JP2003102238A - Combine harvester - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem of a conventional combine harvester in which, although the powered rotation of a reaping input shaft is limited in one direction with a pawl type one-way clutch to avoid the trouble of tines or the like by their reverse rotations, the one-way clutch has low durability because of being built in a pulley or the like, and further to solve the problem of the conventional combine harvester whose engine is fixed to a chassis through vibration-proof elastomer members to reduce vibrations and noises but is contrarily largely vibrated or makes large noises in dependence on the direction of outer loads applied to the output shaft of the engine. SOLUTION: This combine harvester having a counter case 64 for changing and controlling a power from the engine 35 or the like and transmitting the power to the treating systems of a reaping section and the like, respectively, and having a vehicle speed-synchronizing input shaft portion 62 in the counter case 64 is characterized by disposing the pawl type one-way clutch 159 in the vehicle speed-synchronizing input shaft portion 62 and further more enhancing the elastic constant of vibration-proof members 89, 90 on the side of a fly wheel 59 disposed in the belt-driving portion of the engine 35 than that of the vibration-proof members 87, 88 on the side of a drive shaft 63.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combine with low vibration and noise and excellent durability, and more particularly to an arrangement of a one-way clutch provided in a transmission system to a reaper and an arrangement of an engine.

[0002]

2. Description of the Related Art Conventionally, in a combine, a machine frame is placed on a crawler type traveling device, a cutting section is arranged at a front end of the machine frame, and the cutting section projects a grass plate at the front end. Weed the grain culm, raise the case to the rear of it, and raise the case to cause grain culm by the rotation of the tine protruding from the case and raise the stock with a cutting blade arranged at the rear of the sward plate. I try to reap. This cut grain culm is conveyed to the rear by the upper conveying device, the lower conveying device, and the vertical conveying device, and the stock source is inherited from the upper end of the vertical conveying device to the feed chain on the machine side, and the grain culm is contained in the threshing portion. The culm is transported. The power for driving the tines, the cutting blades, the grain culm conveying devices, and the like is input to the reaping input shaft from approximately the center of the lateral width of the machine body via a belt, a chain, or the like. The rotation direction of the power to the reaping input shaft is regulated in one direction by a claw-type one-way clutch in order to avoid troubles due to the reverse drive of the tines, the cutting blades, and each grain transfer device. . Also,
The engine that generates power to each processing system is fixed on the chassis via a vibration-damping member made of an elastic body to reduce vibration and noise generated by the engine itself or due to externally input load. I am trying to do it.

[0003]

However, since the one-way clutch is built in the power transmission tool such as the pulley and the gear, the clutch claws violently slide and collide with each other in the power disengaged state when the vehicle is moving backward. In this case, there is a problem in that the power transmission device causes a defect such as a breakage or a poor fitting to reduce durability, and further, vibration and noise due to sliding / collision of the clutch claws deteriorate the working environment. . Further, since the elastic constants of the anti-vibration members are substantially the same, there is a problem that vibration and noise increase rather depending on the direction of the external load applied to the output shaft of the engine. Furthermore, the driving force from the engine to the handling cylinder of the threshing section and the lower conveyor of the grain tank is output in the right angle direction from the long output shaft protruding from the engine toward the mission case, resulting in a large torque. However, there is a problem that the durability of this output part is deteriorated.

[0004]

The problem to be solved by the present invention is as described above, and the means for solving this problem will be described below. That is, in claim 1,
The counter case is equipped with a counter case that shifts and controls the power from the engine and the mission case and transmits it to each processing system such as the reaping section. The counter case is provided with a vehicle speed tuning input shaft section for inputting power that is synchronized with the traveling speed. In the combine, the claw-type one-way clutch is provided on the vehicle speed tuning input shaft section, and the one-way clutch is a transmission system for shifting the power from the vehicle speed tuning input shaft section to the mowing section by shifting the power from the mowing transmission section. In the above, it is arranged on the upstream side of the mowing transmission unit. In the second aspect, the one-way clutch is embedded in the oil sump in the counter case. According to a third aspect of the present invention, a drive shaft is connected to one end of a crankshaft of the engine, a flywheel and a belt driving unit are provided on the other end, and the engine is mounted on the chassis through a vibration isolating member made of an elastic body. In the fixed combine, the elastic constant of the vibration isolating member on the other end side is higher than that of the vibration isolating member on the one end side. In the fourth aspect, power is output from the other end side to a high torque processing system having a high peak torque, such as a threshing section or a grain tank.

[0005]

1 is a left side view of the combine, FIG. 2 is a plan view of the combine, FIG. 3 is a right side view of the combine, and FIG.
Is a front view, FIG. 5 is a skeleton diagram showing an outline of power transmission configuration, FIG. 6 is a front view of the front of the machine, FIG. 7 is a side view, FIG. 8 is a plan view, and FIG. 9 is a left side view of the counter case. 10 is a right side view, FIG. 11 is a front view, FIG. 12 is a plan sectional view, FIG. 13 is a plan sectional view showing each clutch mechanism of the counter case, and FIG. 14 is a side sectional view of a claw clutch. 15 is a plan view of the same, FIG. 16 is a side sectional view of the clutch gear, FIG. 17 is a plan view of the same, FIG. 18 is a skeleton diagram showing the power transmission configuration from the engine to each processing system, and FIG. 19 is a normal straight cutting operation. 20 is a schematic diagram showing a power transmission path at the time of turning back, FIG. 21 is a schematic diagram showing a power transmission path at the time of high speed running, and FIG. 22 is a power transmission path at the time of HST assistance. Schematic diagram, Figure 23 is middle Plan view of a transmission mechanism, FIG. 24 is a side view of the rotating body, FIG. 25 is likewise rear cross-sectional view, FIG. 26 is a rear sectional view of the same cutting input gear.

First, the overall structure of the combine according to the present invention will be described with reference to FIGS. 1 to 4. The combine has a structure in which the crawler type traveling devices 18L and 18R are supported on the left and right sides of the track frame 1.
Is a left and right machine frame that is erected on the track frame 1, 20 is a threshing unit that has a feed chain 23 and the like stretched to the left side and incorporates a handling cylinder 21 and a processing cylinder, and 71 is a lower part of the threshing unit 20. A sorting device that is located and that sorts the grain that has been threshed, 29 is a grain tank that carries in the grains that have been sorted by the sorting device 71 via the lifting cylinder 30, and 17 is a grain tank of the grain tank 29. A discharge auger that carries the grain out of the machine, and 27 is a straw processing unit that faces the end of the straw chain 28.

Reference numeral 22 is a mowing section provided with a cutting blade 24 and a grain culm transport mechanism, 34 is a cabin behind the mowing section 22, in which a round steering handle 32 and a driver's seat 33 are arranged, and 70 is
On the front part of the left body frame 19L on the side of the cabin 34,
A rotation support portion 25 for rotatably supporting the reaper 22 up and down or left and right is a reaper 22 on the rotation support portion 70.
Is a hydraulic cylinder for moving up and down through the mowing frame 26.

Below the cabin 34, at the front part of the right body frame 19R, an engine 35,
An air-cooling device 2 including a radiator 102 for cooling, and a mission case 36 are arranged, and the power from the engine 35 drives the crawler type traveling devices 18L and 18R to travel, and the grain stems are continuously connected from the front of the combine. It is configured to be harvested and threshed.

Next, an outline of a power transmission configuration from the engine 35 to each processing system will be described with reference to FIGS. A crankshaft 51 for converting reciprocating motion of a piston (not shown) into rotary motion is extended in the engine 35 in the longitudinal direction of the machine body, and a front end of the crankshaft 51 is used as an output shaft 82 and a drive shaft with a universal joint is attached to the output shaft 82. The rear end of 63 is fixed. An input shaft 78 is connected to the front end of the drive shaft 63 with a universal joint, and the input shaft 78 is projected from an input case 79 attached to the upper part of the mission case 36.

On the left side surface of the input case 79, an HS for housing a hydrostatic continuously variable transmission (hereinafter referred to as "HST")
A T case 118 is provided, and in the HST case 118, a turning HST 38 and a straight HST 37 are sequentially installed from the front.
Is installed. From the straight HST 37, the straight HST 37
The straight-movement drive shaft 81 connected to the straight-movement motor shaft 114, which is the output shaft of 37, is provided on the left side so as to project the rotational force transmitted to the input shaft 78 between the forward and reverse rotation directions in the straight-travel HST 37. After controlling the increase / decrease of the rotation speed, it is transmitted to the inside of the transmission case 36, and at the same time, it can be outputted from the linear drive shaft 81.

Further, on the left side of the engine 35, a counter case 64 capable of distributing an appropriate speed to each processing system is arranged. From the counter case 64, an input shaft 75 is provided.
・ 76 and output shafts 91, 92, 93, and 94 are projected.

The vehicle speed tuning input shaft 75 is fixedly provided with a vehicle speed tuning input pulley 66. The vehicle speed tuning input pulley 66 is provided with the straight drive shaft 81 via a belt 61.
Connected to the upper straight drive pulley 80, the straight HST3
The traveling rotation from 7 can be transmitted into the counter case 64.

A direct input pulley 67 is fixedly mounted on the direct input shaft 76, and a pulley 65 on an output shaft 83 formed at the rear end of the crankshaft 51 is fixed to the direct input pulley 67 via a belt 73. Along with being connected, the belt 73 is provided with a threshing clutch 52. The output shaft 83
A pulley 68 is also fixed on the upper part of the pulley 68. The pulley 68 is connected via a belt 69 to a conveyor shaft 85a of a lower conveyor 85 axially mounted on the lower part of the grain tank 29. A grain discharging clutch 84 is provided, and the grain discharging operation can be performed by turning on and off the grain discharging clutch 84.

Regarding the threshing output shaft 91, the output pulley 95 → belt 103 → pulley 104/105/106
→ Handle shaft 2 via transmission gears 107, 108, 109
The threshing output shaft 91 is connected to the belt 103 by the tension pulley 110 that is in contact with the belt 103.
It is possible to connect and disconnect power from the handle cylinder 21 to the handle cylinder 21.

The harvesting output shaft 92 has an output pulley 96.
The output pulley 96 is connected and interlocked with the reaping input shaft 72 via an intermediate transmission mechanism 77 provided on the rotation fulcrum portion 70.
Power can be input to

The selection output shaft 93 has an output pulley 97.
Is fixed, and the output pulley 97 is connected with pulleys 100 and 111 via a belt 98, and the pulley 100 of the pulleys 100 and 111 sends the wind for wind sorting to the sorting device 71. The pulley 111 is fixed on the 99a.
Is fixedly installed on the conveyor shaft 101a of the first conveyor 101 that feeds the grains selected by the selection device 71 to the grain tank 29, so that power can be output from the selection output shaft 93 to each part of the selection device 71. . The feed chain output shaft 94 is linked to the feed chain 23 so as to be interlocked.

In this way, the power from the engine 35 is transmitted to each processing system. In the following, each device related to power control and the transmission path configuration between each device will be described in order from the transmission upstream side.

First, regarding various configurations of the engine 35,
This will be described with reference to FIG. The left and right airframe frames 19L
Horizontal frames 42 and 43 are horizontally mounted on the front portion of 19R, and the horizontal frames 42 and 43 are mounted on the horizontal frame 42 and 43.
The left and right vertical frames 44 and 45 are bridged at substantially equal intervals in parallel to the L and 19R. And the vertical frame 44.4
Vibration-damping members 87 to 90 containing an elastic body such as rubber are fixedly mounted on the engine 5, and the engine 35 is mounted and fixed on the vibration-damping members 87 to 90.

Behind the engine 35, the output shaft 8 is provided.
3, the pulleys 65 and 68 are fixedly mounted on the output shaft 83 in addition to the flywheel 59 that absorbs fluctuations in the generated torque and smoothes the rotation. Of these, the pulley 68 is linked and interlocked with a lower conveyor 85 below the grain tank 29 via a belt 69 extending rightward, and the belt 69 constantly applies a right lateral pulling load 49, On the contrary, the pulley 65 is connected and interlocked with the direct input pulley 67 provided on the left side of the counter case 64 on the left side of the engine 35 via the belt 73.
3, the left lateral pulling load 48 is always applied.

On the other hand, in front of the engine 35, the output shaft 82 is projected, and the output shaft 82 is projected from the input case 79 above the transmission case 36 via the drive shaft 63 with a universal joint. Unlike the output shaft 83, it does not receive a lateral pulling load. The elastic constants of the vibration isolating members 87 and 88 arranged on the output shaft 82 side are the same as the output shaft 8
It is set to be smaller than the elastic constant of the vibration isolation members 89 and 90 arranged on the third side.

In such a structure, on the flywheel 59 side, since the elastic constants of the vibration isolating members 89 and 90 are high, it is possible to sufficiently oppose the reaction force due to the lateral pulling loads 48 and 49, while the lateral pulling load. On the side of the drive shaft 63 that does not receive the vibration, since the elastic constants of the vibration isolation members 87 and 88 are low, the vibration isolation effect can be further enhanced.

That is, the crankshaft 51 of the engine 35
The drive shaft 63 is connected to the output shaft 82 at one end of the engine, the flywheel 59 and the belt drive unit are provided at the output shaft 83 at the other end, and the engine 35 is provided with vibration damping members 87 to 90 made of an elastic body. Since the elastic constants of the vibration isolating members 89/90 on the other end side are higher than those of the vibration isolating members 87/88 on the one end side in the combine fixedly mounted on the chassis via the external shaft applied to the output shaft of the engine, Since the load from the engine can be accurately dealt with, the vibration and noise of the engine can be greatly reduced, and the durability of the engine output section can be improved.

Further, on the output shaft 83 to which the flywheel 59 is attached, the pulley 68 connected to the lower conveyor 85 below the grain tank 29 is also connected to the handling cylinder 21 of the threshing unit 20 via the counter case 64. The pulley 65 is also fixed, but the distance from the engine 35 to the pulleys 65 and 68 is short, so that the torque applied to the output shaft 83 can be small.

That is, since the power is output from the other end side to the high torque processing system having a high peak torque such as the threshing unit 20 and the grain tank 29, the projecting length from the engine 35 can be short, and the output unit This reduces the burden on the product and greatly improves durability.

Next, the transmission structure from the transmission case 36 to the counter case 64 will be described with reference to FIGS. A support plate 153 is bridged in the left-right direction between the left body frame 19L and a vertical frame 152 bridged in parallel with the body frame 19L on the left side of the horizontal frames 42 and 43. Plate 1
The rotation support portion 70 is placed and fixed on the 53 and the horizontal frames 42 and 43.

The rotation support portion 70 is formed by the horizontal frame 42.
A left support 154 having a trapezoidal side view that is erected over the left portion and the support plate 153 on the left portion, and a side view trapezoid erected from the horizontal frame 42 across the right portion of the support plate 153 to the horizontal frame 43. Right support base 155 and the right support base 15
5 and a support 156 bridged in the left-right direction between the upper part of the left support 154.
A support hole 156a for fitting and supporting the rear end of the mowing frame 26 is opened on the left side of the cutting frame 26, and the mowing unit 22 can be rotated leftward about the support hole 156a so as to be side-opened. I am trying.

The transmission case 36 and the counter case 64 are disposed in front and rear of the rotary support portion 70 having the above-described structure, and the linear movement of the forward portion of the linear movement motor shaft 114 protruding from the left side surface of the transmission case 36 is performed. Drive shaft 8
A belt 61 is wound between the linear drive pulley 80 on 1 and the vehicle speed tuning input pulley 66 on the vehicle speed tuning input shaft 75 protruding from the right side surface of the counter case. Then, these linear drive pulley 80, belt 61,
Tuning transmission line 15 including input pulley 66 for vehicle speed tuning
7 is disposed between the right side of the right support 155 of the rotation fulcrum 70 and the left side of the engine 35. Therefore, the reaper 2
Even if 2 is rotated to the left of the machine body about the support hole 156a, there is no interference by the tuning transmission line 157.

In other words, a transmission case 36 provided with an HST type continuously variable transmission consisting of a traveling HST 37 and a turning HST 38 with the rotation fulcrum portion 70 interposed therebetween, and the power from the transmission case 36 and the engine 35 are shifted and A counter case 64 that is controlled and transmitted to each processing system is arranged in front and rear, and a vehicle speed tuning input shaft 75 for inputting power synchronized with the traveling speed into the counter case 64 and a motor shaft of the traveling HST 37. A tuning transmission line 157 is provided to connect and interlock with a certain straight-moving motor shaft 114. The tuning transmission line 157 is provided on the right side opposite to the left side, which is the one side, with respect to the rotation fulcrum portion 70. 15
It is possible to facilitate the attachment and detachment of the mowing portion 22 and the side opening without being interfered with 7, and the belt and the chain itself of the tuning transmission line 157 to be easily attached and detached.

Next, the power transmission structure in the counter case 64 will be described with reference to FIGS. 9 to 22. As shown in FIGS. 9 to 17, in the counter case 64,
The first shaft 161, the second shaft 162, and the third shaft 163 in order from the front.
The fourth shaft 164 is horizontally installed at substantially equal intervals, and the transmission shaft 160 is directly supported in the front-rear direction on the right side of the counter case 64 above the first shaft 161. The threshing output shaft 91 and the direct input shaft 76 are fixed to the front and rear ends of the direct transmission shaft 160, and the bevel gear 167 is fixed to the direct transmission shaft 160 near the direct input shaft 76. There is.

The vehicle speed tuning input shaft 75 is fixed to the right end of the first shaft 161, and a one-way clutch 159 is formed at the left end of the first shaft 161. The vehicle speed tuning input shaft 75 and the first shaft 161 are formed. , And one-way clutch 159
To the vehicle speed tuning input shaft portion 62. In the one-way clutch 159, the claw clutch 165 is spline-fitted onto the first shaft 161, and the claw clutch 16 is
5 is urged to the left by a clutch spring 166 whose right end is fixed by a fixing ring 169, and a plurality of meshing teeth 165a are formed on the left side surface of the pawl clutch 165 while being inclined in the same circumferential direction. Has been done. Further, two clutch gears 170 are pivotally supported on the left side of the one-way clutch 159 and coaxially with the first shaft 161, and the clutch gear 170 is composed of a large diameter gear 170b and a small diameter gear 170c. On the right side surface of the large-diameter gear 170b, a meshing tooth 170a that can be fitted with the meshing tooth 165a is formed.

As a result, the meshing teeth 165a are constantly pressed by the meshing teeth 170a by the elastic force of the clutch spring 166, and when the machine body moves forward, the meshing teeth 165 are formed.
The first shaft 161 rotates in the direction in which a and the meshing tooth 170a are engaged (hereinafter referred to as “forward rotation”), and power is transmitted to the clutch gear 170. Rotating in the opposite direction (hereinafter referred to as "reverse rotation"), the meshing teeth 165
a and the meshing tooth 170a are disengaged, and the clutch gear 17
The power to 0 is cut off.

Since the one-way clutch 159 is arranged on the vehicle speed tuning input shaft portion 62 in the counter case 64 as described above, for example, the meshing teeth 165a of the claw clutch 165 are provided.
Even when the gear teeth 170a of the clutch gear 170 and the meshing teeth 170a of the clutch gear 170 repeatedly slide and collide violently in a power-off state when the vehicle is moving backward, the pawl clutch 165 slides rightward and leftward on the first shaft 161 securely supported. Unlike the conventional power transmission device such as a pulley or a gear, the one-way clutch 159 itself is less likely to be damaged, without causing damage to the power transmission device or defective fitting. . Further, since the one-way clutch 159 is located on the upstream side of the claw clutches 172 and 173 having a power cutoff, which will be described later, the one-way clutch 159 can be arranged at one place, and power transmission loss can be minimized.

That is, a counter case 64 is provided for shifting and controlling the power from the engine 35 and the mission case 36 and transmitting it to each processing system such as the reaper 22. The counter case 64 has a power synchronized with the traveling speed. In the combine provided with the vehicle speed tuning input shaft portion 62 for inputting, the vehicle speed tuning input shaft portion 62 is provided with a claw type one-way clutch 159 and the one-way clutch 159.
Is a transmission system from which the power from the vehicle speed tuning input shaft 62 is changed by the claw-type clutches 172 and 173, which are mowing speed changers, and is output to the mowing section 22.
Since it is arranged on the upstream side of 173, the durability and power transmission efficiency of the power transmission tool and the one-way clutch 159 can be improved.

Further, as shown in FIG. 10, the one-way clutch 159 is submerged below the oil surface 200 of the lubricating oil 218 stored in the counter case 64, and even if the meshing teeth 165a of the claw clutch 165 are engaged. Even when the gear teeth 170a of the clutch gear 170 repeatedly slide and collide violently, the lubricating oil 218 alleviates the impact at that time and absorbs noise.

That is, the one-way clutch 159 is
Since it is embedded in the oil sump in the counter case, vibration and noise of the one-way clutch 159 are suppressed, and the working environment can be improved.

Further, on the second shaft 162, a first claw clutch 172, a second claw clutch 173, and
Two fixed gears 174 are arranged. In the first claw clutch 172 of these, a high speed clutch gear 175 and a low speed clutch gear 17 having mesh teeth fixedly provided on the inner surface thereof.
6 is loosely fitted, and the high speed clutch gear 175 is always meshed with the large diameter gear 170b, and the low speed clutch gear 176 is always meshed with the small diameter gear 170c. Further, sliding clutch claws 177 having meshing teeth fixed on both left and right side surfaces are spline fitted between the high speed clutch gear 175 and the low speed clutch gear 176, and the sliding clutch claws 177 are A shift fork 178 is fitted therein, and the shift fork 178 is fitted over the fork shaft 179 so as to be movable, and is linked and linked to an operating means such as a reaping shift lever (not shown).

Also in the second pawl type clutch 173, the reaping maintenance clutch gear 1 having meshing teeth fixedly provided on the inner surface thereof.
80 and the mowing deceleration clutch gear 181 are loosely fitted, and the mowing maintenance clutch gear 180 and the mowing deceleration clutch gear 18 are
1, the sliding clutch claw 182 having meshing teeth fixed on the left and right side surfaces is spline-fitted, and the shift fork 183 is fitted to the sliding clutch claw 182. 183 also has the fork shaft 179.
It is externally fitted so as to be movable above, and is linked and interlocked with operating means such as a reaping drive switching pedal (not shown).

Further, the fixed gear 174 comprises a chain tuning gear 174a and a cutting tuning gear 174b, and the cutting tuning gear 174b is meshed with a transmission gear 184 fixedly mounted on the cutting output shaft 92, The power transmitted from the first claw clutch 172 and the second claw clutch 173 is output from the mowing output shaft 92 to the mowing unit 22.

A bevel gear 168, a double fixed gear 185, and a vehicle speed tuning input mechanism 186 are arranged in this order from the right on the third shaft 163, and the selection output shaft is provided at the left end of the third shaft 163. 93 is fixedly installed. The bevel gear 168 of these is meshed with the bevel gear 167 on the direct transmission shaft 160, and the power from the direct input shaft 76 is output from the threshing output shaft 91 to the threshing unit 20 and at the same time, the third shaft 163. I'm trying to be transmitted to.

The fixed gear 185 is the small-diameter gear 18
5a and a large diameter gear 185b, of which the small diameter gear 185a is always meshed with the reaping maintenance clutch gear 180, and the large diameter gear 185b is always meshed with the reaping reduction clutch gear 181.

Further, the vehicle speed tuning input mechanism 186 has one planetary gear mechanism, and the planetary gear mechanism is the third planetary gear mechanism.
A sun gear 187 engraved on the outer peripheral surface of the shaft 163, a plurality of planetary gears 188 meshing with the outer periphery of the sun gear 187, an internal gear 189a integrally formed with the ring gear 189 and meshing with the planetary gear 188, and a third gear It is composed of a carrier 191 etc. which is loosely fitted on the shaft 163 and pivotally supports the planetary gear 188. Among them, the planetary gears 188 are evenly arranged radially from the third shaft 163 and rotatably supported by the carrier 191 respectively, and also rotatably supported on the third shaft 163 provided with the sun gear 187. There is. And the ring gear 189
Is always meshed with the chain tuning gear 174a, and the vehicle speed tuning power transmitted to the second shaft 162 is input to the vehicle speed tuning input mechanism 186 via the ring gear 189.

As a result, the output of the constant rotation from the engine 35 is directly output from the input shaft 76 to the bevel gears 167 and 16.
After being transmitted to the third shaft 163 via
3 to the sorting device 71, while the sun gear 187
Is also transmitted. The constant rotation power transmitted to the sun gear 187 is combined with the vehicle speed tuning power input from the second shaft 162 via the ring gear 189, and is transmitted to the carrier 191.

On the fourth shaft 164, the feed chain clutch 192 and the sprocket 19 are arranged in this order from the right.
7 are arranged. In the feed chain clutch 192 of these, a sliding clutch claw 193 is spline-fitted on the fourth shaft 164, and the sliding clutch claw 19 is provided.
3 is urged to the left by a clutch spring 194 whose right end is fixed to the inner wall of the counter case 64, and
The sliding clutch pawl 193 is fitted with a half-shaped tip of a fork shaft 195 that is axially fixed to the counter case 64, and the fork shaft 195 is rotatably connected to an operating means (not shown). . Further, on the left side of the sliding clutch pawl 193, a clutch gear 19 having engaging teeth fixedly provided on the right side surface thereof is provided.
6 is loosely fitted, and the clutch gear 196 is always meshed with the output gear 191a formed on the carrier 191 in the vehicle speed tuning input mechanism 186.

The sprocket 197 is the fourth shaft 1
A sprocket 198 externally fitted and fixed onto the feed chain output shaft 94.
It is linked and linked via a chain 199.

As a result, the sliding clutch pawl 193 is constantly pressed to the left by the elastic force of the clutch spring 194, and when the fork shaft 195 is rotated in this state, the sliding clutch pawl 193 will move. 195 Sliding clutch claw 1
93 and the meshing teeth of the clutch gear 196 are engaged, and the clutch gear 196 → the sliding clutch pawl 193 → the fourth shaft 164 → sprocket 197 → chain 199 → sprocket 19
8 is transmitted to the feed chain 23 from the feed chain output shaft 94. On the contrary, by rotating the fork shaft 195, the sliding clutch pawl 1 is moved to the front semi-cylindrical portion.
When 93 is slid to the right, the engagement of the meshing teeth of the sliding clutch claw 193 and the clutch gear 196 is disengaged, and the power to the feed chain 23 is cut off.

With the above structure, during the normal straight cutting operation, as shown in FIGS. 12, 13, 18, and 19, the power 201 from the output shaft 83 of the engine 35 is used.
Is directly input into the counter case 64 from the input shaft 76, and the power 201a is generated by the bevel gears 167 and 168.
And power 201b, of which power 201a
Passes through the direct transmission shaft 160 and is output as constant power from the threshing output shaft 91 to the threshing unit 20. Power 201b is
When input from the bevel gears 167 and 168 to the third shaft 163, the sun gear 187 in the vehicle speed tuning input mechanism 186 branches into a power 201c and a power 201d, of which the power 201c is output from the sorting output shaft 93 to the sorting device 71.
Output as a constant power.

The power 202 from the straight drive shaft 81 of the mission case 36 is input from the vehicle speed tuning input shaft 75 into the counter case 64, passes from the one-way clutch 159 on the first shaft 161 through the clutch gear 170, and then passes through the first case.
It is input to the claw clutch 172. In the first claw type clutch 172, a reaping shift lever (not shown) is operated to move the shift fork 178 to the left and right, and the sliding clutch claw 177 is slid to the left and right so as to move the high speed clutch gear 175 or the low speed clutch gear 176. By engaging with, it is possible to shift to high and low speed two stages. And this power 20
2 is branched into power 202a and power 202b in the chain tuning gear 174a on the first shaft 161, of which power 202a passes from the mowing tuning gear 174b to the transmission gear 184 and from the mowing output shaft 92 to the mowing section 22. It is output as vehicle speed tuning power.

Further, the power 202b is transmitted from the chain tuning gear 174a to the planetary gear 188 via the ring gear 189, and in the planetary gear 188,
The power 201d transmitted from the sun gear 187 is combined to form the power 203. The power 203 is transmitted in the order of carrier 191, feed chain clutch 192, sprocket 197, chain 199, and sprocket 198, and is output from the feed chain output shaft 94 to the feed chain 23 as vehicle speed synchronizing power.

As described above, by securing the constant power 201d from the engine 35 and adding the power 202b which is synchronized with the vehicle speed from the mission case 36, it is possible to accelerate the rise of the conveying speed in the initial stage of the mowing work. Therefore, it is possible to prevent the occurrence of grain rod clogging due to poor conveyance.

When switching back, as shown in FIGS.
As shown in FIG. 3, FIG. 18, and FIG. 30, the sliding clutch pawl 177 is set to the neutral position by operating the reaping shift lever (not shown), and the power from the linear drive shaft 81 of the transmission case 36 is cut off. By operating the reaping drive switching pedal, the shift fork 183 is moved to the right, and the sliding clutch pawl 1
Slide 82 to the right to engage the reaping maintenance clutch gear 180. As a result, the power 201b from the output shaft 83 of the engine 35 is split into the power 201c and the power 210e in the small diameter gear 185a.

The power 201e is transmitted in the order of the reaping maintenance clutch gear 180-> the sliding clutch pawl 182-> the second shaft 162, and further, in the chain tuning gear 174a, the power 2 is transmitted.
01f and motive power 201g, of which motive power 201
f passes through the cutting synchronization gear 174b and the transmission gear 184,
The reaping output shaft 92 outputs a constant power to the reaper 22. The power 201g is combined with the power 201d in the same manner as the power 202b, and the feed chain output shaft 94
Is output to the feed chain 23 as constant power.

In this way, when the cutting drive switching pedal is operated so that the power 201f from the engine 35 can be output to the cutting unit 22 as a constant power, the case where the machine body is traveling at low speed or in reverse as in turning back However, sufficient power can be transmitted to the mowing section 22, and at a low speed, the mowing blade 24 is driven only at a low speed for reliable cutting, or when the vehicle is moving backward, the one-way clutch 159 operates to mitigate the mowing section 22. It is possible to surely solve the problem that the harvested grain rod does not drive at all and falls off during transportation.

When traveling at a high speed, FIG. 12 and FIG.
As shown in FIG. 3, FIG. 18, and FIG. 21, the reaper shift lever (not shown) is operated to set the sliding clutch pawl 177 to the neutral position, and the power from the linear drive shaft 81 of the transmission case 36 is cut off. By operating the reaping drive switching pedal, the shift fork 183 is moved to the left, and the sliding clutch pawl 1
82 is slid to the left to engage with the mowing deceleration clutch gear 181. As a result, the power 201b from the output shaft 83 of the engine 35 is branched into the power 201c and the power 210h in the large diameter gear 185b.

The power 201h is transmitted in the order of the mowing deceleration clutch gear 181, the sliding clutch pawl 182 and the second shaft 162, and the chain synchronizing gear 174a drives the power 2h.
01i and power 201j, of which power 201
i passes through the cutting synchronization gear 174b and the transmission gear 184,
The reaping output shaft 92 outputs a constant power to the reaper 22. The power 201j is combined with the power 201d in the same manner as the power 202b, and the feed chain output shaft 94
Is output to the feed chain 23 as constant power.

As described above, by operating the reaping drive switching pedal to output the motive power 201i from the engine 35 to the reaping section 22 as a constant motive power, the vehicle speed synchronizing power that is too fast as during high speed running can be obtained. Even when it is output to the mowing unit 22, it is possible to transmit appropriate power to the mowing unit 22, and it is possible to avoid troubles due to too fast mowing or transport of the rods.

Further, when the maximum load is applied to the HST such as running at the maximum speed, FIG. 12, FIG. 13, FIG. 18, FIG.
, The sliding clutch pawl 182 is slid to the left to engage the mowing deceleration clutch gear 181, and the shift fork 202 is moved to the right to be provided to the left of the clutch gear 170. The engaging bar 103 of the forced coupling clutch 171 is pushed into the clutch gear 170, and the clutch gear 170 is engaged and coupled to the first shaft 161. As a result, the power 201b from the output shaft 83 of the engine 35 is
In the large diameter gear 185b, power 201c and power 210
The motive power 210h is branched into the motive power 201k and the motive power 201l in the cutting deceleration clutch gear 181.

Of these, the power 201l is transmitted from the sliding clutch claw 182 to the second shaft 162, and is further branched into the power 201m and the power 201n in the chain tuning gear 174a, of which the power 201m is the cutting tuning gear 17.
4b → Transmission gear 184, and is output as constant power from the cutting output shaft 92 to the cutting unit 22. Power 201n is
Combined with the power 201d, the feed chain output shaft 94
Is output to the feed chain 23 as constant power.

Then, the power 201k is transmitted in the order of the sliding clutch pawl 182 → the second shaft 162 → the first pawl type clutch 172 → the clutch gear 170 → the first shaft 161, and is driven straight from the vehicle speed tuning input shaft 75. H for traveling via shaft 81
Input to ST37. The first claw clutch 172
Thus, it is possible to switch the power 201k between the high and low stages.

In this way, by operating the forcible coupling clutch 171 and outputting the power 201k from the engine 35 as a constant power to the traveling HST 37, the transmission efficiency of HST is poor as during high speed traveling. In case of constant power 201k from engine 35, HST
It is designed to help improve driving performance.

Next, the transmission structure from the counter case 64 to the reaping input shaft 72 will be described with reference to FIGS. 6, 7, and 23 to 26. As described above, the harvesting output shaft 92 of the counter case 64 is fixedly provided with the output pulley 96, and the output pulley 96 is attached to the harvesting input shaft 72 via the intermediate transmission mechanism 77 provided in the rotation fulcrum portion 70. It is linked and linked.

In the intermediate transmission mechanism 77, the base portion 158a of the rotating body 158 is horizontally rotatably supported in the support hole 156a, and the right portion of the input shaft 205 is vertically rotatable on the base portion 158a. The input shaft 205 is supported while being supported.
An intermediate gear 207 is fixedly installed on the right part. On the other hand, a reaping input pulley 204 is fixedly installed at the left end of the input shaft 205, the reaping input pulley 204 is linked and interlocked with the output pulley 96 by a belt 206, and a tension pulley 214 is provided in the middle of the belt 206. It is arranged. The tension pulley 214 is constantly urged from the upper front to the lower front by a traction spring 216 on a mounting frame 215 provided on the left support base 154 of the rotation support unit 70.

Further, a cutting input gear 208 is meshed with the intermediate gear 207, and a fixed cover 158b is detachably attached to the base portion 158a from a diagonally upper front side of the cutting input gear 208 by fixing tools 211 and 212 such as bolts. It is fixed to. The left end of the reaping input shaft 72 is connected to the reaping input gear 208.

In such a configuration, even when the reaper 22 is side-opened toward the left side of the machine, the intermediate transmission mechanism 77 is on the same side as the side-open side.
The reaper 22 is not interfered by the intermediate transmission mechanism 77, and there is no obstacle between the outside of the machine and the intermediate transmission mechanism 77.

That is, in the combine in which the mowing section 22 is arranged in the front of the machine body and the rotation fulcrum section 70 capable of rotating the mowing section 22 to one of the left and right sides is provided, the mowing section 2
Power to the reaping input shaft 72 that drives the motor 2 is input from the same side as the one side via the intermediate transmission mechanism 77, so even when performing inspection and maintenance around the mission case 36, the reaper 22, and the like. Since the reaper 22 can be easily pivoted to one side to open the side, and the intermediate transmission mechanism 77 can be easily accessed, maintainability is greatly improved.

Further, as shown in FIG. 23, the output pulley 9
6. Since the cutting transmission line 217 including the input belt 206 and the cutting input pulley 204 is arranged on the left side of the rotation fulcrum portion 70, even when the cutting portion 22 is side-opened (position 209 → position 210), the input belt It is only necessary to loosen 206 and move it to the position 206a. Moreover, by using the tension pulley 214 and the like, the input belt 2
By setting 06 so that it is always stretched downward, the input belt 206 causes the output pulley 96 and the cutting input pulley 204
Can be prevented from falling off.

That is, in the intermediate transmission mechanism 77, the reaping output shaft 92 is arranged below and rearward of the rotation fulcrum portion 70, and the reaping transmission line 217 from the reaping output shaft 92 to the rotation fulcrum portion 70 has a rotation fulcrum. Since the cutting unit 22 is provided on the same side as the one side with respect to the portion 70, when the cutting unit 22 is opened sideways, the cutting unit 22 is rotated in a direction in which the belt 206 in the cutting transmission line 217 is loosened, so that the belt 206 is broken. It is also possible to prevent the belt 206 from coming off without fail by arranging the tension pulley 214 or the like at an appropriate position and tensioning the belt 206.

Further, as shown in FIG. 24, the reaping input gear 208 connected to the reaping input shaft 72 of the reaping unit 22 has a base portion 158a by fixing tools 211 and 212 such as bolts.
It is possible to easily remove the input belt 206 from the base 158a even when the reaper 22 is removed from the machine body.

That is, the rotating body 158 pivotally supported by the rotating fulcrum portion 70 has the input shaft 20 having the intermediate gear 207 fixedly mounted thereon.
5, and an input pulley 204 is fixed to an end of the input shaft 205 extending toward the one side. The input pulley 204 is connected to an output pulley 96 on the cutting output shaft 92 by a belt 206. Since the input gear 208 on the reaping input shaft 72 is detachably engaged with the intermediate gear 207, the reaper 22 can be easily attached and detached without removing the belt or the like.

[0069]

Since the present invention is constructed as described above,
It has the following effects. That is, as in claim 1, a counter case that shifts and controls the power from the engine or the mission case and transmits it to each processing system such as the reaper is provided, and the counter case is provided with the power synchronized with the traveling speed. In a combine provided with a vehicle speed tuning input shaft section for inputting, a claw-type one-way clutch is provided on the vehicle speed tuning input shaft section, and the one-way clutch shifts power from the vehicle speed tuning input shaft section by a cutting gear shifting section. Since the transmission system up to outputting to the mowing unit is arranged on the upstream side of the mowing transmission, the durability and power transmission efficiency of the power transmission tool and the one-way clutch can be improved.

Since the one-way clutch according to the first aspect is buried in the oil sump in the counter case as described in the second aspect, vibration and noise of the one-way clutch are suppressed, and the working environment can be improved. Of.

According to a third aspect of the present invention, the drive shaft is connected to one end side of the crankshaft of the engine, the flywheel and the belt drive section are provided on the other end side, and the engine is provided with a vibration isolating member made of an elastic body. In the combine fixed to the chassis via the elastic constant of the vibration isolator on the other end side,
Since it is configured to be higher than the vibration isolating member on the one end side, it is possible to accurately cope with the load applied to the output shaft of the engine from the outside, so that the vibration and noise of the engine can be greatly reduced and the durability of the engine output part is improved. be able to.

As in claim 4, since power is output from the other end side of claim 3 to a high torque processing system having a high peak torque, such as a threshing portion and a grain tank, the protrusion length from the engine is increased. The length is short, the load on the output part is small, and the durability is greatly improved.

[Brief description of drawings]

FIG. 1 is an overall left side view of a combine.

FIG. 2 is a plan view of the same.

FIG. 3 is a right side view of the same.

FIG. 4 is a front view of the same.

FIG. 5 is a skeleton diagram showing a power transmission configuration outline.

FIG. 6 is a front view of the front part of the machine body.

FIG. 7 is a side view of the same.

FIG. 8 is a plan view of the same.

FIG. 9 is a left side view of the counter case.

FIG. 10 is a right side view of the same.

FIG. 11 is a front view of the same.

FIG. 12 is a plan sectional view of the same.

FIG. 13 is a plan sectional view showing each clutch mechanism of the counter case.

FIG. 14 is a side sectional view of a pawl clutch.

FIG. 15 is a plan view of the same.

FIG. 16 is a side sectional view of a clutch gear.

FIG. 17 is a plan view of the same.

FIG. 18 is a skeleton diagram showing a power transmission configuration from the engine to each processing system.

FIG. 19 is a schematic diagram showing a power transmission path during a normal straight cutting operation.

FIG. 20 is a schematic diagram showing a power transmission path at the time of turning back.

FIG. 21 is a schematic diagram showing a power transmission path during high-speed traveling.

FIG. 22 is a schematic diagram showing a power transmission path during HST assistance.

FIG. 23 is a plan view showing an intermediate transmission mechanism.

FIG. 24 is a side view of the rotating body.

FIG. 25 is a rear sectional view of the same.

FIG. 26 is a rear sectional view of the reaping input gear.

[Explanation of symbols]

20 Threshing Department 22 Mowing part 29 grain tank 35 engine 36 mission case 51 crankshaft 59 flywheel 62 Vehicle speed tuning input shaft 63 drive shaft 64 counter case 82 Output shaft 83 Output shaft 87/88 Anti-vibration member on one end side 89/90 Anti-vibration member on the other end side 159 one-way clutch 172 ・ 173 Mowing gear shifting unit

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) B60K 17/04 B60K 17/04 C 3J048 17/26 17/26 Z 17/28 17/28 C F16F 15 / 08 F16F 15/08 WF Term (reference) 2B074 AA02 AB01 AC02 AD05 AF02 AG03 BA11 CA01 CD02 CD10 DA01 DA02 DA03 DB03 DD01 DD02 DF03 2B076 AA03 CA19 DA05 DA09 DB06 3D039 AA03 AA04 AA25 AA31 AB13 AB22 AD21 AC32 AD11 AD32 AD31 AD11 AD32 AD11 AD32 AD11 AA08 AB10 AB11 EA04 EA05 EA07 3D043 AA08 AB10 AB11 BA01 BA03 BC02 BC03 BC05 BC06 BC11 BC13 BC15 BE03 3J048 AA01 CB01 DA01 EA01

Claims (4)

[Claims] 1. A counter case that shifts and controls power from an engine or a mission case and transmits the power to each processing system such as a mowing unit, and the counter case is a vehicle speed tuning for inputting power in synchronization with a traveling speed. In a combine provided with an input shaft portion, a claw-type one-way clutch is provided on the vehicle speed tuning input shaft portion, and the one-way clutch outputs the power from the vehicle speed tuning input shaft portion to the cutting portion by shifting the power from the cutting speed shifting portion. In the transmission system up to, the combine is arranged upstream of the mowing transmission. 2. The combine according to claim 1, wherein the one-way clutch is arranged in an oil sump in a counter case. 3. A drive shaft is connected to one end side of a crankshaft of the engine, a flywheel and a belt drive section are provided to the other end side, and the engine is fixed to a chassis through a vibration isolating member made of an elastic body. In the combine that we set up,
The combine, wherein the elastic constant of the vibration isolating member on the other end side is higher than that of the vibration isolating member on the one end side. 4. The combine according to claim 3, wherein power is output from the other end side to a high-torque processing system having a high peak torque, such as a threshing unit and a grain tank.