CN210484249U - Double-section hydraulic cylinder - Google Patents
Double-section hydraulic cylinder Download PDFInfo
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- CN210484249U CN210484249U CN201921277238.3U CN201921277238U CN210484249U CN 210484249 U CN210484249 U CN 210484249U CN 201921277238 U CN201921277238 U CN 201921277238U CN 210484249 U CN210484249 U CN 210484249U
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Abstract
The utility model discloses a two-section hydraulic cylinder, it includes primary piston, secondary piston and cylinder body, is formed with bottom oil charge chamber between the bottom of cylinder body and the primary piston, is formed with middle oil pocket between secondary piston and the primary piston, and this two-section hydraulic cylinder still includes the compensating valve, and it sets up on primary piston, and when primary piston reached withdrawal extreme position earlier or stretched out extreme position, the compensating valve was opened, bottom oil charge chamber and middle oil pocket intercommunication. The utility model discloses a two-section pneumatic cylinder is through setting up the compensating valve on primary piston, thereby arrive extreme position earlier at primary piston, and oil leak or outside oil inflow appear in middle oil pocket and side oil pocket and lead to secondary piston can't reach extreme position when, make the automatic switching that opens and shuts of compensating valve through two-section pneumatic cylinder internal oil pressure differential or mechanical force, thereby it reaches the standard to change the hydraulic pressure oil mass, this two-section pneumatic cylinder has utilized the structural characteristic of two-section pneumatic cylinder itself, do not need manual operation, high convenience and fastness, therefore, the clothes hanger is strong in practicability.
Description
Technical Field
The utility model relates to a two-way flexible length compensation's of two sections pneumatic cylinders that rely on hydraulic oil to promote field, in particular to two sections pneumatic cylinders.
Background
The constant-speed double-section hydraulic cylinder is a common mechanical part for executing a lifting function or a stretching function at present, and has the obvious advantages of short shape length, long stretching stroke and uniform speed compared with the constant-speed single-section hydraulic cylinder.
As shown in fig. 1, the conventional double-joint hydraulic cylinder is composed of a primary piston 2 and a secondary piston 3 which are disposed in a cylinder body 1, both pistons being movable in the axial direction of the cylinder body 1, and at least a part of the secondary piston 3 being disposed inside the primary piston 2. Two cavities are formed between the primary piston 2 and the cylinder body 1, wherein the cavity formed by the inner wall of the cylinder body 1 and the top surface of the primary piston 2 is a bottom oil-filled cavity 10, and the other cavity is a side oil cavity 20; a cavity surrounded by the top surface of the secondary piston 3 and the inner wall of the primary piston 2 is an intermediate oil chamber 30, and the side oil chamber 20 and the intermediate oil chamber 30 are communicated through a communication hole 4 arranged on the surface of the primary piston 2 to form a combined closed oil chamber; the other cavity formed between the secondary piston 3 and the inner wall of the primary piston 2 is the top oil-filled cavity 40 of the double-section hydraulic cylinder. When the bottom oil-filling cavity 10 is filled with hydraulic oil, the oil pressure pushes the primary piston 2 to move in the extending direction, meanwhile, the hydraulic oil in the side oil cavity 20 is extruded into the middle oil cavity 30 through the communicating hole 4, and then the secondary piston 3 is pushed to move in the extending direction until the hydraulic oil in the side oil cavity 20 is completely extruded into the middle oil cavity 30, and at the moment, the primary piston 2 and the secondary piston 3 reach the extending limit positions at the same time; on the contrary, when the top oil-filled cavity 40 is filled with hydraulic oil, the two-section hydraulic cylinder does retraction movement, and the primary piston 2 and the secondary piston 3 move to the retraction limit position simultaneously.
However, when the double-section hydraulic cylinder is used, the sealing state of the oil cavity in the double-section hydraulic cylinder may be damaged due to the influence of factors such as manufacturing accuracy or abrasion of a sealing element, and slow leakage of hydraulic oil may occur, which may cause loss of hydraulic oil in the combined closed oil cavity or inflow of external hydraulic oil. When the hydraulic oil in the closed oil cavity runs off, the secondary piston cannot reach the extending limit position of the double-section hydraulic cylinder when the double-section hydraulic cylinder extends; on the contrary, when the hydraulic oil in the closed middle oil cavity is increased and the hydraulic cylinder does retraction movement, the secondary piston cannot reach the retraction limit position due to the increase of the hydraulic oil in the middle oil cavity. That is, the movement of the cylinder may not reach the set limit extension or limit shortening length due to the inability to meet a complete seal within the cylinder.
SUMMERY OF THE UTILITY MODEL
The to-be-solved technical problem of the utility model is to provide a two-section pneumatic cylinder in order to overcome among the prior art the sealing system in the two-section pneumatic cylinder can't reach the defect of the limit length of settlement in the sealed two-section pneumatic cylinder that leads to completely.
The utility model discloses an above-mentioned technical problem is solved through following technical scheme:
a two-section hydraulic cylinder comprising a primary piston, a secondary piston, and a cylinder body, wherein a bottom oil-filled chamber is formed between the bottom of the cylinder body and the primary piston, and an intermediate oil chamber is formed between the secondary piston and the primary piston,
the double-section hydraulic cylinder further comprises a compensation valve, the compensation valve is arranged on the primary piston, and when the primary piston reaches a retraction limit position or an extension limit position firstly, the compensation valve is opened so that the bottom oil filling cavity is communicated with the middle oil cavity. In a conventional state of the double-section hydraulic cylinder, the primary piston and the secondary piston can reach the limit positions at the same time, so when the primary piston reaches the limit positions firstly, the oil quantity in the middle oil cavity can be adjusted through the circulation of hydraulic oil after the compensation valve is opened, and then the position of the secondary piston is adjusted to meet the requirement that the primary piston and the secondary piston both reach the limit positions.
Preferably, the compensation valve is opened by electrical, hydraulic or mechanical means.
Preferably, the compensation valve is a one-way valve and is opened unidirectionally when the pressure in the bottom oil charge chamber is greater than the sum of the pressure in the intermediate oil chamber and a pressure set value of the compensation valve, which refers to the maximum pressure in the direction in which the compensation valve acts on the bottom oil charge chamber. The setting of the one-way valve can ensure that the one-way valve can be opened only when the pressure of the bottom oil filling cavity is greater than the sum of the pressure of the middle oil cavity and the pressure set value of the compensating valve, so that the influence of the opening of the compensating valve on the set pressure and the oil quantity of the double-section hydraulic cylinder under other conditions is avoided, and the hydraulic oil supplementing effect at the limit position cannot be realized.
Preferably, when the primary piston contacts the bottom of the cylinder, the compensation valve is pushed open by the bottom of the cylinder to communicate the bottom oil-filled chamber with the intermediate oil chamber. When the primary piston contacts the bottom of the cylinder body, the compensation valve is pushed open, the bottom oil filling cavity is communicated with the middle oil cavity, and when redundant hydraulic oil is stored in the middle oil cavity, the redundant hydraulic oil can flow into the bottom oil filling cavity through the compensation valve.
Preferably, a side oil chamber is further formed between the primary piston and the cylinder body, the side oil chamber is communicated with the middle oil chamber through a communication hole arranged on the surface of the primary piston, and the side oil chamber and the middle oil chamber form a closed oil chamber.
Preferably, the compensation valve includes a communication passage and a seal, an end opening of the communication passage to the bottom oil-filled chamber is a bottom opening, an end opening of the communication passage to the intermediate oil chamber is a top opening, the seal is pressed against and seals the bottom opening, and a portion of the seal protrudes from the bottom opening, and when the seal is opened, the compensation valve is opened.
Preferably, the length of the part of the sealing member protruding out of the bottom opening is 1 mm to 2 mm.
Preferably, the seal is compressed against and seals the bottom opening by a spring.
Preferably, the acting force of the spring on the sealing element is smaller than the system pressure of the double-section hydraulic cylinder, and the system pressure refers to the maximum oil inlet pressure of the double-section hydraulic cylinder.
Preferably, the compensation valve opens when the oil pressure at the bottom opening is greater than the sum of the oil pressure at the top opening and the pressure of the spring; when the primary piston is at the retraction limit position, one end of the compensation valve is pushed back to the communication channel through the inner wall of the cylinder body, and the compensation valve is opened.
On the basis of the common knowledge in the field, the above preferred conditions can be combined at will to obtain the preferred embodiments of the present invention.
The utility model discloses an actively advance the effect and lie in: the utility model discloses a two-section pneumatic cylinder is through the mode that sets up the compensating valve on primary piston, thereby arrive extreme position earlier at primary piston, and when oil leak or outside hydraulic oil inflow appeared in middle oil pocket and side oil pocket and lead to the unable condition that reaches extreme position of secondary piston, oil pressure difference or mechanical force through in the two-section pneumatic cylinder make the automatic conversion that opens and shuts of compensating valve, the hydraulic oil mass of middle oil pocket and side oil pocket has been changed, make it reach the standard, it has utilized the structural characteristic of two-section pneumatic cylinder itself, do not need manual operation, high convenience and fast, therefore, the clothes hanger is strong in practicability.
Drawings
Fig. 1 is a schematic structural diagram of a double-section hydraulic cylinder in the prior art.
Fig. 2 is a schematic structural view of a double-section hydraulic cylinder in its retracted extreme position according to a preferred embodiment of the present invention.
Fig. 3 is a schematic structural view of a double-section hydraulic cylinder in its extended limit position according to a preferred embodiment of the present invention.
Fig. 4 is a schematic structural diagram of a compensation valve according to a preferred embodiment of the present invention.
Description of reference numerals:
Compensating valve 5
Seal 52
Bottom oil-filled chamber 10
Top oil-filled chamber 40
Detailed Description
The present invention is further illustrated by way of the following preferred embodiments, but is not intended to be limited thereby within the scope of the embodiments described.
As shown in fig. 2 to 4, the utility model provides a two-section hydraulic cylinder, it includes primary piston 2, secondary piston 3 and cylinder body 1, wherein, be formed with bottom oil charge chamber 10 between the bottom inner wall of cylinder body 1 and the top surface of primary piston 2, another cavity that forms between cylinder body 1 and the primary piston 2 is side oil pocket 20, be formed with middle oil pocket 30 between the top surface of secondary piston 3 and the inner wall of primary piston 2, another cavity that secondary piston 3 and the inner wall of primary piston 2 are constituteed is top oil charge chamber 40, side oil pocket 20 and middle oil pocket 30 communicate through the intercommunicating pore 4 that sets up on primary piston 2 surface, form the closed oil pocket of a combination. The double-section hydraulic cylinder further comprises a compensation valve 5, wherein the compensation valve 5 is arranged on the primary piston 2, and when the primary piston 2 reaches a retraction limit position or an extension limit position firstly, the compensation valve 5 is opened so as to enable the bottom oil filling cavity 10 to be communicated with the middle oil cavity 30. Since the oil amounts in the side oil chamber 20 and the middle oil chamber 30 are set so that the primary piston 2 and the secondary piston 3 can simultaneously reach the limit positions in the moving state when the two-section hydraulic cylinder is in the normal state, when the primary piston 2 reaches the limit positions first, the compensation valve 5 is opened and then hydraulic oil flows, the oil amounts in the side oil chamber 20 and the middle oil chamber 30 can be adjusted, and then the position of the secondary piston 3 is adjusted to meet the requirement that the primary piston 2 and the secondary piston 3 both reach the limit positions. The compensation valve 5 is opened by electrical, hydraulic or mechanical means. In this embodiment, the opening is controlled by hydraulic and mechanical means, as described below. In other embodiments, an electrically controlled opening may be used.
The compensation valve 5 is a one-way valve and the compensation valve 5 is opened one way when the pressure in the bottom oil-filled chamber 10 is greater than the sum of the pressure in the intermediate oil chamber 30 and the pressure set value of the compensation valve 5, which refers to the maximum pressure in the direction in which the compensation valve 5 acts on the bottom oil-filled chamber 10. The compensation valve 5 is set to be a one-way valve, so that the compensation valve 5 can be opened only when the pressure of the bottom oil filling cavity 10 is greater than the sum of the pressure of the middle oil cavity 30 and the pressure set value of the compensation valve 5, and the situation that the set oil quantity of the double-section hydraulic cylinder is influenced by the opening of the compensation valve 5 under other conditions is avoided, and therefore the compensation function at the limit position cannot be achieved. When the primary piston 2 contacts the bottom of the cylinder 1, the compensation valve 5 is pushed open by the bottom of the cylinder 1 to communicate the bottom oil-filled chamber 10 with the intermediate oil chamber 30. At this time, when the excess hydraulic oil is still present in the intermediate oil chamber 30, it can flow into the bottom oil-filled chamber 10 through the compensation valve 5 and be discharged.
Further, the compensation valve 5 includes a communication passage 51 and a seal 52, an end opening of the communication passage 51 to the bottom oil-filled chamber 10 is a bottom opening, an end opening to the intermediate oil chamber 30 is a top opening, the seal 52 is pressed and seals the bottom opening, and a part of the seal 52 protrudes out of the bottom opening, and when the seal 52 is opened, the compensation valve 5 is opened, that is, when the primary piston 2 is at the retraction limit position, the protruding part of the seal 52 pushes back the communication passage 51 through the inner wall of the cylinder 1, and the compensation valve 5 is opened. The length of the portion of the sealing member 52 protruding out of the bottom opening is 1 mm to 2 mm, and in the present embodiment, is set to protrude out by a length of 2 mm. For better sealing effect, the area of the end of the sealing member 52 near the bottom opening may be smaller than the area of the end near the top opening for better sealing effect.
In order to achieve a better pressing effect, the sealing element 52 is pressed on and seals the bottom opening through the spring 53, the sealing element 52 is made of metal, and in other embodiments, other types of materials, such as plastic materials, may be used. The bottom opening and the top opening are at the same oil pressure, i.e. the compensation valve 5 cannot be opened in a normal operation state, and the seal 52 can be opened only when the oil pressure of the bottom oil-filled chamber 10 reaches a certain level, i.e. the hydraulic oil pressure at the bottom opening is greater than the sum of the hydraulic oil pressure at the top opening and the pressure of the spring 53, and the compensation valve 5 is opened. And the force of the spring 53 on the seal 52 is smaller than the system pressure of the double-section hydraulic cylinder, which is the maximum oil inlet pressure of the double-section hydraulic cylinder. The force of the spring 53 on the seal 52 is smaller than the system pressure of the two-section hydraulic cylinder, so that the compensation valve 5 is opened by the increase in oil pressure in the bottom oil charge chamber 10 when the primary piston 2 reaches the limit position.
When the two-section hydraulic cylinder normally operates, namely the hydraulic oil amount in the middle oil cavity 30 and the hydraulic oil amount in the side oil cavity 20 are not changed, hydraulic oil is introduced into the bottom oil-filled cavity 10, the primary piston 2 is pushed to move in the extending direction by the oil pressure, meanwhile, the hydraulic oil in the side oil cavity 20 is extruded into the middle oil cavity 30 through the communication hole 4, and then the secondary piston 3 is pushed to move in the extending direction until the hydraulic oil in the side oil cavity 20 is completely pressed in the middle oil cavity 30, and at the moment, the primary piston 2 and the secondary piston 3 reach the extending limit position simultaneously; on the contrary, when the top oil-filled chamber 40 is filled with hydraulic oil, the hydraulic oil pushes the secondary piston 2 to move in the retracting direction, and simultaneously, the hydraulic oil in the intermediate oil chamber 30 is extruded into the side oil chamber 20 through the communication hole 4, so that the primary piston 3 is pushed to move in the retracting direction until the hydraulic oil in the intermediate oil chamber 30 is completely pressed on the side oil chamber 20, and at this time, the primary piston 2 and the secondary piston 3 reach the retracting limit position at the same time.
After the primary piston 2 is provided with the compensating valve 5, when the double-section hydraulic cylinder moves in the extending direction, hydraulic oil is introduced into the bottom oil-filled cavity 10, the oil pressure pushes the primary piston 2 to move in the extending direction, and meanwhile, the hydraulic oil in the side oil cavity 20 is extruded into the middle oil cavity 30 through the communicating hole 4, and then the secondary piston 3 is pushed to move in the extending direction. When the hydraulic oil in the intermediate oil chamber 30 and the side oil chamber 20 leaks, that is, the amount of the oil becomes small, the primary piston 2 is continuously pressed by the hydraulic oil in the bottom oil-filled chamber 10, so that the primary piston can directly reach the limit position, and the hydraulic oil in the intermediate oil chamber 30 and the side oil chamber 20 runs off, so that the secondary piston 3 cannot reach the limit position. At this time, since the oil pressure in the bottom oil charge chamber 10 is continuously increased until the oil pressure at the bottom opening is greater than the sum of the oil pressure at the top opening, that is, the oil pressure of the intermediate oil chamber 30 and the pressure of the spring 53, the compensation valve 5 is opened, and the hydraulic oil in the bottom oil charge chamber 10 is charged into the intermediate oil chamber 30, and the leaked portion is replenished, so that the secondary piston 3 reaches the limit position. On the other hand, before the two-section hydraulic cylinder moves in the extending direction, since the compensation valve 5 is in the open state at the retracted extreme position, the excess hydraulic oil can also directly flow into the bottom oil-filled chamber 10 from the compensation valve 5 and be discharged, so that the hydraulic oil amount in the middle oil chamber 30 and the side oil chamber 20 does not increase when the two-section hydraulic cylinder moves in the extending direction.
After the primary piston 2 is provided with the compensating valve 5, when the double-section hydraulic cylinder moves in the retracting direction, hydraulic oil is introduced into the top oil-filled cavity 40, the oil pressure pushes the secondary piston 3 to move in the retracting direction, and meanwhile, the hydraulic oil in the middle oil cavity 30 is extruded into the side oil cavity 20 through the communication hole 4, so that the primary piston 2 is pushed to move in the retracting direction. When the hydraulic oil in the intermediate oil chamber 30 and the side oil chamber 20 becomes more due to inflow of the hydraulic oil in other portions, the primary piston 2 continues to receive the pressure transmitted by the hydraulic oil in the top oil-filled chamber 40, and thus the limit position is reached directly, whereas when the hydraulic oil in the intermediate oil chamber 30 and the side oil chamber 20 becomes more, the secondary piston 3 does not reach the limit position yet when the primary piston 2 reaches the limit position directly. At this time, since the primary piston 2 has come into contact with the top inner wall of the cylinder block 1, the portion of the compensation valve 5 protruding out of the bottom opening is pushed in by the inner wall of the cylinder block 1 and the compensation valve 5 is opened, and at this time, the surplus hydraulic oil in the intermediate oil chamber 30 and the side oil chamber 20 flows into the bottom oil-filled chamber 10 through the compensation valve 5 and is discharged, and then the secondary piston 3 reaches the limit position. On the other hand, when the two-section hydraulic cylinder moves in the retracting direction, if the hydraulic oil leakage in the intermediate oil chamber 30 and the side oil chamber 20 is reduced, the secondary piston 3 reaches the limit position first, and when the two-section hydraulic cylinder moves in the retracting direction next time, the compensation valve 5 is opened at the extended limit position to supplement the lost hydraulic oil, and the hydraulic oil amount in the intermediate oil chamber and the side oil chamber is recovered to the normal value, so that the condition that the hydraulic oil amount in the intermediate oil chamber 30 and the side oil chamber 20 is reduced is not considered when the two-section hydraulic cylinder moves in the retracting direction.
Claims (10)
1. A two-section hydraulic cylinder including a primary piston, a secondary piston, and a cylinder block, wherein a bottom oil-filled chamber is formed between a bottom of the cylinder block and the primary piston, and an intermediate oil chamber is formed between the secondary piston and the primary piston,
the double-section hydraulic cylinder further comprises a compensation valve, the compensation valve is arranged on the primary piston, and when the primary piston reaches a retraction limit position or an extension limit position firstly, the compensation valve is opened so that the bottom oil filling cavity is communicated with the middle oil cavity.
2. A double-section hydraulic cylinder as in claim 1 wherein the makeup valve is opened by electrical, hydraulic, or mechanical means.
3. The double-section hydraulic cylinder of claim 2, wherein the compensation valve is a check valve and is opened one way when the pressure in the bottom charge chamber is greater than the sum of the pressure in the intermediate oil chamber and a pressure set point for the compensation valve, the pressure set point for the compensation valve being the maximum pressure in the direction in which the compensation valve acts on the bottom charge chamber.
4. The double-section hydraulic cylinder of claim 3, wherein when the primary piston contacts the bottom of the cylinder block, the compensation valve is pushed open by the bottom of the cylinder block to communicate the bottom oil-filled chamber with the intermediate oil chamber.
5. The two-section hydraulic cylinder as claimed in claim 1, wherein a side oil chamber is further formed between said primary piston and said cylinder block, said side oil chamber communicating with said intermediate oil chamber through a communication hole provided in a surface of said primary piston, said side oil chamber and said intermediate oil chamber forming a closed oil chamber.
6. The double-section hydraulic cylinder according to claim 4, wherein the compensation valve includes a communication passage and a seal, an end of the communication passage that opens to the bottom oil-filling chamber is open at a bottom, an end of the communication passage that opens to the intermediate oil chamber is open at a top, the seal is pressed against and seals the bottom, and a portion of the seal protrudes from the bottom, and when the seal is open, the compensation valve is open.
7. The double-segment hydraulic cylinder of claim 6 wherein the portion of the seal extending out of the bottom opening has a length of 1 mm to 2 mm.
8. The double-segment hydraulic cylinder as claimed in claim 6, wherein the seal is compressed against and seals the bottom opening by a spring.
9. The double-section hydraulic cylinder of claim 8, wherein the force of the spring against the seal is less than a system pressure of the double-section hydraulic cylinder, the system pressure being a maximum oil pressure of the double-section hydraulic cylinder.
10. The double-section hydraulic cylinder of claim 9, wherein the compensation valve opens when the oil pressure at the bottom opening is greater than the sum of the oil pressure at the top opening and the pressure of the spring; when the primary piston is at the retraction limit position, one end of the compensation valve is pushed back to the communication channel through the inner wall of the cylinder body, and the compensation valve is opened.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921277238.3U CN210484249U (en) | 2019-08-05 | 2019-08-05 | Double-section hydraulic cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921277238.3U CN210484249U (en) | 2019-08-05 | 2019-08-05 | Double-section hydraulic cylinder |
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| Publication Number | Publication Date |
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| CN210484249U true CN210484249U (en) | 2020-05-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201921277238.3U Active CN210484249U (en) | 2019-08-05 | 2019-08-05 | Double-section hydraulic cylinder |
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| CN (1) | CN210484249U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110454463A (en) * | 2019-08-05 | 2019-11-15 | 上海医疗器械股份有限公司 | Binodal hydraulic cylinder |
-
2019
- 2019-08-05 CN CN201921277238.3U patent/CN210484249U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110454463A (en) * | 2019-08-05 | 2019-11-15 | 上海医疗器械股份有限公司 | Binodal hydraulic cylinder |
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| TR01 | Transfer of patent right |
Effective date of registration: 20211201 Address after: No.961, Kangqiao Road, Kangqiao Industrial Zone, Pudong New Area, Shanghai, 201315 Patentee after: SHANGHAI FIMET MEDICAL INSTRUMENT Co.,Ltd. Address before: 200136 No. 515, jiajiaqiao Road, Pudong New Area, Shanghai Patentee before: SHANGHAI MEDICAL INSTRUMENTS Co.,Ltd. |
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| TR01 | Transfer of patent right |