CN213595767U - Double-differential-cylinder lifting system of cab - Google Patents
Double-differential-cylinder lifting system of cab Download PDFInfo
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- CN213595767U CN213595767U CN202022302603.0U CN202022302603U CN213595767U CN 213595767 U CN213595767 U CN 213595767U CN 202022302603 U CN202022302603 U CN 202022302603U CN 213595767 U CN213595767 U CN 213595767U
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Abstract
The utility model relates to a double differential oil cylinder lifting system, which comprises a manual pump assembly 10, an auxiliary oil cylinder assembly (1) and a main oil cylinder assembly (5); the manual pump assembly 10 comprises a reversing valve 11, a manual pump 12 and a manual pump oil tank 13; the auxiliary oil cylinder assembly 1 comprises an auxiliary oil cylinder 3, a hydraulic control two-position two-way reversing valve 2 and a hydraulic control one-way valve 4; the main oil cylinder assembly 5 comprises a main oil cylinder 6, a one-way valve II 7, a one-way valve I8 and a one-way valve III 9. The utility model provides a driver's cabin rotation angle less, when the driver's cabin barycenter does not cross the trip axis, must match outside safety support's problem, satisfy the hydro-cylinder simultaneously along with driver's cabin free floating's functional requirement, the structure is succinct more, and is safe high-efficient, weight reduction, cost reduction.
Description
Technical Field
The utility model belongs to heavily block driver's cabin hydraulic pressure system of tumbling, concretely relates to double differential hydro-cylinder system of lifting is applied to heavily block driver's cabin hydraulic pressure system of lifting.
Background
In the existing cab tilting system of the heavy-duty car, for the cab tilting system lifted by adopting the double differential oil cylinders, when the tilting angle of the cab is designed to be smaller and the center of mass of the cab does not exceed the tilting axis, if an external safety supporting system is not added, when an oil cylinder pipeline is broken or manually operated by mistake or a valve in the main oil cylinder fails, the cab falls under the action of gravity, and safety accidents can be caused. In order to prevent the occurrence of safety accidents caused by the failure of a hydraulic system, mechanical safety support systems are mostly arranged, and the mechanical safety support systems are either integrated on a hydraulic cylinder or are separately provided with safety support rods or safety locking pins, so that the complexity of the system structure is increased, and some mechanisms have potential safety hazards in operation, increase the weight and the cost and are relatively complex to operate.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a double differential hydro-cylinder lifting system of driver's cabin has solved that driver's cabin rotation angle is less, and when the driver's cabin barycenter did not cross the trip axis, must match outside safety support's problem, satisfies the hydro-cylinder simultaneously and along with driver's cabin free floating's functional requirement, and the structure is succinct more, and is safe high-efficient, weight reduction, cost reduction.
The technical scheme of the utility model is that a double differential oil cylinder lifting system of a cab comprises a hand pump assembly 10, an auxiliary oil cylinder assembly 1 and a main oil cylinder assembly 5;
the manual pump assembly 10 comprises a reversing valve 11, a manual pump 12 and a manual pump oil tank 13, wherein an oil inlet of the manual pump 12 is communicated with the manual pump oil tank 13 through a one-way valve, an oil outlet of the manual pump 12 is connected with one oil inlet of the reversing valve 11 through the one-way valve, and an oil return port of the reversing valve 11 is connected with the manual pump oil tank 13;
the auxiliary oil cylinder assembly 1 comprises an auxiliary oil cylinder 3, a hydraulic control two-position two-way reversing valve 2 and a hydraulic control one-way valve 4; a rodless cavity liquid port of the auxiliary oil cylinder 3 is communicated with a liquid outlet of the hydraulic control one-way valve 4, meanwhile, the rodless cavity liquid port of the auxiliary oil cylinder is communicated with a liquid port of the hydraulic control two-position two-way reversing valve 2, a liquid inlet of the hydraulic control one-way valve 4 is connected with another liquid port of the hydraulic control two-position two-way reversing valve 2 to form a first oil port f of the auxiliary oil cylinder assembly, a control port d of the hydraulic control two-position two-way reversing valve 2 is communicated with a rod cavity oil port of the auxiliary oil cylinder to form a second oil port e of the auxiliary oil cylinder assembly, and a liquid outlet of the hydraulic control five-way valve 4 of the hydraulic control,
the main oil cylinder assembly 5 comprises a main oil cylinder 6, a second check valve 7, a first check valve 8 and a third check valve 9, wherein a rod cavity of the main oil cylinder 6 is connected with the second oil port to form a third oil port b of the main oil cylinder assembly, a rodless cavity of the main oil cylinder 6 is simultaneously connected with an oil outlet of the first check valve 8 and an oil outlet of the second check valve 7, an oil port f is connected with an oil inlet of the second check valve 7 and then connected with an oil outlet of the third check valve 9, an oil inlet of the third check valve 9 is connected with an oil inlet of the first check valve 8 to form a fourth oil port a of the main oil cylinder assembly, and the fourth oil port a and the third oil port b are respectively connected with two oil outlets of the reversing valve.
The beneficial effects of the utility model are that, the utility model discloses simple structure, self-locking function can be realized to the double cylinder homoenergetic when the disconnection of outside pipeline, and can not influence the self-locking function of another hydro-cylinder when one of them hydro-cylinder self-locking function became invalid. When the vehicle runs, the oil cylinder can realize small damping floating, and the comfort is not influenced. The utility model discloses make the system succinct more, safe high-efficient, weight reduction, cost reduction.
Drawings
FIG. 1 is a schematic diagram of a double differential cylinder lifting system for a cab according to the present invention;
fig. 2 is a schematic structural diagram of the middle master cylinder assembly and the auxiliary cylinder assembly of the present invention.
Detailed Description
The technical solution of the present invention will be further described in detail with reference to the drawings.
As shown in fig. 1 and fig. 2, the present invention relates to a cab double differential cylinder lift system, which comprises a manual pump assembly 10, an auxiliary cylinder assembly 1 and a main cylinder assembly 5.
The manual pump assembly 10 includes a selector valve 11, a manual pump 12, and a manual pump oil tank 13. An oil inlet of the manual pump 12 is communicated with an oil tank 13 of the manual pump through a one-way valve, an oil outlet of the manual pump 12 is connected with an oil inlet of the reversing valve 11 through the one-way valve, and an oil return port of the reversing valve 11 is connected with the oil tank 13 of the manual pump.
As shown in fig. 1 and 2, the slave cylinder assembly 1 includes a slave cylinder 3, a pilot-controlled two-position two-way directional valve 2, and a pilot-controlled check valve 4. A rodless cavity liquid port of the auxiliary oil cylinder 3 is communicated with a liquid outlet of the hydraulic control one-way valve 4, meanwhile, the rodless cavity liquid port of the auxiliary oil cylinder is communicated with a liquid port of the hydraulic control two-position two-way reversing valve 2, a liquid inlet of the hydraulic control one-way valve 4 is connected with another liquid port of the hydraulic control two-position two-way reversing valve 2 to form a first oil port f of the auxiliary oil cylinder assembly, and a control port d of the hydraulic control two-position two-way reversing valve 2 is communicated with a rod cavity oil port of the auxiliary oil cylinder to form a second oil port e of the auxiliary oil cylinder. The oil port five c of the hydraulic control two-position two-way reversing valve 2 is connected with the liquid outlet of the hydraulic control one-way valve 4.
The main oil cylinder assembly 5 comprises a main oil cylinder 6, a one-way valve II 7, a one-way valve I8 and a one-way valve III 9. And a rod cavity of the main oil cylinder 6 is connected with the oil port II to form an oil port III b of the main oil cylinder assembly. And a rodless cavity of the main oil cylinder 6 is simultaneously connected with an oil outlet of the one-way valve I8 and an oil outlet of the one-way valve II 7. The first oil port f is connected with an oil inlet of the second check valve 7 and then connected with an oil outlet of the third check valve 9. An oil inlet of the check valve III 9 is connected with an oil inlet of the check valve I8 to form an oil port IV a of the main oil cylinder assembly. The oil port IV a and the oil port III b are respectively connected with two oil outlets of the reversing valve 11.
As shown in fig. 1, when the pressure of the oil port five c of the hydraulic control two-position two-way reversing valve 2 is greater than the pressure of the control port d, the pressure of the oil port five c of the hydraulic control two-position two-way reversing valve overcomes the acting force of a spring to control the pressure of the control port d so that the valve is in a stop state; when the pressure of the oil port pentac of the hydraulic control two-position two-way reversing valve 2 is equal to the pressure of the control port d, the pressure of the hydraulic control two-position two-way reversing valve is offset between the oil port pentac and the control port d, and the hydraulic control two-position two-way reversing valve is in a communicated state under the action of the spring; when the pressure of the oil port pentac of the hydraulic control two-position two-way reversing valve 2 is smaller than the pressure of the control port d, the pressure of the control port d and the acting force of the spring overcome the pressure of the oil port pentac together to enable the valve to be in a communicated state.
As shown in fig. 1, the upper rodless cavities of the main cylinder 6 and the auxiliary cylinder 3 simultaneously feed oil and have the same pressure, and the effective acting area of the pressure is the sectional area of the piston rod, so that the cylinders can realize differential lifting action.
As shown in figure 1, the main oil cylinder 6 and the auxiliary oil cylinder 3 are arranged in a certain range at the bottom, the rodless cavities of the oil cylinders are communicated, and the oil cylinders can float in the range.
The working process of the utility model is as follows:
as shown in fig. 2, when the cab is lifted, the reversing valve 11 in the manual pump assembly 10 is set to the i position, the manual pump 12 is operated, the pressure oil reaches the oil port four a and the oil port three b through the reversing valve 11, and the pressure oil at the oil port four a reaches the rodless cavity of the main oil cylinder 6 through the check valve one 8 or the check valve three 9 and the check valve two 7; the pressure oil of the oil port IV reaches a rodless cavity of the auxiliary oil cylinder 3 through the check valve III 9 and the hydraulic control check valve 4; meanwhile, the pressure oil of the oil port four a can reach the oil port five c of the hydraulic control two-position two-way reversing valve 2 after the hydraulic control one-way valve 4 is opened, and the pressure oil of the oil port three b can reach the control port d of the hydraulic control two-position two-way reversing valve 2 when entering the rod cavity of the main oil cylinder 6 and the rod cavity of the auxiliary oil cylinder 3. The oil pressure of the oil port five c is the same as that of the control port d, so that the hydraulic control two-position two-way reversing valve 2 is in a IV-position communication state, pressure oil of the oil port four a can enter a rodless cavity of the auxiliary oil cylinder 3 through the check valve three 9 and the hydraulic control two-position two-way reversing valve 2, and the double oil cylinders realize lifting action.
As shown in fig. 2, when the hand pump assembly 10 is not operated after the cab is lifted to any angle beyond the floating range of the oil cylinder, the reversing valve 11 in the hand pump assembly 10 can be set to the i position or the ii position. Under the action of the gravity of the cab, the rodless cavities of the main oil cylinder 6 and the auxiliary oil cylinder 3 are in a high-pressure state, and the rod cavities of the main oil cylinder 6 and the auxiliary oil cylinder 3 are in a low-pressure state, namely the pressure of the oil port pentac is greater than that of the control port d, so that the hydraulic control two-position two-way reversing valve 2 is in a stop state at the III position. At this time, the double oil cylinders are locked. In this state, if the oil port four a, the oil port three b, the oil port two e and the oil port one f are disconnected, the double oil cylinder is still in a locked state, and the descending action cannot occur.
As shown in fig. 2, when the cab is pulled back, the reversing valve 11 in the manual pump assembly 10 is set to the second position, the manual pump 12 is operated, and the pressure oil reaches the oil port three b through the reversing valve 11, enters the rod cavities of the main cylinder 6 and the auxiliary cylinder 3, and reaches the hydraulic control one-way valve 4 and the one-way valve 8, so that the hydraulic control one-way valve 4 and the one-way valve 8 are opened, and the pressure oil also reaches the control port d of the hydraulic control two-position two-way reversing valve 2. In addition, the rodless cavity of the main oil cylinder 6 is communicated with a manual pump oil tank 13 through a first pilot-operated check valve 8 and a reversing valve 11. The rodless cavity of the auxiliary oil cylinder 3 and the oil port five c of the hydraulic control two-position two-way reversing valve 2 are communicated with the manual pump oil tank 13 through the hydraulic control one-way valve 4, the second check valve 7, the first hydraulic control one-way valve 8 and the reversing valve 11, because the pressure of the oil port five c is smaller than the pressure of the control port d, the hydraulic control two-position two-way reversing valve 2 is in a IV-position communication state, and the oil in the rodless cavity of the auxiliary oil cylinder 3 can also flow back to the manual pump oil tank 13 through the hydraulic control two-position two-way reversing valve 2, the second check valve 7, the first. Thereby achieving the pull-back operation of the cab.
As shown in fig. 2, after the cab is retracted, in the driving state, the rodless chambers of the main cylinder 6 and the sub cylinder 3 are in a communication state, and the reversing valve 11 in the manual pump assembly 10 is set at position ii.
When the cab moves downwards, the oil cylinders float along with the oil cylinders, the oil pressures of the rodless cavities of the main oil cylinder 6 and the auxiliary oil cylinder 3 rise simultaneously, the pressure of an oil port pentac and a control port d of the hydraulic control two-position two-way reversing valve 2 is the same, the hydraulic control two-position two-way reversing valve 2 is in the IV-position communication state, and the hydraulic control one-way valve 4 and the one-way valve 8 are also in the opening state. Oil in the main oil cylinder 6 flows back to the oil tank 13 from the rodless cavity of the oil cylinder through the first hydraulic control check valve 8 and the reversing valve 11; oil in the auxiliary oil cylinder 3 flows back to the oil tank 13 from the rodless cavity of the oil cylinder through the hydraulic control one-way valve 4, the second one-way valve 7, the first hydraulic control one-way valve 8 and the reversing valve 11; the oil in the auxiliary oil cylinder 3 can also flow back to the oil tank 13 from the rodless cavity of the oil cylinder through the hydraulic control two-position two-way reversing valve 2, the check valve II 7, the hydraulic control check valve I8 and the reversing valve 11. Therefore, the floating action of the oil cylinder can be realized.
When the cab moves upwards, the oil cylinders float upwards, the oil pressure of rodless cavities on the main oil cylinder 6 and the auxiliary oil cylinder 3 is reduced at the same time, the pressure of an oil port pentac and a control port d of the hydraulic control two-position two-way reversing valve 2 is the same, the hydraulic control two-position two-way reversing valve 2 is in a communicated state of an IV position, and the hydraulic control one- way valves 4 and 8 are also in an opened state under the action of negative pressure, so that oil in the oil tank 13 can be supplemented into the main oil cylinder 6 through the reversing valve 11 and the hydraulic control one-way valve 8; meanwhile, oil in the oil tank 13 is supplemented into the auxiliary oil cylinder 3 through the reversing valve 11, the check valve III 9 and the hydraulic control check valve 4; the oil liquid in the oil tank 13 can also be supplemented into the auxiliary oil cylinder 3 through the reversing valve 11, the check valve III 9 and the hydraulic control two-position two-way reversing valve 2. Therefore, the floating action of the oil cylinder can be realized.
Claims (1)
1. A double differential oil cylinder lifting system of a cab is characterized in that: the lifting system comprises a manual pump assembly (10), an auxiliary oil cylinder assembly (1) and a main oil cylinder assembly (5);
the manual pump assembly (10) comprises a reversing valve (11), a manual pump (12) and a manual pump oil tank (13), an oil inlet of the manual pump (12) is communicated with the manual pump oil tank (13) through a one-way valve, an oil outlet of the manual pump (12) is connected with an oil inlet of the reversing valve (11) through the one-way valve, and an oil return port of the reversing valve (11) is connected with the manual pump oil tank (13);
the auxiliary oil cylinder assembly (1) comprises an auxiliary oil cylinder (3), a hydraulic control two-position two-way reversing valve (2) and a hydraulic control one-way valve (4); a rodless cavity liquid port of the auxiliary oil cylinder (3) is communicated with a liquid outlet of the hydraulic control one-way valve (4), meanwhile, the rodless cavity liquid port of the auxiliary oil cylinder is communicated with a liquid port of the hydraulic control two-position two-way reversing valve (2), a liquid inlet of the hydraulic control one-way valve (4) is connected with another liquid port of the hydraulic control two-position two-way reversing valve (2) to form a first oil port (f) of the auxiliary oil cylinder assembly, a control port (d) of the hydraulic control two-position two-way reversing valve (2) is communicated with a rod cavity liquid port of the auxiliary oil cylinder to form a second oil port (e) of the auxiliary oil cylinder assembly, a fifth oil port (c) of the hydraulic control two-way reversing valve (2) is connected with a,
the main oil cylinder assembly (5) comprises a main oil cylinder (6), a second check valve (7), a first check valve (8) and a third check valve (9), a rod cavity of the main oil cylinder (6) is connected with the second oil port to form a third oil port (b) of the main oil cylinder assembly, a rodless cavity of the main oil cylinder (6) is simultaneously connected with an oil outlet of the first check valve (8) and an oil outlet of the second check valve (7), a first oil port (f) is connected with an oil inlet of the second check valve (7) and then connected with an oil outlet of the third check valve (9), an oil inlet of the third check valve (9) is connected with an oil inlet of the first check valve (8) to form a fourth oil port (a) of the main oil cylinder assembly, and the fourth oil port (a) and the third oil port (b) are respectively connected with two oil outlets of the reversing valve (.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022302603.0U CN213595767U (en) | 2020-10-15 | 2020-10-15 | Double-differential-cylinder lifting system of cab |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022302603.0U CN213595767U (en) | 2020-10-15 | 2020-10-15 | Double-differential-cylinder lifting system of cab |
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| Publication Number | Publication Date |
|---|---|
| CN213595767U true CN213595767U (en) | 2021-07-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202022302603.0U Active CN213595767U (en) | 2020-10-15 | 2020-10-15 | Double-differential-cylinder lifting system of cab |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112125202A (en) * | 2020-10-15 | 2020-12-25 | 北奔重型汽车集团有限公司 | Double-differential-cylinder lifting system of cab |
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2020
- 2020-10-15 CN CN202022302603.0U patent/CN213595767U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112125202A (en) * | 2020-10-15 | 2020-12-25 | 北奔重型汽车集团有限公司 | Double-differential-cylinder lifting system of cab |
| CN112125202B (en) * | 2020-10-15 | 2024-10-01 | 北奔重型汽车集团有限公司 | Lifting method for double differential cylinders of cab |
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