CN201003474Y - Reciprocating-piston type double acting hydraulic compressor - Google Patents
Reciprocating-piston type double acting hydraulic compressor Download PDFInfo
- Publication number
- CN201003474Y CN201003474Y CNU2006200987584U CN200620098758U CN201003474Y CN 201003474 Y CN201003474 Y CN 201003474Y CN U2006200987584 U CNU2006200987584 U CN U2006200987584U CN 200620098758 U CN200620098758 U CN 200620098758U CN 201003474 Y CN201003474 Y CN 201003474Y
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Abstract
The utility model relates to a reciprocate piston type double-acting liquid compressor, consisting of a hydraumatic cylinder, an inlet unit, an outlet unit, an oil-way unit and a control unit, and is characterized in: an I-shaped piston is arranged in the hydraumatic cylinder so as to form four cavities inside the hydraumatic cylinder i.e. orderly the first air cavity, the first oil cavity, the second oil cavity and the second air cavity; the inlet unit is communicated respectively with two air cavities of the double-acting hydraumatic cylinder through a first ball valve; the outlet unit is communicated respectively with the two air cavities of the double-acting hydraumatic cylinder through a cooler; the oil unit is communicated respectively with the two oil cavities of the double-acting hydraumatic cylinder through a reversing valve. Thanks to the adoption of the double-acting liquid compressor, when the aerating pressure is too high, the pressure is compressed rather than lowered, hence the energy efficiently saved; thanks to the adoption of the hydraumatic drive, the compressor produces small noises, requires low cost in production and operation and absorbs and discharges pressure in a wide area; thanks to the adoption of two-step or multi-step compressing, the pressure on the oil pump is reduced and the temperature of the compressing dielectric materials is reduced.
Description
Technical field
The utility model belongs to a kind of hydraulic pressure compressor, particularly a kind of reciprocating piston type double-action hydraulic pressure compressor.
Background technique
At present, known hydraulic pressure compressor has a lot of advantages than connecting rod piston gas compressor.The connecting rod piston gas compressor, its manufacturing technology maturation is used wider.But its amount of parts is many, volume weight and floor space are all big, required motor power is big under many, the identical operating modes of easily damaged parts, therefore, and its operating cost height.And its suction and discharge scope is narrower, the compression noise is big.In order to adapt to the pressure of inspiration(Pi) of its regulation, often will compress again after the pressurized gas step-down, wasted the energy of compressed media.And the hydraulic pressure compressor has two kinds.A kind of is floating piston, does not promptly have piston rod, advances pressure oil below the cylinder, above air inlet, middlely separate with piston.No matter suction pressure is high or low, the pressure of its required hydraulic oil all is the exhaust pressure of gas, and the power of required like this driving machine is just big, wastes energy, and the unit operation cost is also higher.Another kind is a horizontal compressor, and the centre is an oil cylinder, and two ends respectively connect a single-acting cylinder, allows the non-compression chamber of cylinder communicate with atmosphere.This spline structure is comparatively complicated, and its axial length is quite long.Aspect the Stroke Control of hydraulic pressure compressor, at present used all is to increase by a cover mechanism in the cylinder of compressed media, produces electrical signal when piston runs to stop, controls the method for hydraulic oil commutation.This method cost is higher.Because in the compression chamber be high temperature, high pressure, but also explosion-proof, require too high.Be difficult for realizing.
Summary of the invention
It is the double-action compression that the purpose of this utility model is to provide a kind of compresser cylinder, and compression cylinder and oil cylinder unite two into one, in employing aspect the piston stroke control reciprocating piston type double-action hydraulic pressure compressor that the Stroke Control element is controlled the hydraulic oil commutation is installed in hydraulic oil, to overcome above-mentioned deficiency.
To achieve these goals, the utility model is by the double-action hydraulic cylinder, the air inlet unit, exhaust unit, oil circuit unit and control unit constitute, wherein the air inlet unit communicates by the air cavity of first ball valve with the double-action hydraulic cylinder, exhaust unit communicates by the air cavity of cooler with the double-action hydraulic cylinder, the oil circuit unit communicates by the oil pocket of selector valve with the double-action hydraulic cylinder, control unit is realized air inlet, the control of exhaust and oil circuit unit, be characterized in: be provided with an I-shaped piston in the double-action hydraulic cylinder, a spacing dividing plate that is fixed on the cylinder body is set in I-shaped piston, spacing diaphragm housing ring is on the piston rod of I-shaped piston, make and form 4 cavitys in the hydraulic cylinder, be first air cavity in regular turn, first oil pocket, second oil pocket and second air cavity, the air inlet unit communicates with two air cavitys of double-action hydraulic cylinder respectively by first ball valve, exhaust unit communicates with two air cavitys of double-action hydraulic cylinder respectively by cooler, the oil circuit unit communicates with two oil pockets of double-action hydraulic cylinder respectively by selector valve, spacing dividing plate is provided with sensor, and the output of sensor is connected with control unit.
At least two of above-mentioned double-action hydraulic cylinders, the double-action hydraulic cylinder exhaust unit of previous stage communicates with the air inlet unit of back one-level, and the oil circuit unit communicates by the oil pocket of selector valve with each double-action hydraulic cylinder respectively, forms two-stage or multistage compression.
Because the utility model adopts the double-action hydraulic cylinder, make the utility model when pressure of inspiration(Pi) is too high, not need step-down and directly compression, exhaust pressure=suction pressure+oil pressure, hence one can see that, when suction pressure is higher, required oil pressure is on the contrary little, and its driving power is just little, to such an extent as to energy-efficient; The utility model compressor adopts hydraulic driving, so noise is low, low cost of manufacture, low, the suction pressure broad of operating cost, is specially adapted to the higher mesohigh gas of pressure of inspiration(Pi) or the compression of liquid; Adopt two-stage or multistage compression, can reduce the pressure of oil pump, the temperature of reduction compressed media.
Description of drawings
Fig. 1 is a structural principle schematic representation of the present utility model.
Fig. 2 is a two stage compression structural principle schematic representation of the present utility model.
Fig. 3 is the structural representation of the utility model double-action hydraulic cylinder.
Among the figure: 1-first ball valve, the 2-cooler, the 3-safety valve, 4-second ball valve, the 5-one-way valve, the 6-suction valve, the 7-outlet valve, the 8-cylinder, the 9-piston, the 10-accumulator, the 11-filter, the 12-oil cooler, the 13-oil pump, the 14-oil sump, the 15-selector valve, the 16-limit sensors, the 17-relief valve, the 18-lower connecting block, 20-the one O type circle, 21-the 2nd O type circle, the 22-water pipe adapter, 23-water jacket cylinder, the 24-compression cylinder, 25-first y-type seal ring, 27-sensing joint, the spacing dividing plate of 28-, 29-sensing body, 30-second y-type seal ring, the 31-piston rod, the last contiguous block of 32-, 33-air valve gland.
Embodiment
The utility model is described in further detail below in conjunction with drawings and Examples.
The utility model (Fig. 1: solid line partly is gas circuit and liquid road, and dotted portion is a control wiring) piston 9 is installed the back with cylinder 8 and is formed A, B, four chambeies of C, D, and wherein, A, D are air cavity, and B, C are oil pocket.Hydraulic oil is through oil pump 13, and straight-through (state among the figure) that entered filter 11, selector valve 15 by oil sump 14 enters the B chamber, promotes piston 9 and moves upward, and simultaneously, the oil in C chamber then through straight-through (state among the figure), the oil cooler 12 of selector valve 15, is got back to oil sump 14.In the process that piston 9 moves upward, A chamber volume dwindles, and gas pressure increases, and suction valve 6 cuts out, and outlet valve 7 is opened, and gas is discharged in the gas holder through supercooler 2, second ball valve 4 and one-way valve 5, forms the exhaust process in A chamber.In this process, when the A cavity pressure surpasses exhaust pressure, this moment A cavity pressure=B cavity pressure-C cavity pressure+D cavity pressure.Because the C chamber communicates with oil sump, promptly communicates with atmosphere, can disregard, and the D chamber is the gas suction pressure.Therefore, Ci Shi A cavity pressure (being exhaust pressure)=oil pressure+suction pressure.Hence one can see that, and the suction pressure of gas is big more, and required oil pressure is just more little, and power demand is just more little.In the process that piston 9 moves upward, D chamber volume can increase, and cavity pressure reduces, and suction valve 6 is opened, and gas enters the D chamber through first ball valve 1 from suction valve 6, produces the intake process in D chamber.When piston 9 moved to top dead center, piston 9 can contact limit sensors 16, and 15 commutations of control selector valve make selector valve 15 be in the state that intersection communicates.At this moment, pressure oil will flow to the C chamber, and the oil in the B chamber is just got back to oil sump 14, and simultaneously, D finishes compression process in the chamber, and intake process is then finished in the A chamber.So repeatedly.In compression process, if the gas circuit overpressure, gas then enters in the atmosphere by safety valve 3; If the oil circuit pressure transient, 10 effect of playing voltage stabilizing of accumulator; If oil circuit overpressure, pressure oil then can directly be got back to oil sump 14 by relief valve 17.At this moment, by A cavity pressure (being exhaust pressure)=oil pressure+suction pressure as can be known, the required working pressure of oil pump is: row pressure-entrance pressure.Under the certain situation of row pressure, entrance pressure is high more, and required pressure fuel pump is more little, when entrance pressure for hour, the required pressure maximum of oil pump, this moment, power demand also was maximum (establishing power is W1).And traditional crank-connecting rod compressor, when operating mode was identical, entrance pressure was high more, power demand is big more, to join the power of driving machine also big more.When entrance pressure for hour, power demand minimum (establishing power is W2), but the power of driving machine can not hour join by entrance pressure, the power (establishing power is W3) of required driving machine is joined when can only be by entrance pressure maximum.From theory, W1=W2, W3＞W2.In view of this, it is little that this model utility is joined driving machine power, thereby reach energy-conservation and save the purpose of operating cost.
The utility model can change the oil circuit unit into hydraulic workstation (with being installed together in all hydraulic sets of elements); For using two stage compression, increased a cylinder 8, the one-level compression is become two stage compression, can reduce the pressure ratio of gas like this, comparatively favourable to compression process.Certainly can also be increased to three grades or more, the pressure of required like this oil pump just reduces relatively, and it is more favourable to work, but product cost can increase; Simultaneously, if increase discharge capacity, the number of cylinders that only needs to increase each grade gets final product.
The double-action hydraulic cylinder of the utility model model utility compressor is that oil hydraulic cylinder and compression cylinder are united two into one, one end of cylinder is a hydraulic oil, the other end is a compressed media, the centre separates with piston 9, piston 9 is in the process that moves up and down, and in the time of near sensing body 29 moves to sensing joint 27, limit sensors 16 will produce electrical signal, the commutation of pilot pressure oil reaches the purpose that piston 9 commutates.This control has overcome the difficult problem of prior art in piston 9 commutations.On structure, the operation part is than the confidential much less of conventional compression, and easily damaged parts is a standard piece, and it is convenient to change.Adopt distance control, overcome the air valve of traditional compressor and the Strike note of movement parts, reduced noise.
The content that is not described in detail in this specification belongs to related domain professional and technical personnel's known prior art.
Claims (2)
1, a kind of reciprocating piston type double-action hydraulic pressure compressor, by double-action hydraulic cylinder (8), the air inlet unit, exhaust unit, oil circuit unit and control unit constitute, wherein the air inlet unit communicates by the air cavity of first ball valve (1) with double-action hydraulic cylinder (8), exhaust unit communicates by the air cavity of cooler (2) with double-action hydraulic cylinder (8), the oil circuit unit communicates by the oil pocket of selector valve (15) with double-action hydraulic cylinder (8), control unit is realized air inlet, the control of exhaust and oil circuit unit, it is characterized in that: be provided with an I-shaped piston (9) in the double-action hydraulic cylinder (8), a spacing dividing plate (16) that is fixed on the cylinder body is set in I-shaped piston (9), spacing dividing plate (16) is enclosed within on the piston rod (31) of I-shaped piston (9), make and form 4 cavitys in the hydraulic cylinder, 4 cavitys are first air cavity (A) in regular turn, first oil pocket (B), second oil pocket (C) and second air cavity (D), the air inlet unit by first ball valve (1) respectively with two air cavitys (A) of double-action hydraulic cylinder (8), (D) communicate, exhaust unit by cooler (2) respectively with two air cavitys (B) of double-action hydraulic cylinder (8), (C) communicate, the oil circuit unit communicates with two oil pockets of double-action hydraulic cylinder (8) respectively by selector valve (15), spacing dividing plate (16) is provided with sensor, and the output of sensor is connected with control unit.
2, reciprocating piston type double-action hydraulic pressure compressor as claimed in claim 1, it is characterized in that: (8) at least two of double-action hydraulic cylinders, the double-action hydraulic cylinder exhaust unit of previous stage communicates with the air inlet unit of back one-level, the oil circuit unit communicates by the oil pocket of selector valve with each double-action hydraulic cylinder respectively, forms two-stage or multistage compression.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200987584U CN201003474Y (en) | 2006-09-01 | 2006-09-01 | Reciprocating-piston type double acting hydraulic compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200987584U CN201003474Y (en) | 2006-09-01 | 2006-09-01 | Reciprocating-piston type double acting hydraulic compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201003474Y true CN201003474Y (en) | 2008-01-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006200987584U Expired - Lifetime CN201003474Y (en) | 2006-09-01 | 2006-09-01 | Reciprocating-piston type double acting hydraulic compressor |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101907017A (en) * | 2009-06-02 | 2010-12-08 | 杨焕利 | Hydraulic energy converter |
| CN102032145A (en) * | 2010-10-22 | 2011-04-27 | 中国石油天然气股份有限公司 | A differential pressure power booster |
| CN101539132B (en) * | 2009-04-21 | 2012-07-04 | 西安交通大学 | Linear transmission mechanism of reciprocating dynamic machinery |
| CN104533853A (en) * | 2014-12-25 | 2015-04-22 | 北京普发兴业动力科技发展有限责任公司 | Pressure self-adaptive hydraulic reversing system |
| WO2016037500A1 (en) * | 2014-09-09 | 2016-03-17 | 武汉齐达康环保科技有限公司 | Reciprocating plunger-type gas compressor and method |
| CN107859612A (en) * | 2017-11-23 | 2018-03-30 | 陕西昆仑机械装备制造有限责任公司 | Vertical Combination supercharger |
| CN108375999A (en) * | 2018-05-21 | 2018-08-07 | 天津理工大学 | A kind of flow stable-pressure device and its method for stabilizing voltage based on parallel cylinder |
| CN109404252A (en) * | 2017-08-17 | 2019-03-01 | 深圳市重力悟空聚能技术开发有限公司 | A kind of energy-efficient air-conditioning compressor |
| CN110273822A (en) * | 2019-06-09 | 2019-09-24 | 天津融渌众乐科技有限公司 | A kind of energy providing device of pair of positive work energy and negative work total energy approach |
| CN112196846A (en) * | 2020-10-22 | 2021-01-08 | 欧阳友军 | Double-medium low-energy-consumption hydraulic power system and power output method |
| CN112855511A (en) * | 2020-12-30 | 2021-05-28 | 自贡通达机器制造有限公司 | Natural gas hydraulic compressor |
| CN113775504A (en) * | 2021-11-09 | 2021-12-10 | 东营众志石油工程技术有限公司 | Intelligence associated gas supercharging device |
| CN118293047A (en) * | 2024-06-05 | 2024-07-05 | 博山水泵制造厂 | Hydrogen compressor |
-
2006
- 2006-09-01 CN CNU2006200987584U patent/CN201003474Y/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101539132B (en) * | 2009-04-21 | 2012-07-04 | 西安交通大学 | Linear transmission mechanism of reciprocating dynamic machinery |
| CN101907017A (en) * | 2009-06-02 | 2010-12-08 | 杨焕利 | Hydraulic energy converter |
| CN102032145A (en) * | 2010-10-22 | 2011-04-27 | 中国石油天然气股份有限公司 | A differential pressure power booster |
| CN102032145B (en) * | 2010-10-22 | 2012-10-17 | 中国石油天然气股份有限公司 | A differential pressure power booster |
| WO2016037500A1 (en) * | 2014-09-09 | 2016-03-17 | 武汉齐达康环保科技有限公司 | Reciprocating plunger-type gas compressor and method |
| CN104533853A (en) * | 2014-12-25 | 2015-04-22 | 北京普发兴业动力科技发展有限责任公司 | Pressure self-adaptive hydraulic reversing system |
| CN109404252A (en) * | 2017-08-17 | 2019-03-01 | 深圳市重力悟空聚能技术开发有限公司 | A kind of energy-efficient air-conditioning compressor |
| CN107859612A (en) * | 2017-11-23 | 2018-03-30 | 陕西昆仑机械装备制造有限责任公司 | Vertical Combination supercharger |
| CN108375999A (en) * | 2018-05-21 | 2018-08-07 | 天津理工大学 | A kind of flow stable-pressure device and its method for stabilizing voltage based on parallel cylinder |
| CN110273822A (en) * | 2019-06-09 | 2019-09-24 | 天津融渌众乐科技有限公司 | A kind of energy providing device of pair of positive work energy and negative work total energy approach |
| CN112196846A (en) * | 2020-10-22 | 2021-01-08 | 欧阳友军 | Double-medium low-energy-consumption hydraulic power system and power output method |
| CN112855511A (en) * | 2020-12-30 | 2021-05-28 | 自贡通达机器制造有限公司 | Natural gas hydraulic compressor |
| CN113775504A (en) * | 2021-11-09 | 2021-12-10 | 东营众志石油工程技术有限公司 | Intelligence associated gas supercharging device |
| CN118293047A (en) * | 2024-06-05 | 2024-07-05 | 博山水泵制造厂 | Hydrogen compressor |
| CN118293047B (en) * | 2024-06-05 | 2024-11-05 | 博山水泵制造厂 | Hydrogen compressor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| COR | Change of bibliographic data |
Free format text: CORRECT: CO-PATENTEE TO: ZHANG YEJIAN ^ |
|
| CU01 | Correction of utility model patent |
Correction item: Co-patentee Correct: Zhang Yejian Number: 02 Page: The title page Volume: 24 |
|
| CU03 | Correction of utility model patent gazette |
Correction item: Co-patentee Correct: Zhang Yejian Number: 02 Volume: 24 |
|
| ERR | Gazette correction |
Free format text: CORRECT: CO-PATENTEE; FROM: NONE ^ TO: ZHANG YEJIAN ^ |
|
| ASS | Succession or assignment of patent right |
Owner name: WUHAN QIDAKANG ENVIRONMENTAL PROTECTION TECHNOLOGY Free format text: FORMER OWNER: FANG XIANLU Effective date: 20090522 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20090522 Address after: Hi Tech Innovation Center, 626 Hanyang Road, Hanyang District, Hubei, Wuhan Province, China: 430051 Patentee after: WUHAN QIDAKANG ENVIRONMENTAL PROTECTION TECHNOLOGY CO., LTD. Address before: First class (nine) of Wu Jiashan three middle school in Wuhan, Hubei Province, zip code: 430040 Co-patentee before: Zhang Yejian Patentee before: Fang Xian deer |
|
| CX01 | Expiry of patent term |
Granted publication date: 20080109 |
|
| EXPY | Termination of patent right or utility model |