JP3318261B2 - Paddy field machine vibration isolation support device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration support device for a paddy field working machine such as a rice transplanter, and more particularly, to an anti-vibration support device for an engine mount in which a belt power transmission mechanism is used to extract engine power. It concerns the device.

[0002]

2. Description of the Related Art In a rice transplanter, an engine is mounted at a front portion of a body, and power is transmitted to a transmission disposed above a front driving wheel via a belt transmission mechanism. As disclosed in JP-A-159017, the engine is mounted on the body frame via vibration isolating rubber.

[0003]

In the above-mentioned structure, the belt transmission mechanism is disposed so as to be deviated to one of the left and right sides of the engine, and the engine is originally twisted in a direction to be pulled by the belt tension. Power is acting.
Therefore, when a large load is applied to the engine in Fukada or the like, the torsional force described above is increased by the increased belt tension, and the engine is greatly tilted and displaced, so that the distance between the pair of pulley centers is clearly reduced. is there. In this case, there is a problem that a belt slip occurs due to a reduction in the center distance between the pulleys, and a speed ratio changes in a continuously variable transmission structure using split pulleys.

Therefore, as shown in Japanese Patent Application Laid-Open No. H10-48234, a rubber bush is pivotally supported on the left and right ends of a left-right shaft, and a common vibration-proof rubber support is provided on the rear. The engine is designed so that the distance between the pulley centers is unlikely to change by supporting the engine with anti-vibration so that it is relatively easy to oscillate in the vertical direction, but relatively hard to displace in the left and right torsion directions. There is.

According to the vibration damping technique disclosed in the above-mentioned publication, the use of the shaft supporting structure surely suppressed a change in the pulley center distance caused by the inclination of the engine due to the belt tension. Performance was slightly sacrificed, leaving room for further improvement.
SUMMARY OF THE INVENTION An object of the present invention is to provide an anti-vibration support device in which an engine vibration is sufficiently blocked, but the inclination due to belt tension hardly occurs.

Further, in the structure in which the engine power is constituted by a belt continuously variable transmission mechanism using a split pulley, and a movable pulley piece of the split pulley is slid directly in the axial direction by a shift fork, the structure is caused by vibration-proof support. As a result, the contact position between the shift fork and the movable pulley piece tends to deviate from the normal position. In such a case, the operation force for pushing the movable pulley piece becomes heavy. Therefore, it is also an object to maintain a state in which the split pulley can be easily operated while supporting the engine in a vibration-proof manner.

[0007]

Means for Solving the Problems [0014 ] A first aspect of the present invention is a vibration isolating support device for a paddy field working machine, wherein a belt transmission mechanism that acts on an engine output shaft to extract engine power is provided, and a plurality of engines are provided. Vibration-proof support to the fuselage via the elastic mechanism, and the amount of overhang in the horizontal direction from the engine of the plurality of elastic mechanisms arranged on the side where the belt transmission mechanism exists, in the horizontal direction from the engine of other things Is set to be larger than the overhang amount.

According to a second aspect of the present invention, there is provided an anti-vibration support apparatus for a paddy field working machine, wherein a belt transmission mechanism for acting on an engine output shaft to extract the power of the engine is provided, and the engine is prevented from the body via a plurality of elastic mechanisms. The plurality of elastic mechanisms, which are arranged on the side where the belt transmission mechanism is present among the plurality of elastic mechanisms, are inclined more toward the center of the engine than the elastic support directions of those arranged on the side where the belt transmission mechanism is not present. It is characterized by the following.

A third invention is a paddy field work according to the first and second inventions.
Of the plurality of elastic mechanisms
The hardness of the one located on the side where the
It is characterized by being harder than the hardness of other things.

According to a fourth aspect of the present invention, in the vibration damping support device for a paddy working machine according to the first to third aspects, the belt transmission mechanism is configured as a continuously variable transmission mechanism using a split pulley, and a movable pulley piece in the split pulley is A shift fork that slides directly in the axial direction via a bearing, and the shift fork is formed with fork claw portions that act on two opposing locations on the outer peripheral side surface of the bearing; In order to maintain a proper contact position with the side surface of the bearing, a regulating portion capable of contacting the outer peripheral surface of the bearing in the radial direction is formed at an intermediate portion between the two fork claw portions.

[0011] [Operation] According to the first aspect, the overhang amount in the horizontal direction from the engine of the elastic mechanism disposed in the belt transmission mechanism exists side, in the horizontal direction from the engine of the other resilient mechanism By setting it larger than the amount of overhang, the elastic strength of the elastic mechanism located on the side where the belt transmission mechanism is present is increased, while the effective vibration damping support function is obtained with the same elastic strength. And the load conditions acting on each elastic mechanism can be made equal or as close as possible.

Therefore, even when the belt tension is increased in Fukada and the like and the torsional force acting on the engine is increased, the engine is greatly inclined and displaced as in the conventional case, that is, the distance between the pulley centers of the belt transmission mechanism is reduced. As a result, the above-described inconveniences such as the belt slip and the unexpected speed change do not first occur.

When the belt tension acts on one of the left and right sides of the engine, not only does the elastic mechanism on the belt arrangement side bend more in the tension application direction than on the side where the belt is not arranged, but also the engine moves laterally on the belt existing side. The elastic mechanism also bends in the direction in which it moves, that is, the elastic mechanism bends obliquely. In addition to the change in the pulley center distance, the engine-side pulley may move sideways from the belt tension direction.

[0014] Therefore, according to the second aspect, the elastic supporting direction of the elastic mechanism disposed in the belt transmission mechanism exists side, the engine than the elastic support direction of the elastic mechanism disposed in the belt transmission mechanism absence side Since it is tilted to the center, it is possible to cope with the above-mentioned oblique movement of the engine, and without adversely affecting the anti-vibration function such as the shaft support structure, the change in the distance between the pulley centers and the lateral movement of the engine. Can be effectively suppressed.

A general elastic mechanism, such as one in which vibration isolating rubber is baked and integrated between upper and lower plate materials to which stud bolts are fixed, is difficult to exhibit effective vibration isolating performance in both directions. Therefore, by inclining the elastic mechanism in the two combined directions, an effective anti-vibration function can be exhibited.

According to the third aspect of the present invention , a belt is used at Fukada or the like.
Tension increases and the torsional force acting on the engine increases.
However, the engine may tilt and displace
That is, the distance between the pulley centers of the belt transmission mechanism is reduced.
Belt slip, unexpected gear shift, etc.
The inconvenience of is not caused first.

In the case where the belt transmission mechanism has a continuously variable transmission structure using a split pulley and is configured to directly shift the movable pulley piece, a bearing for rotatably supporting the movable pulley by engine vibration is provided. The contact point with the shift fork may be shifted, and the shift operation may become heavy, making it difficult to shift smoothly. As a countermeasure, the configuration of claim 4 is such that a regulating portion is provided at an intermediate portion between two opposed fork claws for operating the bearing of the shift fork so as to be able to radially contact the outer peripheral surface of the bearing. .

That is, even if the pulley and the shift fork are displaced relative to each other due to the vibration, in the direction in which the restricting portion and the belling come into contact with each other, further displacement is prevented by the contact, so that the fork claw and the fork claw can be prevented. The normal contact state with the bearing can be maintained, and a light shift operation can be maintained. In addition, as will be described in detail in the embodiment, when the two shift forks are interlockingly moved by using both the pulleys on the driving side and the driven side as the split pulleys, the above described description is made on the vibration-isolated supported floating side split pulley. In addition to preventing the shift of the shift operation position, the movable pulley piece of the fixed split pulley and the shift fork are also prevented from being indirectly shifted.

[Effect] In the paddy field working machine according to claim 1 or 3 , the elastic strength of the belt-side elastic mechanism is directly (claim 3) or indirectly.
(Claim 1) By means of strengthening, (A) excessive tilting of the engine due to belt tension which causes inconvenience of belt slip and unintended shifting is effectively suppressed without sacrificing vibration damping performance. A vibration damping support device that can be provided.

In the paddy field working machine according to the second aspect , by knowing the bending direction of the elastic mechanism due to the belt tension,
The effect (a) was obtained.

In the paddy field working machine according to the fourth aspect, it is possible to reduce the inconvenience of the shift operation caused by the vibration isolating support structure of the engine, while being a simple modification that only forms a regulating portion for the bearing on the shift fork. A good anti-vibration support device could be provided.

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG. 1, a riding type rice transplanter, which is an example of a paddy field working machine, has a seedling planting at the rear of a riding type self-propelled body 1 via a link mechanism 2 and a hydraulic cylinder 3. As shown in FIG. 2, a transmission case 8 is connected to an output shaft 8a of an engine
Power is transmitted to the input shaft 10a through a belt continuously variable transmission (an example of a belt transmission mechanism) 12 having a split pulley structure.

The self-propelled body 1 has a body frame 7 having a pair of left and right driving front wheels 5 for steering and a pair of right and left driving rear wheels 6.
In addition, an engine 8 and a boarding operation unit 9 are mounted. The front drive wheel 5 is supported on the body frame 7 via a planting / running transmission case 10, and the rear drive wheel 6 is supported on the body frame 7 via an axle case 11. The engine 8 is supported by the body frame 7 including the mission case 10 in a vibration-proof manner.

As shown in FIGS. 2, 5 to 7, the front portion of the transmission case 10 has a front frame 35 projecting forward.
Are connected and integrated, and a support member 36 made of a plate material on which the engine 8 is mounted is stretched by four elastic mechanisms D1, D2, Anti-vibration support is provided via D3 and D4. Each of the elastic mechanisms D1 to D4 has a general structure in which a plate 38 with stud bolts is integrated on the upper and lower surfaces of a cylindrical rubber block 37 by baking. The rubber hardness is the same for all four rubbers.

The right front and rear right elastic mechanisms D2 and D4 are horizontally moved so that their stud bolt axes d2 and d4 are vertically oriented vertically, that is, the elastic support direction is directed upward. In a posture, it is arranged between the support member 36 and the body frame 7 side. The left front elastic mechanism D1 is located between the protruding portion 36a of the support member 36 which protrudes greatly leftward from the engine 8 and the body frame 7 side, so that the stud bolt axis d1 is closer to the upper side and the inner side in the body left and right direction. In addition, the composite obliquely arranged so as to have an elastic supporting direction inclined toward the rear side.

The stud bolt axis d3 of the left rear elastic mechanism D3 is obliquely arranged so as to have an elastic support direction that is inclined upward toward the inside in the left-right direction of the vehicle body. Here, the elastic support direction means each of the elastic mechanisms D1 to D1.
4 corresponds to the surface direction of the plate 38 (the axial direction of the stud bolt).

That is, the amount of extension of the left front elastic mechanism D1 arranged on the side where the belt continuously variable transmission 12 is present from the engine 8 in the horizontal direction is determined by the horizontal direction from the engine 8 of the other elastic mechanisms D2 to D4. Of the left front elastic mechanism D1 and the elastic support direction d1 of the left front elastic mechanism D1.
Is larger than the inclination component toward the engine center in the elastic support directions d2 to d4 of the other elastic mechanisms D2 to D4. The inclination component of the left rear elastic mechanism D3 toward the center of the engine in the elastic supporting direction d3 is the elastic supporting direction d of the right elastic mechanisms D2 and D4.
2, which is larger than the inclination component toward the engine center at d4.

As shown in FIGS. 2 and 3, the belt continuously variable transmission 12 has the input pulley 12A mounted on the output shaft 8a in a detented state, and the output pulley 12B mounted on the input shaft 10a in a detented state. A transmission belt 12C is wound around the two pulleys 12A and 12B, and a tension pulley 12D acting on the transmission belt 12C is provided.

Input pulley 12A and output pulley 12B
Is a fixed pulley piece 12a provided in a fixed position in the axial direction.
The split pulley is configured to change the belt winding radius by moving the movable pulley piece 12b far and near along the axis of the pulley. In other words, while the belt winding radius of the input pulley 12A is increased, while the belt winding radius of the output pulley 12B is reduced, the belt operates on the high-speed side to reduce the belt winding radius of the input pulley 12A. When the belt winding radius of the output pulley 12B is increased, the output pulley 12B operates on the low speed side.

The fixed pulley piece 12 of the input pulley 12A
a and the movable pulley piece 12b are arranged so that the movable pulley piece 12b is positioned on the engine 8 side (inside), and the fixed pulley piece 12a and the movable pulley piece 12b of the output pulley 12B are connected to the movable pulley piece 12b. Are located outside.

As shown in FIG. 4, a first operating shaft 12E, which is parallel to the pulley shaft, is mounted on a steering gear case 13, which is an example of a fixed portion continuously provided above the transmission case 10, along the shaft. The arm 12F is movably mounted, the arm 12F is mounted on the first operation shaft 12E in the axial center position, and the rotation is stopped. The second operation shaft 12G parallel to the pulley shaft center is mounted on the arm 12F in the axial center position. And install it in a detented state.

As the first operation shaft 12E moves in one direction (outward), the first operation shaft 12E moves integrally with the first operation shaft 12E so that the movable pulley piece 12b of the input pulley 12A is wound around the belt against the belt tension. Move to the radius increasing side and
With the movement of the operation shaft 12E in the opposite direction (inward), the first shift which moves integrally with the first operation shaft 12E and allows the movable pulley piece 12b to move to the side where the belt winding radius decreases due to belt tension. Connect the fork 12H to the first operation shaft 12
Attach to E so that it can rotate around its axis.

The second operation shaft 12 integrated with the first operation shaft 12E
Along with the movement in the opposite direction (inward) of G, the movable pulley piece 12b of the output pulley 12B is moved integrally with the second operation shaft 12G to the belt winding radius increasing side, and the second operation shaft 12G is moved. In one direction (outward), the movable pulley piece 12 moves integrally with the second operation shaft 12G.
The second shift fork 12J that allows the belt winding radius to move to the side where the belt winding radius decreases due to the belt tension is rotatably mounted on the second operation shaft 12G around the axis thereof to form the belt continuously variable transmission 12. ing.

That is, by moving the first operating shaft 12E and the second operating shaft 12G in one direction, the belt winding radius of the input pulley 12A is increased, while the belt winding radius of the output pulley 12B is reduced, thereby increasing the speed. To the first operating shaft 12
By moving E and the second operation shaft 12G in the opposite directions, the belt winding radius of the input pulley 12A is reduced, while the belt winding radius of the output pulley 12B is increased to operate at a lower speed. . The arm 12 is attached to the first operation shaft 12E.
The means for stopping F is a key 14.

As shown in FIGS. 2 and 3, the engine output shaft 8a is provided with a pump driving pulley 23 integrated with the boss portion 22 of the input pulley 12A. The tension arm 27 uses the pump shaft 24 as a swing fulcrum. Since the boss portion 22 of the input pulley 12A integrally provided with the pump driving pulley 23 can have a relatively long axial length, the key 28 straddling the movable pulley piece 12b can be made relatively long, and the durability can be improved. It has helped to improve the quality.

The boarding operation unit 9 includes the steering wheel 1
5, a driver's seat 16 and a shift lever 17. As shown in FIGS. 2 to 4, the speed change lever 17 is linked to the first operation shaft 12 </ b> E via a link mechanism 18 so as to perform a speed change operation of the continuously variable transmission 12 in accordance with its swing. The mechanism 19 is configured to be able to hold positions at a plurality of operation positions in a state where human operation is allowed.

The link mechanism 18 is provided with a bell crank 18B interlocked with the speed change lever 17 via a first rod 18A so as to swing around the left-right axis P1 with the swing of the speed change lever 17. The second rod 18 swings around the vertical axis P2 with the swing of the 18B.
Interlocking shaft 18D interlocking with bell crank 18B via C
The first operation shaft 12E is provided at the upper end of the interlocking shaft 18D.
The interlocking shaft 18D is engaged with the interlocking pin 12e attached to the
The operation arm 18E that moves the first operation shaft 12E by swinging together with the operation arm 18E is fixed, and the first operation shaft 12E is moved in one direction, that is, the high-speed side with the swing of the shift lever 17 to the high-speed side. The first operation shaft 12E is moved in the opposite direction, that is, in accordance with the swing of the transmission lever 17 to the low speed side, that is,
It is configured to move to the low speed side.

In the link mechanism 18, specifically, between the bell crank 18B and the second rod 18C, the operation force transmission between the speed change lever 17 and the belt continuously variable transmission 12, that is, the first operation shaft 12E is performed. A winding means 21 is provided to allow relative displacement in the direction, and to provide resistance to the relative displacement between the first operating shaft 12E and the shift lever 17.
And first adjusting means for adjusting the interlocking positional relationship between the shift lever 17 and the first operating shaft 12E, and second adjusting means for adjusting the axial position of the second shift fork 12J with respect to the second operating shaft 12G. Is provided.

Each shift fork 12H, 12J has a fork claw portion 31, 32 acting on two opposing locations on the outer peripheral side surfaces 29a, 30a of the bearings 29, 30.
Are formed, and the fork claws 31 and 32 are formed.
In order to maintain the proper contact position between the outer peripheral surface of the bearing 29 and 30 and the outer peripheral surface of the outer peripheral portion 29a, the fork claw portions 31 and 32 are provided with restricting portions 33 and 34 that can radially contact the outer peripheral surface of the bearing 29 and 30.
Is formed in the middle part.

That is, the output pulley 12B supported by the transmission case 10 and the steering gear case 13
The first operation shaft 12E is supported by a fixed system and is fixed in position. However, the input pulley 12A supported by the engine which is a floating system by anti-vibration support.
Is a variable position. Therefore, the relative position between the input side bearing 29 and the first shift fork 12 </ b> H fluctuates due to vibration, and the pair of fork claws 31, 31 is displaced from the normal axially symmetric position on the outer peripheral side surface 29 a of the input side bearing 29. There is.

When the input pulley 12A and the first shift fork 12H are displaced, the second shift fork 12
The arm 12F that rotatably supports the first operating shaft 12
Due to the swinging movement about E, the pair of fork pawls 32 may deviate from the normal axially symmetric position on the outer peripheral side surface 30a of the output side bearing 30 due to the influence. However, the above-mentioned regulating parts 33, 34
Excessive relative displacement movement of the bearings 29, 30 toward the shift forks 12H, 12J is restricted by the presence of
The normal contact state between the fork pawls 31 and 32 and the bearings 29 and 30 is maintained as much as possible, thereby preventing a heavy shift operation and a shift failure.

[Another Embodiment] In the structure shown in FIG. 6, the rubber blocks 37 in the left front and left rear elastic mechanisms D1 and D3 on the belt continuously variable transmission 12 side.
May be made harder than that of the elastic mechanisms D2 and D4 on the right side, so that the striking is more effective. Although not shown, the left elastic mechanisms D1, D3 and the right elastic mechanisms D2, D4 are not shown.
Means that the overhang amount in the left-right direction from the engine 8 at the disposition position is set to be equal, and the hardness of the rubber block 37 in the left elastic mechanisms D1 and D3 is harder than that of the right elastic mechanisms D2 and D4. good.

[Brief description of the drawings]

FIG. 1 is a side view of a riding rice transplanter.

FIG. 2 is a side view of the belt continuously variable transmission and its operation device.

FIG. 3 is a cutaway rear view of the belt continuously variable transmission.

FIG. 4 is an exploded perspective view of the operation device.

FIG. 5 is a side view showing an engine mounting structure.

FIG. 6 is a plan view showing an engine mounting structure.

FIG. 7 is a front view showing an engine mounting structure.

[Explanation of symbols]

 Reference Signs List 8 engine 8a engine output shaft 12 belt transmission mechanism 12B split pulley 12b movable pulley piece 12J shift fork 30 bearing 30a outer peripheral side surface 32 fork claw portion 34 regulating portion

Continuation of the front page (56) References Japanese Utility Model Showa 50-53504 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F02B 67/04 A01C 11/02 313 B60K 5/12 F02B 77/00 F16F 15/04 F16M 13/02

Claims (4)

(57) [Claims] A belt transmission mechanism for acting on an engine output shaft to take out the power of the engine, and supporting the engine with vibration damping via a plurality of elastic mechanisms to an airframe; A paddy working machine, which is arranged on the side where the belt transmission mechanism is present, has a horizontal extension from the engine that is set to be larger than the horizontal extension from the engine. Vibration support device. 2. A belt transmission mechanism which acts on an engine output shaft to take out the power of the engine is provided, and the engine is supported on the body via a plurality of elastic mechanisms in a vibration-proof manner. An anti-vibration support device for a paddy field working machine, wherein an elastic support direction of a member disposed on the side where the belt transmission mechanism exists is inclined toward the center of the engine with respect to an elastic support direction of a member disposed on the side where the belt transmission mechanism does not exist. (3) Belt transmission mechanism among multiple elastic mechanisms
The hardness of the one placed on the side where
The paddy field working machine according to claim 1 or 2, wherein the paddy field working machine is harder than the degree.
Anti-vibration support device. 4. The belt transmission mechanism is configured as a continuously variable transmission mechanism using a split pulley, and a shift fork that moves a movable pulley piece of the split pulley directly in an axial direction via a bearing is provided. This shift fork is provided with two opposed surfaces on the outer peripheral side surface of the bearing.
In order to form a fork claw portion acting on a portion and maintain a regular contact position between the fork claw portion and the outer peripheral side surface, a regulating portion capable of radially contacting the outer peripheral surface of the bearing is provided. The anti-vibration support device for a paddy working machine according to any one of claims 1 to 3, wherein the anti-vibration support device is formed at an intermediate portion between both fork claws.