JP4915927B2 - Combine - Google Patents

Description

  The present invention relates to a combine equipped with a travel side HST having a variable displacement travel pump and a variable displacement travel motor.

A combine having a traveling side HST having a variable displacement traveling pump and a variable displacement traveling motor in a traveling transmission path has been known.
For example, in Patent Document 1 below, the traveling motor of the traveling side HST is a variable displacement type that can take two stages of output states of a small volume state and a large volume state, and the output state of the variable displacement traveling pump is shown in FIG. There is disclosed a combine in which a changeover switch for switching the output state of the traveling motor is provided on the HST lever to be changed.

The combine described in Patent Document 1 is useful in that the shift width (in other words, the torque width) can be widened by enabling the output state of the travel motor to be switched in two stages. The work efficiency is not considered at all.
That is, the combine described in Patent Document 1 allows the travel motor to take a small volume state during straight running and when not working, and also causes the travel motor to be in a large volume state during turning or cutting. It is only controlled to take, and there is no description about the efficiency of the cutting work.
JP 2004-323014 A

  The present invention has been made in view of the prior art, and is a combine equipped with a travel side HST having a travel pump and a travel motor, both of which are variable displacement types, and can improve the harvesting work efficiency. The purpose is to provide.

The inventor of the present invention is a combine equipped with a travel side HST having a travel pump and a travel motor, both of which are variable displacement type, when the variable volume travel motor is in a small volume state and a large volume state. The power required for travel (hereinafter referred to as travel load) was verified.
The small volume state means a state in which the tilt position of the movable swash plate of the travel motor is close to the neutral position, and the large volume state means that the tilt position of the movable swash plate is This means a state separated from the neutral position.
Therefore, if the tilting position of the movable swash plate of the traveling pump is constant, the output of the traveling motor is faster in the small volume state than in the large volume state.

Specifically, for a large-scale combine (having a body weight of about 6.5 tons) and a medium-sized combine (having a body weight of about 4 tons) equipped with a travel side HST in which both the travel pump and the travel motor are variable displacement types, The travel load when the vehicle speed was changed by operating the movable swash plate of the travel pump was measured with the travel motor held in a small volume state and a large volume state, respectively.
In consideration of the fact that the combine travels straight during the cutting operation, the travel load was verified by traveling the combine straight.

In FIG.1 and FIG.2, the measurement result in a large sized combine and a medium size combine is shown, respectively.
As is clear from FIG. 1 and FIG. 2, when the vehicle speed is constant in both the large combine and the medium combine, the travel power is larger when the travel motor is held in a small volume state. It is lower than when it is held in a state.

  Based on such verification results, the present inventor obtains a new idea that the traveling speed can be increased without increasing the traveling power by setting the traveling motor in a small volume state during the cutting operation. Finally, the present invention has been completed.

Specifically, the present invention is operatively driven by an engine, a traveling side HST that operatively inputs rotational power from the engine, a speed change operation device that operates the traveling side HST, and the traveling side HST. And a threshing device that performs threshing processing on cereals harvested by the reaping device, and the traveling side HST includes the engine A variable displacement travel pump that is operatively connected to the travel pump, and a variable displacement travel motor that is fluidly driven by the travel pump. A pump actuator that changes the volume of the traveling pump, a motor actuator that changes the volume of the traveling motor, the pump actuator, and the motor actuator. A control device that controls the control, wherein the travel motor is configured to be capable of taking a two-stage volume state of a small volume state and a large volume state, and the control device is configured such that the travel motor is in a small volume state. A small volume control mode for controlling the pump actuator so that the output of the traveling side HST changes according to the operation position of the speed change operation member in a state where the motor actuator is controlled to be The pump operating device is controlled so that the output of the traveling side HST changes according to the operation position of the speed change operating member in a state where the motor operating device is controlled so that the travel motor is in a large volume state. Volume control mode and the volume state of the traveling pump by controlling the pump actuator so that the output of the traveling side HST does not change when the volume state of the traveling motor is changed And a transition control mode to change, the combine is configured such that the reaper clutch and the cutting device substantially straight forward state only when it is engaged, it is determined to be in working condition the combine is harvesting, A combine is provided that selects the small volume control mode when it is determined that the combine is in the cutting operation state, and selects the large volume control mode when it is determined that the combine is not in the cutting operation state .

  Preferably, the control device may be configured to disable at least one of the small volume control mode and the large volume control mode based on an artificial signal.

  Preferably, the control device may be configured to select a large volume control mode when the combine is turning.

  Preferably, when the hydraulic pressure of the HST line on the side of the HST line that is in a high pressure among the pair of HST lines that fluidly connect the traveling pump and the traveling motor exceeds a predetermined value in the small volume control mode, It can be configured to transition from a volume control mode to a large volume control mode.

  Preferably, the control device is configured to remove the combine only when the combine is in a substantially straight forward advance state and the harvesting clutch of the harvesting device is in an engaged state, and there is a culm in the harvesting device. It may be configured to determine that it is in a working state.

According to the combine according to the present invention, the output of the travel side HST changes according to the operation position of the speed change operation member in a state where the motor operating device is controlled so that the travel motor is in a small volume state. The output of the travel side HST is the operation position of the speed change operation member in a state in which the motor operation device is controlled so that the travel motor is in a large volume state. A large-volume control mode for controlling the pump operating device so as to change in accordance with the control, and the pump operating device is controlled so that the output of the traveling side HST does not change when the volume state of the traveling motor is changed. And a transition control mode for changing the volume state of the traveling pump, and the small volume control mode is selected when the combine is in the cutting operation state. , It is possible to reduce the running load at the time of cutting work. In other words, the vehicle speed can be increased within the range of power that can be used for traveling, and therefore the cutting work efficiency can be improved.
Furthermore, since it is possible to prevent a difference in traveling speed from occurring during the transition between the small volume state and the large volume state, the traveling operability can be maintained well.

If the configuration is such that the small volume control mode is disabled based on the artificial signal, the traveling torque can be preferentially secured when the traveling load becomes large during the mowing operation in the wet field.
If the large-volume control mode is disabled based on the artificial signal, high-speed traveling can be performed during traveling on the road.

  If the large volume control mode is selected during the turning of the combine, the traveling torque can be preferentially secured when the traveling load becomes large during the turning.

  In the small volume control mode, when the hydraulic pressure of the HST line on the high pressure side of the pair of HST lines fluidly connecting the traveling pump and the traveling motor exceeds a predetermined value, the small volume control mode is switched to the large volume control mode. If it is configured to shift to, in the small volume control mode, it is possible to prevent the operating pressure on the traveling side HST from rising unduly, thereby effectively preventing hydraulic fluid leakage on the traveling side HST, and improving the traveling transmission efficiency. While preventing deterioration, the durability of the traveling side HST can be improved.

  It is determined that the combine is in a working state only when the combine is in a substantially straight forward state and the reaping clutch of the reaping device is in an engaged state, and there is a culm in the reaping device. If constituted, the operation period of the small volume control mode can be stopped to the minimum necessary, and thereby the durability of the traveling side HST can be improved.

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
3 to 5 are a side view, a front view, and a transmission schematic diagram of the combine 1 according to the embodiment of the present invention, respectively.

  As shown in FIGS. 3 to 5, the combine 1 includes a main body frame 2, an engine 9 supported by the main body frame 2, and a pair of left and right traveling devices connected to the main body frame 2. In the embodiment, the crawler type traveling device) 10, the traveling transmission 100 that changes the rotational power from the engine 9 and outputs it to the pair of traveling devices 10, and the book in front of the machine frame 2. A reaping device 30 supported by the machine frame 2 so as to be able to move up and down, a feed chain device 20 for conveying cereals harvested by the reaping device 30 to the left side of the machine frame 2, and the feed chain device 20 The threshing device 40 disposed on the left part of the machine frame 2 and the threshing device 40 so as to perform the threshing process on the cereal bowl conveyed by A constant speed power is operatively input from the swing sorting device 50 disposed below and the engine 9 and a vehicle speed tuned power is operatively input from the following traveling side HST 120 of the traveling transmission 100, A work machine system transmission 200 that outputs rotational power toward a work machine including the reaping device 30, the feed chain device 20, the threshing device 40, and the swing sorting device 50, and a right front portion of the machine frame 2. A driver's seat 5 disposed therein, and a Glen tank 6 that accommodates the grains selected by the swing sorting device 50, the Glen tank 6 disposed behind the driver's seat 5, and the feed chain It includes a waste transporting device 60 that inherits the waste that has been threshed from the device 20 and transports the waste to the rear.

First, the transmission structure in the combine 1 will be described.
The transmission structure of the combine 1 is connected to the traveling system transmission 100 inserted in the traveling system transmission path from the engine 9 to the traveling device 10 and the working machine system transmission path from the engine 9 to the working machine. The work machine transmission 200 is inserted.

FIG. 6 is a schematic transmission diagram of the traveling transmission 100.
As shown in FIGS. 5 and 6, the traveling transmission 100 is composed of a traveling side HST 120 and a turning side HST 130 operatively connected to the engine 9 and the outputs of both the HSTs 120, 130. A traveling system transmission mechanism 140 that transmits to the shafts 55a and 55b and a transmission case 110 that accommodates the traveling system transmission mechanism 140 and supports the traveling side HST 120 and the turning side HST 130 are provided.

FIG. 7 shows a hydraulic circuit diagram of the combine 1.
The travel side HST 120 includes a variable displacement travel pump 120P operatively connected to the engine 9, and a variable displacement travel motor fluidly driven by the travel pump 120P, as shown in FIGS. 120M.

Specifically, the variable displacement travel pump 120P includes a travel-side pump shaft 121 operatively connected to the engine 9, a travel-side hydraulic pump main body 122 supported by the travel-side pump shaft 121 in a relatively non-rotatable manner, Travel pump side volume adjusting means 123 for changing the volume of the travel side hydraulic pump main body 122 is provided.
In the present embodiment, the travel pump side volume adjusting means 123 includes a travel pump side movable swash plate and a travel pump side control shaft that tilts the travel pump side movable swash plate.

The variable displacement travel motor 120M is connected to the travel hydraulic pump main body 122 via a pair of first and second travel HST lines 129a and 129b (see FIG. 7). A travel side motor shaft 126 that supports the travel side hydraulic motor main body 127 so as not to rotate relative to the travel side hydraulic motor main body 127; and a travel motor side volume adjusting means 128 that changes the volume of the travel side hydraulic motor main body 127.
In the present embodiment, the travel motor side volume adjusting means 128 includes a travel motor side movable swash plate and a travel motor side control shaft that tilts the travel motor side movable swash plate.

In the present embodiment, the travel motor side volume adjusting means 128 reduces the volume amount of the travel side hydraulic motor main body 127, thereby making the travel motor 120M a small volume state capable of high speed rotation. It is configured to be able to take two positions: a volume position and a large volume position in which the volume of the travel side hydraulic pump main body 127 is increased, and thereby the travel motor 120M is in a large volume state.
That is, assuming that the amount of hydraulic oil sent from the traveling pump 120P is constant, the traveling motor 120M rotates at a high speed in a small volume state and rotates at a low speed in a large volume state.

The traveling side HST 120 is operated by a speed change operation device.
Specifically, as shown in FIG. 7, the shift operation device includes a shift operation member that can be manually operated, such as an HST lever 310, a travel-side pump actuator 320 that changes the volume of the travel pump 120P, A travel side motor actuating device 330 that changes the volume of the travel motor 120M. The travel side pump actuating device 320 and the travel side motor actuating device 330 are controlled by a control device 400 provided in the combine 1. The operation is controlled.

  The travel-side pump actuator 320 includes a travel-side pump hydraulic piston device 321 and a travel-side pump electromagnetic switching valve 322 that switches supply and discharge of hydraulic fluid to and from the travel-side pump hydraulic piston device 321. ing.

The control device 400 controls the position of the travel-side pump electromagnetic switching valve 322 based on a signal from an operation position detection sensor 410 (see FIG. 5) that detects the operation position of the speed change operation member 310. The traveling pump side movable swash plate is tilted to change the volume of the traveling pump 120P.
When a rotation angle sensor is used as the operation position detection sensor 410, the control device 400 stores the neutral position of the HST lever 310 as an initial value, and the HST lever 310 is based on the initial value. By accumulating the operation direction and the operation angle every time it is operated, the operation position of the HST lever 310 at that time can be recognized.

The travel-side motor actuator 330 has a travel-side motor hydraulic piston device 331 and a travel-side motor electromagnetic switching valve 332 that switches between supply and discharge of hydraulic fluid to the travel-side motor hydraulic piston device 331. ing.
For example, when the travel motor 120M is in the maximum speed output state in the large volume state, the control device 400 sets the travel side motor actuator 330 so that the travel motor 120M shifts from the large volume state to the small volume state. Control the operation.

Preferably, the control device 400 changes the volume state of the travel motor 120M in order to prevent the vehicle speed from changing suddenly when the travel motor 120M is changed between the large volume state and the small volume state. Operation control of the travel-side pump actuator 330 can be performed so that the output rotational speed of the travel motor 120M does not change before and after.
Specifically, the control device 400 includes a relationship between the operating position of the travel-side pump actuator 320 (that is, the tilt position of the travel pump-side movable swash plate) and the output of the travel motor 120M (hereinafter referred to as pump- The motor output relationship) is stored in advance for each case where the traveling motor 120M is in the small volume state and the large volume state.
The control device 400 uses the pump-motor output relationship after the change in the volume state of the travel motor 120M so that the output of the travel motor 120M becomes substantially constant before and after the change in the volume state of the travel motor 120M. The tilt position (target tilt position) of the traveling pump side movable swash plate is calculated and the difference between the target tilt position and the tilt position of the traveling pump side movable swash plate before the transition to the volume state is calculated. A corresponding control signal is output to the travel side pump actuator 320.

  As shown in FIGS. 5 to 7, the turning side HST 130 includes a turning pump 130 </ b> P operatively connected to the engine 9 and a turning motor 130 </ b> M fluidly driven by the turning pump 130 </ b> P.

At least one of the swing pump 130P and the swing motor 130M is a variable displacement type.
In the present embodiment, as shown in FIG. 5, the swing pump 130P is a variable displacement type, and the swing motor 130M is a fixed displacement type.

Specifically, the variable displacement swivel pump 130P includes a swivel pump shaft 131 operatively connected to the engine 9, a swivel hydraulic pump main body 132 supported by the swivel pump shaft 131 so as not to be relatively rotatable, Rotating pump side volume adjusting means 133 for changing the volume of the turning side hydraulic pump main body 132 is provided.
In the present embodiment, the swirl pump side volume adjusting means 133 has a swirl pump side movable swash plate and a swirl pump side control shaft for tilting the swirl pump side movable swash plate.

  The fixed displacement swing motor 130M includes a swing hydraulic motor main body 137 fluidly connected to the swing hydraulic pump main body 132 via a pair of swing first and second HST lines 139a and 139b, and the swing hydraulic pressure. It has a turning side motor shaft 136 that supports the motor body 137 so as not to be relatively rotatable, and a fixed swash plate (not shown) that fixes the volume of the turning side hydraulic motor body.

The turning side HST 130 is operated by a turning operation device.
Specifically, as shown in FIG. 7, the turning operation device includes a turning operation member that can be manually operated, such as a steering handle 350, and a turning-side pump actuator 360 that changes the volume of the turning pump 130P. The swivel pump actuating device 360 is controlled by the control device 400.

  Specifically, the swing-side pump operating device 360 includes a swing-side pump hydraulic piston device 361, and a swing-side pump electromagnetic switching valve 362 that switches supply and discharge of hydraulic oil to and from the swing-side pump hydraulic piston device 361. The position of the revolving-side pump electromagnetic switching valve 362 is controlled by the control device 400.

The control device 400 controls the position of the electromagnetic pump switching valve 362 for the swivel pump based on a signal from a turning angle sensor 420 (see FIG. 5) that detects the turning angle of the steering handle 350. The swing pump hydraulic piston device 361 is operated to tilt the swing pump side movable swash plate.
When a rotation angle sensor is used as the turning angle sensor 420, the control device 400 stores the straight traveling position of the steering handle 350 as an initial value and operates the steering handle 350 with reference to the initial value. Each time the operation direction and the operation angle are cumulatively stored, the operation position of the steering wheel 350 at that time can be recognized.

  As shown in FIG. 6, the traveling transmission mechanism 140 uses a pair of first and second planetary gear mechanisms 170a, b and the rotational power of the traveling motor shaft 126 as the first and second planetary gear mechanisms 170a. , B in the same rotational direction and the rotational power of the turning-side motor shaft 136 is transmitted to one of the first and second planetary gear mechanisms 170a, 170b in the forward rotation direction and the other. And a turning-side output transmission mechanism 190 for transmitting in the reverse direction.

The first and second planetary gear mechanisms 170a and 170b transmit the rotational power from the traveling-side output transmission mechanism 180 and the turning-side output transmission mechanism 190 to the first and second traveling system output shafts 55a and 55b, respectively. Is configured to do.
Specifically, the first and second planetary gear mechanisms 170a, 170b are respectively a sun gear 171, a planetary gear 172 meshed with the sun gear 171 so as to revolve around the sun gear 171, and the planetary gear 172. The carrier 173 revolves around the sun gear 171 together with the planetary gear 172, and the internal gear 174 meshes with the planetary gear 172.
In the present embodiment, the traveling-side output transmission mechanism 180 is operatively connected to the internal gear 174 and the turning-side output transmission mechanism 190 is operatively connected to the sun gear 171, which corresponds to the carrier 173. The traveling system output shafts 55a and 55b are operatively connected.

The travel side output transmission mechanism 180 includes a travel side output shaft 181 operatively connected to the travel side motor shaft 126, a branch shaft 185 operatively connected to the travel side output shaft 181, and rotational power of the branch shaft 185. Is transmitted to the internal gear 174 of the first planetary gear mechanism 170a, and the rotational power of the branch shaft 185 is transmitted to the internal gear 174 of the second planetary gear mechanism 170b. And a second traveling side output gear train 186b.
The first and second traveling side output gear trains 186a, 186b have the same transmission direction and transmission ratio.

In the present embodiment, the travel-side output transmission mechanism 180 includes a parking brake device 182 that can operatively add a braking force to the travel-side motor shaft 126 in addition to the above configuration.
In the present embodiment, the parking brake device 182 is disposed between the travel-side output shaft 181 and the branch shaft 185 in the power transmission direction.
Specifically, the parking brake device 182 receives a rotational power from the travel-side output shaft 181 and outputs it to the branch shaft 185, and selectively applies a braking force to the brake shaft 183. And a brake unit 184 that can be added.

Further, in the present embodiment, the travel side output transmission mechanism 180 includes a sub-transmission mechanism 187 that shifts the rotational power of the travel side motor shaft 124 in multiple stages.
In the present embodiment, the auxiliary transmission mechanism 187 is configured to be capable of multi-stage shifting between the traveling output shaft 181 and the traveling brake shaft 183.

The turning-side output transmission mechanism 190 includes a turning-side output shaft 191 operatively connected to the turning-side motor shaft 136, a common shaft 192 operatively connected to the turning-side output shaft 191, and rotational power of the common shaft 192. Is transmitted to the sun gear 171 of the first planetary gear mechanism 170a, and the second swing is transmitted to the sun gear 171 of the second planetary gear mechanism 170b. Side output gear train 193b.
The first and second turning-side output gear trains 193a and 193b are configured to have the same transmission ratio but opposite transmission directions.

In FIG. 6, reference numeral 194 denotes a turning-side brake device that can operatively apply a braking force to the turning-side motor shaft 134, and reference numeral 195 denotes the turning-side output shaft 134 to the common shaft 192. A clutch device that engages or shuts off power transmission.
Further, reference numeral 155 in FIG. 6 is a cooling fan that is rotationally driven by the power from the input shaft 140, and reference numeral 501 is a charge pump described later.

  The work machine transmission 200 receives constant speed rotational power from the engine 9 and vehicle speed synchronized rotational power from the traveling system HST 120, and constant speed rotation for the threshing device 40 and the swing sorting device 50. Power is output, and constant speed rotational power or vehicle speed synchronized rotational power can be selectively output to the reaping device 30 and the feed chain device 20.

FIG. 8 is a schematic transmission diagram of the work machine transmission 200.
Specifically, as shown in FIGS. 5 and 8, the work machine system transmission 200 includes a counter case 210, a constant speed input shaft 220 operatively connected to the engine 9 via a threshing clutch mechanism 45, and the constant speed transmission. A threshing output shaft 221 that is operatively connected to the speed input shaft 220 and outputs rotational power toward the barrel drive shaft 41 of the threshing device 40; a constant speed transmission shaft 223 that is operatively connected to the constant speed input shaft 220; A vehicle speed tuning input shaft 224 operatively connected to the travel side motor shaft 126, a speed change transmission shaft 225, a vehicle speed tuning side speed change mechanism 240 that shifts between the vehicle speed tuning input shaft 224 and the speed change transmission shaft 225, and A constant speed transmission mechanism 250 that performs a shift between the constant speed transmission shaft 223 and the transmission transmission shaft 225, and the transmission transmission shaft 225 operatively connected to the cutting portion 30. The cutting output shaft 226 for output, the FC transmission mechanism 280 for combining the rotational power of the constant speed transmission shaft 223 and the rotational power of the speed change transmission shaft 225, and the output section of the FC transmission mechanism 280 are operatively connected to the feed. And a feed chain output shaft 227 that outputs rotational power toward the chain portion 20.

In the present embodiment, the constant speed input shaft 220 and the threshing output shaft 221 are integrally formed by a single shaft as shown in FIG.
That is, the single shaft is supported by the counter case 210 along the longitudinal direction of the vehicle so that one end protrudes backward from the counter case 210 and the other end protrudes forward from the counter case 210. The one end portion forms an input end portion that is operatively connected to the engine 9, and the other end portion forms an output end portion that outputs rotational power toward the threshing device 40.

A constant speed input pulley 201 is attached to the constant speed input shaft 220 (the one end portion of the single shaft), and the engine 9 is interposed via a constant speed input belt 202 wound around the constant speed input pulley 201. The constant-speed rotational power is input to the constant-speed input shaft 220.
A threshing output pulley 203 is attached to the threshing output shaft 221 (the other end portion of the single shaft), and the threshing output belt 204 wound around the threshing output pulley 203 is passed to the threshing portion 40. A constant speed rotational power from the engine 9 is transmitted.

  In the present embodiment, the threshing clutch mechanism 45 engages or disengages power transmission from the engine 9 to the constant speed input shaft 220 by applying / releasing tension to the constant speed input belt 202. It is comprised so that it can interrupt | block.

The threshing clutch mechanism 45 is operated by a threshing clutch operating device 510 controlled by the control device 400.
As shown in FIG. 7, the threshing clutch operating device 510 includes a threshing clutch hydraulic piston mechanism 511 and a threshing clutch electromagnetic switching valve 512 that controls the supply and discharge of hydraulic oil to and from the threshing clutch hydraulic piston mechanism 511. And the position of the electromagnetic switching valve 512 for the threshing clutch is controlled by the control device 400 based on an on / off operation of a threshing switch (not shown).

As shown in FIG. 8, the constant speed transmission shaft 223 is arranged in the vehicle width direction so that one end is operatively connected to the constant speed input shaft 220 and the other end protrudes outward from the counter case 210. Along the counter case 210.
The other end of the constant speed transmission shaft 220 forms a swing sorting output shaft 228 that outputs a constant speed rotational power toward the swing sorting device 50.
A swing output pulley 205 is attached to the swing sorting output shaft 228 (the other end of the constant speed transmission shaft 223).

The vehicle speed tuning input shaft 224 is supported by the counter case 210 along the vehicle width direction with one end portion protruding outward from the counter case 210.
A vehicle speed tuning input pulley 206 is attached to the one end of the vehicle speed tuning input shaft 224.
The speed change transmission shaft 225 is supported by the counter case 210 so as to be substantially parallel to the constant speed transmission shaft 223 and the vehicle speed tuning input shaft 224.

  Further, as shown in FIGS. 5 and 8, the work machine transmission 200 includes a one-way clutch 35 interposed between the vehicle speed tuning input shaft 224 and the vehicle speed tuning transmission mechanism 240. .

  The vehicle speed tuning side transmission mechanism 240 is configured to selectively switch the transmission state from the vehicle speed synchronization input shaft 224 to the transmission transmission shaft 225 to a high speed transmission state, a low speed transmission state, or a power cutoff state.

  Specifically, as shown in FIG. 8, the vehicle speed tuning side speed change mechanism 240 includes a high speed gear train 241 and a low speed gear train 242 operatively connected to the vehicle speed tuning input shaft 224, and the high speed gear train 241 or the constant speed. A vehicle speed tuning shifter 243 capable of operatively connecting any one of the gear trains 242 to the speed change transmission shaft 225 is provided.

  The vehicle speed tuning shifter 243 includes a high speed position where the high speed gear train 241 is operatively connected to the speed change transmission shaft 225, a low speed position where the low speed gear train 242 is operatively connected to the speed change transmission shaft 225, and the high speed gear train. 241 and the low-speed gear train 242 can be in a neutral position where the transmission transmission shaft 225 is not operatively connected.

Such a vehicle speed tuning side transmission mechanism 240 is operated by a reaping clutch / transmission operating device 520 controlled by the control device 400.
Specifically, as shown in FIG. 7, the harvesting clutch / transmission operating device 520 performs hydraulic oil supply / discharge control for the harvesting clutch / transmission hydraulic piston mechanism 521 and the harvesting clutch / transmission hydraulic piston mechanism 521. A mowing clutch / shift electromagnetic switching valve 522 is provided.
On the other hand, a cutting switch 430 (see FIG. 7) and a cutting shift lever (not shown) are provided in the vicinity of the driver's seat 5.
The control device 400 controls the position of the harvesting clutch / shift electromagnetic switching valve 522 so that the vehicle speed tuning shifter 243 is positioned at the neutral position based on the OFF operation of the harvesting switch 430, and the harvesting switch 430. , The position control of the cutting clutch / shift electromagnetic switching valve 522 is performed so that the vehicle speed tuning shifter 243 is positioned at a high speed position or a low speed position corresponding to the operation position of the cutting shift lever.

  The constant speed transmission mechanism 250 is configured to selectively switch the transmission state from the constant speed transmission shaft 223 to the transmission transmission shaft 225 to a transmission state, a high-speed cut transmission state, or a power cut-off state.

  Specifically, as shown in FIG. 8, the constant speed side transmission mechanism 250 includes a casting gear train 251 and a high speed cutting gear train 252 operatively connected to the constant speed transmission shaft 223, and the casting gear train 251. Alternatively, a constant speed shifter 253 capable of operatively connecting any one of the high speed cutting gear train 252 to the speed change transmission shaft 225 is provided.

  The constant speed shifter 253 includes a pouring position where the casting gear train 251 is operatively connected to the speed change transmission shaft 225, a high speed cutting position where the high speed cutting gear train 252 is operatively connected to the speed change transmission shaft 225, Both the casting gear train 251 and the high speed cutting gear train 252 can be in a neutral position where the transmission transmission shaft 225 is not operatively connected.

The constant speed side speed change mechanism 250 is operated by a pouring / high speed cutting operation device 530 controlled by the control device 400.
Specifically, as shown in FIG. 7, the pouring / high speed cutting operation device 530 performs hydraulic oil supply / discharge control for the pouring / high speed cutting hydraulic piston mechanism 531 and the pouring / high speed cutting hydraulic piston mechanism 531. And an electromagnetic switching valve 532 for pouring / fast cutting to be performed.
The control device 400 controls the position of the pouring / high speed cut electromagnetic switching valve 532 based on the operation of an operation member (not shown) provided in the vicinity of the driver's seat 5, thereby the constant speed shifter 253. Is positioned at a position corresponding to the operation of the operation member among the pouring position, the high speed cutting position or the neutral position.

The harvesting output shaft 226 is supported by the counter case 210 with one end portion extending outward.
A cutting output pulley 207 is attached to the one end of the cutting output shaft 226.
In the present embodiment, the cutting output shaft 226 is operatively connected to the speed change transmission shaft 225 via a torque limiter 229.

The FC transmission mechanism 280 has a planetary gear mechanism as shown in FIG.
Specifically, the FC speed change mechanism 280 supports a sun gear 281, a planetary gear 282 meshed with the sun gear 281 so as to revolve around the sun gear 281, and the planetary gear 282 so as to be relatively rotatable. A carrier 283 that revolves around the sun gear 281 together with the planetary gear 282 and an internal gear 284 that meshes with the planetary gear 282 are provided, and rotational power of the constant speed transmission shaft 223 is input to the sun gear 281. The rotational power of the transmission shaft 225 is input to the internal gear 284, and the carrier 283 is operatively connected to the feed chain output shaft 227.
In the present embodiment, an FC clutch mechanism 285 is interposed between the carrier 283 and the feed chain output shaft 227.

Here, the hydraulic circuit of the combine 1 will be described.
As shown in FIG. 7, the combine 1 supplies hydraulic oil to the threshing clutch electromagnetic switching valve 512, the mowing clutch / transmission electromagnetic switching valve 522 and the pouring / high speed cutting electromagnetic switching valve 532. The threshing / cutting hydraulic circuit 550, the cutting lifting hydraulic mechanism 561, the lifting hydraulic circuit 560 that controls the supply and discharge of hydraulic fluid to the pair of left and right vehicle lifting hydraulic mechanisms 562 a, 562 b and the auger operating hydraulic mechanism 563, A traveling system hydraulic circuit 570 that controls hydraulic control of a traveling system hydraulic mechanism including the side HST 120 and the turning side HST 130.

As shown in FIG. 7, the traveling system hydraulic circuit 570 is configured such that the traveling hydraulic pump main body 122 and the traveling hydraulic motor main body 127 are fluidly connected to each other so as to form a closed circuit. Side HST lines 129a and 129b, and the swing side first and second HST lines 139a and 139b that fluidly connect the swing side hydraulic pump main body 132 and the swing side hydraulic motor main body 137 so as to form a closed circuit, A charge line 575 for supplying hydraulic fluid to each of the pair of traveling side HST lines 129a and 129b and each of the pair of turning side HST lines 139a and 139b, and a predetermined pressure is set by a relief valve 576 for setting the charge pressure. Toward the charge line 576 adjusted in pressure and the traveling-side pump electromagnetic switching valve 322 A traveling-pump hydraulic fluid line 581 for supplying hydraulic fluid, a traveling-motor hydraulic fluid line 582 for supplying hydraulic fluid toward the traveling-motor electromagnetic switching valve 332, and the turning-pump electromagnetic switching valve And a hydraulic oil line 583 for the swivel pump that supplies the hydraulic oil toward 362.
Note that hydraulic fluid is supplied to the travel side pump hydraulic fluid line 581, the travel side motor hydraulic fluid line 582, and the turning side pump hydraulic fluid line 583 via the charge line 576.

As shown in FIG. 7, the combine 1 according to the present embodiment includes the charge pump 501 and the auxiliary pump 502 in addition to the configuration described above.
Pressure oil is supplied from the auxiliary pump 502 to the lifting hydraulic circuit, and pressure oil is supplied from the charge pump 501 to the charge line 575 and the threshing / reaping hydraulic circuit 550. It is configured.

Here, the control device 400 will be described.
The control device 400 includes a CPU that executes arithmetic processing and a storage unit that stores a control program, which will be described later, and inputs the signals from various setting units and sensors, and the travel side pump based on the control program. A control signal is output to the operating device 320 for driving and the operating device 330 for the traveling motor.

9 to 11 show flowcharts of the control program stored in the control device 400. FIG.
The control program selects a small volume control mode (see FIG. 10), a large volume control mode (see FIG. 11), and a selection control mode for determining whether to select the small volume control mode or the large volume control mode. (Refer to FIG. 9). When the combine 1 is in the cutting operation state, the small volume control mode is selected by the selection control mode.

In the present embodiment, the control device 400 is configured to determine that the cutting device 30 is in the cutting operation state when the cutting device 30 is in the driving state and the combine 1 is in the straight traveling state and the forward traveling state. .
Specifically, as shown in FIG. 9, the selection control mode includes step A-10 for determining whether the reaping device 30 is in a driving state, and a step for determining whether the combine 1 is in a straight traveling state. A-11 and Step A-12 for determining whether or not the combine 1 is in the forward movement state are included.

The determination in step A-10 is determined based on, for example, an input signal from the reaping switch 430 (see FIG. 7).
The determination in step A-11 is, for example, whether or not the input signal from the turning angle sensor 420 (see FIG. 7) that detects the turning angle of the steering handle 350 is within a predetermined threshold range (within a predetermined angle range). Judgment based on.
The determination in step A-12 is made based on, for example, an input signal from an operation position detection sensor 410 (see FIG. 7) that detects the operation position of the speed change operation member 310.

  When a rotation angle sensor is used as the turning angle sensor 420, the control device 400 stores the straight traveling position of the steering handle 350 as an initial value, and the steering handle 350 is based on the initial value. By accumulating the operation direction and the operation angle every time it is operated, the operation position of the steering wheel 350 at that time is recognized, and the control device 400 at that time in step A-11. It is determined whether or not the operation position at is within the range of the threshold value stored in advance.

  Similarly, when a rotation angle sensor is used as the operation position detection sensor 410, the control device 400 stores a neutral position of the HST lever 310 as an initial value and uses the HST lever as a reference based on the initial value. Each time 310 is operated, the operation direction and the operation angle are cumulatively stored, thereby recognizing the operation position of the HST lever 310 at that time, and the control device 400 determines in step A-12. Then, it is determined whether the operation position at that time is the forward side or the reverse side.

  In the present embodiment, the selection control mode includes steps A-20, A-30 and A-31 in addition to the steps as shown in FIG. To do.

In the small volume control mode, the traveling motor actuating device 330 is controlled so that the traveling motor 120M is in a small volume state, and the output state of the traveling motor 120M is set to the operation position of the speed change operation member 310. The travel-side pump actuator 320 is controlled so as to change accordingly.
The small volume state of the travel motor 120M is a state in which the tilt position of the travel motor side movable swash plate is held at a small tilt position close to the neutral position. In this state, the travel motor 120M operates at a high speed. It can be rotated.

  Specifically, as shown in FIG. 10, the small volume control mode is shifted to step B-10 for determining whether or not the traveling motor 120M is in the small volume state, and YES in step B-10. Step B-11, Step B-20 that is shifted in the case of NO in Step B-10, and a transition control mode that follows Step B-20.

The determination in step B-10 is made based on, for example, a signal from a tilt position sensor 450 (see FIG. 7) that detects the tilt position of the travel motor side movable swash plate.
In Step B-20, the control device 400 outputs a control signal to the travel-side motor operating device 330 so that the travel motor 120M is in a small volume state.

Thus, when the travel motor 120M is shifted from the large volume state to the small volume state in step B-20, the output rotation of the travel motor 120M is performed when the amount of oil discharged from the travel pump 120P is constant. The number increases and the traveling speed of the combine 1 increases.
In this regard, in the present embodiment, as described above, the transition control mode is provided after the step B-20, and the transition control mode allows the combine 1 to operate when the volume state of the travel motor 120M changes. It prevents the running speed from changing.

  That is, in the transition control mode, the output state of the travel pump 120P changes by an amount that the output state of the travel motor 120M changes when the travel motor 120M changes state between the small volume state and the large volume state. Thus, the pump actuator 320 is controlled.

  Specifically, as shown in FIG. 10, the transition control mode corresponds to the output change amount of the traveling motor 120M that is accelerated by the traveling motor 120M being shifted from the large volume state to the small volume state. Step C for controlling the travel-side pump actuating device 320 so that the travel-pump-side movable swash plate approaches the neutral position by the corresponding amount (that is, the discharge amount of the travel-side hydraulic pump main body 121 is reduced). -10 and step C-11 for determining whether or not the output of the traveling motor 120M is the number of rotations that matches the operating position of the HST lever 310.

Specifically, as described above, the pump-motor output relationship is stored in advance in the control device 400 for each of the small volume state and the large volume state of the travel motor.
Based on a detection signal from a travel motor output detection sensor 440 (see FIG. 7) that detects the output rotational speed of the travel motor 120M, the control device 400 is in a state before the travel motor 120M is shifted to a small volume state. Is stored, and the traveling motor 120M calculated using the pre-transition motor rotational speed and the pump-motor output relationship is stored. The tilt position of the traveling pump-side movable swash plate in the state before the shift to the small volume state (hereinafter referred to as the pre-transfer pump tilt position) is stored.
In step C-10, the control device 400 uses the pump-motor output relationship so that the output of the traveling motor 120M after the transition to the small volume state matches the motor rotational speed before the transition. , The tilt position of the traveling pump side movable swash plate (hereinafter referred to as the post-transition pump side tilt position) in a state where the travel motor 120M is shifted to the small volume state is calculated, and the post-transition pump side tilt is calculated. The travel-side pump actuator 320 is operated according to the difference between the position and the pre-transition pump-side tilt position.

In step C-11, the control device 400 detects that the actual vehicle speed based on the detection signal from the travel motor output detection sensor 440 detects the operation position of the HST lever 310. It is determined whether or not the operation vehicle speed based on is within a predetermined threshold range.
If NO in step C-11, the process returns to step C-10, and the control device 400 operates the travel-side pump operating device 320 according to the difference between the operating vehicle speed and the actual vehicle speed. .

If YES in step C-11 or step B-10, the control device 400 determines whether or not the HST lever 310 is operated in step B-11.
In step B-11, in addition to determining whether or not the HST lever 310 is operated, the control device 400 determines the operation direction and the operation amount of the HST lever 310 when the HST lever 310 is operated. calculate.
When a rotation angle sensor is used as the operation position detection sensor 410, the control in step B-11 is performed as follows, for example.
That is, the control device 400 determines the operation start time and operation end time of the HST lever 310 based on the signal from the operation position detection sensor 410 and operates between the operation start time and the operation end time. The operation direction and the operation amount of the HST lever 310 are calculated based on a signal from the operation position detection sensor 410.

  If YES in step B-11, the control device 400 uses the pump-motor output relationship in step B-12 to send a control signal corresponding to the operation direction and operation amount to the travel side pump. Output to the actuator.

  Thereafter, the control device 400 determines that the actual vehicle speed based on the detection signal from the travel motor output detection sensor 440 is based on the detection signal from the operation position detection sensor 410 that detects the operation position of the HST lever 310. Is determined to be within a predetermined threshold range (step B-13). If NO, the process returns to step B-12, and the control device 400 determines the actual vehicle speed and the operating vehicle speed. The traveling pump actuating device 320 is actuated according to the difference amount.

Thus, in the combine 1 which concerns on this Embodiment, when it becomes a cutting work state, the said traveling motor 120M will transfer to a small volume state, or will be hold | maintained at a small volume state.
As described in the section of the means for solving the problems, the traveling load when the traveling motor 120M is in the small volume state is smaller than the traveling load when the traveling motor 120M is in the large volume state (FIGS. 1 and 2).
That is, by setting the travel motor 120M in the small volume state, it is possible to travel at the same speed while reducing the travel load compared to the case where the travel motor 120M is in the large volume state.
In other words, by setting the travel motor 120M in a small volume state, it is possible to increase the vehicle speed by using the travel load that is reduced, and therefore it is possible to improve the cutting work efficiency.

  Further, in the present embodiment, as described above, the cutting operation is started when the travel motor 120M is in the large volume state, and even if the travel motor 120M is shifted from the large volume state to the small volume state, the transition is performed. The vehicle speed is kept constant by the control mode. Therefore, the driving operability can be maintained satisfactorily.

Preferably, in the small volume control mode, the control device 400 has a high pressure during forward movement of the pair of first and second travel side HST lines 129a and 129b that fluidly connect the travel pump 120P and the travel motor 120M. When the hydraulic pressure of the first traveling side HST line 129a exceeds a predetermined value, it may be configured to shift from the small volume control mode to the large volume control mode.
By providing such a configuration, it is possible to prevent the hydraulic pressure of the traveling side HST 120 from unreasonably rising in the small volume control mode, thereby effectively preventing hydraulic fluid leakage of the traveling side HST 120 and preventing deterioration of traveling transmission efficiency. In addition, the durability of the traveling side HST 120 can be improved.

  Specifically, as shown in FIG. 10, when the small volume control mode is NO in step B-11 or YES in step B-13, the hydraulic pressure of the first travel side HST line 129a is predetermined. It may be determined whether or not the value is equal to or less than the value.

  The determination in step B-14 is, for example, a signal from a hydraulic pressure detection sensor 460 (see FIG. 7) that detects the hydraulic pressure of the first travel side HST line 129a, and a hydraulic pressure upper limit value stored in advance in the control device 400. Based on

In the large volume control mode, the traveling motor actuating device 330 is controlled so that the traveling motor 120M is in a large volume state, and in this state, the output state of the traveling motor 120M is the operation position of the speed change operation member 310. The travel-side pump actuator 320 is controlled so as to change according to
In FIG. 11 showing the large volume control mode, the same steps as those in the small volume control mode are denoted by the same reference numerals, and detailed description thereof is omitted.

In the large volume control mode, as shown in FIG. 11, step B′-10 for determining whether or not the traveling motor 120M is in the large volume state, and step B shifted to NO in step B′-10. '-20 and a transition control mode following step B'-20.
The determination in step B′-10 is performed based on a signal from the tilt position sensor 450 that detects the tilt position of the travel motor side movable swash plate, for example, as in step B-10.

  In step B'-20, the control device 400 outputs a control signal to the travel side motor actuator 330 so that the travel motor 120M is in a large volume state.

Thus, when the travel motor 120M is shifted from the small volume state to the large volume state in step B′-20, the output of the travel motor 120M is output when the amount of oil discharged from the travel pump 120P is constant. The rotational speed is decelerated and the traveling speed of the combine 1 decreases.
In this regard, in this embodiment, as described above, the transition control mode is provided in the subsequent stage of step B′-20, and by this transition control mode, the combine 1 is changed when the volume state of the travel motor 120M changes. It prevents the running speed from changing.

  The transition control mode in the large-volume control mode is the same as the transition control mode in the small-volume control mode except that Step C-10 is changed to Step C′-10.

  In step C′-10, the control device 400 increases the travel by an amount corresponding to the output change amount of the travel motor 120M that is decelerated by the travel motor 120M being shifted from the small volume state to the large volume state. The travel-side pump actuator 320 is controlled so that the pump-side movable swash plate is separated from the neutral position (that is, the discharge amount of the travel-side hydraulic pump main body 121 is increased).

Specifically, the control device 400 stores a motor rotation speed before the transition of the traveling motor 120M based on a detection signal from the traveling motor output detection sensor 440 (see FIG. 7), and further, the motor before the transition. Stores the pre-transition pump tilt position of the travel pump side movable swash plate in a state before the travel motor 120M calculated using the rotational speed and the pump-motor output relationship is shifted to the large volume state. .
In step C′-10, the control device 400 uses the pump-motor output relationship so that the output of the traveling motor 120M after the transition to the large volume state matches the motor rotational speed before the transition. The traveling position of the traveling pump side movable swash plate in the state where the traveling motor 120M is shifted to the large volume state (post-transition pump-side tilt position) is calculated, and the post-transition pump-side tilt position is calculated. The travel-side pump actuating device 320 is operated in accordance with the amount of difference from the pre-transition pump-side tilt position.

Here, Step A-20, Step A-30, and Step A-31 in the selection control mode will be described.
The selection control mode is preferably only when the harvesting device 30 is in a driving state and the combine 1 is in a straight traveling state and in a forward traveling state, and when there is a cereal in the harvesting device 30. It can be configured to determine that it is in a mowing state.
Specifically, as shown in FIG. 9, the selection control mode may include, in addition to the above steps, a step A-20 for determining whether or not there is cereal in the reaping device 30.
The determination in step A-20 is performed based on, for example, a signal from the grain stalk presence / absence detection sensor 470 (see FIG. 7) provided in the reaping device 30.
By providing such step A-20, the operation time of the small volume control mode can be kept to the minimum necessary, thereby improving the durability of the traveling side HST 120.

Further, in the selection control mode, as shown in FIG. 9, it is determined whether or not to disable the small volume control mode and / or whether to disable the large volume control mode. Step A-31 can be provided.
The determination in step A-30 is performed based on, for example, an ON / OFF operation of a small volume control mode disable switch 480 (see FIG. 7) that can be manually operated.
The determination in step A-31 is made based on, for example, an ON / OFF operation of a large volume control mode disable switch 490 (see FIG. 7) that can be manually operated.

By providing step A-30, the traveling torque can be preferentially ensured when the traveling load becomes large during wet fields.
Also, by providing step A-31, high speed traveling is possible during traveling on the road and the like.

FIG. 1 shows that in a large combine having a body weight of about 6.5 tons, the traveling load when the vehicle speed is changed by operating the movable swash plate of the variable displacement traveling pump in the traveling side HST is variable in the traveling side HST. It is a graph which shows the result of having measured the capacity | capacitance type travel motor in the state hold | maintained at the small volume state and the large volume state, respectively. FIG. 2 shows the variable load type in the travel side HST when the vehicle speed is changed by operating the movable swash plate of the variable displacement travel pump in the travel side HST in a medium-sized combine having a body weight of about 4 tons. It is a graph which shows the result measured in the state where the travel motor was held in the small volume state and the large volume state, respectively. FIG. 3 is a side view of the combine according to the embodiment of the present invention. 4 is a front view of the combine shown in FIG. FIG. 5 is a transmission schematic diagram of the combine shown in FIGS. 3 and 4. FIG. 6 is a transmission schematic diagram of the traveling transmission in the combine shown in FIGS. FIG. 7 is a hydraulic circuit diagram of the combine shown in FIGS. FIG. 8 is a transmission schematic diagram of the work machine transmission in the combine shown in FIGS. 3 to 5 and 7. FIG. 9 is a flowchart of the selection control mode in the control program stored in the control device in the combine shown in FIGS. 3 to 5 and 7. FIG. 10 is a flowchart of the small volume control mode in the control program. FIG. 11 is a flowchart of the large volume control mode in the control program.

1 Combine 9 Engine 10 Traveling device 30 Harvesting device 40 Threshing device 120 Traveling side HST
120P Traveling pump 120M Traveling motor 310 HST lever (shifting operation member)
320 Actuator for pump 330 Actuator for motor 400 Controllers 129a, 129b HST line 240 Mowing clutch (vehicle speed tuning side speed change mechanism)

Claims (5)

An engine, a traveling side HST that operatively inputs rotational power from the engine, a speed change operation device that operates the traveling side HST, a traveling device that is operatively driven by the traveling side HST, and an operation from the engine And a threshing device that performs a threshing process on the culms harvested by the reaping device, and the traveling side HST is a variable displacement type operatively connected to the engine. A travel pump and a variable displacement travel motor that is fluidly driven by the travel pump, wherein the speed change operation device is a speed change operation member that can be manually operated, and a pump that changes the volume of the travel pump Operating device, a motor operating device that changes the volume of the travel motor, a control device that controls the operation of the pump operating device and the motor operating device A combine with,
The travel motor is configured to be capable of taking a two-stage volume state of a small volume state and a large volume state,
The control device controls the pump so that the output of the travel side HST changes according to the operation position of the speed change operation member in a state where the motor operation device is controlled so that the travel motor is in a small volume state. The output of the traveling side HST changes in accordance with the operation position of the speed change operation member in the small volume control mode for controlling the operating device and the motor operating device controlled so that the traveling motor is in the large volume state. A large volume control mode for controlling the pump actuator so that the output of the traveling side HST does not change when the volume state of the traveling motor is changed, and the volume of the traveling pump is controlled. and a transition control mode for changing the state, only when the reaper clutch combine is and the cutting device substantially straight forward state is the engaged state, the con It is configured to determine that the working conditions in cutting, when it is determined that the working state the combine is harvesting selects the small-volume control mode, if it is determined not in the working state the combine is harvesting Is a combine that features a large volume control mode .   The combine according to claim 1, wherein the control device is configured to disable at least one of a small volume control mode and a large volume control mode based on an artificial signal.   The combine according to claim 1 or 2, wherein the control device is configured to select a large volume control mode when the combine is turning.   When the hydraulic pressure of the HST line on the side of the HST line that is in a high pressure among the pair of HST lines that fluidly connect the traveling pump and the traveling motor in the small volume control mode exceeds a predetermined value, the small volume control mode The combine according to any one of claims 1 to 3, wherein the combine is configured to shift to a large volume control mode.   The control device is in a state in which the combine is in a cutting operation state only when the combine is in a substantially straight forward advance state and a cutting clutch of the cutting device is in an engaged state, and a culm exists in the cutting device. The combine according to any one of claims 1 to 4, wherein the combine is determined to be present.

Images