JP2013005769A - Combine harvester - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve problems of a combine harvester such that increased vibration due to insufficient rigidity of a driving gear box support system of a threshing cylinder during threshing operation can cause slippage of a belt, disabling continuous stabilization of threshing performance since the tension of the belt from the driving gear box to a drive shaft of the threshing cylinder cannot be held, and such that the life of the belt is reduced by the slippage of the belt, and the maintenance frequency is increased.SOLUTION: In the combine harvester, the driving gear box 51 of the threshing cylinder is connected to a rear frame 55 supporting a vertical auger portion of a discharge auger device in parallel by two frames of an upper connecting frame 53 and a lower connecting frame 54, and an input shaft 52 of the gear box 51 is disposed between the two frames.

Description

  The present invention relates to a combine equipped with a handling cylinder.

  Conventionally, combine harvesting cereals has left and right crawlers on the lower side of the traveling frame, a harvesting device that harvests cereals at the front of the aircraft, and a whole culling that threshs the harvested cereals received from this reaping device Type threshing device, a storage tank for storing threshing grains provided in parallel with the threshing device, and an engine and a control device on the front side of the storage tank. And the drive gearbox which rotates the barrel of a threshing device is arranged behind the side of the threshing device, and is supported by a vertical frame from the traveling frame, so that its transmission system is simply configured. (Patent Document 1 FIG. 8).

JP2011-67154A

  However, in the technique described in Patent Document 1, the drive gear box support structure is not sufficiently rigid, the drive gear box is vibrated by the driving load of the handling cylinder, or the support member of the drive gear box is deformed. The input shaft or output shaft of the drive gearbox may be deformed. As a result, the tension of the belt that inputs the driving force from the engine side to the driving gear box and the belt that transmits the driving force from the driving gear box to the driving shaft of the handling cylinder is not maintained, and the belt is sufficient for the handling cylinder to slip. There was a problem that the driving force could not be supplied and the threshing performance could not be stabilized at all times, and there was a problem that the belt life was shortened due to slipping of the belt and the maintenance frequency increased.

The present invention has taken the following technical means to solve the above problems.
That is, the invention described in claim 1 includes a threshing device (5) having a handling cylinder (5a) pivoted by a longitudinal handling cylinder shaft (5b) on the traveling frame (2), and the threshing device (5 ) Between the storage tank (6) disposed on the left and right sides of the storage tank, the discharge auger device (9) provided in the storage tank (6), and the threshing device (5) and the storage tank (6). The vertical auger portion (9a) of the discharge auger device (9) is supported by a combine provided with a drive gear box (51) that transmits the driving force from the engine (7) to the cylinder (5a). The rear frame (55) is raised upward from the traveling frame (2), and the upper part of the drive gear box (51) above the input shaft (52) and the rear frame (55) are connected to the upper connecting frame (53). ), The drive gearbox 51) the lower part of the input shaft (52) below the input shaft (52) and the rear frame (55) are connected by a lower connecting frame (54), and the lower connecting frame (54) and the traveling frame (2) are vertically connected. The combine is characterized by being connected by a frame (66).

  According to a second aspect of the present invention, the drive gear box (51) has an output shaft (56) for outputting the driving force input to the input shaft (52) to the barrel shaft (5b) side. 2. The device according to claim 1, wherein the output shaft is arranged between the upper connection frame and the lower connection frame in a plan view. It is a combine.

  According to a third aspect of the present invention, there is provided an input pulley (52a) provided on an input shaft (52) of the drive gearbox (51), and a relay pulley (57a) that is rotated by a driving force from the engine (7). A clutch arm (59) provided with a tension roller (58) that hangs a belt (57b) around the belt (57b) and tensions and relaxes the belt (57b) is rotatably supported on the drive gear box (51). A tension rod (60) for rotating the arm (59) is disposed between the upper connection frame (53) and the lower connection frame (54) in a side view, and the tension rod (60) is operated. The combine according to claim 1 or 2, wherein a tension rod driving part (61) is supported by either the upper connection frame (53) or the lower connection frame (54). It is.

  According to a fourth aspect of the present invention, an intermediate frame (62) having a spring bracket (65) is connected to the upper connection frame (53), and the spring bracket (65) and the tension rod (60) are connected. The combine according to claim 1, 2 or 3, wherein a compression spring (63) is provided between the tip support (64) provided at the tip.

  The invention according to claim 5 is the combine according to any one of claims 1 to 4, wherein the tension rod drive section (61) is disposed rearward of the upper connection frame (53). is there.

  According to the first aspect of the present invention, the upper connecting frame (53) and the lower connecting frame (54) have two frames, and the rear frame (55) having a high rigidity and the drive gearbox (51) of the handling cylinder (5a). ) Can be supported to increase the support rigidity of the drive gear box (51). In particular, by disposing the input shaft (52) of the drive gear box (51) between the upper and lower portions of the upper connecting frame (53) and the lower connecting frame (54), the position variation of the input shaft (52) is suppressed. Can do. With these effects, the driving force can be stably transmitted to the handling cylinder (5a), and the maintenance frequency can be reduced.

  According to the second aspect of the present invention, the output shaft (56) of the drive gearbox (51) is disposed between the upper connecting frame (53) and the lower connecting frame (54) in a plan view, whereby the output shaft (56) The position fluctuation | variation can be suppressed and a driving force can be transmitted to a handling cylinder (5a) stably.

  According to the third aspect of the present invention, the tension rod (60) is disposed between the upper connecting frame (53) and the lower connecting frame (54), and the tension rod driving unit (61) is installed in any of these frames. By connecting the two, the support rigidity of the tension rod (60) and the tension rod driving unit (61) can be increased. As a result, the barrel (5a) can be driven stably, and transmission of driving force from the engine (7) side to the driving gear box (51) and switching between cutoffs can be performed reliably.

  According to the invention of claim 4, the compression spring (63) is provided between the tip support (64) provided at the tip of the tension rod (60) and the spring bracket (65) provided on the intermediate frame (62). By providing, when the first belt (57b) is relaxed by moving the tension rod (60) forward, the forward movement of the tension rod (60) is facilitated and the torque transmission is cut off quickly. Can do. Further, variation in the position of the tension rod (60) due to the backlash of the gear of the tension rod driving section (61) can be suppressed, and the power transmission state and the cutoff state can be switched reliably.

  According to the fifth aspect of the present invention, the tension rod drive unit (61) is arranged behind the coupling portion with the rear frame (55), so that the operator can access the tension rod drive unit (61) from the rear of the combine. It becomes easy to do and the labor of maintenance work, such as adjustment of the length of a tension rod (60), can be reduced.

It is a whole block diagram of a combine. It is a rear view of the transmission part to a handling cylinder. It is a right view of the transmission part to a handling cylinder. It is a principal part enlarged view from the right direction (side view) of the gearbox drive gearbox periphery. It is a principal part enlarged view from the upper direction (plan view) circumference of the gear box for handling cylinder drive. It is a principal part enlarged view around a tension rod part. It is a front view of a spring bracket. It is an internal see-through | perspective right side view of an engine radiator part. It is a radiator block diagram. It is a longitudinal cross-sectional view showing the internal structure of a heat exchange apparatus. It is a transmission system expansion diagram. It is a principal part block diagram of a transmission system. It is a front view of the transmission part of a heat exchange operation state. It is a principal part front view of the transmission part of a discharge ventilation operation state. It is a principal part block diagram of the transmission part at the time of supply / discharge operation | movement.

Embodiments specifically configured based on the above technical idea will be described below with reference to the drawings. As shown in FIG. 1, a combine 1 according to the present invention includes a left and right crawlers 3, 3 having a body main body on the lower side of a traveling frame 2, a reaping device 4 for harvesting cereals at the front of the body, and this reaping A full-throwing-type threshing device 5 for threshing the harvested cereals received from the device 4, a storage tank 6 for storing threshing grains provided in parallel with the threshing device 5, and a connection to the storage tank 6, A discharge auger device 9 that discharges the grain to the outside, and an engine 7 and a control device 8 that are integrally configured on the front side of the storage tank 6 are configured. Further, the full throwing type threshing device 5 has a structure having a handling cylinder 5a pivoted by a longitudinal handling cylinder shaft 5b, and a gear box 51 for driving the handling cylinder 5a by receiving power from the engine 7 is provided. In the rear part of the threshing device 5 and between the threshing device 5 and the storage tank 6, it is provided toward the storage tank 6.

  A barrel 5a provided inside the full throwing type threshing device 5 distributes the power from the engine 7 and drives it. As shown in FIGS. 2 and 3, power from the engine 7 is first fitted from the relay pulley 57a fitted to the relay shaft 57 to the input shaft 52 of the drive gear box 51 of the handling cylinder via the first belt 57b. It is transmitted to the input pulley 52a. The power transmission direction is changed by the driving gear box 51 of the handling cylinder, and the handling pulley fitted to the handling cylinder shaft 5b through the second belt 56b from the output pulley 56a fitted to the output shaft 56 of the driving gear box 51. The barrel drive pulley 5c is driven. The drive gear box 51 is an input unit for power to the drive gear box 51, and is an input shaft 52 that rotates about the axis in the vehicle width direction, and an output unit for power from the gear box 51, and is parallel to the barrel 5b. An output shaft 56 that rotates around a simple axis is provided.

  As shown in FIGS. 4 and 5, the drive gear box 51 is raised from the traveling frame 2 in parallel with the vertical auger portion 9 a of the discharge auger device 9 by two connection frames of an upper connection frame 53 and a lower connection frame 54. The rear frame 55 is firmly coupled. In addition, the lower connection frame 54 is coupled to a vertical frame 66 provided upward from the traveling frame 2. The rear frame 55 adjacent to the vertical auger portion 9a is provided to ensure the rigidity of the vertical auger portion 9a and has high rigidity. Therefore, the rear frame 55 and the drive gear box 51 are firmly coupled to each other. The rigidity of the support structure of the drive gear box 51 can be increased. In addition, the input shaft 52 of the drive gear box 51 is disposed between the upper and lower sides of the two connecting frames 53 and 54. With such a configuration, it is possible to increase the support rigidity of the drive gear box 51, particularly the rigidity of the input shaft 52 in the pitching direction.

  Further, the output shaft 56 of the drive gear box 51 is disposed between the left and right of the two connecting frames 53 and 54. By adopting such a configuration, the support rigidity in the vehicle width direction can be increased, and the position fluctuation of the output shaft 56 can be suppressed.

To connect or disconnect the power from the engine 7 to the drive gear box 51 of the barrel, the first belt 57b wound around the input pulley 52a fitted to the input shaft 52 is tensioned or relaxed using the clutch arm 59. By doing. By moving the tension rod 60, which is rotatably coupled to the upper end of the clutch arm 59, to the rear, the tension roller 58 provided at the lower end of the clutch arm 59 is moved forward, and the power is applied when the first belt 57b is in tension. Communicated. On the contrary, when the tension rod 60 is moved forward, the tension roller 58 of the clutch arm 59 moves rearward and the power is cut off when the first belt 57b is in a relaxed state. The clutch arm 59 is coupled to be rotatable about a support shaft 68 provided in the drive gear box 51.

The tension rod 60 is disposed between the upper connection frame 53 and the lower connection frame 54, and is a tension rod drive that is a motor with a speed reducer coupled to one or both of the connection frame 53 and the lower connection frame 54. Driven by the unit 61. By adopting such a configuration, it is possible to increase the rigidity of the tension rod drive system, that is, the support rigidity of the tension rod 60 and the tension rod drive unit 61, obtain a stable threshing operation and a clutch operation, and reduce maintenance work. Can be planned. Further, the tension rod drive system is arranged on the upper part of the combine 1, and the operator can access the tension rod drive system and easily perform maintenance work simply by removing or opening / closing the cover 72.

  As shown in FIG. 6, the tension rod 60 is fitted with a compression spring 63 on which a compression load acts when the tension rod 60 moves rearward. The compression spring 63 is configured to apply a compression load by a tip support 64 provided at the tip of the tension rod 60 and a spring bracket 65 provided on the intermediate frame 62. The intermediate frame 62 is disposed between the coupling portion 53a of the upper coupling frame 53 with the driving gear box 51 and the coupling portion 53b with the rear frame 55 of the frame 53, and the upper coupling frame 53 and the driving gear box. 51, and a spring bracket 65 is provided at an intermediate portion thereof. By adopting such a configuration, when the tension rod 60 that has been located rearward for tensioning the first belt 57b is moved forward and the first belt 57b is relaxed, the front of the tension rod 60 is increased. The operation can be smoothly performed and the torque transmission can be cut off quickly. Further, variation in the position of the tension rod 60 due to the backlash of the gear of the tension rod driving unit 61 can be suppressed, and the power transmission state and the cutoff state can be switched reliably.

  In this embodiment, a spring that acts in the extending direction is provided, but a spring that acts in the direction of tensioning the first belt 57b is provided between the clutch arm 59 and the tension rod driving unit 61, and the tension roller. It is also possible to adopt a configuration in which 58 is pressed against the first belt 57b.

  The tension rod 60 is divided into two in the longitudinal direction so that the tension load on the first belt 57 b can be easily adjusted, and the length of the tension rod 60 can be adjusted by the turnbuckle 67.

  The spring bracket 65 shown in FIG. 7 is divided into a connecting portion 76 to the intermediate frame 62 and a receiving portion 77 of the compression spring 63 for the purpose of reducing assembly work and maintenance work. The spring bracket 65 is provided with a through hole (through groove) 75 for the tension rod 60. Since the tension rod 60 is rotatably coupled to the tension rod driving unit 61 and the clutch arm 59, the tension rod 60 is moved up and down when moving back and forth. At this time, in order to prevent the tension rod 60 from coming into contact with the spring bracket 65 and unstable tension load on the belt 57b, the through hole 75 has a notch structure. The through hole 75 may have a structure of an elongated hole in the vertical direction.

  At both ends of the compression spring 63, a stepped collar 73 having a small diameter portion that fits into the inner diameter of the compression spring 63 is provided. By adopting such a configuration, the compression spring 63 easily follows the vertical movement of the tension rod 60, and the effect of prompt torque transmission interruption of the compression spring 63 and the effect of suppressing the position variation can be exhibited. In addition, a buckling prevention collar 74 is provided inside the spring 63 and outside the tension rod 60. The buckling prevention collar 74 has the same length as that when a predetermined compression load is applied to the compression spring 63. With such a length, buckling of the compression spring 63 can be prevented, the adjustment of the compression spring 63 is facilitated, and maintenance work can be reduced.

  A worm wheel speed reducer is used as a motor with a speed reducer of the tension rod driving unit 61. This is because the tension rod 60 has a self-locking function in which the operating distance of the tension rod 60 is short and a large thrust is required, and the tension rod 60 is not operated from the clutch arm 59. As a result, the tension load on the first belt 57b is stabilized, a stable threshing operation and a clutch operation can be obtained, and maintenance work can be reduced.

  The tension rod driving unit 61 is disposed behind the connecting portion 53b of the upper connecting frame 53 with the rear frame 55, and is provided below the lateral auger portion 9b of the discharge auger device 9. This arrangement makes it easy for an operator to access the tension rod drive unit 61 from behind the combine without disturbing the turning range of the auger, and shortens the maintenance time such as adjusting the length of the tension rod 60. Maintenance work can be reduced.

  The tension rod 60 is rotatably coupled to an arm 70 fitted to the output shaft outside the tension rod drive unit 61. By operating the output shaft, the tension rod 60 can be driven back and forth by an amount proportional to the length of the arm 70. In addition, the angle sensor 69 main body is provided in addition to the tension rod driving unit 61 including the arm 70 so that the operation amount of the tension rod 60 can be accurately grasped and the operating angle of the clutch arm 59 can be easily adjusted. A pin 71 for driving the angle sensor is provided.

Next, the cooling method of the engine 7 will be described.
Normally, the engine is cooled by installing one radiator on a shaft different from the fan shaft of the engine and circulating cooling water between the engine and the radiator together with direct cooling by the fan. FIG. 10 is a longitudinal sectional view showing an internal configuration of an embodiment of a heat exchange device including the radiator. The heat exchanging device 107 includes a main radiator 101 that exchanges heat with the intake air through a main radiator cover 109 provided with a mesh-like dustproof filter on the outside of the machine body, and main air that sucks in the outside air inside the main radiator 101. It comprises a radiator fan 102, an exhaust fan 108 that blows outward, concentric support shafts 102a and 108a that respectively support the fans 102 and 108, and respective transmission portions. Each transmission portion has transmission belts 110b and 111b between pulleys 102b and 108b provided at the shaft ends of both support shafts 102a and 108a, respectively, and drive pulleys 110a and 111a of the transmission shaft 110 and the reverse rotation shaft 111, respectively. It can be wound and configured to be able to transmit individually.

  11, the transmission shaft 110 and the reverse rotation shaft 111 receive the power of the engine 7 on the transmission shaft 110, and from the transmission shaft 110, the transmission system of FIG. As shown in FIG. 2, the transmission is transmitted by a transmission belt 113 that winds the counter shaft 111 c of the reverse rotation shaft 111 and the compressor shaft 112. In addition, the transmission belts 110b and 111b of both fans 102 and 108 are provided with tension clutches 114 and 115, respectively, so that individual transmission control is possible.

  As shown in the front view of the transmission unit in the heat exchange operation state by the intake of outside air in FIG. 13, the specific configuration of the transmission unit is such that the concentric support shafts 102a and 108a of the fans 102 and 108 are arranged inside the outer cylinder 116a. And is supported by the frame 116 through the outer cylinder 116a. The tension clutches 114 and 115 are supported by the tension arms 117 and 118 so as to be swingable about the respective fulcrums 117a and 118a, and are connected to an action member 119 acting on the tension arms 117 and 118.

  The tension clutches 114 and 115 will be described in detail. As shown in the front view of the main portion of the transmission portion in the exhaust air blowing operation state of FIG. 14, the tension arms 117 and 118 are respectively provided with guide rods 117b and outer rods. The springs 117c and 118c are attached to the 118b, connected through the springs 117c and 118c, and collars 117d and 118d for restricting the expansion of the springs 117c and 118c for compression are provided on the guide rods 117b and 118b, respectively. The rods 117b and 118b are connected to the action member 119. The action member 119 is configured to be able to reciprocate horizontally between two left and right positions by an electric arm 119a driven by a clutch switching motor (switching means) 119b.

  In order to prevent buckling of the springs 117c and 118c and to protect the screws of the guide rods 117b and 118b, a guide tube is provided slidably with respect to the guide rods 117b and 118b and the collars 117d and 118d. , 118d can be overlapped with springs 117c, 118c. Further, the holes of the connecting portions of the tension arms 117 and 118 are formed larger than the outer diameter of the guide tube and smaller than the outer diameters of the collars 117d and 118d.

  As for the operation of the tension clutches 114 and 115 having the above-described configuration, as shown in the configuration diagram of the main part of the transmission portion during the intake / exhaust operation in FIG. 15, the action member 119 is the electric arm 119a in FIG. , The transmission clutch 110b of the main radiator fan 102 transmits power from the transmission shaft 110, and the dust-removed state is the same. In FIG. 15B, when the action member 119 moves to the right, the tension clutch 114 of the main radiator fan 102 cuts the transmission power, and the transmission belt 111b by the tension clutch 115 of the discharge fan 108 transmits power from the reverse shaft 111. Do.

  As described above, since both tension clutches 114 and 115 operate in reverse with respect to both transmission belts 110b and 111b in response to the movement of the acting member 119 to the left and right two positions by the rotation of the electric arm 119a, As a result, when the main radiator fan 102 is operated, the main radiator 101 receives the introduced outside air and performs heat exchange of the cooling water. At this time, the main radiator 101 The main radiator cover 109 provided on the upstream side separates the dust contained in the introduced outside air into its outer surface, and when the exhaust fan 108 is operated, the air blowing direction is discharged from the outside air suction until then, The dust adhering to the outer surface of the radiator cover 109 is discharged outward.

  In this case, the transmission portions of the fans 102 and 108 can drive the exhaust fan 108 without difficulty even until the main radiator fan 102 stops, and the exhaust fan 108 is quickly exhausted by the operation of the exhaust fan 108. From the start of air blowing, it is possible to avoid a large reverse load necessary for switching and driving the transmission portion of the main radiator fan 102 having a large rotational inertia to reverse rotation, and until shifting to discharge air blowing Time loss can be minimized.

When the support rigidity of the drive gear box 51 is increased, the load of the threshing operation of the same body can be increased, and in addition to the configuration of the above-described embodiment, the engine 7 needs to be cooled more than ever.

In order to improve the cooling capacity in this case, a second radiator 103 is installed separately from the main radiator 101 as shown in FIGS. The circulation system of the second radiator 103 is provided in parallel with the main radiator 101. The second radiator 103 is driven by transmitting the rotation of the main radiator fan 102 to the second radiator fan 104 via a transmission shaft 106 disposed between the main radiator 101 and the second radiator 103. With this configuration, forward / reverse rotation of the fan shaft of the second radiator 103 can be obtained, and the configuration can be saved in space.

The fan shaft of the second radiator fan 104 is provided with an electromagnetic clutch 105, and a controller for the electromagnetic clutch 105 is provided so as to be turned on and off by a program. With this configuration, the rotation of the second radiator fan 104, which is normally synchronized with the main radiator fan 102, can be interlocked with a time difference, and the dust of the dust filter for the second radiator fan 104 can be further reduced. Accordingly, the cooling capacity of the engine 7 can be maintained.

DESCRIPTION OF SYMBOLS 1 Combine 2 Traveling frame 5 Threshing apparatus 5a Handling cylinder 5b Handling cylinder 6 Storage tank 7 Engine 9 Discharge auger apparatus 9a Vertical auger part 51 Driving cylinder drive box 52 Input shaft 53 Upper connection frame 54 Lower connection frame 55 Rear frame 56 Output shaft 57 Relay shaft 57a Relay pulley 57b First belt 58 Tension roller 59 Clutch arm 60 Tension rod 61 Tension rod drive unit 62 Intermediate frame 63 Compression spring 64 Tip support 65 Spring bracket 66 Vertical frame

Claims (5)

On the traveling frame (2), a threshing device (5) having a handling cylinder (5a) pivoted on a longitudinal handling cylinder axis (5b);
A storage tank (6) arranged on one side of the threshing device (5);
A discharge auger device (9) provided in the storage tank (6);
In a combine provided with a drive gear box (51) that is arranged between the threshing device (5) and the storage tank (6) and transmits the driving force from the engine (7) to the handling cylinder (5a),
A rear frame (55) that supports the vertical auger portion (9a) of the discharge auger device (9) is raised upward from the traveling frame (2),
A portion of the drive gear box (51) above the input shaft (52) and the rear frame (55) are connected by an upper connection frame (53),
The lower part of the drive gear box (51) below the input shaft (52) and the rear frame (55) are connected by a lower connection frame (54),
The combine characterized by connecting the said lower connection frame (54) and the driving | running | working frame (2) with the vertical frame (66). In the drive gearbox (51),
An output shaft (56) for outputting the driving force input to the input shaft (52) to the handle cylinder shaft (5b) side is provided in parallel with the handle cylinder shaft (5b),
The combine according to claim 1, wherein the output shaft (56) is disposed between the upper connecting frame (53) and the lower connecting frame (54) in a plan view. An input pulley (52a) provided on an input shaft (52) of the drive gearbox (51);
A belt (57b) is wound around a relay pulley (57a) that is rotated by a driving force from the engine (7),
A clutch arm (59) having a tension roller (58) for tensioning and relaxing the belt (57b) is rotatably supported on the drive gear box (51),
A tension rod (60) for rotating the clutch arm (59),
Arranged between the upper connection frame (53) and the lower connection frame (54) in a side view,
A tension rod driving part (61) for operating the tension rod (60),
The combine according to claim 1 or 2, wherein the combine is supported on either the upper connection frame (53) or the lower connection frame (54). An intermediate frame (62) having a spring bracket (65) is connected to the upper connection frame (53),
The compression spring (63) is provided between the spring bracket (65) and a tip support (64) provided at the tip of the tension rod (60). Combine. The tension rod driving part (61)
The combine according to any one of claims 1 to 4, wherein the combine is disposed rearward of the upper connection frame (53).

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