combine

Abstract

To provide a combine capable of decelerating a travelling speed of a travelling device when output rotation of an engine is decelerated so that damage to the engine and a stepless speed variator is suppressed.SOLUTION: A stepless speed variator (30) for performing switching of acceleration and deceleration of output rotation of an engine (E) and a rotation direction is provided on the downstream side of a transmission route of the engine (E). A travelling device (2) is provided on the downstream side of the transmission route of the stepless speed variator (30). A speed change lever (16) for accelerating / decelerating output rotation of the engine (E) and output rotation of the stepless speed variator (30) is provided in a steering part (5). When the output rotation of the engine (E) is less than rating rotation of the engine (E) and is decelerated to preset first set output rotation or more, a controller (50) of the steering part (5) accelerates / decelerates the output rotation of the engine (E), drives a motor (42) for advancing and a motor (43) for backing of the stepless speed variator (30), and decelerates a travelling speed of the travelling device (2) to a preset first set travelling speed without being based on an operation posture of the speed change lever (16).SELECTED DRAWING: Figure 8

Description

[Technical Field]

[0001] The present invention relates to a combine harvester equipped with a continuously variable transmission that increases or decreases the traveling speed of a traveling device. [Background technology]

[0002] In conventional combine harvesters, a technique is known in which a speed change lever provided on the operating section is operated to increase or decrease the output rotation of the engine, and the output rotation of a continuously variable transmission provided on the transmission path between the engine and the traveling device, thereby increasing or decreasing the traveling speed of the traveling device (see Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Publication No. 2022-176677 Summary of the Invention [Problem to be solved by the invention]

[0004] However, with the technology of Patent Document 1, if the engine output rotation continues to slow down due to a large load on the engine, there is a risk that the engine may be damaged due to overheating or that the continuously variable transmission may be damaged due to a decrease in circulating hydraulic oil.

[0005] Therefore, the object of the present invention is to provide a combine that can reduce the running speed of the traveling device when the engine output rotation speed is reduced, thereby preventing damage to the engine and continuously variable transmission. [Means for solving the problem]

[0006] The present invention, which has solved the above problems, is as follows. That is, the invention described in claim 1 is a combine harvester in which a traveling device (2) is provided below a machine frame (1) on which an engine (E) is mounted, a reaping device (3) is provided in front of the machine frame (1), a threshing device (4) is provided behind the reaping device (3) on the left side, and a control unit (5) is provided behind the reaping device (3) on the right side. A continuously variable transmission (30) for increasing / decreasing the output rotation of the engine (E) and switching the rotation direction is provided downstream of the transmission path of the engine (E), a traveling device (2) is provided downstream of the transmission path of the continuously variable transmission (30), a speed change lever (16) for increasing / decreasing the output rotation of the engine (E) and the output rotation of the continuously variable transmission (30) is provided in the operating section (5), and a controller (50) of the operating section (5) The load rate of the engine (E) has been 100% or more for a preset time, and When the output rotation of the engine (E) is reduced to a preset first set output rotation or more below the rated rotation of the engine (E), the output rotation of the engine (E) is increased or decreased and the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) are driven, regardless of the operating position of the speed change lever (16), thereby reducing the traveling speed of the traveling device (2) to a preset first set traveling speed. The set time is set to a time for leveling out fluctuations in the load on the engine (E) caused by fluctuations in the amount of straw transported to the threshing device (4). This is a combine harvester characterized by the above.

[0007] The invention described in claim 2 is a combine described in claim 1, which stops increasing or decreasing the output rotation of the engine (E) when the output rotation of the engine (E) is decelerated to a first set output rotation or more below the rated rotation of the engine (E).

[0008] The invention described in claim 3 is 3. The combine harvester according to claim 1, wherein the set time is set to 3 seconds. is.

[0009]

[0010] Claim 4The invention described is a combine harvester according to claim 1, which, when the output rotation of the engine (E) is slowed down below a first set output rotation to a preset second set output rotation or more, increases or decreases the output rotation of the engine (E) and drives the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) to slow down the running speed of the traveling device (2) to a preset second set running speed that is slower than the first set running speed.

[0011] Claim 5 The invention described in the claims stops the increase / decrease of the output rotation of the engine (E) when the output rotation of the engine (E) is reduced to a second set output rotation or more below a first set output rotation. 4 The combine harvester described above.

[0012] Claim 6 The invention described in the claims stops the increase / decrease of the output rotation of the engine (E) when the output rotation of the engine (E) is reduced to less than a second set output rotation. 4 The combine harvester described above. [Effects of the Invention]

[0013] According to the invention of claim 1, a continuously variable transmission (30) that increases or decreases the output rotation of the engine (E) and switches the rotation direction is provided downstream of the transmission path of the engine (E), a traveling device (2) is provided downstream of the transmission path of the continuously variable transmission (30), a speed change lever (16) that increases or decreases the output rotation of the engine (E) and the output rotation of the continuously variable transmission (30) is provided in the operating section (5), and a controller (50) of the operating section (5) The engine (E) load rate is 100% or more for a preset time, and When the output rotation of the engine (E) is reduced to a preset first set output rotation or more below the rated rotation of the engine (E), the output rotation of the engine (E) is increased or decreased and the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) are driven regardless of the operating position of the speed change lever (16), thereby reducing the traveling speed of the traveling device (2) to a preset first set traveling speed. The set time is set to a time for leveling out the fluctuations in the load on the engine (E) caused by the fluctuations in the amount of straw transported to the threshing device (4).Therefore, when the output rotation of the engine (E) falls below the rated output rotation, the traveling speed of the traveling device (2) is reduced to the first set traveling speed, thereby reducing the load on the engine (E) and the continuously variable transmission (30), and thus it is possible to suppress damage to the engine (E) and the continuously variable transmission (30). Furthermore, the traveling speed of the traveling device (2) can be reduced to the first set traveling speed, thereby suppressing pulsation occurring in the traveling speed.

[0014] According to the invention of claim 2, in addition to the effect of the invention of claim 1, when the output rotation of the engine (E) is decelerated to a first set output rotation or more below the rated rotation of the engine (E), the increase / decrease of the output rotation of the engine (E) is stopped, so that the load on the engine (E) is quickly reduced and damage to the engine (E) can be further suppressed.

[0015] According to the invention of claim 3, in addition to the effects of the invention of claim 1 or 2, The set time was set to 3 seconds. So, This makes it possible to more even out fluctuations in the load on the engine (E).

[0016]

[0017] Claim 4 According to the described invention, in addition to the effect of the invention of claim 1, when the output rotation of the engine (E) is reduced below the first set output rotation and to a preset second set output rotation or more, the output rotation of the engine (E) is increased or decreased and the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) are driven to reduce the traveling speed of the traveling device (2) to a preset second set traveling speed that is slower than the first set traveling speed. Therefore, when the output rotation of the engine (E) becomes less than the first set output rotation, the traveling speed of the traveling device (2) is reduced to the second set traveling speed, thereby further reducing the load applied to the engine (E) and the continuously variable transmission (30) and further suppressing damage to the engine (E) and the continuously variable transmission (30).

[0018] Claim 5 According to the invention described, claims 4In addition to the effects of the invention described above, when the output rotation of the engine (E) is slowed down to a second set output rotation or more below the first set output rotation, the increase / decrease of the output rotation of the engine (E) is stopped, thereby quickly reducing the load on the engine (E) and further suppressing damage to the engine (E).

[0019] Claim 5 According to the invention described, claims 4 In addition to the effects of the invention described above, when the output rotation of the engine (E) is decelerated to less than the second set output rotation, the increase / decrease of the output rotation of the engine (E) is stopped. Therefore, when the output rotation of the engine (E) is less than the second set output rotation, the load on the engine (E) is quickly reduced, thereby further suppressing damage to the engine (E). [Brief explanation of the drawings]

[0020] [Figure 1] FIG. [Figure 2] FIG. [Figure 3] FIG. [Figure 4] 1 is a transmission diagram of the engine output rotation. [Figure 5] FIG. [Figure 6] FIG. 2 is an explanatory diagram of a continuously variable transmission. [Figure 7] This is a connection diagram between the main controller and the engine controller. [Figure 8] This is a method for controlling the engine output rotation. [Figure 9] This is a theoretical control map for the engine. [Figure 10] This is an actual control map of the engine. [Figure 11] FIG. 2 is a perspective view of a support device that supports the reaping device. [Figure 12] FIG. 10 is a perspective view of the left support device of the support device moved to a storage position. [Figure 13] FIG. 10 is a perspective view of the left support device of the support device moved to an open position. [Figure 14] FIG. 10 is a front view of the left support device of the support device with a cover attached to the front part thereof. [Figure 15] FIG. 10 is a left side view of the support device with a cover attached to the front of the left support device. [Figure 16] FIG. 10 is a left side view of the support device with the hook of the right support device engaged with the pin. [Figure 17] FIG. 10 is a left side view of the right support device of the support device with the hook and pin disengaged. DETAILED DESCRIPTION OF THE INVENTION

[0021] As shown in Figures 1 to 3, a traveling device 2 consisting of a pair of left and right crawlers that travels on the soil surface is provided below the body frame 1 of the combine harvester, and a reaping device 3 that harvests stalks in the field is provided in front of the body frame 1. In addition, a threshing device 4 that threshes and sorts the stalks harvested by the reaping device 3 is provided on the rear left side of the reaping device 3, and a control unit 5 on which an operator rides is provided on the rear right side of the reaping device 3.

[0022] An engine room 6 in which an engine E is mounted is provided below the control unit 5, and a grain tank 7 for storing grains that have been threshed and sorted by the threshing device 4 is provided behind the control unit 5. The grains stored in the grain tank 7 are discharged to the outside by a discharge auger (not shown) connected to the grain tank 7.

[0023] A front panel 10 is provided in front of the cockpit of the control section 5, and a side panel 15 is provided to the left of the cockpit.

[0024] A touch panel monitor 11 that displays the traveling speed of the traveling device 2 and the output rotation of the engine E is provided on the left side of the front panel 10, and an operation lever 12 that controls the rotation of the traveling device 2 and the elevation of the reaping device 3 is provided on the right side. The tilt position of the operation lever 12 is measured by an angle sensor such as a potentiometer attached to the bottom of the operation lever 12.

[0025] A main speed change lever (referred to as "speed change lever" in the claims) 16 is provided at the front of the side panel 15 to operate a hydraulic continuously variable transmission 30 that increases or decreases the output rotation of the engine E and switches the direction of rotation, and a sub-speed change lever 17 is provided behind the main speed change lever 16 to operate a transmission 31 that increases or decreases the output rotation of the continuously variable transmission 30.

[0026] In addition, to the right of the main speed change lever 16 is provided an accelerator lever 18 which increases or decreases the output rotation of the engine E via the engine controller 60 without going through the machine controller (the "controller" in the claims) 50, and behind the sub-speed change lever 17 is provided a reaping / threshing lever 19 which operates the connection and disconnection of the reaping clutch 32 and the threshing clutch 33.

[0027] As shown in Fig. 4, the output rotation of the engine E is transmitted to the continuously variable transmission 30 provided on the transmission path A. The output rotation of the engine E transmitted to the input shaft of the continuously variable transmission 30 is increased or decreased in speed and its rotation direction is switched within the continuously variable transmission 30, and then output to the output shaft of the continuously variable transmission 30.

[0028] The output rotation of the continuously variable transmission 30 is transmitted to the transmission 31 and the reaping device 3. The output rotation of the continuously variable transmission 30 transmitted to the input shaft of the transmission 31 is accelerated or decelerated by multiple gears within the transmission 31, and then output to the output shaft of the transmission 31, and the output rotation of the transmission 31 is transmitted to the traveling device 2. In addition, a reaping clutch 32 is provided between the output shaft of the continuously variable transmission 30 and the input shaft of the reaping device 3.

[0029] The output rotation of the engine E is transmitted to the threshing device 4 provided on the transmission path B. In addition, a threshing clutch 33 is provided between the output shaft of the engine E and the input shaft of the threshing device 4.

[0030] As shown in Figure 5, when the main speed change lever 16 is operated to the neutral position, the output rotation of the continuously variable transmission 30 becomes zero. When the main speed change lever 16 is operated from the neutral position to the forward tilt position, the rotation direction of the output rotation of the continuously variable transmission 30 becomes forward, the same as the rotation direction of the output rotation of the engine E. If the tilt angle of the forward tilt position is increased, the output rotation of the engine E and the output rotation of the continuously variable transmission 30 will increase, and if the tilt angle of the forward tilt position is decreased, the output rotation of the engine E and the output rotation of the continuously variable transmission 30 will decrease. The increase or decrease in the output rotation of the engine E is performed by the machine controller 50 and the engine controller 60 via the wireless circuit 53.

[0031] Furthermore, when the main speed change lever 16 is operated from the neutral position to the rear tilt position, the rotation direction of the output rotation of the continuously variable transmission 30 becomes opposite to the rotation direction of the output rotation of the engine E, and when the tilt angle of the rear tilt position is increased, the output rotation of the engine E and the output rotation of the continuously variable transmission 30 increase in speed, and when the tilt angle of the rear tilt position is decreased, the output rotation of the engine E and the output rotation of the continuously variable transmission 30 decrease in speed.

[0032] When the sub-speed change lever 17 is operated to the neutral position, the output rotation of the transmission 31 is not increased or decreased. When the sub-speed change lever 17 is operated from the neutral position to the forward tilt position, the output rotation of the transmission 31 is increased, and when the sub-speed change lever 17 is operated from the neutral position to the rearward tilt position, the output rotation of the transmission 31 is decreased.

[0033] When the accelerator lever 18 is operated to the forward tilt position, the output rotation of the engine E increases, and when the accelerator lever 18 is operated to the rearward tilt position, the output rotation of the engine E decreases. As a result, by operating the accelerator lever 18, the output rotation of the engine E can be increased or decreased to increase or decrease the rotation speed of the threshing drum, etc. of the threshing device 4, thereby enabling efficient threshing and sorting processing.

[0034] When the harvester lever 19 is operated to the forward tilt position, the harvesting clutch 32 and the threshing clutch 33 are disengaged, and the harvesting device 3 and the threshing device 4 are stopped. When the harvester lever 19 is operated to the rearward tilt position, the harvesting clutch 32 and the threshing clutch 33 are engaged, and the output rotation of the engine E is transmitted to the harvesting device 3 and the threshing device 4, driving the harvesting device 3 and the threshing device 4. When the harvester lever 19 is operated to the neutral position, the harvesting clutch 32 is engaged and the threshing clutch 33 is disengaged, so the harvesting device 3 drives and the threshing device 4 is stopped.

[0035] The tilt position, etc. of the main shift lever 16 is measured by an angle sensor 16S such as a potentiometer attached to the bottom of the main shift lever 16, the tilt position, etc. of the sub-shift lever 17 is measured by an angle sensor attached to the bottom of the sub-shift lever 17, the tilt position, etc. of the accelerator lever 18 is measured by an angle sensor 18S attached to the bottom of the accelerator lever 18, and the tilt position, etc. of the mowing lever 19 is measured by an angle sensor 19S attached to the bottom of the mowing lever 19.

[0036] As shown in Fig. 6, the base of a fan-shaped operating tool 41 is supported on the trunnion shaft 40 of the continuously variable transmission 30. A gear 42A supported on the output shaft of a forward motor 42 and a gear 43A supported on the output shaft of a reverse motor 43 are engaged with gears formed on the outer periphery of the operating tool 41. As a result, the forward motor 42 and the reverse motor 43 are driven based on the attitude of the main speed change lever 16, i.e., the measurement value of the angle sensor 16S, to rotate the trunnion shaft 40 of the continuously variable transmission 30, thereby increasing or decreasing the output rotation of the continuously variable transmission 30 and switching the rotation direction.

[0037] In addition, instead of the configuration shown in Figure 6, one side of an arm extending radially can be supported on the trunnion shaft 40 of the continuously variable transmission 30, and a forward cylinder driven by a forward solenoid and a reverse cylinder driven by a reverse solenoid can be connected to the other side of the arm to rotate the trunnion shaft 40 of the continuously variable transmission 30.

[0038] As shown in FIG. 7, the device controller 50 is made up of a processing unit 51 including a CPU and the like, and a storage unit 52 including a ROM, a RAM, a hard disk drive, a flash memory, and the like.

[0039] When the output rotation of the engine E is decelerated to a preset first or second set output rotation due to the load applied to the engine E, the processing unit 51 performs processing such as decelerating the traveling speed of the traveling device 2 to a preset first or second set traveling speed regardless of the tilted posture of the main shift lever 16.

[0040] The storage unit 52 stores preset first and second set output rotation speeds of the engine E, preset first and second set travel speeds of the travel device 2, and the like.

[0041] The machine controller 50 is connected to a monitor 11 for setting the first and second set output rotations, an angle sensor 16S for measuring the tilt position of the main speed change lever 16, an angle sensor 19S for measuring the tilt position of the mowing / removal lever 19, etc. via a predetermined input interface circuit.

[0042] The machine controller 50 is connected to the reaping clutch 32, the threshing clutch 33, and the forward motor 42 and reverse motor 43 that rotate the trunnion shaft 40 of the continuously variable transmission 30 via a specified output interface circuit.

[0043] The engine controller 60 is connected, via a predetermined interface circuit, to an angle sensor 18S that measures the inclination attitude of the accelerator lever 18, a speed sensor 61 that measures the output rotation of the engine E, i.e., the output rotation of the output shaft of the engine E, an opening sensor 62 that measures the opening state of the throttle valve that supplies combustion air to the cylinder of the engine E, a fuel sensor 63 that measures the amount of fuel injected into the cylinder of the engine E, and the like.

[0044] Furthermore, the main machine controller 50 and the engine controller 60 are connected via a wireless circuit 53. As a result, input information from the angle sensor 16S and the like input to the main machine controller 50 is sent to the engine controller 60, and when the main shift lever 16 is operated from the neutral position to the forward tilt position, the output rotation of the engine E can be increased or decreased. Furthermore, input information from the speed sensor 61 input to the engine controller 60 is sent to the main machine controller 50, and the output rotation of the engine E can be controlled based on input such as the output rotation of the engine E.

[0045] As shown in Figure 8, in step S1, the processing unit 51 of the machine controller 50 determines whether the main shift lever 16 has been operated to a position that starts control of the output rotation, etc. of the engine E. For example, if it is determined that the main shift lever 16 has been operated to the neutral position, which is the control start position, the process proceeds to step S2, and if it is determined that the main shift lever 16 has not been operated to the control start position, step S1 is repeated. The operating position of the main shift lever 16 is measured by the angle sensor 16S.

[0046] In step S2, the processing unit 51 drives the throttle valve of the engine E via the wireless circuit 53 and the engine controller 60 to increase the output rotation of the engine E to the rated output rotation, and then proceeds to step S3. The rated output rotation of the engine E mounted on the combine harvester of this embodiment is 2600 rpm, and the green zone is 2000 to 2600 rpm.

[0047] In step S3, the processing unit 51 determines whether the load factor of the engine E is equal to or greater than a preset load factor. If the load factor of the engine E is equal to or greater than the preset load factor, the process proceeds to step S4, and if the load factor of the engine E is less than the preset load factor, the process returns to step S2. The load factor of the engine E is a ratio calculated by dividing the amount of fuel injected into the engine E by the amount of fuel injected into the engine E at rated output rotation, and the amount of fuel injected into the engine E is measured by the fuel sensor 63. In this embodiment, the set load factor of the engine E is set to 100%.

[0048] In step S4, the processing unit 51 determines whether the load rate of engine E has been at or above 100% for a predetermined period of time. If the load rate of engine E has been at or above 100% for a predetermined period of time, the process proceeds to step S5. If the load rate of engine E has not been at or above 100% for a predetermined period of time, the process returns to step S3. This makes it possible to level out fluctuations in the load on engine E due to fluctuations in the amount of straw transported to the threshing device 4, thereby preventing the control system from becoming unstable. The elapsed time is measured by a timer in the machine controller 50. In this embodiment, the set time is set to 3 seconds.

[0049] In step S5, the processing unit 51 determines whether the output rotation of the engine E has decelerated from the rated output rotation. If it is determined that the output rotation of the engine E has decelerated from the rated output rotation, the process proceeds to step S6, and if it is determined that the output rotation of the engine E is maintaining the rated output rotation, the process returns to step S2. The output rotation of the engine E is measured by the speed sensor 61.

[0050] In step S6, the processing unit 51 determines whether the output rotation of the engine E has been decelerated to equal to or greater than a first set output rotation while being less than the rated output rotation. If the output rotation of the engine E has been decelerated to equal to or greater than the first set output rotation while being less than the rated output rotation, the process proceeds to step S7, and if the output rotation of the engine E has been decelerated to less than the first set output rotation, the process proceeds to step S8. In this embodiment, the first set output rotation is set to 2500 rpm, which is 100 rpm slower than the rated output rotation and falls within the green zone.

[0051] In step S7, the processing unit 51 controls the speed of the traveling device 2 to increase or decrease the output rotational speed of the engine E and drive the forward motor 42 and the reverse motor 43 via the radio circuit 53 and the engine controller 60, and then returns to step S1. This reduces the load on the engine E, preventing the engine E from overheating and suppressing damage to the continuously variable transmission 30 due to a reduction in the output rotational speed of the engine E. In this embodiment, the first set traveling speed is set to a traveling speed that is 10% slower than the traveling speed of the traveling device 2 corresponding to the operating position of the main shift lever 16. For example, if the traveling speed of the traveling device 2 corresponding to the operating position of the main shift lever 16 is 40 km / h, the first set traveling speed is set to 36 km / h. Alternatively, the processing unit 51 can stop the control of increasing or decreasing the output rotational speed of the engine E via the radio circuit 53 and the engine controller 60 and drive the forward motor 42 and the reverse motor 43 to slow the traveling speed of the traveling device 2 to the first set traveling speed.

[0052] In step S8, the processing unit 51 determines whether the output rotation of the engine E has been decelerated to equal to or greater than the second set output rotation while being less than the first set output rotation. If the output rotation of the engine E has been decelerated to equal to or greater than the second set output rotation while being less than the first set output rotation, the process proceeds to step S9, and if the output rotation of the engine E has been decelerated to less than the second set output rotation, the process proceeds to step S10. In this embodiment, the second set output rotation is set to 2400 rpm, which is 200 rpm slower than the rated output rotation and falls within the green zone.

[0053] In step S9, the processing unit 51 controls the speed of the traveling device 2 to increase or decrease the output rotational speed of the engine E and drive the forward motor 42 and the reverse motor 43 via the radio circuit 53 and the engine controller 60, and then returns to step S1. This reduces the load on the engine E, thereby more effectively preventing the engine E from overheating and further suppressing damage to the continuously variable transmission 30 due to a reduction in the output rotational speed of the engine E. In this embodiment, the second set traveling speed is set to a traveling speed that is 20% slower than the traveling speed of the traveling device 2 corresponding to the operating position of the main shift lever 16. For example, if the traveling speed of the traveling device 2 corresponding to the operating position of the main shift lever 16 is 40 km / h, the second set traveling speed is set to 32 km / h. Alternatively, the processing unit 51 can stop the control of increasing or decreasing the output rotational speed of the engine E via the radio circuit 53 and the engine controller 60 and drive the forward motor 42 and the reverse motor 43 to slow the traveling speed of the traveling device 2 to the first set traveling speed.

[0054] In step S10, the processing unit 51 stops the control of increasing or decreasing the output rotation speed of the engine E via the radio circuit 53 and the engine controller 60, and then returns to step S1. Note that the processing unit 51 continues to drive the forward motor 42 and the reverse motor 43 to reduce the traveling speed of the traveling device 2. This removes the excessive load applied to the engine E, thereby preventing damage to the engine E.

[0055] Fig. 9 shows a theoretical control map of the output rotation of engine E and the control ratio of forward motor 42 and reverse motor 43 that rotate trunnion shaft 40 of continuously variable transmission 30, i.e., the control ratio of continuously variable transmission 30, and Fig. 10 shows an actual control map of the output rotation of engine E and the control ratio of continuously variable transmission 30. The rated output rotation of engine E installed in the combine harvester of this embodiment is 2600 rpm, and the green zone is 2000 to 2600 rpm.

[0056] The horizontal axis of the theoretical control map and the actual control map indicates the output rotation speed [rpm] of the engine E, and the vertical axis indicates the control ratio [%] of the continuously variable transmission 30.

[0057] 9, the theoretical control map is formed by a first control line C1 to a fifth control line C5. In this specification, the first control line C1 to the fifth control line C5 are collectively referred to as control lines C.

[0058] The first control line C1 sets the control ratio of the continuously variable transmission 30 to 40% when the output rotation of the engine E is 1000 to 1400 rpm, the second control line C2 sets the control ratio of the continuously variable transmission 30 to 40 to 70% when the output rotation of the engine E is 1400 to 1700 rpm, the third control line C3 sets the control ratio of the continuously variable transmission 30 to 70% when the output rotation of the engine E is 1700 to 2000 rpm, the fourth control line C4 sets the control ratio of the continuously variable transmission 30 to 70 to 100% when the output rotation of the engine E is 2000 to 2300 rpm, and the fifth control line C5 sets the control ratio of the continuously variable transmission 30 to 100% when the output rotation of the engine E is 2300 to 2600 rpm. However, there was a risk that the control of the control ratio of the continuously variable transmission 30 would become unstable due to a large drop in output rotation that occurs when a load greater than a predetermined value is applied to the engine E near the lower limit speed of the green zone of the engine E.

[0059] 10, the actual control map is formed by a first control line D1 to a third control line D3. In this specification, the first control line D1 to the third control line D3 are collectively referred to as control lines D.

[0060] The first control line D1 sets the control ratio of the continuously variable transmission 30 to 40% when the output rotation of the engine E is 1000 to 1400 rpm, the second control line D2 sets the control ratio of the continuously variable transmission 30 to 40 to 100% when the output rotation of the engine E is 1400 to 2000 rpm, and the third control line D3 sets the control ratio of the continuously variable transmission 30 to 100% when the output rotation of the engine E is 2000 to 2600 rpm. This makes it possible to prevent the control ratio of the continuously variable transmission 30 from becoming unstable due to a large drop in output rotation that occurs when a load greater than a predetermined level is applied to the engine E near the lower limit speed of the green zone of the engine E. In addition, the number of control lines can be reduced to simplify control.

[0061] In order to clarify the technical significance of the control ratio of the continuously variable transmission 30, the following will explain, as an example, a specific configuration in which, when the main shift lever 16 is operated from the neutral position to the maximum forward tilt position, the output rotation of the engine E is increased within the continuously variable transmission 30, and the output rotation of the continuously variable transmission 30 becomes 120% of the output rotation of the engine E, i.e., the speed increase rate within the continuously variable transmission 30 is 20%.

[0062] The third control line D3 indicates that when the load on the engine E is less than a predetermined value and the output rotation speed of the engine E is greater than 2000 rpm and less than or equal to 2600 rpm, the control ratio is 100%, and the speed increase rate within the continuously variable transmission 30 is 20%. In other words, the output rotation speed of the engine E, which is 2000 to 2600 rpm transmitted to the continuously variable transmission 30, is increased by 20% within the continuously variable transmission 30, and the output rotation speed of the continuously variable transmission 30 becomes 2400 to 3120 rpm.

[0063] The second control line D2 indicates that when the load on the engine E is equal to or greater than a predetermined value and the output rotation speed of the engine E is greater than 1400 rpm and less than or equal to 2000 rpm, the control ratio is 40 to 100%, and the speed increase rate within the continuously variable transmission 30 is 8 to 20%. In other words, the output rotation speed of the engine E, 1400 to 2000 rpm, transmitted to the continuously variable transmission 30 is increased by 8 to 20% within the continuously variable transmission 30, and the output rotation speed of the continuously variable transmission 30 becomes 1512 to 2400 rpm.

[0064] The first control line D1 indicates that when the load on the engine E is equal to or greater than a predetermined value and the output rotation speed of the engine E is greater than 1000 rpm and less than or equal to 1400 rpm, the control ratio is 40% and the speed increase rate within the continuously variable transmission 30 is 8%. In other words, the output rotation speed of the engine E, 1000 to 1400 rpm, transmitted to the continuously variable transmission 30 is increased by 8% within the continuously variable transmission 30, and the output rotation speed of the continuously variable transmission 30 becomes 1080 to 1512 rpm.

[0065] As shown in Figure 11, the support device 70 that supports a transmission tube (not shown) extending in the left-right direction to which the output rotation of the engine E provided at the rear of the harvesting device 3 is transmitted is formed by a left support device 70L arranged on the front left side of the body frame 1 and a right support device 70R arranged on the front right side.

[0066] The left support device 70L is formed from a fixed part 71 that is fixed to the machine frame 1, a support shaft 72 that extends upward from the fixed part 71, and a rotating arm 73 that is rotatably fixed to the support shaft 72 and curves upward and to the right. In addition, a clamping part 74 that clamps the left part of the transmission cylinder is formed at the top of the rotating arm 73, and a plate-shaped dust cover 75 is attached to the front part of the rotating arm 73. This prevents dust from entering the rotating arm 73 and makes it possible to maintain favorable sliding of the sliding parts of the support shaft 72 and the rotating arm 73.

[0067] The right support device 70R is formed of a fixed part 81 that is fixed to the vehicle frame 1, and an arm 82 that extends upward from the fixed part 81. In addition, a clamping part 83 that clamps the right part of the transmission cylinder is formed on the upper part of the arm 82.

[0068] 12 and 13, a circular opening 73A is formed in the lower part of the rotating arm 73, and a generally L-shaped pin 76 is inserted into the opening 73A from above. An engaging member 77 is provided on the upper side of the fixed part 71, and two circular openings 77A and 77B are formed in the engaging member 77, through which the pin 76 is inserted. The openings 77A and 77B are formed approximately 90 degrees apart in the circumferential direction around the axis of the support shaft 72.

[0069] When rotating arm 73 is rotated clockwise around support shaft 72 to the stored position, pin 76 is inserted through openings 73A and 77A, and when rotating arm 73 is rotated counterclockwise around support shaft 72 to the open position, pin 76 is inserted through openings 73A and 77B. This prevents rotating arm 73 from rotating around support shaft 72, allowing maintenance work on reaping device 3 to be performed safely.

[0070] 14 and 15, a generally L-shaped opening 75A is formed in the lower part of the dust cover 75 at a position facing the pin 76, and the length of the upper part of the pin 76 is determined so that the upper part of the pin 76 inserted through the openings 73A and 77A extends to the front side of the dust cover 75 through the opening 75A. This allows the pin 76 to be easily attached to and detached from the openings 77A by moving the pin 76 vertically from outside the dust cover 75. It is also preferable to provide a lid or the like to cover the opening 77A to prevent the upper part of the pin 76 from coming into contact with other members.

[0071] As shown in Figures 16 and 17, the clamping portion 83 is formed of a lower clamping portion 83A provided on the upper side of the arm 82 and having a semicircular arc-shaped cutout portion formed in the upper part, and an upper clamping portion 83B provided on the upper side of the lower clamping portion 83A and having a semicircular arc-shaped cutout portion formed in the lower part.

[0072] Upper clamping portion 83B is rotatably fixed to a support shaft 82A extending in the left-right direction provided at the front of arm 82 via a connecting body 84. An operating lever 85 extending rearward and upward is provided at the rear of connecting body 84 to open and close upper clamping portion 83B.

[0073] A hook member 86 extending rearward and downward is rotatably fixed to a support shaft 85A extending left and right in the middle of the operating lever 85. The tip of the hook member 86 is formed in a roughly J-shape and engages with a pin 87 provided on the upper part of the arm 82, extending left and right.

[0074] The hook member 86 is formed of a leaf spring that can be deformed in the left-right direction. As a result, the tip of the hook member 86 can be deformed to the left to release the engagement between the hook member 86 and the pin 87, and the right part of the transmission tube can be removed from the clamping part 83. [Explanation of symbols]

[0075] 1 Aircraft frame 2 Running gear 3 Reaping device 4. Threshing equipment 5 Control Unit 16 Main gearshift lever (gearshift lever) 30 Continuously variable transmission 42 Forward motor 43 Reverse motor 50 Main controller (controller) E-Engine

Claims

1. A combine harvester having a traveling device (2) provided below a machine frame (1) on which an engine (E) is mounted, a reaping device (3) provided in front of the machine frame (1), a threshing device (4) provided to the left rear of the reaping device (3), and a control unit (5) provided to the right rear of the reaping device (3), A continuously variable transmission (30) for increasing / decreasing the output rotation of the engine (E) and switching the rotation direction is provided downstream of the transmission path of the engine (E), and a traveling device (2) is provided downstream of the transmission path of the continuously variable transmission (30), The control unit (5) is provided with a speed change lever (16) for increasing or decreasing the output rotation of the engine (E) and the output rotation of the continuously variable transmission (30), When a preset time has elapsed in which the load factor of the engine (E) is 100% or more, and the output rotation of the engine (E) is decelerated to a preset first set output rotation or more below the rated rotation of the engine (E), the controller (50) of the operating section (5) increases or decreases the output rotation of the engine (E) and drives the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) to decelerate the traveling speed of the traveling device (2) to a preset first set traveling speed, regardless of the operating attitude of the speed change lever (16); A combine harvester characterized in that the set time is set to a time that evens out fluctuations in the load on the engine (E) caused by fluctuations in the amount of straw transported to the threshing device (4).

2. 2. A combine harvester according to claim 1, wherein when the output rotation of the engine (E) is decelerated to a first set output rotation or more below the rated rotation of the engine (E), the increase / decrease of the output rotation of the engine (E) is stopped.

3. A combine as described in claim 1 or 2, wherein the set time is set to 3 seconds.

4. 2. The combine harvester according to claim 1, wherein, when the output rotation of the engine (E) is decelerated below a first set output rotation to a preset second set output rotation or above, the output rotation of the engine (E) is increased or decreased and the forward motor (42) and the reverse motor (43) of the continuously variable transmission (30) are driven to decelerate the traveling speed of the traveling device (2) to a preset second set traveling speed that is slower than the first set traveling speed.

5. 5. A combine harvester according to claim 4, wherein when the output rotation of the engine (E) is decelerated to a second set output rotation or more below a first set output rotation, the increase / decrease of the output rotation of the engine (E) is stopped.

6. 5. The combine harvester according to claim 4, wherein when the output rotation of the engine (E) is reduced to less than a second set output rotation, the increase / decrease of the output rotation of the engine (E) is stopped.

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