CN104903577A - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- CN104903577A CN104903577A CN201380043693.6A CN201380043693A CN104903577A CN 104903577 A CN104903577 A CN 104903577A CN 201380043693 A CN201380043693 A CN 201380043693A CN 104903577 A CN104903577 A CN 104903577A
- Authority
- CN
- China
- Prior art keywords
- valve plate
- compressor
- cylinder cap
- described cylinder
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
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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
- 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
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
- F04B39/1086—Adaptations or arrangements of distribution members the members being reed valves flat annular reed valves
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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
- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
-
- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/125—Cylinder heads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
The invention relates to a compressor for compressing a refrigerant, comprising a cylinder block, a cylinder cover (12) and a valve plate (10) which is interposed between the cylinder block and the cylinder cover (12), said valve plate (10) being connected to the cylinder cover (12) and/or to the cylinder block without redundancy in the sealing plane.
Description
The present invention relates to compressor, particularly relate to the compressor for compressed refrigerant of preamble according to claim 1.
Not only due to the application of growing techno-globalism, refrigeration technology becomes the industrial department of becoming stronger day by day.Because energy cost rises, people pay close attention to the corresponding energy of consumption such as refrigerator, compressor, air-conditioning system more and more and the most effectively utilize.
Such as, Reciprocting piston compressor in supermarket, industry and the application of marine products industry, all play an important role during the refrigeration of even mobile air conditioner and refrigerator.Reciprocting piston compressor in refrigeration technology usually has the intrinsic medium be arranged on valve plate and activates valve.Valve plate is arranged between cylinder body and cylinder cap self, and the minimum cylinder volume be located in cylinder body (compression volumes) (cylinder inner cavity, cylinder thorax) and the suction gas volume (suction gas volume) be arranged in cylinder cap and pressed gas volume (pressure gas volume) is separated.Herein, valve plate, usually together with the cylinder cap with pretensioning, by fastening screw, is pressed on cylinder body.Herein by using plain seal circle to reach sealing on two sealing planes existed.
As its name indicates, valve plate has suitable valve, these valves under any circumstance allow suction and the discharge of refrigeration agent in predetermined time, so that suction volume and P-V are connected to minimum cylinder volume, thus realize refrigeration agent entering or suction and refrigeration agent discharge in a high voltage state in a low voltage state.Except butterfly valve, ring valve also can be used in this.
Owing to acting on the mechanical load of height on valve plate and high pressure load, the size of valve openings and the thickness of the reticulated work be arranged between each opening or like, depend on that namely active force at that time and pressure act on the load on valve plate.Because the load under extreme operating conditions is relatively high, in practice, by the medium that compresses except for except gaseous state, only liquid state can be adopted in the rare cases, opening is separated by solid support thing, and because flow resistance is comparatively large, from energy angle, this is more bad.
Based on prior art discussed above, therefore object of the present invention is for providing a kind of compressor, and in particular for the compressor of compressed refrigerant, it can guarantee very superiorly thus to operate efficiently compared with the compressor of prior art.
This object is realized by the compressor according to the claims in the present invention 1.
According to the present invention, the suitable compressor for compressed refrigerant comprises gray iron and the valve plate between cylinder body and cylinder cap.Valve plate is connected with cylinder cap and/or cylinder body in compressor.This structure just has suitable stability whereby, thus compared with prior art allows to arrange larger valve openings.The valve openings of compressor can be designed to be larger, and the refrigerant flow rate of this device that can realize or select is larger.
In a possible mode of execution, outside cylinder thorax, valve plate is pressed on cylinder body by fastener (such as fastening screw nail) together with cylinder cap.In addition, valve plate (such as in the center region of cylinder thorax) is crushed on cylinder cap by fastener, and fastener here also can be fastening screw nail form.Be connected with this and accompany, the seal ring in this region is positioned in the plane (plane) identical with the seal ring of valve pocket (valve nests) (center region of cylinder thorax) exterior domain, or in this plane.Therefore identical planar seal ring (flat seal) can be used in two regions to reach sealing.
Preferably, by screw and with its adaptation, the screw thread be arranged in valve plate realizes being connected.This represents a kind of solution reliably.
In a preferred embodiment, connect and occur in pressure unit (pressure unit) or be referred to as in the region of pressure sleeve (pressure nest), namely pressure sleeve (or pressure unit) is connected to cylinder cap.Herein, pressure unit or pressure sleeve, in (the medial axis of the cylinder thorax on the direction that it extends, prolongation medial axis of cylinder thorax, medial axis in the axial direction of each cylinder bore) and the infall of valve plate between valve plate region on extend, and the opening (openings) extended in valve plate, these openings are for discharging by the refrigeration agent compressed.Therefore selectively, from the supporting member (support element) that the inwall of cylinder cap extends towards valve plate direction, especially slightly similar columniform supporting member, is arranged on and sucks in volume or P-V.This supporting member can have the recess for leading for whole connecting element (such as screw, is connected by it), and preferably, this recess is arranged on the center of supporting member bearing of trend (from the outer wall of cylinder cap to valve plate).Selectively, using supporting member oneself as connecting element, such as, valve plate can also be fixed in by binding (bonding), soft soldering (soldering) or melting welding (welding) operation.
The more feature of the present invention is illustrated in the dependent claims.
Set forth below in conjunction with the accompanying drawing based on the specific embodiment of the invention.These accompanying drawings show:
Fig. 1 is the valve plate of the compressor according to general prior art;
Fig. 2 is the three-dimensional cutaway view of cylinder cap according to compressor of the present invention and valve plate;
Fig. 3 is a part for the plan view of Fig. 2 cross-sectional plane;
Fig. 4 is the valve plate according to Fig. 3;
Fig. 5 is the plan view (being somebody's turn to do facing to cylinder body) of the valve plate according to compressor of the present invention (comprising seal ring);
Fig. 6 is the plan view (should facing to cylinder cap) of the valve plate of compressor of the present invention (comprising seal ring) according to Fig. 5;
Fig. 7 is the valve plate according to Fig. 6, but it does not have seal ring.
Fig. 1 shows the valve plate 110 of the compressor of general prior art.Region A approximately corresponds to the diameter (not shown) of cylinder, and its cover by the appropriate section of valve plate 110 and limited by cylinder cap (not shown).First surface 112 representative pressure cross section (pressure cross-section), and second surface 114 represents suction cross section (suction cross-section).Those figure clearly show: may significantly be reduced by reticulated work (webs) 116,118 by maximum cross section in theory, these reticulated works play basic role for the stability of valve plate 110.
In contrast to this, Fig. 2 to Fig. 7 shows the parts of compressor of the present invention.Fig. 2 to Fig. 4 is all the sectional views together with the cylinder cap 12 of compressor of the present invention of valve plate 10 shown in Fig. 2 with Fig. 3, and Fig. 5 to Fig. 7 all shows the plan view of the valve plate 10 of compressor of the present invention.Cylinder cap has recess (recess), is provided with screw 14 in this recess, is fastened to the cylinder body (not shown) of compressor by this cylinder cap 12 of screw.
For each cylinder be provided, cylinder cap 12 all has suction volume or sucks cavity (suction volume) 16 (recess in cylinder cap 12) and P-V 18 (being also the recess in cylinder cap 12), refrigeration agent is inhaled in the cylinder of compressor by sucking volume or sucking cavity 16, and wherein each suction volume 16 is set to the round for being surrounded on corresponding P-V 18.
Valve plate 10 has suction dish (suction disk) or intake panel (suction lamella) 20, with pressure disk (pressure disk) or pressure plate (pressure lamella) 22, its corresponding suction port (suction opening) 24 closed or open in valve plate and pressure port (pressure opening) 26, for cylinder and corresponding suction volume 16, and the gas exchanges between corresponding P-V 18.
Be in the suction dish 20 (namely when it is positioned at the state on valve gap 10) of closed condition by separated from one another with corresponding cylinder cavity (minimum cylinder volume) for suction volume 16, each suction port 24 is opened by the corresponding lifting (lifting-off) from valve plate 10, make to be flowed into minimum cylinder volume by the medium (suction gas, this sentences refrigeration agent form) compressed.Suction dish 20 is realized by the low pressure of minimum cylinder volume leading in imbibition cycle (suction cycle) from the lifting of valve plate 10.By doing like this, suction dish 20 moves from valve plate 10 to minimum cylinder volume direction.Suction dish 20 is formed circle and has suction dish outside diameter d 1 and suction dish internal diameter d2.
The pressure disk 22 (namely when it is positioned on valve plate 10) being in closed condition by P-V 18 and corresponding cylinder cavity (minimum cylinder volume) separated from one another, by opening each pressure port 26 from the suitable lifting of valve plate 10, and allow by medium (gas by compressing) the under high pressure outflow pressure volume 18 compressed.Pressure disk 22 is realized by the high pressure resulted from compression process in minimum cylinder volume from the lifting of valve plate 10.By doing like this, pressure disk 22 moves from valve plate 10 to cylinder cap direction.The same with suction dish 20, pressure disk 22 is also formed as circular and has pressure disk outside diameter d 3 and pressure disk internal diameter d4.In the present embodiment: d4<d3<d2<d1.
Due to the effect of elastic element (form with sinusoidal spring 28), pressure disk 22 is crushed in pressure port 26, and the lifting of pressure disk 22 limits by promoting latch hook (lift catch) 30.Promote that latch hook 30 is annular and be arranged on valve plate 10; By avoiding the lock (form with pin 32) rotating (against rotation), this valve plate 10 is fixed and avoids rotating.Lifting latch hook is roughly circular, or is circular round, and the external diameter promoting latch hook 30 is substantially equal to the outside diameter d 3 of pressure disk 22.
Suction dish 20 (for this reason, especially see Fig. 5) to comprise in two positions of ring protruding and be roughly the suction dish extension part (suction disk extension) 34,36 of rectangle, suction dish extension part 34,36 is separated by 180 degree of angles or toward each other on suction dish.As suction dish 20 self, suction dish extension part 34,36 is also formed corresponding to the disk construction of suction dish 20 plate shaped.Suction dish extension part 34,36 and suction are coiled 20 global formations and are made up of same material.Selectively, suction dish extension part also can be made up of other materials and/or be fixed on suction dish 20 by suitable locking method (as by bonding, soft soldering or melting welding).Suction dish extension part 34,36 all has the recess of elongated hole 38,40 (guiding) shape, and the guide finger 42,44 be arranged in valve plate fits in recess.When suction dish 20 is drawn into minimum cylinder volume and is therefore promoted from suction port 24 in the process that gas is imported into, when guide finger is positioned at outer end (external diameter) of elongated hole 38,40, suction dish extension part 34,36 is moved to pressure disk direction by guide finger 42,44 guiding (or simply: they move inward), and limit the enhancing action of suction dish 20.
Especially as can be seen from Fig. 2 to Fig. 4, in cylinder cap 12, not only screw 14 is used for connecting cylinder body, and each cylinder also has the connecting element of screw 46 form to be used for connecting valve plate 10.Screw 46 all fits in the respective threaded 48 be formed on valve plate 10 in varied situations, and realizes the connection of cylinder cap 12 and valve plate 10.In another embodiment, it is conceivable that valve plate 10 is connected to valve body for this purpose and alternatively or additionally again, be also preferably connected by screw.Except screw connection or screw are as except connecting element, other Placement can also be selected, such as bonding, soft soldering or melting welding.
In order to optimize connection and support performance, arrange the supporting member 50 of near cylindrical in P-V 18, it extends from the outer wall 52 of cylinder cap 12 to the direction of valve plate 10.Supporting member 50 is formed to be provided with the cylindrical of recess 54 at center along medial axis, or be formed the cylinder of indent, wherein supporting member 50 is a bit larger tham (about 2% to 7%) its external diameter in valve plate 10 region at the external diameter in outer wall 52 region of cylinder cap 12.Recess 54 extends from the outer wall of cylinder cap 12 to valve plate 10 direction, and for holding connecting element (screw 46).
In the mode of execution be described, the connection of screw 46 and supporting member 50 is passed through between cylinder cap 12 and valve plate 10, pressure unit all preferably occur in each cylinder of compressor or is referred to as in the region of pressure sleeve (pressure nest) 56, namely occurring in and be connected in the pressure unit of cylinder cap 12 or the region of pressure sleeve.The pressure sleeve of valve plate 10 or pressure unit 56, cylinder thorax (prolongation) medial axis (central shaft of cylinder thorax is in their extension direction at valve plate 10, each cylinder thorax central shaft in axial direction) and region between the intersection of valve plate and opening 26 on extend, wherein pressure port 26 is for discharging by the refrigeration agent compressed.
Determine the lifting height of pressure disk 22 and the lifting latch hook 30 of radial position, axially placed to fit in the recess of valve plate 10.Rising gap is necessary, not produce any redundancy (redundancy), guarantees that the tension force of screw 46 is conducted to the supporting member 50 in cylinder cap 12 by valve plate 10, and does not produce any pressure at sealing plane.In other words, between lifting latch hook 30 and cylinder cap 12, keep small gap, thus make the sealing plane between valve plate 10 and cylinder cap 12 there is not redundancy (redundant).Therefore, between lifting latch hook 30 and cylinder cap 12, be provided with gap, it prevents the sealing surfaces redundancy between valve plate 10 and cylinder cap 12.In order to can limit necessarily for the manufacture of axial play (axial play), the seal ring 58 (cylinder cap seal ring) be arranged between valve plate 10 and cylinder cap 12 can compensate this axial play.Further, seal ring (the second seal ring 59) is also arranged between valve plate 10 and cylinder body.
Fig. 5,6,7 shows the valve plate according to compressor of the present invention, and wherein, Fig. 5 shows the face towards cylinder, Fig. 6 and Fig. 7 shows the face towards cylinder cap 12.Fig. 6 also show seal ring 58 (cylinder cap seal ring).Especially as shown in Figure 7, because cylinder cap 12 and valve plate 10 are promoting the connection in latch hook 30 region, three little reticulated works 60 of blocking pressure port 26 are only needed.As compared to reticulated work 116 (in FIG, 6 reticulated works 116 are necessary) of the prior art herein, the number of reticulated work 60 reduces and wants much narrow.
This is conducive to the Performance optimization of compressor, because in numerous reason, the fill factor (volumetric efficiency) of compressor--namely in each operation cycle with minimum loss (pressure loss, Deng) obtain gas exchanges maximum as far as possible, of crucial importance to Performance optimization.The large intake relevant with displacement volume and pressure cross section are achieved, thus can reduce the pressure loss, allow gas exchanges fast.Maximum cross section can be obtained by the annular disk used.In order to optimally utilize the cross sectional area of cylinder, suction dish and the pressure disk of annular are set up coaxially with each other.Being centrally located on the medial axis of cylinder body of annular disk.
This structure brings multiple beneficial effect:
1, the tension force in the maximum pressure region of valve plate 10 is reduced.
2, the amount of deflection in the maximum pressure region of valve 10 is reduced.
3, the number of reticulated work and/or the width of reticulated work is reduced.
4, maximum cross section (outflow cross section) is expanded.
5, promote latch hook 30 to be usually axially fixed (prior art) by screw.In the present invention, promote latch hook utilize the supporting element that is integrated in cylinder cap and be axially fixed.Therefore, this valve plate 10 especially firmly and reduce the susceptibility of pressure peak, bang or liquid hammer.
6, the equalization of strain compressive force of certain part on high pressure face of screw 46.
Although the present invention is described based on the mode of execution of fixed character combination, the present invention also comprises the more superior combinations as described in (but being not limited to) appended claims that can expect.The all features disclosed in application documents are all needed as essential characteristic of the present invention, as long as they have novelty relative to prior art individually or in combination.
Reference numerals list
10 valve plates
12 cylinder caps
14 screws
16 suck volume
18 P-Vs
20 suction dish or intake panels
22 pressure disk or pressure plate
24 suction ports
26 pressure port
28 sinusoidal springs
30 promote latch hook
32 pins
34 suction dish extension parts
36 suction dish extension parts
38 elongated holes
40 elongated holes
42 guide fingers
44 guide fingers
46 screws
48 screw threads
50 supporting members
The outer wall of 52 cylinder caps 12
54 recesses
56 pressure elements, or pressure external member
58 seal rings
59 second seal rings
60 reticulated works
110 valve plates
112 first surfaces
114 second surfaces
116 reticulated works
118 reticulated works
Claims (10)
1. for the compressor of compressed refrigerant, comprise gray iron (12) and valve plate (10), described valve plate (10), between described cylinder body and described cylinder cap (12), is characterized in that:
Described valve plate (10) is connected to described cylinder cap (12) and/or is connected to described cylinder body, or is anchored on described cylinder cap and/or described cylinder body respectively.
2. compressor according to claim 1, it is characterized in that: described valve plate (10) is connected to described cylinder cap (12) and/or described cylinder body by connecting element especially screw (46), or be anchored on described cylinder cap (12) and/or described cylinder body respectively.
3. according to the compressor of above any one claim, it is characterized in that: described valve plate (10) comprises screw thread (48).
4. according to the compressor of above any one claim, it is characterized in that: described cylinder cap (12) has suction volume (16) and P-V (18), wherein, the supporting member (50) of supporting member (50) especially near cylindrical is disposed in and sucks in volume or P-V (16,18), and the outer wall (52) of described supporting member (50) from cylinder cap (12) extends towards described valve plate (10).
5. compressor according to claim 4, it is characterized in that: described supporting member (50) has the recess that the outer wall (52) from cylinder cap (12) extends towards valve plate (10) direction, and described recess is used to hold described connecting element.
6. according to the compressor of above any one claim, it is characterized in that: described valve plate (10) has one or more suction dish (20) and/or one or more pressure disk (22), described suction dish and described pressure disk are formed annular valve design.
7. according to the compressor of above any one claim, it is characterized in that: described valve plate (10) is with described cylinder cap and/or occur in the pressure external member of described valve plate (10) or the region of pressure elements (56) with the connection of described cylinder body.
8. according to the compressor of above any one claim, it is characterized in that: described valve plate (10) comprises lifting latch hook (30), and described lifting latch hook (30) limits the lifting amplitude of described pressure disk (22) away from described valve plate (10).
9. compressor according to claim 8, is characterized in that: be provided with gap between described lifting latch hook (30) and described cylinder cap (12).
10. according to the compressor of above any one claim, it is characterized in that: followed closely by fastener especially fastening screw, described valve plate (10) is pressed in region cylinder body not covering any cylinder-bore together with described cylinder cap (12), and described cylinder-bore is disposed in described cylinder body.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012016265.0A DE102012016265A1 (en) | 2012-08-17 | 2012-08-17 | compressor |
| DE102012016265.0 | 2012-08-17 | ||
| PCT/EP2013/002477 WO2014026769A1 (en) | 2012-08-17 | 2013-08-17 | Compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104903577A true CN104903577A (en) | 2015-09-09 |
Family
ID=49209312
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380043693.6A Pending CN104903577A (en) | 2012-08-17 | 2013-08-17 | Compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150219084A1 (en) |
| EP (1) | EP2885540A1 (en) |
| CN (1) | CN104903577A (en) |
| DE (1) | DE102012016265A1 (en) |
| WO (1) | WO2014026769A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150226210A1 (en) * | 2014-02-10 | 2015-08-13 | General Electric Company | Linear compressor |
| DE102015015177A1 (en) * | 2014-12-22 | 2016-06-23 | Gea Bock Gmbh | compressor |
| US10436187B2 (en) * | 2015-10-29 | 2019-10-08 | Emerson Climate Technologies, Inc. | Cylinder head assembly for reciprocating compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5174735A (en) * | 1991-04-16 | 1992-12-29 | Tecumseh Products Company | Low reexpansion valve system |
| US5213487A (en) * | 1991-06-26 | 1993-05-25 | Holset Engineering Company, Inc. | Ring valve type air compressor with deformable ring valves |
| DE4440903A1 (en) * | 1994-07-27 | 1996-02-01 | Bitzer Kuehlmaschinenbau Gmbh | Gas compressor |
| CN1525069A (en) * | 2003-02-25 | 2004-09-01 | Compressor suction reed valve | |
| CN101614200A (en) * | 2009-07-17 | 2009-12-30 | 合肥通用机械研究院 | Oil-free compressor used in locomotive |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3050237A (en) * | 1959-06-10 | 1962-08-21 | Worthington Corp | Compressor valve service |
| DE1628147A1 (en) * | 1967-09-01 | 1971-07-01 | Bosch Gmbh Robert | Air compressor |
| US4382749A (en) * | 1980-11-14 | 1983-05-10 | The Trane Company | Reciprocating compressor with integral unloader valve |
| US4752190A (en) * | 1986-06-18 | 1988-06-21 | Tecumseh Products Company | Compressor cylinder head |
-
2012
- 2012-08-17 DE DE102012016265.0A patent/DE102012016265A1/en not_active Withdrawn
-
2013
- 2013-08-17 EP EP13762982.0A patent/EP2885540A1/en not_active Withdrawn
- 2013-08-17 WO PCT/EP2013/002477 patent/WO2014026769A1/en active Application Filing
- 2013-08-17 US US14/422,085 patent/US20150219084A1/en not_active Abandoned
- 2013-08-17 CN CN201380043693.6A patent/CN104903577A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5174735A (en) * | 1991-04-16 | 1992-12-29 | Tecumseh Products Company | Low reexpansion valve system |
| US5213487A (en) * | 1991-06-26 | 1993-05-25 | Holset Engineering Company, Inc. | Ring valve type air compressor with deformable ring valves |
| DE4440903A1 (en) * | 1994-07-27 | 1996-02-01 | Bitzer Kuehlmaschinenbau Gmbh | Gas compressor |
| CN1525069A (en) * | 2003-02-25 | 2004-09-01 | Compressor suction reed valve | |
| CN101614200A (en) * | 2009-07-17 | 2009-12-30 | 合肥通用机械研究院 | Oil-free compressor used in locomotive |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014026769A1 (en) | 2014-02-20 |
| EP2885540A1 (en) | 2015-06-24 |
| WO2014026769A9 (en) | 2015-03-12 |
| US20150219084A1 (en) | 2015-08-06 |
| DE102012016265A1 (en) | 2014-02-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20150909 |
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| RJ01 | Rejection of invention patent application after publication |