EP1991777B1 - Linearverdichter und antriebsaggregat dafür - Google Patents

Linearverdichter und antriebsaggregat dafür Download PDF

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Publication number
EP1991777B1
EP1991777B1 EP07703714.1A EP07703714A EP1991777B1 EP 1991777 B1 EP1991777 B1 EP 1991777B1 EP 07703714 A EP07703714 A EP 07703714A EP 1991777 B1 EP1991777 B1 EP 1991777B1
Authority
EP
European Patent Office
Prior art keywords
drive unit
spring
linear compressor
oscillating body
piston
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.)
Not-in-force
Application number
EP07703714.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1991777A1 (de
Inventor
Jan-Grigor Schubert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BSH Hausgeraete GmbH
Original Assignee
BSH Bosch und Siemens Hausgeraete GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by BSH Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Priority to PL07703714T priority Critical patent/PL1991777T3/pl
Publication of EP1991777A1 publication Critical patent/EP1991777A1/de
Application granted granted Critical
Publication of EP1991777B1 publication Critical patent/EP1991777B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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

Definitions

  • the present invention relates to a linear compressor, in particular for use for compressing refrigerant in a refrigerator, and a drive unit for driving an oscillating piston movement for such a linear compressor.
  • the diaphragm spring has the advantage over many other types of springs that it is difficult to deform transversely to the direction of vibration.
  • the vibrating body is therefore movable only with one degree of freedom, unlike z. B. a suspended on a coil spring vibrating body, which is in principle movable in three degrees of freedom of translation and requires guidance if the mobility should be limited to a single degree of freedom.
  • a guide In a vibrating body held on a diaphragm spring such a guide is not required. Therefore, the movement of such a vibrating body with low friction losses in the necessarily strictly linear guided movement of a piston in a compressor can be implemented.
  • US 6,379,125 B1 does not specify the shape of the diaphragm spring.
  • a concrete example of a diaphragm spring for a linear compressor is in US 5 525 845 B1 shown. This diaphragm spring can stimulate torsional vibrations of the vibrating body.
  • the springs should exert only forces, but no torques on the oscillating body.
  • the object of the invention is to provide a drive unit whose springs meet this requirement.
  • the coil spring is preferably arranged around an imaginary straight line to which the center of gravity of the vibrating body is reciprocally movable.
  • the straight line preferably coincides with a longitudinal axis of the spiral spring.
  • one end of the coil spring engages the periphery of a spring plate, is attached to the center of the vibrating body.
  • At least two diaphragm springs are preferably provided, which engage on areas of the oscillating body which are spaced apart in the direction of the oscillating movement.
  • the invention also relates to a linear compressor having a working chamber, a reciprocating in the working chamber for compressing a working fluid piston and a drive unit as defined above, which is coupled for driving the reciprocating motion to the piston.
  • a linear compressor having a working chamber, a reciprocating in the working chamber for compressing a working fluid piston and a drive unit as defined above, which is coupled for driving the reciprocating motion to the piston.
  • the working chamber is at least partially surrounded by the coil spring.
  • a frame 1 of the linear compressor comprises a base plate 2, protrude from the plate or rib-like projections 3, 4, 5.
  • On the narrow sides of the two opposing projections 3 are two diaphragm springs 6 of the in Fig. 2 screwed type shown.
  • the diaphragm springs 6 each comprise webs 7 resting against the end faces of the projections 3, from whose ends Z- or S-shaped spring arms 8 protrude. The remote from the webs 7 ends of the spring arms 8 meet in a central portion 9 of the diaphragm spring 6 on each other, in which three openings 10, 11 are formed.
  • a vibrating body 12 is secured between the two diaphragm springs 6 by means of screws or rivets (not shown) extending through the upper and lower openings 10 of the diaphragm springs 6.
  • the opening 11 forms a passage for a piston rod 13 which extends between the vibrating body 12 and a compressor assembly 14 carried by the projection 5.
  • two electromagnets 15 are arranged on both sides of the permanent-magnetic oscillating body 12 which can be supplied with current in order to generate opposing magnetic fields between them Fig. 1 shown equilibrium position on a plane passing through the center of gravity of the vibrating body 12 extending straight line G in one or the other direction.
  • the straight line G extends axially through the piston rod 13 and the compressor assembly 14, and at the same time is the axis of symmetry of two spring plates 16 through Spiral springs 17 are pressed against the outer sides of the two diaphragm springs 6.
  • Fig. 3 shows a longitudinal section through a portion of the linear compressor along this straight line G.
  • the spring plates 16 each have at the edge facing away from the diaphragm springs 6 concave side a circumferential rib which fixes a voltage applied to the spring plate 16 last turn of the coil spring 17 in the radial direction.
  • the opposite ends of the coil springs 17 are respectively fixed by projections engaging inside the springs.
  • One is a flat projection 18 on the plate 4 of the frame 1, the other projection 19 is a part of the compressor housing 14th
  • the coil springs 17 are each biased between the spring plates 16 and the projections 18 or 19 carrying them so that at no reversal point of the movement of the vibrating body 12, one of the coil springs 17 is de-energized. Therefore, the coil springs 17 constantly keep the spring plate 16 pressed against the diaphragm springs 6, even when the compressor is in operation and the vibrating body 12 oscillates. Therefore, no firm connection between the spring plates 16 and the diaphragm springs 6 touched by them is required in order to always maintain the contact between them. Since the force of the springs 17 in each case over the entire circumference of the spring plate 16 distributed evenly distributed on the spring plate 16, at most results in a low torque that could cause a tilting of the axes of the spring plate with respect to the straight line G.
  • the high-grade symmetry of the two diaphragm springs 6 also contributes to the fact that they guide the oscillating body 12 exactly linearly.
  • the cut of the Fig. 3 also shows the internal structure of the compressor assembly 14.
  • a piston 21 held by the piston 13 back and forth to suck via a suction port 22 refrigerant in the chamber 20 and the compressed refrigerant to a discharge nozzle 23 again spend.
  • the discharge nozzle 23 communicates an annular space 24 which extends cup-shaped around the chamber 20.
  • a plurality of fine passages 26 is formed, through which a portion of the compressed refrigerant from the annulus 24 can flow back into the chamber 20.
  • the back-flowing refrigerant forms between the partition wall 25 and the flanks of the piston 21 a gas cushion, which prevents a direct sliding contact between the piston 21 and the partition wall 25 during operation and thus keeps the wear of the compressor assembly 14 low. Due to the exactly rectilinear guidance of the oscillating body 12, which is achieved by the suspension with diaphragm and coil springs 6, 17, a small gas flow in the passages 26 is sufficient to create a effective against loops protective gas cushion.
  • two elastically flexible weak points 27 are formed in the piston rod. A slight bending of these weak points 27 makes it possible to compensate for a small offset between the straight line G, on which the center of gravity of the oscillating body 12 moves, and the longitudinal central axis of the chamber 20 or even a slight non-parallelism of both.
  • FIG. 4 and 5 Simplified embodiments of the diaphragm spring are in Fig. 4 and 5 shown.
  • the spring 6 'of Fig. 4 essentially corresponds to a halved diaphragm spring Fig. 3 , with only two S- or Z-shaped curved arms 8, which extend from a web 7 to the central portion 9.
  • the spring 6 "der Fig. 5 the curved arms are replaced by a rectilinear arm 8 ", and thus this example does not fall under the scope of claim 1.
  • the free end of the rectilinear arm 8 does not move exactly on a straight line but on a circular arc, but is this deviation is negligible when the amplitude of the vibrating body is limited so that the sideways component of the movement of the vibrating body is smaller than the lateral play of the piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
EP07703714.1A 2006-02-28 2007-01-09 Linearverdichter und antriebsaggregat dafür Not-in-force EP1991777B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07703714T PL1991777T3 (pl) 2006-02-28 2007-01-09 Sprężarka liniowa i agregat napędowy dla niej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006009232A DE102006009232A1 (de) 2006-02-28 2006-02-28 Linearverdichter und Antriebsaggregat dafür
PCT/EP2007/050163 WO2007098970A1 (de) 2006-02-28 2007-01-09 Linearverdichter und antriebsaggregat dafür

Publications (2)

Publication Number Publication Date
EP1991777A1 EP1991777A1 (de) 2008-11-19
EP1991777B1 true EP1991777B1 (de) 2015-03-18

Family

ID=38024218

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07703714.1A Not-in-force EP1991777B1 (de) 2006-02-28 2007-01-09 Linearverdichter und antriebsaggregat dafür

Country Status (7)

Country Link
US (1) US20090129955A1 (pl)
EP (1) EP1991777B1 (pl)
CN (1) CN101389861A (pl)
DE (1) DE102006009232A1 (pl)
PL (1) PL1991777T3 (pl)
RU (1) RU2429376C2 (pl)
WO (1) WO2007098970A1 (pl)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0224986D0 (en) 2002-10-28 2002-12-04 Smith & Nephew Apparatus
GB0325129D0 (en) 2003-10-28 2003-12-03 Smith & Nephew Apparatus in situ
DE102004062298A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
DE602007004546D1 (de) 2006-09-28 2010-03-18 Tyco Healthcare Tragbares Wundtherapiesystem
DE102007055166A1 (de) 2007-11-19 2009-05-20 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür
DE102007060824A1 (de) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
DE102007060831A1 (de) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Steuergerät für eine Kältemaschine und diese verwendendes Haushaltskältegerät
DE102009047744A1 (de) * 2009-12-09 2011-06-16 BSH Bosch und Siemens Hausgeräte GmbH Verdichter mit einer Pumpkammer
DE102009047743A1 (de) * 2009-12-09 2011-06-16 BSH Bosch und Siemens Hausgeräte GmbH Verdichter mit einem Tragegestell
GB201015656D0 (en) 2010-09-20 2010-10-27 Smith & Nephew Pressure control apparatus
DE102010062731A1 (de) 2010-12-09 2012-06-14 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit einem Linearverdichter
EP2712406B1 (en) * 2011-05-06 2019-01-02 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
BRPI1103647A2 (pt) * 2011-07-07 2013-07-02 Whirlpool Sa disposiÇço entre componentes de compressor linear
BRPI1103447A2 (pt) * 2011-07-19 2013-07-09 Whirlpool Sa feixe de molas para compressor e compressor provido de feixe de molas
BRPI1104172A2 (pt) * 2011-08-31 2015-10-13 Whirlpool Sa compressor linear baseado em mecanismo oscilatório ressonante
US9084845B2 (en) 2011-11-02 2015-07-21 Smith & Nephew Plc Reduced pressure therapy apparatuses and methods of using same
US9427505B2 (en) 2012-05-15 2016-08-30 Smith & Nephew Plc Negative pressure wound therapy apparatus
US9496778B2 (en) 2012-08-22 2016-11-15 Ta Instruments-Waters L.L.C. Electromagnetic motor
KR101495188B1 (ko) * 2012-10-17 2015-02-24 엘지전자 주식회사 왕복동식 압축기
US9841012B2 (en) * 2014-02-10 2017-12-12 Haier Us Appliance Solutions, Inc. Linear compressor
IN2014CH00632A (pl) * 2014-02-11 2015-08-14 Gen Electric
JP6991067B2 (ja) 2014-12-22 2022-01-12 スミス アンド ネフュー ピーエルシー 陰圧閉鎖療法の装置および方法
US10492711B2 (en) * 2015-05-31 2019-12-03 Michael W. Wolfe Handheld portable impulse oscillometer
CN108217203A (zh) * 2017-05-08 2018-06-29 长沙莜芸科技有限公司 一种伸缩定量装置

Family Cites Families (12)

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US4279573A (en) * 1979-07-27 1981-07-21 Rychlik Frank J High pressure pump
US4416588A (en) * 1980-07-18 1983-11-22 Wagner Spray Tech Corporation Air compressor for paint pumps
US5092742A (en) * 1990-03-20 1992-03-03 Allen Paul V Fluid sampling pump
US5525845A (en) * 1994-03-21 1996-06-11 Sunpower, Inc. Fluid bearing with compliant linkage for centering reciprocating bodies
KR100224186B1 (ko) * 1996-01-16 1999-10-15 윤종용 선형 압축기
CN1083939C (zh) * 1996-07-09 2002-05-01 三洋电机株式会社 线性压缩机
US6596032B2 (en) * 1996-10-15 2003-07-22 Fujitsu Limited Document processing apparatus storing and modifying data using effect data
US6077054A (en) * 1997-12-23 2000-06-20 Samsung Electronics Co., Ltd. Stator of linear compressor
KR100480086B1 (ko) * 1998-01-12 2005-06-08 엘지전자 주식회사 리니어 압축기의 흡입손실 저감구조
JP3083518B2 (ja) * 1998-07-03 2000-09-04 三星電子株式会社 リニア圧縮機の内側コア及びシリンダブロックの構造並びに結合方法
JP2001227461A (ja) * 2000-02-14 2001-08-24 Matsushita Electric Ind Co Ltd リニア圧縮機
AU2003301464A1 (en) * 2002-10-16 2004-05-04 Matsushita Refrigeration Company Linear motor and liner compressor using the same

Also Published As

Publication number Publication date
RU2008135043A (ru) 2010-04-10
RU2429376C2 (ru) 2011-09-20
CN101389861A (zh) 2009-03-18
PL1991777T3 (pl) 2015-08-31
DE102006009232A1 (de) 2007-08-30
US20090129955A1 (en) 2009-05-21
WO2007098970A1 (de) 2007-09-07
EP1991777A1 (de) 2008-11-19

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