CN106640602B - A kind of gas compressor with reciprocating - Google Patents
A kind of gas compressor with reciprocating Download PDFInfo
- Publication number
- CN106640602B CN106640602B CN201710035058.3A CN201710035058A CN106640602B CN 106640602 B CN106640602 B CN 106640602B CN 201710035058 A CN201710035058 A CN 201710035058A CN 106640602 B CN106640602 B CN 106640602B
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- cylinder
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- gas injection
- valve
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Classifications
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/08—Actuation of distribution members
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A kind of efficient gas compressor with reciprocating, including fuselage, working chamber part, running part and slave part, working chamber part includes cylinder, cylinder includes cylinder body and cylinder cap, cylinder cap is equipped with intake valve and exhaust valve, and piston is located in the cylinder body and moves back and forth under piston rod drive along inboard wall of cylinder block, and piston rod is connect with running part, working chamber part further includes discharge chamber, and discharge chamber bottom is the cylinder cap；It further include the gas injection valve being located on cylinder cap, when piston stroking upward enters compression stage, gas injection valve is opened under the drive of gas injection valve opening and closing member, will be in the gas injection cylinder body in discharge chamber.Using the present invention, efficiency is not only increased, because reducing the compression ratio in actual compression ratio, delivery temperature is also reduced, is conducive to the promotion of service life.
Description
Technical field
The present invention relates to Compressor Technology fields, more particularly, to a kind of gas compressor with reciprocating.
Background technique
As convert mechanical energy into gas pressure can a kind of power device, what Fig. 1 was provided is the most basic reciprocal
The structural schematic diagram of formula gas compressor, the rotary motion of crankshaft become the straight reciprocating motion of 5 ' of piston by 6 ' of piston rod.
Valve block in 3 ' of 1 ' of inlet valve seat and delivery valve seat, it is suitable when usually being moved up and down with the pressure difference of valve block upper and lower surface with 5 ' of piston
When close or open, a volume (V) and pressure (P) period are surrounded by 2 ' of cylinder cap, 4 ' of cylinder jacket and 5 ' of piston in this way and become
The space of change, the size in space or variation can be indicated that 5 ' of piston is up and down reciprocatingly primary in P-V figure, i.e., one work
Circulation just corresponds to a closed quadrangle in P-V figure.As shown in Fig. 2, the A point in quadrangle ABCD is that a upper job follows
The initial point of the terminal of ring and next circulation, that is, 5 ' of piston corresponded in Fig. 1 go upward to highest point, run in compressor
It is not allow for the possibility of 5 ' of piston collision, 2 ' of cylinder cap in the process, i.e. each working cycles of gas compressor with reciprocating are vented eventually
When, there are a little gap between 5 ' of piston and cylinder cap 2 ', it is pressure at expulsion P that, which just there is a small amount of pressure in this gap,2Gas, with
5 downlink of piston, remaining in in-cylinder pressure is P2Gas start to expand, until pressure drops to B point, i.e. in-cylinder pressure and air inlet
The pressure of system is equal, this stage claims the expansion stage, this stage intake and exhaust valve seat is in closed state, piston-swept
Volume is just VB-VA。
Piston continues traveling downwardly, and in-cylinder pressure is slightly less than the pressure P of gas handling system1, inlet valve seat automatic opening, gas handling system
Gas enter in working cylinder to C point, the i.e. terminal of piston downlink, this stage is known as expiratory phase, this graduated discharge valve
Seat is closed always, and the volume of sucking is VC-VB, piston also do not do work, in addition VC-VAIt is the whole inswept volume of piston.
Piston starts to go upward to D point, V after C pointC-VDBe piston to gas in the jar by P1It is compressed to P2Inswept volume,
This stage is compression stage, this stage intake and exhaust valve seat is in closed state, this step piston is to gas in the jar
It needs to do work, the calculation formula for the W that does work are as follows:
P in formula1·(VC-VB) and P2/P1It is two important performance indexes for reflecting the compressor, the former is P1·(VC-VB) be
The machine is in P1Conveying capacity under state, i.e. VC-VB, and P2/P1Reflection is the machine compression ratio.Obvious conveying capacity is bigger, consumes function
Rate is also big, same P2/P1Bigger, then consumed power is also bigger, such as P2/P1Approach 1, then as can be seen from the above equation, disappeared
The function of consumption is just close to zero.K is polytropic exponent in formula, and force feed determines that the gas of component just corresponds to a determining K value.
Piston continues uplink, because cylinder pressure has reached P2, drain tap unlatching, this stage is exhaust rank
Section, this stage terminate when piston stroking upward is to highest point.The volume of exhaust is VD-VA, while there are few between piston and cylinder cap
Amount volumetric pressure is P2Gas enter next working cycles, it should be noted that this stage, gas is passed through row by piston
Air valve seat need to consume a part of power when being pressed into exhaust system.
The foregoing describe the corresponding quadrangles on P-V figure of its working cycles in gas compressor with reciprocating operation
ABCD is briefly explained, while also being addressed power consumption and being occurred mainly in compression stage, and provides calculating formula (1).
Meanwhile a working cycles can only correspond to a quadrangle on P-V figure, and quadrangle area is bigger, is consumed
Function is also bigger, and the relationship between delivery temperature and compression ratio is given in addition to formula (1).
From above formula (1) and (2) as can be seen that compression ratio P2/P1Bigger, spent power is also bigger, and delivery temperature is also got over
Height such as works as P conversely, compression ratio is smaller1Approach P2When, consumed external work approach zero, delivery temperature is also close to intake air temperature.
Quadrangle ABCD and quadrangle AB ' C ' D ' is the gas of the same same component of reciprocating compressor force feed in Fig. 3,
And two different operating conditions that pressure at expulsion is equal, the admission pressure P of quadrangle AB ' C ' D '1' is greater than the air inlet pressure of quadrangle ABCD
Power P1, it is clear that the area of quadrangle ABCD is greater than the area of quadrangle AB ' C ' D ', i.e. power spent by quadrangle ABCD should be big
In the power of quadrangle AB ' C ' D ', because being same compressor, the whole inswept volume of the two quadrangle pistons just answers phase
Deng i.e. VC-VA=VC'-VA, and cylinder mouth pressure is equal, so respective exhaust valve DA and D ' A are overlapped on a horizontal line,
And D ' A is greater than DA, can obtain from Fig. 3:
D ' A=DA+D ' D
That is VD'-VA=(VD-VA)+(VD'-VD)
Wherein, VD'-VAIt is under quadrangle A ' B ' C ' D ' operating condition, is P by pressure1', volume VC'-VAGas compression extremely
P2Pressure venting, in an amount of from VD'-VA。
VD-VAIt is under quadrangle ABCD operating condition, by pressure P1Volume is VC-VAGas compression to P2Pressure venting,
Amount is VD-VA。VD'-VDIt is under above-mentioned two different operating conditions, with pressure P2The difference of the volume of discharge.
Show the compressor of one with Fig. 3 same performance, the operating condition set is normal in this way as quadrangle ABCD in Fig. 3
When operation, which should repeat to run under quadrangle ABCD.Pressure in compression stage cylinder is lower than the pressure of discharge chamber, now as right
It is P that the compressor, which only will be vented cavity pressure by certain particular technology means in compression stage,2Gas be introduced into working cylinder
It is interior, if the amount being introduced into is V in Fig. 3D'-VDIt is P with the pressure in cylinder1Gas mixing after, quadrangle AB ' C ' should be equal to
D ' is P to the gas pressure in cylinder at the end of sucting stage1' rather than the P at the end of sucting stage in quadrangle ABCD1,
Occur to be by P in cylinder in compression stage1' gas compression is to P2, rather than P in quadrangle ABCD1It is compressed to P2.It is vented rank
Amount of the section through delivery valve seat discharge is VD'-VA, and what the deduction obtained in discharge chamber was injected in compression stage, it is finally obtained
It is still V shown in quadrangle ABCDD-VAAmount.In this way for reciprocating compressor, followed in its each running work
Ring, as being P by exhaust system pressure in compression stage2Gas be introduced into working cylinder, it is true in this way to occur in cylinder
Compression ratio be less than the compression ratio of former setting, just reduce power consumption needed for original, moreover it is possible to guarantee that the performance of former setting does not change.
By analyzing above it is found that before the present invention when operation of reciprocating compressor, piston is reciprocal each time just corresponding in P-V
Scheme a unique quadrangle, the compression ratio of compression stage is exactly the ratio between the pressure of discharge chamber and the pressure of inlet chamber, and living
There is no any associated components of generation between at the top of plug and cylinder.
Summary of the invention
It is an object of the invention to change the structure of gas compressor with reciprocating working chamber part in the prior art, guaranteeing
Under conditions of former operating condition is constant, the compression ratio really occurred in cylinder is set to be less than the compression ratio of former setting, to reduce power consumption
And delivery temperature, the technical solution adopted is that: a kind of gas compressor with reciprocating, including fuselage, working chamber part, driving section
Divide and slave part, the working chamber part include cylinder, the cylinder includes cylinder body and cylinder cap, and the cylinder cap is equipped with air inlet
Valve and exhaust valve, piston are located in the cylinder body and move back and forth under piston rod drive along inboard wall of cylinder block, the piston rod with
Running part connection, it is characterised in that: the working chamber part further includes discharge chamber, and the discharge chamber bottom is the cylinder cap,
It further include the gas injection valve being located on the cylinder cap, when the piston stroking upward enters compression stage, the gas injection valve is in gas injection valve
Opening and closing member drives lower opening, the gas in discharge chamber is injected in the cylinder body, the gas injection valve opening and closing member includes and institute
It states piston connection and passes through the interlocking lever of cylinder cap axle sleeve, the interlocking lever sets away from one end of the piston and stirs component, also wraps
It includes in the gas injection valve flap opening mechanism stirring component and being used cooperatively.
Technical characteristic of the invention is also: the gas injection valve flap opening mechanism includes the gas injection connecting with gas injection valve flap
Valve valve rod, the valve rod and connector are hinged, and the connector is connect with by lever, described to be connected by lever one end by lever branch
On seat, the other end is matched with the component of stirring.
Technical characteristic of the invention is also: described by lever includes that can be movable relatively by lever mobile jib and by lever pair
Bar, it is described to be connect by lever mobile jib with the passive rod bearing, it is described to be set and the end stirring component and cooperating by lever secondary bar
Portion.
Technical characteristic of the invention is also: described to be equipped with by lever mobile jib and between lever secondary bar torsionspring.
Technical characteristic of the invention is also: described that tension spring and pressure spring are equipped between lever mobile jib and passive rod bearing.
The beneficial effects of the present invention are:
1) guarantee performance it is constant under the premise of, i.e., flow and capacity it is constant under conditions of, make to actually occur at compression
Compression ratio in the process, less than the compression ratio that need to originally set, then spent power is low, that is, improves efficiency.
2) in former setting one, high-pressure reciprocating compressor needs multi-stage compression, and structure is complicated, and investment is larger, uses this hair
Bright selectively to improve to wherein certain stage compression ratio, design so on the whole may design few level-one or two than original
Grade compression.
3) using the present invention, efficiency is not only increased, because reducing the compression ratio in actual compression ratio, also reduces exhaust temperature
Degree, is conducive to the promotion of service life.
Detailed description of the invention
Attached drawing 1 is that gas compressor schematic illustration, attached drawing 2 are P-V figures in the prior art, and attached drawing 3 is same reciprocating
P-V schemes under two kinds of gas compressor different operating conditions, and attached drawing 4 is a kind of knot that exhaust valve is placed in cylinder head in the prior art
Structure,
Attached drawing 5 is one structural schematic diagram of the embodiment of the present invention, and attached drawing 6-10 is each different movement moments in embodiment one
Position view, attached drawing 11 are exhaust valve valve cover structure schematic diagrames, and attached drawing 12 is the top view of attached drawing 10, and attached drawing 13 is the present invention
Embodiment two.Wherein:
1 ' is intake valve, and 2 ' are cylinder caps, and 3 ' are exhaust valves, and 4 ' are cylinder jacket, and 5 ' are pistons, and 6 ' are piston rods.
It 1 " is to cover greatly, 2 " be safety spring, 3 " be bolt, 4 " be nut, 5 " be exhaust valve valve deck, 6 " be exhaust valve bullet
It spring, 7 " is be be are exhaust valve base, 8 " exhaust valve valve block, 9 " body, 10 " suction valve chip, 11 " cylinder sleeve, 12 " it is piston,
It 13 " is piston ring, 14 " be inspiration valve seat, 15 " be exhaust valve.
1 is tegillum, and 2 be to cover greatly, and 3 be safety spring, and 4 be spring base, and 5 be to stir ring, and 6 be interlocking lever, and 7 be bolt, and 8 are
Nut, 9 be to pad greatly, and 10 be exhaust valve valve deck, and 11 be exhaust valve, and 12 be exhaust valve valve block, and 13 be exhaust valve base, and 14 be living
Plug, 15 be axle sleeve, and 16 be gas injection valve, and 17 be gas injection valve valve rod, and 18 be gas injection valve body, and 19 be gas injection valve flap, and 20 be gas injection
Valve spring, 21 be cylinder jacket, and 22 be exhaust valve spring, and 23 be passive rod bearing, and 24 be tension spring, and 25 be pressure spring, and 26 be small axis, 27
It is by lever mobile jib, 28 be connector, and 29 be torsionspring, and 30 be by lever secondary bar, and 31 be the cover, and 32 be cylinder cap, and 33 be cylinder
Set.
Specific embodiment
With reference to the accompanying drawing, description of specific embodiments of the present invention.Before making the present invention, reciprocating gas pressure
When contracting machine is run, only one quadrangle on piston just corresponding P-V figure reciprocal each time, the compression ratio of compression stage is exactly to arrange
The ratio between pressure and the pressure of inlet chamber of air cavity, and there is no any associated component of generation between piston and cylinder top.
Before describing this patent implementing measure, the prior art that also patent is implemented in reply is had gained some understanding.Attached drawing 4 is will to be vented
Valve, which is mounted on cylinder head and includes mutually to close on one of numerous structure types of component, need to illustrate exhaust valve 15 " is used as one
A mechanism is made of exhaust valve valve deck 5 ", exhaust valve spring 6 ", exhaust valve base 7 " and exhaust valve valve block 8 " etc., and by spiral shell
Bolt 3 ", nut 4 " is tightened to a complete component, and in addition cylinder sleeve 11 " external and body 9 " lower section is inlet chamber, body 9 " with
Big lid 1 " between be discharge chamber.On exhaust valve 15 " passing through safety spring 2 " and big lid 1 " being fixed on cylinder sleeve 11 ".
The present invention is in this technical field of gas compressor with reciprocating, if an one end is in discharge chamber, centre is worn
Cross the bar that cylinder head, the other end are then connected with piston and can move up and down with piston synchronous can be when this bar moves up and down in due course
Certain component being in discharge chamber is stirred, makes it to be mounted on the gas injection valve of cylinder head in compression stage lifting, will be vented
In the cylinder that intracavitary gas injection is being compressed, to reduce the compression ratio of compression stage, that is, power consumption and delivery temperature are reduced,
And the duty requirements of former setting are constant.From the above analysis content as it can be seen that implementing this technology only needs to add and can move with piston synchronous
Bar and cylinder cap is outer and certain components in discharge chamber and the gas injection valve being placed on cylinder cap, and these parts only with
Piston and the component of cylinder head are related.
Implementing measure:
What Fig. 5 to Figure 10 was indicated is that exhaust valve is mounted at the top of cylinder jacket, and piston is in each of which working cycles
Certain a bit of stroke, the more coherent moment for implementing this technology.
The axle sleeve in exhaust valve 11 is passed through in the middle part of interlocking lever 6 equipped with ring 5 is stirred on the interlocking lever 6 on discharge chamber top in Fig. 5
15, lower end is then mounted on piston 14, and such interlocking lever 6 synchronous with piston 14 can move up and down.What Fig. 5 was indicated is piston 14
The expanded air inlet of downlink, there are also a bit of unfinished suction strokes, but do not touch also by the moment before lever.
By lever by being formed by lever mobile jib 27, by lever secondary bar 30 and torsionspring 29, can be passed through by lever secondary bar 30
Torsionspring 29 is rotated clockwise to by lever mobile jib 27 as certain angle.And the small of passive rod bearing 23 is fixed on by lever
On axis 26, the rotation of certain angle can be made to small axis 26 by lever in this way, passive rod bearing 23 is then fixed on exhaust valve valve deck 10
On radial vertically hung scroll without grate flow channel.In addition there are tension spring 24 and pressure spring 25 between lever mobile jib 27 and passive rod bearing 23,
Wherein the both ends of tension spring 24 are separately fixed at passive rod bearing 23 and by lever mobile jibs 27, and pressure spring 25 is only secured to by lever branch
On seat 23.
One aperture is had by 27 front end of lever mobile jib, it is sufficiently strong with having with the gas injection valve valve rod 17 that is placed in exhaust valve 11
Degree, non-telescope deformation are simultaneously connect with the connector 28 that force feed medium does not react, which can be selected the materials such as seizing wire
Material is made.
Gas injection valve 16 is made of gas injection valve body 18, gas injection valve valve rod 17, gas injection valve spring 20 and gas injection valve flap 19 etc..
The ring that is not struck by lever touching, even if touching, once departing from ring 5 is stirred, it also can be in the effect of multiple springs
Under be restored to stable state as shown in Figure 5.
It stirs ring 5 to continue traveling downwardly in company with piston 14, affect by lever to minimum point, here it is the moments that Fig. 6 is shown.
As soon as the 14 downlink moment of piston in Fig. 6 is restored to steady as shown in Figure 5 by lever departing from ring 5 is stirred
Fixed, stationary state stirs the disengaging of ring 5 and after lever, is continued traveling downwardly a bit of limited unfinished suction stroke, on preparation starts
Capable moment, here it is moments shown in Fig. 7.Piston 14 is advanced into compression stage on starting, and equally only dials through very little a trip
Rotating ring 5 is touched from bottom to top in company with piston 14, and but without affecting by the scene of lever, here it is the moments that Fig. 8 describes.It stirs
Ring 5 continues uplink in company with piston 14, while being lifted by lever to highest point, i.e. Figure 10 shows moment.
In this bit of stroke of Fig. 8 to Fig. 9, due to being lifted by lever, gas injection valve valve rod 17 is lifted by connector 28, is made
The sealing surface that gas injection valve flap 19 is detached from gas injection valve body 18 is obtained, the pressure in this trip, cylinder is still less than exhaust
Intracavitary pressure, in this way in this trip of Fig. 8 to Fig. 9, exhaust cavity pressure is P2Gas cylinder is entered by gas injection valve
It is interior, the pressure in cylinder is improved, while also reducing the compression ratio of compression stage.
A moment of piston stroking upward to highest point is shown in Figure 10, and piston is to the gas in cylinder in this trip
Implement unfinished compression and exhaust, piston stroking upward to highest point, it is meant that this exhaust phase terminates, i.e. this working cycles knot
Beam, then piston downlink starts next working cycles again.
The arrangement in the hole of passive rod bearing 23, gas injection valve body 18, axle sleeve 15 and bolt in Fig. 5, can be from exhaust valve
See in the part drawing (Figure 11 and Figure 12) of valve deck 10, mid diameter D1Hole axle sleeve is installed, 3 diameters are D2Hole setting
Gas injection valve body, three diameters are D3Hole for installing bolt, in addition on the valve deck of Figure 11 three be free of the diameter of exhaust passage
There is screw hole M on vertically hung scrolld, for fixing passive rod bearing.
In addition, can go out from Figure 11 and Figure 12, three can be stirred by lever simultaneously by stirring ring for one, can lift three simultaneously
Gas injection valve valve rod 17, such effect is more preferable.
Bolt and nut prevent 18 axial float of axle sleeve 15 and gas injection valve body by big pad 9, also by exhaust valve valve deck 10,
It is vented one complete exhaust valve part of composition such as valve base 13, exhaust valve valve block 12 and exhaust valve spring 22.
6 up and down motion stroke of interlocking lever is compensated by with piston 14, tegillum 1.
Exhaust valve is fixed on cylinder head by big lid 2, tegillum 1 and spring base 4 by safety spring 3.
It is cylinder cap rather than exhaust valve that Figure 13, which is at the top of cylinder jacket, implements the schematic diagram of this technology, implements the original of this technology
The components for managing and being directly used in this technology as hereinbefore, repeat no more.
Certainly, above description is not limitation of the present invention, and the present invention is also not limited to the example above, the art
The variations, modifications, additions or substitutions that those of ordinary skill is made within the essential scope of the present invention also belong to guarantor of the invention
Protect range.
Claims (5)
1. a kind of gas compressor with reciprocating, including fuselage, working chamber part, running part and slave part, the working chamber
Part includes cylinder, and the cylinder includes cylinder body and cylinder cap, and the cylinder cap is equipped with intake valve and exhaust valve, and piston is located at described
It is moved back and forth in cylinder body and under piston rod drive along inboard wall of cylinder block, the piston rod is connect with running part, it is characterised in that:
The working chamber part further includes discharge chamber, and it further includes the note being located on the cylinder cap that the discharge chamber bottom, which is the cylinder cap,
Air valve, when the piston stroking upward enters compression stage, the gas injection valve is opened under the drive of gas injection valve opening and closing member, will be vented
Intracavitary gas injects in the cylinder body, and the gas injection valve opening and closing member includes connecting with the piston and passing through cylinder cap axle sleeve
Interlocking lever, it further includes being used cooperatively with the component of stirring that the interlocking lever, which sets away from one end of the piston and stirs component,
Gas injection valve flap opening mechanism.
2. gas compressor described in accordance with the claim 1, it is characterised in that: the gas injection valve flap opening mechanism includes and note
The gas injection valve valve rod of air valve flap connection, the valve rod and connector are hinged, and the connector is connect with by lever, described passive
Bar one end connects on passive rod bearing, and the other end is matched with the component of stirring.
3. gas compressor according to claim 2, it is characterised in that: it is described by lever include can be movable relatively it is passive
Bar mobile jib and by lever secondary bar, it is described to be connect by lever mobile jib with the passive rod bearing, it is described by lever secondary bar set with it is described
Stir the end of component cooperation.
4. gas compressor described in accordance with the claim 3, it is characterised in that: described by lever mobile jib and by between lever secondary bar
Equipped with torsionspring.
5. gas compressor described in accordance with the claim 3, it is characterised in that: described by between lever mobile jib and passive rod bearing
Equipped with tension spring and pressure spring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611219766 | 2016-12-26 | ||
| CN2016112197664 | 2016-12-26 |
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| Publication Number | Publication Date |
|---|---|
| CN106640602A CN106640602A (en) | 2017-05-10 |
| CN106640602B true CN106640602B (en) | 2019-01-11 |
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| CN201710035058.3A Expired - Fee Related CN106640602B (en) | 2016-12-26 | 2017-01-18 | A kind of gas compressor with reciprocating |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109084985A (en) * | 2018-10-31 | 2018-12-25 | 中船动力研究院有限公司 | A kind of scavenging flowing test system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2195629Y (en) * | 1994-03-25 | 1995-04-26 | 傅泽萱 | Compressor for air conditioner of vehicle |
| JP2000283037A (en) * | 1999-03-29 | 2000-10-10 | Tokyo Gas Co Ltd | Compressor |
| JP4007446B2 (en) * | 2002-09-30 | 2007-11-14 | 日産ディーゼル工業株式会社 | Air compressor device |
| CN201953605U (en) * | 2010-12-17 | 2011-08-31 | 靳北彪 | Discharge-type high-efficiency gas compressor |
| CN206503696U (en) * | 2016-12-26 | 2017-09-19 | 金继英 | A kind of efficient gas compressor with reciprocating |
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Granted publication date: 20190111 Termination date: 20220118 |