JP2007029039A - Travel transmission of combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a travel transmission of a combine harvester, which can quickly accelerate the backward travel speed of the combine harvester and can thereby improve the efficiency of works, for example, when a forward reaping travel and a backward non-reaping travel are repeated. <P>SOLUTION: This travel transmission of the combine harvester includes a hydraulic variable speed transmission 3 composed of a variable volume type hydraulic pump 1 and a variable volume type hydraulic motor 2, and a connection means is provided for increasing the oil delivery quantity of the hydraulic pump 1 in response to the increase of a forward or rearward travel speed-changing operation quantity from the neutral region of a speed-changing operation tool to accelerate the output rotation of the hydraulic motor 2 in the normal or adverse rotation direction, and for accelerating the output rotation of the hydraulic motor 2 in relation to the backward operation of the speed-changing operation tool in the reverse rotation direction in a larger acceleration quantity than an acceleration quantity due to the increase in the oil delivery quantity of the hydraulic pump 1. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a traveling transmission for a combine.

  Conventionally, in a combine, the hydraulic stepless transmission is continuously shifted in the forward / reverse direction by forward / backward tilting operation of the shift lever, and moves forward and backward. When the vehicle is switched to the reverse travel state in which the vehicle travels without performing the travel, it has been demanded that the reverse travel be performed quickly to move and improve the work efficiency.

Therefore, for example, as shown in Patent Document 1, in a hydraulic continuously variable transmission that transmits a traveling device, a gear that shifts sequentially from a neutral position to a forward side and a reverse side to shift to a high speed transmission ratio. A technique has been attempted in which the forward shift operation angle of the lever required to change the transmission ratio of the hydraulic continuously variable transmission by a constant ratio is set larger than the reverse shift operation angle.
Japanese Utility Model Publication No. 5-19639

  However, in the configuration described in Patent Document 1 described above, the hydraulic motor side of the hydraulic continuously variable transmission is not provided with a transmission means, and the output rotation of the hydraulic motor is increased by increasing the amount of oil discharged from the hydraulic pump. There is no means to increase speed other than speed.

  Therefore, in order to obtain the output rotation of the hydraulic motor according to the operation amount of the speed change lever, the link ratio of the link mechanism that links from this speed change lever to the swash plate angle adjustment arm that adjusts the discharge oil amount of the hydraulic pump, It must be changed and set between the forward side and the reverse side.

  If such a measure is not taken, when the shift lever is operated backward by a certain amount, the shift lever can be driven backward only at the same speed as when the shift lever is operated forward by the same amount. Improve work efficiency.

In order to solve the above-mentioned problems, the present invention takes the following technical means.
That is, according to the first aspect of the present invention, a hydraulic continuously variable transmission (3) is constituted by a variable displacement hydraulic pump (1) and a variable displacement hydraulic motor (2), and a transmission operation tool (4). Output of the hydraulic motor (2) by adjusting the swash plate angle of the hydraulic pump (1) in accordance with an increase in the forward / reverse speed change operation amount from the neutral range, and increasing the amount of oil discharged from the hydraulic pump (1). The rotation speed is increased in the forward and reverse direction, and the swash plate angle of the hydraulic motor (2) is adjusted stepwise in relation to the reverse operation of the speed change operation tool (4). Characterized in that there is provided linking means (5) capable of increasing the output rotation of 2) in the reverse direction by a speed increase amount larger than the speed increase amount by adjusting the swash plate angle of the hydraulic pump (1). This is a combine travel transmission.

  Thus, when the transmission operating tool 4 is operated from the neutral range to the forward side, the amount of oil discharged from the hydraulic pump 1 increases, and the output rotation of the hydraulic motor 2 that receives this oil discharge increases in the forward rotation direction. The vehicle body equipped with the transmission is accelerated in the forward direction. On the other hand, when the speed changer 4 is operated from the neutral range to the reverse side, the amount of oil discharged from the hydraulic pump 1 increases, and the swash plate angle of the hydraulic motor 2 is adjusted stepwise by the connecting means 5. The output rotation is increased in the reverse direction by a speed increase amount larger than the speed increase amount due to the increase in the discharge oil amount of the hydraulic pump 1, and the combine is speedily increased in the reverse direction.

  According to a second aspect of the present invention, a hydraulic continuously variable transmission (3) is constituted by a variable displacement hydraulic pump (1) and a variable displacement hydraulic motor (2), and a transmission operation tool (4). Output of the hydraulic motor (2) by adjusting the swash plate angle of the hydraulic pump (1) in accordance with an increase in the forward / reverse speed change operation amount from the neutral range, and increasing the amount of oil discharged from the hydraulic pump (1). The rotation of the hydraulic motor (2) is linked to increase the rotation in the forward / reverse direction, and the hydraulic motor (2) is tilted in relation to the ascent of the mowing device (11) to the non-working position and the reverse operation of the speed change operation tool (4). Connecting means capable of adjusting the panel angle and increasing the output rotation of the hydraulic motor (2) in the reverse direction with a speed increase amount larger than the speed increase amount by adjusting the swash plate angle of the hydraulic pump (1). The present invention is a combine traveling transmission apparatus characterized in that (5) is provided.

  Accordingly, when the speed changer 4 is operated from the neutral range to the forward side, the swash plate angle of the hydraulic pump 1 increases, the amount of oil discharged from the hydraulic pump 1 increases, and the output of the hydraulic motor 2 that receives this discharged oil. The rotation speed is increased in the forward direction, and the vehicle body on which the traveling transmission is mounted is increased in the forward direction. On the other hand, when the shift operating tool 4 is operated from the neutral range to the reverse side with the reaping device 11 raised beyond the non-working position, the swash plate angle of the hydraulic pump 1 increases and the amount of oil discharged from the hydraulic pump 1 increases. The swash plate angle of the hydraulic motor 2 is automatically reduced by the connecting means 5 so that the output rotation of the hydraulic motor 2 is greater than the speed increase due to the increase in the amount of oil discharged from the hydraulic pump 1. The speed is increased in the reverse direction by the amount, and the combine is speeded up in the backward direction.

  According to the first aspect of the invention, the reverse rotation direction of the output rotation of the hydraulic motor 2 is increased by a speed increase amount greater than the speed increase amount due to the increase in the discharge oil amount of the hydraulic pump 1 by the reverse operation of the speed change operation tool 4. Thus, the speed of the combine can be increased rapidly in the reverse direction. For example, the work efficiency can be improved in a work mode in which the cutting operation traveling by the forward movement and the non-cutting operation traveling by the backward movement are repeated.

  According to the invention described in claim 2, by automatically adjusting the swash plate angle of the hydraulic motor 2 linked to the lifting of the reaping device 11 to the non-working position and the operation of the shift operation tool 4 to the reverse side, The output rotation of the hydraulic motor 2 can be increased in the reverse direction by a speed increase amount greater than the speed increase amount due to the increase in the discharge oil amount of the hydraulic pump 1, and the combine can be speedily increased in the reverse direction. The work efficiency can be improved by agile turning in the field where the work traveling by the forward movement and the non-working traveling by the backward movement are repeated.

An embodiment of a traveling transmission apparatus according to the present invention will be described by exemplifying a self-detaching combine.
As shown in FIGS. 1 and 2, this combine is equipped with a steering unit 8, a threshing device 9, and a grain storage device 10 on the upper side of the left and right traveling devices 7, 7 wound around the crawler 6, A reaping device 11 is provided on the front side of the threshing device 9 so as to be adjustable up and down by an expansion and contraction operation of a hydraulic cylinder 12 for reaping and lifting.

  The harvesting device 11 supports the rear upper end portion of the post-cutting frame 13 on the upper portion of the mowing suspension stand 13 erected on the front portion of the machine body so as to be rotatable up and down. In addition, a pre-cutting processing device including a weed cocoon 14, a pulling device 15, a scraping device 16, a stock transporting device 17, and a cutting blade device 18 is provided.

  The threshing device 9 includes a handling cylinder 19 and a processing cylinder 20 that are internally pivoted in an upper handling chamber, a dust exhaust fan 21 that is pivoted on the rear side of the handling chamber, and a swing sorting that is built in a lower sorting chamber. It comprises a shelf 22, a red pepper 23, a first spiral 24, a second spiral 25, a first cereal spiral 26 linked to the first spiral 24, and a second cereal spiral 27 linked to the second spiral 25. .

  The grain storage device 10 includes a bottom conveying spiral 28 pivoted on the bottom of the tank body, a cerealing spiral 29 for cerealing grains on the rear side of the tank body in conjunction with the bottom conveying spiral 28, and the lifting It comprises a discharge spiral 30 that is interlocked with the upper end of the grain spiral 29 so as to be pivotable up and down.

  The left and right traveling devices 7 and 7 wind left and right crawlers 6 and 6 around left and right drive wheels 32 and 32 driven from a mission case 31 and a plurality of rolling wheels 33 and 33 arranged behind the left and right drive wheels 32 and 32. Configure.

  As shown in FIG. 2, in the transmission case 31, an auxiliary transmission gear 35 is provided so as to be slidable only in the axial direction with respect to the upper input shaft 34. By selectively meshing with a group of transmission gears 37 fixed to the intermediate shaft 36 disposed on the side, a three-stage auxiliary transmission mechanism 38 of high speed (running), medium speed (standard), and low speed (slope) is provided. Constitute. The auxiliary transmission gear 35 is slid by a forward / backward tilting operation of an auxiliary transmission lever 39 provided in the control unit 8. Further, the output gear 40 fixed to the intermediate shaft 36 is meshed with a center gear 42 provided at the center of the lower side clutch shaft 41, and left and right side clutch gears 43, 43 are provided on the left and right sides of the center gear 42, respectively. The side brakes 44, 44 are disposed outside the left and right side clutch gears 43, 43 so as to be slidably engaged and disengaged. Further, the wheel gears 46, 46 fixed to the inner ends of the left and right axles 45, 45 provided on the lower side are meshed with the left and right side clutch gears 43, 43. The drive wheels 32, 32 are fixed to the outer ends of the left and right axles 45, 45.

  Further, a branch transmission case 47 is attached to the upper outer side of the transmission case 31, and a gear 48 fixed to the protruding end side of the input shaft 34 and an intermediate feed chain drive shaft 49 in the branch transmission case 47. A fixed intermediate gear 50 and a gear 52 provided on a spline-connected shaft of an output shaft 51 of a hydrostatic continuously variable transmission (hydraulic continuously variable transmission) 3 are provided.

  A cutting output pulley 54 is attached to the protruding end of the input shaft 34 at the top of the transmission case 31 via a one-way clutch 53, while a cutting input pulley arranged at the rear upper end of the post-cutting frame 13 in the cutting device 11. A tension type cutting clutch is formed by winding a cutting transmission belt 56 between the belt and the belt 55. Further, a feed chain output pulley 57 is attached to the protruding end of the feed chain drive shaft 49, and a transmission belt 61 is wound between the input pulley 60 attached to the inner end of the feed chain transmission shaft 58 via a one-way clutch 59. The feed chain clutch 63 is configured by providing a tension roller 62 for applying tension to the transmission belt 61.

  The hydrostatic continuously variable transmission 3 is attached to the inside of the upper part of the branch transmission case 47. As shown in FIG. 3, the hydrostatic continuously variable transmission 3 receives a plunger-type hydraulic pump 1 that is driven by an input shaft 64 and discharges hydraulic oil, and receives and outputs oil discharged from the hydraulic pump 1. A closed circuit is formed by connecting the plunger-type hydraulic motor 2 that drives and rotates the shaft 51 with a high pressure oil passage 65 on the forward side (forward rotation side) and a low pressure oil passage 66 on the reverse side (reverse rotation side). This is the configuration. Further, the high pressure oil passage 65 and the low pressure oil passage 66 are short-circuited by an oil passage in which a check valve 67 and a throttle valve 68 are connected in series, and from each of the high pressure oil passage 65 and the low pressure oil passage 66. A relief valve 71 is connected to a lower charge oil passage 72 through reverse check valves 69 and 70. The charge oil passage 72 is for replenishing the aforementioned closed circuit leak oil from the oil tank 73. The hydraulic pump 1 and the hydraulic motor 2 are configured such that the displacement of the plunger and the amount of discharged oil can be changed by adjusting the angle of the internal swash plate, and the hydraulic pressure can be changed. The swash plate angle of the pump 1 is mechanically linked so as to be changed via the link mechanism by the forward and backward tilting of the main transmission lever 4 provided in the control unit 8. The swash plate angle of the hydraulic motor 2 is configured to be operated via the interlocking rod 75 by the operation of the electric motor type HST motor swash plate switching actuator 74.

  Further, a cooling fan 76 for the hydrostatic continuously variable transmission 3 is attached to the projecting end of the input shaft 64 of the hydrostatic continuously variable transmission 3, An input pulley 80 to which driving force is input from an output shaft 77 of the engine E via an output pulley 78 and a transmission belt 79 is attached. Further, from the threshing output pulley 81 attached to the output shaft 77 through the belt transmission mechanism 82, the handling cylinder 19, the processing cylinder 20, the dust exhaust fan 21, the swing sorting shelf 22, the red pepper 23, the first spiral 24, The second spiral 25 is configured to be driven in conjunction. Further, the bottom conveying spiral 28 is driven in conjunction with a discharge output pulley 83 attached to the output shaft 77 via a belt transmission mechanism 82 and the like.

  Further, the auxiliary transmission shifter 85 that slides the auxiliary transmission gear 35 from the auxiliary transmission lever 39 standing on the side operation pad 85 of the control unit 8 via the auxiliary transmission rod 84 is configured to rotate. In addition, the swash plate angle of the hydraulic pump 1 of the hydrostatic continuously variable transmission 3 is operated from the main transmission lever 4 through the main transmission rod 86. Further, a sub-shift running shift sensor 87 for detecting the operation position of the sub-transmission lever 39 is provided at the base of the sub-transmission lever 39, and the main transmission lever 4 is tilted in the backward direction at the base of the main transmission lever 4. A reverse detection sensor 88 for detecting the movement and a cutting clutch engaging sensor 90 for detecting that the cutting clutch lever 89 has been operated to the input side are provided at the base of the cutting clutch lever 89. Further, a cutting height detection sensor 91 for detecting the height of the cutting device 11 with respect to the airframe from the amount of vertical rotation of the post-cutting frame 13 is provided.

  As shown in FIG. 4, on the input side of the controller 92, the reverse detection sensor 88, the reverse speed setting dial 93 provided on the front operation panel of the control unit 8, the auxiliary shift travel shift sensor 87, the cutting While the clutch engagement sensor 90 and the cutting height detection sensor 91 are connected, the HST motor swash plate switching actuator 74 is connected to the output side of the controller 92. This is the connecting means 5.

  With the above configuration, when the main speed change lever 4 is operated forward, the swash plate angle of the hydraulic pump 1 of the hydrostatic continuously variable transmission 3 is increased via the main speed change rod 86 and the amount of discharged oil is increased. As the amount of oil supplied to the hydraulic motor 2 increases, the output shaft 51 of the hydraulic motor 2 increases in the forward direction, and the combine increases in the forward direction.

  On the other hand, when the main speed change lever 4 is operated to the reverse side, this operation state is detected by the reverse detection sensor 88, and an output from the controller 92 to the HST motor swash plate switching actuator 74 is made. As a result, the amount of oil required for one rotation decreases, and as a result, the output shaft 51 of the hydraulic motor 2 increases in the reverse direction, and the combine increases in the reverse direction.

  Accordingly, the swash plate angle of the hydraulic motor 2 is reduced during reverse travel, so that the output shaft 51 of the hydraulic motor 2 can be obtained even when the operation angle of the main shift lever 4 toward the forward side and the operation angle toward the reverse side are the same. The output rotational speed of the rear side is larger than the forward side. Thus, when the operation angle of the main shift lever 4 toward the forward side and the operation angle toward the reverse side are the same, the reverse travel speed becomes larger than the forward travel speed.

This state is shown in FIG.
FIG. 5 is a graph in which the horizontal axis is the tilting operation position of the main shift lever 4 and the vertical axis is the vehicle speed. On the forward travel side, the sub-shift (running), the sub-shift (standard), and the sub-shift (slope) ), The vehicle speed increases linearly at different fixed speed ratios. On the other hand, on the reverse travel side, the vehicle speed is constant as shown by the solid line, regardless of whether the sub-shift is the sub-shift (travel), the sub-shift (standard), or the sub-shift (slope). The ratio increases linearly, and this increase ratio is equivalent to the sub-shift (travel) on the forward travel side. The vehicle speed when the main transmission lever 4 is in the forward highest speed position and the vehicle speed when the main transmission lever 4 is in the reverse highest speed position are set to be substantially the same. In addition, by making the maximum reverse speed at the sub-shift (travel) and the maximum reverse speed at the sub-shift (standard) substantially the same, the driver's speed sensation becomes substantially constant regardless of the sub-shift position. Increased safety.

  Further, by operating the reverse speed setting dial 93, it is possible to arbitrarily change the speed increase ratio of the vehicle speed on the reverse travel side. That is, the gradient of the solid line in FIG. 5 can be arbitrarily changed. Thereby, the speed increase rate of the reverse speed can be adjusted according to the skill level of the operator, and the safety and work efficiency can be improved. Note that the change range of the gradient of the solid line may be regulated to a predetermined width.

  The reverse speed setting dial 93 may be disposed on the front operation panel of the control unit 8 between a steering operation lever standing at a position closer to the outside and a central monitor. In addition, characters “high”, “medium”, and “low” are displayed along the periphery of the dial.

  When the auxiliary transmission lever 39 is operated to the “travel” position, this operation position is detected by the auxiliary transmission movement shift sensor 87, and the main transmission lever 4 is operated to the reverse side as described above. Further, the output from the controller 92 to the HST motor swash plate switching actuator 74 is restricted, and the swash plate angle of the hydraulic motor 2 is controlled so as not to become small or only small. As a result, the speed increase ratio at the time of reverse travel is suppressed to avoid the danger of high speed reverse travel, and the combine travels while suppressing the decrease in the output torque of the hydraulic motor 2 due to the swash plate angle of the hydraulic motor 2 becoming smaller. It is possible to prevent the situation from being impossible.

  Further, as shown in FIG. 6, when the vehicle is moving backward, the controller 92 controls the HST motor swash plate so that the speed increase ratio in the case of the sub-shift (slope) matches the speed increase ratio in the case of the sub-shift (standard). An output to the switching actuator 74 may be set. As a result, the reverse travel speed due to the sub-shift (slipping) becomes the same as the reverse travel speed due to the sub-shift (standard), and the work efficiency can be improved. Further, the reverse travel speed may be switched to a plurality of stages in the sub-shift (standard) or sub-shift (slope) state. By arbitrarily switching the reverse speed to multiple stages in this way, the work can be performed safely and efficiently according to the level of proficiency of the pilot. If the reverse travel speed is switched to a two-stage switch, it is easy for the driver to understand. , The operator can operate without confusion.

  If the reverse speed setting dial 93 is provided on the inner side surface portion of the grip portion of the main transmission lever 4, the inner surface portion of the grip portion of the auxiliary transmission lever 39, or the upper surface portion of the steering lever, in addition to the aforementioned front operation panel, The operability can be further improved.

  Further, as shown in FIG. 8, if the automatic adjustment of the swash plate angle of the hydraulic motor 2 is performed in four stages, N, n-1, 2, and 1, the gear ratio at each shift stage is fixed. The driver can adjust to the sense of speed. Further, it can be constructed at a lower cost than the configuration in which the swash plate angle of the hydraulic motor is adjusted steplessly.

  Further, as shown in the graph showing the relationship between the operation angle of the main transmission lever and the vehicle speed shown in FIG. 9, the throttle valve 68 (neutral orifice) is installed in the reverse high pressure circuit in the hydraulic circuit in the hydrostatic continuously variable transmission 3. ), The vehicle speed at the time of reverse travel is lower than the vehicle speed at the time of forward travel. However, as shown in the graph showing the relationship between the operation angle of the main shift lever and the vehicle speed shown in FIG. By controlling the panel angle, it is possible to correct this decrease in vehicle speed during reverse travel.

  Also, when the cutting clutch lever sensor 90 is turned on by turning on the cutting clutch lever 89, or when the main transmission lever 4 is reversely operated with the cutting clutch lever 89 turned on by turning on the cutting clutch lever 89. In addition, an output may be made from the controller 92 to the HST motor swash plate switching actuator 74 so that the swash plate angle of the hydraulic motor 2 is switched to the high speed side. As a result, as shown in FIG. 11, when the cutting clutch is disengaged, the swash plate angle of the hydraulic motor 2 is not switched to the high speed side even if the main transmission lever 4 is operated backward, and the reverse speed is suppressed. , Safe.

  Further, when the cutting device 11 is raised to the set non-cutting work height, or when the main shift lever 4 is operated backward in a state where the cutting device 11 is raised to the set non-cutting work height, the controller 92 performs HST. An output may be made to the motor swash plate switching actuator 74 so that the swash plate angle of the hydraulic motor 2 is switched to the high speed side. Thus, as shown in FIG. 11, when the reaping device 11 is at an appropriate height for reaping work, the swash plate angle of the hydraulic motor 2 is not switched to the high speed side even if the main transmission lever 4 is operated backward. Since the reverse speed is suppressed, it is safe. Further, since the reaping device 11 is raised during reverse travel, the reaping device 11 is unlikely to interfere with the ground, and damage to the reaping device 11 can be prevented.

As shown in FIG. 11, the reverse speed is increased at a constant ratio with respect to the forward speed.
As shown in FIG. 12, a reverse speed increasing arm 94 is provided on the rear side of the main speed change lever 4 so as to be pivotable forward and backward, and a stopper 95 is provided. The rear arm end of the reverse speed increasing arm 94 and the hydraulic motor are provided. Two swash plate angle adjusting arms 96 may be connected by an interlocking rod 97. Thus, when the main speed change lever 4 is operated to a position in the reverse operation range, the main speed change lever 4 comes into contact with the reverse speed increase arm 94, and thereafter, the reverse speed increase arm is operated by the reverse speed increase operation of the main speed change lever 4. 94 is rotated rearward, and the swash plate angle adjusting arm 96 of the hydraulic motor 2 is rotated stepwise via the interlocking rod 97, so that the reverse speed exceeds the set speed A as shown in FIG. After that, the swash plate angle of the hydraulic motor 2 is changed to the speed increasing side. Thus, the reverse speed can be adjusted according to the size and conditions of the field.

  Further, as shown in FIGS. 14 and 15, the swash plate angle adjusting arm 96 of the hydraulic motor 2 may be configured to rotate and adjust by the left and right operation of the main transmission lever 4. That is, a swash plate angle interlocking adjustment arm 98 having a long hole along the range of forward and backward rotation of the main transmission lever 4 is provided so as to be tiltable in the left-right direction, and the main transmission lever 4 is moved upward from the long hole of the swash plate angle interlocking adjustment arm 98. The arm protruding from the swash plate angle interlocking adjustment arm 98 to the left and right sides and the swash plate angle adjusting arm 96 of the hydraulic motor 2 are connected by the interlocking rod 97. Thus, when the main transmission lever 4 is tilted to the reverse operation path side along the crank-shaped operation path of the main transmission lever 4 operation guide guide, the hydraulic motor 2 is moved from the swash plate angle interlocking adjustment arm 98 via the interlocking rod 97. The swash plate angle adjusting arm 96 is rotated, and the swash plate angle of the hydraulic motor 2 is changed to the speed increasing side.

  In addition, as shown in FIGS. 16, 17, and 18, in the fuselage body, the upper left portion of the reaping device 11, the right front portion of the control portion 8, the upper left rear portion of the threshing device 9, and the grain storage device 10. Blinkers 99a, 99b, 99c, 99d are provided on the rear upper part. Then, as shown in FIG. 19, the fuel remaining amount sensor 101 of the fuel tank is connected to the controller 100 on the input side, and the blinkers 99a, 99b, 99c, and 99d are connected to the output side. Accordingly, based on the detection result of the fuel remaining amount sensor 101, when the fuel remaining amount sensor 101 detects a fuel remaining amount equal to or less than a set amount, the winkers 99a, 99b, 99c, and 99d are turned on by the output from the controller 100. Configure to blink. Accordingly, it is possible to notify the surrounding third parties that the fuel has run out and to start preparation for refueling, so that it is possible to improve the work efficiency of the combine.

  Further, three cocoon sensors 102a, 102b, and 102c are attached to the inside of the grain storage device 10 at different heights, and as shown in FIG. While the sensors 102a, 102b and 102c are connected, the turn signals 99a, 99b, 99c and 99d are connected to the output side thereof. Therefore, as shown in FIG. 21, the blinking state of the blinkers 99a, 99b, 99c, and 99d is changed every time the three culm sensors 102a, 102b, and 102c having different heights detect the accumulated grains. Thus, the third party is informed of the storage state of the grain, the time until the grain storage device 10 becomes full is estimated, and the preparation of the koji discharging work from the grain storage device 10 is efficiently performed. Can be done well. The waveforms shown in FIG. 21 are output signals to the winkers 99a, 99b, 99c, and 99d, with the horizontal axis representing time and the vertical axis representing output ON.

  Further, as shown in FIG. 22, in addition to the above configuration, the fuel remaining amount sensor 101 is connected to the input side of the controller 103. Then, as shown in FIG. 23, when the fuel remaining amount sensor 101 detects a fuel remaining amount equal to or less than the set amount, the blinking intervals at which the blinkers 99a, 99b, 99c, and 99d blink by the output from the controller 100, and three The blinking intervals at which the blinkers 99a, 99b, 99c, and 99d blink when the accumulated grains are detected by the straw sensors 102a, 102b, and 102c are set differently. Thereby, the change of a some work state, ie, the fuel remaining amount and the grain storage amount, can be distinguished and notified.

  Moreover, as shown in FIG. 24, it is good to comprise so that the work light 105 which consists of LED may be attached to the inside lower side of the upper cover 104 of the raising apparatus 15 in the reaping apparatus 11, and the front of the weed ridge 14 may be illuminated. As shown in FIG. 25, the work lamp 105 has a configuration in which a plurality of LEDs 107 are arranged in a horizontally long case 106 having a predetermined width T, and a lens 108 is arranged on the front side of the LEDs 107. Further, the predetermined width T of the case 106 of the work lamp 105 is set according to the width of the plurality of pulling devices 15 arranged. Further, the predetermined width T of the case 106 of the work lamp 105 may be set and arranged in accordance with the raising passage width of the plurality of raising devices 15 arranged. Thereby, even if it becomes dark, it can work comfortably.

In addition, as shown in FIG. 27, the meter panel unit 108 may be arranged so as to float a predetermined distance from the front panel in the control unit 8. The meter panel unit 108 includes a liquid crystal display surface 109 for displaying a grain storage amount and abnormality information, a lower tachometer 110, a liquid crystal display changeover switch 111 disposed above and below the left side, and a right side. A work light switch 112 and a horn switch 113 for turning on / off the work lights 105 arranged above and below are provided.
Further, a lever 114 for operating blinking operation of the blinkers 99a, 99b, 99c, 99d and lighting of the headlamp is provided so as to protrude from the right side surface of the meter panel unit 108. With such an arrangement, the liquid crystal display surface 109 is easy to see, the arrangement of switches is easy to understand, and these switches can be operated easily. In addition, since the liquid crystal display surface 109 and the tachometer 110 are arranged vertically, it is easier to view these display information at the same time as compared with a configuration in which they are arranged left and right.

  FIG. 28 shows a configuration in which the headlamp switch 115 is arranged above the work lamp switch 112 in the meter panel unit 108 in FIG.

It is a side view for description of a combine. It is explanatory drawing of the transmission mechanism of a combine. 1 is a hydraulic circuit diagram of a hydrostatic continuously variable transmission. It is a control block diagram of a connection means. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a graph which shows the relationship between the operation angle of the main transmission lever in another Example, and a vehicle speed. It is a graph which shows the relationship between the operation angle of the main transmission lever in a prior art, and a vehicle speed. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a side view for description of a combine. It is a graph which shows the relationship between the operation angle of a main speed-change lever, and a vehicle speed. It is a side view for description of a combine. It is explanatory drawing of the principal part in FIG. It is a left view of a combine. It is a right view of a combine. It is a top view of a combine. It is a block circuit diagram. It is a block circuit diagram. It is explanatory drawing of the output waveform to a blinker. It is a block circuit diagram. It is explanatory drawing of the output waveform to a blinker. It is a side view for description of a raising apparatus part. FIG. FIG. It is explanatory drawing of a meter panel unit. It is explanatory drawing of the meter panel unit of another structure.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic pump 2 Hydraulic motor 3 Hydraulic continuously variable transmission (hydrostatic continuously variable transmission)
4 Shifting operation tool (main shifting lever)
5 Linking means 11 Mowing device

Claims (2)

  The variable displacement hydraulic pump (1) and the variable displacement hydraulic motor (2) constitute a hydraulic continuously variable transmission (3), and the forward / reverse shift operation amount from the neutral range of the transmission operation tool (4). The swash plate angle of the hydraulic pump (1) is adjusted in accordance with the increase of the hydraulic pump to increase the amount of oil discharged from the hydraulic pump (1) to increase the output rotation of the hydraulic motor (2) in the forward and reverse directions. And the swash plate angle of the hydraulic motor (2) is adjusted stepwise in relation to the reverse operation of the speed change operation tool (4), and the output rotation of the hydraulic motor (2) is controlled by the hydraulic pump ( A traveling traveling transmission for a combine, characterized in that there is provided linking means (5) capable of increasing the speed in the reverse direction by a speed increasing amount larger than the speed increasing amount by adjusting the swash plate angle of 1). The variable displacement hydraulic pump (1) and the variable displacement hydraulic motor (2) constitute a hydraulic continuously variable transmission (3), and the forward / reverse shift operation amount from the neutral range of the transmission operation tool (4). The swash plate angle of the hydraulic pump (1) is adjusted in accordance with the increase of the hydraulic pump to increase the amount of oil discharged from the hydraulic pump (1) to increase the output rotation of the hydraulic motor (2) in the forward and reverse directions. And adjusting the swash plate angle of the hydraulic motor (2) in relation to the raising of the cutting device (11) to the non-working position and the reverse operation of the speed change operation tool (4). Characterized in that there is provided linking means (5) capable of increasing the output rotation of 2) in the reverse direction by a speed increase amount larger than the speed increase amount by adjusting the swash plate angle of the hydraulic pump (1). Combined travel transmission.

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