JP2004323014A - Combined running gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a combined running gear capable of achieving the downsizing of a gear by the simplification of a configuration and the reduction in manufacture costs, while securing the speed range of an output shaft for a transmission machine. <P>SOLUTION: The gear includes an auxiliary variable-speed mechanism with a two-stage changeover type for a high revolution and a low revolution. The gear is of a two-stage changeover type for a high speed and a low speed by a hydraulic operation with a HST hydraulic motor 3 configured to be of a variable-speed system that provides a speed-changing control in response to a command. The gear is configured to allow the hydraulic motor 3 to perform 2-stage changeover for a high speed and a low speed by providing the HST lever 22 with a selector 23 of a push-button switch type, and turning the hydraulic motor 3 to continuous speed variation by the operation of the HST lever 22, as well as by the manipulation of fingers that are gripping the HST lever 22 and conducting a tilting operation. Thereby, the gear is configured to obtain four kinds of vehicle speeds by combining the two-stage changeover of the hydraulic motor 3 with the two-stage changeover of the auxiliary variable-speed mechanism and a wheel torque that is in inversely proportional relationship to these vehicle speeds. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a traveling device for a combine, and more particularly to a traveling device for a combine that can reduce the size and the manufacturing cost of the transmission by simplifying the configuration while securing the speed range of the output shaft of the transmission. .

The traveling device of the combine is configured by a continuously variable transmission, a transmission, and the like using a variable hydraulic pump and a hydraulic motor. The hydraulic variable pump of the continuously variable transmission includes an HST lever, and outputs a hydraulic pressure according to the operation of the HST lever while being driven by a prime mover. The hydraulic motor receives the hydraulic pressure of the variable hydraulic pump and outputs rotational power at a stepless rotational speed in accordance with the tilt of the HST lever of the variable hydraulic pump. The transmission includes a branch shaft for extracting the harvesting power of the combine, and a subtransmission mechanism, a differential traveling device, and the like between the branch shaft and the output shaft. The traveling speed of the combine constructed as described above can be steplessly adjusted by operating the HST lever through the hydraulic pressure of the variable hydraulic pump, including selection of forward / backward travel. Further, by switching the combination of gears according to the lever operation of the subtransmission mechanism, a speed range suitable for the work can be selected. Steering adjustment is performed by a differential traveling device. (For example, refer to Patent Document 1.)
JP-A-2-41980 (FIG. 13)

  However, since the combine traveling device including the above-described transmission is configured intensively in a necessary range with various mechanisms and members in order to satisfy many functions as described above, after securing required specifications, Further miniaturization and simplification of the configuration have reached their limits.

  SUMMARY OF THE INVENTION It is an object of the present invention to provide a combine traveling device that can reduce the size of the device by simplifying the configuration and reduce the manufacturing cost while securing the speed range of the output shaft of the transmission.

  The present invention has taken the following technical measures in order to solve the above problems.

  That is, a hydraulic variable pump 2 driven by the prime mover E and outputting hydraulic pressure in accordance with the operation of the HST lever 22, a hydraulic motor 3 for receiving the hydraulic pressure of the hydraulic variable pump 2 and outputting rotational power, An input shaft 8 receiving rotational power from the motor 3, a two-speed switching type sub-transmission mechanism composed of a transmission member 10 for high rotation and low rotation, and further outputs traveling power from the sub-transmission mechanism. The hydraulic motor includes left and right output shafts 11, 11; a differential unit for differentiating the left and right output shafts 11, 11; and a differential adjusting unit for adjusting a differential amount of the differential unit. The HST lever 22 is provided with a push-button switch type changeover switch 23 in the HST lever 22 as a variable speed type capable of performing a shift control in accordance with a command. The operation of the hydraulic variable pump 2 The HST lever 22 is operated to change the speed of the hydraulic motor 3 continuously, and at the same time, the changeover switch 23 is operated by the operation of a finger that is tilted while holding the HST lever 22 to move the hydraulic motor 3 between high speed and low speed. The two-stage switching of the hydraulic motor 3 and the two-stage switching of the transmission member 10 are combined to provide four types of vehicle speeds and an inversely proportional relationship with the vehicle speeds. This is a combine traveling device characterized in that it is configured to obtain a wheel torque.

  According to the present invention, the left and right output shafts 11, 11 can be differentially driven by the differential unit, and the differential adjustment unit can adjust the differential amount of the differential unit and turn the output shaft.

  Further, by combining the two-stage switching of the hydraulic motor 3 and the two-stage switching of the auxiliary transmission mechanism, it is possible to obtain four types of vehicle speeds and wheel torque in an inversely proportional relationship with the vehicle speeds. Since the variable type is used, the rotation range on the output side by the auxiliary transmission mechanism can be expanded and the required traveling speed range can be secured, so the structure of the transmission can be simplified by reducing the number of gear reduction stages. it can.

  Further, since the changeover switch 23 for selecting the rotation speed of the hydraulic motor 3 is arranged on the HST lever 22, the changeover switch 23 can be operated by finger operation simultaneously with the operation of the HST lever 22. , The speed selection operation of the hydraulic motor 3 can be performed without affecting other operations.

  An embodiment specifically configured based on the above-described technical idea will be described below with reference to the drawings with reference to the drawings.

  FIG. 1 is a development diagram of a transmission system showing a basic configuration of the combine traveling device of the present invention.

  In FIG. 1, a combine traveling device 1 receives a rotational power from a prime mover E on an input pulley 2a, and outputs a hydraulic pressure in a stepless manner in response to an operation of an HST lever. It comprises a hydraulic motor 3 that receives and outputs rotational power, and a transmission 4 that receives rotational power from the hydraulic motor 3 and outputs running power.

  The variable hydraulic pump 2 constitutes a set of continuously variable transmissions together with a hydraulic motor 3, and the hydraulic motor 3 is configured to have a variable speed with a swash plate mechanism and the like capable of controlling a shift according to a command. The hydraulic motor 3 is, for example, two-stage switching between “high speed” and “low speed” by hydraulic operation via a hydraulic switching valve 5, and a switch 6 for commanding the operation is attached to a sub-transmission switching lever 7 described later. This constitutes the control system. The control system of the hydraulic motor 3 is set to “low speed” when no control oil pressure is received, and is set to “high speed” when the control oil pressure is received by switching the hydraulic switching valve 5. The swash plate is connected to a hydraulic switching valve 5 via an actuator 5a for controlling the swash plate.

  The transmission 4 includes an input shaft 8 that receives rotational power from the hydraulic motor 3, a branch shaft 9 that separates the cutting power from the pulley 9 a, and a transmission member 10 that includes the branch shaft 9 as an auxiliary transmission shaft. And a differential unit for causing the clutch differential mechanism 19 to differentiate the left and right output shafts 11, in addition to the left and right output shafts 11, 11 for outputting the traveling power at a further reduced speed from the auxiliary transmission mechanism. And a differential adjusting unit such as a turning clutch 12 for adjusting the differential amount of the moving unit.

  The speed change member 10 of the auxiliary speed change mechanism is configured to be capable of shifting along the branch shaft 9 from the auxiliary speed changeover lever 7 via a wire 7a and a shift fork 10a. By arranging 14a and 14b on the counter shaft 14, a subtransmission mechanism is constituted.

  The differential portion is provided with an intermediate shaft 15 that meshes with the output gear 14 c of the counter shaft 14 and divides the auxiliary speed power into two systems. From the intermediate shaft 15, a part of the power is input to the clutch differential mechanism 19. It is configured as follows. The clutch differential mechanism 19 includes a center gear 19a on the side clutch shaft 18 which always meshes with the gear 15a of the intermediate shaft 15. The center gear 19a is selectively driven by the pawl clutch when the vehicle is running straight, and when the vehicle is turning, the left and right are selectively driven. It is transmitted to the differential gears 18L and 18R. The left and right differential gears 18L and 18R mesh with the left and right output shafts 11 and 11 to transmit their power.

  The differential adjuster is provided with a side gear shaft 16 that is controlled to transmit the remaining power from the intermediate shaft 15 by the turning clutch 12. The side gear shaft 16 is provided with the parking brake 13 and the left and right The side gears 16L and 16R are pivotally supported. The intermediate shaft 15 always meshes with the spin turn gear 12a of the turning clutch 12 and meshes with the mild turn gear 12b of the turning clutch 12 via the two-stage switching shift member 17a and the countershaft 17. The differential adjustment power for the spin turn and the mild turn that can be switched in two stages is transmitted to the side gear shaft 16. The side gears 16L and 16R receive the differential adjustment power from the side gear shaft 16 to the corresponding left and right sides in response to the turning command by the pawl clutch, and transmit the left and right differential power to the left and right output shafts 11 and 11, respectively. It meshes with the gears 18L, 18R. Further, when the turning clutch 12 is completely connected, a spin turn at a predetermined gear ratio (や or ３) is performed, and by adjusting the pressure of the turning clutch 12, a brake turn is performed.

  In the combine traveling device 1 configured as described above, the hydraulic switching valve 5 is switched according to a command of the switch 6 attached to the sub-transmission switching lever 7, and the hydraulic pressure is received by the control unit of the hydraulic motor 3. The motor 3 is switched to the "high speed" side. As a result, the reference rotation input from the hydraulic motor 3 to the transmission 4 is switched from “low speed” to “high speed”.

  Further, in the subtransmission mechanism of the transmission 4, the shifting member 10 is shifted through the wire 7 a and the shift fork 10 a by the tilting operation of the subtransmission switching lever 7. By the shifting operation of the transmission member 10, the meshing of the gears 14a and 14b having different numbers of teeth on the counter shaft 14 is switched, so that the rotation speed ratio from the input shaft 8 of the transmission 4 to the counter shaft 14 changes.

  Therefore, as shown in the traveling characteristic graph of the combination of the hydraulic motor and the sub-transmission mechanism in FIG. 2, by combining the switching of the hydraulic motor 3 and the switching of the transmission member 10, the "low speed" of the hydraulic motor 3 and the sub-transmission Four types of vehicle speeds, that is, four types of vehicles that are inversely proportional to the vehicle speed, from the case where the low rotation speed of the mechanism is selected to the combination where “high speed” of the hydraulic motor 3 and the high rotation speed of the auxiliary transmission mechanism are selected. Wheel torque can be obtained. In this case, erroneous operation can be prevented by associating the harvesting operation of the combine with the selection of “low speed” of the hydraulic motor 3.

  As described above, in the combine traveling device 1, the output rotation range of the subtransmission mechanism 10 is expanded by using the variable speed motor for the hydraulic motor 3. Therefore, the required traveling speed range can be secured without requiring a large reduction ratio between the auxiliary transmission mechanism 10 and the output shafts 11 and 11 in the transmission 4, and the transmission can be performed by reducing the number of gear reduction stages. The configuration of the motive 4 can be simplified.

  The hydraulic motor 3 and the auxiliary transmission mechanism are not limited to the two-stage switching, but the hydraulic motor 3 is switched to the two-stage switching by the changeover switch 6 and the auxiliary transmission mechanism 10 is changed to the two-stage switching by the auxiliary transmission switching lever 7 as described above. In the case of gear shifting, a combined traveling device that can switch the output rotation speed of the combine traveling device 1 in a wide range by a simple operation combination of the changeover switch 6 and the subtransmission switching lever 7 is simply configured. Can be.

  Next, an example of the configuration of a combine traveling device in which the changeover switch of the hydraulic motor is arranged on the HST lever will be described. FIG. 3 is an exploded view of the transmission system of the combine traveling device in which the changeover switch of the hydraulic motor is arranged on the HST lever. In the following, description of the same members will be omitted by giving the same reference numerals.

  3, the combine traveling device 21 includes a changeover switch 23 such as a push button switch integrated with an HST lever 22 for operating the hydraulic variable pump 2. The HST lever 22 is connected to the variable hydraulic pump 2 via a wire 22a or the like, and forms an operation system thereof. Further, the changeover switch 23 constitutes an operation system for switching the hydraulic motor 3 between “high speed” and “low speed” via the hydraulic pressure switching valve 5 in two stages.

  When the changeover switch 23 for selecting the rotation speed of the hydraulic motor 3 is provided on the HST lever 22 as in the above configuration, the hydraulic motor 3 is continuously variable by operating the HST lever 22 so that the traveling speed of the airframe is increased. And at the same time, the changeover switch 23 can be operated by the operation of the finger when the HST lever 22 is gripped and tilted. Therefore, when the vehicle speed is changed by operating the HST lever 22, the combine traveling device 21 can perform the speed selection operation of the hydraulic motor 3 without affecting other operations.

  Next, a configuration example of the interlocking control of the reaping unit by switching the hydraulic motor of the combine traveling device will be described.

  FIG. 4 is a development view of a transmission system of a configuration example in which the mowing unit is interlocked by switching the hydraulic motor of the combine traveling device.

  In FIG. 4, a combine traveling device 31 is provided with an actuator 33 such as a cylinder for controlling the tilting of a cutting lever 32 for operating a cutting unit (not shown), and the hydraulic motor 3 by the hydraulic switching valve 5 is attached to the actuator 33. Introduce control oil pressure for speed switching. The reaping lever 32 is connected to a reaping clutch 34 that is connected and disconnected by a change in belt tension via a wire 32a so that the reaping unit is operated by the tilting operation.

  In the combine traveling device 31 having the above-described configuration, when the "low speed" is selected in which the hydraulic motor 3 does not receive the control hydraulic pressure by the hydraulic switching valve 5, the actuator 33 in the same control system does not generate a regulating force. 32 can be operated at any time. That is, while the hydraulic motor 3 is running at a "low speed", the mowing lever 32 is operated to move the mowing clutch 34 to the power connection side, so that the mowing unit can be operated. On the other hand, when “high speed” is selected by sending the control oil pressure to the hydraulic motor 3 by the oil pressure switching valve 5, the control oil pressure restricts the reaping lever 32 to the power cutoff position via the actuator 33, and tilts Regulate operations. That is, while the hydraulic motor 3 is running at "high speed", the operation of the cutting lever 32 is restricted. Therefore, erroneous operation of the reaping lever 32 at the time of selecting "high speed" can be prevented, and careless operation of the reaping unit can be avoided.

  Next, a configuration example of a combine traveling device that switches a hydraulic motor in conjunction with a differential steering operation of the combine will be described.

  FIG. 5 is a development view of a transmission system of a configuration example of a combine traveling device that switches a hydraulic motor in conjunction with a differential steering operation of the combine.

  In FIG. 5, the transmission 4 of the combine traveling device 41 is provided with a turning clutch 12 for differentially operating the output shafts 11, 11 in response to a steering operation of a power steering lever (not shown). The turning clutch 12 has two built-in clutches operated by hydraulic pressure, and has a differential hydraulic circuit composed of a pair of cylinders 44 a and 44 a differentially connected to a hydraulic pressure switching valve 44. The hydraulic pressure switching valve 44 is connected to a control circuit including an amplifying unit such as a relay 43 for amplifying each signal from a steering detection switch 42 for detecting a steering operation due to left and right tilting of a power steering lever (not shown). The hydraulic switching valve 5 for switching the speed of the hydraulic motor 3 is connected to both terminals of the steering detection switch 42 via an amplifying unit such as a relay 46, so that the hydraulic motor 3 can be used for detecting a left or right tilting operation detection signal. A control circuit for switching to “low speed” is provided.

  In the combine traveling device 41 having the above-described configuration, when the power steering lever is steered to turn the airframe, the hydraulic switching valve 44 is switched in response to a signal from the steering detection switch 42 to perform a differential operation. The turning clutch 12 differentially operates via the pair of cylinders 44a, 44a of the dynamic hydraulic circuit. At this time, the hydraulic switching valve 5 performs a switching operation according to the signal of the steering detection switch 42, and the hydraulic motor 3 is switched to “low speed”. Thereafter, by returning the power steering lever to the neutral position, the switching signal of the hydraulic switching valve 5 is terminated, and the straight traveling under the original traveling conditions is continued.

  Therefore, when the power steering lever is steered to turn the body, the body is turned by the turning clutch 12 while the traveling speed is suppressed by switching the hydraulic motor 3 and a large output torque is secured. As a result, the turning operation of the aircraft can be stably performed. This also plays a role of backing up safe running in a field with unstable ground against an inadvertent turning operation during straight running at "high speed".

FIG. 1 is a development view of a transmission system according to a basic configuration of a combine traveling device of the present invention. 2 is a traveling characteristic graph of a combination of a hydraulic motor and an auxiliary transmission mechanism of the combine traveling device in FIG. 1. FIG. 4 is a development view of a transmission system in which a changeover switch of a hydraulic motor of the combine traveling device of the present invention is arranged on an HST lever. FIG. 4 is a development view of a transmission system of a configuration example in which a combine harvester is interlocked and controlled by the combine traveling device of the present invention. FIG. 2 is a development view of a transmission system of a configuration example in which the combine traveling device of the present invention is controlled in conjunction with a differential steering operation of an airframe.

Explanation of reference numerals

E Primer 2 Variable hydraulic pump 3 Hydraulic motor 8 Input shaft 10 Transmission member 11 Output shaft 22 HST lever
23 Changeover switch

Claims (1)

  A hydraulic variable pump 2 driven by the prime mover E to output a hydraulic pressure in accordance with the operation of the HST lever 22; a hydraulic motor 3 that receives the hydraulic pressure of the hydraulic variable pump 2 and outputs rotational power; An input shaft 8 that receives rotational power from the gear 3, a two-speed switching type sub-transmission mechanism composed of a transmission member 10 for high rotation and low rotation, and a left and right side that outputs traveling power at a further reduced speed from the auxiliary transmission mechanism. The hydraulic motor 3 is provided with output shafts 11 and 11, a differential unit for differentiating the left and right output shafts 11 and 11, and a differential adjustment unit for adjusting the differential amount of the differential units. The HST lever 22 is provided with a push-button switch type changeover switch 23 as a variable speed type capable of performing a shift control in accordance with a command. Operate the variable hydraulic pump 2 by operating 22 The HST lever 22 is operated to change the speed of the hydraulic motor 3 continuously and the changeover switch 23 is operated by the operation of a finger that is tilted while holding the HST lever 22 to move the hydraulic motor 3 between high speed and low speed. The vehicle is configured to be able to switch gears, and two types of vehicle speeds are combined with two-stage switching of the hydraulic motor 3 and two-stage switching of the speed change member 10 so that the wheel torque is in inverse proportion to the vehicle speed. A traveling device for a combine, comprising:

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