CN101014770A - Linear compressor - Google Patents
Linear compressor Download PDFInfo
- Publication number
- CN101014770A CN101014770A CNA2005800135864A CN200580013586A CN101014770A CN 101014770 A CN101014770 A CN 101014770A CN A2005800135864 A CNA2005800135864 A CN A2005800135864A CN 200580013586 A CN200580013586 A CN 200580013586A CN 101014770 A CN101014770 A CN 101014770A
- Authority
- CN
- China
- Prior art keywords
- linearkompressor
- piston
- cylinder
- flange
- stage
- 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.)
- Granted
Links
- 238000004891 communication Methods 0.000 claims abstract description 9
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 238000007599 discharging Methods 0.000 claims description 8
- 238000003860 storage Methods 0.000 claims description 6
- 239000008041 oiling agent Substances 0.000 claims description 4
- 239000011148 porous material Substances 0.000 claims description 4
- 238000001816 cooling Methods 0.000 claims description 3
- 230000001050 lubricating effect Effects 0.000 claims 2
- 239000012530 fluid Substances 0.000 claims 1
- 239000000314 lubricant Substances 0.000 claims 1
- 239000007789 gas Substances 0.000 description 11
- 238000005057 refrigeration Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000000969 carrier Substances 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Images
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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
-
- 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
- F04B39/0005—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 adaptations of pistons
- F04B39/0016—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 adaptations of pistons with valve arranged in the piston
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
The present invention refers to a linear compressor comprising a piston (9) arranged slidably inside a cylinder (15); in said cylinder (15) the piston (9) defines a first low-pressure chamber (21) and a second high- pressure chamber (22), said piston being further provided with communication means (23) between said first and said second chamber (21, 22), which are controlled by valve means (24) to establish such communication therebetween.
Description
The present invention relates to a kind of Linearkompressor, especially, wish to be used for family type or industrial chiller plant.
In in the past this several years, because the chiller plant MANUFACTURER is growing the pressing for of validity of the compressor of feature for relying on ever-increasing level of efficiency, the type of employed compressor has had variation gradually, promptly, MANUFACTURER shifts to the reciprocal compressor of linear class from traditional reciprocal compressor that is driven by turning motor gradually, promptly by linear electric motor, this linear electric machine generally includes: stator, be provided with mobile member slidably with respect to this stator, it has the linear reciprocating motion that is produced by magnetic field, and the piston of compressor is installed on this mobile member.
Though consider from the angle of performance, efficient and reliability, Linearkompressor has advantage clearly, but it presents some the relevant problems of ability with its actual these favorable characteristics of acquisition gradually, and these problems may make these compressor design and make very complicated.At first, different with traditional compressor, Linearkompressor is without any the top dead center that mechanically promptly must determine and lower dead center, so consider and prevent that same piston from colliding on the cylinder head unfriendly, here produce the needs that isolated plant is set, with the piston position in the control cylinder.Top dead center in order to ensure piston is positioned at from the position in the very little gap of cylinder head, is decided to be the gap of 0.1mm usually, so that reduce so-called clearance volume to greatest extent, this control will be with point-device degree operation.Any bigger distance, even only increase a few tenths of of millimeter, the serious decline that all can produce performance characteristics, thus produce the needs of the electronic type control apparatus of very expensive and accurate complexity here, to achieve this end.
And, owing to will guarantee the correct stroke of piston, these compressors need the available and proportional return force of displacement mobile member, and the simplest available method that guarantees this power provides one and is connected in the fixed base of compressor and the mechanical spring of mobile member rightly, like this so that therefore the mechanical device that obtains can work in the resonate mode of harmonic generation of being forced to of line frequency; But when breaking away from resonance condition, the Linearkompressor that is equipped with this device can be seriously damaged on its overall performance characteristic usually.
With what further notice be, under the situation that does not mean that suitable performance loss, since about two factors, the refrigeration capacity value, i.e. and the variation of the refrigeration that can obtain by the Linearkompressor of present known type can not reach very big degree; This variation of refrigeration capacity for example can be because the needs that certain relevant is used; Perhaps even consider that the power output by making compressor is adapted to the required actual refrigeration capacity of specific run refrigerator in period and conserve energy.In fact, as writing down in the above, because from restriction with respect to the position of the middle oscillation point of the dead-centre position of cylinder head and piston, even under the situation that does not change motor efficiency, it is unmodifiable that the latter is actually, the variation of stroke of piston causes performance loss, and therefore draws the compressor performance loss from it.Because this restriction needs the resonance condition of system to remain unchanged, so the variation of piston oscillation frequency neither feasible selection, because it is impossible realize under the condition that compressor performance does not lose.
Therefore, main purpose of the present invention is by a kind of Linearkompressor is provided, wherein performance and efficiency characteristic have nothing to do in, promptly do not rely on and be not subjected to its structure, design and running requirement and variable effect in any case fully yet, so with the defective in the technological scheme of eliminating above-mentioned prior art.
A main purpose in the above-mentioned target of the present invention is, a kind of Linearkompressor is provided, and wherein, provided its refrigeration work consumption and exported the possibility that obtains wide variation, and these changes the reason that does not become same compressor overall performance performance degradation.
Another main purpose of the present invention is to provide a kind of Linearkompressor, wherein, position with respect to the piston top dead center of cylinder head can allow bigger tolerance, and this does not damage the overall performance characteristic of compressor, therefore the device that is used in the control piston position simplifications that become, and therefore make to spend and significantly reduce.
The further main purpose of the present invention is by changing the stroke of piston, or it exports adjustable possibility with respect to amplitude and the clearance or the dead volume of mid point with the refrigeration work consumption of guaranteeing compressor, and the energy efficiency value is remained unchanged at high level.
Still another main purpose of the present invention is that a kind of Linearkompressor will be provided, and its structure is very simple, and simultaneously, compares with Linearkompressor of the prior art, guarantees constant or even the efficient that may improve and the operational flexibility of improvement.
At last, in any case, the important purpose of the present invention is to provide a kind of Linearkompressor, and its cost is low and competitive, and can be by means of the machine and the technology manufacturing that obtain easily.
According to the present invention, with the above-mentioned purpose and advantage and further purpose and the advantage that become apparent, can combine in the description of carrying out from below as in the Linearkompressor of feature described in the claims 1 and characteristic, obtaining.
According to given below concrete but be not unique embodiment's description, can more easily understand the further feature and advantage of Linearkompressor of the present invention, this embodiment is described with reference to accompanying drawing as non-limitative example, wherein:
Fig. 1 is the longitdinal cross-section diagram of Linearkompressor of the present invention;
Fig. 2 is the detailed view of Fig. 1 sectional view;
The sketch that schematically illustrates of Fig. 3 Linearkompressor operation period of the present invention;
Fig. 4 is for along the schematic representation of Linearkompressor of the present invention that becomes 90 ° section with respect to Fig. 1.
The diagram of quoting and listing above the reference with the Linearkompressor of 1 expression, comprises rotor 2 usually, and it is mainly formed by the outer yoke 3 that is wound with the coil (not shown) with in the face of the interior yoke 4 of outer yoke 3 settings, and outer yoke and interior yoke are provided with so that form air gap 5 at interval.
Linearkompressor further comprises mobile member 6, and it comprises base 7, is extended with a pair of arm (not shown) from this base in mode well known in the prior art, and each in these arms all is provided with magnet and is placed in the air gap 5.Linearkompressor also comprises axle 8, and the end of axle 8 is connected with piston 9 securely, and wherein, base 7 is firmly attached to chassis 10, and this chassis 10 is connected in resonant spring 11 in turn.
As knowing very much in the prior art, provide energy by ac power supply to compressor, cause the generation of magnetic flux, it makes mobile member 6 fulfil reciprocating type translational motion with respect to rotor 6; By axle 8, this motion sends piston 9 to then.
In cylinder 15 inside, piston 9 limits first Room 21 or the low pressure chamber as will further illustrating better, with second Room 22 or as also being the hyperbaric chamber that better illustrates further, wherein, these two chambers are the variable-displacement chambers by the determining positions of the piston 9 in the cylinder 15; Two chambers 21 and 22 are arranged on the piston 9 and are interconnected by setting up as the through hole 23 of communication valve means 24 controls of leaf valve by at least one.
Because so acquired structure, piston 9 can be at the both direction of cylinder 15 inside pressurized gas alternately, therefore, form two compression stages, wherein, take place simultaneously by being arranged on the interior sucting stage in discharging in intercommunicating pore 23 on the piston 9 and communication valve means 24, the first low pressure chambers 21 or output stage and second hyperbaric chamber 22.In other words, press cycles is divided into anti-phase two stages of mutual one-tenth that change mutually with 180 °.
The working method of above-mentioned Linearkompressor is as follows, and is special in Fig. 2 and press cycles chart shown in Figure 3, in Fig. 3, represents the position of cylinder 15 inner carriers 9 to represent atmospheric pressure value corresponding to Y-axis: from lower dead center X corresponding to X-axis
1Beginning, wherein, piston 9 is positioned at the position with flange 13 vicinities, moves when piston 9 is away from flange 13 in its stroke, and the interior gas (the A-B curve of chart among Fig. 3) of clearance volume that is retained in first Room 21 is expanded, from pressure P
1Become the pressure P that is equivalent to suction pressure (some B)
2This pressure P
2Inhalation valve 17 is opened, the result, by managing 18 and suction port 16, gas is inhaled into first low pressure or precompression chamber 21 (sucting stage, line B-C) from the storage 19 with suction pipe; Last at sucting stage, piston 9 is positioned at its top dead center X
2, top dead center is positioned at from the position of lid 20 minimum clearances, therefore, is that first low pressure chamber 21 defines maximum volume.
Take place simultaneously with this sucting stage A-B-C in first low pressure chamber 21, and from corresponding to lower dead center X
1The position of piston 9 begin, the gases that are present in second hyperbaric chamber 22 at first are compressed, from pressure P
1Increase discharging or delivery pressure P
3(curve A-E), its value reaches the degree that discharging or delivery valve device 30 are opened to the force value that arrives, and therefore realizes discharging, promptly makes gas output (output stage, line E-F) by the delivery outlet 25 that covers on 20.At last (the some F) of this discharging or output stage, piston 9 is positioned at and is equivalent to its top dead center X
2The position, from the position of lid 20 minimum clearances that are provided with delivery outlet 25.Then, from this position, the dislocation of piston 9 motion beginning is oppositely moved, therefore, determined the expansion (curve F-D) of the gas in the clearance volume in second hyperbaric chamber 22, simultaneously, (curve C-D) reaches pressure P to have determined to be retained in first low pressure chamber 21 compression that sucks gas
1The value that arrives, thus balance (some D) between first Room 21 and second Room 22, set up.This force value is opened the communication valve means 24 that is arranged on the piston 9, therefore, can make precompressed gas flow into second Room 22 (line D-A) from first Room 21 by the through hole on the piston 9 23, finally reaches the lower dead center X of its shift motion up to the latter
1By this way, Linearkompressor of the present invention has been finished a cycle that is equivalent to two anti-phase mutually compression stages, as being included in the zone between an A, B, C, the D and being included in shown in the zone between an A, E, F, the D occurring in high pressure phase in second Room occurring in periods of low pressure in first Room 21 among Fig. 3.
Lubricated and the cooling unit that can be preferably used on the Linearkompressor of the present invention has further been described: by means of pump 31 in Fig. 1 and Fig. 4, oiling agent is collected into storage 32, and make it flow through first passage 33 and one or more first hole 34 that circumferentially is arranged on the cylinder type guide way 12, so that lubricated axle 8.Thus, then, oiling agent by second channel 35, be arranged at second hole 36 on the flange 13 and the third channel 37 that is positioned on the lining 14 of cylinder 15 flows into a cavity, promptly be arranged in the chuck 38 in the lining 14 to cool off the wall of cylinder 15, owing to make cylinder wall keep more low temperature, thereby reach the purpose that not only helps the thermal efficiency but also improve the integral energy efficient of compressor.
For thereby lube pistons 9 reduces its frictional force in moving process, a certain amount of oiling agent is brought first low pressure chamber 21 into by the outer surface of part axle 8.
From the top description of having made, can easily understand, Linearkompressor of the present invention is actual can to reach all previously described purpose and advantages: in fact, by Linearkompressor of the present invention, even provided under the situation of the piston 9 vibration restrictions that are equivalent to top dead center and lower dead center, still can obtain the possibility of high refrigeration output quantity, this restriction may be positioned at from corresponding cylinder end, promptly covers 20 and flange 13 position quite at a distance.Therefore, do not need as opposite single stage compressor in the prior art is desired, exist in the clearance that all will guarantee the 0.1mm minimum flow of being scheduled in any case, therefore allow to use the low and therefore position of the lower device control piston 9 of cost of accurate complexity and accuracy.
And, by the way compression stage is divided into two stages, compare with single stage compressor with identical clearance volume, can obtain much higher volumetric efficiency.In addition, the refrigeration capacity output of compressor can be regulated according to two factors: by changing shift motion or the change clearance volume with respect to the piston 9 of mid point between top dead center and the lower dead center, energy efficiency can be remained on constant high level and the reduction of having got rid of any estimable compressor overall performance simultaneously.
Like this, the performance characteristic of compressor of the present invention and efficiency characteristic have nothing to do in, promptly be not fixed against and be not subjected to any materially affect of its structure, design and running requirement and variation.
The further advantage of Linearkompressor of the present invention is from such fact, it is embodied in such mode so that guaranteed that its structure oversimplifies to greatest extent, and, make under the situation about doubling not needing, guarantee that simultaneously high characteristic renders a service as any compressor components such as piston, cylinder head or valves.
Certainly, can predict, the present invention can pass through numerous modifications and variations, can unite use with multiple no application, does not all depart from the scope of the present invention.
What should further notice is, can select to be used to realize the shape and size of material of the present invention and single part at every turn, the most suitably being fit to any specific needs or meeting the needs of any related application, this does not also mean that any running counter to the scope of the invention.
Claims (10)
1. Linearkompressor, comprise the piston (9) that is arranged at slidably in the cylinder (15), it is characterized in that, in described cylinder (15), described piston (9) defines first low pressure chamber (21) and second hyperbaric chamber (22), described piston also is provided with the control communication apparatus (23) between described first Room and described second Room (21,22), is controlled to set up this connection betwixt by control valve unit (24).
2. Linearkompressor as claimed in claim 1, wherein, described first Room and described second Room (21,22) have the variable capacity by described cylinder (15) inner carrier (9) determining positions.
3. Linearkompressor as claimed in claim 1, wherein, described communication apparatus comprises that at least one is arranged on the intercommunicating pore (23) on the described piston (9).
4. the described Linearkompressor of each claim as described above, wherein, described piston (9) is the part of movable part (6), this movable part (6) comprises base (7), is extended with axle (8) from it, at the described piston of an end portion supports (9) of axle (8).
5. Linearkompressor as claimed in claim 4, wherein, described axle (8) is contained in the guide way (12) that ends at flange (13) slidably, and this flange (13) is provided with at least one inlet hole (16) by inhalation valve (17) control.
6. Linearkompressor as claimed in claim 5, wherein, described flange (13) is wholely set with described guide way (12).
7. Linearkompressor as claimed in claim 3, wherein, described piston (9) in described cylinder (15) to the both direction compressed fluid, therefore produce two compression stages, wherein by described intercommunicating pore (23) and described communication valve means (24), the sucting stage in the discharging of described first low pressure chamber (21) or output stage and described second hyperbaric chamber (22) takes place simultaneously.
8. as claim 3 and 5 described Linearkompressors, wherein, the shift motion that described piston (9) moves away from described flange (13), in first low pressure chamber (21), formed expansion stage (AB) and sucting stage (BC) by described inhalation valve (17) control, in second hyperbaric chamber (22), be discharged control valve unit (30) control and form compression stage (AE) and discharge phase (EF), during the described compression stage of the described sucting stage of first low pressure chamber (21) and second hyperbaric chamber (22), described intercommunicating pore (23) is closed by described communication valve means (24).
9. the Linearkompressor of each claim or its combination as described above, it is characterized in that, it further comprises lubricating and cooling, lubricating and cooling is included between storage (32) and one or more first hole (34) that circumferentially is arranged on this cylinder type guide way (12) sets up the first passage (33) that is communicated with, and is fit to by described first passage (33) and described first hole (34) recycle pump (31) from described storage (32) conveyor lubricant between described (8) and described guide way (12).
10. Linearkompressor as claimed in claim 9, wherein, described oiling agent is further by second channel (35), be arranged on second hole (36) on the described flange (13) and be arranged on the interior third channel (37) of described cylinder (15), flow into cavity or chuck (38) in the wall that is arranged on described cylinder (15) from described guide way (12).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IT000029A ITPN20040029A1 (en) | 2004-04-29 | 2004-04-29 | LINEAR COMPRESSOR |
| ITPN2004A000029 | 2004-04-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101014770A true CN101014770A (en) | 2007-08-08 |
| CN100540894C CN100540894C (en) | 2009-09-16 |
Family
ID=34963342
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800135864A Expired - Fee Related CN100540894C (en) | 2004-04-29 | 2005-03-23 | Linearkompressor |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US20080063549A1 (en) |
| EP (1) | EP1740831B1 (en) |
| JP (1) | JP2007534882A (en) |
| CN (1) | CN100540894C (en) |
| AT (1) | ATE465343T1 (en) |
| BR (1) | BRPI0509952A (en) |
| DE (1) | DE602005020763D1 (en) |
| IT (1) | ITPN20040029A1 (en) |
| MX (1) | MXPA06011843A (en) |
| WO (1) | WO2005106249A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101939542A (en) * | 2008-02-06 | 2011-01-05 | Bsh博世和西门子家用器具有限公司 | Compressor unit |
| CN104110360A (en) * | 2013-04-22 | 2014-10-22 | 海尔集团公司 | Linear compressor and lubricating method thereof |
| CN108386335A (en) * | 2017-02-03 | 2018-08-10 | Lg电子株式会社 | Reciprocating dynamic compressor |
| CN110360079A (en) * | 2018-04-10 | 2019-10-22 | Lg电子株式会社 | Linearkompressor |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101932834B (en) * | 2007-10-24 | 2015-07-01 | Lg电子株式会社 | Linear compressor |
| PL2957671T3 (en) | 2009-06-29 | 2019-03-29 | Electrolux Home Products Corporation N.V. | Appliance for drying laundry |
| EP2270274B2 (en) | 2009-06-29 | 2022-01-12 | Electrolux Home Products Corporation N.V. | Appliance for drying laundry |
| CN106029972B (en) * | 2014-03-21 | 2019-01-22 | 伊莱克斯家用电器股份公司 | Clothesdrier |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1069802A (en) | 1952-01-10 | 1954-07-13 | Roulements A Billes Miniatures | Short stroke piston pump |
| US2985359A (en) * | 1956-06-29 | 1961-05-23 | Robert H Hunter | Hand pump |
| GB1551522A (en) * | 1977-04-05 | 1979-08-30 | Syndicat Des Coproprietaires D | Free-stroke compressor having a high compression ratio |
| EP0028144A1 (en) * | 1979-10-29 | 1981-05-06 | Gordon Davey | Support system for a reciprocating compressor piston |
| US4566291A (en) * | 1983-02-14 | 1986-01-28 | General Pneumatics Corporation | Closed cycle cryogenic cooling apparatus |
| US4832578A (en) * | 1986-11-14 | 1989-05-23 | The B.F. Goodrich Company | Multi-stage compressor |
| DE4304786A1 (en) * | 1993-02-17 | 1994-08-18 | Zeolith Tech | Manually operated vacuum pump |
| GB9307775D0 (en) * | 1993-04-15 | 1993-06-02 | Framo Dev Ltd | Sealing system |
| US6015270A (en) * | 1996-04-30 | 2000-01-18 | Air Conditioning Technologies | Linear compressor or pump with integral motor |
| US6016270A (en) | 1998-03-06 | 2000-01-18 | Alliance Semiconductor Corporation | Flash memory architecture that utilizes a time-shared address bus scheme and separate memory cell access paths for simultaneous read/write operations |
-
2004
- 2004-04-29 IT IT000029A patent/ITPN20040029A1/en unknown
-
2005
- 2005-03-23 BR BRPI0509952-8A patent/BRPI0509952A/en not_active IP Right Cessation
- 2005-03-23 JP JP2007510008A patent/JP2007534882A/en active Pending
- 2005-03-23 MX MXPA06011843A patent/MXPA06011843A/en not_active Application Discontinuation
- 2005-03-23 WO PCT/EP2005/051357 patent/WO2005106249A1/en active Application Filing
- 2005-03-23 AT AT05729530T patent/ATE465343T1/en not_active IP Right Cessation
- 2005-03-23 US US11/587,767 patent/US20080063549A1/en not_active Abandoned
- 2005-03-23 CN CNB2005800135864A patent/CN100540894C/en not_active Expired - Fee Related
- 2005-03-23 EP EP05729530A patent/EP1740831B1/en not_active Not-in-force
- 2005-03-23 DE DE602005020763T patent/DE602005020763D1/en active Active
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101939542A (en) * | 2008-02-06 | 2011-01-05 | Bsh博世和西门子家用器具有限公司 | Compressor unit |
| CN104110360A (en) * | 2013-04-22 | 2014-10-22 | 海尔集团公司 | Linear compressor and lubricating method thereof |
| CN104110360B (en) * | 2013-04-22 | 2016-09-28 | 青岛海尔智能技术研发有限公司 | A kind of linear compressor and lubricating method thereof |
| CN108386335A (en) * | 2017-02-03 | 2018-08-10 | Lg电子株式会社 | Reciprocating dynamic compressor |
| CN108386335B (en) * | 2017-02-03 | 2020-03-17 | Lg电子株式会社 | Reciprocating compressor |
| US10883484B2 (en) | 2017-02-03 | 2021-01-05 | Lg Electronics Inc. | Reciprocating compressor |
| CN110360079A (en) * | 2018-04-10 | 2019-10-22 | Lg电子株式会社 | Linearkompressor |
| US10935017B2 (en) | 2018-04-10 | 2021-03-02 | Lg Electronics Inc. | Linear compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| MXPA06011843A (en) | 2007-03-21 |
| DE602005020763D1 (en) | 2010-06-02 |
| EP1740831A1 (en) | 2007-01-10 |
| BRPI0509952A (en) | 2007-09-25 |
| JP2007534882A (en) | 2007-11-29 |
| US20080063549A1 (en) | 2008-03-13 |
| WO2005106249A1 (en) | 2005-11-10 |
| ATE465343T1 (en) | 2010-05-15 |
| ITPN20040029A1 (en) | 2004-07-29 |
| CN100540894C (en) | 2009-09-16 |
| EP1740831B1 (en) | 2010-04-21 |
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