Reciprocating low-speed heavy-load hydraulic pump with variable action area

Abstract

A reciprocating low-speed heavy-load hydraulic pump with a variable action area comprises a plurality of hydraulic cylinder units (3) and moving members (1, 2). Two ends of the hydraulic cylinder units (3) are separately connected with the moving members (1, 2) via mechanical structures. The moving members (1, 2) move relative to each other. The hydraulic cylinder unit (3) consists of a hydraulic cylinder (4), a reversing valve (5) and a one-way valve (6). The hydraulic cylinder (4), the reversing valve (5) and the one-way valve (6) are connected with each other via hydraulic pipelines. Based on different magnitudes of driving force, the hydraulic pump can proactively configure and form different combinations of hydraulic cylinder units, and further adjust the size of an equivalent action area. Therefore, even if the magnitude of the driving force changes, it can be ensured that the hydraulic pump consisting of hydraulic cylinder units outputs oil liquid with a relatively stable pressure for use by a subsequently connected system. The reciprocating low-speed heavy-load hydraulic pump with a variable action area is advantageous in high conversion efficiency, a simple system structure and good working stability.

Claims

1. A reciprocating low-speed heavy-load hydraulic pump with variable action area comprising a set of hydraulic cylinder units, a first moving member, and a second moving member, wherein each of the hydraulic cylinder units has two ends, one of the two ends is connected to the first moving member and the other of the two ends is connected to the second moving member via mechanical structures, the hydraulic cylinder units extend and retract to form a relative displacement between the first moving member and the second moving member under an external force, and each of the hydraulic cylinder units includes a respective hydraulic cylinder, a respective reversing valve and a respective one-way valve connected with each other via hydraulic pipelines.

2. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 1, wherein when the reversing valve is in a control position, an oil port A is in communication with an oil port B, and when it is not in the control position, the oil port A is not in communication with the oil port B.

3. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 2, wherein the reversing valve is in the form of a two-position two-way solenoid reversing valve, and that the oil port B is cut off in one direction towards the oil port A.

4. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 2, wherein the reversing valve is in the form of a two-position two-way solenoid reversing valve, and that the oil port A and the oil port B are cut off in two directions.

5. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 1, wherein the hydraulic cylinder is in the form of a single-rod piston cylinder.

6. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 1, wherein the hydraulic cylinder is in the form of a plunger cylinder.

7. The reciprocating low-speed heavy-load hydraulic pump with variable action area according to claim 1, wherein the hydraulic cylinder is in the form of a two-rod piston cylinder.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic view of the principle of the present invention;

(2) FIG. 2 is a schematic view showing the system principle of the hydraulic cylinder units (3);

(3) FIG. 3 is a schematic view showing the system principle of a first embodiment of the hydraulic cylinder units (3);

(4) FIG. 4 is a schematic view showing the system principle of a second embodiment of the hydraulic cylinder units (3);

(5) FIG. 5 is a schematic view showing the system principle of a third embodiment of the hydraulic cylinder units (3).

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

(6) Referring to FIG. 1, a reciprocating low-speed heavy-load hydraulic pump with variable action area comprises a plurality of sets of hydraulic cylinder units (3), a moving member (1), and a moving member (2), characterized in that each of the hydraulic cylinder units (3) has two ends connected with the moving member (1) and the moving member (2) via mechanical structures, respectively, the moving member (1) and the moving member (2) move relatively to each other, each of the hydraulic cylinder units (3) consists of a hydraulic cylinder (4), a reversing valve (5) and a one-way valve (6) connected with each other via hydraulic pipelines.

(7) The operating principle is as follows: there is a relative replacement between the moving member (1) and the moving member (2) under an external force. The hydraulic cylinder units (3) extend and retract reciprocally, suck oil through an oil port D, and converge and output pressure oil through an oil port C. The hydraulic pump can output relatively stable pressure oil by configuring various operation combinations of a different number or different area magnitudes of the hydraulic cylinder units (3) based on different magnitudes of external force.

(8) Referring to FIG. 2, shown is a schematic view of the system principle of the hydraulic cylinder units (3). Each of the hydraulic cylinder units (3) consists of a hydraulic cylinder (4), a reversing valve (5) and a one-way valve (6) connected with each other via hydraulic pipelines. When the reversing valve (5) is in a control position, an oil port A is in communication with an oil port B, and when it is not in the control position, the oil port A is not in communication with the oil port B.

(9) The operating principle is as follows: when the reversing valve (5) is not in the control position, the oil port A is not in communication with the oil port B. When the hydraulic cylinder (4) retracts, the hydraulic cylinder (4) outputs pressure oil through the one-way valve (6) from the oil port C and simultaneously sucks oil from the oil port D; when the hydraulic cylinder (4) extends, oil is outputted from the oil port D and through the reversing valve (5) to the oil port C and is inputted into the hydraulic cylinder (4). If the inputted hydraulic flow is not enough, the hydraulic cylinder (4) sucks oil from a hydraulic oil tank through the port D and the reversing valve (5). When the reversing valve (5) is in a control position, the oil port A is in communication with the oil port B, and the hydraulic cylinder (4) freely extends and retracts and does not output any pressure oil. The one-way valve (6) is mainly used to ensure that all the pressure oil outputted by the hydraulic cylinder units (3) flows to the same location without mutual interference.

(10) Referring to FIG. 3, shown is a schematic view of the system principle of a first embodiment of the hydraulic cylinder units (3). Each of the hydraulic cylinder units (3) mainly consists of a single-rod piston cylinder (4), a two-position two-way solenoid reversing valve (5) and a one-way valve (6).

(11) The operation is as follows: when the electromagnet is not energized, the two-position two-way solenoid reversing valve (5) works in the right position, and at this time, the oil port B is cut off in one direction towards the oil port A. When the single-rod piston cylinder (4) retracts, the rodless chamber of the single-rod piston cylinder (4) thereof outputs pressure oil through the one-way valve (6) from the oil port C and the rod chamber of the single-rod piston cylinder (4) thereof sucks oil from the oil port D; when the single-rod piston cylinder (4) extends, oil is outputted from the rod chamber of the single-rod piston cylinder (4) and is inputted through the two-position two-way solenoid reversing valve (5) into the rodless chamber of the single-rod piston cylinder (4). Since the rodless chamber has a different area from the rod chamber, the rodless chamber of the single-rod piston cylinder (4) will have a change of volume larger than the rod chamber, the single-rod piston cylinder (4) also sucks oil from the oil port D through the two-position two-way solenoid reversing valve (5). When the electromagnet is energized, the two-position two-way solenoid reversing valve (5) works in the left position, the oil port A is in communication with the oil port B, the rod and rodless chambers of the single-rod piston cylinder (4) communicate with each other and both are in communication with the oil port D. At this time, the single-rod piston cylinder (4) freely extends and retracts and does not output any pressure oil.

(12) Referring to FIG. 4, shown is a schematic view of the system principle of a second embodiment of the hydraulic cylinder units (3). Each of the hydraulic cylinder units (3) mainly consists of a plunger cylinder (4), a two-position two-way solenoid reversing valve (5) and a one-way valve (6).

(13) The operation is as follows: when the electromagnet is not energized, the two-position two-way solenoid reversing valve (5) works in the right position, and at this time, the oil port B is cut off in one direction towards the oil port A. When the plunger cylinder (4) retracts, the plunger cylinder (4) outputs pressure oil through the one-way valve (6) from the oil port C; when the plunger cylinder (4) extends, the plunger cylinder (4) sucks oil through the two-position two-way solenoid reversing valve (5) from the oil port D. When the electromagnet is energized, the two-position two-way solenoid reversing valve (5) works in the left position, the oil port A is in communication with the oil port B, the plunger cylinder (4) is in communication with the oil port D. At this time, the plunger cylinder (4) freely extends and retracts and does not output any pressure oil.

(14) Referring to FIG. 5, shown is a schematic view of the system principle of a third embodiment of the hydraulic cylinder units (3). Each of the hydraulic cylinder units (3) mainly consists of a two-rod piston cylinder (4), a two-position two-way solenoid reversing valve (5) and a one-way valve (6).

(15) The operation is as follows: when the electromagnet is not energized, the two-position two-way solenoid reversing valve (5) works in the right position, and at this time, the oil port A and the oil port B are cut off in two directions. When the two-rod piston cylinder (4) moves downward, the lower chamber of the two-rod piston cylinder (4) thereof outputs pressure oil through the one-way valve (6) from the oil port C, and the upper chamber of the two-rod piston cylinder (4) thereof sucks oil through the one-way valve (6) from the oil port D; when the two-rod piston cylinder (4) moves upward, the lower chamber of the two-rod piston cylinder (4) sucks oil through the one-way valve (6) from the oil port D, and the upper chamber of the two-rod piston cylinder (4) outputs pressure oil through the one-way valve (6) from the oil port C. When the electromagnet is energized, the two-position two-way solenoid reversing valve (5) works in the left position, the oil port A is in communication with the oil port B, both the upper and lower chambers of the two-rod piston cylinder (4) are in communication with the oil port D through the one-way valve (6). At this time, the two-rod piston cylinder (4) freely extends and retracts and does not output any pressure oil. If there is oil leakage loss during freely extending and retracting, oil is supplied into the system through the one-way valve (6) from the oil port D.