EP1831559A1 - Compresseur lineaire et unite d'entrainement pour ledit compresseur - Google Patents

Compresseur lineaire et unite d'entrainement pour ledit compresseur

Info

Publication number
EP1831559A1
EP1831559A1 EP05845997A EP05845997A EP1831559A1 EP 1831559 A1 EP1831559 A1 EP 1831559A1 EP 05845997 A EP05845997 A EP 05845997A EP 05845997 A EP05845997 A EP 05845997A EP 1831559 A1 EP1831559 A1 EP 1831559A1
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
Application number
EP05845997A
Other languages
German (de)
English (en)
Other versions
EP1831559B1 (fr
Inventor
Alexander Schade
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=35814082&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1831559(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by BSH Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Publication of EP1831559A1 publication Critical patent/EP1831559A1/fr
Application granted granted Critical
Publication of EP1831559B1 publication Critical patent/EP1831559B1/fr
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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 refrigerants in a refrigerator, and in particular a drive unit for driving an oscillating linear 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 pressurized 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 1 is known from US 6 641 377 B2.
  • each piston is held by two respective two-armed diaphragm springs.
  • each diaphragm spring exerts a torque on the piston in the deflected state. If this torque is not compensated for exactly, the piston in addition to its linear oscillatory motion of a torsional vibration, and it can be wobbled movements of the piston are excited, which can lead to contact between the piston and cylinder and consequently to increased wear.
  • Object of the present invention is to provide a low-wear 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 allows a large stroke of the vibrating body, or reach a high throughput at low piston diameter can.
  • the object is achieved in that the plurality of arms of the diaphragm spring each engage with one end on the frame and with another end on the vibrating body, and that the arms between the two ends in pairs have sections with opposite curvature.
  • the arms do not extend in the shortest path between the two ends, so that when the vibrating body is deflected they can stretch and approach the rectilinear shape without having to stretch the material of the arms.
  • the diaphragm spring has pairs of arms with portions curved in respective opposite directions.
  • each arm has a single unidirectional curved section.
  • Each such arm also exerts a torque on the oscillating body supported by it, which, however, is compensated by the pair of oppositely curved arms paired with it.
  • 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 oscillating body is reliably guided linearly in the direction of the desired oscillatory movement, and a lateral evasive movement, which could lead to contact between a piston carried by the oscillating body and a cylinder surrounding the piston, can be avoided.
  • the arms of a same diaphragm spring preferably hang together in one piece at their attacking on the frame ends and / or at their attacking on the oscillating body ends.
  • the frame engaging ends may be connected by a frame integral with the leaf springs.
  • 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. However, such a weak diaphragm spring would result in a low natural frequency of the drive unit - A -
  • each arm is preferably associated with a return spring, which counteracts deformation of the arm, so that the diaphragm spring together with the return springs each form an elastic system whose rigidity is significantly greater than that Diaphragm spring alone.
  • the effective spring constant of the correlation 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 shows a schematic section through 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. 4 is a partially sectioned side view of a linear compressor with the diaphragm spring shown in Fig. 3; and Fig. 5 shows a further embodiment of a diaphragm spring.
  • the linear compressor for a refrigerator shown in Fig. 1 comprises a compressor chamber 1, which is bounded on the one hand by a movable piston 2 and on the other hand by a cylinder 3, which is composed of a pipe section 4 and a cover 5.
  • a suction nozzle, a discharge nozzle and valves that allow an influx of refrigerant in the compressor chamber only via the suction nozzle and a drain only via the discharge nozzle.
  • the pipe section 4 is concentrically surrounded by a second pipe section 6 and connected to it via a radial flange 7.
  • a diaphragm spring 8 At the end facing away from the flange 7 of the pipe section 6, the circumference of a diaphragm spring 8 is fixed.
  • a vibrating body 9 At the center of the diaphragm spring 8, a vibrating body 9 is mounted, which is composed of a piston rod 10, to which the piston 2 is articulated, a flange 11 fixed to the piston rod 10 and a permanent magnet 12 which is secured to the flange 11 and into the space between the pipe sections 6, 4 dips. Also housed in the gap electromagnets for exerting a force in the direction of the piston rod 10 on the permanent magnet 12 are omitted in the figure.
  • the diaphragm spring 8 is made of spring steel or other elastically deformable but substantially non-stretchable material.
  • the central region of the diaphragm spring 8 is elastically deflectable with little force in a direction perpendicular to the plane of FIG. 2, the deflection resulting in the arms 14 slightly reducing their curvature in plan view and the central region being rotated slightly counterclockwise.
  • the resistance of the diaphragm spring 8 against a displacement of the central region in the plane of Fig. 2 is substantially greater than the resistance to a deflection perpendicular to this plane, so that at the Opening 15 of the diaphragm spring 8 fixed end of the piston rod 10 is reliably guided linearly movable.
  • a second embodiment of the diaphragm spring 8 is shown in Fig. 3 in a plan view.
  • This embodiment has a closed outer ring 13.
  • This ring is here of rectangular shape, but this is of little importance for the function of the diaphragm spring.
  • the two sections 18, 19 of each arm 14 each have opposite direction of curvature.
  • Four holes 20 for attachment of the diaphragm spring are located at the corners of the frame thirteenth
  • Fig. 4 shows a partially sectioned side view of a linear compressor in which diaphragm springs 8 of the type shown in Fig. 3 are used.
  • 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 is provided to receive unillustrated electromagnets for driving a reciprocating motion of a permanent magnet inserted into the oscillating mass.
  • the ends of the oscillating mass 24 are at the central portions 16 of two diaphragm springs 8 of the form shown in Fig. 3 by means of screws or rivets 25th attached.
  • the frame 13 of each diaphragm spring 8 in turn rests on projecting from the ceiling 22 and the bottom 23 of the central chamber 21 webs 26.
  • the height of the webs 26 defines the maximum stroke of 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 diaphragm springs 8 are held on the webs 26 each by screws or rivets 27, each crossing a foot piece 28 of an upper or lower yoke 29, 30 and one of the holes 19 in the corners of the frame 13 and engage in the central chamber 21.
  • the lower yoke 30 supports two coil springs 31, each of which is placed so that free headers 32 of them, as indicated by a dash-dotted outline in Fig. 3, respectively contact the curved portions 18 of two arms 14 when deflected downwardly , and so 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.
  • the diaphragm springs can therefore be made very thin and easily deformable, so that no material fatigue occurs even with long-lasting operation, because the energy that the diaphragm springs for lack of sufficient rigidity are unable to store, can be absorbed by appropriately sized coil springs 31.
  • the diaphragm springs are each combined with coil springs with different spring constants, each resulting in different natural frequencies of the oscillatory system.
  • Fig. 5 shows a modification of the diaphragm spring 8 of Fig. 3, which is used in their place in the compressor of FIG.
  • the outer frame 13 has been omitted. 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 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)

Abstract

Unité d'entraînement pour un compresseur linéaire, qui comporte un châssis (21, 29, 30) et un corps oscillant (24, 10) monté dans le châssis (21, 29, 30) par l'intermédiaire d'au moins un ressort à membrane (8) et effectuant un mouvement de va-et-vient dans une direction. Le ressort à membrane (8) comporte plusieurs bras (14) dont l'une des extrémités repose sur le châssis (21, 29, 30) et dont l'autre extrémité repose sur le corps oscillant (24). Chaque paire de bras (14) possède entre les deux extrémités des segments incurvés opposés (18, 19).
EP05845997.5A 2004-12-23 2005-11-30 Compresseur lineaire et unite d'entrainement pour ledit compresseur Revoked EP1831559B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004062302A DE102004062302A1 (de) 2004-12-23 2004-12-23 Linearverdichter und Antriebsaggregat dafür
PCT/EP2005/056356 WO2006069884A1 (fr) 2004-12-23 2005-11-30 Compresseur lineaire et unite d'entrainement pour ledit compresseur

Publications (2)

Publication Number Publication Date
EP1831559A1 true EP1831559A1 (fr) 2007-09-12
EP1831559B1 EP1831559B1 (fr) 2015-01-28

Family

ID=35814082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05845997.5A Revoked EP1831559B1 (fr) 2004-12-23 2005-11-30 Compresseur lineaire et unite d'entrainement pour ledit compresseur

Country Status (6)

Country Link
US (1) US20080089796A1 (fr)
EP (1) EP1831559B1 (fr)
CN (1) CN101087954B (fr)
DE (1) DE102004062302A1 (fr)
RU (1) RU2376497C2 (fr)
WO (1) WO2006069884A1 (fr)

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GB0224986D0 (en) 2002-10-28 2002-12-04 Smith & Nephew Apparatus
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DE102004062301A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür
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
GB0723855D0 (en) 2007-12-06 2008-01-16 Smith & Nephew Apparatus and method for wound volume measurement
BRPI0902557B1 (pt) 2009-07-08 2020-03-10 Embraco Indústria De Compressores E Soluções E Refrigeração Ltda. Compressor linear
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BRPI1005184B1 (pt) * 2010-12-27 2020-09-24 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda. Mecanismo ressonante para compressores lineares
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
WO2013058671A1 (fr) * 2011-10-18 2013-04-25 Открытое акционерное общество "Елатомский приборный завод" Dispositif pour mesurer la tension intra-oculaire à travers la paupière
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CN111336088B (zh) * 2020-02-13 2021-11-02 杭州电子科技大学 一种直线型臂板弹簧线性压缩机
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Also Published As

Publication number Publication date
RU2376497C2 (ru) 2009-12-20
US20080089796A1 (en) 2008-04-17
CN101087954B (zh) 2011-04-06
RU2007121771A (ru) 2009-01-27
CN101087954A (zh) 2007-12-12
DE102004062302A1 (de) 2006-07-13
EP1831559B1 (fr) 2015-01-28
WO2006069884A1 (fr) 2006-07-06

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