CN204113810U - A kind of high-pressure high-flow Sealing test system - Google Patents
A kind of high-pressure high-flow Sealing test system Download PDFInfo
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- CN204113810U CN204113810U CN201420541229.1U CN201420541229U CN204113810U CN 204113810 U CN204113810 U CN 204113810U CN 201420541229 U CN201420541229 U CN 201420541229U CN 204113810 U CN204113810 U CN 204113810U
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- pressure
- valve
- hydraulic cylinder
- test fluid
- loading hydraulic
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Abstract
The utility model discloses a kind of high-pressure high-flow Sealing test system, this system comprises high-voltage electromagnetic selector valve, radial plunger pump, variable-frequency motor, electromagnetic relief valve, test fluid cylinder pressure, loading hydraulic cylinder, one-way throttle valve etc.In the utility model, Sealing is arranged on larger-size test fluid cylinder pressure, the loading hydraulic cylinder utilizing size less and larger-size test fluid cylinder pressure with the use of, loading hydraulic cylinder, on the one hand for test fluid cylinder pressure provides on-load pressure, utilizes the rodless cavity difference in areas of test fluid cylinder pressure and loading hydraulic cylinder oily for test fluid cylinder pressure supplements the high-volume hydraulic that high-pressure small-displacement radial plunger pump can not provide simultaneously.Overcome Sealing test system in the past and, to the dependence of high-pressure large-displacement pump, reduce the power level of variable-frequency motor, what reduce test stand builds cost.
Description
Technical field
The utility model relates to hydraulic control system field, particularly a kind of high-pressure high-flow Sealing test system based on high-pressure small-displacement oil hydraulic pump.
Background technique
In the process of a hydraulic cylinder sealing element of exploitation, the object test of product is often as last link of design, and thus the quality of object test effect has conclusive effect for the performance assessing this product, directly concerns the success or failure of design.In the test carrying out the test of hydraulic cylinder sealing element sealing effect, in order to better simulate the actual conditions of Sealing, often need high-pressure high-flow hydraulic oil source.
Tradition obtains high-pressure high-flow hydraulic oil and mainly contains following two approach: the first directly adopts high-pressure high-flow pump to obtain, although the system structure that this method is set up is relatively simple, but the motor needing power level higher matches with it, therefore its cost is higher, huge structure, energy consumption is high, and macroeconomic is not high; The second be adopt low pressure and mass flow pump and pressurizing cylinder with the use of, although comparatively the first declines the power level of this entire system to some extent, but its complex structure, Economy is still not high, the more important thing is that the technology of current pressurizing cylinder is also immature, this will certainly affect the reliability and stability of whole system.
Model utility content
Main purpose of the present utility model is to overcome above-mentioned defect of the prior art, proposes the high-pressure high-flow Sealing test system based on high-pressure low-flow oil hydraulic pump that a kind of structure is simple, reduce costs.
The utility model adopts following technological scheme:
A kind of high-pressure high-flow Sealing test system, is characterized in that: comprise radial plunger pump 1, variable-frequency motor 2, electromagnetic relief valve 3, high-voltage electromagnetic selector valve 4, first one-way throttle valve 5, second one-way throttle valve 6, loading hydraulic cylinder 7 and test fluid cylinder pressure 8; The transmission shaft of this radial plunger pump 1 is connected with variable-frequency motor 2 output shaft, the oil outlet of radial plunger pump 1 is connected to the filler opening of electromagnetic relief valve 3, and the T mouth of the filler opening of radial plunger pump 1, the oil outlet of electromagnetic relief valve 3 and high-voltage electromagnetic selector valve 4 is all connected to fuel tank; The piston rod of loading hydraulic cylinder 7 is connected with the piston rod of test fluid cylinder pressure 8; The A mouth of high-voltage electromagnetic selector valve 4 divides two-way, and road first one-way throttle valve 5 is connected to the rodless cavity of loading hydraulic cylinder 7, and another road is directly connected with the rodless cavity of test fluid cylinder pressure 8; The B mouth of high-voltage electromagnetic selector valve 4 divides two-way, and road second one-way throttle valve 6 is connected to the rod chamber of loading hydraulic cylinder 7, and another road is directly connected with the rod chamber of test fluid cylinder pressure 8.
Preferably, described radial plunger pump is high-pressure small-displacement radial plunger pump.
Preferably, the first one-way throttle valve 5 comprises one-way valve in parallel and throttle valve, and the conducting direction of one-way valve is that the A mouth of high-voltage electromagnetic selector valve 4 flows to loading hydraulic cylinder 7 rodless cavity.
Preferably, the second one-way throttle valve 6 comprises one-way valve in parallel and throttle valve, and the conducting direction of one-way valve is that the B mouth of high-voltage electromagnetic selector valve 4 flows to loading hydraulic cylinder 7 rod chamber.
Preferably, described loading hydraulic cylinder 7 is identical with the diameter of piston rod of described test fluid cylinder pressure 8, the rodless cavity diameter D of described loading hydraulic cylinder 7
2be less than the rodless cavity diameter D of test fluid cylinder pressure 8
1.
From above-mentioned to description of the present utility model, compared with prior art, the utility model has following beneficial effect:
One, by the difference in areas of the rodless cavity of appropriate design two oil hydraulic cylinders, make to utilize a high-pressure low-flow pump just can meet the demand of test, eliminate the dependence to high-power pump and motor, thus make whole system power level and cost etc. comparatively before two schemes had and significantly reduced, what regulate solenoid directional control valve obtains the movement direction that electric position can change oil hydraulic cylinder, regulate one-way throttle valve choke area can the pressure of hydraulic control cylinder respective cavities, the rotating speed of adjustment variable-frequency motor can control the travelling speed of push rod.
Two, be instead of in conventional ADS driving by the adjustment of motor speed and realize matching of oil hydraulic pump flow and the required flow of test by changing hydraulic pump discharge.Thus system can adopt metering pump to replace variable displacement pump, this not only lowers cost, simultaneously because the change discharge capacity of the relative variable displacement pump of variable speed of motor has dynamic response faster, and then can realize the coupling of oil hydraulic pump flow and the required flow of test dynamically.
Accompanying drawing explanation
Fig. 1 structure principle chart of the present utility model.
Wherein:
1, radial plunger pump 2, variable-frequency motor
3, electromagnetic relief valve 4, high-voltage electromagnetic selector valve
5, the first one-way throttle valve 6, second one-way throttle valve
7, loading hydraulic cylinder 8, test fluid cylinder pressure
9, fuel tank
Embodiment
Below by way of embodiment, the utility model will be further described.
With reference to Fig. 1, a kind of high-pressure high-flow Sealing test system, comprises radial plunger pump 1, variable-frequency motor 2, electromagnetic relief valve 3, high-voltage electromagnetic selector valve 4, first one-way throttle valve 5, second one-way throttle valve 6, loading hydraulic cylinder 7 and test fluid cylinder pressure 8.The transmission shaft of this radial plunger pump 1 is connected with variable-frequency motor 2 output shaft, the oil outlet of radial plunger pump 1 is connected to the filler opening of electromagnetic relief valve 3, the T mouth of the filler opening of radial plunger pump 1, the oil outlet of electromagnetic relief valve 3 and high-voltage electromagnetic selector valve 4 is all connected to fuel tank 9, and fuel tank 9 can arrange one or more according to actual needs.
The piston rod of loading hydraulic cylinder 7 is connected with the piston rod of test fluid cylinder pressure 8.The A mouth of high-voltage electromagnetic selector valve 4 divides two-way, one tunnel first one-way throttle valve 5 is connected to the rodless cavity of loading hydraulic cylinder 7, another road is directly connected with the rodless cavity of test fluid cylinder pressure 8, first one-way throttle valve 5 comprises one-way valve in parallel and throttle valve, and wherein the conducting direction of one-way valve is that the A mouth of high-voltage electromagnetic selector valve 4 flows to loading hydraulic cylinder 7 rodless cavity.The B mouth of high-voltage electromagnetic selector valve 4 divides two-way, one tunnel second one-way throttle valve 6 is connected to the rod chamber of loading hydraulic cylinder 7, another road is directly connected with the rod chamber of test fluid cylinder pressure 8, second one-way throttle valve 6 comprises one-way valve in parallel and throttle valve, and wherein the conducting direction of one-way valve is that the B mouth of high-voltage electromagnetic selector valve 4 flows to loading hydraulic cylinder 7 rod chamber.
Radial plunger pump 1 of the present utility model is high-pressure small-displacement radial plunger pump, the high pressure of the conventional industrial oil hydraulic pump of high-pressure large-displacement is generally less than 35MPa, but flow can reach a few hectolitre, even larger, but the pressure rating of high-pressure small-displacement radial plunger pump of the present utility model is 45MPa, 63MPa etc., flow is less, is generally less than 20L/min.Loading hydraulic cylinder 7 is identical with the diameter of piston rod d of test fluid cylinder pressure 8, and the diameter of rodless cavity is different, the rodless cavity diameter D of loading hydraulic cylinder 7
2be less than the rodless cavity diameter D of test fluid cylinder pressure 8
1.The radial plunger pump 1 that oil sources is variable-frequency motor 2, high-pressure small-displacement and fuel tank 9 coordinate to be provided, and is regulated the speed of test fluid cylinder pressure 8 by the adjustment of variable-frequency motor 2 rotating speed.In the utility model, Sealing is arranged on larger-size test fluid cylinder pressure 8, the loading hydraulic cylinder 7 utilizing size less and larger-size test fluid cylinder pressure 8 with the use of, loading hydraulic cylinder 7 one aspect provides on-load pressure for test fluid cylinder pressure 8, utilizes the rodless cavity difference in areas of test fluid cylinder pressure 8 and loading hydraulic cylinder 7 to supplement the high-volume hydraulic oil that high-pressure small-displacement radial plunger pump 1 can not provide for test fluid cylinder pressure 7 simultaneously.Overcome Sealing test system in the past and, to the dependence of high-pressure large-displacement pump, reduce the power level of variable-frequency motor, what reduce test stand builds cost.
The rodless cavity diameter of setting loading hydraulic cylinder 7 is D
2, rodless cavity and rod chamber pressure is respectively p
i1, p
i3, the rodless cavity diameter of setting test fluid cylinder pressure 8 is D
1, rodless cavity and rod chamber pressure are respectively p
i2, p
i4, the flow of setting radial plunger pump 1 is Q
p.
The working principle that the utility model is detailed is as follows:
Position one: when high-voltage electromagnetic selector valve 4 both sides electromagnet all must not electricity time, selector valve is positioned at meta, P mouth is connected with T mouth, the high pressure liquid force feed that high-pressure small-displacement radial plunger pump 1 exports enters valve body by the P mouth of high-voltage electromagnetic selector valve 4, directly flow back to fuel tank 9 by its T mouth, now cylinder pressure p
i1, p
i2, p
i3, p
i4equal, test system does not work.
Position two: when the left side electromagnet of high-voltage electromagnetic selector valve 4 obtains electric, selector valve P mouth is connected with A mouth, and T mouth is connected with B mouth.The high-pressure low-flow hydraulic oil that now radial plunger pump 1 of high-pressure small-displacement is discharged enters the rodless cavity of test fluid cylinder pressure 8 together with the hydraulic oil of loading hydraulic cylinder 7 rodless cavity, supposes that this hourly velocity of loading hydraulic cylinder 7 and test fluid cylinder pressure 8 is v
1, the flow Q of the radial plunger pump 1 of high-pressure small-displacement
p, then meet following relation:
Therefore,
therefore by appropriate design D
1and D
2namely the test condition of high-pressure high-flow is realized by high-pressure small-displacement radial plunger pump 1.
The non-return valve function of the first one-way throttle valve 5 is oppositely ended, and the hydraulic oil of loading hydraulic cylinder 7 rodless cavity flows through the restriction of the first one-way throttle valve 5, by the rodless cavity pressure p regulating the aperture of the restriction of the first one-way throttle valve 5 to realize regulating loading hydraulic cylinder 7
i1, due to loading hydraulic cylinder 7 rod chamber pressure p
i3with the rod chamber pressure p of test fluid cylinder pressure 8
i4be approximately zero, so the rodless cavity pressure P of test fluid cylinder pressure 8
i2=P
i1* D
2/ D
1, and then achieve the function of the rodless cavity pressure being regulated test fluid cylinder pressure 8 by the first one-way throttle valve 5.
Position three: when the right side electromagnet of high-voltage electromagnetic selector valve 4 obtains electric, selector valve P mouth is connected with B mouth, and T mouth is connected with A mouth.The high-pressure low-flow hydraulic oil that now high-pressure small-displacement radial plunger pump 1 is discharged enters the rod chamber of test fluid cylinder pressure 8 together with the hydraulic oil of loading hydraulic cylinder 7 rod chamber, supposes that the speed of now loading hydraulic cylinder 7 and test fluid cylinder pressure 8 is v
2, the flow Q of high-pressure small-displacement radial plunger pump 1
p, then meet following relation:
Therefore,
therefore by appropriate design D
1and D
2namely the test condition of high-pressure high-flow is realized by high-pressure small-displacement radial plunger pump 1.
The non-return valve function of the second one-way throttle valve 6 is oppositely ended, the hydraulic oil of the rod chamber of loading hydraulic cylinder 7 flows through the restriction of the second one-way throttle valve 6, by the rod chamber pressure p regulating the aperture of the restriction of the second one-way throttle valve 6 to realize regulating loading hydraulic cylinder 7
i3, due to loading hydraulic cylinder 7 rodless cavity pressure p
i1with the rodless cavity pressure p of test fluid cylinder pressure 8
i2be approximately zero, so the rod chamber pressure P of test fluid cylinder pressure 8
i4=P
i3* (D
2-d)/(D
1-d), and then achieve the function of the rod chamber pressure being regulated test fluid cylinder pressure 8 by the second one-way throttle valve 6.
Above are only embodiment of the present utility model; the test of oil hydraulic cylinder confidential paper is only an application direction of the present utility model; design concept of the present utility model is not limited thereto; all changes utilizing this design the utility model to be carried out to unsubstantiality, all should belong to the behavior of invading the utility model protection domain.
Claims (5)
1. a high-pressure high-flow Sealing test system, is characterized in that: comprise radial plunger pump (1), variable-frequency motor (2), electromagnetic relief valve (3), high-voltage electromagnetic selector valve (4), the first one-way throttle valve (5), the second one-way throttle valve (6), loading hydraulic cylinder (7) and test fluid cylinder pressure (8); The transmission shaft of this radial plunger pump (1) is connected with variable-frequency motor (2) output shaft, the oil outlet of radial plunger pump (1) is connected to the filler opening of electromagnetic relief valve (3), and the T mouth of the filler opening of radial plunger pump (1), the oil outlet of electromagnetic relief valve (3) and high-voltage electromagnetic selector valve (4) is all connected to fuel tank; The piston rod of loading hydraulic cylinder (7) is connected with the piston rod of test fluid cylinder pressure (8); The A mouth of high-voltage electromagnetic selector valve (4) divides two-way, and a road first one-way throttle valve (5) is connected to the rodless cavity of loading hydraulic cylinder (7), and another road is directly connected with the rodless cavity of test fluid cylinder pressure (8); The B mouth of high-voltage electromagnetic selector valve (4) divides two-way, and a road second one-way throttle valve (6) is connected to the rod chamber of loading hydraulic cylinder (7), and another road is directly connected with the rod chamber of test fluid cylinder pressure (8).
2. a kind of high-pressure high-flow Sealing test system as claimed in claim 1, is characterized in that: described radial plunger pump (1) is high-pressure small-displacement radial plunger pump.
3. a kind of high-pressure high-flow Sealing test system as claimed in claim 1, it is characterized in that: the first one-way throttle valve (5) comprises one-way valve in parallel and throttle valve, the conducting direction of one-way valve is that the A mouth of high-voltage electromagnetic selector valve (4) flows to loading hydraulic cylinder (7) rodless cavity.
4. a kind of high-pressure high-flow Sealing test system as claimed in claim 1, it is characterized in that: the second one-way throttle valve (6) comprises one-way valve in parallel and throttle valve, the conducting direction of one-way valve is that the B mouth of high-voltage electromagnetic selector valve (4) flows to loading hydraulic cylinder (7) rod chamber.
5. a kind of high-pressure high-flow Sealing test system as claimed in claim 1, it is characterized in that: described loading hydraulic cylinder (7) is identical with the diameter of piston rod of described test fluid cylinder pressure (8), the rodless cavity diameter D of described loading hydraulic cylinder (7)
2be less than the rodless cavity diameter D of test fluid cylinder pressure (8)
1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420541229.1U CN204113810U (en) | 2014-09-19 | 2014-09-19 | A kind of high-pressure high-flow Sealing test system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420541229.1U CN204113810U (en) | 2014-09-19 | 2014-09-19 | A kind of high-pressure high-flow Sealing test system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204113810U true CN204113810U (en) | 2015-01-21 |
Family
ID=52331124
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420541229.1U Withdrawn - After Issue CN204113810U (en) | 2014-09-19 | 2014-09-19 | A kind of high-pressure high-flow Sealing test system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204113810U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196829A (en) * | 2014-09-19 | 2014-12-10 | 华侨大学 | High-pressure high-flow sealing part test system |
| CN109386515A (en) * | 2018-12-06 | 2019-02-26 | 哈工新欧(岳阳)测控装备有限公司 | Energy-saving large_sized hydraulic cylinder testing stand |
-
2014
- 2014-09-19 CN CN201420541229.1U patent/CN204113810U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196829A (en) * | 2014-09-19 | 2014-12-10 | 华侨大学 | High-pressure high-flow sealing part test system |
| CN104196829B (en) * | 2014-09-19 | 2017-05-03 | 华侨大学 | High-pressure high-flow sealing part test system |
| CN109386515A (en) * | 2018-12-06 | 2019-02-26 | 哈工新欧(岳阳)测控装备有限公司 | Energy-saving large_sized hydraulic cylinder testing stand |
| CN109386515B (en) * | 2018-12-06 | 2024-03-19 | 哈工新欧(岳阳)测控装备有限公司 | Energy-saving large-sized hydraulic cylinder test bed |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20150121 Effective date of abandoning: 20170503 |