CN104214071A - Reciprocating plunger type gas compressor and method - Google Patents
Reciprocating plunger type gas compressor and method Download PDFInfo
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- CN104214071A CN104214071A CN201410454848.1A CN201410454848A CN104214071A CN 104214071 A CN104214071 A CN 104214071A CN 201410454848 A CN201410454848 A CN 201410454848A CN 104214071 A CN104214071 A CN 104214071A
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- 238000000034 method Methods 0.000 title claims abstract description 30
- 239000003921 oil Substances 0.000 claims abstract description 184
- 238000007906 compression Methods 0.000 claims abstract description 24
- 230000006835 compression Effects 0.000 claims abstract description 22
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 7
- 238000001816 cooling Methods 0.000 claims description 16
- 230000033001 locomotion Effects 0.000 claims description 15
- 239000010727 cylinder oil Substances 0.000 claims description 13
- 238000007789 sealing Methods 0.000 claims description 7
- 230000000694 effects Effects 0.000 claims description 4
- 238000007599 discharging Methods 0.000 claims description 3
- 238000013022 venting Methods 0.000 claims description 3
- 239000007788 liquid Substances 0.000 abstract description 3
- 230000003247 decreasing effect Effects 0.000 abstract 2
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000000047 product Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons
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- Engineering & Computer Science (AREA)
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Abstract
The invention relates to a compressor and a method, in particular to a reciprocating plunger type gas compressor and a method, which belong to the field of gas compression. The compressor which converts driving energy into hydraulic energy uses hydraulic oil to push a hydraulic piston, so that a plunger is driven to move up and down to compress gas, meanwhile, an air cylinder structure, the upper end and lower end of which are symmetric, is adopted, medium enters one air cylinder when compressed by another air cylinder, and consequently, not only is the energy of the sucked gas not wasted, but also the efficiency is high and energy is saved. The reciprocating plunger type gas compressor is particularly suitable for compressing medium-pressure and high-pressure gas or liquid with high suction pressure, moreover, because two-stage or multi-stage compression is adopted, the pressure of an oil pump can be decreased, the temperature of compressed medium can be decreased, and meanwhile, since hydraulic driving is adopted, noise is reduced effectively.
Description
Technical field
The present invention relates to a kind of compressor and method, belong to gas compression field, be specifically related to a kind of reciprocating plunger type gas compressor and method.
Background technique
At present, compressor of the prior art comprises hydraulic compressor and the compression of connecting rod gas piston.
Connecting rod piston gas compressor, its manufacturing technology is ripe, applies wider.But its amount of parts is many, volume weight and floor space are all comparatively large, required motor power is large under more, the identical operating mode of easily damaged parts, and operating cost is high; Meanwhile, its suction and discharge scope compared with narrow, compression noise large.In addition, in order to adapt to the pressure of inspiration(Pi) of its regulation, often needing to compress after pressurized gas step-down again, wasting the energy of compressed media.
Hydraulic compressor piston is mainly I shape piston, and piston contacts with cylinder barrel, by the seal ring sealing between piston and cylinder barrel, very high to the requirement of cylinder barrel like this, must ensure cylinder barrel roughness and straightness accuracy; And in the middle of long-term running, once occur in cylinder that impurity will scratch cylinder barrel and seal ring, leak air phenomenon at once; In addition, because cylinder barrel difficulty of processing is large, and alternate material is limited, and hydraulic compressor is very high to requirements for gas quality, pressurized gas limitednumber.
Summary of the invention
The present invention mainly solve manufacture cost existing for prior art compared with high, compression noise is large, the problem that operating power consumption is high, provide a kind of reciprocating plunger type gas compressor and method, the energy that this reciprocating plunger type gas compressor and method neither waste suction gas self is energy-efficient again, adopts hydraulic driving to effectively reduce noise simultaneously.
The present invention also has an object to be that the running environment of solution existing for prior art is limited, gas medium requires higher problem, provide a kind of reciprocating plunger type gas compressor and method, this reciprocating plunger type gas compressor and method adopt plunger type piston, go for various operating mode, lower to the requirement of compressed media.
Above-mentioned technical problem of the present invention is mainly solved by following technical proposals:
A kind of reciprocating plunger type gas compressor, comprise: host computer system, the control system be connected with host computer system and cooling system, the power system be connected with control system, described host computer system comprises: main frame cylinder, described main frame cylinder comprises: plunger, the first cylinder, oil cylinder, wherein:
One end of described first cylinder is connected with oil cylinder, and the other end is provided with the first cylinder contiguous block, and described plunger enters in cylinder through after oil cylinder, and forms seal chamber A with described first cylinder contiguous block;
Described plunger is positioned in in-oil cylinder part and is provided with oil cylinder piston, and described oil cylinder is divided into oil pocket B and the oil pocket C of upper and lower two sealings by described oil cylinder piston;
Described seal chamber A is provided with the first suction valve, first row air valve, described oil pocket B and oil pocket C is respectively arranged with oil cylinder oil inlet mouth;
Described first suction valve is connected with the inlet end of compressor by control system;
Described oil pocket B is connected with control system respectively with the oil cylinder oil inlet mouth on oil pocket C;
Described first row air valve is connected with the exhaust end of compressor by cooling system.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, also comprise the second cylinder, the other end being connected to oil cylinder of described second cylinder and the first cylinder symmetry, described plunger enters from one end of the second cylinder after described second cylinder and forms seal chamber D with the second cylinder contiguous block the second cylinder the other end, described seal chamber D is provided with the second suction valve and second row air valve, described second suction valve is connected with the inlet end of compressor by control system, and described second row air valve is connected with the exhaust end of compressor by cooling system.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, described host computer system has more than one, forms multi-stage compression system, wherein:
The oil cylinder oil inlet mouth of each host computer system described is connected with control system respectively;
First row air valve and the second row air valve of the first suction valve of the host computer systems at different levels in described host computer system, the second suction valve and upper level host computer system communicate;
First suction valve, second suction valve of first order host computer system are communicated with the inlet end of compressor by control system;
The first row air valve of afterbody host computer system is connected with the exhaust end of compressor respectively with second row air valve.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, described control system comprises the first ball valve, selector valve, wherein: described one end of first ball valve is connected with the inlet end of compressor, the other end is connected with the first suction valve and the second suction valve, one end of described selector valve is connected with the oil cylinder oil inlet mouth on oil pocket C with oil pocket B respectively, and the other end is connected with power system.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, described cooling system comprises: cooler, oil cooler, and one end of described cooler is connected with second row air valve with first row air valve, and the other end is connected with the exhaust end of compressor; One end of described oil cooler is connected with selector valve, and the other end is connected with the oil sump in power system.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, described power system comprises: oil cooler, accumulator, filter, oil pump, relief valve and oil sump, wherein: described oil pump and relief valve are parallel with one another to be connected with one end of filter with oil sump respectively afterwards, the other end of described filter is connected with accumulator and selector valve connects, and one end that described selector valve is connected with filter is also connected with oil sump.
Optimize, above-mentioned a kind of reciprocating plunger type gas compressor, also comprise process system, described process system comprises: safety valve, the second ball valve, one-way valve, described safety valve is connected with cooling system, one end of described second ball valve is connected with cooling system, and the other end is connected with compressor air-discharging end by one-way valve.
Utilize any one above-mentioned reciprocating plunger type gas compressor to carry out a method for gas compression, comprising:
Oiling step: by control system to an oiling in oil pocket B or oil pocket C, thus push oil cylinder piston movement makes one in seal chamber A or seal chamber D to be compressed;
Air inlet step: by ambient atmos suction seal chamber A or seal chamber D;
Steps of exhausting: when being reached required pressure by the gas pressure in the seal chamber that compresses, gas is discharged;
Switch step: control system is swung to, oiling in another oil pocket, thus promote oil cylinder piston reversing motion, perform air inlet step.
Optimize, the method of above-mentioned gas compression, described oiling step is: hydraulic oil is through oil pump, straight-through of entering in oil pocket B or oil pocket C of filter and selector valve is entered successively by oil sump, promote cylinder piston motion, meanwhile, the oil of another oil pocket, then through the straight-through of selector valve and oil cooler, gets back to oil sump;
Described air inlet step is: oil cylinder piston drives plunger motion, and un-compressed seal chamber volume is increased, opens the suction valve of this cavity, gas, through the first ball valve, enters un-compressed seal chamber from the first suction valve or the second suction valve;
Described steps of exhausting is: cylinder piston motion drives plunger motion, by the seal chamber smaller volume compressed, gas pressure increases, its suction valve is closed, when being reached the pressure of required compression by the gas pressure in the seal chamber that compresses, its outlet valve is opened, and gas is discharged through supercooler, the second venting ball valve and one-way valve;
Described switch step is: when plunger motion is to top, selector valve commutation is in the state of intersecting and communicating, and pressure oil, by flowing to previously not by the oil pocket of oiling, was previously got back to oil sump by the oil in the oil pocket of oiling simultaneously, oil cylinder piston reversing motion under the effect of pressure oil, then performs air inlet step.
Therefore, tool of the present invention has the following advantages:
1, energy-conserving and environment-protective more: Suck and exhaust pressure is wider, the energy of not wasting suction gas self and energy-efficient, be specially adapted to the higher mesohigh gas of pressure of inspiration(Pi) or liquid compression, and two-stage or multistage compression can be adopted, the pressure of oil pump can be reduced, reduce the temperature of compressed media, adopt hydraulic driving to effectively reduce noise simultaneously.
2, effectively reduce costs: owing to adopting hydraulic driving, therefore low cost of manufacture, operating cost are low.
3, more multi-operating mode can be adapted to: adopt plunger type piston, go for various operating mode, lower to medium requirements, existing hydraulic piston engine can not meet this requirement, the shale gas, coal-seam gas etc. of such as domestic present exploitation.
4, later maintenance is convenient to: because this unit is for various gas-liquid medium mixed input supercharging, in therefore increasing, body facilitates later stage detachable maintaining.
5, tightness is better: cylinder and oil cylinder are positioned at independent cylinder separately, and middle also have middle body to keep apart, even if therefore Sealing is damaged, gas also can not infiltrate into hydraulic oil.
Accompanying drawing explanation
Fig. 1 is the structural drawing of the embodiment of the present invention 1.
Fig. 2 is the structural drawing of the main frame cylinder of the embodiment of the present invention 1.
Fig. 3 is the structural drawing of the embodiment of the present invention 2.
Embodiment
Below by embodiment, and by reference to the accompanying drawings, technological scheme of the present invention is described in further detail.In figure, first ball valve 1, first suction valve 2, second suction valve 3, first row air valve 4, second row air valve 5, main frame cylinder 6, selector valve 8, cooler 9, safety valve 10, second ball valve 11, one-way valve 12, oil cooler 13, accumulator 14, filter 15, oil pump 16, relief valve 17, oil sump 18, first cylinder contiguous block 21, plunger 22, cylinder 23, cylinder barrel flange 24, cylinder intermediate mass 25, oil cylinder intermediate mass 26, oil cylinder piston seal ring 27, oil cylinder piston 28, oil cylinder 29, long draw 30, short rod 31, second cylinder contiguous block 32, vent hole 33, cylinder seal 34, cylinder seal 35, oil cylinder oil inlet mouth 36, second cylinder 37.
Embodiment 1:
See Fig. 1, a kind of reciprocating plunger type gas compressor, comprising: host computer system, the control system be connected with host computer system and cooling system, the power system be connected with control system.
Host computer system comprises main frame cylinder 6.As shown in Figure 2, main frame cylinder 6 comprises: plunger 22, first cylinder 23, second cylinder 37, oil cylinder 29, wherein: one end of the first cylinder 23 is connected with oil cylinder 29, the other end is provided with the first cylinder contiguous block 21, plunger 22 enters in cylinder 23 through after oil cylinder 29, and forms seal chamber A with the first cylinder contiguous block 21; The both sides that seal chamber A is relative are respectively arranged with the first suction valve 2, first row air valve 4; The other end being connected to oil cylinder 29 of the second cylinder 37 and the first cylinder 23 symmetry, plunger 22 forms seal chamber D with the second cylinder contiguous block 32 second cylinder 37 the other end after one end of the second cylinder 37 enters the second cylinder 37; The both sides that seal chamber D is relative are respectively arranged with the second suction valve 3 and second row air valve 5; First suction valve 2, second suction valve 3 is connected with the inlet end of compressor by control system; First row air valve 4, second row air valve 5 are connected with the exhaust end of compressor by cooling system; The part that plunger 22 is positioned at oil cylinder 29 is provided with oil cylinder piston 28, is provided with oil cylinder piston seal ring 27, oil cylinder 29 is divided into oil pocket B and the oil pocket C of upper and lower two sealings by this oil cylinder piston 28; Oil pocket B with oil pocket C is respectively arranged with the oil cylinder oil inlet mouth 36 be connected with control system; The connection part place of the first cylinder 23 and oil cylinder 29 connection part and the second cylinder 37 and oil cylinder 29 is provided with cylinder intermediate mass 25 and oil cylinder intermediate mass 26, this cylinder intermediate mass 25 and oil cylinder intermediate mass 26 are fixed on the cylinder flange 24 of the first cylinder 23 and the second cylinder 37 by long draw 30, in the cylinder, block 25 is provided with cylinder seal 34, described oil cylinder intermediate mass 26 is provided with cylinder seal 35; Oil cylinder 29 and cylinder are kept apart by cylinder intermediate mass 25, oil cylinder intermediate mass 26, even if therefore Sealing is damaged, gas also can not infiltrate into hydraulic oil.
Power system comprises accumulator 14, filter 15, oil pump 16, relief valve 17 and oil sump 18 and forms, after oil pump 16 is in parallel with relief valve 17, one end is connected with oil sump 18, the other end is connected with filter 15, and the other end of filter 15 is connected with the selector valve 8 of accumulator 14 and control system.
Cooling system comprises cooler 9 and oil cooler 13, the inlet end of cooler 9 is connected with first row air valve 4, second row air valve 5, safety valve 10 and second ball valve 11 of outlet side and process system are connected, and oil cooler 13 one end connects selector valve 8, and the other end connects oil sump 18.
Process gas system comprises safety valve 10, second ball valve 11, one-way valve 12 and pipeline composition, and safety valve 10 is connected with the cooler 9 of cooling system with one end of the second ball valve 11, and the other end is connected with compressor air-discharging end by one-way valve 12.
Control system comprises the first ball valve 1, first suction valve 2, second suction valve 3, first row air valve 4, the inlet end of second row air valve 5 and selector valve 8, first ball valve 1 one termination compressor, and one end is connected with the first suction valve 2 and the second suction valve 3 simultaneously in addition; First row air valve 4 and second row air valve 5 are connected with cooler 9 more simultaneously, and one end of selector valve 8 is connected with the oil cylinder oil inlet mouth 36 in the B chamber of main frame cylinder 6 and C chamber, and the other end is connected with filter 15 and oil cooler 13 respectively;
Plunger 22, oil cylinder piston 28 forms A, B, C, D tetra-chambeies after main frame cylinder 6 is installed, and wherein, A, D are air cavity, and B, C are oil pocket.Hydraulic oil is through oil pump 16, and the state in straight-through Fig. 1 of filter 15 and selector valve 8 that entered successively by oil sump 18 enters B chamber, and promote oil cylinder piston 28 and move downward, meanwhile, oil then state and the oil cooler 13 in straight-through Fig. 1 of selector valve 8 in C chamber, gets back to oil sump 18.In the process that oil cylinder piston 28 moves downward, A chamber volume can increase, and cavity pressure reduces, and the first suction valve 2 is opened, and gas, through the first ball valve 1, enters A chamber from the first suction valve 2, produces the intake process in A chamber.Simultaneously, D chamber smaller volume, gas pressure increases, second suction valve 3 cuts out, produce the compression process in D chamber, when the pressure in D chamber reaches the pressure of the i.e. required compression of pressure that second row air valve 5 can bear, second row air valve 5 is opened, gas is discharged in gas holder through supercooler 9, second venting ball valve 11 and one-way valve 12, forms the exhaust process in D chamber.
In the process, when D cavity pressure exceedes exhaust pressure, now D cavity pressure=A cavity pressure-C cavity pressure+B cavity pressure.Because C chamber communicates with oil sump, namely communicate with air, can disregard, and A chamber is gas inlet pressure.Therefore, D cavity pressure now and exhaust pressure=oil pressure+suction pressure.It can thus be appreciated that the suction pressure of gas is larger, required oil pressure is less, and power demand is less.
When plunger 22 moves to top, oil pressure can raise rapidly, and selector valve 8 commutates after receiving signal, and now selector valve 8 is in the state of intersecting and communicating.At this moment, pressure oil will flow to C chamber, and oil sump 18 just got back to by the oil in B chamber, and oil cylinder piston 28 moves upward under the effect of pressure oil, D chamber volume can increase, and cavity pressure reduces, and the second suction valve 3 is opened, gas, through the first ball valve 1, enters D chamber from the second suction valve 3, produces the intake process in D chamber.Simultaneously, A chamber smaller volume, gas pressure increases, first suction valve 2 cuts out, when the pressure in A chamber reaches the pressure of the i.e. required compression of pressure that first row air valve 4 bears, first row air valve 4 is opened, and gas is discharged in gas holder through supercooler 9, second ball valve 11 and one-way valve 12, forms the exhaust process in A chamber.
In the process, when A cavity pressure exceedes exhaust pressure, now A cavity pressure=D cavity pressure-B cavity pressure+C cavity pressure.Because B chamber communicates with oil sump, namely communicate with air, can disregard, and A chamber is gas inlet pressure.Therefore, A cavity pressure now and exhaust pressure=oil pressure+suction pressure.It can thus be appreciated that the suction pressure of gas is larger, required oil pressure is less, and power demand is less.
When plunger 22 moves to top, oil pressure can raise rapidly, and selector valve 8 commutates after receiving signal, and now selector valve 8 is in the state of intersecting and communicating.At this moment, pressure oil will flow to B chamber, and oil sump 18 just got back to by the oil in C chamber, and oil cylinder piston 28 is at the moved downward of pressure oil, A chamber volume can increase, and cavity pressure reduces, and the second suction valve 3 is opened, gas, through the first ball valve 1, enters A chamber from the second suction valve 3, produces the intake process in A chamber.Simultaneously, D chamber smaller volume, gas pressure increases, first suction valve 2 cuts out, when the pressure in D chamber reaches the pressure of the i.e. required compression of pressure that first row air valve 4 bears, first row air valve 4 is opened, and gas is discharged in gas holder through supercooler 9, second ball valve 11 and one-way valve 12, forms the exhaust process in D chamber.
Embodiment 2:
Fig. 3 is second embodiment of the present invention.For using two stage compression, add a main frame cylinder 6,
The oil cylinder oil inlet mouth 36 of two host computer systems is connected with control system respectively; In second host computer system, the first row air valve 4 of the first suction valve 2, second suction valve 3 and upper level host computer system and second row air valve 5 communicate; First suction valve 2, second suction valve 3 of first host computer system is communicated with the inlet end of compressor by control system; The first row air valve 4 of second host computer system is connected with the exhaust end of compressor respectively with second row air valve 5.
One stage of compression is become two stage compression by the present embodiment, can reduce the pressure ratio of gas like this, to compression process advantageously.Certainly can also be increased to three grades or more, the pressure of required like this oil pump just reduces relatively, and advantageously, but the cost of product can increase in work; Meanwhile, if discharge capacity will be increased, only need the number of cylinders increasing every one-level.
Meanwhile, in the present embodiment, power system has been changed into a hydraulic workstation, be installed together by all hydraulic sets of elements, thus reduced volume.
This patent promotes hydraulic piston with hydraulic oil thus drives plunger upward and downward to compress gas, and upper and lower two ends are symmetrical cylinder, when compressed media above, enter medium below, below compressed media time, enter medium above, centre is oil hydraulic cylinder, is separated by piston.
In the present invention, main easily damaged parts is cylinder seal, changes sealing for convenience, and cylinder intermediate mass 25 oil cylinder intermediate mass 26 is for what separate, and object dismantles oil cylinder to not need when dismantling cylinder, and design improves a lot than before;
Be connected on cylinder at the first cylinder contiguous block 21 and the second cylinder contiguous block 32 respectively by short rod 31; the cylinder wall being positioned at cylinder intermediate mass 25 and oil cylinder intermediate mass 26 abutted surface at the first cylinder 23 and the second cylinder 37 is provided with vent hole 33; this vent hole 33 plays the effect of protection cylinder seal; when cylinder seal 34 damages; medium flows out from vent hole 33, prevents from damaging cylinder seal 35.
Specific embodiment described herein is only to the explanation for example of the present invention's spirit.Those skilled in the art can make various amendment or supplement or adopt similar mode to substitute to described specific embodiment, but can not depart from spirit of the present invention or surmount the scope that appended claims defines.
Although more employ the first ball valve 1 herein, first suction valve 2, second suction valve 3, first row air valve 4, second row air valve 5, main frame cylinder 6, selector valve 8, cooler 9, safety valve 10, second ball valve 11, one-way valve 12, oil cooler 13, accumulator 14, filter 15, oil pump 16, relief valve 17, oil sump 18, first cylinder contiguous block 21, plunger 22, cylinder 23, cylinder barrel flange 24, cylinder intermediate mass 25, oil cylinder intermediate mass 26, oil cylinder piston seal ring 27, oil cylinder piston 28, oil cylinder 29, long draw 30, short rod 31, second cylinder contiguous block 32, vent hole 33, cylinder seal 34, cylinder seal 35, oil cylinder oil inlet mouth 36, second term such as cylinder 37 grade, but do not get rid of the possibility using other term.Using these terms, is to describe more easily and explaining essence of the present invention; The restriction that they are construed to any one additional is all contrary with spirit of the present invention.
Claims (9)
1. a reciprocating plunger type gas compressor, comprise: host computer system, the control system be connected with host computer system and cooling system, the power system be connected with control system, it is characterized in that, described host computer system comprises: main frame cylinder (6), described main frame cylinder (6) comprising: plunger (22), the first cylinder (23), oil cylinder (29), wherein:
One end of described first cylinder (23) is connected with oil cylinder (29), the other end is provided with the first cylinder contiguous block (21), described plunger (22) enters in cylinder (23) through after oil cylinder (29), and forms seal chamber A with described first cylinder contiguous block (21);
The part that described plunger (22) is positioned at oil cylinder (29) is provided with oil cylinder piston (28), and described oil cylinder (29) is divided into oil pocket B and the oil pocket C of upper and lower two sealings by described oil cylinder piston (28);
Described seal chamber A is provided with the first suction valve (2), first row air valve (4), described oil pocket B and oil pocket C is respectively arranged with oil cylinder oil inlet mouth (36);
Described first suction valve (2) is connected with the inlet end of compressor by control system;
Described oil pocket B is connected with control system respectively with the oil cylinder oil inlet mouth (36) on oil pocket C;
Described first row air valve (4) is connected with the exhaust end of compressor by cooling system.
2. a kind of reciprocating plunger type gas compressor according to claim 1, it is characterized in that, also comprise the second cylinder (37), the other end being connected to oil cylinder (29) that described second cylinder (37) is symmetrical with the first cylinder (23), described plunger (22) enters described second cylinder (37) and forms seal chamber D with the second cylinder contiguous block (32) the second cylinder (37) the other end afterwards from one end of the second cylinder (37), described seal chamber D is provided with the second suction valve (3) and second row air valve (5), described second suction valve (3) is connected with the inlet end of compressor by control system, described second row air valve (5) is connected with the exhaust end of compressor by cooling system.
3. a kind of reciprocating plunger type gas compressor according to claim 2, it is characterized in that, described host computer system has more than one, forms multi-stage compression system, wherein:
The oil cylinder oil inlet mouth (36) of each host computer system described is connected with control system respectively;
First row air valve (4) and the second row air valve (5) of first suction valve (2) of the host computer systems at different levels in described host computer system, the second suction valve (3) and upper level host computer system communicate;
First suction valve (2), second suction valve (3) of first order host computer system are communicated with the inlet end of compressor by control system;
The first row air valve (4) of afterbody host computer system is connected with the exhaust end of compressor respectively with second row air valve (5).
4. a kind of reciprocating plunger type gas compressor according to claim 2, it is characterized in that, described control system comprises the first ball valve (1), selector valve (8), wherein: one end of described first ball valve (1) is connected with the inlet end of compressor, the other end is connected with the first suction valve (2) and the second suction valve (3), one end of described selector valve (8) is connected with the oil cylinder oil inlet mouth (36) on oil pocket C with oil pocket B respectively, and the other end is connected with power system.
5. a kind of reciprocating plunger type gas compressor according to claim 4, it is characterized in that, described cooling system comprises: cooler (9), oil cooler (13), one end of described cooler (9) is connected with second row air valve (5) with first row air valve (4), and the other end is connected with the exhaust end of compressor; One end of described oil cooler (13) is connected with selector valve (8), and the other end is connected with the oil sump (18) in power system.
6. a kind of reciprocating plunger type gas compressor according to claim 4, it is characterized in that, described power system comprises: oil cooler (13), accumulator (14), filter (15), oil pump (16), relief valve (17) and oil sump (18), wherein: described oil pump (16) and relief valve (17) are parallel with one another to be connected with oil sump (18) one end with filter (15) respectively afterwards, the other end of described filter (15) is connected with accumulator (14) and selector valve (8) connects, one end that described selector valve (8) is connected with filter (15) is also connected with oil sump (18).
7. a kind of reciprocating plunger type gas compressor according to claim 2, it is characterized in that, also comprise process system, described process system comprises: safety valve (10), the second ball valve (11), one-way valve (12), described safety valve (10) is connected with cooling system, one end of described second ball valve (11) is connected with cooling system, and the other end is connected with compressor air-discharging end by one-way valve (12).
8. utilize any one the reciprocating plunger type gas compressor described in claim 1-6 to carry out a method for gas compression, it is characterized in that, comprising:
Oiling step: by control system to an oiling in oil pocket B or oil pocket C, thus push oil cylinder piston movement makes one in seal chamber A or seal chamber D to be compressed;
Air inlet step: by ambient atmos suction seal chamber A or seal chamber D;
Steps of exhausting: when being reached required pressure by the gas pressure in the seal chamber that compresses, gas is discharged;
Switch step: control system is swung to, oiling in another oil pocket, thus promote oil cylinder piston reversing motion, perform air inlet step.
9. the method for gas compression according to claim 7, is characterized in that,
Described oiling step is: hydraulic oil is through oil pump (16), straight-through of entering in oil pocket B or oil pocket C of filter (15) and selector valve (8) is entered successively by oil sump (18), promote oil cylinder piston (28) motion, simultaneously, the oil of another oil pocket, then through the straight-through of selector valve (8) and oil cooler (13), gets back to oil sump (18);
Described air inlet step is: oil cylinder piston (28) drives plunger (22) motion, un-compressed seal chamber volume is increased, open the suction valve of this cavity, gas, through the first ball valve (1), enters un-compressed seal chamber from the first suction valve (2) or the second suction valve (3);
Described steps of exhausting is: oil cylinder piston (28) motion drives plunger (22) motion, by the seal chamber smaller volume compressed, gas pressure increases, its suction valve is closed, when being reached the pressure of required compression by the gas pressure in the seal chamber that compresses, its outlet valve is opened, and gas is discharged through supercooler (9), the second venting ball valve (11) and one-way valve (12);
Described switch step is: when plunger (22) moves to top, selector valve (8) commutation is in the state of intersecting and communicating, pressure oil will flow to previously not by the oil pocket of oiling, previously got back to oil sump (18) by the oil in the oil pocket of oiling simultaneously, oil cylinder piston (28) reversing motion under the effect of pressure oil, then performs air inlet step.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410454848.1A CN104214071B (en) | 2014-09-09 | 2014-09-09 | Reciprocating plunger type gas compressor and method |
| PCT/CN2015/080751 WO2016037500A1 (en) | 2014-09-09 | 2015-06-04 | Reciprocating plunger-type gas compressor and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410454848.1A CN104214071B (en) | 2014-09-09 | 2014-09-09 | Reciprocating plunger type gas compressor and method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104214071A true CN104214071A (en) | 2014-12-17 |
| CN104214071B CN104214071B (en) | 2017-02-15 |
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| CN201410454848.1A Active CN104214071B (en) | 2014-09-09 | 2014-09-09 | Reciprocating plunger type gas compressor and method |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| 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 |
| CN105422449A (en) * | 2015-12-22 | 2016-03-23 | 西安交通大学 | Cantilever type oil-free double-toothed rotor compressor |
| CN105569979A (en) * | 2016-01-30 | 2016-05-11 | 西安昆仑工业（集团）有限责任公司 | Vertical combination oil gas cylinder 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 |
| CN108457930A (en) * | 2018-04-08 | 2018-08-28 | 中国重汽集团南充海乐机械有限公司 | A kind of automobile-used single-acting piston type multistage synchronous fuel tank of disabled's boarding |
| CN109653985A (en) * | 2018-12-13 | 2019-04-19 | 武汉齐达康环保科技股份有限公司 | A kind of hydrogen gas compressor host and compression method |
| CN109973370A (en) * | 2019-04-24 | 2019-07-05 | 江苏恒久机械股份有限公司 | A kind of hydraulic-driven membrane compressor |
| CN110107485A (en) * | 2019-06-01 | 2019-08-09 | 成都天高机电设备有限公司 | A kind of commutation valve type diaphragm pump system |
| CN111365211A (en) * | 2020-03-06 | 2020-07-03 | 西安交通大学 | Swing reversing two-stage supercharging zero-clearance ionic liquid compressor |
| CN111365210A (en) * | 2020-03-06 | 2020-07-03 | 西安交通大学 | Efficient supercharging zero-clearance type ionic liquid compressor with accurately adjustable piston stroke |
| CN111365212A (en) * | 2020-03-06 | 2020-07-03 | 西安交通大学 | Phase difference real-time adjustable three-stage supercharging zero-clearance type ionic liquid compressor |
| CN111365211B (en) * | 2020-03-06 | 2021-04-27 | 西安交通大学 | Swing reversing two-stage supercharging zero-clearance ionic liquid compressor |
| CN111365212B (en) * | 2020-03-06 | 2021-06-22 | 西安交通大学 | Phase difference real-time adjustable three-stage supercharging zero-clearance type ionic liquid compressor |
| CN111365210B (en) * | 2020-03-06 | 2021-08-10 | 西安交通大学 | Efficient supercharging zero-clearance type ionic liquid compressor with accurately adjustable piston stroke |
| CN114198288A (en) * | 2021-12-04 | 2022-03-18 | 江阴市富仁高科股份有限公司 | Multistage supercharging zero-clearance type ionic liquid compressor |
| CN115681074A (en) * | 2022-10-14 | 2023-02-03 | 西安交通大学 | Double-piston two-stage supercharging porous medium efficient heat exchange type ionic liquid compressor |
| CN115681074B (en) * | 2022-10-14 | 2023-11-14 | 西安交通大学 | Double-piston two-stage supercharging porous medium efficient heat exchange type ionic liquid compressor |
| CN117191286A (en) * | 2023-08-28 | 2023-12-08 | 烟台东德实业有限公司 | Sealing element performance system for simultaneously detecting multiple pressure states of circulating liquid seal cylinder |
| CN117191286B (en) * | 2023-08-28 | 2024-05-07 | 烟台东德实业有限公司 | Sealing element performance system for simultaneously detecting multiple pressure states of circulating liquid seal cylinder |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016037500A1 (en) | 2016-03-17 |
| CN104214071B (en) | 2017-02-15 |
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Denomination of invention: A reciprocating plunger gas compressor and method Granted publication date: 20170215 Pledgee: Agricultural Bank of China Limited Hubei pilot Free Trade Zone Wuhan Area Branch Pledgor: WUHAN QIDAKANG ENERGY EQUIPMENT CO.,LTD. Registration number: Y2024980029364 |