JP2011112179A - Hydraulic circuit of combine harvester - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To allow a combine harvester to travel without troubles even in the event of a failure of a flow dividing valve by providing a hydraulic circuit structure such that pressure oil discharged from one hydraulic pump is supplied to a traveling hydraulic transmission and a mowing hydraulic transmission by the flow dividing valve. <P>SOLUTION: The hydraulic circuit includes: a main hydraulic pump (11) which delivers pressure oil to a traveling clutch operation hydraulic circuit (T) and a main hydraulic circuit (W) which performs machine body attitude control and mowing/auger lifting control; and a sub-hydraulic pump (22) which delivers pressure oil to a traveling continuously variable transmission circuit (1) and a mowing continuously variable transmission circuit (2). The pressure oil by the sub-hydraulic pump (22) is distributed to the traveling continuously variable transmission circuit (1) and the mowing continuously variable transmission circuit (2) by a variable-speed flow dividing valve (23), and a variable-speed supply conduit (41) for delivering pressure oil from the sub-hydraulic pump (22) to the variable-speed flow dividing valve (23) and a traveling distribution conduit (43) for delivering the pressure oil from the variable-speed flow dividing valve (23) to the traveling continuously variable transmission circuit (1) are allowed to communicate with each other by an emergency path (46) through an emergency check valve (40) which performs releasing operation at a predetermined pressure. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a configuration of a hydraulic circuit used for lifting control of a reaping device and stability control of front, rear, left, and right of a combiner in a combine.

  For example, as described in Patent Document 1 and Patent Document 2 below, the combine hydraulic circuit includes a traveling hydraulic circuit that controls a traveling brake and a turning brake, a cutting lift hydraulic circuit that controls the lifting device, and rolling of the fuselage. It is composed of a number of hydraulic circuits such as a machine control hydraulic circuit that controls pitching and an auger lifting hydraulic circuit that controls the lifting and lowering of the grain discharging auger.

JP 2003-206907 A JP 2009-118787 A

  In the combine hydraulic circuit, the hydraulic oil discharged from one hydraulic pump is appropriately distributed and supplied to the traveling hydraulic transmission and the cutting hydraulic transmission by the diverter valve. This will hinder cutting and shifting. For example, when the pressure oil supply to the traveling hydraulic transmission is decreased, the traveling speed is decreased or the shift cannot be performed.

  Therefore, in the present invention, in the combine, the hydraulic circuit configuration that supplies the hydraulic oil discharged from one hydraulic pump to the traveling hydraulic transmission and the cutting hydraulic transmission with the diversion valve, the traveling is hindered even if the diversion valve fails. It is a problem to be able to do without.

The problems of the present invention are solved by the following technical means.
The invention according to claim 1 is provided with a main hydraulic pump (11) for sending pressure oil to the traveling clutch operation hydraulic circuit (T) and a main hydraulic circuit (W) for performing body posture control and mowing / auger raising / lowering control, In a combined hydraulic circuit provided with a sub hydraulic pump (22) for sending pressure oil to the traveling continuously variable transmission circuit (1) and the cutting continuously variable transmission circuit (2), the pressure oil of the sub hydraulic pump (22) is shifted to a variable speed diversion valve. (23) A transmission supply line (41) for distributing pressure oil to the traveling continuously variable transmission circuit (1) and the cutting continuously variable transmission circuit (2) and sending pressure oil from the sub hydraulic pump (22) to the variable speed diverter valve (23). And an emergency path (46) through an emergency check valve (40) that releases the hydraulic oil from the variable speed diversion valve (23) to the travel continuously variable transmission circuit (1) with a predetermined pressure. The combined hydraulic circuit is characterized in that it is communicated with each other.

  With this configuration, when the flow of the shift diverter valve (23) becomes poor and the pressure of the shift supply pipe (41) rises, the emergency check valve (40) is activated and the travel continuously variable transmission circuit ( 1) It is possible to perform traveling shift without any trouble by supplying pressure oil.

  The invention according to claim 2 is characterized in that the variable speed diversion valve (23) and the emergency check valve (40) are provided in a distribution hydraulic block (45) formed integrally. Combined hydraulic circuit.

  According to the first aspect of the present invention, even when the shift diverter valve (23) becomes inoperable, pressure oil is supplied to the traveling continuously variable transmission circuit (1) through the emergency road (46) to allow traveling. This makes it possible to move from the field to the repair shop for repair, and improve the work efficiency of the combine.

  According to the invention described in claim 2, in addition to the effects of the invention described in claim 1, the emergency path (46) is provided in the distribution hydraulic block (45), so that piping is not necessary, The entire hydraulic piping structure can be simplified.

It is a hydraulic circuit diagram of a combine showing an embodiment of the present invention. It is the elements on larger scale of the hydraulic circuit of the combine which shows this invention Example. It is the elements on larger scale of the hydraulic circuit which shows another Example. It is an expanded sectional view of a distribution hydraulic block. It is a sectional side view of a relief valve. It is a sectional side view of the Lily valve which shows another Example. It is a sectional side view of the Lily valve which shows another Example. It is a sectional side view of a hydraulic cylinder.

Next, an embodiment of the present invention will be described.
As shown in FIG. 1, the combine hydraulic control circuit controls the pilot oil supplied from the oil tank 10 through the continuously variable transmission circuit 1 by the main hydraulic pump 11 to a predetermined pressure by the first pressure reducing valve 12. The flow branches from the valve 24 toward the travel clutch operating hydraulic circuit T and from the pilot switching valve 5 toward the main hydraulic circuit W.

  The pressure oil passing through the pilot valve 24 toward the travel clutch operating hydraulic circuit T flows toward the left pilot pressure switching valve 16L via the left first throttle 8L and the right pilot pressure switching valve 16R via the right first throttle 8R. Branch to the flow toward.

  In the left pilot pressure switching valve 16L, the flow to the left electromagnetic proportional valve 17L through the left second throttle 7L and further to the left traveling brake cylinder 18L and the pressure oil on the supply side of the left electromagnetic proportional valve 17L are supplied to the left clutch. The flow is switched to the flow toward the switching electromagnetic valve 14L. The return oil of the left traveling brake cylinder 18L is returned to the oil tank 10 from the left electromagnetic proportional valve 17L.

  The left clutch switching electromagnetic valve 14L is supplied with the secondary pressure pressure oil that has passed through the left first throttle 8L through the left check valve 9L. In the left clutch switching electromagnetic valve 14L, pressure oil is supplied to one side of the left steering clutch cylinder 15L, or the left pilot pressure switching valve 16L is switched as the pilot pressure of the left pilot pressure switching valve 16L, and the left second throttle 7L is opened. The passed pressure oil is supplied to the other of the left steering clutch cylinder 15L.

The left pilot pressure switching valve 16L, the left electromagnetic proportional valve 17L, the left clutch switching electromagnetic valve 14L, and the left check valve 9L are incorporated as an integrated left hydraulic control block 35L.
In the right pilot pressure switching valve 16R, the flow that is supplied to the right solenoid proportional valve 17R through the right second throttle 7R and further toward the right traveling brake cylinder 18R, and the pressure oil on the supply side of the right solenoid proportional valve 17R are transferred to the right. The flow is switched to the flow toward the clutch switching electromagnetic valve 14R. The return oil of the right traveling brake cylinder 18R is returned to the oil tank 10 from the right electromagnetic proportional valve 17R.

  The right clutch switching electromagnetic valve 14R is supplied with the secondary pressure pressure oil that has passed through the right first throttle 8R through the right check valve 9R. In the right clutch switching solenoid valve 14R, pressure oil is supplied to one side of the right steering clutch cylinder 15R, or the right pilot pressure switching valve 16R is switched as the pilot pressure of the right pilot pressure switching valve 16R to open the right second throttle 7R. The passed pressure oil is supplied to the other side of the right lateral clutch cylinder 15R.

The right pilot pressure switching valve 15R, the right electromagnetic proportional valve 17R, the right clutch switching electromagnetic valve 14R, and the right check valve 9R are incorporated as an integral right hydraulic control block 35R.
A drain oil passage leading to the oil tank 10 is provided on the pressure oil supply side of the first pressure reducing valve 12 via the electromagnetic opening / closing valve, and this electromagnetic opening / closing is performed when the hydraulic cylinders of the traveling system circuit T and the working system circuit W are not used. If the valve is opened and the pressure oil is immediately returned to the oil tank 10, the driving load of the main hydraulic pump 11 is reduced. When using the cutting lift cylinder 28a, the auger lift cylinder 28b, the left rolling cylinder 28c, the right rolling cylinder 28d, and the pitching cylinder 28e, the electromagnetic on-off valve is closed and the pressure oil is adjusted to the pressure of the first pressure reducing valve 12. Hold.

  Pressure oil discharged from the main hydraulic pump 11 is sent to the proportional flow rate control valve 26 via the pilot switching valve 5 and the electromagnetic switching valve 6, and the auger elevating cylinder 28 b, the left rolling cylinder 28 c, the right rolling cylinder 28 d and the pitching cylinder 28 e are sent. It flows to the main hydraulic circuit W to be controlled.

  The electromagnetic switching valve 6 switches between supply of pressure oil to the traveling clutch operation hydraulic circuit T, cutting / auger up / down control and rolling / pitching control of the airframe, and is sent to the first pilot valve 19 and the second pilot valve 20.

Pressure oil is sent from the pilot switching valve 5 to the proportional flow control valve 26 via the manual switching valve 21.
The pressure oil sent to the proportional flow rate control valve 26 is an ascending switch valve 26a, a descending switch valve 26b, a relief valve 26e, and an ascending variable regulator for adjusting the ascending switch valve 26a and the descending switch valve 26b. One of the control flows controlled by the regulating valve 26c and the regulating valve 26d for lowering is connected to the cutting lift cylinder 28a via the first pilot check valve 30a so that oil can be fed, and the control flow of the proportional flow control valve 26 is controlled. The other of these is connected to the auger elevating cylinder 28b via the second pilot check valve 30b so that oil can be fed.

  The pressure oil sent from the pilot switching valve 5 through the manual switching valve 21 is a vehicle body control circuit to the left rolling switching solenoid valve 27c, the right rolling switching solenoid valve 27d, and the pitching switching solenoid valve 27e through the proportional flow control valve 26. Sent to. The vehicle body control circuit is provided with a vehicle body control relief valve 54 to stabilize the pressure of the supplied pressure oil.

  The manual switching valve 21 can be manually operated for rolling and pitching of the vehicle body when manually neutralized in the event of a hydraulic circuit trouble, but its structure cuts off the oil supply on the pressure supply side when neutral, as shown in FIG. Like to do.

  The pressure oil sent to the left rolling switching solenoid valve 27c is connected to the left rolling cylinder 28c via the third pilot check valve 30c and the second check throttle valve 29c so as to be able to feed oil, and to the right rolling switching solenoid valve 27d. The sent pressure oil is connected to the right rolling cylinder 28d via the fourth pilot check valve 30d and the third check valve-equipped throttle valve 29d so as to be fed, and the pressure oil sent to the pitching switching electromagnetic valve 27e is The fifth pilot check valve 30e and the fifth check throttle valve 29e are connected to the pitching cylinder 28e so that oil can be fed.

  As shown in FIG. 3, when the switching solenoid valve 52 is provided between the first pilot valve 19 and the second pilot valve 20 from the solenoid switching valve 6, the cutting lift cylinder 28a is lifted and lowered even when the auger lift cylinder 28b is lowered. Can work.

  Further, in this circuit configuration, the cutting and auger relief valve 53 is provided in the pressure oil supply path to the second pilot valve 20, so that the high pressure of the vehicle body control circuit such as the left rolling cylinder 28c is increased by the cutting lifting cylinder 28a and the auger lifting cylinder. 28b can be prevented from joining.

  The pressure oil discharged from the sub hydraulic pump 22 in the traveling continuously variable transmission circuit 1 is supplied from the transmission supply line 41 to the transmission branch valve 23 and distributed, and approximately 70% of the hydraulic oil from the transmission supply line 41 does not travel. The remaining 30% of the pressure oil is sent to the stepless transmission circuit 1 from the cutting transmission line 42 to the cutting continuously variable transmission circuit 2.

  As shown in FIG. 2, the speed change supply pipe 41 and the travel distribution pipe line 43 are connected by an emergency path 46 via an emergency check valve 40, and the speed change flow distribution valve 23 is clogged or the flow rate is reduced. When the pressure at 41 increases, the emergency check valve 40 opens and pressure oil is sent directly from the emergency road 46 to the travel continuously variable transmission circuit 1 to enable travel shift.

Further, as shown in FIG. 4, the emergency check valve 40 is accommodated in a distribution hydraulic block 45 made of cast iron that accommodates the shift diversion valve 23 and the seventh check valve 25, and does not need to be piped.
A cracking pressure is applied to the pressure oil return flow path of the relief valve 26e of the proportional flow control valve 26 for controlling the cutting lift cylinder 28a and the auger lift cylinder 28b by the sixth pressure regulating check valve 34, and the seventh check valve 25 is set. Via the replenishment oil passage 70 and the supply passage of the cutting continuously variable transmission circuit 2. The cracking pressure of the sixth pressure regulation check valve 34 is set to be lower than the charge pressure of the cutting hydraulic shift charge circuit 2. (E.g., with respect to the charge pressure 5 kgf / cm ² the cracking pressure and 2kgf / cm ^2.)
The sixth pressure regulating check valve 34 and the seventh check valve 25 may be integrated into a hydraulic block in which the manual switching valve 21 is incorporated.

  FIG. 5 shows a cross-sectional structure of the first pilot valve 19 and the second pilot valve 20. A first end face plate 50 a of a spool 48 for switching the flow path in the valve body 47 is elastically springed by a spring 49. By attaching the first end face plate 50a to the spool 48 by caulking, the cutting portion of the spool 48 is reduced and the manufacturing cost is reduced.

  FIG. 6 shows an example in which a pilot valve is provided in the hydraulic block 51. The second end face plate 50 b attached to the end of the spool 48 by caulking is applied to the end face 47 a of the valve body 47 to restrict movement.

  FIG. 7 shows a sectional view of the relief valve. Inside the valve body 61, a steel ball 65 is springed by a spring 63 against a relief seat 64 provided with a relief hole 66. The partial insertion portion L, which is about half of the entire insertion portion of the 64 valve body 61, has a slight difference in diameter from the insertion hole diameter of the valve body 61. With this structure, the override is good and there is no relief squeal.

  FIG. 8 shows a seal structure of a piston rod 55 of a hydraulic cylinder that operates a side clutch or the like. A cylinder head 56 is fitted to the transmission case 59, a dust seal 60 is fitted to the cylinder head 56 on the outlet side of the piston rod 55 fitted to the cylinder head 56, and the end face of the cylinder head 56 and the dust seal 60 are fitted with a washer 57. The washer 57 is fixed to the transmission case 59 with a C-shaped retaining ring 58. With this structure, a C-type retaining ring for fixing the dust seal 60 to the cylinder head 56 is not necessary, and the cost is reduced.

  The oil flowing through the closed circuit of the traveling continuously variable transmission circuit 1 can be supplied to the oil suspension of the vehicle body, the oil suspension of the seat, or the oil support portion of the brake pedal to absorb vibration.

DESCRIPTION OF SYMBOLS 1 Traveling continuously variable transmission circuit 2 Mowing continuously variable transmission circuit 11 Main hydraulic pump 22 Sub hydraulic pump 23 Shifting diverter valve 40 Emergency check valve 41 Shifting supply line 43 Traveling distribution line 45 Distribution hydraulic block 46 Emergency path 70 Supplementary oil path T Travel clutch operating hydraulic circuit W Main hydraulic circuit

Claims (2)

  A main hydraulic pump (11) for supplying pressure oil to the traveling clutch operation hydraulic circuit (T) and the main hydraulic circuit (W) for performing body posture control and mowing / auger raising / lowering control is provided, and the traveling continuously variable transmission circuit (1) In a combined hydraulic circuit provided with a sub-hydraulic pump (22) for sending pressure oil to the mowing continuously variable transmission circuit (2), a traveling continuously variable transmission circuit for the pressure oil of the sub-hydraulic pump (22) by a variable speed diverter valve (23). (1) and the cutting continuously variable transmission circuit (2), and travels from the transmission supply line (41) and the transmission branching valve (23) for sending pressure oil from the sub hydraulic pump (22) to the transmission branching valve (23). A combine characterized in that a travel distribution line (43) for sending pressure oil to the continuously variable transmission circuit (1) is communicated with an emergency path (46) via an emergency check valve (40) that is released at a predetermined pressure. Hydraulic circuit.   The combine hydraulic circuit according to claim 1, wherein the shift diverter valve (23) and the emergency check valve (40) are provided in an integrally formed distribution hydraulic block (45).

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