WO2015045437A1 - コンバイン - Google Patents
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- Publication number
- WO2015045437A1 WO2015045437A1 PCT/JP2014/054399 JP2014054399W WO2015045437A1 WO 2015045437 A1 WO2015045437 A1 WO 2015045437A1 JP 2014054399 W JP2014054399 W JP 2014054399W WO 2015045437 A1 WO2015045437 A1 WO 2015045437A1
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- WO
- WIPO (PCT)
- Prior art keywords
- continuously variable
- transmission
- transmission case
- planetary
- variable transmission
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01D—HARVESTING; MOWING
- A01D41/00—Combines, i.e. harvesters or mowers combined with threshing devices
- A01D41/02—Self-propelled combines
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01D—HARVESTING; MOWING
- A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
- A01D69/03—Driving mechanisms or parts thereof for harvesters or mowers fluid
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01D—HARVESTING; MOWING
- A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
- A01D69/06—Gearings
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
- A01F12/00—Parts or details of threshing apparatus
- A01F12/56—Driving mechanisms for the threshing parts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/20—Off-Road Vehicles
- B60Y2200/22—Agricultural vehicles
- B60Y2200/222—Harvesters
Definitions
- the present invention relates to a combine.
- the rotational speed of the driving force output from the continuously variable transmission unit changes, and the planetary transmission unit changes the driving force from the continuously variable transmission unit and the driving force from the engine.
- the combined drive force that is output by combining the output and the combined drive force changes, and the combined drive force with the changed rotation speed is transmitted to the travel device, so that the travel device can be operated simply by shifting the continuously variable transmission. Can be driven smoothly.
- the driving force from the continuously variable transmission unit and the driving force from the engine are combined by the planetary transmission unit and the combined driving force is transmitted to the traveling device, the engine output can be efficiently transmitted to the traveling device.
- This combine includes an input shaft for inputting driving force from the engine, a hydraulic pump for inputting the driving force of the input shaft, and a hydraulic motor driven by the hydraulic pump as a hydraulic continuously variable transmission unit.
- This is a hydraulic continuously variable transmission, and the driving force of the input shaft and the output of the hydraulic continuously variable transmission are input to the planetary transmission unit and synthesized, and the combined driving force from the planetary transmission unit is transmitted to the traveling device. Is configured to do.
- the continuously variable transmission chamber that accommodates the continuously variable transmission portion of the transmission case needs to be filled or substantially filled with hydraulic oil due to the structure of the continuously variable transmission portion. If the lubricating oil is stored in the planetary transmission chamber that houses the planetary transmission part of the transmission case in a full or nearly full state, the driving resistance of the planetary transmission part due to the lubricating oil increases, so the lubricating oil in the planetary transmission chamber Keep the amount of storage of the minimum amount not the full amount.
- the port block forming the drive circuit needs to be made of a material having high strength such as iron.
- the continuously variable transmission chamber and the planetary transmission chamber are separated by the port block, so if the transmission case is made of a lightweight material such as an aluminum alloy, the continuously variable transmission portion of the transmission case It is necessary to separately produce a continuously variable transmission case portion for housing the planetary transmission case portion and a planetary transmission case portion for housing the planetary transmission portion of the transmission case.
- An object of the present invention is to provide a combine that can reduce the weight of a transmission case at low cost.
- An object of the present invention is to provide a continuously variable transmission without providing a special speed reduction function to the traveling transmission device, while the traveling device can be smoothly driven and shifted easily and the engine output can be efficiently transmitted to the traveling device.
- An object of the present invention is to provide a combine that can avoid defective driving.
- This type of combine is equipped with an oil filter for hydraulic oil supplied to the continuously variable transmission.
- ⁇ Oil filters need to be replaced over time.
- the time required for the maintenance work increases.
- An object of the present invention is to provide a combine that can be equipped with an oil filter and a motor control valve mechanism in a state where maintenance work is easy.
- the means for solving the problem [1] is as follows.
- the combine according to the present invention is: A hydrostatic continuously variable transmission unit that has a hydraulic pump and a hydraulic motor and inputs a driving force from the engine to shift, and a combination of the driving force from the engine and the output of the continuously variable transmission unit A planetary transmission unit that outputs a driving force to the traveling device; and a transmission device that includes the continuously variable transmission unit and a transmission case that houses the planetary transmission unit;
- a continuously variable transmission case portion that accommodates the continuously variable transmission portion of the transmission case is integrally formed with a planetary transmission case portion that accommodates the planetary transmission portion of the transmission case;
- a partition that partitions the continuously variable transmission chamber that accommodates the continuously variable transmission portion of the continuously variable transmission case portion and the planetary transmission chamber that accommodates the planetary transmission portion of the planetary transmission case portion is provided inside the transmission case. It is characterized by being.
- the continuously variable transmission chamber and the planetary transmission chamber are separated by the partition wall provided inside the transmission case. Therefore, even if the continuously variable transmission case portion of the transmission case is formed integrally with the planetary transmission case portion, The hydraulic oil in the step transmission chamber does not flow out into the planetary transmission chamber, and the continuously variable transmission case portion can be made at once with a light material together with the planetary transmission case portion.
- a transmission case can be produced lightly and inexpensively, and a combine that is equipped with a speed change transmission device and is convenient for speed change can be advantageously obtained in terms of weight and economy.
- the planetary transmission case portion is formed with respect to the first divided planetary transmission case portion in which the continuously variable transmission case portion is integrally formed and the partition wall is provided, and the first divided planetary transmission case portion. It is preferable that the second variable planetary transmission case part is configured to be freely divided into the second divided planetary transmission case part located on the side opposite to the side where the continuously variable transmission case part is located.
- the planetary transmission case portion can be greatly opened by dividing the planetary transmission case portion into the first divided planetary transmission case portion and the second divided planetary transmission case portion. Easy assembly work.
- a port block forming a drive circuit for connecting the hydraulic pump and the hydraulic motor is attached to an end portion of the continuously variable transmission case portion opposite to the side to which the planetary transmission case portion is connected. It is preferable that
- the continuously variable transmission case portion can be integrally formed with the planetary transmission case portion, and the transmission case can be provided while providing high strength to the port block. It can be obtained lightly and inexpensively.
- the port block can be easily detached from the end side of the continuously variable transmission case portion where the planetary transmission case portion is not connected, and the drive circuit is easily inspected.
- the transmission case is formed such that the continuously variable transmission case portion and the planetary transmission case portion are aligned in a lateral direction of the traveling machine body, and the shape of the transmission case in a top view of the traveling machine body is It is preferable that the traveling vehicle body rear side end of the continuously variable transmission case portion is formed in a shape located on the traveling vehicle body front side of the traveling vehicle body rear side end of the planetary transmission case portion.
- a notch-shaped space can be formed in the lateral end portion of the rear end side of the transmission case as viewed from the top of the traveling machine body. It can be equipped compactly so that it does not project sideways or project too much.
- the front side of the valve mechanism is covered with a continuously variable transmission case part
- the lateral side is covered with a planetary transmission case part
- the continuously variable transmission case part and the planetary transmission case part can be used as guard means, and the valve mechanism can be protected.
- the shape of the transmission case in a top view of the traveling machine body is such that the traveling machine body rear side end of the continuously variable transmission case part is located on the traveling machine body front side rather than the traveling machine body rear side end of the planetary transmission case part. It is preferable that a shift control valve mechanism for performing a shift operation of the hydraulic pump is provided in a space formed by forming the shape.
- the speed change control valve mechanism is arranged near the hydraulic pump to be controlled, and the speed of the operation oil path connecting the speed change control valve mechanism and the hydraulic pump is shortened. It can be equipped compactly so that it does not protrude rearward or sideways from the transmission case, or it does not protrude so much, and the front and side of the shift control valve mechanism are covered with a continuously variable transmission case part and a planetary transmission case part. Thus, the shift control valve mechanism can be protected.
- the engine is located behind the traveling machine body of the transmission case.
- the transmission case is made wider than the interval between the planetary transmission case unit and the engine.
- the rear side of the notch-like space can be widely opened in the top view of the traveling vehicle body that can be configured at the lateral end portion on the rear end side, and the space can be easily used for deployment of the valve mechanism.
- the driving force from the engine is input to the planetary transmission unit and the continuously variable transmission unit from the lateral outer side of the planetary transmission case unit opposite to the side where the continuously variable transmission case unit is connected. It is preferable to be configured as described above.
- the structure of the continuously variable transmission unit side is simpler than the input from the continuously variable transmission unit side, and the need for charging more oil than the planetary transmission unit side is high. Sealability can be improved.
- the transmission case is formed such that the continuously variable transmission case portion and the planetary transmission case portion are aligned in a lateral direction of the traveling machine body, and the continuously variable transmission case portion of the planetary transmission case portion is connected.
- a traveling transmission case that is coupled to a lateral side opposite to the transmission side and that inputs a composite driving force from the planetary transmission unit and transmits it to a traveling device, the traveling transmission case having an upper end at the planetary transmission case unit
- the driving force from the engine is arranged laterally outside the planetary transmission case portion on the side opposite to the side to which the continuously variable transmission case portion is connected, It is preferable that the driving transmission case is configured to be input to the planetary transmission unit and the continuously variable transmission unit from above.
- the space generated by the height difference between the upper end of the planetary transmission case and the upper end of the traveling transmission case is used for the input transmission path to the planetary transmission unit and the continuously variable transmission unit. it can.
- the transmission case is formed such that the continuously variable transmission case portion and the planetary transmission case portion are aligned in the lateral direction of the traveling vehicle body, and the inclination is lower toward the rear side of the traveling aircraft body at the upper portion of the transmission case.
- An inclining portion formed in a shape, and a drive mode of the speed change transmission device, a first mode in which the continuously variable transmission portion performs a speed change operation and the planetary transmission portion does not perform a speed change operation, the continuously variable transmission portion and the planetary transmission It is preferable that a valve mechanism that switches to the second mode in which the part performs a speed change operation and switches the rotation direction of the output of the transmission transmission device between the forward rotation direction and the reverse rotation direction is provided in the inclined portion.
- an empty space is formed above the transmission case by providing an inclined portion at the top of the transmission case, and the valve mechanism is deployed in the inclined portion by utilizing this empty space as a storage space for the valve mechanism.
- the valve mechanism can be supported compactly in the transmission case.
- the combine according to the present invention is: An input shaft for inputting driving force from the engine, a hydrostatic continuously variable transmission for shifting the driving force of the input shaft, and a driving force for the input shaft and driving of a continuously variable output shaft of the continuously variable transmission
- a speed change transmission device provided with a planetary transmission unit that combines a force and outputs a combined driving force from the planetary output shaft;
- a travel transmission device for transmitting the combined driving force from the planetary output shaft to a travel device;
- the speed change transmission device is provided with a speed reduction output shaft that is linked to the planetary output shaft via a speed reduction transmission mechanism and decelerates the combined driving force from the planetary output shaft and outputs it to the travel transmission device.
- the traveling device can be smoothly driven by changing the speed of the continuously variable transmission. Further, since the driving force from the continuously variable output shaft and the driving force from the input shaft are combined by the planetary transmission unit and the combined driving force is transmitted to the traveling device, the engine output can be efficiently transmitted to the traveling device.
- the rotational speed of the driving force input to the input shaft is set to an appropriate rotational speed, the rotational speed of the driving force input to the continuously variable transmission section will not be slow, and drive failure will occur in the continuously variable transmission section. Can be avoided. Even if the rotational speed of the combined driving force output from the planetary output shaft is increased by setting the rotational speed of the driving force input to the input shaft to a rotational speed at which no drive failure occurs in the continuously variable transmission unit, Since the combined driving force from the planetary output shaft is decelerated by the deceleration output shaft and transmitted to the traveling transmission device, it can be avoided that the traveling speed of the traveling device becomes too fast. And it is not necessary to provide the traveling transmission device with a deceleration function for avoiding the driving speed of the traveling device from becoming too fast.
- the traveling transmission apparatus can be made simple and lightweight without a special speed reduction mechanism.
- the speed change transmission device is disposed in front of the traveling body of the engine, and the input shaft and the continuously variable output shaft are disposed in front of the traveling body of the deceleration output shaft.
- the part where the continuously variable transmission unit and the planetary transmission part of the transmission transmission device are located is positioned in front of the traveling machine body than the part of the transmission transmission device where the deceleration output shaft is located. It is easy to avoid interference between the device and the engine. Further, the distance between the input shaft and the engine can be made larger than the distance between the deceleration output shaft and the engine. Even when the engine and the input shaft are linked by the transmission belt, the tension means for tensioning the transmission belt is connected to the engine.
- the power transmission belt can be properly placed between the input shaft and the transmission belt in a predetermined tension state so that transmission from the engine to the input shaft can be appropriately performed.
- the input shaft and the stepless output shaft are arranged in the vertical direction of the traveling machine body.
- the hydraulic pump and the hydraulic motor constituting the continuously variable transmission unit can be arranged in the vertical direction of the traveling machine body, the drive circuit for connecting the hydraulic pump and the hydraulic motor, the formation of the actuator for operating the hydraulic pump, Easy to install.
- the transmission mechanism includes a transmission mechanism that transmits the driving force of the input shaft to the planetary transmission unit, the transmission mechanism includes a relay shaft, and the driving force of the input shaft does not rotate forward unless the relay shaft is interposed.
- Power is transmitted to the planetary transmission unit as power, and is transmitted to the planetary transmission unit as reverse rotational power via the relay shaft, and the relay shaft is connected to the input shaft and the continuously variable output shaft in the vertical direction of the traveling machine body. It is preferable that it is located between the input shaft and the continuously variable output shaft in the longitudinal direction of the traveling machine.
- the relay shaft When the relay shaft is positioned in front of the input shaft and the continuously variable output shaft in the longitudinal direction of the traveling machine body, the relay shaft is positioned on the side opposite to the side where the deceleration output shaft is positioned with respect to the input shaft and the continuously variable output shaft. As a result, the longitudinal length of the transmission body of the speed change transmission device becomes longer due to the provision of the relay shaft. On the other hand, according to the present invention, it is possible to suppress an increase in the longitudinal direction length of the traveling body of the speed change transmission device due to the provision of the relay shaft.
- the input shaft and the continuously variable output shaft are arranged vertically in front of the deceleration output shaft so that the transmission from the engine to the input shaft can be performed appropriately and the drive circuit and actuator are easily formed and mounted.
- the relay shaft is located above the deceleration output shaft.
- the speed change transmission can be arranged in front of the engine in a state where the input shaft is not too close to the engine and not too far away. Therefore, even when the engine and the input shaft are interlocked by the transmission belt, tension means for tensioning the transmission belt can be appropriately arranged between the engine and the input shaft, and the transmission belt is input from the engine with a predetermined tension state. Transmission to the shaft can be performed appropriately.
- the input shaft, the continuously variable output shaft, and the relay shaft are positioned above the deceleration output shaft.
- the vertical direction of the traveling machine body in which the input shaft and the continuously variable output shaft are arranged can be set to the vertical direction or a direction close thereto, and a drive circuit for connecting the hydraulic pump and the hydraulic motor, an actuator for operating the hydraulic pump, Easy to install.
- a transmission case that accommodates the continuously variable transmission unit and the planetary transmission unit is provided, and the relay shaft is located on an upper side inside the planetary transmission case unit that accommodates the planetary transmission unit in the transmission case. It is preferable that an inclined portion that is deployed and is formed on the upper portion of the planetary transmission case portion so as to have a lower inclined shape toward the rear side of the traveling aircraft body.
- the relay shaft is positioned between the input shaft and the continuously variable output shaft in the vertical direction of the traveling machine body, and is positioned behind the input shaft and the continuously variable output shaft in the longitudinal direction of the traveling machine body.
- the inclined portion is provided on the upper part of the planetary transmission case part, an empty space can be formed above the planetary transmission case part. Therefore, for example, if the vacant space is utilized as a storage space for the valve mechanism and the valve mechanism is provided in the inclined portion, the valve mechanism can be compactly supported by the transmission case.
- the drive mode of the deceleration output shaft includes a first mode in which the continuously variable transmission section performs a shift operation and the planetary transmission section does not perform a shift operation, and the continuously variable transmission section and the planetary transmission section perform a shift operation.
- a valve mechanism is provided for switching to the second mode and switching the rotation direction of the deceleration output shaft between the forward rotation direction and the reverse rotation direction, and the valve mechanism is disposed at the inclined portion of the planetary transmission case portion. It is preferable.
- the valve mechanism is arranged in the planetary transmission case part by utilizing the empty space formed above the planetary transmission case part by providing the inclined part on the upper part of the planetary transmission case part as the storage space of the valve mechanism. Therefore, the valve mechanism can be supported compactly in the transmission case.
- the transmission case is formed such that the continuously variable transmission case part and the planetary transmission case part are arranged in a lateral direction of the traveling machine body, and the continuously variable transmission part and the planetary transmission are provided in the transmission case. It is preferable that a partition wall partitioning the part is provided, and the valve mechanism is disposed in a portion of the inclined portion near the partition wall.
- the valve mechanism can be brought close to the partition wall. Therefore, when the valve mechanism and the controlled object are connected by the operation oil passage formed in the partition wall, the valve mechanism and the operation oil passage can be easily connected by a short connection oil passage.
- the combine according to the present invention is: An engine provided below the driving unit; A hydrostatic continuously variable transmission that shifts by inputting a driving force from the engine, and a planetary transmission unit that combines the driving force from the engine and the driving force from the continuously variable transmission, A shift transmission that outputs the combined driving force from the planetary transmission unit to the traveling device, and Below the driving unit, the transmission gearing device is arranged in front of the traveling machine rather than the engine, An oil filter that acts on hydraulic oil supplied to the continuously variable transmission unit, and a motor control valve mechanism that performs a shift operation of the hydraulic motor of the continuously variable transmission unit are provided on a front surface portion or a lateral outer surface portion of the transmission device. It is characterized by being arranged in the vertical direction.
- the oil filter and the motor control valve mechanism are arranged on the front surface portion or the lateral outer surface portion of the speed change transmission device disposed in front of the traveling machine body than the engine, the oil filter and motor control valve mechanism on the front side of the traveling machine body. Or it is easy to ensure a working space on the lateral outer side of the traveling machine body.
- the oil filter and the motor control valve mechanism are arranged in the vertical direction, even if the lateral width of the working space that can be secured on the traveling machine body front side or the running machine body lateral side of the oil filter and the motor control valve mechanism is relatively narrow, Easy access to oil filter and motor control valve mechanism.
- the maintenance work for the oil filter and the motor control valve mechanism can be performed efficiently because it is easy to secure a working space or reach easily.
- the oil filter and the motor control valve mechanism are arranged on the front surface portion.
- the oil filter and the motor control valve mechanism can be compactly disposed within the lateral width of the transmission.
- the oil filter is disposed above the motor control valve mechanism.
- the upper part of the motor control valve mechanism can be covered with the oil filter.
- the conveyed harvested cereal mealer touches the motor control valve mechanism. It is advantageous that it can be easily avoided.
- the oil filter and the motor control valve mechanism are arranged in a portion of the front surface portion that is closer to the lateral outer side of the traveling body.
- the oil filter and the motor control valve mechanism are arranged on the front surface portion, the oil filter and the motor control valve mechanism are positioned on the laterally outer side portion of the traveling machine body, for example, above the speed change transmission device.
- the oil filter and the motor control valve mechanism are positioned on the laterally outer side portion of the traveling machine body, for example, above the speed change transmission device.
- the speed change transmission device includes a transmission case that houses the continuously variable transmission section and the planetary transmission section, and the transmission case includes a continuously variable transmission chamber that houses the continuously variable transmission section, and the planetary transmission.
- a planetary transmission chamber that accommodates a portion; and a partition that partitions the continuously variable transmission chamber and the planetary transmission chamber; and the oil filter and the motor control valve mechanism that overlap the partition in the front portion It is preferable that it is deployed in.
- the oil filter and the motor control valve mechanism can be firmly supported by the portion of the front surface portion that is reinforced by the partition wall. Further, when the operation oil passage for connecting the motor control valve mechanism and the hydraulic motor is formed in the partition wall, the motor control valve mechanism can be connected to the operation oil passage with a short connection oil passage.
- the oil filter and the motor control valve mechanism are arranged on the front surface portion, and a speed increasing hydraulic cylinder that presses the swash plate so as to tilt the swash plate of the hydraulic motor to the speed increasing side. And a deceleration hydraulic cylinder that presses against the swash plate so as to tilt the swash plate to the deceleration side, and the speed-up hydraulic cylinder and the deceleration hydraulic cylinder are connected to the swash plate. It is preferable that the left and right are arranged.
- the operating oil passage connecting the motor control valve mechanism and the speed increasing hydraulic cylinder is disposed so as to pass through the side opposite to the side where the speed reducing hydraulic cylinder is located with respect to the speed increasing hydraulic cylinder.
- An operation oil path connecting the mechanism and the deceleration hydraulic cylinder can be provided so as to pass through the opposite side of the deceleration hydraulic cylinder from the side where the acceleration hydraulic cylinder is located. Therefore, the path of each operation oil path can be formed as a simple path as compared with the case where any of the operation oil paths is provided so as to pass through the same side with respect to the acceleration hydraulic cylinder and the deceleration hydraulic cylinder.
- FIG. 3 is a hydraulic circuit diagram for performing a speed change operation of the speed change transmission. It is a block diagram which shows the operating device of a transmission gearbox. Explanation showing the relationship among the operating state of the forward clutch, the reverse clutch and the switching clutch, the drive mode of the transmission, the speed change state of the continuously variable transmission, the rotational direction of the deceleration output shaft, and the rotational speed of the deceleration output shaft.
- FIG. 1 is a left side view showing an entire combine according to an embodiment of the present invention.
- FIG. 2 is a right side view showing the entire combine according to the embodiment of the present invention.
- the combine according to the embodiment of the present invention is equipped with a pair of left and right crawler type traveling devices 2, 2 at the lower part of the body frame 1, It has a running aircraft to run.
- the traveling machine body includes a boarding type driving unit 3 provided at the front end portion on the right end side, and is configured to be mounted on and operated by the driving unit 3.
- the driving unit 3 includes a driving cabin 3a.
- the cutting part 4 is connected to a part on the front end side of the machine body frame 1 and located on the left side of the driving part 3.
- a threshing device 5 is provided in the left area at the rear of the machine frame 1, and a grain tank 6 is provided in the right area at the rear of the machine frame 1.
- This combine is for harvesting rice, wheat, etc. that can be harvested in six rows, and is structured as follows.
- the reaping part 4 includes a reaping part frame 10 that is swingable forward and backward from the front end of the machine body frame 1, and the reaping part frame 10 is oscillated by an elevating cylinder 11. Ascending / descending operation state in which the front end side of 10 is lowered near the ground, and the ascending non-operation state in which the cutting unit frame 10 is elevated from the ground. The reaping part 4 is driven in the descending operation state, thereby reaping the planted cereal and supplying the reaped device 5 to the threshing device 5.
- a plurality of dividers 12 arranged and supported on the front end of the cutting unit frame 10 in the lateral direction of the traveling machine guide the planted culm to be harvested among the planted culms to the pulling device 13 located at the rear.
- Each of the six pulling devices 13 raises and processes the planted cereal rice cake by raising it with the raising claws.
- the clipper type mowing device 14 supported by the mowing unit frame 10 behind the pulling device 13 cuts the planted culm stock in the raised state and cuts the planted culm.
- a conveying device 15 located from above the reaping device 14 to the front of the threshing device 5 conveys the harvested cereal masher to the left side of the traveling machine body and feeds it to the rear side of the traveling machine body and supplies it to the conveying start end of the threshing feed chain 5a.
- the threshing device 5 feeds the tip side of the harvested cereal cocoon to the handling room while sandwiching the stock side of the chopped cereal meal by the threshing feed chain 5a and transporting it to the rear side of the traveling machine body.
- the harvested cereal meal is threshed by the handling cylinder 16 that rotates around the core, and the grain obtained by the threshing process is supplied to the sorting unit 17.
- the sorting unit 17 performs a sorting process for separating the grain from dust, and the grain after the sorting process is carried out of the threshing machine and supplied to the grain tank 6.
- the grain tank 6 stores the grain supplied from the threshing device 5.
- the grain tank 6 is provided with an unloader 18 having a vertical screw conveyor 18a arranged on the rear side in the vertical direction of the traveling machine body, and the stored grain can be taken out by the unloader 18.
- the unloader 18 includes a vertical screw conveyor 18a and a horizontal screw conveyor 18b extended from the upper end of the vertical screw conveyor 18a so as to be swingable up and down.
- the transmission device that drives the reaping unit 4, the threshing device 5, and the traveling device 2 will be described.
- an engine 7 is provided below the operation unit 3. More specifically, the engine 7 is provided below the portion of the driving unit 3 where the driver seat 3b is located. The engine 7 is provided below the seat support 3c that supports the driver's seat 3b with the top plate portion. The engine 7 is supported by an engine support frame portion 1 a of the body frame 1 via a cushion rubber 9.
- FIG. 6 is a schematic diagram showing the transmission device.
- the engine 7 is provided with an output shaft 7a that faces the traveling machine body inwardly.
- the driving force of the output shaft 7a is transmitted to the input shaft 21a of the cutting transmission 21 by the engine side transmission means 20 provided with a transmission belt.
- the driving force of the output shaft 21b of the cutting transmission 21 is configured to be transmitted to the input shaft 4a of the cutting unit 4 by the cutting unit side transmission means 22 having a transmission gear.
- the cutting transmission 21 is constituted by a hydrostatic continuously variable transmission.
- the engine side transmission means 20 is provided with a belt tension type clutch 20a, and power transmission to the cutting transmission 21 can be turned on and off by operation of the clutch 20a.
- the driving force of the output shaft 7a of the engine 7 is input to the threshing input case 23 by the threshing transmission means 24 provided with a transmission belt.
- the driving force input to the threshing input case 23 is configured to be transmitted from the first output shaft 23 a to the handling cylinder 16.
- the driving force input to the threshing input case 23 is transmitted from the second output shaft 23b to the sorting unit 17 and the threshing feed chain 5a.
- the threshing transmission means 24 is provided with a belt tension type clutch 24a, and power transmission to the handling cylinder 16, the sorting unit 17 and the threshing feed chain 5a can be turned on and off by operation of the clutch 24a.
- the driving force of the output shaft 7a of the engine 7 is input to the speed change transmission device 30 by the traveling transmission means 26 provided with the transmission belt 25.
- the traveling transmission means 26 includes a tension wheel 27 that applies a transmission tension to the transmission belt 25.
- the tension wheel 27 has a clutch function, and power transmission to the speed change transmission device 30 can be turned on and off by switching the tension wheel 27.
- the output of the transmission device 30 is transmitted to the traveling transmission device 31 and transmitted from the pair of left and right output shafts 31a, 31a provided at the lower portion of the traveling transmission device 31 to the crawler drive wheels 2a of the left and right traveling devices 2, 2. It is comprised so that it may do.
- the left and right output shafts 31 a are accommodated in a cylindrical output shaft case 33 extending from a traveling transmission case 32 provided in the traveling transmission device 31.
- the traveling transmission device 31 is disposed between the front end portions of the left and right traveling devices 2.
- the traveling transmission device 31 is supported on the front end portion of the body frame 1 via a connecting member 34.
- the traveling transmission device 31 includes a traveling transmission case 32 supported by the body frame 1 and also receives the output of the transmission transmission device 30 and branches the input driving force to the left and right to output a pair of left and right output shafts 31a and 31a.
- the traveling mission includes a pair of left and right steering clutches, a turning brake, a slow turning clutch, and a reverse clutch.
- the pair of left and right steering clutches are used to switch the left and right traveling devices 2 and 2 to a stopped state to steer the traveling vehicle body leftward or rightward.
- the turning brake applies a brake to the traveling device 2 on the inner side of the left and right traveling devices 2 and 2 to cause the traveling machine body to turn on the ground.
- the slow turning clutch makes the driving speed of the traveling device 2 on the inner side of the left and right traveling devices 2 and 2 lower than the driving speed of the traveling device 2 on the outer side of the turning, and makes the traveling body turn larger than the pivot turning. It turns slowly so that it turns with a radius.
- the reverse clutch turns the traveling machine body smaller than the cruciform turn by making the driving direction of the traveling device 2 inside the turning of the left and right traveling devices 2 and 2 opposite to the driving direction of the traveling device 2 outside the turning. It is a super-spinning one that turns around with a radius.
- the transmission device 30 will be described. As shown in FIGS. 3, 4, and 5, the transmission device 30 is disposed below the driving unit 3 and in front of the traveling body of the engine 7. More specifically, the transmission device 30 is disposed below the floor portion 3 d of the operating unit 3. A transmission case 35 provided in the speed change transmission device 30 is supported by the travel transmission case 32, and the speed change transmission device 30 is supported by the body frame 1 via the travel transmission device 31.
- FIG. 7 is a development view of the transmission device 30 in a longitudinal section state.
- the speed change transmission device 30 includes a transmission case 35 having a lateral side connected to a side portion on the right side of the traveling machine body of the upper end portion of the traveling transmission case 32. ing.
- the speed change transmission device 30 includes an input shaft 37 facing the traveling machine body that is rotatably supported inside the transmission case 35, and a travel that is rotatably supported by the transmission case 35 and the travel transmission case 32 below the input shaft 37.
- It includes a deceleration output shaft 38 that faces the fuselage, a continuously variable transmission 40 and a planetary transmission unit 50 housed in a transmission case 35, and a transmission mechanism 60 that is provided across the input shaft 37 and the planetary transmission unit 50. .
- the input shaft 37 is connected to the pulley shaft 28 disposed concentrically with the input shaft 37 on the lateral outer side of the transmission case 35 so as to rotate integrally.
- the pulley shaft 28 constitutes the traveling transmission means 26.
- the pulley shaft 28 is rotatably supported via a bearing in a cylindrical shaft case 29 that extends from the lateral side portion of the transmission case 35 inwardly of the traveling machine body.
- the extending end side of the shaft case 29 is supported by the traveling transmission case 32 via a connecting rod 29a.
- the continuously variable transmission unit 40 includes a hydraulic pump 41 having a pump shaft 41 a disposed concentrically with the input shaft 37, and a motor that is disposed below the hydraulic pump 41 and that faces the traveling machine body. And a hydraulic motor 42 having a shaft 42a.
- the pump shaft 41a and the motor shaft 42a are rotatably supported by a port block 43 and a transmission case 35 disposed on the side opposite to the side where the planetary transmission unit 50 is located with respect to the continuously variable transmission unit 40.
- the port block 43 is attached to the end of the transmission case 35 on the side where the continuously variable transmission 40 is located.
- the pump shaft 41a and the input shaft 37 are coupled so as to rotate integrally by a coupling member 37a (see FIG. 8).
- the connecting member 37a is fitted to the pump shaft 41a and the input shaft 37 from the outside, and is connected to the pump shaft 41a and the input shaft 37 so as to integrally rotate with the spline structure.
- the hydraulic pump 41 is an axial plunger type and a variable displacement type hydraulic pump.
- the hydraulic motor 42 is an axial plunger type and a variable displacement type hydraulic motor.
- the hydraulic pump 41 and the hydraulic motor 42 are connected by a drive circuit 44 (see FIG. 15) formed in the port block 43.
- the hydraulic pump 41 functions as a so-called main transmission
- the hydraulic motor 42 functions as a so-called auxiliary transmission.
- the continuously variable transmission unit 40 inputs the driving force transmitted from the engine 7 to the input shaft 37 to the pump shaft 41a, and converts the input driving force into a driving force in the forward rotation direction and a driving force in the reverse rotation direction.
- the hydrostatic continuously variable transmission unit is configured so that the rotational speed of the driving force in the forward rotation direction and the reverse rotation direction is changed to a stepless step and output from the motor shaft 42a.
- the motor shaft 42a constitutes a continuously variable output shaft of the continuously variable transmission 40.
- the motor shaft 42a will be referred to as a continuously variable output shaft 42a.
- the continuously variable transmission 40 is switched to the neutral state, the forward drive state, and the reverse drive state by performing the swash plate angle changing operation of the hydraulic pump 41.
- the continuously variable transmission 40 stops the continuously variable output shaft 42a when switched to the neutral state.
- the continuously variable transmission unit 40 is switched to the forward drive state, the continuously variable output shaft 42a is driven in the forward rotation direction, and the swash plate angle changing operation is performed, thereby reducing the forward rotation speed of the continuously variable output shaft 42a.
- the continuously variable transmission unit 40 switches to the reverse rotation drive state, thereby driving the continuously variable output shaft 42a in the reverse rotation direction, and performing a swash plate angle changing operation, whereby the reverse rotation speed of the continuously variable output shaft 42a.
- the planetary transmission unit 50 is arranged concentrically with the stepless output shaft 42 a and is rotatably supported by the transmission case 35, and the rotation support shaft 51.
- the sun gear 52 supported to rotate integrally, a plurality of planetary gears 53 meshed with the sun gear 52, and the planetary gears 53 are rotatably supported on the rotation support shaft 51 with the planetary gears 53 rotatably supported.
- an output shaft 56 is arranged concentrically with the stepless output shaft 42 a and is rotatably supported by the transmission case 35, and the rotation support shaft 51.
- the sun gear 52 supported to rotate integrally, a plurality of planetary gears 53 meshed with the sun gear 52, and the planetary gears 53 are rotatably supported on the rotation support shaft 51 with
- the rotation support shaft 51 is connected to the stepless output shaft 42a so as to rotate integrally with the connection member 51a.
- the connecting member 51a is fitted to the rotation support shaft 51 and the continuously variable output shaft 42a from the outside, and is connected to the rotation support shaft 51 and the continuously variable output shaft 42a so as to be integrally rotated by a spline structure.
- the planetary output shaft 56 and the ring gear 55 are connected by an annular interlocking member 57 so as to rotate integrally.
- the teeth provided on the outer peripheral portion of the interlocking member 57 mesh with the inner teeth of the ring gear 55, and the interlocking member 57 and the planetary output shaft 56 are integrally formed, so that the interlocking member 57 includes the ring gear 55 and the planetary output shaft 56. Are connected so as to rotate together.
- a switching clutch 70 having a clutch body 71 is provided across the planetary output shaft 56 and the sun gear 52.
- the clutch body 71 is supported on the rotary spindle 51 so as to be slidable.
- the clutch body 72 provided between the clutch body 71 and the interlocking member 57 is turned on, and the switching clutch 70 is switched to the engaged state.
- the clutch main body 72 is turned off, and the switching clutch 70 is switched to the cut state.
- the clutch main body 72 includes a meshing tooth on the output shaft side provided on the interlocking member 57 and a meshing tooth provided on the clutch body 71 so as to be engaged with and disengaged from the meshing tooth on the output shaft side. It is.
- the clutch body 71 is provided with connecting teeth that slidably engage with connecting teeth provided on the side of the sun gear 52.
- the clutch body 71 is configured to be slid while sliding the connecting teeth of the clutch body 71 with respect to the connecting teeth of the sun gear 52. Even when the clutch body 71 switches the switching clutch 70 between the engaged state and the disengaged state, the meshing state of the coupling teeth of the clutch body 71 and the coupling teeth of the sun gear 52 is maintained. It is configured to be maintained in a state where it is connected to 52 so as to rotate integrally.
- the switching clutch 70 when the switching clutch 70 is operated to be switched to the engaged state, the rotating support shaft 51, the sun gear 52, the planetary gear 53, and the ring gear 55 are operated to rotate integrally, thereby disabling the speed change operation of the planetary transmission unit 50.
- the output from the continuously variable output shaft 42a of the continuously variable transmission 40 can be transmitted to the planetary output shaft 56 without being shifted.
- the switching clutch 70 When the switching clutch 70 is switched to the disengaged state, the rotation support shaft 51, the sun gear 52, the planetary gear 53, and the ring gear 55 are released from the integral rotation, and the planetary transmission unit 50 can perform a speed change operation.
- the transmission mechanism 60 includes a traveling machine body-side relay shaft 61 that is rotatably supported inside the transmission case 35, and a transmission unit 62 that interlocks the input shaft 37 and the relay shaft 61.
- the forward transmission gear 63 supported in a relatively rotatable manner on the input shaft 37 in a state interlocked with the teeth provided on the carrier 54 and the relay shaft 61 in a state interlocked with the teeth of the carrier 54 so as to be relatively rotatable.
- a supported reverse transmission gear 64 is provided in a relatively rotatable manner on the input shaft 37 in a state interlocked with the teeth provided on the carrier 54 and the relay shaft 61 in a state interlocked with the teeth of the carrier 54 so as to be relatively rotatable.
- the transmission unit 62 includes an input shaft gear 62a that is supported so as to rotate integrally with the input shaft 37, and a relay shaft gear 62b that is supported so as to rotate integrally with the relay shaft 61 while meshing with the input shaft gear 62a. I have.
- a forward clutch 66 having a forward clutch body 65 is provided between the forward transmission gear 63 and the input shaft 37.
- the forward clutch body 65 is supported so as to rotate integrally with a spline portion provided on the input shaft 37 and to be slidable.
- the forward clutch 66 is put into an engaged state by operating a clutch body 66a provided between the forward clutch body 65 and the forward transmission gear 63. Perform switching operation.
- the forward clutch body 65 is slid in a direction away from the forward transmission gear 63, the forward clutch 66 is switched to the disengaged state by disengaging the clutch body 66a.
- the clutch body 66a includes a meshing tooth provided on a side portion of the forward transmission gear 63 and a meshing tooth provided on the forward clutch body 65 so as to be detachable from the meshing tooth, and is configured as a meshing clutch. .
- the forward clutch 66 When the forward clutch 66 is switched to the engaged state, the driving force of the input shaft 37 is transmitted to the forward transmission gear 63 via the forward clutch body 65 and the clutch body 66a, and the forward transmission gear 63 transfers to the carrier 54. introduce.
- the forward clutch 66 When the forward clutch 66 is switched to the disengaged state, the forward transmission gear 63 and the input shaft 37 are allowed to rotate relative to each other, and transmission from the input shaft 37 to the carrier 54 is cut off.
- a reverse clutch 68 including a reverse clutch body 67 is provided across the reverse transmission gear 64 and the relay shaft 61.
- the reverse clutch body 67 is supported so as to rotate integrally with a spline portion provided on the relay shaft 61 and to be slidable.
- the reverse clutch 68 is put into an engaged state by operating a clutch body 68a provided between the reverse clutch body 67 and the reverse transmission gear 64. Perform switching operation.
- the reverse clutch body 67 is slid in a direction away from the reverse transmission gear 64, the reverse clutch 68 is switched to the disengaged state by disengaging the clutch body 68a.
- the clutch body 68a includes a meshing tooth provided on a side portion of the reverse transmission gear 64 and a meshing tooth provided on the reverse clutch body 67 so as to be detachable from the meshing tooth, and is configured as a meshing clutch. .
- the reverse clutch 68 When the reverse clutch 68 is switched to the engaged state, the driving force of the input shaft 37 is transmitted to the reverse transmission gear 64 via the transmission portion 62, the reverse clutch body 67, and the clutch body 68a. To the carrier 54. When the reverse clutch 68 is switched to the disengaged state, the reverse transmission gear 64 and the relay shaft 61 are allowed to rotate relative to each other, and transmission from the input shaft 37 to the carrier 54 is cut off.
- the transmission mechanism 60 when the forward clutch 66 is switched to the engaged state and the reverse clutch 68 is switched to the disconnected state, the driving force of the input shaft 37 is applied to the carrier 54 without passing through the relay shaft 61. Transmit as positive rotational power.
- the transmission mechanism 60 cuts off transmission from the input shaft 37 to the carrier 54 when the forward clutch 66 and the reverse clutch 68 are switched to the disengaged state.
- the deceleration output shaft 38 is interlocked with the planetary output shaft 56 via a deceleration transmission mechanism 75 inside the transmission case 35.
- the deceleration output shaft 38 is interlocked with a pair of input gears 31 b and 31 c included in the traveling transmission device 31 inside the traveling transmission case 32.
- the speed reduction transmission mechanism 75 includes a small diameter gear 76 provided so as to rotate integrally with the planetary output shaft 56, a large diameter gear 77 provided so as to rotate integrally with the speed reduction output shaft 38 while meshing with the small diameter gear 76, and It has.
- the continuously variable transmission unit 40 of the continuously variable transmission unit 40 and the planetary transmission unit 50 performs a shifting action, and the driving force of the continuously variable output shaft 40a is output from the planetary output shaft 56. Even in the case where both the continuously variable transmission unit 40 and the planetary transmission unit 50 perform a speed change operation and a combined driving force is output from the planetary output shaft 56, the driving force of the planetary output shaft 56 is applied to the operation of the deceleration transmission mechanism 75. And then transmitted to the input gears 31b and 31c of the traveling transmission 31.
- the transmission device 30 inputs the driving force from the engine 7 to the input shaft 37, and the driving force from the engine 7 input to the input shaft 37 is transmitted to the continuously variable transmission unit 40 and the planetary transmission unit 50.
- the gear is shifted only by the continuously variable transmission unit 40, and the driving force after this shift is transmitted from the continuously variable output shaft 42a to the deceleration transmission mechanism 75 via the planetary output shaft 56 to decelerate, and then the transmission output from the deceleration output shaft 38.
- the driving force from the engine 7 that is output to the device 31 or input to the input shaft 37 is shifted by the continuously variable transmission 40, and the driving force after the shifting and the driving from the engine 7 that is input to the input shaft 37 are changed.
- the combined driving force is transmitted from the planetary output shaft 56 to the deceleration transmission mechanism 75 and decelerated, and then output from the deceleration output shaft 38 to the traveling transmission device 31.
- FIG. 17 shows the operating state of the forward clutch 66, the reverse clutch 68, and the switching clutch 70, the drive mode of the transmission 30, the shift state of the continuously variable transmission 40, the rotational direction of the deceleration output shaft 38, It is explanatory drawing which shows the relationship with the rotational speed of the deceleration output shaft.
- 17 indicates the forward transmission state of the continuously variable transmission unit 40, and “R” indicates the reverse transmission state of the continuously variable transmission unit 40.
- 17, “OFF” indicates the disengaged state of the forward clutch 66, the reverse clutch 68, and the switching clutch 70
- “ON” indicates the engaged state of the forward clutch 66, the reverse clutch 68, and the switching clutch 70.
- 17 indicates the forward rotation direction of the deceleration output shaft 38
- “reverse rotation” indicates the reverse rotation direction of the deceleration output shaft 38.
- “FL” shown in FIG. 17 indicates that the deceleration output shaft 38 is driven in a low speed rotation region in forward rotation
- “FM” indicates that the deceleration output shaft 38 is driven in a medium speed rotation region in forward rotation.
- “FH” indicates that the deceleration output shaft 38 is driven in a high-speed rotation region in forward rotation.
- RL shown in FIG. 17 indicates that the deceleration output shaft 38 is driven in a low speed rotation region in the reverse rotation, and
- RM indicates that the deceleration output shaft 38 is driven in a medium speed rotation region in the reverse rotation.
- RH indicates that the deceleration output shaft 38 is driven in a high-speed rotation region in the reverse rotation.
- the transmission 30 is referred to as a first mode (hereinafter referred to as HST mode). )become.
- HST mode a first mode
- the continuously variable transmission 40 is shifted and the planetary transmission 50 is not shifted, and the driving force of the input shaft 37 is input to the continuously variable transmission 40 and shifted.
- the force is transmitted from the continuously variable output shaft 42a to the deceleration transmission mechanism 75 via the planetary output shaft 56 to decelerate, and the deceleration output shaft 38 is driven by the decelerated driving force.
- the speed change transmission device 30 is switched to the second mode (hereinafter referred to as HMT mode). It will be called).
- HMT mode the transmission device 30 shifts the continuously variable transmission unit 40 and the planetary transmission unit 50, inputs the driving force of the input shaft 37 to the continuously variable transmission unit 40, and the input shaft The driving force of 37 is combined by the planetary transmission unit 50, and the combined driving force is transmitted from the planetary output shaft 56 to the deceleration transmission mechanism 75 to decelerate, and the deceleration output shaft 38 is driven by the reduced combined driving force.
- the swash plate angle of the hydraulic pump 41 is configured to be changed by a servo cylinder 80.
- the switching operation of the switching clutch 70 includes a spring 71 a that urges the clutch body 71 toward the clutch body 72 and a hydraulic pressure that moves the clutch body 71 toward the clutch body 72. It is configured to be performed by the piston 71b.
- the forward clutch 66 is changed over by a spring 65a for urging the forward clutch body 65 to the cut side of the clutch body 66a, and an operation for moving the forward clutch body 65 to the entry side of the clutch body 66a.
- the hydraulic piston 65b As shown in FIGS.
- the switching operation of the reverse clutch 68 is performed by operating the spring 67a for urging the reverse clutch body 67 to the cut side of the clutch body 68a and moving the reverse clutch body 67 to the entry side of the clutch body 68a. And the hydraulic piston 67b.
- a shift control valve mechanism 81 that performs a shift operation of the hydraulic pump 41 by controlling a servo cylinder 80, and hydraulic pistons 65b, 67b, 71b of the forward clutch 66, the reverse clutch 68, and the switching clutch 70 are provided.
- a valve mechanism 82 that switches the drive mode of the transmission device 30 between the HST mode and the HMT mode and switches the output rotation direction of the transmission device 30 between the forward rotation direction and the reverse rotation direction. It is linked to.
- An operation position sensor 86 that detects the operation position of the main transmission lever 85, an engine rotation sensor 87 that detects the output speed of the engine 7, a continuously variable output rotation sensor 88 that detects the output speed of the continuously variable transmission 40, and the transmission 30.
- a shift output rotation sensor 89 that detects the output speed of the motor is linked to the control device 83.
- the control device 83 is constituted by a microcomputer, and the shift control means 90 is provided in the control device 83.
- the speed change control means 90 changes the drive mode of the speed change transmission device 30, the rotational direction of the deceleration output shaft 38, and the rotational speed of the deceleration output shaft 38 to the drive mode, rotational direction and rotational speed corresponding to the operating position of the main speed change lever 85.
- the shift control valve mechanism 81 and the valve mechanism 82 are controlled based on detection information from the operation position sensor 86, the engine rotation sensor 87, the continuously variable output rotation sensor 88, and the shift output rotation sensor 89. It is.
- the shift control means 90 As shown, the deceleration output shaft 38 can be driven at a variable speed.
- FIG. 18 is an explanatory diagram showing the relationship between the speed change state of the continuously variable transmission 40, the rotational direction of the deceleration output shaft 38, and the rotational speed of the deceleration output shaft 38.
- the horizontal axis in FIG. 18 indicates the speed change state of the continuously variable transmission 40
- the vertical axis indicates the rotation direction and rotation speed of the deceleration output shaft 38.
- “N” on the horizontal axis indicates the neutral state of the continuously variable transmission 40
- “ ⁇ max” on the horizontal axis indicates the highest speed position in the reverse drive state of the continuously variable transmission 40
- “+ max” on the horizontal axis "Indicates the highest speed position of the continuously variable transmission 40 in the forward drive state.
- the solid line FL shown in FIG. 18 indicates the output of the deceleration output shaft 38 driven in the HST mode and forward rotation
- the solid lines FM and FH indicate the output of the deceleration output shaft 38 driven in the HMT mode and forward rotation. Indicates the output.
- the main transmission lever 85 When the main transmission lever 85 is operated from the neutral position “N” to the forward travel range “F” (see FIG. 16), the forward clutch 66 and the reverse clutch 68 are operated to be disconnected, the switching clutch 70 is operated to be engaged, The transmission device 30 enters the HST mode (first mode).
- the operation position of the main speed change lever 85 is set to the first intermediate position of the forward range “F”. Until this occurs, the forward clutch 66 and the reverse clutch 68 are maintained in the disengaged state, and the switching clutch 70 is maintained in the engaged state, and the deceleration output shaft 38 is driven in the forward rotation direction in the HST mode.
- the forward clutch 66 When the operation position of the main transmission lever 85 reaches the first intermediate position of the forward travel range “F”, the forward clutch 66 is switched to the on state, the switching clutch 70 is switched to the disengaged state, and the speed change transmission device 30 is turned to HST.
- the mode is switched to the HMT mode (second mode).
- the forward clutch 66 is switched to the engaged state at a timing when the rotational speeds of the forward clutch body 65 and the forward transmission gear 63 coincide with each other so that a switching shock does not occur.
- the forward clutch 66 and the reverse clutch 68 are operated to be disengaged, and the switching clutch 70 is operated to be engaged.
- the transmission device 30 enters the HST mode.
- the operation position of the main speed change lever 85 is set to the first intermediate position of the reverse range “R”. Until this occurs, the forward clutch 66 and the reverse clutch 68 are maintained in the disengaged state, and the switching clutch 70 is maintained in the engaged state, and the deceleration output shaft 38 is driven in the reverse rotation direction in the HST mode.
- the continuously variable transmission 40 is decelerated toward the maximum speed position “ ⁇ max” in the reverse drive state, and the reverse rotation speed of the deceleration output shaft 38 increases steplessly. I will do it.
- the continuously variable transmission 40 is shifted to the highest speed position “ ⁇ max” in the reverse drive state, and the reverse rotation of the deceleration output shaft 38 is performed. The speed becomes “RV1”.
- the reverse clutch 68 When the operation position of the main transmission lever 85 reaches the first intermediate position of the reverse travel range “R”, the reverse clutch 68 is switched to the on state, the switch clutch 70 is switched to the disengagement state, and the speed change transmission 30 is set to HST. Switch from mode to HMT mode. Switching to the engaged state of the reverse clutch 68 is performed at a timing when the rotational speeds of the reverse clutch body 67 and the reverse transmission gear 64 coincide with each other so that a switching shock does not occur.
- the reverse clutch 68 When the main transmission lever 85 is operated from the first intermediate position of the reverse range “R” toward the reverse maximum speed position, the reverse clutch 68 is maintained in the engaged state, and the forward clutch 66 is maintained in the disengaged state. The clutch 70 is maintained in the disengaged state, and the deceleration output shaft 38 is driven in the reverse rotation direction in the HMT mode. As indicated by the solid line RM, the continuously variable transmission 40 is decelerated toward the neutral state “n” in the reverse drive state, and the reverse rotation speed of the deceleration output shaft 38 increases steplessly. Go. When the operation position of the main speed change lever 85 becomes the second intermediate position of the reverse range “R”, the continuously variable transmission 40 is changed from the reverse drive state to the forward drive state.
- FIG. 11 is a left side view showing the transmission device 30.
- FIG. 12 is a right side view showing the transmission device 30.
- FIG. 13 is a plan view showing the speed change transmission device 30.
- the input shaft 37, the relay shaft 61, and the continuously variable output shaft 42 a are arranged above the deceleration output shaft 38.
- the relay shaft 61 is positioned between the input shaft 37 and the continuously variable output shaft 42a in the vertical direction of the traveling machine body, and the relay shaft 61 is positioned behind the input shaft 37 and the continuously variable output shaft 42a in the longitudinal direction of the traveling machine body. I'm allowed.
- the input shaft 37 and the continuously variable output shaft 42a are arranged in the vertical direction of the traveling machine body.
- the relay shaft 61 is disposed slightly in front of the deceleration output shaft 38.
- the arrangement of the hydraulic pump 41 and the hydraulic motor 42 is arranged in the vertical direction of the traveling machine body so that the operation of forming the drive circuit 44 and the like in the port block 43 is facilitated.
- the interval between the input shaft 37 and the output shaft 7a of the engine 7 is set to an appropriate interval so that the transmission by the traveling transmission means 26 can be accurately performed without making the longitudinal length of the traveling transmission means 26 so long. It is.
- the length of the transmission case 35 in the front-rear direction can be shortened without protruding the relay shaft 61 forward.
- the transmission case 35 includes a continuously variable transmission case unit 95 that houses the continuously variable transmission unit 40, and a planetary transmission case unit 96 that houses the planetary transmission unit 50 and the transmission mechanism 60.
- a continuously variable transmission case unit 95 that houses the continuously variable transmission unit 40
- a planetary transmission case unit 96 that houses the planetary transmission unit 50 and the transmission mechanism 60.
- the continuously variable transmission unit 40 and the planetary transmission unit 50 are accommodated in the transmission case 35 side by side in the traveling machine body lateral direction. More specifically, the continuously variable transmission unit 40 and the planetary transmission unit 50 are accommodated in the transmission case 35 side by side where the continuously variable transmission unit 40 is located on the opposite side of the planetary transmission unit 50 from the side where the traveling transmission device 31 is located. It is.
- the continuously variable transmission case 95 is formed integrally with the planetary transmission case 96.
- the drive oil is stored in a full or almost full state, and the planetary transmission part 50 and the transmission mechanism 60 of the planetary transmission case part 96 are provided.
- Lubricating oil is stored in the planetary transmission chamber 96A to be accommodated in a state where the oil level is lower than the oil level of the continuously variable transmission chamber 95A. Therefore, the continuously variable transmission chamber 95A and the planetary transmission chamber 96A are partitioned by the partition wall 97 provided inside the transmission case 35 to prevent the driving oil in the continuously variable transmission chamber 95A from flowing into the planetary transmission chamber 96A.
- the continuously variable transmission case portion 95 and the planetary transmission case portion 96 are produced by molding an aluminum alloy material.
- the partition wall 97 is formed integrally with the transmission case 35 and made of an aluminum alloy material.
- the planetary transmission case unit 96 includes a first divided planetary transmission case unit 98 in which a continuously variable transmission case unit 95 is integrally formed and a partition wall 97 is provided, and a continuously variable transmission case with respect to the first divided planetary transmission case unit 98.
- the first divided planetary transmission case part 98 and the second divided planetary transmission case part 99 joined to each other at the joining surface 100 are provided on the side opposite to the side where the part 95 is located.
- the planetary transmission case unit 96 is divided into a first divided planetary transmission case unit 98 and a second divided planetary transmission case unit 99 with the joint surface 100 as a divided surface. And it is comprised so that the inside of the planetary transmission case part 96 may be opened largely.
- the port block 43 is removed and the inside of the continuously variable transmission case unit 95 is opened.
- the port block 43 is made of iron or the like so as to have a strength that can withstand the high pressure of the drive oil applied to the drive circuit 44 that connects the hydraulic pump 41 and the hydraulic motor 42.
- the input shaft 37 is connected to the pulley shaft 28 constituting the traveling transmission means 26 on the laterally outer side of the planetary transmission case 96, so that the driving force input from the engine 7 of the transmission 30 can be input to the planetary gear.
- This is performed from the lateral outer side of the transmission case 96 on the side where the traveling transmission device 31 is connected.
- the traveling transmission case 32 is arranged such that the upper end 32 t is positioned below the upper end 96 t of the planetary transmission case 96, and the pulley shaft 28 is positioned above the traveling transmission case 32. That is, the input of the driving force from the engine 7 of the speed change transmission device 30 is performed from a portion on the lateral outer side of the planetary transmission case portion 96 and located above the traveling transmission case 32.
- the transmission control valve mechanism 81 is disposed in a notch-like space S as viewed from above the traveling machine body formed on the lateral end portion on the rear end side of the transmission case 35.
- the space S has the shape of the transmission case 35 in a top view of the traveling machine body, and the traveling machine body rear side end 95r of the continuously variable transmission case 95 is located in front of the traveling machine body rear end 96r of the planetary transmission case part 96. It is formed by making it a shape.
- the space S forms a wide space between the speed change transmission device 30 and the engine 7 so that the engine 7 located behind the speed change transmission device 30 does not become an obstacle to the provision of the speed change control valve mechanism 81.
- the valve mechanism 82 is disposed at the upper part of the transmission case 35. More specifically, the valve mechanism 82 is arranged in an inclined portion 93 formed in an inclined shape lower in the upper part of the transmission case 35 toward the rear side of the traveling machine body. The inclined portion 93 is provided in an upper part of the planetary transmission case portion 96 in the transmission case 35.
- the input shaft 37 is disposed above the relay shaft 61, and the relay shaft 61 is disposed on the upper side inside the planetary transmission case portion 96, thereby providing the inclined portion 93 on the planetary transmission case portion 96.
- the inclined portion 93 on the upper part of the planetary transmission case 96 an empty space is formed above the planetary transmission case 96, and the empty space is utilized as a storage space for the valve mechanism 82 to transmit the valve mechanism 82 to the transmission case 35. It is supported compactly.
- the valve mechanism 82 is disposed in a portion near the partition wall 97 in the inclined portion 93. Therefore, the valve mechanism 82 is moved closer to the operation oil passage formed inside the partition wall 97 so as to connect the valve mechanism 82 and the hydraulic pistons 65b and 67b of the forward clutch 66 and the reverse clutch 68, and The length of the connecting oil passage connecting the valve mechanism 82 can be shortened.
- a charge pump 102 is movably provided in the transmission 30. Specifically, the charge pump 102 is accommodated in a portion of the planetary transmission case portion 96 to which the shaft case 29 is connected. The charge pump 102 is configured to be interlocked with the input shaft 37 and driven by the driving force from the engine 7 transmitted to the input shaft 37.
- the charge pump 102 is constituted by a trochoid pump.
- the suction oil passage 103 extending from the suction side of the charge pump 102 is connected to the traveling transmission case 32.
- the discharge side of the charge pump 102 and the replenishment oil passage 104 of the continuously variable transmission 40 are connected via an oil supply passage 106 provided with an oil filter 105.
- the charge pump 102 sucks the lubricating oil stored in the traveling transmission case 32 and supplies the sucked lubricating oil to the continuously variable transmission unit 40 after removing foreign matters such as iron powder by the oil filter 105.
- the hydraulic motor 42 of the continuously variable transmission 40 is constituted by a variable displacement hydraulic motor. As shown in FIGS. 7 and 10, the swash plate 42 b of the hydraulic motor 42 is tilted by a pair of hydraulic cylinders 107 and 108 housed inside the continuously variable transmission case portion 95 based on the operation of a sub shift lever (not shown). The hydraulic motor 42 is shifted by a pair of hydraulic cylinders 107 and 108.
- the pair of hydraulic cylinders 107 and 108 are allocated to the left and right sides of the traveling machine body of the swash plate 42b.
- One hydraulic cylinder 107 of the pair of hydraulic cylinders 107, 108 is operated to tilt the swash plate 42b to the speed increasing side by pressing the piston 107a from one side in the lateral direction of the traveling body against the operation portion 42c of the swash plate 42b. It is comprised so that it may do.
- one hydraulic cylinder 107 constitutes a speed increasing hydraulic cylinder that shifts the hydraulic motor 42 to the speed increasing side.
- the other hydraulic cylinder 108 of the pair of hydraulic cylinders 107 and 108 pushes the piston 108a against the operation portion 42c of the swash plate 42b from the other in the lateral direction of the traveling machine body to tilt the swash plate 42b to the deceleration side. It is deployed as follows. Therefore, the other hydraulic cylinder 108 constitutes a deceleration hydraulic cylinder that operates the hydraulic motor 42 to the deceleration side.
- a hydraulic circuit for operating the pair of hydraulic cylinders 107 and 108 (acceleration hydraulic cylinder and deceleration hydraulic cylinder) is configured as shown in FIG.
- a motor control valve mechanism 111 is connected to the pair of hydraulic cylinders 107 and 108 via a pair of operation oil passages 110 and 110.
- the motor control valve mechanism 111 and a portion of the oil supply passage 106 on the downstream side of the oil filter 105 are connected by a pilot oil passage 112.
- the motor control valve mechanism 111 includes a pair of directional control valves 111a and 11b connected to a pair of hydraulic cylinders 107 and 108, respectively.
- the motor control valve mechanism 111 is supplied to the oil supply passage 106 by the charge pump 102 and takes in the lubricating oil from which foreign matter has been removed by the oil filter 105 through the pilot oil passage 112.
- the motor control valve mechanism 111 is switched to the speed increasing side, the lubricating oil taken in from the oil supply passage 106 is supplied from one direction control valve 111a to one hydraulic cylinder 107 (speed increasing hydraulic cylinder) as operating oil.
- the motor control valve mechanism 111 is switched to the deceleration side, the lubricating oil taken in from the oil supply passage 106 is supplied as operation oil from the other directional control valve 111b to the other hydraulic cylinder 108 (acceleration hydraulic cylinder).
- the pair of directional control valves 111a and 111b is configured by an electromagnetic control valve and is configured to be switched by an electric operation command from an auxiliary transmission operating tool provided in the operation unit 3.
- the oil filter 105 and the motor control valve mechanism 111 are arranged vertically on the front surface portion 30f of the transmission 30 so that maintenance can be easily performed from the front of the traveling machine body. It has been deployed. As shown in FIG. 14 (a), the oil filter 105 and the motor control valve mechanism 111 are disposed at a site off the transport path of the transport device 15 so that the harvested cereals transported by the transport device 15 are difficult to touch. It is. The oil filter 105 and the motor control valve mechanism 111 are arranged in a portion of the front surface portion 30f of the transmission device 30 that is closer to the lateral outer side of the traveling machine body.
- An oil filter 105 is provided above the motor control valve mechanism 111. Thereby, it is easier to avoid contact between the motor control valve mechanism 111 and the harvested cereal meal being conveyed.
- the oil filter 105 and the motor control valve mechanism 111 are disposed at a location overlapping the partition wall 97 in the front surface portion 30f.
- FIG. 14A is a plan view showing the reaping part 4 in the closed state.
- FIG. 14B is a plan view showing the reaping part 4 in the open state.
- the cutting unit 4 is closed for work supported in the forward direction by swinging around the open / close axis P of the traveling machine body that is disposed at the base of the cutting unit frame 10. It is configured to be switchable between a state and an open state for management supported obliquely laterally outward. Therefore, when the oil filter 105 and the motor control valve mechanism 111 are exchanged or inspected, the cutting unit 4 is switched to the open state, thereby forming a wide working space in front of the transmission 30 and facilitating the operation. It can be done.
- the oil filter 105 includes a mounting screw portion 105C provided on the base end side, and is detachably attached to the filter support portion 140 provided on the front surface portion 30f of the transmission case 35 by the mounting screw portion 105C. It is configured in a cassette structure to support it.
- the filter support 140 is connected to the oil supply passage 141 that communicates with the pre-filtration region 105A of the oil filter 105, the extraction oil passage 142 that communicates with the post-filtration region 105B of the oil filter 105, and the oil supply passage 141 and the extraction oil passage 142.
- An oil drain passage 143 and a drain cylinder portion 144 are formed.
- a drain plug 150 is attached to the drain cylinder portion 144.
- FIG. 20 is a cross-sectional view showing the drain plug 150.
- the drain plug 150 includes a plug main body 151 and an operation unit 152 connected to the proximal end side of the plug main body 151.
- a drain channel 153 is formed inside the plug body 151.
- the drain channel 153 is open to the distal end side of the plug body 151.
- Seal rings 154 are mounted at two locations on the outer peripheral portion on the distal end side of the plug main body 151.
- a drain hole 155 is provided on the proximal end side of the plug body 151. The drain hole 155 communicates with the drain channel 153.
- FIG. 19A is a cross-sectional view showing the filter support 140 in a normal state in which the oil filter 105 is operated.
- the drain plug 150 in a normal time when the oil filter 105 is actuated, the drain plug 150 is closed with the plug body 151 inserted into the oil drainage path 143, and the screw provided in the operation unit 152 The part 152a is fixed in the closed state by fitting into the screw part in the drain cylinder part 144.
- the oil supply passage 141 is closed by closing the opening of the oil supply passage 141 facing the oil discharge passage 143 at a portion located between the two seal rings 154 and 154 of the plug body 151.
- the drain oil passage 142 through the drain oil passage 143, and the drain hole 155 enters the drain cylinder portion 144 and is closed by the drain cylinder portion 144. Let the action take place.
- FIG. 19B is a cross-sectional view showing the filter support portion 140 during drain operation.
- the operating portion 152 when the operating portion 152 is rotated to release the fitting between the screw portion 152a and the drain cylinder portion 144, and the fitting between the screw portion 15a and the drain cylinder portion 144 is released,
- the plug main body 151 is slid toward the outside of the drain cylinder 144 to open the drain plug 150.
- the plug body 151 is detached from the oil supply passage 141 and opens the oil supply passage 141, so that the oil supply passage 141 and the take-out oil passage 142 are in communication with each other through the oil discharge passage 143.
- the drain hole 155 comes out of the drain cylinder portion 144, so that the hydraulic oil located inside the oil filter 105 flows out from the oil supply passage 141 and the extraction oil passage 142 to the oil discharge passage 143, and is discharged.
- the fluid flows from the channel 143 to the drain channel 153 and flows out from the drain hole 155. Therefore, prior to removing the oil filter 105 from the filter support part 140, if the drain plug 150 is operated to open, the hydraulic oil can be taken out from the oil filter 105, and the oil filter 105 is removed from the filter support part 140. It is possible to avoid the hydraulic oil from spilling out from the oil filter 105 at the same time as removing from the oil filter.
- the oil supply passage 141 and the extraction oil passage 142 are communicated with the drain hole 155 through the oil discharge passage 143 and the drain passage 153, and the hydraulic oil located inside the oil filter 105 is supplied to the oil supply passage 141. Since the oil can be discharged from both the oil passages 142 and 142, the hydraulic oil can be discharged quickly from the oil filter 105.
- the length that the plug main body 151 protrudes outward from the drain cylinder part 144 it is possible to adjust the extraction position of the drain hole 155 with respect to the drain cylinder part 144, which is convenient. Also, by adjusting the rotation of the drain plug 150, the opening direction of the drain hole 155 can be adjusted in the front-rear direction, which is convenient.
- one operating oil path 110 of a pair of operating oil paths 110, 110 connecting the motor control valve mechanism 111 and the pair of hydraulic cylinders 107, 108 is transmitted from the motor control valve mechanism 111. It is formed so as to enter the front wall portion of the case 35, pass through the partition wall 97 from the front wall portion, and reach the right hydraulic cylinder 107.
- the other operating oil passage 110 of the pair of operating oil passages 110, 110 enters the front wall portion of the transmission case 35 from the motor control valve mechanism 111, and passes through the inside of the front wall portion from this position in the lateral direction.
- the port block 43 is formed so as to reach from the inside of the port block 43 to the left hydraulic cylinder 108.
- the shift control valve mechanism 81 includes a pair of electromagnetic proportional valves 115 and 115 connected to the servo cylinder 80 via a pair of operation oil passages 114 and 114.
- the pair of electromagnetic proportional valves 115 and 115 are connected to the oil supply passage 106 via a pilot oil passage 117 provided with an oil filter 116.
- a circuit pressure adjusting mechanism 120 is provided in the oil supply passage 106.
- the circuit pressure adjusting mechanism 120 includes a pair of relief valves 122 and 123 connected to the oil supply passage 106 via a relief circuit 121, and an opening / closing valve 124 provided in the relief circuit 121.
- the on-off valve 124 is configured to be switched by an electromagnetic direction control valve 125.
- the circuit pressure adjusting mechanism 120 is configured to switch and adjust the circuit pressure of the oil supply passage 106 in two steps, high and low, by switching the on-off valve 124. That is, the on-off valve 124 is closed to close a portion located between the pair of relief valves 122 and 123 in the relief circuit 121, and the low-pressure relief of the pair of relief valves 122 and 123. The connection between the valve 123 and the oil supply passage 106 is disconnected. As a result, the relief pressure of the relief circuit 121 is set to a high relief pressure by the relief valve 122 on the high pressure side, and the circuit pressure of the oil supply passage 106 is adjusted to a high pressure.
- the opening / closing valve 124 When the opening / closing valve 124 is opened, a portion located between the pair of relief valves 122 and 123 in the relief circuit 121 is opened, and the relief valve 123 on the low pressure side is connected to the oil supply passage 106.
- the relief pressure of the relief circuit 121 is set to a low relief pressure by the relief valve 123 on the low pressure side, and the circuit pressure of the oil supply passage 106 is adjusted to a low pressure.
- the valve mechanism 82 for switching to the direction includes four electromagnetic direction control valves 126 to 129.
- the electromagnetic directional control valve 126 supplies and discharges the operating oil to and from the hydraulic piston 71b of the switching clutch 70, and switches the switching clutch 70 between the disengaged state and the engaged state.
- the electromagnetic direction control valve 127 supplies oil to the hydraulic piston 65b of the forward clutch 66 to switch the forward clutch 66 to the engaged state.
- the electromagnetic direction control valve 128 supplies oil to the hydraulic piston 67b of the reverse clutch 68 and switches the reverse clutch 68 to the engaged state.
- the electromagnetic direction control valve 129 supplies oil to the hydraulic pistons 65b and 67b of the forward clutch 66 and the reverse clutch 68 to switch the forward clutch 66 and the reverse clutch 68 to the disengaged state. .
- the four electromagnetic directional control valves 126 to 129 are configured to supply operating oil from the hydraulic pump 131 via the oil supply passage 130.
- the hydraulic pump 131 is configured to be driven by the input shaft 37 and is mounted on the speed change transmission device 30.
- a mission control valve mechanism 133 is connected to the oil supply passage 130 via a pressure control valve 132 that sets the system pressure of the valve mechanism 82.
- the mission control valve mechanism 133 switches and operates the steering clutch, the turning brake, the slow turning clutch, and the reverse rotation clutch provided in the traveling transmission device 31.
- a switching valve for lubrication is connected to the oil supply passage 130, the forward clutch 66 and the reverse clutch 68 are switched to the disengaged state, and the switching clutch 70 is switched to the engaged state, that is, the transmission transmission 30 is switched to the HST mode.
- the pressure oil may be extracted from the oil supply passage 130 by the switching valve, and the extracted operation oil may be supplied to the upper side inside the planetary transmission case 96 as a lubricating oil.
- the traveling device 2 can be driven to change speed in the first mode (HST mode) and the second mode (HMT mode) even in reverse travel is shown.
- (Relay shaft 61) is not provided, and in reverse traveling, the traveling device 2 may be configured to be driven to change speed only in the first mode (HST mode).
- the continuously variable transmission unit 40 and the planetary transmission unit 50 are arranged in the traveling machine body lateral direction, but may be implemented in the traveling machine body longitudinal direction.
- the example in which the planetary transmission case unit 96 is configured to be divided into two parts, that is, the first divided planetary transmission case unit 98 and the second divided planetary transmission case unit 99 is shown. It may be configured to be divided into two. That is, the second divided planetary transmission case part 99 is divided into an upper end side second divided planetary transmission case part corresponding to the upper end part of the first divided planetary transmission case part 98 and a lower end side part of the first divided planetary transmission case part 98. It may be configured to be freely divideable into a lower end side second divided planetary transmission case portion corresponding to.
- the shape of the transmission case 35 in the top view of the traveling machine body is such that the traveling machine body rear side end 95r of the continuously variable transmission case part 95 is more than the traveling machine body rear side end 96r of the planetary transmission case part 96.
- the traveling machine body rear side end 95r of the continuously variable transmission case part 95 is located in the traveling machine body rear side rather than the traveling machine body rear side end 96r of the planetary transmission case part 96.
- This is implemented by forming a shape in which the traveling machine body rear side end 95r of the continuously variable transmission case 95 and the traveling machine body rear side end 96r of the planetary transmission case part 96 are linearly aligned in the lateral direction of the traveling machine body. May be.
- the upper end 32t of the traveling transmission case 32 is positioned below the upper end 96t of the planetary transmission case 96.
- the upper end 32t of the traveling transmission case 32 is the planetary transmission. It is configured to be positioned above the upper end 96t of the case portion 96, or configured so that the upper end 32t of the traveling transmission case 32 and the upper end 96t of the planetary transmission case portion 96 are positioned at the same height. May be.
- the input shaft 37, the continuously variable output shaft 42a, and the relay shaft 61 are disposed above the deceleration output shaft 38.
- the input shaft 37, the continuously variable output shaft 42a, and the relay shaft are illustrated. 61 may be provided in front of the deceleration output shaft 38.
- valve mechanism 82 is provided in the planetary transmission case 96 in the above-described embodiment.
- valve mechanism 82 is provided in the continuously variable transmission case 95 or a support member different from the transmission 30. May be deployed and implemented.
- the present invention can be used not only for self-removal type but also for ordinary type combine harvesters.
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Abstract
Description
すなわち、伝動ケースのうちの無段変速部を収容する無段変速室には、無段変速部の構造上、作動油を充満又はほぼ充満させる必要がある。伝動ケースのうちの遊星伝動部を収容する遊星伝動室に潤滑油を満杯や満杯に近い状態で貯留すると、潤滑油に起因する遊星伝動部の駆動抵抗が大きくなるため、遊星伝動室における潤滑油の貯留量は、満杯量にせず、必要最小限の量にする。従って、無段変速室と遊星伝動室とを、油が自由に流通しないように仕切る必要がある。
油圧ポンプと油圧モータとを接続する駆動回路には、高圧の作動油圧が掛かるため、駆動回路を形成するポートブロックは、鉄など高強度を備えた素材によって作製する必要がある。
つまり、従来の技術を採用した場合、無段変速室と遊星伝動室とをポートブロックによって仕切るため、伝動ケースをアルミ合金など軽量な素材によって作製しようとすると、伝動ケースのうちの無段変速部を収容する無段変速ケース部と、伝動ケースのうちの遊星伝動部を収容する遊星伝動ケース部とを、別々に作製する必要がある。
本発明の目的は、伝動ケースを安価に軽量化できるコンバインを提供することにある。
本発明によるコンバインは、
油圧ポンプ及び油圧モータを有し、エンジンからの駆動力を入力して変速する静油圧式の無段変速部と、前記エンジンからの駆動力と前記無段変速部の出力とを合成して合成駆動力を走行装置に出力する遊星伝動部と、前記無段変速部及び前記遊星伝動部を収容する伝動ケースとが備えられた変速伝動装置を設け、
前記伝動ケースのうちの前記無段変速部を収容する無段変速ケース部を、前記伝動ケースのうちの前記遊星伝動部を収容する遊星伝動ケース部に一体形成し、
前記無段変速ケース部の前記無段変速部を収容する無段変速室と、前記遊星伝動ケース部の前記遊星伝動部を収容する遊星伝動室とを仕切る隔壁を、前記伝動ケースの内部に備えてあることを特徴とする。
本発明によるコンバインは、
エンジンからの駆動力を入力する入力軸と、前記入力軸の駆動力を変速する静油圧式の無段変速部と、前記入力軸の駆動力と前記無段変速部の無段出力軸の駆動力とを合成して合成駆動力を遊星出力軸から出力する遊星伝動部とが備えられた変速伝動装置を設け、
前記遊星出力軸からの前記合成駆動力を走行装置に伝達する走行伝動装置を設け、
前記遊星出力軸に減速伝動機構を介して連動され、前記遊星出力軸からの前記合成駆動力を減速して前記走行伝動装置に出力する減速出力軸を、前記変速伝動装置に備えてあることを特徴とする。
従って、変速伝動装置を走行機体前後方向長さが短いコンパクトなものにして、比較的狭いスペースに配備できる。
本発明によるコンバインは、
運転部の下方に設けられたエンジンと、
前記エンジンからの駆動力を入力して変速する静油圧式の無段変速部、及び前記エンジンからの駆動力と前記無段変速部からの駆動力とを合成する遊星伝動部を有し、前記遊星伝動部からの合成駆動力を走行装置に出力する変速伝動装置と、を備え、
前記運転部の下方において、前記変速伝動装置を前記エンジンよりも走行機体前方に配備し、
前記無段変速部に供給される作動油に作用するオイルフィルターと、前記無段変速部の油圧モータの変速操作を行なうモータ制御バルブ機構とを、前記変速伝動装置の前面部又は横外面部に、上下方向に並べて配備してあることを特徴とする。
本構成によると、エンジンよりも走行機体前方に配備した変速伝動装置の前面部又は横外面部にオイルフィルター及びモータ制御バルブ機構を配備したものだから、オイルフィルター及びモータ制御バルブ機構の走行機体前方側又は走行機体横外側に作業用スペースを確保し易い。また、オイルフィルターとモータ制御バルブ機構とを上下方向に並べたものだから、オイルフィルター及びモータ制御バルブ機構の走行機体前方側又は走行機体横外側に確保できる作業スペースの横幅が比較的狭くても、オイルフィルター及びモータ制御バルブ機構に対して手が届き易い。
従って、本発明によると、オイルフィルター及びモータ制御バルブ機構に対するメンテナンス作業を行なうのに、作業用スペースを確保し易とか、手が届き易くて能率よく作業できる。
本発明において、前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部に配備してあると好適である。
本発明によると、オイルフィルター及びモータ制御バルブ機構を変速伝動装置の横幅内にコンパクトに配備できる。
本発明において、前記オイルフィルターを前記モータ制御バルブ機構の上方に配備してあると好適である。
本発明によると、モータ制御バルブ機構の上方をオイルフィルターによって覆うことができ、たとえば変速伝動装置の上方を刈取穀稈が搬送される場合、搬送される刈取穀稈がモータ制御バルブ機構に触れることを回避し易くできるなど有利である。
本発明において、前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部のうちの走行体横外側寄りの部位に配備してあると好適である。
本発明によると、オイルフィルター及びモータ制御バルブ機構を前面部に配備するものでありながら、オイルフィルター及びモータ制御バルブ機構を走行機体の横外側寄りの部位に位置させ、たとえば変速伝動装置の上方を刈取穀稈が搬送される場合、搬送される刈取穀稈がオイルフィルター及びモータ制御バルブ機構に触れることを回避し易くできるなど有利である。
本発明において、前記変速伝動装置は、前記無段変速部及び前記遊星伝動部を収容する伝動ケースを備え、前記伝動ケースは、前記無段変速部を収容する無段変速室と、前記遊星伝動部を収容する遊星伝動室と、前記無段変速室と前記遊星伝動室とを仕切る隔壁と、を備え、前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部のうち、前記隔壁に重なる箇所に配備してあると好適である。
本発明によると、前面部のうちの隔壁による補強を受ける部位によってオイルフィルター及びモータ制御バルブ機構を強固に支持させることができる。また、モータ制御バルブ機構と油圧モータとを接続する操作油路を隔壁に形成する場合、モータ制御バルブ機構を操作油路に対して短い接続油路で接続することができる。
本発明によると、モータ制御バルブ機構と増速油圧シリンダとを接続する操作油路を、増速油圧シリンダに対して減速油圧シリンダが位置する側と反対側を通るように配備し、モータ制御バルブ機構と減速油圧シリンダとを接続する操作油路を、減速油圧シリンダに対して増速油圧シリンダが位置する側と反対側を通るように配備することができる。従って、いずれの操作油路も増速油圧シリンダ及び減速油圧シリンダに対して同じ側を通るように配備するに比べ、各操作油路の経路を簡素な経路に形成できる。
図1は、本発明の実施例に係るコンバインの全体を示す左側面図である。図2は、本発明の実施例に係るコンバインの全体を示す右側面図である。図1,2に示すように、本発明の実施例に係るコンバインは、機体フレーム1の下部に左右一対のクローラ式の走行装置2,2が装備され、左右一対の走行装置2,2によって自走する走行機体を備えている。走行機体は、右端側の前端部に設けられた搭乗型の運転部3を備え、この運転部3に搭乗して操縦するように構成してある。運転部3には、運転キャビン3aを備えてある。機体フレーム1の前端側の部位であって、運転部3の左横側方に位置する部位に刈取部4を連結してある。機体フレーム1の後部の左領域に脱穀装置5を設け、機体フレーム1の後部の右領域に穀粒タンク6を設けてある。
図3,4,5に示すように、運転部3の下方に、エンジン7を設けてある。詳述すると、エンジン7は、運転部3のうちの運転座席3bが位置する部位の下方に設けてある。エンジン7は、運転座席3bを天板部で支持する座席支持台3cの下方に設けてある。エンジン7は、機体フレーム1のうちのエンジン支持フレーム部1aにクッションゴム9を介して支持されている。
図3,4,5に示すように、変速伝動装置30は、運転部3の下方であって、エンジン7の走行機体前方に配置してある。詳述すると、変速伝動装置30は、運転部3のうちの床部3dの下方に配置してある。変速伝動装置30に備えてある伝動ケース35が走行伝動ケース32に支持されており、変速伝動装置30は、走行伝動装置31を介して機体フレーム1に支持されている。
一対の油圧シリンダ107,108に一対の操作油路110,110を介してモータ制御バルブ機構111を接続してある。モータ制御バルブ機構111と、給油路106のうちのオイルフィルター105よりも下流側の部位とを、パイロット油路112によって接続してある。モータ制御バルブ機構111は、一対の油圧シリンダ107,108に各別に接続された一対の方向制御弁111a,11bを備えている。
すなわち、開閉弁124は、閉じ操作されることにより、リリーフ回路121のうちの一対のリリーフ弁122,123の間に位置する部位を閉じ、一対のリリーフ弁122,123のうちの低圧側のリリーフ弁123と給油路106との接続を絶つ。この結果、リリーフ回路121のリリーフ圧が高圧側のリリーフ弁122によって高リリーフ圧に設定され、給油路106の回路圧が高圧に調整される。
(1)上記した実施例では、隔壁97を伝動ケース35に一体成形した例を示したが、伝動ケース35とは別部材に作製してから伝動ケース35に装着するよう構成して実施してもよい。
(14)上記した実施例では、オイルフィルター105をモータ制御バルブ機構111の上方に配備した例を示しが、オイルフィルター105をモータ制御バルブ機構111の下方に配備し手実施してもよい。
(15)上記した実施例では、増速油圧シリンダ107と減速油圧シリンダ108とを斜板42bに対して走行機体左右に振り分けて配備した例を示したが、増速油圧シリンダ107及び減速油圧シリンダ108を共に斜板42bの左横側あるいは右横側に配備して実施してもよい。
3 運転部
7 エンジン
30 変速伝動装置
30f 前面部
30s 横外面部
31 走行伝動装置
32 走行伝動ケース
32t 上端
35 伝動ケース
37 入力軸
38 減速出力軸
40 無段変速部
41 油圧ポンプ
42 油圧モータ
42a モータ軸
42b 斜板
43 ポートブロック
44 駆動回路
50 遊星伝動部
56 遊星出力軸
60 伝動機構
61 中継軸
75 減速伝動機構
81 変速制御バルブ機構
82 バルブ機構
93 傾斜部位
95 無段変速ケース部
95A 無段変速室
95r 走行機体後方側端
96 遊星伝動ケース部
96A 遊星伝動室
96t 上端
96r 走行機体後方側端
97 隔壁
98 第1分割遊星伝動ケース部
99 第2分割遊星伝動ケース部
105 オイルフィルター
107 増速油圧シリンダ
108 減速油圧シリンダ
111 モータ制御バルブ機構
Claims (24)
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油圧ポンプ及び油圧モータを有し、エンジンからの駆動力を入力して変速する静油圧式の無段変速部と、前記エンジンからの駆動力と前記無段変速部の出力とを合成して合成駆動力を走行装置に出力する遊星伝動部と、前記無段変速部及び前記遊星伝動部を収容する伝動ケースとが備えられた変速伝動装置を設け、
前記伝動ケースのうちの前記無段変速部を収容する無段変速ケース部を、前記伝動ケースのうちの前記遊星伝動部を収容する遊星伝動ケース部に一体形成し、
前記無段変速ケース部の前記無段変速部を収容する無段変速室と、前記遊星伝動ケース部の前記遊星伝動部を収容する遊星伝動室とを仕切る隔壁を、前記伝動ケースの内部に備えてあるコンバイン。
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前記遊星伝動ケース部を、前記無段変速ケース部が一体形成され、かつ前記隔壁が備えられた第1分割遊星伝動ケース部と、前記第1分割遊星伝動ケース部に対して前記無段変速ケース部が位置する側とは反対側に位置する第2分割遊星伝動ケース部とに分割自在に構成してある請求項1に記載のコンバイン。
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前記油圧ポンプと前記油圧モータとを接続する駆動回路を形成するポートブロックを、前記無段変速ケース部の前記遊星伝動ケース部が連結する側とは反対側の端部に装着してある請求項1又は2に記載のコンバイン。
- 前記伝動ケースは、前記無段変速ケース部と前記遊星伝動ケース部とが走行機体横方向に並ぶように形成してあり、
前記伝動ケースの走行機体上面視での形状を、前記無段変速ケース部の走行機体後方側端が前記遊星伝動ケース部の走行機体後方側端よりも走行機体前方側に位置する形状に形成してある請求項1~3のいずれか一項に記載のコンバイン。
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前記伝動ケースの走行機体上面視での形状を、前記無段変速ケース部の走行機体後方側端が前記遊星伝動ケース部の走行機体後方側端よりも走行機体前方側に位置する形状に形成することによって構成された空間に、前記油圧ポンプの変速操作を行なう変速制御バルブ機構を配備してある請求項4に記載のコンバイン。
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前記エンジンが前記伝動ケースの走行機体後方に位置している請求項4又は5に記載のコンバイン。
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前記エンジンからの駆動力を、前記遊星伝動ケース部の前記無段変速ケース部が連結している側と反対側の横外側から前記遊星伝動部及び前記無段変速部に入力するように構成してある請求項4~6のいずれか一項に記載のコンバイン。
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前記伝動ケースは、前記無段変速ケース部と前記遊星伝動ケース部とが走行機体横方向に並ぶように形成してあり、
前記遊星伝動ケース部の前記無段変速ケース部が連結する側と反対側の横側部に連結され、前記遊星伝動部からの合成駆動力を入力して走行装置に伝達する走行伝動ケースを備え、
前記走行伝動ケースは、上端が前記遊星伝動ケース部の上端よりも下方に位置するように配備され、
前記エンジンからの駆動力を、前記遊星伝動ケース部の前記無段変速ケース部が連結している側と反対側の横外側であって、前記走行伝動ケースの上方から前記遊星伝動部及び前記無段変速部に入力するように構成してある請求項1~7のいずれか一項に記載のコンバイン。 -
前記伝動ケースは、前記無段変速ケース部と前記遊星伝動ケース部とが走行機体横方向に並ぶように形成してあり、
前記伝動ケースの上部に、走行機体後方側ほど低い傾斜形状に形成した傾斜部位を備え、
前記変速伝動装置の駆動モードを、前記無段変速部が変速作用して前記遊星伝動部が変速作用しない第1モードと、前記無段変速部及び前記遊星伝動部が変速作用する第2モードとに切換え、かつ前記変速伝動装置の出力の回転方向を前進回転方向と後進回転方向とに切り換えるバルブ機構を、前記傾斜部位に配備してある請求項1~8のいずれか一項に記載のコンバイン。 -
エンジンからの駆動力を入力する入力軸と、前記入力軸の駆動力を変速する静油圧式の無段変速部と、前記入力軸の駆動力と前記無段変速部の無段出力軸の駆動力とを合成して合成駆動力を遊星出力軸から出力する遊星伝動部とが備えられた変速伝動装置を設け、
前記遊星出力軸からの前記合成駆動力を走行装置に伝達する走行伝動装置を設け、
前記遊星出力軸に減速伝動機構を介して連動され、前記遊星出力軸からの前記合成駆動力を減速して前記走行伝動装置に出力する減速出力軸を、前記変速伝動装置に備えてあるコンバイン。
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前記変速伝動装置は、前記エンジンの走行機体前方に配備され、
前記入力軸及び前記無段出力軸は、前記減速出力軸よりも走行機体前方に配備されている請求項10に記載のコンバイン。
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前記入力軸と前記無段出力軸とは、走行機体上下方向に並んでいる請求項10又は11に記載のコンバイン。
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前記入力軸の駆動力を前記遊星伝動部に伝達する伝動機構を備え、
前記伝動機構に中継軸を備え、
前記入力軸の駆動力は、前記中継軸を介さないと、正回転動力として前記遊星伝動部に伝動され、前記中継軸を介すると、逆回転動力として前記遊星伝動部に伝動され、
前記中継軸は、走行機体上下方向で前記入力軸と前記無段出力軸との間に位置し、かつ走行機体前後方向で前記入力軸及び前記無段出力軸よりも後方に位置している請求項10~12のいずれか一項に記載のコンバイン。
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前記中継軸は、前記減速出力軸の上方に位置している請求項13に記載のコンバイン。
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前記入力軸、前記無段出力軸及び前記中継軸は、前記減速出力軸よりも上方に位置している請求項13又は14に記載のコンバイン。
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前記無段変速部及び前記遊星伝動部を収容する伝動ケースを備え、
前記中継軸は、前記伝動ケースのうちの前記遊星伝動部を収容する遊星伝動ケース部の内部における上部側に配備し、
前記遊星伝動ケース部の上部に、走行機体後方側ほど低い傾斜形状に形成した傾斜部位を備えてある請求項13~15のいずれか一項に記載のコンバイン。
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前記減速出力軸の駆動モードを、前記無段変速部が変速作用して前記遊星伝動部が変速作用しない第1モードと、前記無段変速部及び前記遊星伝動部が変速作用する第2モードとに切換え、かつ前記減速出力軸の回転方向を前進回転方向と後進回転方向とに切り換えるバルブ機構を備え、
前記バルブ機構は、前記遊星伝動ケース部の前記傾斜部位に配備してある請求項16に記載のコンバイン。
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前記伝動ケースは、前記無段変速ケース部と前記遊星伝動ケース部とが走行機体横方向に並ぶように形成してあり、
前記伝動ケースに、前記無段変速部と前記遊星伝動部とを仕切る隔壁を備え、
前記バルブ機構は、前記傾斜部位のうちの前記隔壁寄りの部位に配備してある請求項17に記載のコンバイン。 -
運転部の下方に設けられたエンジンと、
前記エンジンからの駆動力を入力して変速する静油圧式の無段変速部、及び前記エンジンからの駆動力と前記無段変速部からの駆動力とを合成する遊星伝動部を有し、前記遊星伝動部からの合成駆動力を走行装置に出力する変速伝動装置と、を備え、
前記運転部の下方において、前記変速伝動装置を前記エンジンよりも走行機体前方に配備し、
前記無段変速部に供給される作動油に作用するオイルフィルターと、前記無段変速部の油圧モータの変速操作を行なうモータ制御バルブ機構とを、前記変速伝動装置の前面部又は横外面部に、上下方向に並べて配備してあるコンバイン。
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前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部に配備してある請求項19に記載のコンバイン。
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前記オイルフィルターを前記モータ制御バルブ機構の上方に配備してある請求項19又は20に記載のコンバイン。
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前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部のうちの走行体横外側寄りの部位に配備してある請求項19~21のいずれか一項に記載のコンバイン。
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前記変速伝動装置は、前記無段変速部及び前記遊星伝動部を収容する伝動ケースを備え、
前記伝動ケースは、前記無段変速部を収容する無段変速室と、前記遊星伝動部を収容する遊星伝動室と、前記無段変速室と前記遊星伝動室とを仕切る隔壁と、を備え、
前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部のうち、前記隔壁に重なる箇所に配備してある請求項19~22のいずれか一項に記載のコンバイン。
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前記オイルフィルター及び前記モータ制御バルブ機構を、前記前面部に配備し、
前記油圧モータの斜板を増速側に傾動操作するよう前記斜板に対して押圧作用する増速油圧シリンダと、前記斜板を減速側に傾動操作するよう前記斜板に対して押圧作用する減速油圧シリンダとを備え、
前記増速油圧シリンダと前記減速油圧シリンダとを、前記斜板に対して走行機体左右に振り分けて配備してある請求項19~23のいずれか一項に記載のコンバイン。
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2014
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- 2014-02-25 CN CN201480051896.4A patent/CN105556173B/zh not_active Expired - Fee Related
- 2014-02-25 KR KR1020167010610A patent/KR102301361B1/ko active IP Right Grant
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JP2009045991A (ja) * | 2007-08-17 | 2009-03-05 | Yanmar Co Ltd | 作業車両 |
JP2011069416A (ja) * | 2009-09-24 | 2011-04-07 | Kubota Corp | 刈取収穫機の走行変速装置 |
JP2012211672A (ja) * | 2011-03-31 | 2012-11-01 | Kubota Corp | 変速伝動装置 |
JP2013173392A (ja) * | 2012-02-23 | 2013-09-05 | Kubota Corp | 作業車用のトランスミッション |
JP2013190069A (ja) * | 2012-03-14 | 2013-09-26 | Kubota Corp | コンバインの走行伝動装置 |
JP2013188185A (ja) * | 2012-03-14 | 2013-09-26 | Kubota Corp | 収穫機用のトランスミッション及びそのトランスミッションを用いた収穫機 |
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CN109780178A (zh) * | 2019-03-21 | 2019-05-21 | 杨仁忠 | 变速箱与传动箱固定连接器 |
Also Published As
Publication number | Publication date |
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CN105556173A (zh) | 2016-05-04 |
CN105556173B (zh) | 2019-04-09 |
KR20160061376A (ko) | 2016-05-31 |
KR102301361B1 (ko) | 2021-09-14 |
US20160238118A1 (en) | 2016-08-18 |
US9845857B2 (en) | 2017-12-19 |
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