CN117212268A - Hydraulic system of four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder and control method thereof - Google Patents
Hydraulic system of four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder and control method thereof Download PDFInfo
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Abstract
A hydraulic system of a four-quadrant working closed pump driving single-rod double-acting piston hydraulic cylinder and a control method thereof. According to the system disclosed by the invention, when the I, II quadrant works, the oil return port of the closed pump is supplemented by adopting the open type constant-pressure variable pump, so that the flow rate of the oil return port of the closed pump is the same as the flow rate of the oil outlet, and the closed pump is ensured to work normally. The oil supplementing flow is the oil supplementing flow required by the system, and no throttling loss and overflow loss exist. When the III and IV quadrants work, the overflow valve is adopted to realize the oil drain from the rodless cavity of the hydraulic cylinder to the oil tank, so that the oil return port flow and the oil outlet flow of the closed pump are the same, and the normal work of the closed pump is ensured. The oil drainage flow is the oil drainage flow required by the system, and no throttling loss exists. The pressure transmitter is used for detecting the pressure of a rodless cavity and a rod cavity of the hydraulic cylinder, calculating the size of a load and judging the direction of the load, and judging and switching working quadrants by combining the movement direction of a piston rod, so that the hydraulic cylinder is accurate in detection, rapid in switching, small in impact and stable in operation.
Description
Technical Field
The invention relates to the technical field of hydraulic transmission of mechanical equipment, in particular to a driving mechanism of a four-quadrant working closed pump driving single-rod double-acting piston hydraulic cylinder on the equipment.
Background
Various mechanical devices widely use single-rod double-acting piston hydraulic cylinders, and the mechanism is driven to move by controlling the expansion and contraction direction and speed of a piston rod of the hydraulic cylinder.
The hydraulic cylinder is a single-rod double-acting piston cylinder, and the hydraulic speed regulation loop mode is generally as follows:
the open valve-controlled throttling speed regulation loop uses a constant displacement pump for oil supply, and is matched with a switch-type reversing valve and a throttle valve or a proportional reversing valve to realize reversing and throttling speed regulation, so that overflow loss and throttling loss are caused;
the open valve-controlled volume throttling speed regulating loop uses a constant pressure variable pump to supply oil, and is matched with a switch type reversing valve and a throttle valve or a proportional reversing valve to realize reversing and throttling speed regulation, so that throttling loss exists.
The open pump control volume speed regulation loop uses a variable pump to regulate speed, and is matched with a switch type reversing valve to realize reversing, so that overflow loss and throttling loss are avoided.
In the speed regulation mode, the piston rod can only drive a load with the action direction opposite to the movement direction of the piston rod (the piston rod is pressed when the piston rod is extended and the piston rod is pulled when the piston rod is retracted), if the load with the action direction same as the movement direction of the piston rod is required to be driven (the piston rod is pulled when the piston rod is extended and the piston rod is pressed when the piston rod is retracted), a balance valve or a throttle valve is connected to an oil path of the hydraulic cylinder, the balance valve or the throttle valve has throttling loss and heating, and the balance valve vibrates relatively more when in operation. Changing the movement direction of the mechanism requires switching the valve position of the reversing valve, and the action of the reversing valve is stopped, delayed and impacted when the reversing valve passes through the middle position of the reversing valve in the switching process.
Because the flow rates of the oil inlet and the oil outlet of the closed pump are the same, a double-rod double-acting piston hydraulic cylinder (called a double-rod hydraulic cylinder for short) is usually driven, the effective areas of two cavities of the piston are the same, and the flow rates of the two cavities are the same. The oil outlet and the oil return port of the closed pump are directly connected with the oil ports of the two cavities of the hydraulic cylinder, and the reversing valve is not arranged in the middle, so that the local loss of the reversing valve is avoided. When the system works normally, no overflow loss and throttle loss exist, and the system efficiency is high. The closed pump can continuously change the flow and the flow direction by changing the displacement, and when the direction is switched, the flow is changed from large to small to zero, and the other direction is changed from small to large, so that the reversing delay and the impact are avoided, and the driving control is accurate and sensitive. If a load with the same action direction as the movement direction of the piston rod is required to be driven (the piston rod is pulled when the piston rod is extended and the piston rod is pressed when the piston rod is retracted), the hydraulic cylinder can reversely drive the closed pump, and the closed pump reversely drives the motor or the engine to realize reverse towing braking, so that reverse towing braking power generation can be realized for some motor systems, and the energy consumption is reduced.
The double-rod hydraulic cylinder can bidirectionally output rods, and has large occupied space and high manufacturing cost. In practical application, a single-rod double-acting piston hydraulic cylinder (called a single-rod hydraulic cylinder for short) is only needed in a common mechanism. The effective areas of the rod cavity and the rodless cavity of the single-rod-outlet hydraulic cylinder are different, and the corresponding flow of the rod cavity is smaller than the flow of the rodless cavity under the same movement speed of the piston rod. Because of unbalanced flow, the closed pump and the single-rod hydraulic cylinder cannot be directly connected for use. According to the movement direction and the load direction of the piston rod, the working condition of the hydraulic cylinder can be divided into four quadrants. If the closed pump is required to drive the single-rod hydraulic cylinder, when the hydraulic cylinder works in four quadrants, the problems of oil supplementing of the closed pump and oil draining of the hydraulic cylinder are solved according to the movement direction of the piston rod. In the same direction movement process of the piston rod, the load direction can be changed, the system needs to detect and judge the change of the load direction in real time, and meanwhile, the system can be switched to the corresponding quadrant operation to ensure the normal operation of the system.
The existing technical literature related to a closed pump driving single-rod hydraulic cylinder only analyzes the working condition of a single quadrant, and a complete and specific control method for switching the quadrant working of a closed pump driving single-rod piston hydraulic cylinder working in four quadrants is not provided.
Disclosure of Invention
The invention provides a hydraulic system of a four-quadrant working closed pump driving single-rod double-acting piston hydraulic cylinder.
The technical scheme adopted by the invention is as follows:
the hydraulic system comprises a main pump 1, an oil supplementing pump 2, a hydraulic cylinder 3, a first reversing valve 4, a first overflow valve 5, a second overflow valve 6, a second reversing valve 7, a third reversing valve 8, a third overflow valve 9, a fourth overflow valve 10, a first pressure transmitter 11 and a second pressure transmitter 12.
The main pump 1 is a closed swash plate electric proportion bidirectional variable pump and comprises proportion electromagnets m1 and m2 for controlling displacement. When m1 is electrified, the swashplate deflects positively, and the oil is returned from the port A and the port B of the main pump 1. And when m2 is electrified, the swashplate reversely deflects, and the oil is returned from the oil outlet A of the port B of the main pump 1. The flow is in direct proportion to the current of the proportional electromagnets m1 and m2, and the flow of the oil outlet is the same as the flow of the oil return port.
The oil supplementing pump 2 is an open type swash plate constant pressure variable pump, the pressure of the outlet P is always the same as the pressure of the pressure control port X, and the flow provided by the outlet P is the flow required by the system.
The hydraulic cylinder 3 is a single-rod double-acting piston hydraulic cylinder and is used for driving a load. The area of the rod cavity is A2, the area of the rodless cavity is A1, and the area ratio coefficient
The first reversing valve 4 is a two-position four-way electromagnetic reversing valve and comprises an electromagnet m3.
The first relief valve 5 is a low flow direct acting relief valve, the set pressure is Pbmax, determined by the maximum reverse load against extension of the piston rod.
The second relief valve 6 is a small flow direct acting relief valve, the set pressure is Pbmin, and is determined according to the minimum oil supplementing pressure of the system (generally 2.5 Mpa).
The second reversing valve 7 is a two-position two-way electro-hydraulic reversing valve and comprises an electromagnet m4.
The third reversing valve 8 is a three-position four-way electro-hydraulic reversing valve and comprises electromagnets m5 and m6.
The third relief valve 9 is a pilot relief valve with a large flow rate, and the set pressure is Pxmax, and is determined by overcoming the maximum forward load when the piston rod is retracted.
The fourth relief valve 10 is a pilot relief valve with a large flow rate, and the set pressure is Pxmax and is determined by the minimum relief pressure of the system (typically 2.5 Mpa).
The first pressure transmitter 11 detects the rod cavity pressure P2 of the hydraulic cylinder 3.
The second pressure transmitter 12 detects the rodless cavity pressure P1 of the hydraulic cylinder 3.
The port B of the main pump 1 is connected with the port B of the hydraulic cylinder 3, the first pressure transmitter 11 and the port A of the second reversing valve 7. The port A of the main pump 1 is connected with the port A of the hydraulic cylinder 3, the second pressure transmitter 12 and the port P of the third reversing valve 8.
The port A of the first reversing valve 4 is connected with the port P of the first overflow valve 5, the port B of the first reversing valve 4 is connected with the port P of the second overflow valve 6, and the port P of the first reversing valve 4 is connected with the port X of the oil supplementing pump 2.
The P port of the oil supplementing variable pump 2 is connected with the P port of the second reversing valve 7.
The A port of the third reversing valve 8 is connected with the P port of the third overflow valve 9, and the B port of the third reversing valve 8 is connected with the P port of the fourth overflow valve 10.
The S port of the oil supplementing pump 2, the T port of the first reversing valve 4, the T port of the third reversing valve 8, the T port of the first overflow valve 5, the T port of the second overflow valve 6, the T port of the third overflow valve 9 and the T port of the fourth overflow valve 10 are connected with an oil tank.
And when m3 is powered off, the P port of the second overflow valve 6 is communicated with the X port of the oil supplementing pump 2. And when m3 is electrified, the P port of the first overflow valve 5 is communicated with the X port of the oil supplementing pump 2. And when m4 is electrified, the P port of the oil supplementing pump 2 is communicated with the B port of the main pump 1. When m5 is electrified, the port P of the fourth relief valve 10 is communicated with the port A of the main pump 1. When m6 is electrified, the port P of the third relief valve 9 is communicated with the port A of the main pump 1.
The hydraulic system schematic is shown in fig. 1.
The invention has the following effects and benefits:
when the first quadrant and the second quadrant work, the open constant-pressure variable pump is adopted to supplement oil to the oil return port of the closed pump, so that the flow rate of the oil return port of the closed pump is the same as the flow rate of the oil outlet, and the closed pump is ensured to work normally. The oil supplementing flow is the oil supplementing flow required by the system, and no throttling loss and overflow loss exist.
When the III and IV quadrants work, the overflow valve is adopted to realize the oil drain from the rodless cavity of the hydraulic cylinder to the oil tank, so that the oil return port flow and the oil outlet flow of the closed pump are the same, and the normal work of the closed pump is ensured. The oil drainage flow is the oil drainage flow required by the system, and no throttling loss exists.
The pressure transmitter is used for detecting the pressure of a rodless cavity and a rod cavity of the hydraulic cylinder, calculating the size of a load, judging the direction of the load, combining the movement direction of a piston rod, judging and switching working quadrants, and the hydraulic cylinder is accurate in detection, rapid in switching, small in impact and stable in operation.
Drawings
Fig. 1 is a schematic diagram of a hydraulic system.
Fig. 2 is a schematic diagram of the four-quadrant operation of the hydraulic cylinder.
Fig. 3 is a hydraulic cylinder four-quadrant work electromagnet action table.
Fig. 4 is a schematic diagram of the hydraulic principle when the hydraulic cylinder is deactivated.
Fig. 5 is a schematic diagram of the hydraulic principle of the hydraulic cylinder in quadrant I.
Fig. 6 is a schematic diagram of the hydraulic principle of the hydraulic cylinder in quadrant II.
Fig. 7 is a schematic diagram of the hydraulic principle of the working of the third quadrant of the hydraulic cylinder.
Fig. 8 is a schematic diagram of the hydraulic principle of the hydraulic cylinder in quadrant IV.
The drawings include: the hydraulic system comprises a main pump 1, an oil supplementing pump 2, a hydraulic cylinder 3, a first reversing valve 4, a first overflow valve 5, a second overflow valve 6, a second reversing valve 7, a third reversing valve 8, a third overflow valve 9, a fourth overflow valve 10, a first pressure transmitter 11 and a second pressure transmitter 12.
Detailed Description
The following describes specific embodiments of the present invention in detail with reference to the technical scheme and the accompanying drawings.
As shown in fig. 2, when the hydraulic cylinder works, the piston rod extends to move forward (indicated as v+), the piston rod retracts to move backward (indicated as v+), the load presses the piston rod to load forward (indicated as f+), and the load pulls the piston rod to load backward (indicated as f+), so that four working quadrants of the hydraulic cylinder are formed. Wherein quadrants I and II are forward motion, and switching between quadrants I and II occurs during motion if the load direction changes. Wherein quadrants III and IV are reversed, and switching between quadrants III and IV occurs during movement if the load direction changes.
As shown in fig. 3, the electromagnet is powered on and off under each working condition when the hydraulic system works, + represents power on, and-represents power off, m1 and m2 are proportional electromagnets, and the rest is a switch electromagnet.
When the hydraulic cylinder is stopped: as shown in FIG. 4, all electromagnets are powered off, the swash plate of the main pump 1 returns to zero, zero displacement is achieved, the ports A and B of the main pump 1 have zero flow, and the hydraulic cylinder 3 stops acting.
Quadrant I operation of the hydraulic cylinder: as shown in fig. 5, when the electromagnets m1 and m4 are energized, the outflow flow of port a of the main pump 1 is Q, the outflow flow of port a of the main pump enters the rodless chamber of the hydraulic cylinder 3, the piston rod extends, the outflow flow of the rod chamber is kQ, the inflow flow of port B of the main pump 1 is Q, and the oil supplementing pump 2 supplies the oil supplementing flow (1-k) Q to port B of the main pump 1. The port P of the second relief valve 6 is connected to the pressure control port X of the supplemental pump 2, and the pump port pressure of the supplemental pump 2, i.e., the rod cavity pressure of the hydraulic cylinder 3, is stabilized to Pbmin. According to the force balance on the piston rod, F=P1.A1-P2.A2=P1.A1-Pbmin.A2 is more than or equal to 0 in the quadrant, wherein P1 is the rodless cavity pressure of the hydraulic cylinder 3, A1 is the effective area of the rodless cavity of the hydraulic cylinder 3, P2 is the rod cavity pressure of the hydraulic cylinder 3, A2 is the effective area of the rod cavity of the hydraulic cylinder 3,if F < 0, the operation is switched to the quadrant II operation. Summary of the working principles of quadrant I: the rodless cavity pressure P1 of the hydraulic cylinder 3 overcomes the forward load F, the rod cavity pressure P2 is kept to be the minimum oil supplementing pressure Pbmin, and meanwhile, the port B of the main pump 1 is supplemented with oil.
And (3) working in a second quadrant of the hydraulic cylinder: as shown in fig. 6, when the electromagnets m1, m3 and m4 are energized, the outflow flow of port a of the main pump 1 is Q, the outflow flow of the rod-free cavity entering the hydraulic cylinder 3, the piston rod extends, the outflow flow of the rod-free cavity is kQ, the inflow flow of port B of the main pump 1 is Q, and the oil supplementing pump 2 supplies the oil supplementing flow (1-k) Q to port B of the main pump 1. The P port of the first relief valve 5 is connected to the pressure control port X of the supplemental pump 2, and the pump port pressure of the supplemental pump 2, i.e., the rod-side cavity pressure of the hydraulic cylinder 3, is stabilized to Pbmax. In this quadrant, f=p1·a1-p2·a2=p1·a1-pbmax·a2 < 0, depending on the force balance on the piston rod. If F is more than or equal to 0, switching to the quadrant I operation. Summary of quadrant II working principles: the rod cavity pressure P2 of the hydraulic cylinder 3 is increased and maintained to Pbmax to overcome the reverse load F, and the port B of the main pump 1 is replenished with oil. The maximum reverse load that can be overcome in this quadrant is f= -p2·a2= -pbmax·a2, where p1=0.
And (3) working in a third quadrant of the hydraulic cylinder: as shown in fig. 7, the electromagnets m2 and m5 are electrified, the outflow flow of the port B of the main pump 1 is Q, the outflow flow of the rodless cavity enters the rod cavity of the hydraulic cylinder 3, the piston rod is retracted, and the outflow flow of the rodless cavity isThe inflow flow of the port A of the main pump 1 is Q, and the outflow flow from the port A of the hydraulic cylinder 3 to the oil tank through the port P of the fourth overflow valve 10 is +.>The pressure of the port A of the main pump 1, namely the rodless cavity of the hydraulic cylinder 3, is stabilized to be Pxmin. In this quadrant, f=p1·a1-p2·a2=pxmin·a1-p2·a2, depending on the force balance on the piston rod, is less than or equal to 0. If F > 0, then switch to quadrant IV operation. Summary of the working principles of quadrant III: the rod cavity pressure P2 of the hydraulic cylinder 3 overcomes the reverse load F, and the rodless cavity pressure P1 is kept to be the minimum oil drainage pressure Pxmin, and meanwhile oil is drained to an opening A of the hydraulic cylinder 3.
Quadrant IV operation of the hydraulic cylinder: as shown in fig. 8, the electromagnets m2 and m6 are electrified, the outflow flow of the port B of the main pump 1 is Q, the outflow flow of the rodless cavity enters the rod cavity of the hydraulic cylinder 3, the piston rod is retracted, and the outflow flow of the rodless cavity isThe inflow flow of the port A of the main pump 1 is Q, and the outflow flow from the port A of the hydraulic cylinder 3 to the oil tank through the port P of the third overflow valve 9 is +.>The port a of the main pump 1, i.e. the rodless cavity of the hydraulic cylinder 3, is pressure stabilized at Pxmax. F=p1·a1-p2·a2=pxmax·a1-p2·a2 > 0, depending on the force balance on the piston rod. If F is less than or equal to 0,then a switch is made to quadrant III operation. Summary of quadrant IV operating principle: the rodless cavity pressure P1 of the hydraulic cylinder 3 is raised and maintained at Pxmax to overcome the forward load F while draining the port a of the hydraulic cylinder 3. The maximum forward load that can be overcome in this quadrant is f=p1·a1=pxmax·a1, where p2=0.
Claims (7)
1. The hydraulic system of the four-quadrant working closed pump driving single-rod double-acting piston hydraulic cylinder is characterized by comprising a main pump (1), an oil supplementing pump (2), a hydraulic cylinder (3), a first reversing valve (4), a first overflow valve (5), a second overflow valve (6), a second reversing valve (7), a third reversing valve (8), a third overflow valve (9), a fourth overflow valve (10), a first pressure transmitter (11) and a second pressure transmitter (12);
the main pump (1) is a closed swash plate electric proportion bidirectional variable pump and comprises proportion electromagnets m1 and m2 for controlling displacement; the oil supplementing pump (2) is an open type swash plate constant pressure variable pump; the hydraulic cylinder (3) is a single-rod double-acting piston hydraulic cylinder; the first reversing valve (4) is a two-position four-way electromagnetic reversing valve and comprises an electromagnet m3; the first overflow valve (5) is a low-flow direct-acting overflow valve, and the set pressure is Pbmax; the second overflow valve (6) is a direct-acting overflow valve with small flow, and the set pressure is Pbmin; the second reversing valve (7) is a two-position two-way electro-hydraulic reversing valve and comprises an electromagnet m4; the third reversing valve (8) is a three-position four-way electro-hydraulic reversing valve and comprises electromagnets m5 and m6; the third relief valve (9) is a pilot relief valve with large flow, and the set pressure is Pxmax; the fourth overflow valve (10) is a pilot overflow valve with large flow, and the set pressure is Pxmin; the first pressure transmitter (11) detects the rod cavity pressure P2 of the hydraulic cylinder (3); the second pressure transmitter (12) detects the rodless cavity pressure P1 of the hydraulic cylinder (3);
the port B of the main pump (1) is connected with the port B of the hydraulic cylinder (3), the port A of the first pressure transmitter (11) and the second reversing valve (7); the port A of the main pump (1) is connected with the port A of the hydraulic cylinder (3), the second pressure transmitter (12) and the port P of the third reversing valve (8); the port A of the first reversing valve (4) is connected with the port P of the first overflow valve (5), the port B of the first reversing valve (4) is connected with the port P of the second overflow valve (6), and the port P of the first reversing valve (4) is connected with the port X of the oil supplementing pump (2); the P port of the oil supplementing variable pump (2) is connected with the P port of the second reversing valve (7); the port A of the third reversing valve (8) is connected with the port P of the third overflow valve (9), and the port B of the third reversing valve (8) is connected with the port P of the fourth overflow valve (10); the S port of the oil supplementing pump (2), the T port of the first reversing valve (4), the T port of the third reversing valve (8), the T port of the first overflow valve (5), the T port of the second overflow valve (6), the T port of the third overflow valve (9) and the T port of the fourth overflow valve (10) are connected with an oil tank.
2. The hydraulic system of the four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder according to claim 1, characterized in that when m3 is powered off, the port P of the second relief valve (6) is communicated with the port X of the oil supplementing pump (2); when m3 is electrified, the P port of the first overflow valve (5) is communicated with the X port of the oil supplementing pump (2); when m4 is electrified, the P port of the oil supplementing pump (2) is communicated with the B port of the main pump (1); when m5 is electrified, the P port of the fourth overflow valve (10) is communicated with the A port of the main pump (1); and when m6 is electrified, the port P of the third overflow valve (9) is communicated with the port A of the main pump (1).
3. A control method of a hydraulic system of a four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder according to claim 1 or 2, characterized in that all electromagnets are powered off, the main pump (1) has zero displacement, the ports a and B of the main pump (1) have zero flow, and the hydraulic cylinder stops moving.
4. The control method of the hydraulic system of the four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder, according to claim 1, is characterized in that the hydraulic cylinder is in quadrant I, electromagnets m1 and m4 are electrified, the outflow flow of an A port of a main pump (1) is Q, the hydraulic system enters a rodless cavity of a hydraulic cylinder (3), a piston rod stretches out, the outflow flow of the rod cavity is kQ, and the oil supplementing flow of a B port of a supplementing oil pump (2) to the main pump (1) is (1-k) Q; the pressure of a rod cavity of the hydraulic cylinder (3) is Pbmin, and the load on a piston rod is F=P1.A1-Pbmin.A2 more than or equal to 0; if F is less than 0, switching to the quadrant II operation; wherein P1 is the rodless cavity pressure of the hydraulic cylinder (3), A1 is the effective area of the rodless cavity of the hydraulic cylinder (3), P2 is the rod cavity pressure of the hydraulic cylinder (3), A2 is the effective area of the rod cavity of the hydraulic cylinder (3),
5. the control method of the hydraulic system of the four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder, according to claim 1, is characterized in that the hydraulic cylinder is in quadrant II working, electromagnets m1, m3 and m4 are electrified, the outflow flow of an A port of a main pump (1) is Q, the outflow flow of the A port enters a rodless cavity of the hydraulic cylinder (3), a piston rod stretches out, the outflow flow of the rod cavity is kQ, and the oil supplementing flow of a B port of a supplementing oil pump (2) to the main pump (1) is (1-k) Q; the pressure of a rod cavity of the hydraulic cylinder (3) is Pbmax, and the load on a piston rod is F=P1.A1-Pbmax.A2 < 0; if F is more than or equal to 0, switching to the quadrant I operation.
6. The control method of the hydraulic system of the four-quadrant operated closed pump driven single-rod double-acting piston hydraulic cylinder according to claim 1, characterized in that the hydraulic cylinder in quadrant III is operated, electromagnets m2 and m5 are electrified, the outflow flow of the port B of the main pump (1) is Q, the outflow flow of the port B enters a rod cavity of the hydraulic cylinder (3), the piston rod is retracted, and the outflow flow of the rodless cavity isThe flow rate from the port A of the hydraulic cylinder (3) to the oil drain of the oil tank is +.>The rodless cavity pressure of the hydraulic cylinder (3) is Pxmin, and the load on a piston rod is F=Pxmin.A1-P2.A2 which is less than or equal to 0; if F > 0, then switch to quadrant IV operation.
7. The control method of the hydraulic system of the four-quadrant operated closed pump-driven single-rod double-acting piston hydraulic cylinder according to claim 1, characterized in that the hydraulic cylinder is operated in the IV quadrant, the electromagnets m2 and m6 are electrified, the outflow flow rate of the port B of the main pump (1) is Q, the outflow flow rate of the port B enters the rod cavity of the hydraulic cylinder 3, the piston rod is retracted, and the outflow flow rate of the rodless cavity isThe flow rate from the port A of the hydraulic cylinder (3) to the oil tank drain through the port P of the third overflow valve (9) is +.>The rodless cavity pressure of the hydraulic cylinder (3) is Pxmax, and the load on a piston rod is F=Pxmax.A1-P2.A2 > 0; if F is less than or equal to 0, switching to the quadrant III operation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311259578.4A CN117212268A (en) | 2023-09-27 | 2023-09-27 | Hydraulic system of four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder and control method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311259578.4A CN117212268A (en) | 2023-09-27 | 2023-09-27 | Hydraulic system of four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder and control method thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117212268A true CN117212268A (en) | 2023-12-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311259578.4A Pending CN117212268A (en) | 2023-09-27 | 2023-09-27 | Hydraulic system of four-quadrant working closed pump driven single-rod double-acting piston hydraulic cylinder and control method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117212268A (en) |
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2023
- 2023-09-27 CN CN202311259578.4A patent/CN117212268A/en active Pending
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