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US20090129955A1 - Linear Compressor and Drive Unit Therefor - Google Patents

Linear Compressor and Drive Unit Therefor Download PDF

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Publication number
US20090129955A1
US20090129955A1 US12/224,511 US22451107A US2009129955A1 US 20090129955 A1 US20090129955 A1 US 20090129955A1 US 22451107 A US22451107 A US 22451107A US 2009129955 A1 US2009129955 A1 US 2009129955A1
Authority
US
United States
Prior art keywords
drive unit
frame
spring
reciprocating
coil spring
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
Application number
US12/224,511
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English (en)
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
Assigned to BSH BOSCH UND SIEMENS HAUSGERAETE GMBH reassignment BSH BOSCH UND SIEMENS HAUSGERAETE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHUBERT, JAN-GRIGOR
Publication of US20090129955A1 publication Critical patent/US20090129955A1/en
Abandoned legal-status Critical Current

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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 in compressing refrigerant in a refrigerating device, and a drive unit for driving an oscillating piston movement for such a linear compressor.
  • U.S. Pat. No. 6,596,032B2 discloses a linear compressor whose drive unit comprises a frame and an oscillating 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, connected by an articulated joint to the piston rod, a piston that can move with a reciprocating motion in a cylinder.
  • the movement of the piston is driven by an electromagnet disposed all around the cylinder that interacts with the permanent magnet.
  • a disc-shaped diaphragm spring is screwed onto the piston rod in the center, and the outer edge of the diaphragm spring is connected to a yoke that surrounds the cylinder, the electromagnet and the permanent magnet.
  • the diaphragm spring Compared with many other types of spring, the diaphragm spring has the advantage that it can only be deformed with difficulty at right angles to the oscillation direction. Hence the oscillating body can only move with one degree of freedom, unlike an oscillating body suspended from a coil spring, for example, which always has three degrees of freedom of translational motion, and requires a guide if the motion is to be restricted to a single degree of freedom. Such a guide is not required for an oscillating body supported on a diaphragm spring. Hence the movement of such an oscillating body can be converted with low friction losses into the movement of a piston in a compressor, which is necessarily guided along a strictly linear path.
  • the oscillating body and the diaphragm spring form an oscillatory system whose resonant frequency is determined by the mass of the oscillating body and of the diaphragm spring, and the stiffness of the diaphragm spring.
  • the diaphragm spring permits only small oscillation amplitudes because each deflection of the oscillating body is associated with an extension of the diaphragm spring.
  • the small oscillation amplitude means it is difficult to make the dead volume of the cylinder reliably small. The larger the dead volume, however, the lower the efficiency of the compressor.
  • the short travel also compels the cylinder to be designed with a large diameter relative to the length in order to achieve a given capacity. It is costly to seal the correspondingly large piston circumference.
  • Another option for increasing the capacity is to make the diaphragm spring very stiff in order to increase the resonant frequency thereby.
  • the stiffer the diaphragm spring also means that there is a greater risk of the spring suffering fatigue for a given oscillation amplitude. This means that, in order to avoid fatigue, the amplitude must be made smaller the stiffer the spring, so that again a satisfactory increase in capacity cannot be achieved in this way.
  • the object of the present invention is to create a drive unit for a linear compressor having a frame and an oscillating body mounted in the frame via a diaphragm spring, in which the diaphragm spring allows large travel of the oscillating body without the risk of fatigue, so that a high capacity can be achieved for a small piston diameter.
  • a coil spring in addition to the diaphragm spring, is attached to the oscillating body and the frame and can be extended and compressed in the direction of movement. It is thereby possible to split the functions of guiding the oscillating body and of temporary storage of its kinetic energy.
  • the coil spring is only slightly suited to constraining the oscillating body along an exactly defined straight line, but it is not difficult to dimension it to sustain both a desired amplitude of movement and a desired frequency of movement of the oscillating body without the risk of material fatigue.
  • the diaphragm spring must have only a small material thickness in order to achieve a desired large oscillation amplitude.
  • the springs should only exert forces but no turning moments on the oscillating body.
  • the coil spring is preferably disposed around an imaginary straight line along which the center of gravity of the oscillating body can perform a reciprocating motion.
  • the straight line preferably coincides with a longitudinal axis of the coil spring.
  • the diaphragm spring In order to prevent the diaphragm spring exerting a turning moment, or in order to minimize such a turning moment, the diaphragm spring preferably has an axis of symmetry that coincides with the straight line, or a plane of symmetry on which the straight line lies.
  • one end of the coil spring preferably acts on the circumference of a spring plate to whose center the oscillating body is attached.
  • the diaphragm spring In order to make the diaphragm spring slightly deformable in the direction of movement, it preferably has a plurality of bent arms, one end of each arm being fixed to the frame and another end to the oscillating body.
  • At least two diaphragm springs are preferably provided, which act on areas of the oscillating body that are set apart in the direction of the oscillating movement.
  • the subject of the invention is also a linear compressor having a working chamber, a piston performing a reciprocating motion in the working chamber in order to compress a working fluid, and a drive unit as defined above, which is coupled to the piston to drive the reciprocating motion.
  • a linear compressor having a working chamber, a piston performing a reciprocating motion in the working chamber in order to compress a working fluid, and a drive unit as defined above, which is coupled to the piston to drive the reciprocating motion.
  • the working chamber it can be advantageous for the working chamber to be surrounded at least partially by the coil spring.
  • FIG. 1 shows a perspective view of a linear compressor according to the invention
  • FIG. 2 shows one of the two diaphragm springs of the linear compressor of FIG. 1 ;
  • FIG. 3 shows a schematic section through part of the linear compressor along an imaginary straight line G
  • FIG. 4 shows an alternative embodiment of the diaphragm spring of the linear compressor
  • FIG. 5 shows a further simplified embodiment of the diaphragm spring.
  • a frame 1 of the linear compressor comprises a base plate 2 from which extend protrusions 3 , 4 , 5 in the form of plates or ribs.
  • Two diaphragm springs 6 of the type shown in FIG. 2 are screwed onto the narrow sides of the two facing protrusions 3 .
  • the diaphragm springs 6 each comprise edge sections 7 , which rest against the end faces of the protrusions 3 and from whose ends extend Z-shaped or S-shaped spring arms 8 .
  • the ends of the spring arms 8 remote from the edge sections 7 meet each other in a center section 9 of the diaphragm spring 6 in which three holes 10 , 11 are formed.
  • An oscillating body 12 is fixed between the two diaphragm springs 6 using screws or rivets (not shown), which extend through the upper and lower holes 10 of the diaphragm springs 6 .
  • the hole 11 forms a passage for a piston rod 13 , which extends between the oscillating body 12 and a compressor assembly 14 carried by the protrusion 5 .
  • Two electromagnets 15 are arranged on either side of the permanently magnetic oscillating body 12 in a hollow space bounded by the protrusions 3 and the diaphragm springs 6 , with current being able to flow through said electromagnets in order to generate between them opposite magnetic fields to each other, which deflect the oscillating body 12 out of its equilibrium position shown in FIG. 1 along a straight line G running through the center of gravity of the oscillating body 12 in the one or the other direction.
  • the straight line G runs axially through the piston rod 13 and the compressor assembly 14 , and simultaneously forms the axis of symmetry of two spring plates 16 , which are pressed by coil springs 17 against the outer faces of the two diaphragm springs 6 .
  • FIG. 3 shows a longitudinal section through part of the linear compressor along this straight line G.
  • the spring plates 16 each have a ridge running around the edge of their concave side facing away from the diaphragm springs 6 , which fixes in a radial direction a last turn of the coil spring 17 resting against the spring plates 16 .
  • the opposite ends of the coil springs 17 are each fixed by protrusions extending inside the springs.
  • One is a flat protrusion 18 on the plate 4 of the frame 1 ; the other protrusion 19 is part of the compressor housing 14 .
  • the coil springs 17 are each stretched between the spring plates 16 and the protrusions 18 or 19 that support them in such a way that at no reversal point of the movement of the oscillating body 12 is one of the coil springs 17 not under tension.
  • the coil springs 17 hence constantly press the spring plates 16 against the diaphragm springs 6 , even when the compressor is operating and the oscillating body 12 is oscillating. Hence there is no need for the spring plates 16 to be fixed to the diaphragm springs 6 that they touch in order to maintain constant contact between them.
  • the diaphragm springs 6 and the oscillating body 12 supported by them is subjected by the coil springs 17 to forces aligned substantially only exactly in the direction of the straight line G but to negligible turning moments that could excite movement of the center of gravity of the oscillating body 12 outside the line G.
  • the high degree of symmetry of the two diaphragm springs 6 also contributes to their guiding the oscillating body 12 exactly along a line.
  • the section in FIG. 3 also shows the internal design of the compressor assembly 14 .
  • a piston 21 held by the piston rod 13 can perform reciprocating motion in an internal chamber 20 of the compressor assembly 14 in order to suck refrigerant into the chamber 20 via suction pipe 22 , and output the compressed refrigerant again at a pressure pipe 23 .
  • An annular space 24 extending in a cup shape around the chamber 20 communicates with the pressure pipe 23 .
  • the edges of the piston 21 brush along the dividing wall 25 between the chamber 20 and the annular space 24 , in which are formed a multiplicity of narrow passages 26 through which some of the compressed refrigerant can flow out of the annular space 24 back into the chamber 20 .
  • the returning refrigerant forms a gas cushion between the dividing wall 25 and the edges of the piston 21 , this cushion preventing direct frictional contact between piston 21 and dividing wall 25 and hence keeping down wear of the compressor assembly 14 .
  • a low gas flow rate in the passages 26 is sufficient to create a gas cushion effective in protecting against friction.
  • two elastically deflectable weak points 27 are formed in the piston rod 13 .
  • a slight deflection of these weak points 27 makes it possible to compensate for a small offset between the straight line G along which the center of gravity of the oscillating body 12 moves and the central longitudinal axis of the chamber 20 or even to compensate for a slight non-parallelism between the two.
  • FIGS. 4 and 5 Simplified embodiments of the diaphragm spring are shown in FIGS. 4 and 5 .
  • the spring 6 ′ of FIG. 4 essentially corresponds to half a diaphragm spring from FIG. 3 , having just two arms bent into an S-shape or a Z-shape, which extend from an edge section 7 to the center section 9 .
  • the bent arms are replaced by a straight arm 8 ′′.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
US12/224,511 2006-02-28 2007-01-09 Linear Compressor and Drive Unit Therefor Abandoned US20090129955A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006009232A DE102006009232A1 (de) 2006-02-28 2006-02-28 Linearverdichter und Antriebsaggregat dafür
DE102006009232.5 2006-02-28
PCT/EP2007/050163 WO2007098970A1 (de) 2006-02-28 2007-01-09 Linearverdichter und antriebsaggregat dafür

Publications (1)

Publication Number Publication Date
US20090129955A1 true US20090129955A1 (en) 2009-05-21

Family

ID=38024218

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/224,511 Abandoned US20090129955A1 (en) 2006-02-28 2007-01-09 Linear Compressor and Drive Unit Therefor

Country Status (7)

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

Cited By (19)

* Cited by examiner, † Cited by third party
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
US20140105761A1 (en) * 2012-10-17 2014-04-17 Jungsik Park Reciprocating compressor
US20140147305A1 (en) * 2011-05-06 2014-05-29 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
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
US9084845B2 (en) 2011-11-02 2015-07-21 Smith & Nephew Plc Reduced pressure therapy apparatuses and methods of using same
US20150226201A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226468A1 (en) * 2014-02-11 2015-08-13 General Electric Company Linear oscillation system having a suspension system and a method for assembling the 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
US20160345860A1 (en) * 2015-05-31 2016-12-01 Michael W. Wolfe Handheld Portable Impulse Oscillometer
US9844473B2 (en) 2002-10-28 2017-12-19 Smith & Nephew Plc Apparatus for aspirating, irrigating and cleansing wounds
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
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 (6)

* Cited by examiner, † Cited by third party
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
DE102007060831A1 (de) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Steuergerät für eine Kältemaschine und diese verwendendes Haushaltskältegerät
DE102007060824A1 (de) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
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
DE102010062731A1 (de) 2010-12-09 2012-06-14 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit einem Linearverdichter

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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
US5772410A (en) * 1996-01-16 1998-06-30 Samsung Electronics Co., Ltd. Linear compressor with compact motor
US6379125B1 (en) * 1996-07-09 2002-04-30 Sanyo Electric Co., Ltd. Linear compressor
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
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US6238192B1 (en) * 1998-07-03 2001-05-29 Samsung Electronics Co., Ltd. Inner core/cylinder block assembly for linear compressor and method for assembling the same
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US20050244290A1 (en) * 2002-10-16 2005-11-03 Ko Inagaki Linear motor, and linear compressor using the same

Cited By (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US7896623B2 (en) * 2004-12-23 2011-03-01 Bsh Bosch Und Siemens Hausgeraete Gmbh Linear compressor with spring arrangement
US20070292286A1 (en) * 2004-12-23 2007-12-20 Bsh Bosch Und Siemens Hausgerate Gmbh Linear Compressor
US10130526B2 (en) 2006-09-28 2018-11-20 Smith & Nephew, Inc. Portable wound therapy system
US11141325B2 (en) 2006-09-28 2021-10-12 Smith & Nephew, Inc. Portable wound therapy system
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
US12115302B2 (en) 2006-09-28 2024-10-15 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
US11027051B2 (en) 2010-09-20 2021-06-08 Smith & Nephew Plc Pressure control apparatus
US12226611B2 (en) 2010-09-20 2025-02-18 Smith & Nephew Plc Pressure control apparatus
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
US9709047B2 (en) * 2011-05-06 2017-07-18 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
US20140147305A1 (en) * 2011-05-06 2014-05-29 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
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
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
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
US10299964B2 (en) 2012-05-15 2019-05-28 Smith & Nephew Plc Negative pressure wound therapy apparatus
US12116991B2 (en) 2012-05-15 2024-10-15 Smith & Nephew Plc Negative pressure wound therapy apparatus
US10702418B2 (en) 2012-05-15 2020-07-07 Smith & Nephew Plc Negative pressure wound therapy apparatus
US9545465B2 (en) 2012-05-15 2017-01-17 Smith & Newphew 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
US20140105761A1 (en) * 2012-10-17 2014-04-17 Jungsik Park Reciprocating compressor
US20150226201A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US9841012B2 (en) * 2014-02-10 2017-12-12 Haier Us Appliance Solutions, Inc. Linear compressor
US20150226468A1 (en) * 2014-02-11 2015-08-13 General Electric Company Linear oscillation system having a suspension system and a method for assembling the same
US9752809B2 (en) * 2014-02-11 2017-09-05 Haier Us Appliance Solutions, Inc. Linear oscillation system having a suspension system and a method for assembling the same
US10737002B2 (en) 2014-12-22 2020-08-11 Smith & Nephew Plc Pressure sampling systems and methods for negative pressure wound therapy
US10973965B2 (en) 2014-12-22 2021-04-13 Smith & Nephew Plc Systems and methods of calibrating operating parameters of negative pressure wound therapy apparatuses
US11654228B2 (en) 2014-12-22 2023-05-23 Smith & Nephew Plc Status indication for negative pressure wound therapy
US10780202B2 (en) 2014-12-22 2020-09-22 Smith & Nephew Plc Noise reduction for negative pressure wound therapy apparatuses
US10682446B2 (en) 2014-12-22 2020-06-16 Smith & Nephew Plc Dressing status detection for negative pressure wound therapy
US20160345860A1 (en) * 2015-05-31 2016-12-01 Michael W. Wolfe Handheld Portable Impulse Oscillometer
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

Also Published As

Publication number Publication date
CN101389861A (zh) 2009-03-18
RU2429376C2 (ru) 2011-09-20
WO2007098970A1 (de) 2007-09-07
DE102006009232A1 (de) 2007-08-30
EP1991777B1 (de) 2015-03-18
PL1991777T3 (pl) 2015-08-31
EP1991777A1 (de) 2008-11-19
RU2008135043A (ru) 2010-04-10

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