KR101789133B1 - Riding agricultural machine - Google Patents

Abstract

In the mid-mount type passenger-type reverberation machine in which the engine is disposed at the rear portion of the traveling vehicle, the structure of the traveling gas is simplified and the weight is centered. The traveling vehicle 1 has an engine 18, a traveling mission case 19, and a rear axle case 25. The traveling mission case 19 and the rear axle case 25 are connected by a joint member 32. The engine 18 is supported from the front and rear by the front bracket 48 provided on the joint member 32 and the rear bracket 49 provided on the rear axle case 25. [ The joint member 32 is fixed to the lower portion of the traveling mission case 19, so that the height of the engine 18 can be reduced to achieve a low center of gravity of the traveling vehicle.

Description

{RIDING AGRICULTURAL MACHINE}

BACKGROUND OF THE INVENTION Field of the Invention [0002] The present invention relates to a passenger-type hoisting machine such as a passenger-type reversing machine.

The passenger type rearing machine has a running vehicle supported by front wheels and rear wheels, and a seedling-type unit (seedling-type unit) is arranged behind the running vehicle so as to be adjustable in height. The traveling vehicle is provided with a seat and a steering wheel and an engine mounted thereon, and running and work (for example, a seedling portion) are performed by the power from the engine. More specifically, the power (output) of the engine is transmitted to the transmission having the traveling mission case, a part of the engine output becomes the driving power and is transmitted to the front wheel and the rear wheel, . When equipped with a stabilizing rotor or a fertilizer, these are also driven by the power of the engine.

The passenger type rearing machine is generally of a four-wheel drive type so that power is transmitted from the traveling mission case through the front axle device to the front wheels and from the traveling mission case through the rear axle case. (Front mounted type) in which the engine is disposed in front of the axle of the front wheels and a type in which the engine is disposed between the front and rear wheels (or in the lower part of the seat) (mid-mount type: For example, Patent Document 1 to Patent Document 3).

When the engine is disposed in the front portion of the traveling vehicle, there is a case where the engine / auxiliary machinery, power steering for the steering and the like are arranged in a narrow space. There is an advantage that freedom of design is increased because restrictions on the arrangement of the traveling mission case and the steering mechanism are reduced.

The shape and arrangement of the traveling mission case are closely related to the arrangement of the engine. In Patent Document 1, the traveling mission case is disposed on the rear side of the engine, the rear portion of the engine is supported by the traveling mission case, And is supported by a long support frame.

On the other hand, in the rice making machine of Patent Document 2, the left and right rear axle cases are separated, and power is separately transmitted from the traveling mission case to the left and right rear axle cases. The left and right rear axle cases are fixed to each other via long rolling levers, and a running mission case is disposed in front of the rolling lever. A vertical frame extending rearward is fixed to the rear surface of the traveling mission case, and the rolling lever is connected to the vertical frame so that the rolling lever can be rolled (rotatably). The engine is supported by a vertical frame.

The right and left rear axle cases are separated from each other and the power transmission is separately transmitted from the traveling mission case to the left and right rear axle cases. The left and right rear axle cases are fixed to a transversely long rear frame. The rear frame and the traveling mission case are connected to each other by long left and right main frames in the longitudinal direction, and the engine is supported by the left and right main frames .

By changing the traveling speed and timing of the seedling, the distance between the seedling and the seedling can be adjusted (changed) in a plurality of steps. In the pasting period, ≪ / RTI > The gear group for changing the forbearing distance may be built in a traveling mission case or in a bobbin case disposed outside the traveling mission case. In the latter example, in the case of Patent Document 3, The rear frame, which connects the case, has a boss case fixed. On the other hand, as an example of embedding in a traveling mission case, there is, for example, Patent Document 4.

Japanese Patent Application Laid-Open No. 2006-197942 Japanese Patent No. 2600971 Japanese Patent Application Laid-Open No. 2002-291309 Japanese Patent Application Laid-Open No. 2006-67969

However, since the traveling device of the passive-type agitating operation is provided with the lifting and lowering device arranged at the back thereof, it is preferable that the center of gravity of the traveling device is located as far as possible. However, if the traveling mission case is disposed at the rear of the engine as in Patent Document 1, the center of gravity of the traveling vehicle moves backward as much as it is, and therefore it is not necessarily preferable from the viewpoint of weight balance.

Patent Document 1 discloses a basic structure in which a T-shaped chassis is formed by a front wheel support frame and a support frame extending rearward from the right and left intermediate portions thereof in a plan view and an engine or a traveling mission case is mounted on the chassis , It is worrisome that costs are increased due to a large number of absent points.

On the other hand, in Patent Document 2, since the traveling mission case is disposed in front of the engine, it is excellent in terms of stability, but the vertical frame and the rolling lever rotate relative to each other. On the other hand, in Patent Document 3, since the left and right main frames are fixed to the rear frame, the running mission case, the main frame and the rear frame constitute a framework of a rigid structure. Therefore, Patent Document 3, It can be said that the support stability is high.

However, in Patent Document 3, since the engine is supported only by the main frame, a large bending load acts on the main frame, and therefore, there is a possibility that the main frame must be made excessively strong.

[0004] In the pastor, there is a car body cover having a shape different from that of the car body cover having a control floor and a shoulder portion. A seat is arranged at a position of a shoulder portion of the car body cover, and a person is carried on the shoulder portion of the car body cover. So that the user can perform the operation. However, in Patent Document 3, the engine is disposed in the space covered with the shoulder portion of the vehicle body cover, but the engine is supported only by the main frame, so that the engine is positioned on the front side portion of the space covered by the shoulder portion of the vehicle body cover, There is a risk that the cooling performance of the engine is deteriorated because the heat of the engine cover is filled in the space surrounded by the vehicle body cover or the heat of the engine is transmitted to the driver and the operating environment is deteriorated.

As in Patent Document 3, when the boss case is attached to the rear frame, the maintenance and switching operation are facilitated as compared with the case where the gear group is incorporated in the traveling mission case. However, There is an advantage that the running mission case and its internal structure can be made common in a plurality of models. However, since a large load acts on the b-period case, there is a possibility that the rear frame must be made to have an excessively strong structure in the structure in which the b-case case is attached to the rear frame connecting the left and right rear axle cases as in Patent Document 3 .

The present invention has been made in view of the above-described state of the art, and it is an object of the present invention to provide a more improved passenger-type threshing machine. In addition, the present application discloses a lot of new configurations, and it is also an object of the present invention to provide these new configurations. That is, the novel arrangements disclosed herein may be independent claims.

In the passenger-type threshing machine according to the present invention, the engine, the running mission case and the rear axle case are arranged in the running vehicle having the front wheel and the rear wheel, the engine is positioned in the rear of the running mission case, And the rear axle case extends in a series of left and right directions and has left and right rear wheels attached thereto, and the traveling mission case and the rear axle case are connected by a joint member. Further, the above-described configuration is developed as a basic configuration and has many configurations as follows.

First, according to a first aspect of the present invention, in the above basic structure, the joint member is fixed relative to the traveling mission case and the rear axle case so that the engine is supported by at least the joint member and the rear axle case.

According to a second aspect of the present invention, in the first aspect of the present invention, the front wheel is attached to the traveling mission case through a front axle device, while the engine includes a front bracket fixed to the joint member and a rear bracket fixed to the rear axle case. As shown in Fig.

A third aspect of the present invention according to the second aspect is characterized in that the front bracket has a pair of left and right base members fixed to left and right sides of the joint member in a posture of substantially V-shaped when viewed from the front of the traveling base, A front portion of the engine is fastened to the rear portion of the engine through a vibration proof rubber and a portion of the front portion bracket and the joint member is extended to the rear axle case from the traveling mission case, The rear wheel drive shaft is passing through.

A fourth invention according to the second invention or the third invention comprises a steering floor on which an operator is mounted and a seat on which the operator sits with the feet raised on the steering floor, The engine is disposed below the seat and the lower surface of the engine is positioned below the upper surface of the traveling mission case by positioning the joint member below the upper surface of the traveling mission case.

A fifth aspect of the present invention is the one of the first to third aspects of the present invention. In this invention, the working device is connected to the rear of the traveling vehicle, and the power drawn from the inside of the traveling mission case is transmitted to the relay gear case And the transmission gear case is indirectly attached to the rear axle case either directly or through a bracket.

According to a sixth aspect of the present invention, a fifth aspect of the present invention is a preferred embodiment. In the present invention, the joint member is fixed to the rear axle case through a bracket plate, and a protrusion for fixing the relay gear case to the bracket plate is formed , And the relay gear case is fixed to the bracket and the rear axle case.

(Effects of the Invention)

However, since both the traveling mission case and the rear axle case are provided with a gear group therein, the structure is durable and has a high strength. In the present invention, since the traveling mission case and the rear axle case of a sturdy structure are fixed through the joint member, the traveling mission case, the joint member and the rear axle case function as a structural member (strength member) constituting the skeleton of the traveling gas. Therefore, the traveling gas can secure a high fastness while simplifying the structure as a whole.

According to the present invention, since the joint member and the rear axle case can be used as the supporting members of the engine, the structure of the traveling vehicle can be simplified and the cost can be reduced. Further, since the traveling mission case is disposed in front of the engine, the center of gravity of the traveling vehicle can be pulled forward as far as possible, contributing to improvement in stability.

Further, the engine is also supported by the rear axle case, but as described above, the rear axle case has a durable structure, and the rear axle case extends in the left-right direction, so that the engine is stably supported. As a result, no external force is applied to the joint member around the axis. Therefore, it is possible to stably and well support the engine without making the joint member excessively strong.

Further, since the engine is also supported by the rear axle case, the engine can be arranged behind the patent document 3. Therefore, it is possible to prevent the heat from being filled in or prevent it from being contributed to the improvement of the cooling performance, and to prevent the operating environment from deteriorating.

In the case of the front wheel drive system, the traveling power shifted by the traveling mission case is transmitted to the front axle device, but in this case, it is reasonable to attach the front axle device to the traveling mission case. Since the front axle is attached to the traveling mission case, the traveling mission case and the rear axle case (the front axle case) A considerable gap is generated between them.

Although the engine can be supported in three letters of the traveling mission case, the joint member, and the rear axle case, in reality, the front and rear length of the engine is not long enough to span the running mission case and the rear axle case. Therefore, it is practical to support the front portion of the engine with the joint member and the rear portion with the rear axle case as in the second invention. In the second invention, since the engine is supported by the joint member and the rear axle case through the front bracket and the rear bracket, the freedom of design of the joint member and the rear axle case is not hindered.

The shape of the front portion bracket to be fixed to the joint member can be designed as required. However, when the V-shaped foot portion is employed as in the third invention, since the front portion bracket and the joint member have a triangle structure, There is an advantage that the strength against the force to be twisted around the shaft center is significantly increased. There is also the advantage that the drive shaft is protected by the front bracket.

The fourth invention is advantageous in that the front axle can be attached reasonably if the running mission case is disposed below the control floor. Further, since the height of the joint member can be made as low as possible and the engine can be arranged at a low level, The center of gravity of the whole can be lowered to improve the stability, and it is also possible to secure a space for arranging the fuel tank between the seat and the engine.

In the fifth aspect of the present invention, for example, the relay gear case like the boss case is fixed to the rear axle case. However, since the rear axle case has a sturdy structure as described above, Can be firmly fixed.

In the sixth invention, for example, the bracket plate is welded to the joint member, and the bracket plate is fixed to the rear axle case, whereby the joint member can be securely fixed to the rear axle case. Further, in the sixth invention, since the relay gear case is also fixed to the bracket plate, the relay gear case can be supported in a wide range, so that the attachment strength can be improved. Further, since the bracket plate is also used for fixing the joint member and attaching the relay gear case, the structure can be simplified as much.

1 is an overall side view of a rice miller according to an embodiment.
2 is a plan view of a rice miller.
3 is a perspective view of the traveling vehicle with the vehicle body cover attached thereto.
4 is a perspective view of the traveling vehicle with the vehicle body cover removed.
5 is a side view of the traveling vehicle with the vehicle body cover removed.
Fig. 6 (A) is a side view of a recessed portion, and Fig. 6 (B) is a partial perspective view of a traveling mission case portion.
7 is an exploded plan view of the recess;
Figure 8 is a side view of the recess.
9 is an exploded perspective view of the recess.
Fig. 10 (A) is a perspective view of the traveling mission case, and Fig. 10 (B) is an exploded perspective view of the traveling mission case 1 and the joint member.
11 is an exploded perspective view of the rear axle case and the joint member.
12 is a plan view of a modified example.
13 is a side view of a modified example.
Fig. 14 is a perspective view of the recess as seen from the right side. Fig.
15 is a right side view of the recess.
16 is a plan view of the recess.
17 is an exploded perspective view of the recess.
Fig. 18 (A) is a perspective view of the recessed portion viewed from the rear, and Fig. 18 (B) is a perspective view of the foamed case in an inverted state.
Fig. 19A is a power system diagram of the bobbin period changing apparatus, Fig. 19B is a diagram showing a combination of gears, and Fig. 19C is a diagram of another example.
20 is a perspective view of a group of gears for period change.
Fig. 21 (A) is a left side view of the group of gears for changing the period, and Fig. 21 (B) is a side view of the main portion.
Fig. 22 (A) is a side view showing the operating system, and Fig. 22 (B) is a view showing the bobbin case from below.
Fig. 23 is a perspective view of a portion around the boss case; Fig.
24 is a perspective view of the operating system viewed from the right rear side.
Fig. 25 (A) is a perspective view of the operating system from the left rear side, and Fig. 25 (B) is a perspective view of the clutch operating mechanism.

Next, an embodiment of the present invention will be described with reference to the drawings. The present embodiment is applied to a passenger type weaving machine (hereinafter simply referred to as " a rice milling machine "). In the following description, the words " back and forth " and " left and right " are used to specify the directions, but these words are based on the direction of the driver who is seated in the forward direction unless otherwise noted.

(One). Overview of the rice milling period

First, the outline of the rice milling machine is explained. As shown in Figs. 1 and 2, the rice milling machine has a traveling body 1 and a seedling feeding unit 2 as main elements, and the traveling body 1 has left and right front wheels 3 and rear wheels 4 . The seedling type feeding device 2 is a method of scraping one seedling from the seedling mat one by one, and has a seedling, a feeding device, and the like, but is not directly related to the present invention, and a description thereof will be omitted.

The traveling base (1) has a seat (5) and a steering handle (6) disposed in front of it. The seat 5 and the steering wheel 6 are disposed at the right and left intermediate positions of the traveling base 1. The steering handle 6 is provided in a steering mechanism section covered with a bonnet 7. A spare leg 8 is provided on the front side of the seat 5 on both sides of the seat 5 and a fertilizer 9 is provided on the rear side of the seat 5. As shown in Fig. 3, a part of the running vehicle 1 on which a person is to be carried is covered with a vehicle body cover 10, and the vehicle body cover 10 constitutes a steering floor 10a on which the operator rides.

4, the running vehicle 1 includes left and right side frames 12 extending in the front-rear direction, a front frame 12 connected to the left and right side frames 12 in the vicinity of the front end thereof, And a long rear frame 14 connected to the rear ends of the left and right side frames 12. A body frame (chassis) constituting the core of the skeleton of the traveling vehicle 1 is constituted by these side frames 12, the front frame 13 and the rear frame 14. A bumper (15) is disposed in front of the side frame (12).

The side frame 12 is bent approximately in the front part in a substantially horizontal position with the front and rear middle part as a boundary and in the rear part with a rear position. That is, the rear half of the side frame 12 is an inclined portion 12a whose height increases toward the rear. For example, as shown in Fig. 2, the outward branching frame 16 protruding outwardly and horizontally long in the lateral direction is fixed to the left and right side frames 12 by welding, and two outward branching frames 16 The preliminary plant 8 is fixed. On the right and left outside sides of the side frame 12, auxiliary frames 17 extending in the front-rear direction are arranged in parallel when viewed in plan. The auxiliary frame (17) is welded to the outwardly bifurcated frame (16).

For example, as shown in Fig. 5, when the engine 18 is positioned at a position below the inclined portion 12a of the side frame 12 as seen from the side, the crankshaft 18c is extended in the left- And a traveling mission case 19 constituting a traveling transmission device is disposed in front of the engine 18 and below the horizontal portion of the side frame 12. The traveling mission case 19 is covered from above by the steering floor 10a of the vehicle body cover 10. [ In other words, the traveling mission case 19 is disposed below the control floor 10a. Although there is nothing to say, the traveling mission case 19 is provided with a gear group, a clutch, and a brake.

A crankshaft of the engine 18 is exposed to the left while an HST (hydrostatic constant speed transmission) 20 as an example of a continuously variable transmission is attached to the left side of the traveling mission case 19, Is transferred to the HST (20) by the belt (21). The engine 18 is disposed in an inclined posture in which the cylinder bore is rearwardly curved with respect to the vertical line, and the rear line angle is approximately equal to the inclination angle of the slant portion 12a in the side frame 12. [

For example, as shown in Fig. 6, the engine 18 includes a generator 18d and a silencer 18e as an auxiliary machine. The generator 18d is disposed on the left side of the cylinder head (or the engine body) 18h, and the silencer 18e is disposed above the cylinder head 18h. As shown in Fig. 4, an air cleaner 18f is disposed on the right side of the muffler 18e. Further, both the silencer 18d and the air cleaner 18f are covered with a cover, and in the drawings, the cover is depicted as an appearance. For example, as shown in Fig. 6, the generator 18d is driven by the crankshaft 18c through the belt 18g.

A front axle device 22 is attached to the left and right side surfaces of the front portion of the traveling mission case 19 and the front wheel 3 is rotatably supported by the front axle device 22. [ The seat 5 is positioned substantially at the left and right intermediate portions of the running vehicle 1 and is located above the first half of the inclined portion 12a of the side frame 12 when viewed from the side. On the other hand, as can be understood from Fig. 5, the front portion of the engine 18 is disposed so as to overlap with the seat 5 when viewed in plan. Thus, the engine 18 is projected rearward of the seat 5 at a ratio of about half or more in the rear direction. A large space is formed between the seat 5 and the engine 18, and the fuel tank 23 is disposed in this space.

A rear axle case 25 is disposed at an oblique rear of the engine 18 and a rear axle 25c (see Fig. 4) protruding laterally from the rear axle case 25 It is fixed. 5, the rear axle case 25 is formed by projecting left and right rearward protruding portions 25b from left and right base portions 25a and the rear axle 25c is provided at the rearward protruding portion 25b . A rear support 27 is fixed to the left and right rearward projecting portions 25b through brackets 26 (see Figs. 7 and 9), respectively, and the rear support 27 is fixed to the rear frame 14 . The rear support 27 is slightly inclined forward when viewed from the side.

3, a link mechanism composed of a top link 28 and a lower link 29 is connected to a rear end of the traveling base 1, and a hitch 30 connected to both links 28, A seedling feeding device 2 is connected. The top link 28 is vertically rotatably connected to the rear support 27 and the lower link 29 is connected to the rear support 27 so as to be vertically rotatable. The link mechanism is vertically rotated by a hydraulic lifting cylinder 31 connected to the rear frame 14. [

For example, as shown in Fig. 6 (A), the traveling mission case 19 and the rear axle case 25 are connected by a joint member 32 having a hollow square shape. 6 (B), a power steering unit 34 is fixed to the front frame 13 via a bracket 33. The power steering unit 34 and the front portion of the traveling mission case 19 And is fixed by an additional bolt. Therefore, in the present embodiment, the power steering unit 34 also serves as the structural member of the traveling base 1, but since the power steering unit 34 incorporates gears and has a sturdy structure, Can be exercised.

(2). Connection structure

Next, a connection structure of the traveling mission case 19, the joint member 32, and the rear axle case 25 will be described. First, the relationship between the traveling mission case 19 and the joint member 32 will be described.

7 and 10, in the front portion of the traveling mission case 19, the lower portion of the traveling mission case 19 is lowered in a downward direction, The left and right projecting portions 19a and 19b are formed and the front axle device 22 is attached to the left and right projecting portions 19a and 19b. The left protruding portion 19a largely protrudes, but this is because the differential gear unit is disposed inside.

As shown in Figs. 9 and 10, the rear portion of the traveling mission case 19 where the HST 20 is fixed is cut out when viewed in plan. That is, a left stepped portion 36 is formed on the left side surface of the traveling mission case 19 and exposed rearwardly and leftwardly. A drive output shaft 37 protrudes rearward below the left stepped portion 36 . A drive shaft (exactly, a rear wheel drive shaft) 38 (see FIG. 5) is connected to the drive output shaft 37 via a universal joint. A rear end of the drive shaft 38 is connected to the input shaft (Not shown) through a universal joint.

The base 25a of the rear axle case 25 is provided with a long axis horizontally and laterally transversely extended from the drive shaft via a bevel gear. And is transmitted to the shaft 25c. Therefore, the rear axle case 25 has a base portion 25a that extends in the left-right direction and forms a backward protruding portion 25b at both left and right ends of the base portion 25a. The rear axle case 25 is, for example, a cast product and has a sturdy structure in order to support a gear group or a shaft.

As can be clearly understood from Fig. 10, a fixed portion 39, which is open toward the front, is formed at a portion below the left stepped portion 36 of the traveling mission case 19. The fixing portion 39 is exposed to both the left and right sides. On the other hand, the U-shaped holder bracket 40 is welded to the front end of the joint member 32 when seen in plan view that surrounds and supports the fixed portion 39 of the traveling mission case 19. The holder bracket 40 And is fixed to the fixing portion 39 with bolts 41. The bolt 41 is of two types, that is, it extends in the left-right direction and the front-rear direction. Therefore, the joint member 32 and the traveling mission case 19 are firmly fixed.

The fixing structure of the joint member 32 and the rear axle case 25 is clearly shown in Fig. That is, the end plate 42 is fixed to the rear end surface of the joint member 32 by welding and the end plate 42 is fixed to the fixing portion 43 on the front surface of the rear axle case 25 with the bolts 44 . The end plate 42 corresponds to the bracket plate described in the claims. The fixed portion 43 of the rear axle case 25 protrudes forward from the base portion 25a and has a hollow structure open toward the front.

7 and 10, a work power output section 45 projecting laterally is provided in the rear portion of the right side surface portion of the traveling mission case 19, and the work power output section 45 And the work power output shaft 46 is connected through a universal joint. The working power output shaft 46 is connected to a bumper period adjusting device 47 which is slightly shown in Figs. 1 and 5. The relationship between the rotational speed of the front and rear wheels 3 and 4 and the driving timing of the bumper device is shown in Fig. The period of the food part is adjusted by adjusting the period adjusting device 47 (the details of the period adjusting device 47 will be described later).

The end plate 42 of the joint member 32 is provided with a projecting portion 42a projecting to the right and the boss case constituting the boss period adjusting device is also fixed to the projecting portion 42a.

(3). Engine support structure

Next, the supporting structure of the engine 18 will be described. 9, the front portion of the engine 18 is attached to the front bracket 48 fixed to the joint member 32, and the rear portion thereof is attached to the rear axle case 48 through the rear bracket 49. [ (Not shown). The front bracket 48 has left and right foot portions 50 fixed to the side surface of the joint member 32 and a top member 51 arranged to be inserted into the left and right foot portions 50.

The foot portion 50 is made of a channel material and is widened toward the left and right as it goes upward in the front view. Therefore, the left and right foot portions 50 are in a substantially V-shaped posture. The upper member 51 is mounted on the foot portion 50 through a cylindrical front anti-vibration rubber 52. The upper portion member 51, the front anti-vibration rubber 52 and the foot portion 50 are bolted Respectively. The upper surface of the foot member 50 and the upper surface member 51 are inclined at a certain angle? 1 with respect to the horizontal plane when viewed from the side, ). In other words, the supporting surface of the front anti-vibration rubber 52 is inclined at an angle of? 1 with respect to the horizontal.

A horizontal portion 51a is provided at the rear end of the upper member 51 and the engine 18 is fastened to the horizontal portion 51a with bolts 53 and nuts. More specifically, outboard flange portions 18a and 18b are provided at the lower end of the cylinder block constituting the engine 18, and a front flange portion 18a of the front flange portion 18a is engaged with the upper member 51 of the front bracket 48 Respectively.

Since the foot 50 of the front bracket 48 is in the V-shaped posture, there is a space of an inverted trapezoidal shape when viewed from the front side surrounded by the front bracket 48 and the joint member 32, The above-mentioned drive shaft 38 passes through. 6, when viewed from the side, the drive shaft 38 is inclined rearward relative to the horizontal. As shown in Fig. 7, the drive shaft 38 is inclined so as to lean to the left as it goes backward in a plan view. And passes through a space surrounded by the front bracket 48 and the joint member 32 in a tilted posture when viewed in plan view.

The rear bracket 49 is fixed to the base portion 25a of the rear axle case 25 but is not directly fixed but attached to a pair of left and right auxiliary brackets 54 fixed to the rear axle case 25 have. The auxiliary bracket 54 has an upper horizontal portion 54a and a lower vertical portion 54b and the inclined portion is a rear portion of the horizontal plane with respect to the horizontal plane. The upper horizontal portion 54a is upwardly inclined to the rear axle case 25 And the lower vertical portion 54b is fixed to the front surface of the rear axle case 25 with a bolt.

The rear bracket 49 is attached to the rear bracket 54 and the rear bracket 54 by means of bolts and nuts Respectively. The rear portion vibration proof rubber 56 has its axial center foreground with respect to the vertical line so that the portion of the rear portion bracket 49 overlapped with the rear portion vibration damping rubber 56 is also slightly inclined at the angle? (In other words, the supporting surface of the rear portion vibration-proof rubber 56 is inclined at an angle of? 2 with respect to the horizontal).

In this example,? 1 and? 2 are set to be the same, but it is also possible to set them at different angles as in the modified example described later. An upper horizontal portion 49a is formed at the front end of the rear bracket 49 and the rear flange portion 18b of the engine 18 is fastened to the upper horizontal portion 49a with bolts 53 Reference). The axes of the vibration-proof rubbers 52 and 56 are inclined (90 ° -? 1) and (90 -? 2) with respect to the horizontal, respectively, with respect to the axis (line extending in the expansion and contraction direction).

The auxiliary bracket 54 is fastened to the boss portion 55 in order to form a space between the auxiliary bracket 54 and the rear axle case 25 to facilitate the attachment of the rear anti-vibration rubber 56. That is, in order to secure a space for arranging the nuts inside the sub bracket 54,

9, the front and rear flange portions 18a, 18b of the engine 18 are formed with a pair of left and right holes 57, 58 through which the bolts 53 are fitted. The pair of the left and right holes 57 and 58 is elongated left and right so as to absorb machining error and assembly error of each member so that the engine 18 can be securely mounted. 7 and 9, the bolt holes of the front brackets 48 and the rear axle case 25 are formed by the long holes 59 and the two round holes 60 arranged side by side Three sets are set, and one is made into the long hole 59, so that machining error and assembly error can be absorbed. It is also possible to correspond to two kinds of engines 18 of different sizes by forming two round holes 60. [

5, the tension pulley 62 is in contact with the belt 21 that transmits the power of the engine 18 to the HST 20 from above. Although not shown, the tension pulley 62 is attached to a pivotable arm, and an appropriate tension is applied to the belt 21 by pulling the arm downward by a spring. However, the lower end of the spring pulling the arm And is connected to a bracket fixed to the upper member 51 constituting the bracket 48. [ That is, the front bracket 48 also constitutes a part of the tension applying means of the belt 21. Therefore, the structure as a whole can be simplified.

(4). Summary · Benefits of Implementation

As described above, in the present embodiment, not only the traveling mission case 19 and the rear axle case 25 are provided for the structural member of the traveling base 1 by providing the joint member 32, but also the rear axle case 25 and the joint member 32, the entire structure of the traveling vehicle 1 can be simplified. Further, the respective effects described in the effect of the invention are exhibited.

Conventionally, the elevating cylinder is disposed in an inclined posture when viewed from the front side of the rear axle case. In the present embodiment, however, the elevating cylinder 31 is suspended from the rear frame 14. Therefore, the engine 18 can be disposed as far back as possible without being disturbed by the lifting cylinder 31, and as a result, it is also easy to support the engine 18 in the rear axle case 25. [ This is an advantage of the present embodiment.

When the axial center of the front portion vibration damping rubber 52 is tilted as viewed from the side as in the present embodiment, the forward force of the tensile force acting on the engine 18 through the belt 21 is transmitted to the front portion vibration damping rubber 52 So that the support function is excellent. Since the axes of the front portion vibration damping rubber 52 and the rear portion vibration damping rubber 56 are inclined to the assembling posture when they are viewed from the side (that is, ) Is excellent in stability of support.

For example, as shown in Fig. 6, it is possible to form the oil inlet 61 at the lower end portion of the engine 18 and at the front end portion and the rear end portion. 7, the oil injection port 61 is located at the left step of the engine 18, but the rear end surface of the running mission case 19 is shifted to the right side of the oil injection port 61, Or the level gauge can be carried out without being disturbed by the traveling mission case 19. It is also possible to use the oil inlet 61 on the rear side. In this case, there is an advantage that it is not necessary to individually remove the body cover 10. The oil inlet may be formed at another site.

(5). Variation of engine support structure

Modifications are shown in Figs. 12 and 13. Fig. This modified example is basically the same as the above-described embodiment, and differs in several points. The generator 18d is disposed almost directly above the crankshaft 18c and the muffler 18e is disposed on the rear side of the generator 18d as the first difference point. In other words, a large space is formed behind the generator 18d and a large silencer 18e is disposed in this space. Therefore, engine sound can be remarkably suppressed. The cutout portion 23a is formed in the left side portion of the fuel tank 23 in order to prevent the generator 18d and the fuel tank 23 from interfering with each other.

The inclination angles? 1 and? 2 of the front anti-vibration rubber 52 are different from each other. For example, in Fig. 6,? 1 and? 2 are set to less than 30 占 However, in the modification of Figs. 12 and 13,? 1 is set to about 45 占 and? 2 is set to about 35 占. Since the transmission case 19 is disposed in front of the engine 18, the engine 18 tends to be pulled forward and retracted by the belt 21 as shown by a line with arrows O1, (Or by the front bracket 48) by the front anti-vibration rubber 52 because of the large angle of about 45 DEG.

In the patent document 1, although the engine is disposed in an inclined posture, since the anti-vibration rubber is only mounted on a horizontal bracket, if the engine is pulled by the belt, the engine is separated from the anti-vibration rubber, . On the other hand, in this embodiment, since the tensile force acts to compress the front anti-vibration rubber 52 even if the engine 18 is pulled forward by the belt 21, the support stability of the engine 18 is excellent.

The extension line O2 of the shaft center of the front portion vibration damping rubber 52 and the extension line O3 of the back vibration damping rubber portion 56 intersect near the center of gravity of the engine 18 when viewed from the side, Therefore, the effect of vibration prevention is also high. In other words, the dust-proofing effect of the engine 18 is most effectively exhibited when the load due to the vibration acts from the waterline direction with respect to the supporting surface of the vibration-proofing rubbers 52, 56. However, The vibration of the head 18 is not sufficiently exerted and conversely the center of gravity of the engine 18 is lower than the point of intersection of the extension lines O1 and O2 of both axial centers The center of gravity of the engine 18 and the point of intersection of the extension lines O1 and O2 of the both shaft centers as shown in the present modified example are shifted to the side It is possible to effectively suppress the vibration of the engine 18 and to exhibit a high dust-proof performance, if they are approached or approximated when viewed.

13, the tension pulley 21a is connected to the free end of an arm 63 rotatably connected to the engine body, and the arm 63 is pulled downward by a spring 64. As shown in Fig. The lower end of the spring 64 is connected to a bracket 65 fixed to the upper member 51 constituting the front side bracket 48 (this also applies to the above-described embodiment).

As shown in Fig. 12, the air cleaner 18f is disposed on the right side of the cylinder head 18h, so that the cylinder head 18h is exposed upward. 3, the shoulder portion 10b of the body cover 10 is formed with a cutout portion 66 that opens rearward and covers the canopy 67 with a removable lid 67. The lid 67, however, (It is also possible to form the window hole in the shoulder portion 10b of the body cover 10 and block the window hole with the cover 67).

In the past, it was troublesome to separate the body cover 10 at every simple maintenance of the peripheral portion of the cylinder head 18h, such as replacement of the ignition plug. However, in this embodiment, only by removing the cover 67 It is user-friendly since simple maintenance of the peripheral portion of the cylinder head 18h can be performed. This is one of the advantages of the present embodiment, and can be an independent invention as an improvement of the prior art.

(6). Attachment structure of the period changer

Next, the bimodal variation device 47 will be described. First, the appearance, the attachment structure and the internal mechanism will be mainly described with reference to Figs. 17 and 18. Fig. The boss period changing device 47 has a boss case 70 and a member such as a gear is disposed inside the boss case 47. [ The input shaft 71 is projected forward from the boss case 70 and the output shaft (PTO shaft) 72 is extended from the input shaft 71 And is projected rearward, and the specific driving shaft 73 protrudes upward. A first operating shaft 74 and a second operating shaft 75 are vertically disposed opposite to each other on the front surface and a main clutch operating shaft 76 protrudes from the upper surface.

18B is a state in which the bodyside case 70 is turned upside down. As can be easily understood from this figure, the lower end of the bodyside case 70 is provided with a rib- 77 are provided in the lower fastening portion 77, and a tapped hole 78 is formed in the lower fastening portion 77. 17, a right projecting portion 42a is formed on the end plate 42 fixed to the rear end of the joint member 29 and the projecting portion 42a is connected to the lower fastening portion 77 ) With bolts (79). As can be understood from Fig. 17, a horizontal piece 42b extending to the projecting portion 42a is formed at the lower end of the end plate 42, and therefore, the end plate 42 has a sturdy structure.

The L-shaped rear bracket 81 is fixed to the transverse boss 80 provided on the rear portion of the boss case 70 with the transverse bolt 82 when seen from the side, Is fixed to the rear axle case 25 by the bolts 83 in the longitudinal direction. The rear axle case 25 is provided with an upward boss body 84 for supporting the rear bracket 81. For example, as shown in Fig. 16, the bodyside case 70 is located in the right-hand room of the engine 18 in plan view.

(7). Internal structure of the case

Next, the internal structure (transmission system) of the bodyside case 70 will be described with reference to Figs. 19 to 21. Fig. As shown in Fig. 19 (A), a first gear 85 and a second gear 86 of the same diameter are fixed to the input shaft 71. As shown in Fig. Both gears 85 and 86 have the same diameter, but the number of teeth of the second gear 86 is slightly smaller than that of the first gear 85.

The input shaft 71 and the output shaft 72 are disposed concentrically. A cylindrical intermediate shaft 87 is fitted to the input shaft 71 so as to be rotatable relative to the input shaft 71 and the intermediate shaft 87 is engaged with the output shaft 72 in a state in which the intermediate shaft 87 rotates together with the output shaft 72. The third gear 88 and the fourth gear 89 are slidably fitted to the intermediate shaft 87 by spline fitting or the like and are fitted relatively non-rotatably. Further, on the intermediate shaft 87, the first booster gear 90 is relatively rotatably and slidably fitted.

A cam-type main clutch 91 is provided on the output shaft 72. The main clutch 91 is composed of a fixed part 91a and a sliding part 91b and the sliding part 91b is fixed to the fixed part 91a by the clutch spring 92 Respectively. The power transmission from the input shaft 71 to the output shaft 72 is interrupted when the sliding part 91b is separated from the fixed part 91a against the clutch spring 92. [ The main clutch 91 is shut off when the vehicle is running on the road or when the vehicle is turning in the working of the food. The shutting operation of the main clutch 91 is performed by lowering the main clutch operating shaft 76. [

An idle shaft 94 extending in parallel with the input shaft 71 and the output shaft 72 when viewed from the side is rotatably supported in the inside of the idle period case 70, A fifth gear 95 that can be engaged with the gear 85 or the second gear 86 is slidably engaged with the spline or the like so as to be non-rotatably fitted. The fifth gear 95 has a number of teeth that is twice as many as the number of teeth of the first gear 85 or the second gear 86. The fifth gear 95 has a first position engaged with the first gear 85, It is possible to select the second position and the neutral position which is separated from the first gear and the second gear 85, 86.

Although one fifth gear 95 is selectively engaged with the first gear 85 or the second gear 86 in the present embodiment, as shown in a separate example in Fig. 19C, the first gear 85 The first reduction gear 95a engaged with the first gear 85 and the second reduction gear 95b engaged with the second gear 86 are provided in one sliding barrel and the sliding barrel is moved It is also possible to adopt a configuration in which power is transmitted to either one of the two reduction gears 95a and 95b (in this case, it is advantageous in design because a simple shape gear can be used).

The ratio of the number of teeth of the fifth gear 95 with respect to the first gear 85 and the second gear 86 is set such that the ratio of the number of teeth of the fifth gear 95 to the first gear 85 The ratio of the number of teeth of the fifth gear 95 with respect to the second gear 86 can be set to about 2.3 times as large as that of the first gear 85 in the case of the modification of Fig. 19 (C) The ratio of the first reduction gear 95a to the second reduction gear 95b can be set to about 2.0 times and the ratio of the second reduction gear 95b to the second gear 86 can be set to about 2.3 times.

The idle shaft 94 is provided with a sixth gear 96 for engaging and disengaging with the third gear 88, a seventh gear 97 for engaging and disengaging with the fourth gear 89, The second booster gear 98, which is always engaged with the first booster gear 90, is fixed. The ratio of the number of teeth of the seventh gear 97 to the fourth gear 89 is set to be smaller than the ratio of the sixth gear 96 to the third gear 88. [ The rotational speed of the intermediate shaft 87 (and the output shaft 72) is lower than the rotational speed of the fourth gear 89 and the seventh gear 97 in the state where the third gear 88 and the sixth gear 96 are engaged with each other The state of engagement is lowered. The ratio of the number of teeth of the sixth gear 96 to the third gear 88 is about 1.94 and the ratio of the number of teeth of the seventh gear 97 to the fourth gear 89 To about 1.41.

The first booster gear 90 and the second booster gear 98 are non-circular profiles such as ellipses and have the same number of teeth. Therefore, in the state where the rotation of the idle shaft 94 is transmitted to the intermediate shaft 87 and the output shaft 72 through the both of the differential gears 90 and 98, the rotation speed of the idle shaft 94 and the output shaft 72 And the output shaft 72 rotates while changing the angular velocity periodically. Both of the booster gears 90 and 98 are non-circular and always kept in engagement with each other due to the specificity that the engagement posture is constant.

The fourth gear 89 and the first booster gear 90 are provided with an intermediate clutch 99 capable of engaging and disengaging. The fourth gear 89 slides further to the right through the state of being once engaged with the seventh gear 97 from the state of Fig. 19 (A). As a result, the intermediate clutch 99 is engaged. When the intermediate clutch 99 is engaged, the power of the idle shaft 94 is transmitted to the output shaft 72 through the booster gears 98 and 90. [

In a state where the intermediate clutch 99 is engaged, the third gear 88 and the fourth gear 89 are idling. Accordingly, the intermediate clutch 99 has a function of connecting / disconnecting the connection between the intermediate shaft 87 and the first booster gear 90. As another means for connecting / disconnecting the connection between the intermediate shaft 87 and the first booster gear 90, a movable clutch member is provided on the intermediate shaft 87, It is also possible to connect / disconnect the power to the body, but in this case, a shifter or a lever for operating the movable clutch body is separately required. On the other hand, in the present embodiment, since the intermediate clutch 99 can be connected / disconnected by the lever that operates the third gear 88 and the fourth gear 89, there is an advantage that the structure becomes very simple.

Fig. 19 (A) shows a neutral state in which no power is transmitted from the input shaft 71 to the output shaft 72. Fig. The fifth gear 95 is selectively switched to the first gear 85 and the second gear 86 so that the rotation of the input shaft 71 is transmitted to the idle shaft 94 in an amplified state. As described above, the rotational amplification factor is higher in a state in which the fifth gear 95 is meshed with the second gear 86.

The intermediate shaft 87 slides so that the third gear 88 and the fourth gear 89 selectively engage the sixth gear 96 and the seventh gear 97 to rotate the idle shaft 94 Is amplified and transmitted to the intermediate shaft 87 (output shaft 72). Also in this case, as described above, the state in which the sixth gear 96 is meshed with the third gear 88 has a high gain. The intermediate shaft 87 is slid and the intermediate clutch 99 is connected so that the rotation of the idle shaft 94 is transmitted to the intermediate shaft 87 (the output shaft 72). In this case, the ratio of the number of revolutions of the idle shaft 94 and the intermediate shaft 87 (output shaft 72) is 1: 1 as described above.

As a result, the fifth gear 95 is slid to perform two-step switching, and the intermediate shaft 87 slides to perform three-step switching. Therefore, there are six combinations in total. This combination is shown in Fig. 19 (B). In the table, the names of the gears are omitted and only the numbers of the symbols are shown. The arrows indicate paths through which power is transmitted. The table indicates the numbers of I to VI of the Roman numerals in the order of the lower amplification rate of the number of revolutions of the output shaft 72 with respect to the number of revolutions of the input shaft 71. [ The numbers in parentheses on the right side of Roman numerals indicate examples of abandonment per 3.3 square meters. As can be understood from this table, the expiration period changing device 47 of the present embodiment covers most of the entire area of the genital and plantation.

A forward rotation shaft 100 extending in parallel with the input shaft 71 and the output shaft 72 is rotatably disposed at an upper portion of the boss case 70. The first gear 85 And an articulation clutch 102 are provided on the outer circumferential surface of the eccentric gear 102, The application clutch 78 is composed of a fixed part 102a fixed to the eighth gear 101 and a sliding part 102b slidably fitted to the artificial rotary shaft 100 by spline fitting, , And the sliding part 102b is biased toward the fixed part 102a by a spring. A pair of bevel gears 103 to be engaged with each other is provided on the specific rotation shaft 100 and the specific drive shaft 73.

(8). Operation mode of change of period

Next, the operation modes of the first operating shaft 74, the second operating shaft 75, and the main clutch operating shaft 76 will be described with reference to Figs. 21 to 25 mainly. 21 (A), the first operating shaft 74 is for slidingly operating the fifth gear 95, and has a first shifter 104 for sliding the fifth gear 95 have. On the other hand, the first shifter 105 is provided on the fifth gear 95 to engage with the first shifter 104 so as to be relatively rotatable.

The fifth gear 95 is engaged with the first gear 85 when the first operation shaft 74 is pushed forwardly and the fifth gear 95 is engaged with the second gear 86 when the first operation shaft 74 is pushed inward, Lt; / RTI > The fifth gear 95 can be kept in a neutral state in which it is not engaged with the first gear 85 and the second gear 86 by positioning the first operating shaft 74 in the front and rear intermediate portions, It is held either fully pulled or fully immersed.

The second operating shaft 75 is for sliding operation of the intermediate shaft 87 and forms a plurality of annular grooves 106 on the intermediate shaft 87 while the second operating shaft 75 is provided with an intermediate shaft 87 A plurality of second shifters 107 to be fitted in the annular grooves 106 of the first and second gears 87 and 87 are provided and the second shifter 107 is slid by sliding the second operating shaft 75 in the axial direction, 88 can be switched to the three positions in which they are meshed with the sixth gear 96 and the state in which the fourth gear 89 is engaged with the seventh gear 97 and the intermediate clutch 99 is engaged .

For example, as shown in Figs. 22 and 23, a lever bracket 108 is disposed at a front portion of the bobbin case 70. As shown in Fig. The lever bracket 108 is L-shaped as viewed from the front with the upward side plate 108a, and the downward piece 108b (see FIG. 22 (B)) is provided at the lower end thereof and the downward piece 108b And is fixed to the front surface of the bobbin case 70 with bolts 109.

The lever bracket 108 is provided with a pin 112 so that the first operation lever 110 for operating the first operation shaft 74 and the second operation lever 111 for operating the second operation shaft 75 are rotated substantially horizontally, (Refer to FIG. 23 (B) and FIG. 25 (A)). The first operation lever 110 has a substantially U-shaped base portion and a long lower end extending from the first long hole 113 formed in the side plate 108a of the lever bracket 108 Respectively. A handle 110a is attached to the tip of the first operation lever 110. [

23 (B), the first operation lever 110 is bent so as to extend outward from the lever bracket 108 so as to extend in the outward direction, and the locking portion 110b 1 cutout groove 114 formed in the first operating shaft 74. The cut- Therefore, the first operation lever 110 can be rotated horizontally to switch two positions with the neutral position in between.

As shown in Fig. 23 (B), the second operation lever 111 also has a substantially U-shaped configuration. As shown in Fig. 25 (A), the U- Both levers 110 and 111 are connected to each other by a single pin 112 so as to be horizontally rotatable. Therefore, it can be made compact and contributes to cost reduction.

As can be understood from FIG. 23 (B), the cylindrical block body 115 is fitted in the second operation shaft 75 so as to be positionally adjustable by a nut, and the upper and lower And the headed pin 116 is fitted in the upper and lower elongated holes 117 formed in the second operation lever 111. The headed pin 116 is of a T shape and is inserted into the slot 117 of the second operation lever 110 and then rotated by 90 degrees so as to be fitted into the second operation shaft 75 in this position.

The upper side of the second operating lever 111 extends longer than the lower half and the upper side passes through the second long hole 90 formed in the side plate 108a of the lever bracket 108. [ A handle 111a is also attached to the front end of the second operation lever 111. [ As shown in Fig. 21 (B) and Fig. 23, a downward locking piece 111b is provided in a portion of the second operation lever 111 that fits into the second long hole 90, while a second long hole 118 Three locking grooves 118a are formed in the back and forth direction so that the locking pieces 111b are engaged with and separated from each other. Therefore, the second operation lever 111 (the second operation shaft 75) can be selectively held in three positions.

Since the levers 110 and 111 for operating the operating shafts 74 and 75 are attached to the lever bracket 108 fixed to the boss case 70 in this embodiment, Most can be unitized. As a result, the assembling efficiency of the passenger type rearing machine can be improved.

As shown in Fig. 21 (B), the side plate 108a of the lever bracket 108 displays the relationship between the positions of the levers 110 and 111 and the number of abandonment. That is, the number of abandonment decreases or increases due to the movement position of the first operation lever 110 is indicated by the letters "few" and "many", and the second long hole 118 Few "and" many "are displayed in correspondence to the words indicating the function of the first operation lever 110, and the second long hole 90 is interposed therebetween The number of abandonment is displayed on the upper and lower sides.

Accordingly, a person can visually understand the number of food abandonment from the positions of the first operation lever 110 and the second operation lever 111. [ That is, when the first operation lever 110 is "few", the position of the second operation lever 111 corresponds to the number of times of the food aeration indicated under the second long hole 118, Many ", the position of the second operation lever 111 corresponds to the number of food abandonment indicated above the second long hole 118. The combination of the displays of the levers 110 and 111 is also one of the features of the present embodiment and can be an independent invention.

(9). Operation type of clutch operated shaft

Next, the operation modes of the main clutch 91 and the apply clutch 78 are mainly described with reference to Figs. 21 and 23 to 24. Fig. As shown in Fig. 21, a rod-shaped first cam 76a is fixed to the main clutch operating shaft 76, and a ring-shaped second cam 120 is overlapped on the first cam 76a from the rear . The second cam 120 is fitted on the output shaft 72 in a freely rotatable state and the second cam 120 is non-rotatably and slidably fitted on the output shaft 72. The second cam 120, The sliding part 91b of the main clutch 91 is relatively rotatably and non-slidably connected. Further, the second cam 120 is biased forward by the clutch spring 121.

The contact surface between the first cam 76a and the second cam 120 is inclined with respect to the axis of the main clutch operation shaft 76 when seen from the side and when the first cam 76a rises, The clutch spring 121 is pushed forward, and the main clutch 91 is moved forward by the sliding part 91b. When the first cam 76a descends, the second cam 120 retreats against the clutch spring 92. Then, the main clutch 91 slides the sliding part 91b away from the fixed part 91a, do.

As shown in Figs. 23 to 24, a top bracket 122 of a rearward opening U-shape is fixed at the upper end of the boss case 70, And a long operation shaft 123 is attached. On the other hand, an annular groove is formed in the main clutch operation shaft 76, and the first arm 124, which is fixed to the operation shaft 123, is fitted into the annular groove of the main clutch operation shaft 76.

Therefore, when the operating shaft 123 rotates and the main clutch operating shaft 76 rises, the main clutch 91 is connected. 23, the first arm 124 is on the main clutch operation shaft 76, but this is for indicating the pivoting posture of the first arm 94. Actually, as shown in Fig. 25, the first arm 124 Is fitted into the annular groove of the main clutch operating shaft 76. [

An upward second arm 125 is fixed to the operation shaft 123 and the rear end of the long rod 126 is connected to the second arm 125 by a pin in the forward and rearward directions (126) is separated from the second arm (125). 22 (A), a lever panel 127 is disposed on the upper part of the side where the side frame 9 begins to be inclined, and a third arm 128, which is connected to the lever panel 127 at the upper end, And the front end of the operating rod 126 is connected to the lower end of the operating rod 126. [

One end of the wire rope 130 is connected to the lower end of the third arm 128 through a spring 129. The other end of the wire 130 is connected to a food operation lever 131 (see FIG. 3). When the rod 126 is pulled forward through the third arm 128 by the operation of the food-portion operating lever 131, the main clutch operating shaft 76 rises and the main clutch 91 is connected. A torsion type torsion spring 132 is inserted into the operation shaft 123 to bias the operation shaft 123 in the clutch connection direction.

21 (A), a shifter 133 with a flange is attached to the sliding part 102b constituting the inventive clutch 102 so as to be relatively rotatable and non-slidable, and the shifter 133 And is biased in the connection direction by the spring 134. [ The flat surface formed at the lower end of the artificial clutch operation shaft 135 is opposed to the side surface of the flange 133a accommodated in the shifter 133.

The friction clutch control shaft 135 is rotatably supported on the boss case 70. The friction clutch 102 is rotatably supported by the friction clutch control shaft 135 in a state in which the flat surface of the lower end thereof is in close contact with the flange 133a of the shifter 133, The shifter 133 and the sliding part 102b are retracted against the spring 134 in a state in which the arc surface of the lower end of the friction clutch operation shaft 102 is in close contact with the flange of the shifter 133 The dosing clutch 102 is shut off.

25, the upper end of the friction clutch control shaft 135 projects upward from the boss case 70. A fourth arm 138 is fixed to the friction clutch operation shaft 125, The fourth arm 136 and the second arm 125 fixed to the operation shaft 123 are connected by the wire rod 137. [ When the operating rod 126 is pulled forward, the specific clutch operating shaft 135 rotates in the connecting direction in accordance with the rotation of the second arm 125. [ That is, the main clutch 91 and the application clutch 102 are simultaneously connected / disconnected.

(10). theorem

As described above, in the present embodiment, since the boss period can be adjusted to six levels by operating the two levers 110 and 111, it is possible to easily respond to a wide range of demands of the customer without requiring troublesome work such as replacement of gears . If the configuration in which the levers 110 and 111 are exposed to the outside of the traveling base 1 as in the embodiment is employed, there is an advantage that the operation of the levers 110 and 111 can be performed easily.

It is also possible to embed the boss period changing device 47 in the traveling mission case 13 or to fix the boss case 70 to the traveling mission case 13, Is disposed near the rear axle case 25, there is an advantage that the power take-out structure to the seedling type seedling device 2 and the fertilizing device 7 is simplified. Furthermore, by disposing the output shaft 71 and the input shaft 72 in a concentric (coaxial) manner as in the present embodiment, the gear shifting structure can be simplified and the bobbin period changing device 47 can be made compact.

The idle shaft 94 may be disposed on the side of the input shaft 71 and the output shaft 72. The idle shaft 94 may be disposed below the input shaft 71 and the output shaft 72 as in the present embodiment It is possible to make the width of the bottom surface period changing device 47 as small as possible so that the boss case 70 can be moved to the inside of the traveling base 1 as much as possible, Can be prevented from being brought into contact with each other.

In the present embodiment, the open period is switched in six stages, but the number of switching stages can be arbitrarily set. For example, the number of abandonment times such as 37 abandonment and 43 abandonment can be set as needed. It is also possible to install three or more operating levers. Further, the lever is not limited to a rotary type such as a horizontal rotary type, and various types such as a rotary type (a holding type, a handle type) and a method of sliding an axial type can be adopted.

In addition, the blooming period in the rearing period is generally classified as a number of aquifers per 3.3 square meters, and a total of 37 blooms, 40 blooms or 43 blooms, 50 blooms, 60 blooms, 70 blooms, 80 blobs or 85 blobs, 90 blobs Is set. In general, 37 or 40 cancellations are called croaker planting, and 60 or more are often called paddy planting. The yield of rice is not proportional to the number of abandonment, but there is a fact that the activity of seedlings is increased by the planting of the genitalia, and the abandonment is promoted. Therefore, the yield per unit area does not change even if it is crooked, In some cases, crop yields are higher than paddy planting. It can be said that the merit of the penis is recognized and recently, there is a tendency of penis rejuvenation.

It has been conventionally done to change the boss period by the operation of the lever, and it is assumed that Patent Document 4 has two levers. However, in Patent Document 4, since the for-period adjusting portion is incorporated in the traveling mission case, the operating lever is also installed in the traveling mission case. However, the traveling mission case is disposed below the vehicle body cover.

On the other hand, in the present embodiment, since the for-period adjusting device 47 is provided in the rear axle case 25, the operation of the levers 110 and 111 can be performed very simply. In addition, since there are two (a plurality of) levers, it is possible to perform the adjustment by a multistage. In addition, as in the present embodiment, arranging the two levers 110 and 111 at the same position with the height up and down is advantageous in that the baffle adjusting device 47 can be made compact. When the operation levers 110 and 111 are configured to be rotatable as in the present embodiment, there is an advantage that the shifters 104 and 107 can be slidably operated by the principle of the lever.

In the present invention, the rotation of the input shaft is first decelerated, but it is clear that the number of rotations of the input shaft becomes higher than that of the conventional one if the number of rotations of the output shaft is the same as the conventional one. That is, it is possible to perform the seedling work at a low speed while rotating the input shaft of the crucible changing device at a higher speed than the conventional one. As a result, the shaft diameter of the input shaft can be made smaller than that of the prior art, thereby contributing to cost reduction and weight reduction. The stress can be made small and the twist deformation can be remarkably suppressed (thereby preventing deviation of the locus of the food portion claws and realizing a proper food portion).

And, in the seedling type bookkeeping such as the rice paddy, the rotation of the engine is transmitted to the transmission having the traveling mission case, so that a part of the power is consumed for driving and the other part is consumed for the seedling. Therefore, it is not possible to adopt a means of installing a reduction gear in the traveling mission case and delivering the reduced rotation to the period changing device, but there is a possibility that the internal structure of the traveling mission case is complicated.

On the other hand, the present embodiment decelerates largely (about 1/2) in the step of putting power into the period changing device 47, and has the deceleration function in itself, and therefore, It is possible to prevent the mechanism from becoming complicated. In other words, the present invention allows the engine to be maintained at a suitable rotational speed in a low-speed work load region without complicating the traveling transmission device by providing a deceleration function at the most upstream portion of the transmission mechanism as the period changing device. This is an advantage of the present embodiment.

Patent Literature 3 and Patent Literature 4 disclose a period changing device, but these have problems in operability and functions. On the other hand, this embodiment has many advantages as described above. Therefore, provision of an improved period changing device can be understood as an object of the present invention.

(11). Other

The present invention can be variously embodied in addition to the above embodiments. For example, the object of the present invention is not limited to the pasture, but can also be applied to other passive farming machines such as harlequins and vegetable transplants. The structure and arrangement of the engine can be selected as needed. For example, it is possible to arrange the cylinder bores in a vertical posture or to arrange the crankshaft in a posture extending in the front-rear direction.

The structure of the running mission case, the joint member, and the rear axle case can be arbitrarily designed and modified within the range not to impair its function. For example, it is also possible to use a round pipe or a channel material for the joint member.

(Industrial availability)

The present invention has high usability because it can be embodied in a passenger-type farming machine such as a rice milling machine. Therefore, it can be used industrially.

1: running vehicle 2: seedling feeding device as an example of working device
3: front wheel 4: rear wheel
5: Seat 12: Side frame
18: engine 19: running mission case
22: front axle device 25: rear axle case
32: joint member 38: drive shaft
42: end plate (bracket plate) 47:
48: front bracket 49: rear bracket
50: foot portion of the front bracket 51: upper member of the front bracket
52, 56: anti-vibration rubber 54: auxiliary bracket

Claims (6)

An engine, a traveling mission case, and a rear axle case are disposed in a traveling vehicle having front and rear wheels, with the engine positioned on the rear side of the traveling mission case and the rear axle case positioned on the rear side thereof, The left and right rear wheels are attached to the left and right rear wheels, and the traveling mission case and the rear axle case are connected by a joint member,
Wherein the joint member is fixed relative to the travel mission case and the rear axle case so that the joint member is supported by at least the joint member and the rear axle case,
Wherein the front wheel is attached to the traveling mission case through a front axle device while the engine is supported from front and rear by a front bracket fixed to the joint member and a rear bracket fixed to the rear axle case,
The front bracket has left and right member members fixed to left and right sides of the joint member in a posture of substantially V-shaped when viewed from the front of the running vehicle, and left and right long members fixed to the top of the foot member, And a rear drive shaft extending from the traveling mission case toward the rear axle case passes through a space surrounded by the front bracket and the joint member. A passenger type farming machine. delete delete delete delete delete

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