US20080008607A1 - Linear Compressor And Corresponding Drive Unit - Google Patents
Linear Compressor And Corresponding Drive Unit Download PDFInfo
- Publication number
- US20080008607A1 US20080008607A1 US11/794,011 US79401105A US2008008607A1 US 20080008607 A1 US20080008607 A1 US 20080008607A1 US 79401105 A US79401105 A US 79401105A US 2008008607 A1 US2008008607 A1 US 2008008607A1
- Authority
- US
- United States
- Prior art keywords
- drive unit
- spring
- frame
- diaphragm spring
- unit according
- 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.)
- Abandoned
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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
- This invention relates to a linear compressor, in particular for use for compressing refrigerant in a refrigerating device, and in particular a drive unit for driving an oscillating piston movement for such a linear compressor.
- U.S. Pat. No. 6,506,032B2 discloses a linear compressor whose drive unit comprises a frame and an oscillating body mounted in the frame by means of 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, which piston moves back and forth in a cylinder.
- the movement of the piston is driven by an electromagnet arranged around the cylinder, which electromagnet interacts with the permanent magnet.
- a disc-shaped diaphragm spring is screwed centrally to the piston rod and the outer edge of the diaphragm spring is connected to a yoke which surrounds the cylinder, the electromagnet and the permanent magnet.
- the oscillating body and the diaphragm spring form an oscillating system whose natural frequency is determined by the mass of the oscillating body and the diaphragm spring, as well as by the stiffness of the diaphragm spring.
- the diagram spring only permits small oscillation amplitudes because any deflection of the oscillating body is associated with an expansion of the diaphragm spring. Due to the low oscillating amplitude it is difficult to reduce the dead volume of the cylinder reliably. However, the higher the dead volume the lower the efficiency of the compressor. The short stroke also necessitates designing the cylinder with a diameter that is proportional to the length in order to achieve a given throughput. It is expensive to seal the correspondingly large circumference of the piston sufficiently.
- a compressed gas bearing is provided for the piston, i.e. the cylinder wall covered by the piston has openings which are connected to the high pressure outlet of the linear compressor to form a gas cushion between the inner wall of the cylinder and the piston.
- a compressed gas bearing only functions if the required excess pressure is present at the outlet of the linear compressor, i.e. not when the compressor starts or stops. At these times there is a risk that the piston will grind against the cylinder wall, resulting in premature wear of the compressor.
- a linear compressor is disclosed in U.S. Pat. No. 6,641,377 B2.
- each piston is retained by two two-armed diaphragm springs.
- the limbs Due to the curvature of the limbs a longer piston stroke is possible.
- the limbs are more easily deformable, in the longitudinal direction of the piston, than transversely to it, so that they counteract a contact between the piston and the cylinder wall.
- the oscillating frequency of the piston must not be too low. This oscillating frequency is all the higher the stiffer the diaphragm spring. However, there is a risk that too rigid a diaphragm spring may result in fatigue at high oscillation amplitudes.
- the object of this invention is to provide a drive unit for a linear compressor with a frame and an oscillating body mounted by means of a diaphragm spring, in which the diaphragm spring permits a long stroke of the oscillating body without risk of fatigue and which is able to achieve a high throughput with a small piston diameter.
- the limbs of the at least one diaphragm spring should be produced from a very thin material. Its strength may be just sufficient to prevent lateral deflection of the oscillating body. However, such a weak diaphragm spring would result in a low natural frequency of the drive unit and hence, at a predetermined stroke, in a low throughput of a compressor driven by the drive unit.
- a readjusting spring is therefore assigned, according to the invention, to each limb, which spring counteracts a deformation of the limb so that the diaphragm spring, together with the readjusting springs, forms an elastic system whose stiffness is considerably greater than that of the diaphragm spring alone.
- each limb has an individual section curved in one direction.
- Each such limb also exerts a torque on the oscillating body supported by it when deflected, so that together with the back and forth movement a rotary oscillation of the oscillating body is also excited.
- a rotationally symmetrical structure of at least parts of the compressor may be required.
- pairs of limbs curved in opposite directions may also be provided.
- the torques induced on the differently curved limbs are mutually compensating, so that the oscillating body performs absolutely no or hardly any rotary oscillation in connection with its back and forth movement.
- Each limb preferably has two sections curved in different directions. Since the differently curved sections also generate torques in opposite directions in this case too, the torque of each individual limb may therefore be made very small or caused to disappear altogether.
- the oscillating body is reliably guided linearly in the direction of the desired oscillating movement by the two diaphragm springs, and a lateral deflection movement, which could result in contact between a piston supported by the oscillating body and a cylinder surrounding the piston, can be avoided.
- the limbs of the same diaphragm spring are preferably joined integrally together at their ends engaging on the frame and/or at their ends engaging on the oscillating body.
- the ends engaging on the frame may also be connected by a frame integral with the leaf springs.
- the effective spring constant of the combination of diaphragm and readjusting spring may be made adjustable so that the natural frequency of the drive unit can be adapted as required.
- a helical spring is preferably used as the readjusting spring.
- a further subject matter of the invention is a linear compressor with a working chamber, a piston that can be moved back and forth in the working chamber to compress a working fluid, and a drive unit of the type described above, coupled to the piston, for driving the back and forth movement.
- FIG. 1 shows a diagrammatic section through a linear compressor
- FIG. 2 shows an elevation of a diaphragm spring for use in the linear compressor in FIG. 1 according to the invention
- FIG. 3 shows an elevation of a second design of a diaphragm spring.
- FIG. 1 shows a partially cut side view of a linear compressor.
- the compressor has a frame with a central chamber 21 , in which openings are formed in two opposing walls, here with reference to the representation in the figure designed as ceiling 22 and floor 23 , for the sake of clarity, through which openings a rod-shaped oscillating mass 24 extends with a certain clearance.
- Chamber 21 is provided to accommodate electromagnets, not shown, for driving a back and forth movement of a permanent magnet inserted in oscillating mass 24 .
- oscillating mass 24 are fastened to central regions 16 of two diaphragm springs 8 of by means of screws or rivets 25
- Diaphragm spring 8 has a closed outer ring or frame 13 which is rectangular in shape, which is stabilised before installation in the compressor and protects against distortion.
- Four limbs 14 extend from the corners of frame 13 towards central region 16 , each of them being formed from three rectilinear sections 17 and two curved sections 18 , 19 connecting sections 17 .
- the two sections 18 , 19 of each limb 14 are each curved in opposite directions.
- Four bores 20 for fastening the diaphragm spring are located in the corners of frame 13 .
- each diaphragm spring 8 rests on bridges 26 projecting from ceiling 22 or floor 23 of central chamber 21 .
- Diaphragm springs 8 are retained on bridges 26 by means of screws or rivets 27 , which each intersect a foot section 28 of the upper and lower yoke 29 , 30 , respectively, and one of bores 20 in the corners of frame 13 and engage in central chamber 21 .
- the height of bridges 26 determines the maximum stroke of the movement of oscillating mass 24 ; if this maximum stroke is exceeded, the central regions 16 of diaphragm spring 8 strike against ceiling 22 and bottom 23 respectively.
- Lower yoke 30 supports two helical springs 31 , each of which is positioned so that free head piece 32 of these springs each touch curved sections 18 of two limbs 14 , as also denoted as a dash-dot outline in FIG. 2 , when they are deflected downwards and therefore resist a downward deflection of oscillating mass 24 .
- Corresponding helical springs 31 which touch curved sections 18 of limbs of upper diaphragm spring 8 and counteract an upward deflection of the oscillating mass, are provided on upper yoke 29 .
- Upper yoke 29 also supports a cylinder 33 in which a piston connected to oscillating mass 24 by means of a piston rod 10 , not shown in the figure, is able to move back and forth. Since oscillating mass 24 is guided exactly linearly by the two diaphragm springs 8 , piston rod 12 , and with it the piston supported by it, cannot deviate transversely to the direction of movement and grinding of the piston against the inner wall of cylinder 33 can be avoided. Due to the movement of the piston on the inner wall of cylinder 33 , fluid is sucked in through a suction connection 24 of cylinder 323 , is compressed and is again ejected via a pressure connection 35 .
- oscillating mass 24 When oscillating mass 24 is located at one of the points of inversion on its trajectory, its entire kinetic energy is stored in the diaphragm springs 8 and the helical springs 31 in the form of deformation energy, the distribution of the energy among the spring types depending on their respective spring constants.
- the diaphragm springs may therefore be made very thin and easily deformable so that no material fatigue occurs even during protracted operation.
- For the energy which the diaphragm springs are unable to store due to insufficient stiffness may be absorbed by suitably dimensioned helical springs 31 .
- compressors with different throughputs can be achieved with the same model of diaphragm spring if the diaphragm springs are each combined with helical springs with different spring constants, resulting in different natural frequencies of the oscillating system.
- FIG. 3 shows a modification of diaphragm spring 8 from FIG. 3 , which can be used in its stead in the compressor shown in FIG. 4 .
- outer protective frame 13 is omitted and instead only the three right and two left limbs 14 are connected at their ends facing away from central region 16 by a material strip 34 .
- the limbs are wider, given the same external dimensions of the diaphragm spring, and are therefore stiffer than those of the spring in FIG. 2 .
- the mode of operation is no different to that of the diaphragm spring shown in 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)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004062301A DE102004062301A1 (de) | 2004-12-23 | 2004-12-23 | Linearverdichter und Antriebsaggregat dafür |
DE102004062301.5 | 2004-12-23 | ||
PCT/EP2005/056359 WO2006069885A1 (de) | 2004-12-23 | 2005-11-30 | Linearverdichter und antriebsaggregat dafür |
Publications (1)
Publication Number | Publication Date |
---|---|
US20080008607A1 true US20080008607A1 (en) | 2008-01-10 |
Family
ID=35708955
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/794,011 Abandoned US20080008607A1 (en) | 2004-12-23 | 2005-11-30 | Linear Compressor And Corresponding Drive Unit |
Country Status (8)
Country | Link |
---|---|
US (1) | US20080008607A1 (ru) |
EP (1) | EP1831558B1 (ru) |
CN (1) | CN100476204C (ru) |
AT (1) | ATE513993T1 (ru) |
DE (1) | DE102004062301A1 (ru) |
ES (1) | ES2366195T3 (ru) |
RU (1) | RU2386052C2 (ru) |
WO (1) | WO2006069885A1 (ru) |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070292286A1 (en) * | 2004-12-23 | 2007-12-20 | Bsh Bosch Und Siemens Hausgerate Gmbh | Linear Compressor |
US20140054980A1 (en) * | 2012-08-22 | 2014-02-27 | Tom Andrikowich | Electromagnetic motor |
US20140193278A1 (en) * | 2011-07-04 | 2014-07-10 | Whirlpool S.A. | Adapting device for linear compressor, and compressor provided with such device |
US20140234145A1 (en) * | 2011-07-07 | 2014-08-21 | Whirlpool S.A. | Arrangement of components of a linear compressor |
US20140241911A1 (en) * | 2011-07-19 | 2014-08-28 | Whirlpool S.A. | Leaf spring and compressor with leaf spring |
US20140301874A1 (en) * | 2011-08-31 | 2014-10-09 | Whirlpool S.A. | Linear compressor based on resonant oscillating mechanism |
CN104330249A (zh) * | 2014-10-16 | 2015-02-04 | 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 |
CN104330248A (zh) * | 2014-10-16 | 2015-02-04 | 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 |
US9084845B2 (en) | 2011-11-02 | 2015-07-21 | Smith & Nephew Plc | Reduced pressure therapy apparatuses and methods of using same |
US9227000B2 (en) | 2006-09-28 | 2016-01-05 | Smith & Nephew, Inc. | Portable wound therapy system |
US9427505B2 (en) | 2012-05-15 | 2016-08-30 | Smith & Nephew Plc | Negative pressure wound therapy apparatus |
US9446178B2 (en) | 2003-10-28 | 2016-09-20 | Smith & Nephew Plc | Wound cleansing apparatus in-situ |
US9844473B2 (en) | 2002-10-28 | 2017-12-19 | Smith & Nephew Plc | Apparatus for aspirating, irrigating and cleansing wounds |
US10682446B2 (en) | 2014-12-22 | 2020-06-16 | Smith & Nephew Plc | Dressing status detection for negative pressure wound therapy |
US11027051B2 (en) | 2010-09-20 | 2021-06-08 | Smith & Nephew Plc | Pressure control apparatus |
US12029549B2 (en) | 2007-12-06 | 2024-07-09 | Smith & Nephew Plc | Apparatus and method for wound volume measurement |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Citations (22)
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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 |
US4634297A (en) * | 1981-04-15 | 1987-01-06 | Sven Schriwer | Means for sealing of a bearing space formed in hydrostatic and aerostatic bearings adapted to receive a fluid |
US4966789A (en) * | 1985-02-12 | 1990-10-30 | Masco Corporation Of Indiana | Process of manufacturing seal members having a low friction coefficient |
US4974498A (en) * | 1987-03-31 | 1990-12-04 | Jerome Lemelson | Internal combustion engines and engine components |
US5140905A (en) * | 1990-11-30 | 1992-08-25 | Mechanical Technology Incorporated | Stabilizing gas bearing in free piston machines |
US5186137A (en) * | 1987-02-27 | 1993-02-16 | Salzmann Willy E | Rocking-piston machine |
US5255521A (en) * | 1991-06-13 | 1993-10-26 | Sumitomo Heavy Industries, Ltd. | Gas cycle engine for refrigerator |
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 |
US5772410A (en) * | 1996-01-16 | 1998-06-30 | Samsung Electronics Co., Ltd. | Linear compressor with compact motor |
US5779455A (en) * | 1994-11-14 | 1998-07-14 | Steiger; Anton | Device for guiding and centering a machine component |
US6073648A (en) * | 1999-04-26 | 2000-06-13 | Watson Grinding And Manufacturing Company | Metal element having a laminated coating |
US6273688B1 (en) * | 1998-10-13 | 2001-08-14 | Matsushita Electric Industrial Co., Ltd. | Linear compressor |
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US6641377B2 (en) * | 2000-11-13 | 2003-11-04 | Fuji Electric Co., Ltd. | Linear compressor with a plurality of support springs and a dual compression unit |
US6832899B2 (en) * | 2000-07-17 | 2004-12-21 | Empresa Brasileira De Compressores S.A. Embraco | Vibration dampening system for a reciprocating compressor with a linear motor |
US20050144967A1 (en) * | 2002-06-25 | 2005-07-07 | Bsh Bosch Und Siemens Hausgerate Gmbh | Condenser-evaporator shell configuration for a refrigerating device |
US20050244290A1 (en) * | 2002-10-16 | 2005-11-03 | Ko Inagaki | Linear motor, and linear compressor using the same |
US20060083628A1 (en) * | 2002-12-27 | 2006-04-20 | Hiroshi Kanai | Swach plate type variable displayment compressor for supercritical refrigeration cycle |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6056519A (en) * | 1997-10-15 | 2000-05-02 | Matsushita Refrigeration Company | Structure of vibrating compressor |
-
2004
- 2004-12-23 DE DE102004062301A patent/DE102004062301A1/de not_active Withdrawn
-
2005
- 2005-11-30 AT AT05817429T patent/ATE513993T1/de active
- 2005-11-30 ES ES05817429T patent/ES2366195T3/es active Active
- 2005-11-30 RU RU2007121334/06A patent/RU2386052C2/ru not_active IP Right Cessation
- 2005-11-30 US US11/794,011 patent/US20080008607A1/en not_active Abandoned
- 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 EP EP05817429A patent/EP1831558B1/de not_active Not-in-force
Patent Citations (22)
Publication number | Priority date | Publication date | Assignee | Title |
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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 |
US4634297A (en) * | 1981-04-15 | 1987-01-06 | Sven Schriwer | Means for sealing of a bearing space formed in hydrostatic and aerostatic bearings adapted to receive a fluid |
US4966789A (en) * | 1985-02-12 | 1990-10-30 | Masco Corporation Of Indiana | Process of manufacturing seal members having a low friction coefficient |
US5186137A (en) * | 1987-02-27 | 1993-02-16 | Salzmann Willy E | Rocking-piston machine |
US4974498A (en) * | 1987-03-31 | 1990-12-04 | Jerome Lemelson | Internal combustion engines and engine components |
US5140905A (en) * | 1990-11-30 | 1992-08-25 | Mechanical Technology Incorporated | Stabilizing gas bearing in free piston machines |
US5255521A (en) * | 1991-06-13 | 1993-10-26 | Sumitomo Heavy Industries, Ltd. | Gas cycle engine for refrigerator |
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 |
US5779455A (en) * | 1994-11-14 | 1998-07-14 | Steiger; Anton | Device for guiding and centering a machine component |
US5772410A (en) * | 1996-01-16 | 1998-06-30 | Samsung Electronics Co., Ltd. | Linear compressor with compact motor |
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 |
US6506032B2 (en) * | 2000-02-14 | 2003-01-14 | Matsushita Electric Industrial Co., Ltd. | Linear compressor |
US6832899B2 (en) * | 2000-07-17 | 2004-12-21 | Empresa Brasileira De Compressores S.A. Embraco | Vibration dampening system for a reciprocating compressor with a linear motor |
US6641377B2 (en) * | 2000-11-13 | 2003-11-04 | Fuji Electric Co., Ltd. | Linear compressor with a plurality of support springs and a dual compression unit |
US20020155012A1 (en) * | 2001-04-24 | 2002-10-24 | Mnde Technologies L.L.C. | Electromagnetic device particularly useful as a vibrator for a fluid pump |
US20050144967A1 (en) * | 2002-06-25 | 2005-07-07 | Bsh Bosch Und Siemens Hausgerate Gmbh | Condenser-evaporator shell configuration for a refrigerating device |
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US20060083628A1 (en) * | 2002-12-27 | 2006-04-20 | Hiroshi Kanai | Swach plate type variable displayment compressor for supercritical refrigeration cycle |
Cited By (40)
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---|---|---|---|---|
US10842678B2 (en) | 2002-10-28 | 2020-11-24 | Smith & Nephew Plc | Apparatus for aspirating, irrigating and cleansing wounds |
US10278869B2 (en) | 2002-10-28 | 2019-05-07 | Smith & Nephew Plc | Apparatus for aspirating, irrigating and cleansing wounds |
US9844473B2 (en) | 2002-10-28 | 2017-12-19 | Smith & Nephew Plc | Apparatus for aspirating, irrigating and cleansing wounds |
US9452248B2 (en) | 2003-10-28 | 2016-09-27 | Smith & Nephew Plc | Wound cleansing apparatus in-situ |
US9446178B2 (en) | 2003-10-28 | 2016-09-20 | Smith & Nephew Plc | Wound cleansing apparatus in-situ |
US20070292286A1 (en) * | 2004-12-23 | 2007-12-20 | Bsh Bosch Und Siemens Hausgerate Gmbh | Linear Compressor |
US7896623B2 (en) * | 2004-12-23 | 2011-03-01 | Bsh Bosch Und Siemens Hausgeraete Gmbh | Linear compressor with spring arrangement |
US9227000B2 (en) | 2006-09-28 | 2016-01-05 | Smith & Nephew, Inc. | Portable wound therapy system |
US9642955B2 (en) | 2006-09-28 | 2017-05-09 | Smith & Nephew, Inc. | Portable wound therapy system |
US11141325B2 (en) | 2006-09-28 | 2021-10-12 | Smith & Nephew, Inc. | Portable wound therapy system |
US10130526B2 (en) | 2006-09-28 | 2018-11-20 | Smith & Nephew, Inc. | Portable wound therapy system |
US12029549B2 (en) | 2007-12-06 | 2024-07-09 | Smith & Nephew Plc | Apparatus and method for wound volume measurement |
US11623039B2 (en) | 2010-09-20 | 2023-04-11 | Smith & Nephew Plc | Systems and methods for controlling operation of a reduced pressure therapy system |
US11534540B2 (en) | 2010-09-20 | 2022-12-27 | Smith & Nephew Plc | Pressure control apparatus |
US11027051B2 (en) | 2010-09-20 | 2021-06-08 | Smith & Nephew Plc | Pressure control apparatus |
US20140193278A1 (en) * | 2011-07-04 | 2014-07-10 | Whirlpool S.A. | Adapting device for linear compressor, and compressor provided with such device |
US9797388B2 (en) * | 2011-07-04 | 2017-10-24 | Whirlpool S.A. | Adapting device for linear compressor, and compressor provided with such device |
US9562526B2 (en) * | 2011-07-07 | 2017-02-07 | Whirlpool S.A. | Arrangement of components of a linear compressor |
US20140234145A1 (en) * | 2011-07-07 | 2014-08-21 | Whirlpool S.A. | Arrangement of components of a linear compressor |
US20140241911A1 (en) * | 2011-07-19 | 2014-08-28 | Whirlpool S.A. | Leaf spring and compressor with leaf spring |
US9534591B2 (en) * | 2011-08-31 | 2017-01-03 | Whirlpool S.A. | Linear compressor based on resonant oscillating mechanism |
US20140301874A1 (en) * | 2011-08-31 | 2014-10-09 | Whirlpool S.A. | Linear compressor based on resonant oscillating mechanism |
US11253639B2 (en) | 2011-11-02 | 2022-02-22 | Smith & Nephew Plc | Reduced pressure therapy apparatuses and methods of using same |
US9084845B2 (en) | 2011-11-02 | 2015-07-21 | Smith & Nephew Plc | Reduced pressure therapy apparatuses and methods of using same |
US10143783B2 (en) | 2011-11-02 | 2018-12-04 | Smith & Nephew Plc | Reduced pressure therapy apparatuses and methods of using same |
US11648342B2 (en) | 2011-11-02 | 2023-05-16 | Smith & Nephew Plc | Reduced pressure therapy apparatuses and methods of using same |
US9545465B2 (en) | 2012-05-15 | 2017-01-17 | Smith & Newphew Plc | Negative pressure wound therapy apparatus |
US10702418B2 (en) | 2012-05-15 | 2020-07-07 | Smith & Nephew Plc | Negative pressure wound therapy apparatus |
US9427505B2 (en) | 2012-05-15 | 2016-08-30 | Smith & Nephew Plc | Negative pressure wound therapy apparatus |
US10299964B2 (en) | 2012-05-15 | 2019-05-28 | Smith & Nephew Plc | Negative pressure wound therapy apparatus |
US9496778B2 (en) * | 2012-08-22 | 2016-11-15 | Ta Instruments-Waters L.L.C. | Electromagnetic motor |
US20140054980A1 (en) * | 2012-08-22 | 2014-02-27 | Tom Andrikowich | Electromagnetic motor |
US9768675B2 (en) | 2012-08-22 | 2017-09-19 | Ta Instruments-Waters L.L.C. | Electromagnetic motor |
CN104330249A (zh) * | 2014-10-16 | 2015-02-04 | 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 |
CN104330248A (zh) * | 2014-10-16 | 2015-02-04 | 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 |
US10973965B2 (en) | 2014-12-22 | 2021-04-13 | Smith & Nephew Plc | Systems and methods of calibrating operating parameters of negative pressure wound therapy apparatuses |
US10780202B2 (en) | 2014-12-22 | 2020-09-22 | Smith & Nephew Plc | Noise reduction for negative pressure wound therapy apparatuses |
US10737002B2 (en) | 2014-12-22 | 2020-08-11 | Smith & Nephew Plc | Pressure sampling systems and methods for negative pressure wound therapy |
US10682446B2 (en) | 2014-12-22 | 2020-06-16 | Smith & Nephew Plc | Dressing status detection for negative pressure wound therapy |
US11654228B2 (en) | 2014-12-22 | 2023-05-23 | Smith & Nephew Plc | Status indication for negative pressure wound therapy |
Also Published As
Publication number | Publication date |
---|---|
WO2006069885A1 (de) | 2006-07-06 |
CN100476204C (zh) | 2009-04-08 |
CN101087953A (zh) | 2007-12-12 |
ATE513993T1 (de) | 2011-07-15 |
EP1831558A1 (de) | 2007-09-12 |
EP1831558B1 (de) | 2011-06-22 |
RU2007121334A (ru) | 2009-01-27 |
RU2386052C2 (ru) | 2010-04-10 |
ES2366195T3 (es) | 2011-10-18 |
DE102004062301A1 (de) | 2006-07-13 |
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