Hydraulic circuit for loader

Abstract

An optional-attachment-operating direction switching valve is provided in a part of an unloading passage which part is on the upstream of an arm-operating direction switching valve and a bucket-operating direction switching valve. The hydraulic circuit is arranged such that the optional-attachment-operating direction switching valve receives pressure oil from a pressure oil supply passage which branches from the part of the unloading passage on the upstream of the optional-attachment-operating direction switching valve, the arm-operating direction switching valve receives pressure oil from a pressure oil supply passage which branches from a part of the unloading passage which part is between the optional-attachment-operating direction switching valve and the arm-operating direction switching valve, and the bucket-operating direction switching valve receives the pressure oil from a pressure oil supply passage which branches from a part of the unloading passage which part is between the optional-attachment-operating direction switching valve and the bucket-operating direction switching valve.

Claims

1. A hydraulic circuit for a loader, comprising: an unloading passage connected to a hydraulic pump; an arm-operating direction switching valve configured to supply to or exhaust from an arm actuator, pressure oil from the hydraulic pump; a bucket-operating direction switching valve configured to supply to or exhaust from a bucket actuator, the pressure oil from the hydraulic pump; and an optional-attachment-operating direction switching valve configured to supply to or exhaust from an attachment actuator configured to actuate an optional attachment, the pressure oil from the hydraulic pump, wherein, the optional-attachment-operating direction switching valve is provided in a part of the unloading passage on the upstream of the arm-operating direction switching valve and the bucket-operating direction switching valve, the optional-attachment-operating direction switching valve receives the pressure oil from an optional-attachment-operating pressure oil supply passage which branches from a part of the unloading passage on the upstream of the optional-attachment-operating direction switching valve, the arm-operating direction switching valve receives the pressure oil from an arm-operating pressure oil supply passage which branches from a part of the unloading passage between the optional-attachment-operating direction switching valve and the arm-operating direction switching valve, the bucket-operating direction switching valve receives the pressure oil from a bucket-operating pressure oil supply passage which branches from a part of the unloading passage between the optional-attachment-operating direction switching valve and the bucket-operating direction switching valve, a bypass passage is provided to connect the part of the unloading passage on the upstream of the optional-attachment-operating direction switching valve with either the part of the unloading passage between the optional-attachment-operating direction switching valve and the arm-operating direction switching valve or the part of the unloading passage between the optional-attachment-operating direction switching valve and the bucket-operating direction switching valve, and a flow rate control valve which allows a predetermined flow rate of the pressure oil to flow in the bypass passage is provided in the bypass passage.

2. The hydraulic circuit according to claim 1, wherein, a distributing valve is provided in the part of the unloading passage on the upstream of the optional-attachment-operating direction switching valve, and the distributing valve is configured to change flow distribution between the pressure oil flowing in the unloading passage and the pressure oil flowing in the optional-attachment-operating pressure oil supply passage, in accordance with a load pressure of the attachment actuator.

3. The hydraulic circuit according to claim 2, wherein, the flow rate control valve includes: a variable throttle provided in the bypass passage; and a bypass valve to which pressures on the upstream and the downstream of the variable throttle are input and which is configured to keep the pressures on the upstream and the downstream of the variable throttle to be constant.

4. The hydraulic circuit according to claim 1, wherein, the flow rate control valve includes: a variable throttle provided in the bypass passage; and a bypass valve to which pressures on the upstream and the downstream of the variable throttle are input and which is configured to keep the pressures on the upstream and the downstream of the variable throttle to be constant.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a hydraulic circuit diagram of a stack valve for a loader of an embodiment of the present invention.

(2) FIG. 2 is an enlarged view of an upper part of the hydraulic circuit shown in FIG. 1, in which the state of the middle stroke region of the spool of the optional-attachment-operating direction switching valve is indicated by dotted lines.

(3) FIG. 3 is a hydraulic circuit diagram showing a state in which the spool of the optional-attachment-operating direction switching valve has been moved from the middle stroke region shown in FIG. 2 to the full stroke position.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

(4) The following will describe an embodiment of the present invention with reference to figures.

(5) (Circuit Diagram of Hydraulic Circuit)

(6) Referring to FIGS. 1 to 3, a hydraulic circuit 1 of a stack valve for a loader of the embodiment of the present invention will be described. The hydraulic circuit 1 is a hydraulic circuit including direction switching valves 6, 7, and 8 which are provided in series in an unloading passage 21 which is connected to a hydraulic pump 2. This hydraulic circuit 1 shown in FIG. 1 may be understood as a stack valve including direction switching valves 6, 7, and 8 provided in series. In such a case, indicated by the reference numeral 1 is a stack valve.

(7) The loader which is not illustrated is provided with attachments such as an arm attached to the front part of the loader main body and a bucket attached to the leading end portion of the arm. In addition to these attachments, an optional attachment is attached to the loader which employs the hydraulic circuit 1 of the present embodiment. Examples of the optional attachment includes a rotary blade for mowing and a drill. The explanation below presupposes that a rotary blade for mowing is attached to the loader as an optional attachment. The optional attachment is not limited to the rotary blade for mowing and the drill.

(8) The arm which is not illustrated is moved by an arm cylinder 4 (arm actuator). The arm moves up as pressure oil is supplied to a head-side chamber 4a of the arm cylinder 4, and moves down as the pressure oil is supplied to a rod-side chamber 4b. The bucket is moved by a bucket cylinder 5 (bucket actuator). The bucket performs a dumping action (forward tilting) as the pressure oil is supplied to a head-side chamber 5a of the bucket cylinder 5, and performs a scooping action (backward tilting) as the pressure oil is supplied to a rod-side chamber 5b.

(9) The rotary blade is operated by a hydraulic motor 3 (optional attachment actuator) and rotates as the pressure oil is supplied to the hydraulic motor 3.

(10) As shown in FIG. 1, the hydraulic circuit 1 of the present embodiment includes an arm-operating direction switching valve 7, a bucket-operating direction switching valve 8, an optional-attachment-operating direction switching valve 6, a distributing valve 9, and a flow rate control valve 10. The hydraulic circuit 1 is a circuit which is connected to a hydraulic pump 2, the arm cylinder 4 for moving the arm, the bucket cylinder 5 for moving the bucket, the hydraulic motor 3 for rotating the rotary blade, and a tank 13 to which the oil returns.

(11) The optional-attachment-operating direction switching valve 6 is provided in a part of the unloading passage 21 which is on the upstream of the arm-operating direction switching valve 7 and the bucket-operating direction switching valve 8. The arm-operating direction switching valve 7 is provided in a part of the unloading passage 21 which is on the upstream of the bucket-operating direction switching valve 8. The arm-operating direction switching valve 7 may be provided in a part of the unloading passage 21 on the downstream of the bucket-operating direction switching valve 8.

(12) The distributing valve 9 is provided in a part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6. The distributing valve 9 is preferably provided as an element constituting the hydraulic circuit of the present invention but is not an essential element.

(13) A part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6 and the distributing valve 9 is connected, by a bypass passage 25, with a part of the unloading passage 21 between the optional-attachment-operating direction switching valve 6 and the arm-operating direction switching valve 7. On this bypass passage 25 is provided a flow rate control valve 10. Alternatively, the part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6 and the distributing valve 9 may be connected, by the bypass passage 25, with a part of the unloading passage 21 between the arm-operating direction switching valve 7 and the bucket-operating direction switching valve 8, and the flow rate control valve 10 may be provided on this bypass passage 25.

(14) When the arm-operating direction switching valve 7 is provided in the part of the unloading passage 21 on the downstream of the bucket-operating direction switching valve 8, for example, the part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6 and the distributing valve 9 is connected, by the bypass passage 25, with a part of the unloading passage 21 between the optional-attachment-operating direction switching valve 6 and the bucket-operating direction switching valve 8, and the flow rate control valve 10 is provided on this bypass passage 25. Alternatively, the part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6 and the distributing valve 9 may be connected, by the bypass passage 25, with the part of the unloading passage 21 between the bucket-operating direction switching valve 8 and the arm-operating direction switching valve 7, and the flow rate control valve 10 may be provided on this bypass passage 25. The bypass passage 25 and the flow rate control valve 10 are preferably provided as elements constituting the hydraulic circuit of the present invention, but are not essential elements.

(15) <Arm-Operating Direction Switching Valve>

(16) The arm-operating direction switching valve 7 is a three-position direction switching valve configured to supply or exhaust, to or from the arm cylinder 4, pressure oil from the exhaust hydraulic pump 2. To this arm-operating direction switching valve 7, pressure oil is supplied from a pressure oil supply passage 23 (arm-operating pressure oil supply passage) which branches from the part of the unloading passage 21 between the optional-attachment-operating direction switching valve 6 and the arm-operating direction switching valve 7.

(17) <Bucket-Operating Direction Switching Valve>

(18) The bucket-operating direction switching valve 8 is a three-position direction switching valve which is configured to supply or exhaust, to or from the bucket cylinder 5, pressure oil from the hydraulic pump 2. To this bucket-operating direction switching valve 8, pressure oil is supplied from a pressure oil supply passage 24 (bucket-operating pressure oil supply passage) which branches from the part of the unloading passage 21 between the arm-operating direction switching valve 7 and the bucket-operating direction switching valve 8.

(19) <Optional-Attachment-Operating Direction Switching Valve>

(20) The optional-attachment-operating direction switching valve 6 is a three-position direction switching valve which is configured to supply or exhaust, to or from the hydraulic motor 3, pressure oil from the hydraulic pump 2. To this optional-attachment-operating direction switching valve 6, pressure oil is supplied from a pressure oil supply passage 22 (optional attachment pressure oil supply passage) which branches, via the distributing valve 9, from the part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6. When the distributing valve 9 is not provided, the pressure oil supply passage 22 (optional attachment pressure oil supply passage) directly branches from the part of the unloading passage 21 on the upstream of the optional-attachment-operating direction switching valve 6.

(21) <Distributing Valve>

(22) The distributing valve 9 is a three-position valve which is configured to change the flow distribution between the pressure oil flowing in the unloading passage 21 and the pressure oil flowing in the pressure oil supply passage 22, in accordance with the load pressure on the hydraulic motor 3. To one of two chambers of the distributing valve 9 (i.e., a chamber on the position 9c side), the pressure of the pressure oil supply passage 22 heading for the hydraulic motor 3 (i.e., the pump pressure of the hydraulic pump 2 and the hydraulic pressure between the distributing valve 9 and the optional-attachment-operating direction switching valve 6) is input. To the other one of the chambers of the distributing valve 9 (i.e., a chamber on the position 9a side), the pressure of a tank passage 25 is input when the optional-attachment-operating direction switching valve 6 is at the position 6b (neutral position) (see FIG. 1). In the other one of the chambers of the distributing valve 9 (i.e., a changer on the position 9a side), a spring 26 is provided.

(23) As shown in FIG. 3, when the optional-attachment-operating direction switching valve 6 is at the position 6a or the position 6c (full stroke position), the load pressure of the hydraulic motor 3 is input to the other one of the chambers of the distributing valve 9 (i.e., a changer on the position 9a side). Furthermore, as shown in FIG. 2, also when the optional-attachment-operating direction switching valve 6 is at the middle stroke region 6x or 6y, the load pressure of the hydraulic motor 3 is input to the other one of the chambers of the distributing valve 9 (i.e., a chamber on the position 9a side).

(24) <Flow Rate Control Valve>

(25) The flow rate control valve 10 is a valve configured to allow a predetermined amount of pressure oil to flow in the bypass passage 25. This flow rate control valve 10 is constituted by a variable throttle 11 provided on the bypass passage 25 and a bypass valve 12 which receives the pressures on the upstream and downstream of the variable throttle 11 and keeps the difference between the pressures on the upstream and downstream of the variable throttle 11 to be constant. To one of two chambers of the bypass valve 12 (i.e., a chamber on the position 12b side), the pressure on the upstream of the variable throttle 11 in the bypass passage 25 is input. To the other one of the chambers of the bypass valve 12 (i.e., a chamber on the position 12a side), the pressure on the downstream of the variable throttle 11 is input. In the other chamber of the bypass valve 12 (i.e., a chamber on the position 12a side), a spring 27 is provided.

(26) (Operation of Hydraulic Circuit (Effects))

(27) (Case Where Optional-Attachment-Operating Direction Switching Valve 6 is at Neutral Position (Position 6b))

(28) The operation of the hydraulic circuit 1 will be described. Assume that the operator does not operate the hydraulic motor 3 which is configured to rotate the rotary blade, i.e., the operator does not operate the optional-attachment-operating direction switching valve 6. In this case, the optional-attachment-operating direction switching valve 6 is at the neutral position (position 6b) (see FIG. 1). Because the difference between the hydraulic pressures in the one chamber (on the position 9c side) and the other chamber (on the position 9a side) of the distributing valve 9 is higher than the spring force of the spring 26, the distributing valve 9 is moved to the position 9c. For this reason, pressure oil from the hydraulic pump 2 flows in the unloading passage 21.

(29) (Case Where Optional-Attachment-Operating Direction Switching Valve 6 is at Middle Stroke Region 6x or 6y)

(30) Assume that the operator simultaneously operates the arm cylinder 4 for moving the arm and the hydraulic motor for rotating the rotary blade, i.e., simultaneously operates the arm-operating direction switching valve 7 and the optional-attachment-operating direction switching valve 6. In this connection, assume further that the optional-attachment-operating direction switching valve 6 is not at the full stroke position but, as shown in FIG. 2, at the middle stroke region 6x (or 6y) (see FIG. 2). In this case, because the optional-attachment-operating direction switching valve 6 is provided in a part of the unloading passage 21 on the upstream of the arm-operating direction switching valve 7, the pressure oil is more likely to flow into the optional-attachment-operating direction switching valve 6 than to flow into the arm-operating direction switching valve 7. On this account, the operation of the optional-attachment-operating direction switching valve 6 is preferred to the operation of the arm-operating direction switching valve 7. This improves the operability of the rotary blade attached to the loader. It is noted that the same effect is achieved when the operator simultaneously operates the bucket cylinder 5 and the hydraulic motor 3. (The same holds true for the case where the optional-attachment-operating direction switching valve 6 is at the full stroke position).

(31) In regard to the above, the distributing valve 9 is balanced at a position where the difference between the pressure in the pressure oil supply passage 22 (i.e., the pump pressure of the hydraulic pump 2 and the hydraulic pressure between the distributing valve 9 and the optional-attachment-operating direction switching valve 6) and the load pressure of the hydraulic motor 3 (i.e., the pressure on the downstream of the throttle 28 of the optional-attachment-operating direction switching valve 6) is equal to the spring force of the spring 26 (i.e., a position between the positions 9a, 9b, and 9c).

(32) <Case Where Load Pressure of Hydraulic Motor 3 Becomes High>

(33) The pressure in the chamber on the position 9a side of the distributing valve 9 becomes high and hence the distributing valve 9 moves to the position 9a side. Because the distributing valve 9 moves in a direction in which the area of the passage toward the unloading passage 21 is decreased, the pressure in the pressure oil supply passage 22 (i.e., the pump pressure of the hydraulic pump and the hydraulic pressure between the distributing valve 9 and the optional-attachment-operating direction switching valve 6) increases. The distributing valve 9 is balanced at a position where the difference between the hydraulic pressures applied to one and the other chambers of the distributing valve 9 (i.e., chambers on the position 9c side and on the position 9a side) is equal to the spring force of the spring 26.

(34) <Case Where Load Pressure of Hydraulic Motor 3 Becomes Low>

(35) The pressure in the chamber of the distributing valve 9 on the position 9a side becomes low, and hence the distributing valve 9 moves to the position 9c side. Because the distributing valve 9 moves in a direction in which the area of the passage toward the unloading passage 21 is increased, the pressure in the pressure oil supply passage 22 (i.e., the pump pressure of the hydraulic pump and the hydraulic pressure between the distributing valve 9 and the optional-attachment-operating direction switching valve 6) decreases. The distributing valve 9 is balanced at a position where the difference between the hydraulic pressures applied to one and the other chambers of the distributing valve 9 (chambers on the position 9c side and on the position 9a side) is equal to the spring force of the spring 26.

(36) As such, as the difference between the pressures on the upstream and downstream of the throttle 28 of the optional-attachment-operating direction switching valve 6 is always kept constant by the distributing valve 9, the pressure oil is supplied to the hydraulic motor 3 at a constant flow rate (the flow distribution between the pressure oil flowing in the unloading passage 21 and the pressure oil flowing in the pressure oil supply passage 22 is changed), even if the load pressure of the hydraulic motor 3 changes (i.e., in accordance with the load pressure of the hydraulic motor 3).

(37) The throttle 28 is formed in such a way that the passage of the pressure oil is tightened on account of the presence of the optional-attachment-operating direction switching valve 6 at the middle stroke region 6x.

(38) (Case Where Optional-Attachment-Operating Direction Switching Valve 6 is at Full Stroke Position (Position 6a or 6c))

(39) Assume that the operator sets the optional-attachment-operating direction switching valve 6 at the full stroke position (see FIG. 3). In this regard, the present embodiment assumes that the aperture area on the meter-in side of the optional-attachment-operating direction switching valve 6 at the full stroke position (position 6a) is not tightened. In this case, the difference between the pressures before and after the pressure oil passes the optional-attachment-operating direction switching valve 6 is smaller than the cracking force of the spring 26 of the distributing valve 9. The distributing valve 9 therefore takes the position 9a and the pressure oil no longer flows into a part of the unloading passage 21 on the downstream of the distributing valve 9. All of the pressure oil from the hydraulic pump flows into the optional-attachment-operating direction switching valve 6.

(40) When the aperture area on the meter-in side of the optional-attachment-operating direction switching valve 6 at the full stroke position (position 6a) is tightened (i.e., a throttle is provided), the distributing valve 9 operates in the same way as in the case where the optional-attachment-operating direction switching valve 6 is at the middle stroke region 6x (see FIG. 2). (The same holds true for the full stroke position (position 6c)).

(41) <Effect of Distributing Valve>

(42) Because the distributing valve 9 is provided in the hydraulic circuit 1, the pressure oil supplied from the hydraulic pump 2 flows into the hydraulic motor 3 at a constant flow rate in accordance with the degree of opening of the optional-attachment-operating direction switching valve 6, irrespective of a change in the load pressure on the hydraulic motor 3, and the pressure oil flows into the arm cylinder 4 or the bucket cylinder 5 at a predetermined flow rate at least.

(43) <Effects of Flow Rate Control Valve>

(44) In addition to the above, in the present embodiment the hydraulic circuit 1 is provided with the bypass passage 25 and the flow rate control valve 10 which have been described above. Assume that the operator simultaneously operates the arm-operating direction switching valve 7 and the optional-attachment-operating direction switching valve 6. Assume further that the load pressure on the arm cylinder 4 is changed. In this case, even if the load pressure on the arm cylinder 4 is changed, redundant oil returns from the unloading passage 21 to the tank 13, because the difference between the pressures on the upstream and downstream of the variable throttle 11 provided on the bypass passage 25 is kept at constant by the bypass valve 12. To put it differently, because the bypass passage 25 and the flow rate control valve 10 are provided in the hydraulic circuit 1, the pressure oil supplied from the hydraulic pump 2 flows into the arm cylinder 4 at a constant flow rate in accordance with the degree of opening of the arm-operating direction switching valve 7, irrespective of a change in the load pressure on the arm cylinder 4. It is noted that the same effect is achieved when the operator simultaneously operates the bucket cylinder 5 and the hydraulic motor 3.

(45) In addition to the above, because the throttle is arranged to be variable (variable throttle 11), the balance of the amount of the pressure oil supplied to the arm cylinder 4 (or the bucket cylinder 5), when the arm cylinder 4 (or the bucket cylinder 5) and the hydraulic motor 3 are simultaneously operated is changeable at will.