EP1831558A1 - Linearverdichter und antriebsaggregat dafür - Google Patents
Linearverdichter und antriebsaggregat dafürInfo
- Publication number
- EP1831558A1 EP1831558A1 EP05817429A EP05817429A EP1831558A1 EP 1831558 A1 EP1831558 A1 EP 1831558A1 EP 05817429 A EP05817429 A EP 05817429A EP 05817429 A EP05817429 A EP 05817429A EP 1831558 A1 EP1831558 A1 EP 1831558A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive unit
- diaphragm spring
- unit according
- spring
- frame
- 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
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 in particular a drive unit for driving an oscillating piston movement for such a linear compressor.
- a linear compressor is known, the drive unit of which comprises a frame and a vibrating body mounted in the frame via a diaphragm spring.
- the oscillating body comprises a permanent magnet, a piston rod rigidly connected to the permanent magnet, and a piston articulated to the piston rod and reciprocable in a cylinder.
- the movement of the piston is driven by an electromagnet arranged around the cylinder, which interacts with the permanent magnet.
- a disc-shaped diaphragm spring is bolted to the center of the piston rod, and the outer edge of the diaphragm spring is connected to a yoke surrounding the cylinder, the electromagnet and the permanent magnet.
- the oscillating body and the diaphragm spring form a vibratory system whose natural frequency is determined by the mass of the oscillating body and the diaphragm spring and the stiffness of the diaphragm spring.
- the diaphragm spring allows only small vibration amplitudes, since each deflection of the vibrating body is associated with an expansion of the diaphragm spring. Due to the low vibration amplitude, it is difficult to reliably make the dead volume of the cylinder small. However, the larger the dead volume, the worse the efficiency of the compressor. The small stroke also forces the cylinder to be proportionate to the large diameter length to achieve a given throughput. It is complicated to adequately seal the correspondingly large circumference of the piston.
- a gas pressure bearing for the piston is provided, that is, the swept by the piston cylinder wall has openings that communicate with the high pressure outlet of the Linear compressor are connected to form a gas cushion between the inner wall of the cylinder and the piston.
- a compressed gas bearing only works if the required overpressure is present at the outlet of the linear compressor, that is not when the compressor starts or runs out. At these times, there is a risk that the piston grinds on the cylinder wall, so that the compressor wears prematurely.
- a linear compressor according to the preamble of claim 2 is known from US 6 641 377 B2.
- each piston is held by two respective two-armed diaphragm springs.
- the arms Due to the curvature of the arms, an enlarged piston stroke is possible.
- the arms are easier to deform in the longitudinal direction of the piston than transversely thereto, so that they counteract contact of the piston with the cylinder wall.
- the oscillation frequency of the piston In order to achieve a desired throughput of the compressor, the oscillation frequency of the piston must not be too low. This oscillation frequency is higher, the stiffer the diaphragm spring is. However, too stiff a diaphragm spring runs the risk of becoming tired at high vibration amplitudes.
- Object of the present invention is to provide a drive unit for a linear compressor with a frame and mounted in the frame via a diaphragm spring vibrating body in which the diaphragm spring without risk of fatigue allows a large stroke of the vibrating body, so that a high throughput at low Piston diameter can be achieved.
- the arms of the at least one diaphragm spring should be made of a very thin material. Its strength can be so tight that it is sufficient only to prevent lateral deflection of the vibrating body.
- a weak diaphragm spring would lead to a low natural frequency of the drive unit and thus at a given stroke to a low throughput of a driven by the drive unit compressor.
- each arm is associated with a return spring, which counteracts a deformation of the arm, so that the diaphragm spring together with the return springs each forms an elastic system whose rigidity is significantly greater than that of the diaphragm spring alone.
- each arm has a single unidirectional curved section.
- Such an arm also exerts a torque on the oscillating body carried by it during deflection, so that, together with the reciprocating movement, a torsional vibration of the oscillating body is also excited.
- a rotationally symmetrical design of at least parts of the compressor may be required.
- each arm has two portions curved in different directions. Again, since the different curved portions cause torques in opposite directions, so that the torque of each arm can be made very small or made to disappear.
- the arms of a same diaphragm spring preferably hang at their attacking ends on the frame and / or at their attacking on the vibrating body ends respectively - A -
- the frame engaging ends may be connected by a frame integral with the leaf springs.
- the effective spring constant of the combination of diaphragm spring and return spring can be made adjustable in order to tune the natural frequency of the drive unit as needed.
- a coil spring is preferably used.
- 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 coupled to drive the reciprocating motion to the piston drive unit of the type described above.
- Fig. 1 is a partially sectioned side view of a linear compressor
- Fig. 2 is a plan view of a diaphragm spring for use in the linear compressor of Fig. 1 according to the invention.
- Fig. 3 is a plan view of a second embodiment of a diaphragm spring.
- Fig. 1 shows a partially sectioned side view of a linear compressor.
- the compressor has a frame with a central chamber 21, wherein in two opposite walls, here with reference to the illustration in FIG. For the sake of clarity, referred to as ceiling 22 and bottom 23, openings are formed, through which play a rod-shaped oscillating mass 24 extends.
- the chamber 21 is provided to receive unillustrated electromagnets for driving a reciprocating motion of a permanent magnet inserted into the oscillating mass 24.
- the ends of the oscillating mass 24 are fastened to central regions 16 of two diaphragm springs 8 by means of screws or rivets 25.
- the diaphragm spring 8 has a closed outer ring or frame 13 of rectangular shape, which stabilizes it prior to installation in the compressor and protects against bending. From the corners of the frame 13, four arms 14 extend toward the central region 16, each of which is composed of three straight sections 17 and two curved sections 18, 19 connecting the sections 17. The two sections 18, 19 of each arm 14 each have opposite direction of curvature. Four holes 20 for attachment of the diaphragm spring 8 are located at the corners of the frame thirteenth
- each diaphragm spring 8 rests on projecting from the ceiling 22 and the bottom 23 of the central chamber 21 webs 26.
- the diaphragm springs 8 are held on the webs 26 respectively by screws or rivets 27, each having a foot 28 of an upper or lower yoke 29, 30 and one of the holes 20 in the corners of the frame 13 intersect and engage in the central chamber 21.
- the height of the webs 26 determines the maximum stroke of the movement of the oscillating mass 24; If this maximum stroke is exceeded, the central regions 16 of the diaphragm spring 8 abut against the ceiling 22 or floor 23.
- the lower yoke 30 carries two coil springs 31, each of which is placed so that free headers 32 of them, as indicated as a dash-dotted outline in Fig. 2, each contact the curved portions 18 of two arms 14, if after deflected down, and thus resist a deflection of the oscillating mass 24 down.
- Corresponding coil springs 31, which contact the curved portions 18 of arms of the upper diaphragm spring 8 and counteract upward deflection of the oscillating mass, are provided on the upper yoke 29.
- the upper yoke 29 also carries a cylinder 33 into which a piston connected to the oscillating mass 24 via a piston rod 10, which is not visible in the figure, can be moved back and forth. Since the oscillating mass 24 is guided exactly linearly by the two diaphragm springs 8, the piston rod 12 and with it the piston carried by it can not move transversely to the direction of movement, and grinding of the piston on the inner wall of the cylinder 33 can be avoided. As a result of the movement of the piston, fluid is sucked in via a suction port 34 of the cylinder 33, compressed and expelled again via a pressure port 35.
- the diaphragm springs can therefore be made very thin and easily deformable, so that no material fatigue occurs even with long-term operation, because the energy that can not store the diaphragm springs for lack of sufficient rigidity, can be absorbed by appropriately sized coil springs 31.
- diaphragm spring compressors with different throughput can be realized by the diaphragm springs are each combined with coil springs with different spring constants, each resulting in different natural frequencies of the oscillatory system.
- Fig. 3 shows a modification of the diaphragm spring 8 of Fig. 3, which is used in their place in the compressor of FIG.
- the protective outer frame 13 has been eliminated; Instead, only the two right and the two left arms 14 are connected at their ends remote from the central region 16 by a strip of material 34.
- the arms are wider at the same outer dimensions of the diaphragm spring and thus stiffer than that of the spring of Fig. 2. The operation does not differ from that of the diaphragm spring of FIG. 3.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004062301A DE102004062301A1 (de) | 2004-12-23 | 2004-12-23 | Linearverdichter und Antriebsaggregat dafür |
PCT/EP2005/056359 WO2006069885A1 (de) | 2004-12-23 | 2005-11-30 | Linearverdichter und antriebsaggregat dafür |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1831558A1 true EP1831558A1 (de) | 2007-09-12 |
EP1831558B1 EP1831558B1 (de) | 2011-06-22 |
Family
ID=35708955
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05817429A Not-in-force EP1831558B1 (de) | 2004-12-23 | 2005-11-30 | Linearverdichter und antriebsaggregat dafür |
Country Status (8)
Country | Link |
---|---|
US (1) | US20080008607A1 (de) |
EP (1) | EP1831558B1 (de) |
CN (1) | CN100476204C (de) |
AT (1) | ATE513993T1 (de) |
DE (1) | DE102004062301A1 (de) |
ES (1) | ES2366195T3 (de) |
RU (1) | RU2386052C2 (de) |
WO (1) | WO2006069885A1 (de) |
Families Citing this family (17)
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 |
CA2604623C (en) | 2006-09-28 | 2018-10-30 | Tyco Healthcare Group Lp | Portable wound therapy system |
DE102007055166A1 (de) | 2007-11-19 | 2009-05-20 | BSH Bosch und Siemens Hausgeräte GmbH | Linearverdichter und Antriebsaggregat dafür |
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 |
BRPI1103355A2 (pt) * | 2011-07-04 | 2013-07-23 | Whirlpool Sa | dispositivo adaptador para compressor linear, e compressor provido do referido dispositivo |
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 |
CN104330249B (zh) * | 2014-10-16 | 2016-12-07 | 中国科学院上海技术物理研究所 | 直线压缩机蜗旋板弹簧径向刚度的测试装置及制造方法 |
CN104330248B (zh) * | 2014-10-16 | 2016-12-07 | 中国科学院上海技术物理研究所 | 直线压缩机蜗旋板弹簧轴向刚度的测试装置及制造方法 |
WO2016103035A2 (en) | 2014-12-22 | 2016-06-30 | Smith & Nephew Plc | Negative pressure wound therapy apparatus and methods |
Family Cites Families (23)
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US1996160A (en) * | 1933-12-23 | 1935-04-02 | Teves Kg Alfred | Driving unit for fluid pumps |
US2315222A (en) * | 1939-04-25 | 1943-03-30 | Nash Kelvinator Corp | Refrigerating apparatus |
US2907304A (en) * | 1957-04-04 | 1959-10-06 | Macks Elmer Fred | Fluid actuated mechanism |
SE434084C (sv) * | 1981-04-15 | 1985-08-20 | Sven Schriwer | Forfarande och anordning for att teta ett vid hydrostatiska eller aerostatiska lager bildat fluidummottagningsanpassat lagringsutrymme |
IT1182433B (it) * | 1985-02-12 | 1987-10-05 | Gevipi Ag | Organi di tenuta in materiale duro aventi basso coefficiente di attrito |
KR960004203B1 (ko) * | 1987-02-27 | 1996-03-28 | 빌리 에른스트 잘쯔만 | 진자(振子)피스톤 기관 |
US4960643A (en) * | 1987-03-31 | 1990-10-02 | Lemelson Jerome H | Composite synthetic materials |
US5140905A (en) * | 1990-11-30 | 1992-08-25 | Mechanical Technology Incorporated | Stabilizing gas bearing in free piston machines |
JP2518671Y2 (ja) * | 1991-06-13 | 1996-11-27 | 住友重機械工業株式会社 | 冷却機用ガスサイクル機関 |
US5318412A (en) * | 1992-04-03 | 1994-06-07 | General Electric Company | Flexible suspension for an oil free linear motor compressor |
US5525845A (en) * | 1994-03-21 | 1996-06-11 | Sunpower, Inc. | Fluid bearing with compliant linkage for centering reciprocating bodies |
DK0739449T3 (da) * | 1994-11-14 | 1998-10-07 | Anton Steiger | Indretning til styring og centrering af et maskinelement |
KR100224186B1 (ko) * | 1996-01-16 | 1999-10-15 | 윤종용 | 선형 압축기 |
US6056519A (en) * | 1997-10-15 | 2000-05-02 | Matsushita Refrigeration Company | Structure of vibrating compressor |
US6273688B1 (en) * | 1998-10-13 | 2001-08-14 | Matsushita Electric Industrial Co., Ltd. | Linear compressor |
US6073648A (en) * | 1999-04-26 | 2000-06-13 | Watson Grinding And Manufacturing Company | Metal element having a laminated coating |
JP2001227461A (ja) * | 2000-02-14 | 2001-08-24 | Matsushita Electric Ind Co Ltd | リニア圧縮機 |
BR0003293A (pt) * | 2000-07-17 | 2002-02-26 | Brasil Compressores Sa | Sistema amortecedor de vibração para compressor alternativo com motor linear |
JP4345250B2 (ja) * | 2000-11-13 | 2009-10-14 | 富士電機システムズ株式会社 | 圧縮機 |
IL142779A0 (en) * | 2001-04-24 | 2002-03-10 | Mnde Technologies L L C | Electromagnetic device particularly useful as a vibrator for a fluid pump |
DE20209839U1 (de) * | 2002-06-25 | 2002-09-12 | Bsh Bosch Siemens Hausgeraete | Verdichter-Verdunstungsschale-Anordnung |
CN100459378C (zh) * | 2002-10-16 | 2009-02-04 | 松下冷机株式会社 | 线性电动机和采用它的线性压缩机 |
JPWO2004061306A1 (ja) * | 2002-12-27 | 2006-05-11 | 株式会社ヴァレオサーマルシステムズ | 超臨界冷凍サイクル用の斜板式可変容量コンプレッサ |
-
2004
- 2004-12-23 DE DE102004062301A patent/DE102004062301A1/de not_active Withdrawn
-
2005
- 2005-11-30 ES ES05817429T patent/ES2366195T3/es active Active
- 2005-11-30 AT AT05817429T patent/ATE513993T1/de active
- 2005-11-30 EP EP05817429A patent/EP1831558B1/de not_active Not-in-force
- 2005-11-30 RU RU2007121334/06A patent/RU2386052C2/ru not_active IP Right Cessation
- 2005-11-30 CN CNB2005800444694A patent/CN100476204C/zh not_active Expired - Fee Related
- 2005-11-30 WO PCT/EP2005/056359 patent/WO2006069885A1/de active Application Filing
- 2005-11-30 US US11/794,011 patent/US20080008607A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2006069885A1 * |
Also Published As
Publication number | Publication date |
---|---|
ATE513993T1 (de) | 2011-07-15 |
CN101087953A (zh) | 2007-12-12 |
WO2006069885A1 (de) | 2006-07-06 |
US20080008607A1 (en) | 2008-01-10 |
DE102004062301A1 (de) | 2006-07-13 |
CN100476204C (zh) | 2009-04-08 |
ES2366195T3 (es) | 2011-10-18 |
RU2386052C2 (ru) | 2010-04-10 |
EP1831558B1 (de) | 2011-06-22 |
RU2007121334A (ru) | 2009-01-27 |
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