EP1991777A1 - Linear compressor and drive unit therefor - Google Patents

Linear compressor and drive unit therefor

Info

Publication number
EP1991777A1
EP1991777A1 EP07703714A EP07703714A EP1991777A1 EP 1991777 A1 EP1991777 A1 EP 1991777A1 EP 07703714 A EP07703714 A EP 07703714A EP 07703714 A EP07703714 A EP 07703714A EP 1991777 A1 EP1991777 A1 EP 1991777A1
Authority
EP
European Patent Office
Prior art keywords
drive unit
spring
unit according
frame
linear compressor
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
EP07703714A
Other languages
German (de)
French (fr)
Other versions
EP1991777B1 (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
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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/en
Publication of EP1991777A1 publication Critical patent/EP1991777A1/en
Application granted granted Critical
Publication of EP1991777B1 publication Critical patent/EP1991777B1/en
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.
  • 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 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.
  • 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 hub also forces the cylinder to be made in proportion to the large diameter length to achieve a given throughput. It is complicated to adequately seal the correspondingly large circumference of the piston.
  • Another way to increase the throughput is to make the diaphragm spring very stiff so as to increase the natural frequency.
  • 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 object is achieved in that in addition to the diaphragm spring, a coil spring attached to the vibrating body and the frame and in the direction of movement is stretchable and compressible. Thereby, it is possible to divide the functions of guiding the vibrating body and temporarily storing its kinetic energy.
  • the coil spring is poorly suited to forcing the vibrating body to a well-defined straight-line path, but it is not difficult to size it to support both a desired amplitude of motion and a desired frequency of movement of the vibrating body without the risk of material fatigue.
  • the diaphragm spring may only have a small material thickness in order to achieve a desired large oscillation amplitude.
  • the helical spring is preferably arranged around an imaginary straight line, on which the center of gravity of the oscillating body is movable to and fro.
  • the straight line preferably coincides with a longitudinal axis of the spiral spring.
  • the diaphragm spring In order to prevent the diaphragm spring from exerting a torque or to minimize such a torque, the diaphragm spring preferably has an axis of symmetry which coincides with the straight line or a plane of symmetry in which the straight line runs.
  • one end of the coil spring engages the periphery of a spring plate, is attached to the center of the vibrating body.
  • the diaphragm spring In order to make the diaphragm spring easily deformable in the direction of movement, it preferably has a plurality of curved arms, one end of which is fixed to the frame and another end to the oscillating 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.
  • FIG. 1 is a perspective view of a linear compressor according to the invention
  • FIG. 2 shows one of the two diaphragm springs of the linear compressor from FIG. 1;
  • Fig. 5 is a further simplified embodiment of the diaphragm spring.
  • a frame 1 of the linear compressor comprises a base plate 2, protrude from the plate or rib-like projections 3, 4, 5.
  • two diaphragm springs 6 of the type shown in Fig. 2 are screwed.
  • 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 1 1 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, which are energized to generate between them opposing magnetic fields, the oscillating body 12 from its equilibrium position shown in FIG to deflect the center of gravity of the oscillating 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 of their side facing away from the diaphragm springs 6 concave side a circumferential rib, which is applied to the spring plate 16 last turn of the coil spring 17 in the radial Direction fixed.
  • 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 section of Fig. 3 also shows the internal structure of the compressor assembly 14. In an internal chamber 20 of the compressor assembly 14, a held by the piston rod 13 piston 21 back and forth to suck via a suction port 22 refrigerant into the chamber 20 and to spend the compressed refrigerant at a pressure port 23 again. With 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 low 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.
  • FIGS. 4 and 5 Simplified embodiments of the diaphragm spring are shown in FIGS. 4 and 5.
  • the spring 6 'of Fig. 4 substantially corresponds to a halved diaphragm spring of Fig. 3, with only two S- or Z-shaped curved arms 8, which extend from a web 7 to the central portion 9.
  • the curved arms are replaced by a straight arm 8".
  • its free end does not move exactly on a straight line, but on a circular arc, 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)

Abstract

The drive unit for a linear compressor comprises a frame (1) and an oscillation body (12), connected to the frame (1) by means of a membrane spring (6) and guided to move back and forth in relation to the frame in a straight line. A coil spring (17) is connected to the oscillation body (12) and the frame and may be extended and compressed in the direction of the movement.

Description

Linearverdichter und Antriebsaggregat dafür Linear compressor and drive unit for it
Die vorliegende Erfindung betrifft einen Linearverdichter, insbesondere für den Einsatz zum Verdichten von Kältemittel in einem Kältegerät, und ein Antriebsaggregat zum Antreiben einer oszillierenden Kolbenbewegung für einen solchen Linearverdichter.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.
Aus US 6 596 032B2 ist ein Linearverdichter bekannt, dessen Antriebsaggregat ein Gestell und einen in dem Gestell über eine Membranfeder gelagerten Schwingkörper umfasst. Der Schwingkörper umfasst einen Permanentmagneten, eine mit dem Permanentmagneten starr verbundene Kolbenstange und einen an die Kolbenstange angelenkten Kolben, der in einem Zylinder hin- und her beweglich ist. Die Bewegung des Kolbens ist angetrieben durch einen rings um den Zylinder angeordneten Elektromagneten, der mit dem Permanentmagneten wechselwirkt. Eine scheibenförmige Membranfeder ist mittig an der Kolbenstange verschraubt, und der äußere Rand der Membranfeder ist einem Joch verbunden, das den Zylinder, den Elektromagneten und den Permanentmagneten umgibt.From US Pat. No. 6,596,032B2 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.
Die Membranfeder hat gegenüber vielen anderen Federtypen den Vorteil, dass sie quer zur Schwingrichtung nur schwer verformbar ist. Der Schwingkörper ist daher nur mit einem Freiheitsgrad beweglich, anders als z. B. ein an einer Schraubenfeder aufgehängter Schwingkörper, der prinzipiell in drei Freiheitsgraden der Translation beweglich ist und einer Führung bedarf, wenn die Beweglichkeit auf einen einzigen Freiheitsgrad eingeschränkt sein soll. Bei einem an einer Membranfeder gehaltenen Schwingkörper ist eine solche Führung nicht erforderlich. Deshalb ist die Bewegung eines solchen Schwingkörpers mit geringen Reibungsverlusten in die notwendigerweise streng linear geführte Bewegung eines Kolbens in einem Verdichter umsetzbar.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. 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.
Der Schwingkörper und die Membranfeder bilden ein schwingfähiges System, dessen Eigenfrequenz durch die Masse des Schwingkörpers und der Membranfeder sowie die Steifigkeit der Membranfeder bestimmt ist. Die Membranfeder lässt nur kleine Schwingungsamplituden zu, da jede Auslenkung des Schwingkörpers mit einer Dehnung der Membranfeder verbunden ist. Aufgrund der geringen Schwingungsamplitude ist es schwierig, das Totvolumen des Zylinders zuverlässig klein zu machen. Je größer aber das Totvolumen ist, um so schlechter ist der Wirkungsgrad des Verdichters. Der kleine Hub zwingt ferner dazu, den Zylinder mit in Verhältnis zur Länge großem Durchmesser auszubilden, um einen gegebenen Durchsatz zu erreichen. Es ist aufwändig, den entsprechend großen Umfang des Kolbens hinreichend abzudichten.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 hub also forces the cylinder to be made in proportion to the large diameter length to achieve a given throughput. It is complicated to adequately seal the correspondingly large circumference of the piston.
Eine andere Möglichkeit, den Durchsatz zu erhöhen, ist, die Membranfeder sehr steif zu machen, um so die Eigenfrequenz zu erhöhen. Je steifer die Membranfeder ist, um so größer ist aber auch die Gefahr, dass diese bei einer gegebenen Schwingungsamplitude ermüdet. D. h. um die Ermüdung zu vermeiden, muss die Amplitude um so kleiner gemacht werden, je steifer die Feder ist, so dass auch auf diese Weise eine befriedigende Durchsatzsteigerung nicht zu erreichen ist.Another way to increase the throughput is to make the diaphragm spring very stiff so as to increase the natural frequency. The stiffer the diaphragm spring is, but the greater is the risk that it fatigues at a given amplitude of vibration. Ie. To avoid fatigue, the smaller the stiffness of the spring, the smaller the amplitude, so that even in this way a satisfactory increase in throughput can not be achieved.
Aufgabe der vorliegenden Erfindung ist, ein Antriebsaggregat für einen Linearverdichter mit einem Gestell und einem in dem Gestell über eine Membranfeder gelagerten Schwingkörper zu schaffen, bei dem die Membranfeder ohne Gefahr von Ermüdung einen großen Hub des Schwingkörpers erlaubt, so dass ein hoher Durchsatz bei geringem Kolbendurchmesser erreicht werden kann.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.
Die Aufgabe wird dadurch gelöst, dass zusätzlich zu der Membranfeder eine Schraubenfeder an dem Schwingkörper und dem Gestell befestigt und in Richtung der Bewegung dehn- und stauchbar ist. Dadurch ist es möglich, die Funktionen des Führens des Schwingkörpers und des zeitweiligen Speicherns von dessen Bewegungsenergie aufzuteilen. Die Schraubenfeder ist nur wenig geeignet, den Schwingkörper auf eine exakt definierte geradlinige Bahn zu zwingen, aber es ist nicht schwierig, sie so zu dimensionieren, dass sie sowohl eine gewünschte Bewegungsamplitude als auch eine gewünschte Bewegungsfrequenz des Schwingkörpers ohne Gefahr von Materialermüdung unterstützt. Die Membranfeder darf nur eine geringe Materialstärke aufweisen, um eine gewünschte große Schwingungsamplitude zu erreichen. Eine solche Membranfeder würde, wenn sie allein die Funktion der zeitweiligen Energiespeicherung wahrzunehmen hätte, nur eine niedrige Eigenfrequenz des Schwingkörpers erlauben. Durch Parallelschaltung der zwei Typen von Federn jedoch werden alle drei Anforderungen, die nach einer strengem Führung des Schwingkörpers, nach einer großen Amplitude und einer hohen Schwingfrequenz, gleichzeitig erfüllbar. Idealerweise sollten die Federn lediglich Kräfte, aber keine Drehmomente auf den Schwingkörper ausüben. Zu diesem Zweck ist die Schraubenfeder vorzugsweise um eine imaginäre Gerade herum angeordnet, auf welche der Schwerpunkt des Schwingkörpers hin und her beweglich ist. Vorzugsweise fällt die Gerade mit einer Längsachse der Spiralfeder zusammen.The object is achieved in that in addition to the diaphragm spring, a coil spring attached to the vibrating body and the frame and in the direction of movement is stretchable and compressible. Thereby, it is possible to divide the functions of guiding the vibrating body and temporarily storing its kinetic energy. The coil spring is poorly suited to forcing the vibrating body to a well-defined straight-line path, but it is not difficult to size it to support both a desired amplitude of motion and a desired frequency of movement of the vibrating body without the risk of material fatigue. The diaphragm spring may only have a small material thickness in order to achieve a desired large oscillation amplitude. Such a diaphragm spring, if it alone would have to perform the function of temporary energy storage, would allow only a low natural frequency of the oscillating body. By connecting the two types of springs in parallel, however, all three requirements that can be met simultaneously after a strict guidance of the oscillating body, after a large amplitude and a high oscillation frequency. Ideally, the springs should exert only forces, but no torques on the oscillating body. For this purpose, the helical spring is preferably arranged around an imaginary straight line, on which the center of gravity of the oscillating body is movable to and fro. The straight line preferably coincides with a longitudinal axis of the spiral spring.
Um zu verhindern, dass die Membranfeder ein Drehmoment ausübt, oder um ein solches Drehmoment gering zu halten, hat die Membranfeder vorzugsweise eine Symmetrieachse, die mit der Geraden zusammenfällt, oder eine Symmetrieebene, in welcher die Gerade verläuft.In order to prevent the diaphragm spring from exerting a torque or to minimize such a torque, the diaphragm spring preferably has an axis of symmetry which coincides with the straight line or a plane of symmetry in which the straight line runs.
Um die Kraft der Spiralfeder drehmomentfrei in den Schwingkörper einzuleiten, ist bevorzugt, dass ein Ende der Spiralfeder an der Peripherie eines Federtellers angreift, an dessen Mittelpunkt der Schwingkörper befestigt ist.To initiate the force of the coil spring torque-free in the oscillating body, it is preferred that one end of the coil spring engages the periphery of a spring plate, is attached to the center of the vibrating body.
Um die Membranfeder in der Bewegungsrichtung leicht verformbar zu machen, weist sie vorzugsweise mehrere gekrümmte Arme auf, von denen jeweils ein Ende am Gestell und ein anderes Ende am Schwingkörper fest ist.In order to make the diaphragm spring easily deformable in the direction of movement, it preferably has a plurality of curved arms, one end of which is fixed to the frame and another end to the oscillating body.
Um die Genauigkeit der Führung des Schwingkörpers entlang der Geraden zu verbessern, sind vorzugsweise wenigstens zwei Membranfedern vorgesehen, die an in Richtung der Schwingbewegung beabstandeten Bereichen des Schwingkörpers angreifen.In order to improve the accuracy of the guidance of the oscillating body along the straight line, 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.
Gegenstand der Erfindung ist auch ein Linearverdichter mit einer Arbeitskammer, einem in der Arbeitskammer zum Verdichten eines Arbeitsfluids hin und her beweglichen Kolben und einem Antriebsaggregat wie oben definiert, das zum Antreiben der Hin- und Herbewegung an den Kolben gekoppelt ist. Um einen solchen Linearverdichter kompakt zu machen, kann es zweckmäßig sein, dass die Arbeitskammer wenigstens teilweise von der Schraubenfeder umgeben ist.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. To make such a linear compressor compact, it may be appropriate that the working chamber is at least partially surrounded by the coil spring.
Weitere Merkmale und Vorteile der Erfindung ergeben sich aus der nachfolgenden Beschreibung von Ausführungsbeispielen unter Bezugnahme auf die beigefügten Figuren. Es zeigen: Fig. 1 eine perspektivische Ansicht eines erfindungsgemäßen Linearverdichters;Further features and advantages of the invention will become apparent from the following description of embodiments with reference to the accompanying figures. Show it: Fig. 1 is a perspective view of a linear compressor according to the invention;
Fig. 2 eine der zwei Membranfedern des Linearverdichters aus Fig. 1 ;FIG. 2 shows one of the two diaphragm springs of the linear compressor from FIG. 1; FIG.
Fig. 3 einen schematischen Schnitt durch einen Teil des Linearverdichters entlang einer imaginären Geraden G;3 shows a schematic section through part of the linear compressor along an imaginary straight line G;
Fig. 4 eine alternative Ausgestaltung der Membranfeder des Linearverdichters; und4 shows an alternative embodiment of the diaphragm spring of the linear compressor. and
Fig. 5 eine nochmals vereinfachte Ausgestaltung der Membranfeder.Fig. 5 is a further simplified embodiment of the diaphragm spring.
Ein Gestell 1 des Linearverdichters umfasst eine Grundplatte 2, von der platten- oder rippenartige Vorsprünge 3, 4, 5 abstehen. An den Schmalseiten der zwei einander gegenüberstehenden Vorsprünge 3 sind zwei Membranfedern 6 des in Fig. 2 dargestellten Typs verschraubt. Die Membranfedern 6 umfassen jeweils an den Stirnseiten der Vorsprünge 3 anliegende Stege 7, von deren Enden Z- bzw. S-förmige Federarme 8 abstehen. Die von den Stegen 7 entfernten Enden der Federarme 8 treffen in einem Mittelabschnitt 9 der Membranfeder 6 aufeinander, in welchem drei Öffnungen 10, 11 gebildet sind. Ein Schwingkörper 12 ist zwischen den zwei Membranfedern 6 mit Hilfe von (nicht dargestellten) Schrauben oder Nieten befestigt, die sich durch die oberen und unteren Öffnungen 10 der Membranfedern 6 erstrecken. Die Öffnung 1 1 bildet einen Durchgang für eine Kolbenstange 13, die sich zwischen dem Schwingkörper 12 und einer von dem Vorsprung 5 getragenen Verdichterbaugruppe 14 erstreckt.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, two diaphragm springs 6 of the type shown in Fig. 2 are screwed. 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 1 1 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.
In einem von den Vorsprüngen 3 und den Membranfedern 6 begrenzen Hohlraum sind beiderseits des permanentmagnetischen Schwingkörpers 12 zwei Elektromagnete 15 angeordnet, die bestrombar sind, um zwischen sich einander entgegengesetzte Magnetfelder erzeugen, die den Schwingkörper 12 aus seiner in Fig. 1 gezeigten Gleichgewichtsstellung auf einer durch den Schwerpunkt des Schwingkörpers 12 verlaufenden Geraden G in die eine oder die andere Richtung auszulenken.In a cavity bounded by the projections 3 and the diaphragm springs 6 two electromagnets 15 are arranged on both sides of the permanent magnetic oscillating body, which are energized to generate between them opposing magnetic fields, the oscillating body 12 from its equilibrium position shown in FIG to deflect the center of gravity of the oscillating body 12 extending straight line G in one or the other direction.
Die Gerade G verläuft axial durch die Kolbenstange 13 und die Verdichterbaugruppe 14, und sie ist gleichzeitig die Symmetrieachse von zwei Federtellern 16, die durch Spiralfedern 17 gegen die Außenseiten der zwei Membranfedern 6 gedrückt sind. Fig. 3 zeigt einen Längsschnitt durch einen Teil des linearen Verdichters entlang dieser Geraden G. Die Federteller 16 haben jeweils am Rand ihrer von den Membranfedern 6 abgewandten konkaven Seite eine umlaufende Rippe, die eine an dem Federteller 16 anliegende letzte Windung der Schraubenfeder 17 in radialer Richtung fixiert. Die entgegengesetzten Enden der Schraubenfedern 17 sind jeweils durch ins Innere der Federn eingreifende Vorsprünge fixiert. Einer ist ein flacher Vorsprung 18 an der Platte 4 des Gestells 1 , der andere Vorsprung 19 ist ein Teil des Verdichtergehäuses 14.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 of their side facing away from the diaphragm springs 6 concave side a circumferential rib, which is applied to the spring plate 16 last turn of the coil spring 17 in the radial Direction fixed. 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
Die Schraubenfedern 17 sind jeweils zwischen den Federtellern 16 und den sie tragenden Vorsprüngen 18 oder 19 so vorgespannt, dass an keinem Umkehrpunkt der Bewegung des Schwingkörpers 12 eine der Schraubenfedern 17 spannungslos wird. Die Schraubenfedern 17 halten daher ständig die Federteller 16 gegen die Membranfedern 6 gedrückt, auch wenn der Verdichter in Betrieb ist und der Schwingkörper 12 oszilliert. Es ist daher keine feste Verbindung zwischen den Federtellern 16 und den von ihnen berührten Membranfedern 6 erforderlich, um den Kontakt zwischen ihnen stets aufrecht zu erhalten. Da die Kraft der Federn 17 jeweils über den gesamten Umfang der Federteller 16 recht gleichmäßig verteilt auf die Federteller 16 einwirkt, resultiert allenfalls ein geringes Drehmoment, das eine Verkippung der Achsen der Federteller in Bezug auf die Gerade G bewirken könnte. Doch selbst wenn ein solches Drehmoment aufträte, könnte es mangels einer materialschlüssigen Verbindung zwischen den Federtellern 16 und den Membranfedern 6 nicht auf letztere übertragen werden. Auf Grund der zu den Membranfedern 6 hin verjüngten Form der Federteller 16 leiten diese die Kraft der Schraubenfeder 17 sehr nah an der Linie G in die Membranfedern 6 ein, so dass selbst bei einer ungleichmäßigen Kraftverteilung ein daraus resultierendes, auf die Membranfedern 6 einwirkendes Drehmoment klein bleibt. Die Membranfedern 6 und der von ihnen gehaltene Schwingkörper 12 ist also durch die Schraubenfedern 17 im wesentlichen nur exakt in Richtung der Geraden G orientierten Kräften, aber keinen nennenswerten Drehmomenten ausgesetzt, die eine Bewegung des Schwerpunkts des Schwingkörpers 12 abseits der Linie G anregen könnten.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. But even if such a torque occurred, it could not be transferred to the latter for lack of a material connection between the spring plates 16 and the diaphragm springs 6. Due to the tapered to the diaphragm springs 6 shape of the spring plate 16, these direct the force of the coil spring 17 very close to the line G in the diaphragm springs 6, so that even with an uneven force distribution, a resulting, acting on the diaphragm springs 6 small torque remains. The diaphragm springs 6 and held by them vibrating body 12 is therefore exposed by the coil springs 17 substantially only exactly in the direction of the line G oriented forces, but no significant torques that could stimulate a movement of the center of gravity of the vibrating body 12 off the line G.
Auch die hochgradige Symmetrie der zwei Membranfedern 6 trägt dazu bei, dass diese den Schwingkörper 12 exakt linear führen. Der Schnitt der Fig. 3 zeigt auch den inneren Aufbau der Verdichterbaugruppe 14. In einer internen Kammer 20 der Verdichterbaugruppe 14 ist ein von der Kolbenstange 13 gehaltener Kolben 21 hin und her verschiebbar, um über einen Saugstutzen 22 Kältemittel in die Kammer 20 zu saugen und das verdichtete Kältemittel an einem Druckstutzen 23 wieder auszugeben. Mit dem Druckstutzen 23 kommuniziert ein Ringraum 24, der sich becherförmig um die Kammer 20 erstreckt. In der von den Flanken des Kolbens 21 überstrichenen Trennwand 25 zwischen der Kammer 20 und dem Ringraum 24 ist eine Vielzahl von feinen Durchgängen 26 gebildet, durch die ein Teil des verdichteten Kältemittels aus dem Ringraum 24 zurück in die Kammer 20 strömen kann. Das rückströmende Kältemittel bildet zwischen der Trennwand 25 und den Flanken des Kolbens 21 ein Gaskissen, welches im Betrieb einen direkten schleifenden Kontakt zwischen Kolben 21 und Trennwand 25 verhindert und so den Verschleiß der Verdichterbaugruppe 14 gering hält. Auf Grund der exakt geradlinigen Führung des Schwingkörpers 12, die durch die Aufhängung mit Membran- und Schraubenfedern 6, 17 erreicht wird, genügt ein geringer Gasdurchsatz in den Durchgängen 26, um ein wirksam vor Schleifen schützendes Gaskissen zu schaffen.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 section of Fig. 3 also shows the internal structure of the compressor assembly 14. In an internal chamber 20 of the compressor assembly 14, a held by the piston rod 13 piston 21 back and forth to suck via a suction port 22 refrigerant into the chamber 20 and to spend the compressed refrigerant at a pressure port 23 again. With the discharge nozzle 23 communicates an annular space 24 which extends cup-shaped around the chamber 20. In the swept by the flanks of the piston 21 dividing wall 25 between the chamber 20 and the annular space 24 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 low gas flow in the passages 26 is sufficient to create a effective against loops protective gas cushion.
Um geringfügige Ungenauigkeiten bei der Ausrichtung des Antriebsaggregats und der Verdichterbaugruppe zueinander zu kompensieren, die anderenfalls auch zum Reiben des Kolbens 21 an der Wand 25 führen könnten, sind in der Kolbenstange 13 zwei elastisch biegsame Schwachstellen 27 gebildet. Eine leichte Verbiegung dieser Schwachstellen 27 erlaubt es, einen kleinen Versatz zwischen der Geraden G, auf der sich der Schwerpunkt des Schwingkörpers 12 bewegt, und der Längsmittelachse der Kammer 20 oder auch eine geringfügige Nichtparallelität beider zu kompensieren.To compensate for minor inaccuracies in the alignment of the drive unit and the compressor assembly to each other, which could otherwise lead to rubbing of the piston 21 on the wall 25, 13 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.
Vereinfachte Ausgestaltungen der Membranfeder sind in Fig. 4 und 5 gezeigt. Die Feder 6' der Fig. 4 entspricht im Wesentlichen einer halbierten Membranfeder aus Fig. 3, mit nur zwei S- bzw. Z-förmig gekrümmten Armen 8, die sich von einem Steg 7 zum Mittelabschnitt 9 erstrecken. Bei der Feder 6" der Fig. 5 sind die gekrümmten Arme durch einen geradlinigen Arm 8" ersetzt. Dessen freies Ende bewegt sich zwar genau genommen nicht exakt auf einer Geraden, sondern auf einem Kreisbogen, doch ist diese Abweichung vernachlässigbar, wenn die Amplitude des Schwingkörpers so begrenzt ist, dass die Seitwärtskomponente der Bewegung des Schwingkörpers kleiner als das seitliche Spiel des Kolbens ist. Simplified embodiments of the diaphragm spring are shown in FIGS. 4 and 5. The spring 6 'of Fig. 4 substantially corresponds to a halved diaphragm spring of Fig. 3, with only two S- or Z-shaped curved arms 8, which extend from a web 7 to the central portion 9. In the spring 6 "of Fig. 5, the curved arms are replaced by a straight arm 8". Although its free end, strictly speaking, does not move exactly on a straight line, but on a circular arc, 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.

Claims

Patentansprüche claims
1. Antriebsaggregat für einen Linearverdichter mit einem Gestell (1 ) und einem durch wenigstens eine Membranfeder (6) mit dem Gestell (1 ) verbundenen und in Bezug auf das Gestell geradlinig hin und her beweglich geführten Schwingkörper(12), dadurch gekennzeichnet, dass eine Schraubenfeder (17) an dem Schwingkörper (12) und dem Gestell angreift und in Richtung der Bewegung dehn- und stauchbar ist.1. Drive unit for a linear compressor with a frame (1) and a by at least one diaphragm spring (6) connected to the frame (1) and in relation to the frame rectilinear back and forth guided oscillating body (12), characterized in that a Coil spring (17) on the vibrating body (12) and the frame attacks and is stretchable and compressible in the direction of movement.
2. Antriebsaggregat nach Anspruch 1 , dadurch gekennzeichnet, dass die Schraubenfeder (17) sich um eine Gerade G herum erstreckt, auf weicher der Schwerpunkt des Schwingkörpers (12) hin und her beweglich ist.2. Drive unit according to claim 1, characterized in that the helical spring (17) extends around a straight line G around, on which the center of gravity of the oscillating body (12) is movable to and fro.
3. Antriebsaggregat nach Anspruch 2, dadurch gekennzeichnet, dass die Gerade (G) mit einer Längsachse der Spiralfeder (17) zusammenfällt.3. Drive unit according to claim 2, characterized in that the straight line (G) coincides with a longitudinal axis of the spiral spring (17).
4. Antriebsaggregat nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Gerade (G) eine Symmetrieachse oder Teil einer Symmetrieebene der Membranfeder (6) ist.4. Drive unit according to claim 2 or 3, characterized in that the straight line (G) is an axis of symmetry or part of a plane of symmetry of the diaphragm spring (6).
5. Antriebsaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein Ende der Spiralfeder (17) an der Peripherie eines Federtellers (16) angreift, dessen Mittelpunkt gegen den Schwingkörper (12) drückt.5. Drive unit according to one of the preceding claims, characterized in that one end of the spiral spring (17) acts on the periphery of a spring plate (16), the center of which presses against the oscillating body (12).
6. Antriebsaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membranfeder (6) mehrere gekrümmte Arme (8) umfasst, von denen jeweils ein Ende am Gestell (1 ) und ein anderes Ende (9) am Schwingkörper (12) fest ist.6. Drive unit according to one of the preceding claims, characterized in that the diaphragm spring (6) comprises a plurality of curved arms (8), of which one end of the frame (1) and another end (9) on the oscillating body (12) is fixed ,
7. Antriebsaggregat nach Anspruch 6, dadurch gekennzeichnet, dass jeder Arm (8) zwei in unterschiedliche Richtungen gekrümmte Abschnitte aufweist. 7. Drive unit according to claim 6, characterized in that each arm (8) has two sections curved in different directions.
8. Antriebsaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es wenigstens eine zweite Membranfeder (6) umfasst, und dass die erste und die zweite Membranfeder (6) an in Richtung der Schwingbewegung beabstandeten Bereichen des Schwingkörpers (12) angreifen.8. Drive unit according to one of the preceding claims, characterized in that it comprises at least one second diaphragm spring (6), and in that the first and the second diaphragm spring (6) engage in the direction of the oscillating movement spaced areas of the oscillating body (12).
9. Linearverdichter mit einer Arbeitskammer (20), einem in der Arbeitskammer (20) zum Verdichten eines Arbeitsfluids hin und her beweglichen Kolben (21 ) und einem zum Antreiben der Hin- und Herbewegung an den Kolben (21 ) gekoppelten Antriebsaggregat nach einem der vorhergehenden Ansprüche.9. A linear compressor having a working chamber (20), in the working chamber (20) for compressing a working fluid reciprocally movable piston (21) and for driving the reciprocating motion to the piston (21) coupled to the drive unit according to one of the preceding Claims.
10. Linearverdichter nach Anspruch 9, dadurch gekennzeichnet, dass eine Kolbenstange (13) sich zwischen dem Kolben (21 ) und dem Schwingkörper (12) auf der Geraden (G) erstreckt.10. A linear compressor according to claim 9, characterized in that a piston rod (13) extends between the piston (21) and the oscillating body (12) on the straight line (G).
1 1. Linearverdichter nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass die Arbeitskammer (20) wenigstens teilweise von der Schraubenfeder (17) umgeben ist. 1 1. A linear compressor according to claim 9 or 10, characterized in that the working chamber (20) is at least partially surrounded by the coil spring (17).
EP07703714.1A 2006-02-28 2007-01-09 Linear compressor and drive unit therefor Not-in-force EP1991777B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07703714T PL1991777T3 (en) 2006-02-28 2007-01-09 Linear compressor and drive unit therefor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006009232A DE102006009232A1 (en) 2006-02-28 2006-02-28 Power supply unit for linear compressor in cooling equipment has coil spring that is expandable and compressible, and which is biased against swinging body
PCT/EP2007/050163 WO2007098970A1 (en) 2006-02-28 2007-01-09 Linear compressor and drive unit therefor

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EP1991777A1 true EP1991777A1 (en) 2008-11-19
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US (1) US20090129955A1 (en)
EP (1) EP1991777B1 (en)
CN (1) CN101389861A (en)
DE (1) DE102006009232A1 (en)
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WO (1) WO2007098970A1 (en)

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 (en) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH linear compressor
CA2872297C (en) 2006-09-28 2016-10-11 Smith & Nephew, Inc. Portable wound therapy system
DE102007055166A1 (en) 2007-11-19 2009-05-20 BSH Bosch und Siemens Hausgeräte GmbH Linear compressor and drive unit for it
DE102007060831A1 (en) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Control unit for a refrigerating machine and household refrigerating appliance using the same
DE102007060824A1 (en) 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Linear compressor for refrigerator, has set of diaphragm springs engaging at longitudinally spaced areas of armature, where one of diaphragm springs is unconnected with one of stand parts and other diaphragm spring is attached at stand part
DE102009047743A1 (en) * 2009-12-09 2011-06-16 BSH Bosch und Siemens Hausgeräte GmbH Compressor with a carrying frame
DE102009047744A1 (en) * 2009-12-09 2011-06-16 BSH Bosch und Siemens Hausgeräte GmbH Compressor with a pumping chamber
GB201015656D0 (en) 2010-09-20 2010-10-27 Smith & Nephew Pressure control apparatus
DE102010062731A1 (en) 2010-12-09 2012-06-14 BSH Bosch und Siemens Hausgeräte GmbH Cooling appliance e.g. refrigerator used in e.g. household, comprises linear compressor including a rotor, and centering device for carrying out radial centering of rotor by magnetic field
US9709047B2 (en) * 2011-05-06 2017-07-18 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
BRPI1103647A2 (en) * 2011-07-07 2013-07-02 Whirlpool Sa arrangement between linear compressor components
BRPI1103447A2 (en) * 2011-07-19 2013-07-09 Whirlpool Sa spring bundle for compressor and spring bundled compressor
BRPI1104172A2 (en) 2011-08-31 2015-10-13 Whirlpool Sa 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
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 (en) * 2012-10-17 2015-02-24 엘지전자 주식회사 Reciprocating compressor
US9841012B2 (en) * 2014-02-10 2017-12-12 Haier Us Appliance Solutions, Inc. Linear compressor
IN2014CH00632A (en) * 2014-02-11 2015-08-14 Gen Electric
WO2016103032A1 (en) 2014-12-22 2016-06-30 Smith & Nephew Plc Negative pressure wound therapy apparatus and methods
US10492711B2 (en) * 2015-05-31 2019-12-03 Michael W. Wolfe Handheld portable impulse oscillometer
CN108217203A (en) * 2017-05-08 2018-06-29 长沙莜芸科技有限公司 A kind of flexible proportioning device

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (en) * 1996-01-16 1999-10-15 윤종용 Linear compressorr
CN1083939C (en) * 1996-07-09 2002-05-01 三洋电机株式会社 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
KR100480086B1 (en) * 1998-01-12 2005-06-08 엘지전자 주식회사 Suction loss reduction structure of linear compressor
JP3083518B2 (en) * 1998-07-03 2000-09-04 三星電子株式会社 Structure and connection method of inner core and cylinder block of linear compressor
JP2001227461A (en) * 2000-02-14 2001-08-24 Matsushita Electric Ind Co Ltd Linear compressor
US7078832B2 (en) * 2002-10-16 2006-07-18 Matsushita Refrigeration Company Linear motor, and linear compressor using the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007098970A1 *

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PL1991777T3 (en) 2015-08-31
RU2429376C2 (en) 2011-09-20
WO2007098970A1 (en) 2007-09-07
DE102006009232A1 (en) 2007-08-30
RU2008135043A (en) 2010-04-10
US20090129955A1 (en) 2009-05-21
CN101389861A (en) 2009-03-18
EP1991777B1 (en) 2015-03-18

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