JP4419350B2 - Traveling device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a traveling device such as a combine and a tractor.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, in a vehicle having a pair of left and right crawler travel devices such as a combine, each continuously variable transmission mechanism (hereinafter referred to as “HST”) for traveling and turning, and left and right side clutch mechanisms, a differential transmission mechanism, a reverse counter gear 2. Description of the Related Art A traveling device that includes a mechanism and the like and continuously and continuously reverses an axle inside a turn by driving the differential transmission mechanism by a turning HST is known.
[0003]
[Problems to be solved by the invention]
As described above, the conventional traveling apparatus is configured to rotate the differential transmission mechanism by the turning HST and to make a turn by making the left and right axles differential, but the turning HST controls the output rotation at a very low speed. This makes it difficult to turn at extremely low speeds. Further, since the differential gear in the differential case of the differential transmission mechanism always rotates during straight travel, there is a problem that durability of the differential case is lowered.
The present invention has been made to solve the above-described conventional problems, and an object of the present invention is to provide a traveling device that can perform a smooth turn and that has a simplified configuration. .
[0004]
[Means for Solving the Problems]
To achieve the above object, the present invention is, on the left and right sides of the first center gear (16) provided in the service id clutch shaft (3), the left and right side clutch performing power intermittently to the left and right traveling devices (17L , 17R) and is provided, is provided a pair of right and left planetary gear mechanism on the right and left sides of the steering clutch shaft (3) second center gear (19 fixed to the transmission downstream side of the differential shaft (4) of) the first The left and right sides to which the driving force of the side clutch shaft (3) is transmitted when the first center gear (16) is engaged with the second center gear (19) and the left and right side clutches (17L, 17R) are in the connected state. the clutch gear (18L, 18R), the left and right carrier (20L, 20R) of said planetary gear mechanism and respectively engaging the left and right brake for controlling the rotation of left and right carrier (20L, 20R) (71 , 71R) and is provided, the left and right hollow respectively right and left planetary gear mechanism the sun gear (Z1L, a structure assembled integrally with Z1R), left and right cover for covering the planetary gear mechanism of the left and right from the outside (62L, 62R) and removed, and the left and right planetary gear mechanism and the travel device, characterized in that where the structure can be removably attached to the sun gear (Z1L, differential shaft via a Z1R) (4) without disassembling the mission.
[0005]
[0006]
【The invention's effect】
According to the present invention, it is possible to perform a circular smooth turning, moreover, a hollow sun gear (Z1L, Z1R) integrated planetary gear mechanism, without degrading the mission, through the sun gear (Z1L, Z1R) because of the configuration that can be detachably attached to the differential shaft of the transmission body (4) Te, Ru can be easily performed maintenance.
[0007]
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is an overall view showing an example of a combine relating to the present invention.
The illustrated combine includes a crawler a, a crawler drive shaft (also referred to as an axle or a wheel shaft) b, a cutting part c, a feed chain d that feeds the harvested culm to a threshing machine, and a threshing machine e. And a grain tank f for storing the threshed grain and an auger g for discharging the stored grain to the outside of the machine.
[0009]
FIG. 2 is a switch layout diagram of a combine driver's seat.
The HST lever 41 tilts back and forth to increase or decrease the vehicle speed. When the HST lever 41 is tilted forward from the neutral position in the figure, the speed increases in the forward direction, and when tilted backward, the speed increases in the reverse direction. When the vehicle is returned from the forward or reverse position to the neutral position, the vehicle decelerates and the aircraft stops at the neutral position.
The accelerator lever 42 tilts back and forth to open and close the throttle to increase or decrease the engine speed. When it is tilted backward, the throttle opens to increase the engine speed, and when it is tilted forward, the throttle closes to close the engine speed. Lower.
The power steering lever 43 is tilted back and forth and to the left and right to operate raising and lowering of the cutting part and turning of the machine body. The cutting part rises when tilted backward from the neutral position, and the cutting part descends when tilted forward. Also, the aircraft turns left when it is tilted to the left, and turns right when it is tilted to the right.
[0010]
Next, the configuration of the transmission device will be described.
3 is a sectional view of the traveling device according to the present invention, FIG. 4 is a side view thereof, FIG. 5 is a transmission line diagram thereof, FIG. 6 is an external perspective view of a planetary gear mechanism, and FIG.
Power from the engine is transmitted to the input shaft 7 of the HST 9 via an engine pulley attached to the output shaft of the engine and an input pulley 8 wound by a belt. Then, by driving the output shaft 10 of the HST 9, the auxiliary transmission shaft 1 is driven via the gear 12 of the auxiliary transmission shaft 1 that meshes with the gear 11 provided on the output shaft 10. In addition to the gear 12, the auxiliary transmission shaft 1 is provided with a gear 14a, a gear 14b, and a gear 14c. The counter transmission 2 is engaged with gears 15a, 15b, and 15c of the counter shaft 2 that mesh with the auxiliary transmission gears 14a, 14b, and 14c. Thus, the counter shaft 2 is driven. By switching the shifter (not shown), the meshing positions of the auxiliary transmission gears 14a, 14b, 14c and the gears 15a, 15b, 15c of the counter shaft 2 are switched, whereby the counter shaft 2 is shifted to high speed, medium speed, and low speed. To drive. Further, a cutting output pulley 13 is attached to one end of the auxiliary transmission shaft 1 and is wound around a cutting input pulley 32 (see FIG. 3) for driving the cutting unit by a belt. A one-way clutch is interposed between the auxiliary transmission shaft 1 and the cutting output pulley 13.
[0011]
By driving the counter shaft 2, the side clutch shaft 3 is driven via a center gear (first center gear) 16 of the side clutch shaft 3 that meshes with the gear 15 b provided on the same counter shaft 2.
[0012]
The side clutch shaft 3 is provided with two friction multi-plate clutches, a side clutch 17R and a side clutch 17L, symmetrically with respect to the center gear 16 and tilted by the tilting operation of the power steering lever 43. The hydraulic cylinder is operated according to the operation angle (detected by a potentiometer (not shown)), and the side clutch 17R and the side clutch 17L are controlled to be in a connected state and a non-connected state, respectively. Straight running of the aircraft, the left and right side clutch 17R and the side clutch 17L transmits the driving force both in the compression spring (not shown) and always connected, hydraulically.
[0013]
The center gear 16 provided on the side clutch shaft 3 meshes with a center gear (second center gear) 19 fixed to the differential shaft 4 of the differential transmission mechanism.
Here, the differential transmission mechanism will be described.
In the present embodiment, the differential transmission mechanism is constituted by a planetary gear mechanism. Referring to FIGS. 3 and 5 to 7, this differential transmission mechanism is provided symmetrically with respect to the center gear 19 of the differential shaft 4. The right differential transmission mechanism has a planetary gear 21R composed of two gears Z2 (R) and Z3 (R) with different gear diameters and a planetary gear 23R on the inner peripheral surface side of the carrier 20R shaped like a shallow cylinder. Are alternately arranged, and one planetary gear 21R is supported at both ends by the carrier 20R and its input gear 20 (G) R by a pin 35 of its central shaft and is rotatably supported. The other planetary gear 23R is supported at both ends by the center shaft 36 on the carrier 20R and the input gear 20 (G) R and is rotatably supported. Further, two types of opening holes 37 and 38 are formed in the peripheral surface of the carrier 20R, and a part of the outer periphery of the gear Z2 (R) of the planetary gear 21R is exposed from the one opening hole 37, and the other side. A part of the outer periphery of the planetary gear 23R is exposed from the opening hole 38. When these gears are completely accommodated in the carrier 20R, the size of the carrier increases. However, the size of the carrier can be reduced by providing such an opening hole.
[0014]
Further, the sun gear Z 1R hollow fixed to the differential shaft 4 is disposed at the center of the carrier 20R, rotatably configured carrier 20R is bearing differential shaft 4 side around the differential shaft 4 is doing. Further, the rotation gear 22R is rotatably configured to be a bearing to the sun gear Z 1R around differential shaft 4 while being loaded into the inside of the carrier 20R having two gear Z4 (R) and 24R having different gear diameters is doing. Gear portion of the sun gear Z 1R is arranged on the casing side surface. In order to increase the reduction ratio, the sun gear needs to have a small diameter. However, if the sun gear is arranged on the center side, the entire shaft becomes small in diameter, making it difficult to ensure strength. The output gear is on the side of the case. Although it arrange | positions at the side surface side and a case width | variety becomes large, such a malfunction can be eliminated by arrange | positioning at the case side surface side as mentioned above.
[0015]
Here, as can be seen with reference to FIG. 5, the sun gear Z 1R meshes with the gear Z2 (R) of the planetary gear 21R, the gear Z3 (R) of the planetary gear 21R meshes with the planetary gear 23R, and the The planetary gear 23R meshes with the gear Z4 (R) of the rotating gear 22R. The side clutch gear 18R interposed on the side clutch shaft 3 meshes with the carrier 20R.
As described above, the planetary gear mechanism is configured so as to be integrated with the hollow sun gears Z 1R and Z1L . Therefore, the planetary gear mechanism can be easily assembled and the difference between the planetary gear mechanisms via the hollow sun gears Z 1R and Z1L. The movable shaft 4 can be configured to be detachable. Therefore, the planetary gear mechanism can be detached from the transmission main body, and maintenance can be easily performed.
The right differential transmission mechanism has been described above, but the configuration of the left differential transmission mechanism is the same.
[0016]
When the left and right side clutches 17R and 17L are engaged, that is, in the connected state, the driving force of the side clutch shaft 3 is transmitted to the side clutch gears 18R and 18L, and at the same time, the center gear 19 of the differential shaft 4 is turned on. Is transmitted to the differential shaft 4 through the gears 24R and 24L, gears 26R and 26L, gears 27R and 27L, gears 28R and 28L, gears 29R and 29L, and gears 30R and 30L. The left and right axles b and b are driven. In the drawing, 31R and 31L indicate sprockets attached to the left and right axles b and b, respectively.
[0017]
In the above configuration, when the engine is started and the airframe travels straight, power is transmitted from the output shaft 10 of the HST 9 to the auxiliary transmission shaft 1 and the counter shaft 2. Then, the side clutch shaft 3 is driven via the center gear 16 of the side clutch shaft 3 that meshes with the gear 15b of the counter shaft 2. When going straight, the left and right side clutches 17R, 17L are in the same state and are in a connected state. Therefore, the driving force of the side clutch shaft 3 is transmitted to the left and right side clutch gears 18R, 18L, and both the side clutch gears 18R, 18L are rotationally driven.
[0018]
The power is transmitted to the carriers 20R and 20L of the differential transmission mechanism that mesh with the left and right side clutch gears 18R and 18L, respectively, and at the same time, the differential shaft 4 that meshes with the center gear 16 of the side clutch shaft 3 Power is transmitted to the center gear 19 and the differential shaft 4 is driven to rotate. The rotation of the differential shaft 4 causes the sun gears Z 1R and Z1L to rotate, and further the gears Z2 (R, L), the gears Z3 (R, L), the planetary gears 23R, The driving force is sequentially transmitted to 23L, the gears Z4 (R, L) of the rotary gears 22R, 22L, and the gears 24R, 24L. During straight travel, the rotation of the center gear 19 of the differential shaft 4 and the carriers 20R and 20L coincides. In FIG. 7, the rotation direction of another gear when the gear Z4 (R, L) rotates counterclockwise is indicated by an arrow.
And the left and right axles b, b are rotationally driven in the same direction at the same speed.
[0019]
Next, a description will be given of when the aircraft is turning.
For example, when the power steering lever 43 is tilted to the right and the aircraft is turned to the right, when the power steering lever 43 is tilted, the side clutch 17R on the tilting operation side is first disconnected. At the same time, according to the tilting operation angle of the power steering lever 43, when the vehicle turns by the gear speed ratio of the sun gear Z1R, the gear Z2 (R) of the planetary gear 21R, the gear Z3 (R), and the gear Z4 (R) of the rotating gear 22R. The rotation speed of the rotation gear 24R changes.
[0020]
FIG. 8 is a diagram showing the relationship among the rotational speeds of the carrier 20 (R), the sun gear Z1R , and the rotating gear Z4 (R).
When the right turning, the sun gear Z 1R is rotated at a constant rotational speed by integration of the differential shaft 4 in the same manner as in the straight ahead. When the rotational speed of the carrier 20R is reduced according to the tilting operation angle of the power steering lever 43, the rotational speed of the rotary gear Z4 (R) is also reduced. Thus, while the outer side and the inner side of the turn are rotating in the same direction and the inner side of the turn is rotating lower than the outer side, the turning is performed at a gentle turning angle (herein referred to as “mild turn”). If the gear ratio of the planetary gear mechanism is set to 1/3, the gear Z4 (R) is zero as shown in the figure when the rotation speed of the carrier 20R becomes 1/3 of the rotation speed of the sun gear Z1 (R). When the axle b on the inside of the turn stops rotating, it becomes a brake turn. Further, when the rotation speed of the carrier 20R is decelerated, the gear Z4 (R) is in a reverse rotation state, and the outer side and the inner side of the turning are rotated in the opposite directions to form a spin turn.
[0021]
Thus, if the gear transmission ratio is set, the above-described mild turn, brake turn, and 1/3 spin turn are possible. When the side clutch 17R is actuated steplessly, the stepless speed change can be performed up to 1/3 spin turn. In addition, more accurate turning control can be performed by detecting the rotation speed of any of the transmission shafts with a rotation sensor and performing feedback control to the hydraulic cylinder.
Although the above description has been made on the right turn, in the case of the left turn, the side clutch 17L is disengaged, and the rest is the same as the operation in the case of the right turn described above.
[0022]
Here, the hydraulic layout shown in FIG. 9 will be described. When the engine 33 is started, the oil in the oil tank 52 is sucked through the gear pump 50 and sent to the control valve 53, where it is divided into left and right. Sent to left and right side clutches. The left and right side clutches 17L and 17R are brought into a connected state (an engaged state) by the hydraulic pressure. Further, the oil is sent from the oil tank 52 to the HST 9. When the HST 9 is not used, a part is returned to the oil tank 52 via the oil cooler 54. Further, the oil tank 52 is sent to a cutting up / down cylinder 58, an auger up / down cylinder 59, a pitching cylinder 57, and left and right rolling cylinders 56 through a control valve 55.
[0023]
Further, as can be seen from the side view of FIG. 4, the above-described transmission device has a side clutch and a differential transmission mechanism disposed between the crawler a and the step 61 for getting on and off. The side clutch and the differential transmission mechanism can be maintained at a position where the driver's seat does not get in the way.
Further, since the side clutch shaft 3 and the differential shaft 4 are arranged substantially horizontally, the height of the mission can be lowered correspondingly, and interference with other components can also be reduced.
Further, since the differential transmission mechanism is arranged on the front side of the transmission device, maintenance of the planetary gear mechanism having a complicated structure is easy.
[0024]
Referring to FIG. 3, the left and right drive shafts 6R, 6L on the upper side of the left and right axles b, b have a configuration in which the shaft 6R on the side where the mowing transmission vertical frame (not shown) is located is shortened. . According to such a configuration, the harvester can be brought close to the threshing machine in the combine, and the length of the machine body can be made compact.
[0025]
Further, as shown in FIGS. 3 and 4, left and right covers 62R and 62L are provided to cover the side clutch portion and the differential transmission mechanism portion from the outside. Thereby, the inspection and maintenance of the whole side clutch part and the differential transmission mechanism part, replacement | exchange, etc. can be performed easily, without disassembling a transmission.
Further, the pair of left and right planetary gear mechanisms (differential transmission mechanism) described above is configured to control the rotation of the carriers 20R and L with the pair of left and right brakes 71R and L, and the difference between the inner diameter portions of the brakes 71R and L A bearing 72 for supporting the moving shaft 4 is provided. Thereby, the dimension between bearings can be shortened, the bearing life can be improved, and the shaft can be prevented from bending.
[0026]
Further, in the planetary gear mechanism described above, the planetary gear mechanism is configured by approximating the outer diameter of the carrier 20 (R, L) and the maximum diameter portion of the planetary gears 21R and 23R disposed in the carrier. The whole can be made compact. As shown in FIG. 11, the carrier 20R is supported on the sun gear Z1R side via a bearing 73, and the carrier input gear 20 (G) R is supported on the rotary output gear 22R side via a needle bearing 74. ing. That is, the carrier case constituted by carrier 20R and the input gear 20 (G) R, for constitution with both ends supported by the sun gear Z 1R and the rotation output gear 22R, can reliably support the carrier case, the carrier The meshing of each gear is properly maintained.
[0027]
As indicated by a, b, c in FIG. 11, between the planetary gear 21R of the planetary gear mechanism, by a meshing configuration of three rows of gears and 23R, to the sun gear Z 1R or we rotate the output gear 22R The reduction gear ratio in the planetary gear mechanism can be increased. In addition, when the two rows configuration, it is necessary to the planetary gears 21R meshing with the sun gear Z 1R larger diameter, therefore it planetary gear mechanism becomes large, it size by a three-row configuration as described above The reduction ratio can be taken and it can be made compact.
[0028]
Further, in the arrangement of the planetary gear mechanism shown in FIG. 7, the rotating shaft 36 of the planetary gear 23R that meshes with the gear Z4 (R) of the rotating gear 22R is changed from the rotating shaft 35 of the planetary gear 21R that meshes with the sun gear Z1R. A configuration in which the distance from the center is arranged on the large diameter side, that is, “B” in FIG. 7 is configured to be larger than “A”. To a large reduction ratio by the planetary gear, the sun gear Z 1R or al planetary gears 21R and it is necessary to increase the reduction ratio between the rotation gear 22R from the gear Z3 (R), in order that the gear Z3 (R ) Need to reduce the number of teeth. By configuring as described above, this gear ratio problem can be solved, and as a result, the reduction ratio of the planetary gear mechanism can be increased.
[Brief description of the drawings]
FIG. 1 is an overall side view showing an example of a combine according to the present invention.
FIG. 2 is a switch layout diagram of a combine driver's seat.
FIG. 3 is a cross-sectional view of a transmission device.
FIG. 4 is a side view of the transmission device.
FIG. 5 is a transmission diagram of the transmission device.
FIG. 6 is an external perspective view of a planetary gear mechanism.
FIG. 7 is a cross-sectional view showing the arrangement of gears of the planetary gear mechanism.
FIG. 8 is a diagram showing the relationship of gear rotation speed in the planetary gear mechanism.
FIG. 9 is a hydraulic layout diagram of the travel device.
FIG. 10 is an enlarged cross-sectional view of a side clutch portion and a planetary gear mechanism.
FIG. 11 is a cross-sectional view of a main part of the planetary gear mechanism.
[Explanation of symbols]
a crawler b crawler drive shaft c cutting part d feed chain e threshing machine f grain tank g auger 1 auxiliary transmission shaft 3 side clutch shaft 4 differential shaft 9 HST
13 Cutting output pulley 14a Sub transmission gear 14b Sub transmission gear 14c Sub transmission gear 16 Center gear (first center gear)
17R Side clutch 17L Side clutch 18R Side clutch gear 18L Side clutch gear 19 Center gear (second center gear)
20R carrier 20L carrier 21R planetary gear 21L planetary gear 22R rotation gear 22L rotation gear 23R planetary gear 23L planetary gear 25 parking brake 41 HST lever 42 accelerator lever 43 power steering lever
62R right cover
62L left cover
Z1L left sun gear
Z1R right sun gear

Claims (1)

The left and right sides of the first center gear (16) provided in the service id clutch shaft (3), the left and right side clutch (17L, 17R) for performing power intermittently to the left and right traveling device is provided, the side clutch shaft (3 ) Is provided with a pair of left and right planetary gear mechanisms on both the left and right sides of the second center gear (19) fixed to the differential shaft (4) on the lower transmission side , and the first center gear (16) is connected to the second center gear ( 19) and the left and right side clutch gears (18L, 18R) to which the driving force of the side clutch shaft (3) is transmitted when the left and right side clutches (17L, 17R) are in the connected state are connected to the planetary gears. left and right carrier (20L, 20R) of the mechanism and the respective engagement, the left and right brakes (71L, 71R) and provided for controlling the rotation of left and right carrier (20L, 20R), the left and right planet gears The respective structure left and right hollow sun gear (Z1L, Z1R) a structure assembled integrally with, remove the left and right cover covering the planetary gear mechanism of the left and right from the outside (62L, 62R), without disassembling the mission the left and right planetary gear mechanism the sun gear (Z1L, Z1R) running device being characterized in that a configuration that can be removably attached to the differential shaft via the (4).

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