the working output shaft 74 is fitted into the ball bearing 37. .. In this state, the transmission gear accommodating space S1 and the breather discharge space S2 are in a state of communicating with each other with the partition wall portion 36 interposed therebetween through a slight gap between the steel balls constituting the ball bearing 37. That is, the location of the ball bearing 37 functions as a breather introduction path that enables the communication of the lubricating oil from the transmission gear accommodating space S1 to the breather discharge space S2, and the ball bearing as a defoaming means is provided in this breather introduction path. 37 is provided, and when the lubricating oil tries to pass through a slight gap between the steel balls of the ball bearing 37, the bubbles in the lubricating oil are compressed or come into contact with the rotating steel balls to be destroyed. It becomes easy to be done. That is, it will be defoamed.

The breather pipe 80 as the breather device 8 is provided so as to communicate with the breather discharge space S2 at a position one step lower than the uppermost level H1 of the transmission case 34 and near the uppermost position of the breather discharge space S2.
Therefore, even if a large number of bubbles are generated in the lubricating oil in the transmission gear accommodating space S1 due to the stirring action of the transmission gear group 35, the lubricating oil containing the bubbles passes through the gap of the rotating ball bearing 37 and the breather. When entering the discharge space S2, the ball bearing 37 undergoes a defoaming action. As a result, the number of air bubbles in the lubricating oil that has entered the breather discharge space S2 can be reduced as much as possible, and the ejection of the lubricating oil containing air bubbles from the breather pipe 80 can be suppressed.

[Another Embodiment]
Hereinafter, another embodiment will be described. Each of the following separate embodiments may be applied to the above embodiment in combination as long as there is no contradiction. The scope of the present invention is not limited to the contents of these embodiments.

(1) In the above-described embodiment, the front wheels 1F and 1F and the rear wheels 1R and 1R are shown as traveling devices, but either one of the front traveling device or the rear traveling device, or the entire traveling device is a crawler. It may be an expression.
For other configurations, the same configurations as those in the above-described embodiment may be adopted.

(2) In the above embodiment, the boarding unit 4 has a structure provided with a cabin 40, but the present invention is not limited to this, and for example, a structure having a canopy or no cover is provided. It doesn't matter if it is a thing.
For other configurations, the same configurations as those in the above-described embodiment may be adopted.

(3) In the above-described embodiment, the transmission 32 is composed of a combination of a hydrostatic continuously variable transmission 33 and a transmission case 34 including a transmission gear group 35 having a plurality of transmission gear pairs. Although the above is illustrated, the structure may be combined with a planetary gear mechanism (not shown), a continuously variable transmission mechanism such as a belt transmission mechanism, or an engine without using the hydrostatic continuously variable transmission 33. The structure may be such that the power is directly introduced into the transmission case 34.
For other configurations, the same configurations as those in the above-described embodiment may be adopted.

(4) In the above-described embodiment, as the defoaming means, a ball bearing 37 that supports the work output shaft 74, which is a shaft body extending over the transmission gear accommodating space S1 and the breather discharge space S2 as a separate space, is used. Although examples have been given, the structure is not necessarily limited to this structure.
For example, the bearing is not limited to the ball bearing 37, and a needle bearing (not shown) may be adopted. Further, the present invention is not limited to the bearing, and a wire mesh or a perforated plate having a mesh structure that easily bursts air bubbles in the lubricating oil may be used as the defoaming means.
For other configurations, the same configurations as those in the above-described embodiment may be adopted.

The present invention is applicable not only to a riding work machine equipped with a liquid spraying device or a powder or granular material spraying device, but also to various riding working machines equipped with a working device capable of working on agricultural products in a field.

1F, 1R Traveling device 2 Working device 8 Breathering device 10 Aircraft frame 16 Relay shaft 27 Spraying pump 27B Transmission belt 31 Motor 32 Transmission 33 Static hydraulic stepless transmission 34 Transmission case 35 Gear transmission mechanism 36 Partition 37 Means 50 1st input shaft 51 1st output shaft 60 Traveling speed change mechanism 70 Work transmission mechanism 71 Work input shaft 73 Intermediate cylinder shaft 73d Drill hole 74 Work output shaft S1 Transmission gear accommodation space S2 Separate space (breather discharge space) )

Claims (10)

Inside the transmission case, there is a transmission gear accommodation space inside the gear transmission mechanism,
A separate space partitioned via a partition wall with respect to the transmission gear accommodating space is provided.
A breather device that communicates with the outside air is provided in the separate space.
In the breather introduction path that enables the communication of lubricating oil from the transmission gear accommodating space to the other space.
A passenger work machine equipped with a defoaming means for eliminating air bubbles contained in the lubricating oil passing through the breather introduction path. The passenger working machine according to claim 1, wherein the defoaming means is a bearing that supports a shaft body that penetrates the partition wall portion and extends over the transmission gear accommodating space and the separate space. The passenger working machine according to claim 1 or 2, wherein the breather device is connected to the separate space at a position lower than the maximum height position of the transmission gear accommodating space. The passenger work machine according to any one of claims 1 to 3, wherein the breather device is provided at the maximum height position in the separate space. Airframe frame and
The prime mover mounted and supported on the airframe frame,
A traveling device provided below the fuselage frame and capable of traveling to the ground based on the power of the prime mover.
A work device that can work on crops in the field,
A transmission that shifts and outputs the power of the prime mover is provided.
The transmission has a hydrostatic continuously variable transmission capable of receiving the power of the prime mover on the first input shaft to shift gears and outputting the power after shifting to the first output shaft.
The gear transmission mechanism incorporated in the transmission case is provided.
A work transmission mechanism capable of transmitting power based on the first input shaft to the work device via a plurality of work drive gears and power based on the first output shaft for a plurality of travelings to the gear transmission mechanism. A traveling transmission mechanism that can be transmitted to the traveling device via a drive gear is provided.
The passenger work machine according to any one of claims 1 to 4, wherein the work transmission mechanism and the traveling transmission mechanism are vertically distributed in the transmission gear accommodating space of the transmission case. The work input shaft integrally connected to the work transmission mechanism in the direction of the rotation axis core and the work input shaft projecting from the transmission case to the side opposite to the position of the prime mover and to the work apparatus. The passenger work machine according to claim 5, further comprising a work output shaft capable of transmitting power. The working device includes a liquid spraying device capable of spraying liquid on crops in the field.
A spraying pump capable of driving the liquid spraying device is provided above the working output shaft.
Pulleys around which a transmission belt is wound are provided on each of the work output shaft and the input shaft of the spraying pump 27.
The passenger work machine according to claim 6, wherein a relay shaft capable of transmitting power to the work device other than the liquid spraying device is connected to a protruding tip of the work output shaft. The passenger work machine according to claim 6 or 7, wherein an intermediate tubular shaft capable of transmitting the rotational power of the work input shaft to the work output shaft is fitted onto the work input shaft. A drill hole is formed on the outer peripheral surface of the intermediate cylinder shaft, and the intermediate cylinder shaft is provided on the work input shaft and can supply lubricating oil to a bearing supporting the intermediate cylinder shaft through the drill hole. The passenger working machine according to claim 8, which is configured. The passenger work machine according to any one of claims 1 to 9, wherein the passenger work machine is a passenger management machine.

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