CN214221644U - Double-oil-cylinder synchronous lifting hydraulic system - Google Patents
Double-oil-cylinder synchronous lifting hydraulic system Download PDFInfo
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- CN214221644U CN214221644U CN202022628992.6U CN202022628992U CN214221644U CN 214221644 U CN214221644 U CN 214221644U CN 202022628992 U CN202022628992 U CN 202022628992U CN 214221644 U CN214221644 U CN 214221644U
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- 230000001360 synchronised effect Effects 0.000 title claims abstract description 10
- 239000003921 oil Substances 0.000 abstract description 221
- 239000010720 hydraulic oil Substances 0.000 abstract description 30
- 238000000034 method Methods 0.000 description 6
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Abstract
The utility model provides a synchronous lift hydraulic system of double cylinder, its characterized in that: the variable-amplitude oil cylinder control system comprises a first variable-amplitude oil cylinder, a first balance valve, a second variable-amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB; hydraulic oil can flow into the second balance valve from the rodless cavity port of the first luffing oil cylinder, flows through the third balance valve, then flows into the second luffing oil cylinder, finally flows out of the control oil port LB, flows into the third balance valve from the rodless cavity port of the second luffing oil cylinder, flows through the second balance valve, then flows into the first luffing oil cylinder, and finally flows out of the control oil port LB; the oil passages of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are communicated, so that the pressure balance between the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder can be realized.
Description
Technical Field
The utility model relates to a two hydro-cylinder synchronous system, concretely relates to two hydro-cylinder hydraulic system that goes up and down in step.
Background
The double oil cylinders of the actuating mechanism in the prior art solve the problem of different pressures of the two oil cylinders by installing a balance valve.
The application document with the application number of 201110365008.4 and the publication number of 2012.6.20 discloses a double-oil-cylinder synchronization system of a bridge detection operation vehicle, the system at least comprises a double-drive oil cylinder, a balance valve and two one-way back pressure valves for independently adjusting back pressure, the double-drive oil cylinder is a double-action oil cylinder, two ends of each drive oil cylinder are respectively hinged with a fixing seat and a U-shaped cross-section working platform, the two drive oil cylinders and oil ways thereof are connected in parallel, the one-way back pressure valves are respectively connected between working oil ports of rod cavity oil ports of the two drive oil cylinders and the balance valve or are not connected between the rod cavity oil ports of the two drive oil cylinders and the direction valve through the balance valve, and the rodless cavity oil ways of the two drive oil cylinders are respectively connected with another working oil port of the balance valve after being converged. The substitute of the one-way back pressure valve is a one-way back pressure valve group for independently adjusting back pressure.
But oil ports of rod cavities of two driving oil cylinders of the system are only connected with one-way back pressure valve; meanwhile, the two one-way back pressure valves are respectively connected with the balance valve, and the two one-way back pressure valves are not connected; when hydraulic oil flows in from the port A of the balance valve, the hydraulic oil flows through one of the driving oil cylinders and the one-way back pressure valve connected with the driving oil cylinder, and then flows out from the port B of the balance valve; hydraulic oil cannot circulate between the two driving oil cylinders; the pressure balance of the two driving oil cylinders can not be realized, so that when two one-way back pressure valve sections are inconsistent or the performances are different, the pressure between the two driving oil cylinders is different, and the driving oil cylinders can shake during working.
Disclosure of Invention
The utility model provides a realize two hydro-cylinder pressure balance, hydro-cylinder decline stable two hydro-cylinder hydraulic system that goes up and down in step.
In order to achieve the above purpose, the technical scheme of the utility model is that: a double-oil-cylinder synchronous lifting hydraulic system comprises a first variable amplitude oil cylinder, a first balance valve, a second variable amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB;
the first amplitude-variable oil cylinder, the second amplitude-variable oil cylinder and the oil circuit connection thereof are connected in parallel, rodless cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LB, and rod cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LA;
the first balance valve is connected between the rodless cavity opening of the first luffing oil cylinder and the control oil port LB; the fourth balance valve is connected between the rodless cavity opening of the second variable amplitude oil cylinder and the control oil port LB; the rodless cavity port of the first luffing oil cylinder is also connected with a second balance valve; the rodless cavity port of the second variable amplitude oil cylinder is also connected with a third balance valve; the second balance valve is also connected with the third balance valve; and control oil ports of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve are also connected with a control oil port LA.
Further, the first balance valve comprises a first check valve and a first overflow valve; an oil inlet of the first overflow valve is connected with a rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the first overflow valve is connected with a control oil port LB; a control oil port of the first overflow valve is connected with a control oil port LA; an oil inlet of the first check valve is connected with an oil outlet of the first overflow valve, and an oil outlet of the first check valve is connected with an oil inlet of the first overflow valve.
Further, the fourth balancing valve comprises a fourth one-way valve and a fourth overflow valve; an oil inlet of the fourth overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, an oil outlet of the fourth overflow valve is connected with a control oil port LB, and a control oil port of the fourth overflow valve is connected with a control oil port LA; an oil inlet of the fourth one-way valve is connected with an oil outlet of the fourth overflow valve, and an oil outlet of the fourth one-way valve is connected with a rodless cavity opening of the second variable amplitude oil cylinder.
Further, the second balance valve comprises a second check valve and a second overflow valve; the third balance valve comprises a third check valve and a third overflow valve; an oil inlet of the second overflow valve is connected with the rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the second overflow valve is connected with an oil outlet of the third overflow valve; a control oil port of the second overflow valve is connected with a control oil port of the first overflow valve; an oil inlet of a third overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, and a control oil port of the third overflow valve is connected with a control oil port of a fourth overflow valve; an oil inlet of the second one-way valve is connected with an oil outlet of the second overflow valve, and an oil outlet of the second one-way valve is connected with an oil inlet of the second overflow valve; an oil inlet of the third one-way valve is connected with an oil outlet of the third overflow valve, and an oil outlet of the third one-way valve is connected with an oil inlet of the second overflow valve.
Furthermore, the control oil ports LA and LB are connected with an oil tank through a hydraulic pump through a reversing valve.
The working principle of the hydraulic system is as follows: the hydraulic oil is pumped into the control oil port LA through the reversing valve by the hydraulic pump, the hydraulic oil respectively enters the first amplitude cylinder and the second amplitude cylinder from the control oil port LA, meanwhile, the hydraulic oil of the control oil port LA is respectively input into the control oil port of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve, in the process of feeding the hydraulic oil, the hydraulic oil in the rodless cavity of the first amplitude cylinder flows back to the control oil port LB through the first balance valve and then flows back to the oil tank, and meanwhile, the hydraulic oil in the rodless cavity of the second amplitude cylinder flows back to the control oil port LB through the third balance valve and then flows back to the oil tank. In the process, if the oil pressure in the rodless cavities of the first luffing oil cylinder and the second luffing oil cylinder is unbalanced, the oil pressure in the rodless cavities is balanced through the second balance valve and the third balance valve, specifically, if the oil pressure in the rodless cavity of the first luffing oil cylinder is greater than the oil pressure in the rodless cavity of the second luffing oil cylinder, under the action of the second balance valve and the third balance valve, part of hydraulic oil in the rodless cavity of the first luffing oil cylinder flows into the rodless cavity of the second luffing oil cylinder through the second balance valve and the third balance valve, otherwise, the hydraulic oil flows reversely.
If the hydraulic oil flows in from the control oil port LB through the control reversing valve, the hydraulic oil enters the first amplitude-variable oil cylinder through the first balance valve, and the return oil of the first amplitude-variable oil cylinder flows back from the control oil port LA; meanwhile, hydraulic oil enters the second amplitude-variable oil cylinder through the fourth balance valve, and return oil of the second amplitude-variable oil cylinder flows back from the control oil port LA; in the process, if the oil pressure in the rodless cavities of the first luffing oil cylinder and the second luffing oil cylinder is unbalanced, the oil pressure in the rodless cavities is balanced through the second balance valve and the third balance valve, specifically, if the oil pressure in the rodless cavity of the first luffing oil cylinder is greater than the oil pressure in the rodless cavity of the second luffing oil cylinder, under the action of the second balance valve and the third balance valve, part of hydraulic oil in the rodless cavity of the first luffing oil cylinder flows into the rodless cavity of the second luffing oil cylinder through the second balance valve and the third balance valve, otherwise, the hydraulic oil flows reversely.
In the hydraulic system, due to the arrangement of the first balance valve, the first balance valve can prevent the first luffing cylinder from undesirably moving downwards and allow an operator to enable the first luffing cylinder to move upwards at a certain speed and keep at a certain position; in addition, the first balance valve can be used for placing actions generated by actions prior to the hydraulic pump due to load energy on the first luffing cylinder, so that the cavitation phenomenon and the load runaway phenomenon of the first luffing cylinder are effectively eliminated; furthermore, the first balancing valve can prevent the runaway of the moving load when the pipe in the hydraulic circuit bursts or seriously leaks.
Similarly, for the fourth balancing valve and the second luffing cylinder, the function of the fourth balancing valve relative to the second luffing cylinder is the same as the function of the first balancing valve relative to the first luffing cylinder.
In addition, due to the fact that the second balance valve and the third balance valve are arranged, the pressure of the first amplitude-changing oil cylinder and the pressure of the second amplitude-changing oil cylinder can be balanced, the first amplitude-changing oil cylinder and the second amplitude-changing oil cylinder are better in synchronism, and the phenomenon that the first amplitude-changing oil cylinder and the second amplitude-changing oil cylinder are clamped is avoided.
Drawings
Fig. 1 is a hydraulic schematic diagram of the present invention.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1, the double-cylinder synchronous lifting hydraulic system comprises an oil tank, a first luffing cylinder 51, a first balance valve 1, a second balance valve 2, a second luffing cylinder 52, a third balance valve 3, a fourth balance valve 4, a control oil port LA and a control oil port LB; the control oil port LA is connected with one oil port of the oil tank, and the control oil port LB is connected with the other oil port of the oil tank.
The first luffing oil cylinder 51, the second luffing oil cylinder 52 and the oil circuit connection thereof are connected in parallel, rodless cavities of the first luffing oil cylinder 51 and the second luffing oil cylinder 52 are both connected with a control oil port LB, and rodless cavities of the first luffing oil cylinder 51 and the second luffing oil cylinder 52 are both connected with a control oil port LA.
The first balance valve 1 is connected between the rodless cavity opening of the first luffing cylinder 51 and the control oil port LB; the fourth balance valve 4 is connected between the rodless cavity opening of the second luffing cylinder 52 and the control oil port LB; the rodless cavity opening of the first luffing cylinder 51 is also connected with the second balance valve 2; the rodless cavity opening of the second luffing cylinder 52 is also connected with the third balanced valve 3; the second balance valve 2 is also connected with a third balance valve 3; the control ends of the first balance valve 1, the second balance valve 2, the third balance valve 3 and the fourth balance valve 4 are all connected with a control oil port LA.
The first balance valve 1 comprises a first check valve 12 and a first overflow valve 11 which are connected in parallel; the second balance valve 2 comprises a second check valve 22 and a second overflow valve 21 which are connected in parallel; the third balance valve 3 comprises a third check valve 32 and a third overflow valve 31 which are connected in parallel; the fourth balancing valve 4 comprises a fourth non return valve 42 and a fourth spill valve 41 connected in parallel.
An oil inlet of the first overflow valve 11 is connected with a rodless cavity port of the first luffing oil cylinder 51, and an oil outlet of the first overflow valve 11 is connected with a control oil port LB; the control port of the first overflow valve 11 is connected to the control port LA.
An oil inlet of the first check valve 12 is connected with an oil outlet of the first overflow valve 11, and an oil outlet of the first check valve 12 is connected with an oil inlet of the first overflow valve 11.
An oil inlet of the second overflow valve 21 is connected with a rodless cavity port of the first luffing oil cylinder 51, and an oil outlet of the second overflow valve 21 is connected with an oil outlet of the third overflow valve 31; a control oil port of the second overflow valve 21 is connected with a control oil port of the first overflow valve 11; an oil inlet of the third overflow valve 31 is connected with a rodless cavity port of the second luffing oil cylinder 52, and a control oil port of the third overflow valve 31 is connected with a control oil port of the fourth overflow valve 41.
An oil inlet of the second check valve 22 is connected with an oil outlet of the second overflow valve 21, and an oil outlet of the second check valve 22 is connected with an oil inlet of the second overflow valve 21; an oil inlet of the third check valve 32 is connected with an oil outlet of the third overflow valve 31, and an oil outlet of the third check valve 32 is connected with an oil inlet of the second overflow valve 21.
An oil inlet of the fourth overflow valve 41 is connected with a rodless cavity opening of the second luffing oil cylinder 52, an oil outlet of the fourth overflow valve 41 is connected with a control oil port LB, and a control oil port of the fourth overflow valve 41 is connected with a control oil port LA.
An oil inlet of the fourth one-way valve 42 is connected with an oil outlet of the fourth overflow valve 41, and an oil outlet of the fourth one-way valve 42 is connected with a rodless cavity opening of the second luffing cylinder 52.
The working principle of the hydraulic system is as follows: hydraulic oil is pumped into the control oil port LA through the reversing valve by the hydraulic pump, the hydraulic oil respectively enters the first amplitude cylinder 51 and the second amplitude cylinder 52 from the control oil port LA, meanwhile, the hydraulic oil of the control oil port LA is respectively input into the control oil ports of the first balance valve 1, the second balance valve 2, the third balance valve 3 and the fourth balance valve 4, in the process of feeding the hydraulic oil, the hydraulic oil in the rodless cavity of the first amplitude cylinder 51 flows back to the control oil port LB through the first balance valve 1 and then flows back to the oil tank, and meanwhile, the hydraulic oil in the rodless cavity of the second amplitude cylinder 52 flows back to the control oil port LB through the third balance valve 3 and then flows back to the oil tank. In the above process, when the oil pressures in the rodless cavities of the first luffing cylinder 51 and the second luffing cylinder are unbalanced, the oil pressures in the rodless cavities are balanced by the second balance valve 2 and the third balance valve 3, specifically, if the oil pressure in the rodless cavity of the first luffing cylinder 51 is greater than the oil pressure in the rodless cavity of the second luffing cylinder 52, under the action of the second balance valve 2 and the third balance valve 3, part of the hydraulic oil in the rodless cavity of the first luffing cylinder 51 flows into the rodless cavity of the second luffing cylinder 52 through the second balance valve 2 and the third balance valve 3, otherwise, the hydraulic oil flows in the reverse direction.
If the hydraulic oil flows in from the control oil port LB through the control reversing valve, the hydraulic oil enters the first luffing cylinder 51 through the first balance valve 1, and the return oil of the first luffing cylinder 51 flows back from the control oil port LA; meanwhile, the hydraulic oil enters the second luffing cylinder 52 through the fourth balance valve 4, and the return oil of the second luffing cylinder 52 flows back from the control oil port LA; in the above process, when the oil pressures in the rodless cavities of the first luffing cylinder 51 and the second luffing cylinder are unbalanced, the oil pressures in the rodless cavities are balanced by the second balance valve 2 and the third balance valve 3, specifically, if the oil pressure in the rodless cavity of the first luffing cylinder 51 is greater than the oil pressure in the rodless cavity of the second luffing cylinder 52, under the action of the second balance valve 2 and the third balance valve 3, part of the hydraulic oil in the rodless cavity of the first luffing cylinder 51 flows into the rodless cavity of the second luffing cylinder 52 through the second balance valve 2 and the third balance valve 3, otherwise, the hydraulic oil flows in the reverse direction.
In the system, due to the arrangement of the first balance valve 1, in the direction of a visual angle shown in fig. 1, the first balance valve 1 can prevent the first luffing cylinder 51 from undesirably moving downwards and allow an operator to move the first luffing cylinder 51 upwards at a certain speed and keep the first luffing cylinder 51 at a certain position; in addition, the first balance valve 1 can be used for placing actions generated by actions prior to the hydraulic pump due to load energy on the first luffing cylinder 51, so that the cavitation phenomenon and the load runaway phenomenon of the first luffing cylinder 51 are effectively eliminated; furthermore, the first counter balance valve 1 prevents the runaway of the moving load when the line in the hydraulic circuit bursts or leaks seriously.
Likewise, the action of the fourth balancing valve 4 with respect to the second luffing cylinder 52 is the same for the fourth balancing valve 4 and the second luffing cylinder 52 as for the first balancing valve 1 with respect to the first luffing cylinder 51.
In addition, due to the arrangement of the second and third balance valves, the pressure of the first luffing cylinder 51 and the second luffing cylinder 52 can be balanced, the synchronism of the first luffing cylinder 51 and the second luffing cylinder 52 is better, and the phenomenon that the first luffing cylinder 51 and the second luffing cylinder 52 are blocked is avoided.
Claims (5)
1. The utility model provides a two hydro-cylinders hydraulic system that goes up and down in step which characterized in that: the variable-amplitude oil cylinder control system comprises a first variable-amplitude oil cylinder, a first balance valve, a second variable-amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB;
the first amplitude-variable oil cylinder, the second amplitude-variable oil cylinder and the oil circuit connection thereof are connected in parallel, rodless cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LB, and rod cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LA;
the first balance valve is connected between the rodless cavity opening of the first luffing oil cylinder and the control oil port LB; the fourth balance valve is connected between the rodless cavity opening of the second variable amplitude oil cylinder and the control oil port LB; the rodless cavity port of the first luffing oil cylinder is also connected with a second balance valve; the rodless cavity port of the second variable amplitude oil cylinder is also connected with a third balance valve; the second balance valve is also connected with the third balance valve; and control oil ports of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve are also connected with a control oil port LA.
2. The double-cylinder synchronous lifting hydraulic system according to claim 1, characterized in that: the first balance valve comprises a first check valve and a first overflow valve; an oil inlet of the first overflow valve is connected with a rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the first overflow valve is connected with a control oil port LB; a control oil port of the first overflow valve is connected with a control oil port LA; an oil inlet of the first check valve is connected with an oil outlet of the first overflow valve, and an oil outlet of the first check valve is connected with an oil inlet of the first overflow valve.
3. The double-cylinder synchronous lifting hydraulic system according to claim 1 or 2, characterized in that: the fourth balancing valve comprises a fourth one-way valve and a fourth overflow valve; an oil inlet of the fourth overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, an oil outlet of the fourth overflow valve is connected with a control oil port LB, and a control oil port of the fourth overflow valve is connected with a control oil port LA; an oil inlet of the fourth one-way valve is connected with an oil outlet of the fourth overflow valve, and an oil outlet of the fourth one-way valve is connected with a rodless cavity opening of the second variable amplitude oil cylinder.
4. The double-cylinder synchronous lifting hydraulic system according to claim 3, characterized in that: the second balance valve comprises a second check valve and a second overflow valve; the third balance valve comprises a third check valve and a third overflow valve; an oil inlet of the second overflow valve is connected with the rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the second overflow valve is connected with an oil outlet of the third overflow valve; a control oil port of the second overflow valve is connected with a control oil port of the first overflow valve; an oil inlet of a third overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, and a control oil port of the third overflow valve is connected with a control oil port of a fourth overflow valve; an oil inlet of the second one-way valve is connected with an oil outlet of the second overflow valve, and an oil outlet of the second one-way valve is connected with an oil inlet of the second overflow valve; an oil inlet of the third one-way valve is connected with an oil outlet of the third overflow valve, and an oil outlet of the third one-way valve is connected with an oil inlet of the second overflow valve.
5. The double-cylinder synchronous lifting hydraulic system according to claim 1, characterized in that: the control oil ports LA and LB are connected with an oil tank through a hydraulic pump through a reversing valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022628992.6U CN214221644U (en) | 2020-11-13 | 2020-11-13 | Double-oil-cylinder synchronous lifting hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022628992.6U CN214221644U (en) | 2020-11-13 | 2020-11-13 | Double-oil-cylinder synchronous lifting hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214221644U true CN214221644U (en) | 2021-09-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022628992.6U Expired - Fee Related CN214221644U (en) | 2020-11-13 | 2020-11-13 | Double-oil-cylinder synchronous lifting hydraulic system |
Country Status (1)
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| CN (1) | CN214221644U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215802A (en) * | 2021-11-10 | 2022-03-22 | 中船华南船舶机械有限公司 | Control method of hydraulic system of elevator |
-
2020
- 2020-11-13 CN CN202022628992.6U patent/CN214221644U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215802A (en) * | 2021-11-10 | 2022-03-22 | 中船华南船舶机械有限公司 | Control method of hydraulic system of elevator |
| CN114215802B (en) * | 2021-11-10 | 2024-05-31 | 中船华南船舶机械有限公司 | Control method of hydraulic system of lifter |
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Granted publication date: 20210917 |