JP5295331B2 - Farm work vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a working vehicle capable of improving a standing start or creep-speed travelling performance and capable of easily improving the working efficiency even in the high-speed movement work with a large load. <P>SOLUTION: This working vehicle includes: a hydraulic pump 28 and a hydraulic motor 29 as a hydraulic transmitting mechanism 30 for transmitting driving force of an engine 2; and a synthetic output shaft 42 for outputting converted speeds by synthesizing the output from the engine 2 and the output from the hydraulic motor 28. The hydraulic pump 28 is controlled to normally or reversely rotate so as to rotate the synthetic output shaft 42 in one direction at converted speeds. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

The present invention relates to combine harvesters and rice transplanters-tractor of any agricultural working vehicle for threshing process harvests continuously culms comprise e.g. reaper and threshing unit.

  Conventionally, gear transmission has high power transmission efficiency, but there is a problem that the operability cannot be improved by stepped shifting. In addition, the hydraulic continuously variable transmission mechanism has excellent operability due to the continuously variable transmission that can start from zero, with the initial speed starting from zero, but there is a limit to the power transmission efficiency and there is a problem that the power loss at low speed increases. is there. A belt type continuously variable transmission mechanism using a V-belt and a pulley can perform a highly efficient continuously variable transmission, but there is a problem that the initial speed cannot start from zero. Therefore, work vehicles such as combiners require smooth entry / exit of the field, shifting operation with less shock, starting operation that does not require a clutch, speed adjustment adapted to the situation such as work or the surface, etc., high power transmission efficiency, and zero start A continuously variable transmission that is possible and a simple gear shifting operation are desired. Therefore, the operability when using hydraulic pressure without the power loss due to the combined use of the planetary gear mechanism with the hydraulic transmission mechanism and the use of the hydraulic transmission mechanism alone There is a means for forming a complex transmission mechanism that is compatible with high transmission efficiency when a gear (mechanism) is used.

JP 2000-127782 A JP-A-53-120047

  However, in this conventional complex transmission mechanism, a variable displacement type is used for the hydraulic pump constituting the hydraulic transmission mechanism and a constant displacement type is used for the hydraulic motor, and an operation arm for operating the swash plate of the hydraulic pump is −1. When changing from neutral to +1, the output of the combined transmission mechanism is changed from 0 to the maximum rotation, and the output of the combined transmission mechanism is switched between forward and reverse by the forward / reverse switching mechanism to move forward and backward. In addition to the structural complexity of requiring a separate forward / reverse switching mechanism, the forward / reverse switching mechanism is required for each forward / reverse operation lever during forward / backward travel. There was a troublesome operation such as switching operation.

Accordingly, the present invention is intended to provide agricultural work vehicle which has been subjected to improvement considering these situation.

In order to achieve the object, the invention according to claim 1 is directed to a hydraulic pump (28) and a hydraulic motor (29) as a hydraulic transmission mechanism (30) for shifting and outputting the power of the engine (21), A planetary gear mechanism (41) that combines the power of the engine (21) and the shift output of the hydraulic motor (29), and the combined output of the planetary gear mechanism (41) is transmitted as a rotational force in one direction from zero to the maximum speed. combined output shaft (42) to be, and in agricultural work vehicle equipped with a transmission case (22) having PTO output shaft (34), wherein the motor shaft of the hydraulic motor (29) (35) the sun gear (36) engaging shaft is supported, said sun gear (36). to the free rotation shaft supporting the carrier gear (37), rotatably mounted planetary gears (38) to the carrier gear (37), the flop to said sun gear (36) Netarigiya (38) are meshed, the planetary gear (38) to provide a ring gear (40) to be engaged, is engaging shaft supported the ring gear (40) to said combined output shaft (42), said sun gear (36), wherein The planetary gear (38) and the ring gear (40) form the planetary gear mechanism (41), and the transmission output of the hydraulic motor (29) and the one-way transmitted from the engine (21) to the carrier gear (37). by combining the constant rotation force, and configured to communicate to said synthesized output shaft from the ring gear as a one-way rotational force of zero to the maximum speed (40) (42), the pump shaft before Symbol hydraulic pump (28) (31) while configured to drive the PTO output shaft (34) in the in the maximum reverse angle swash plate tilt angle of the hydraulic pump (28) Sang When the rotation speed of (36) is set to the maximum reverse rotation speed, the carrier gear (37) is configured such that the rotation of the ring gear (40) becomes zero by synthesizing a constant rotational force in one direction of the carrier gear (37). ) And the planetary gear mechanism (41) .

The invention according to claim 1 includes a hydraulic pump (28) and a hydraulic motor (29) as a hydraulic transmission mechanism (30) for shifting and outputting the power of the engine (21), the power of the engine (21), and the A planetary gear mechanism (41) that combines the shift output of the hydraulic motor (29), and a combined output shaft (42) through which the combined output of the planetary gear mechanism (41) is transmitted as a rotational force in one direction from zero to the maximum speed. and in agricultural work vehicle equipped with a transmission case (22) having PTO output shaft (34), to the engagement shaft supported the sun gear (36) to the motor shaft of the hydraulic motor (29) (35), the sun gear (36). to the free rotation shaft supporting the carrier gear (37), wherein the carrier gear (37) is provided a planetary gear (38) rotatably, said planetary gear (38) meshes with the sun gear (36) So, the planetary gear (38) to provide a ring gear (40) to be engaged, the said ring gear in the combined output shaft (42) and (40) is engaging shaft supported, the sun gear (36), said planetary gear (38) and said The planetary gear mechanism (41) is formed by the ring gear (40), and the shift output of the hydraulic motor (29) and the one-way constant rotational force transmitted from the engine (21) to the carrier gear (37) are combined. to, and configured to communicate from said ring gear (40) as a one-way rotational force of zero to maximum speed to said combined output shaft (42), the PTO before Symbol pump shaft of the hydraulic pump (28) (31) while it configured to drive the output shaft (34), reversing the rotation speed of the sun gear (36) of the swash plate tilting angle of the hydraulic pump (28) in the maximum reverse angle The carrier gear (37) and the planetary gear mechanism (41) are configured such that when the rotation speed is increased, a constant rotational force in one direction of the carrier gear (37) is combined to make the rotation of the ring gear (40) zero. since those are the composition, and the output torque at zero start easily be secured, it is to be Ru can be improved zero start or very low speed running performance.

It is a whole side view of a combine. It is a whole top view of a combine. It is explanatory drawing of a driving system. It is explanatory drawing of a planetary gear mechanism part. It is explanatory drawing which shows the 0 rotation state of a synthetic | combination output shaft. It is explanatory drawing which shows the highest efficiency rotation state of a synthetic | combination output shaft. It is explanatory drawing which shows the highest rotation state of a synthetic | combination output shaft. It is explanatory drawing which shows the rotation state of a synthetic | combination output shaft. It is explanatory drawing which shows the relationship between the main transmission lever and a hydraulic transmission mechanism. It is rotation explanatory drawing of a planetary gear mechanism. It is output explanatory drawing of a hydraulic transmission mechanism. It is output explanatory drawing by the side of a transmission gear. It is output explanatory drawing of a synthetic | combination output shaft. It is engine output explanatory drawing of low speed driving | running | working. It is engine output explanatory drawing of medium speed driving | running | working. It is engine output explanatory drawing of high speed driving | running | working.

  Embodiments of the present invention will be described below in detail with reference to the drawings. 1 is an overall side view of a combine, and FIG. 2 is a plan view thereof. In FIG. 1, 1 is a track frame on which a traveling crawler 2 as a pair of left and right traveling members is installed, and 3 is a machine base installed on the track frame 1 Reference numeral 4 denotes a threshing section that stretches the feed chain 5 on the left side and incorporates a handling cylinder 6 and a processing cylinder 7; 8, a reaping section that includes a cutting blade 9 and a culm conveying mechanism 10; and 11, a reaping frame 12. A hydraulic cylinder that raises and lowers the mowing unit 8 through 13, a waste disposal processing unit 13 that faces the end of the waste chain 14, 15 a grain tank that carries the grain from the threshing unit 4 through the milling cylinder 16, and 17 A discharge auger for unloading the grains in the tank 15, 18 is a driver's cab provided with a round steering handle 19 and a driver's seat 20, and 21 is an engine provided below the driver's seat 20. Configured to cut and thresh There.

  In the figure, 22 is a transmission case for driving the traveling crawler 2, and 23 is a side column provided on the left side of the cab 18. The main transmission lever 24, auxiliary transmission lever 25, mowing clutch lever 26, and threshing clutch lever 27 are connected to the side column. 23.

  As shown in FIGS. 3 and 4, a set of continuously variable hydraulic transmission mechanism 30 formed of a variable displacement hydraulic pump 28 and a hydraulic motor 29 is provided on one side of the transmission case 22. The pump shaft 31 is connected to the engine 2 so that the output of the engine 2 is transmitted to the hydraulic transmission mechanism 30, and the transmission shaft 32 having a small diameter is supported on the pump shaft 31 that protrudes into the transmission case 22, and the PTO output pulley The power of the transmission gear 32 is transmitted to a PTO output shaft 34 having 33.

  Further, a sun gear 36 is engaged with a motor shaft 35 of a hydraulic transmission mechanism 30 that protrudes into the transmission case 22, and a large-diameter carrier gear 37 is always engaged with the small-diameter transmission gear 32. The carrier gear 37 is supported on a rotating shaft, and three planetary gears 38 are rotatably provided on the carrier gear 37 via a shaft 39. The planetary gear 38 is engaged with the sun gear 36, and the ring gear 40 engaged with the planetary gear 38 is provided. The planetary gear mechanism 41 is formed by the gears 36, 38, and 40.

  Further, both ends of the composite output shaft 42 are rotatably supported by the sun gear 36 and the transmission case 22, and the ring gear 40 is rotatably supported by the composite output shaft 42. As shown in FIGS. A forward / reverse rotation output, which is a continuously variable hydraulic shift output of the hydraulic pump 28 and the hydraulic motor 29 of the transmission mechanism 30, and a rotation output (constant rotation in one direction) of the transmission gear 32 and the carrier gear 37 are used as the differential of the planetary gear mechanism 41. It is synthesized by action and transmitted to the synthesized output shaft 42 as a rotational force in one direction from zero to the maximum speed.

  The combined output shaft 42 is connected to the auxiliary transmission gear shaft 44 through a pair of gears 43, and the parking brake 47 is connected through a pair of low-speed gear 45 and high-speed gear 46 constituting the auxiliary transmission gear portion 44a. The auxiliary transmission gear shaft 44 is connected to a parking brake shaft 48 having a left and right side clutch shafts 51 and 52 having left and right side clutches 49 and 50, and left and right front axles 55 and 56 via left and right transmission shafts 53 and 54. The shaft 48 is connected to drive the drive sprocket 57 of the traveling crawler 2 so that the vehicle body moves forward and backward and turns left and right.

  As shown in FIGS. 3 and 5 to 9, hydraulic shift operation arms 62 and 63 are connected to the swash plates 58 and 59 of the hydraulic pump 28 and the hydraulic motor 29 via control shafts 60 and 61, respectively. -63 is connected to the main speed change lever 24 via a rod or the like, and the rotation angle of the swash plates 58 and 59 is changed by the operation of the main speed change lever 24 to control the rotation of the composite output shaft 42. Yes.

  When the main transmission lever 24 is operated between the neutral position N and the forward maximum speed position F2, the inclination angle θa of the swash plate 59 of the hydraulic motor 29 is kept constant and the swash plate 58 of the hydraulic pump 28 is maintained. Only the inclination angle is changed from the maximum reverse rotation angle -α to the maximum forward rotation angle + α to perform forward traveling in which the moving speed of the vehicle body is changed from 0 to the maximum speed V2, while the main transmission lever 24 is set to the neutral position N and the reverse maximum. When operating between the high speed positions R, only the swash plate 59 of the hydraulic motor 29 is kept at a constant inclination angle θa and a low speed side (with the inclination angle of the swash plate 58 of the hydraulic pump 28 kept at the maximum reverse rotation angle −α. The vehicle travels backward to change the moving speed of the vehicle speed from 0 to the maximum speed V1 by changing the angle between the swash plate 59 and the constant inclination angle θb.

  That is, as shown in FIGS. 5 and 9, the main transmission lever 24 is operated to the neutral position N, the hydraulic pump 28 swash plate 58 is inclined at −α, and the hydraulic motor 29 swash plate 59 is inclined at the inclination angle θa. 10 (1), the sun gear 36 rotates in the clockwise direction at the maximum rotation and rotates the planetary gear 38 counterclockwise. At the same time, the carrier gear 37 is moved by the transmission gear 32. By rotating, the planetary gear 38 is revolved clockwise to rotate counterclockwise, the rotation of the ring gear 40 is made zero, and the combined output shaft 42 is stopped and maintained (position A, moving speed in FIG. 9). Is 0).

  Further, as shown in FIG. 6, the main transmission lever 24 is operated to the first forward speed position F1, the swash plate 58 of the hydraulic pump 28 is tilted at an inclination angle 0 (upright state), and the swash plate 59 of the hydraulic motor 29 is tilted at an inclination angle θa. When the hydraulic transmission mechanism 30 is driven, as shown in FIG. 10 (2), the sun gear 36 is stopped, the carrier gear 37 is rotated by the transmission gear 32, and the planetary gear 38 is rotated in the clockwise direction while rotating in the clockwise direction. The combined output shaft 42 is rotated by the gear power of the transmission gear 32 (position B in FIG. 9, the moving speed is the forward V1 position and the maximum efficiency state).

  Further, as shown in FIG. 7, the main transmission lever 24 is operated to the forward second speed position F2, and the swash plate 58 of the hydraulic pump 28 is set to the inclination angle + α and the swash plate 59 of the hydraulic motor 29 is set to the inclination angle θa. When driving, as shown in FIG. 10 (3), the sun gear 36 rotates in the counterclockwise direction at the maximum rotation, the planetary gear 38 rotates in the clockwise direction, and the carrier gear 37 is rotated in the clockwise direction while rotating in the clockwise direction. , And the combined output shaft 42 is rotated by adding the hydraulic transmission force from the sun gear 36 and the power of the transmission gear 32 (position C in FIG. 9, the moving speed is the forward V2 position, the highest speed state).

  Further, as shown in FIG. 8, the main transmission lever 24 is operated to the reverse position R, and the swash plate 58 of the hydraulic pump 28 is hydraulically inclined at an inclination angle -α and the swash plate 59 of the hydraulic motor 29 is hydraulically inclined at an inclination angle θb (θb <θa). When the speed change mechanism 30 is driven, the rotation of the hydraulic motor 29 (sun gear 36) is decelerated from the state of FIG. 10 (1), and the rotation of the composite output shaft 42 is reversed from the normal rotation state during forward movement (D in FIG. 9). The position and moving speed are in the reverse travel state at the reverse V1 position).

  And, for example, with respect to the general input power 100, the input power of the engine 2 is reduced when traveling at a low speed as shown in FIG. When the hydraulic transmission power is 50 and the hydraulic transmission power 50 returns to the pump shaft 31 and the transmission power on the gear 32 side becomes 150, the loss of the gear 32 is 3, and the hydraulic transmission mechanism 30 is lost. 15 and the output power is obtained at a rate of 82. Further, as shown in FIG. 15, when the vehicle travels at a medium speed where the transmission power of the hydraulic transmission mechanism 30 is zero, the transmission power on the gear 32 side is 100, the loss of the gear 32 is 2, and the output power is 98. Obtained in proportion. Further, as shown in FIG. 16, when traveling at high speed, when the hydraulic transmission power is 40 and the transmission power on the gear 32 side is 60, the loss of the gear 32 is 1, the loss of the hydraulic transmission mechanism 30 is 12, and the output The power is obtained at a ratio of 87, and the angle of the hydraulic motor operation arm 63 is maintained at a set value. For example, the angle of the hydraulic pump speed change operation arm 62 is changed from −1 to 0 to 1 as shown in FIG. Thus, when the motor shaft 35 is rotated from -N to 0 to + N and the gear 32 side is rotated N times regardless of the angle of the arm 62 as shown in FIG. The gears 32 and 37 and the planetary gear mechanism 41 are composed so that the vehicle body travels forward so that the combined output shaft 42 rotates 0 to 2N with respect to an angle of 62.

  In addition, when the angle of the hydraulic pump operation arm 62 is −1 and the angle of the hydraulic motor operation arm 63 is returned to the neutral side from the setting, the composite output shaft 42 is reversely rotated so that 0 to N rotations are provided. Is configured to travel backward.

  As is clear from the above, in a work vehicle including a composite transmission mechanism 64 that combines the outputs of the hydraulic transmission mechanism 30 for transmitting the driving force of the engine 2 and outputs of the transmission gear 32 to output the transmission, a set of variable displacement type The hydraulic transmission mechanism 30 is formed by the hydraulic pump 28 and the hydraulic motor 29, and the combined output shaft 42 of the composite transmission mechanism 64 is shifted in the normal rotation direction by the swash plate 58 angle control of the hydraulic pump 28. By providing the combined output shaft 42 of the composite speed change mechanism 64 so as to shift and rotate in the reverse direction by swash plate 59 angle control, there is no need to separately provide a complicated forward / reverse switching mechanism (forward / reverse switching mechanism). A simple operation of a lever or pedal that adjusts the swash plate 59 of the motor 29 makes it easy to switch between forward and backward movements, and easily secures output torque at the time of zero start, which is very slow. Improve line performance, yet it is possible to achieve such facilitate effectively improve work efficiency by using the output of the larger high in work efficiency of power transmission load.

  Further, the swash plate 58 angle of the hydraulic motor 29 is kept constant, the swash plate 58 angle of the hydraulic pump 28 is controlled to be forward and reverse, and the combined output shaft 42 of the composite transmission mechanism 64 is rotated in the forward direction. Smooth and easy shifting in forward travel by rotating the composite output shaft 42 in one direction (forward rotation) with a simple operation simply by operating the 58 swash plate angle of the hydraulic pump 28 with a single lever or the like. Etc. can be easily made possible.

  Further, the swash plate 58 angle of the hydraulic pump 28 is held at the reverse rotation side maximum output position (the combined output shaft 42 rotates 0 times), and the swash plate 58 angle of the hydraulic motor 29 is controlled to the neutral side from the setting, thereby combining the composite transmission mechanism. By rotating the 64 composite output shafts 42 in the reverse rotation direction, the swash plate 58 angle of the hydraulic motor 29 can be operated in one direction opposite to the composite output shaft 42 (reverse rotation) by a simple operation such as a single lever. ), The smooth and easy shifting in the reverse traveling can be easily performed.

  In addition, a forward traveling shift is performed by the swash plate 58 angle control of the hydraulic pump 28, and a backward traveling shift is performed by the swash plate 58 angle control of the hydraulic motor 29, whereby one set of the hydraulic pump 28 and the hydraulic motor. By using only the hydraulic transmission mechanism 30 comprising 29, it is possible to easily perform forward / reverse traveling with zero start, efficient output, etc., and to improve traveling performance.

  As is apparent from the above-described embodiments, the present invention provides a working vehicle including a hydraulic transmission mechanism 30 that transmits the driving force of the engine 2 and a composite transmission mechanism 64 that combines the outputs of the transmission gear 32 and outputs the transmission. The variable displacement hydraulic pump 28 and the hydraulic motor 29 form a hydraulic transmission mechanism 30, and the combined output shaft 42 of the composite transmission mechanism 64 is shifted in the normal rotation direction by controlling the swash plate 58 angle of the hydraulic pump 28. Since the combined output shaft 42 of the composite transmission mechanism 64 is rotationally rotated in the reverse direction by controlling the swash plate 59 angle of the hydraulic motor 29, there is no need to provide a separate complicated forward / reverse switching mechanism (forward / reverse switching mechanism). A simple operation of a lever or pedal that adjusts the swash plate 59 of the hydraulic motor 29 makes it easy to switch between forward and backward travel, and easily secures the output torque at the time of zero start to Running performance is improved and yet as it can be easily achieved, such as improvement of the work efficiency by effectively utilizing the output of the high power transmission efficiency even in a large work load.

  Further, the swash plate 58 angle of the hydraulic motor 29 is held constant, and the swash plate 58 angle of the hydraulic pump 28 is controlled to be forward and reverse to rotate the composite output shaft 42 of the composite transmission mechanism 64 in the forward rotation direction. Therefore, the composite output shaft 42 can be shifted and rotated in one direction (forward rotation) with a simple operation simply by operating the swash plate 58 angle of the hydraulic pump 28 with a single lever or the like. Therefore, it is possible to easily change the speed.

  Further, the swash plate 58 angle of the hydraulic pump 28 is held at the maximum reverse rotation output position, and the swash plate 58 angle of the hydraulic motor 29 is controlled to the neutral side from the setting, so that the composite output shaft 42 of the composite transmission mechanism 64 is rotated in the reverse rotation direction. Therefore, the swash plate 58 of the hydraulic motor 29 can be rotated in one direction (reverse rotation) opposite to the combined output shaft 42 by a simple operation such as operating a single lever. It is possible to easily make a smooth and easy shift in reverse travel.

  Further, the forward travel shift is performed by the swash plate 58 angle control of the hydraulic pump 28, and the reverse travel shift is performed by the swash plate 58 angle control of the hydraulic motor 29. By using only the hydraulic speed change mechanism 30 including the hydraulic motor 29, it is possible to easily perform forward / reverse traveling with zero start, efficient output, etc., and to improve traveling performance.

2 Engine 28 Hydraulic pump 29 Hydraulic motor 30 Hydraulic transmission mechanism 42 Composite output shaft

Claims (1)

A hydraulic pump (28) and a hydraulic motor (29) as a hydraulic transmission mechanism (30) for shifting and outputting the power of the engine (21), the power of the engine (21), and the shift output of the hydraulic motor (29) A planetary gear mechanism (41), a combined output shaft (42) to which a combined output of the planetary gear mechanism (41) is transmitted as a rotational force in one direction of zero to maximum speed, and a PTO output shaft (34) in agricultural work vehicle that includes a transmission case (22) having a,
A sun gear (36) is supported on the motor shaft (35) of the hydraulic motor (29) , a carrier gear (37) is supported on the sun gear (36 ) and a planetary gear (38) is supported on the carrier gear (37). ) Is rotatably provided, the sun gear (36) is engaged with the planetary gear (38), the ring gear (40) is engaged with the planetary gear (38), and the combined output shaft (42) is provided with the ring gear (40). The planetary gear mechanism (41) is formed by the sun gear (36), the planetary gear (38), and the ring gear (40).
The ring gear is generated as a rotational force in one direction from zero to the maximum speed by combining the shift output of the hydraulic motor (29) and the constant rotational force in one direction transmitted from the engine (21) to the carrier gear (37). (40) said configured to convey the combined output shaft (42) from, while configured to drive the PTO output shaft (34) in front Symbol pump shaft of the hydraulic pump (28) (31),
When the swash plate inclination angle of the hydraulic pump (28) is set to the maximum reverse rotation angle and the rotational speed of the sun gear (36) is set to the maximum reverse rotation speed, a constant rotational force in one direction of the carrier gear (37) is synthesized. The carrier gear (37) and the planetary gear mechanism (41) are composed so that the rotation of the ring gear (40) is zero.
Agricultural work vehicle.

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