EP2212556B1 - Compresseur linéaire et groupe d'entraînement pour celui-ci - Google Patents

Compresseur linéaire et groupe d'entraînement pour celui-ci Download PDF

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Publication number
EP2212556B1
EP2212556B1 EP08852620A EP08852620A EP2212556B1 EP 2212556 B1 EP2212556 B1 EP 2212556B1 EP 08852620 A EP08852620 A EP 08852620A EP 08852620 A EP08852620 A EP 08852620A EP 2212556 B1 EP2212556 B1 EP 2212556B1
Authority
EP
European Patent Office
Prior art keywords
drive unit
unit according
diaphragm spring
spring
diaphragm
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.)
Not-in-force
Application number
EP08852620A
Other languages
German (de)
English (en)
Other versions
EP2212556A1 (fr
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
Publication of EP2212556A1 publication Critical patent/EP2212556A1/fr
Application granted granted Critical
Publication of EP2212556B1 publication Critical patent/EP2212556B1/fr
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.
  • Out DE 10 2004 062 301 A1 is a drive unit for a linear compressor with a frame, a known in the frame via at least one diaphragm spring, reciprocally movable oscillating body and at least one parallel to the movement acting auxiliary spring known.
  • the diaphragm spring of this known drive unit comprises four arms which are integrally connected to one another on the oscillating body and extend in each case zigzag outwards from the oscillating body to attachment points on the frame. Since the arms of the diaphragm spring are easier to deform in the direction of movement of the oscillating body than transversely thereto, they ensure a precise guidance of the oscillating body, without requiring additional guide parts.
  • the diaphragm spring 50 When the linear compressor is in operation, the diaphragm spring 50 experiences load changes per second, corresponding to the frequency of the AC voltage with which the compressor is operated.
  • the material of the leaf spring In order to achieve a life of the linear compressor of many years, corresponding to the life expectancy of the rotary-driven compressors introduced on the market, the material of the leaf spring has to withstand many millions of load changes without significant damage or fatigue. This goal is difficult to achieve with the currently known forms of diaphragm springs.
  • the publication DE 10 2006 009 232 A1 shows a generic drive unit of a linear compressor according to the preamble of claim 1 comprising a frame and connected by at least one diaphragm spring to the frame and in relation to the frame rectilinear reciprocating guided oscillating body.
  • a helical spring acts on the oscillating body and the frame and is stretchable and compressible in the direction of movement.
  • Object of the present invention is therefore to provide a drive unit for a linear compressor, which works reliably for a long time with high probability.
  • the bending moments occurring in the leaf spring in the deflected state are distributed unevenly over the length of the leaf spring: they are greatest at the attachment points, i. where the lever arm of each other attachment point is greatest, and minimally in the middle, where opposite torques of the two attachment points compensate each other.
  • the attachment points are conveniently located at two opposite ends of the elongated diaphragm spring.
  • the diaphragm spring preferably has a constant thickness and in the middle region a smaller width than at the fastening points.
  • the membrane can be made in a simple manner from flat material of constant thickness, in particular punched out of spring plate.
  • the diaphragm spring should be free of openings.
  • the cross section of the diaphragm spring expediently varies continuously in the longitudinal direction of the diaphragm spring. It is particularly advantageous if the change in cross section beyond that in the longitudinal direction is continuously differentiable.
  • the diaphragm spring should be free of openings. Namely, if an opening tapers toward one of the attachment points, the forces acting in the spring tend to concentrate at the tip, so that in the course of operation material damage preferably occurs in the vicinity of such a tip. If, on the other hand, a wall of the opening facing the attachment point is rounded off, the change in the cross-sectional area of the diaphragm spring is inevitably discontinuous, and a uniform distribution of the deformation stress on the spring can not be achieved.
  • the requirement for a continuous change of the cross section in the longitudinal direction of the spring is equivalent to a continuous or stepless course of the longitudinal edges of the spring, and a continuously differentiable cross section corresponds to a bend-free course of the longitudinal edges.
  • the above requirements are easy to fulfill because the diaphragm spring has at least one concave edge.
  • the curvature of the deflected diaphragm spring should change its sign across its middle section. In the middle section then necessarily exists an undeformed site.
  • a shape of the deformable region of the diaphragm spring has proven to be particularly resistant, comprising in longitudinal section two mutually inversion-symmetrical arcs, in particular parabolic arcs.
  • a curve function that describes the edge profile of such a diaphragm spring can not be specified in analytical form, but a specialist can make a prototype of such a diaphragm spring without inventive effort by starting from a diaphragm spring of any shape whose longitudinal section detected in the deflected state and from Places whose curvature is smaller than desired, abrading material.
  • an arc shape can be realized whose curvature increases linearly from a clamped edge region up to a local maximum, from there it decreases linearly to a local minimum while the sign changes, and from there rises again to zero.
  • the material of the diaphragm spring should be as thin as possible and thus easily flexible.
  • a slightly flexible diaphragm spring has a low resonance frequency.
  • the resonant frequency is in turn proportional to the capacity of a linear compressor in which the drive unit is used. Therefore, a high resonance frequency is desired from the viewpoint of the capacity.
  • at least one parallel to the movement of the oscillating body acting auxiliary spring is provided.
  • the stiffness of the diaphragm spring parallel to the movement is preferably smaller than that of the auxiliary spring.
  • the time sequence and in particular the period of the oscillatory movement is essentially determined by the auxiliary spring, while the diaphragm spring essentially determines the path of the oscillating body during the oscillating movement.
  • the auxiliary spring may conveniently be a coil spring.
  • the center of gravity of the oscillating body (5) is then preferably movable along the longitudinal axis of the helical spring.
  • the drive unit comprises two auxiliary springs, which are connected to each other at two first ends and to the oscillating body and extend in opposite directions in the direction of movement.
  • auxiliary springs which are connected to each other at two first ends and to the oscillating body and extend in opposite directions in the direction of movement.
  • Such a linear compressor preferably has a compressor chamber coupled to the oscillating body by a piston rod. Since the suspension of the oscillating body on the leaf spring, the oscillating body on a slightly 'curved path leads, but the compression chamber requires a precisely linear drive movement, a transverse component of the movement of the oscillating body can be compensated by means of the piston rod.
  • the piston rod is surrounded by the at least one auxiliary spring.
  • auxiliary springs In order to introduce the force of the auxiliary springs in the oscillating body, preferably carries the piston rod a flange, press against the two auxiliary springs from opposite directions.
  • the in Fig. 1 shown linear compressor has a frame 1 with a base plate on which two E-shaped soft iron cores 2 are mounted mirror-symmetrically opposite each other. Of the three mutually facing legs 3 of the soft iron cores 2 each of the middle is hidden by a magnetic coil 4, by the winding it extends.
  • the Membrane springs 6, 7 made of spring steel in each case substantially the shape of a rectangle waisted by recesses along its longitudinal sides.
  • a plurality of mounting holes 8 are formed, which serve for anchoring the diaphragm spring 6, 7 on an end face of the oscillating body 5 or on an edge of a projecting from the base plate side wall 9 of the frame 1 by means of screws, rivets or the like , which pass through the mounting holes 8 and openings of clamping plates 14.
  • the clamping plates 14 are in Fig. 1 shown transparent to leave the mounting holes 8 visible.
  • the edge portions of the diaphragm spring 6 are, by being clamped between the clamping plates 14 and the end face of the oscillating body 5 and the edge of the side wall 9, protected from any deformation.
  • the deformable surface of the diaphragm spring 6 lying between the attachment points is free of openings of any kind.
  • a piston rod 11 which connects the vibrating body 5 with a reciprocating in a pumping chamber 12, not shown piston extends.
  • the holes 8 are each on two parallel, in Fig. 2 dash-dotted lines drawn.
  • a control circuit applied to the magnetic coils 4 with an alternating current of controlled frequency and amplitude, to generate between each of the middle and the two outer legs 3 magnetic fields with alternating orientation.
  • the vibrating body 5 includes a permanent magnet which is subjected to an oscillating force by the magnetic field thus generated and drives a swinging motion of the vibrating body 5.
  • the two diaphragm springs 6, 7 guide the vibrating body 5 on a slightly curved path, wherein movement of the vibrating body 5 transversely to the direction of movement of the piston in the pumping chamber 12 is absorbed by a corresponding oscillating movement of the piston rod 11 and is not transmitted to the piston.
  • the path on which the oscillating body 5 moves is exactly defined by the diaphragm springs 6, 7.
  • the capacity of the compressor is proportional to the resonant frequency of the oscillating body 5.
  • To stiffen the oscillatory system in the direction of movement of the piston are two coil springs 16, 17, each attacking on opposite sides of a projecting from the piston rod 11 flange 18 and of which the one 16 at a movement of the diaphragm spring 6 limiting intermediate edge 19 of the frame 1 and the other 17 is supported on the pumping chamber 12.
  • the coil springs 16, 17 are exactly centered on the piston rod 11 by means of flat circular disks 20 and a ring 21, and by a truncated cone 22, of the flange 18 on its two sides, of the intermediate wall 19 and of the pumping chamber 12 from into the interior of the coil springs 16, 17 engage. Due to the centering is excluded that the coil springs 16, 17 except a desired force in the direction of the piston rod 11 and a torque on the oscillating system of oscillating body 5, piston rod 11 and piston exert.
  • Fig. 2 shows a plan view of one of the two identical spring plates 6.7. Between the clamped edge portions of the deformable main portion extends with continuous, inwardly curved longitudinal edges 15. The course of the longitudinal edges is chosen so that when the spring plate 6 and 7 is deflected, a longitudinal section with the in Fig. 3
  • the major portion has two oppositely curved halves 23, 24.
  • the curvature is zero at each edge of each half 23, 24, ie at a center line 25, at which the halves 23, 24 adjoin one another, and where Pass the halves into the clamped edge sections.
  • the center line 25 is also the point at which the width of the diaphragm spring 26 is minimal. From each edge, the curvature increases linearly toward the center of the respective half 23, 24, ie the points 26 of maximum curvature are each located in a distance corresponding to a quarter of the length of the main section from its center 25 or its edges.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (21)

  1. Groupe d'entraînement pour un compresseur linéaire comprenant un bâti (1, 9), un corps oscillant (5) et un ressort à diaphragme (6, 7) fixé en un premier point de fixation sur le bâti (1) et en un second point de fixation sur le corps oscillant (5), de manière à assurer un mouvement de va-et-vient du corps oscillant (5) sur le bâti (1, 9), caractérisé en ce que le ressort à diaphragme (6, 7) présente dans une zone (25) située entre les deux points de fixation, une surface de section inférieure à celle aux points de fixation, une section du ressort à diaphragme (6, 7) variant continûment dans le sens longitudinal du ressort à diaphragme (6, 7).
  2. Groupe d'entraînement selon la revendication 1, caractérisé en ce que la zone (25) est située au moins approximativement au centre entre le premier et le second point de fixation.
  3. Groupe d'entraînement selon la revendication 1 ou 2, caractérisé en ce que les points de fixation se trouvent à deux extrémités opposées du ressort à diaphragme allongé (6, 7).
  4. Groupe d'entraînement selon l'une des revendications 1 à 3, caractérisé en ce que le ressort à diaphragme (6, 7) présente une épaisseur de matière constante, et dans la zone centrale (25) une largeur inférieure à celle aux points de fixation.
  5. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé en ce que la section varie continûment dans le sens longitudinal du ressort à diaphragme (6, 7).
  6. Groupe d'entraînement selon la revendication 5, caractérisé en ce que la section est différenciable continûment dans le sens longitudinal du ressort à diaphragme (6, 7).
  7. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé en ce qu'une zone déformable (23, 24) du ressort à diaphragme (6, 7) est dépourvue d'ouvertures.
  8. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé en ce que le ressort à diaphragme (6, 7) présente un bord concave (15) au moins sur l'un de ses côtés longs.
  9. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé en ce que la courbure du ressort à diaphragme (6, 7) change de signe au-delà de la zone centrale (25) de celui-ci.
  10. Groupe d'entraînement selon la revendication 9, caractérisé en ce que le ressort à diaphragme écarté (6, 7) comprend en coupe longitudinale deux arcs (23, 24) de symétrie inverse l'un par rapport à l'autre.
  11. Groupe d'entraînement selon la revendication 10, caractérisé en ce que les arcs (23, 24) sont paraboliques.
  12. Groupe d'entraînement selon la revendication 10, caractérisé en ce que la courbure varie linéairement sur la longueur des arcs (23, 24).
  13. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé en ce qu'il comprend au moins un deuxième ressort à diaphragme (7, 6), et en ce que le premier et le deuxième ressort à diaphragme (6, 7) viennent en prise dans des régions espacées dans le sens du mouvement oscillant du corps oscillant (5).
  14. Groupe d'entraînement selon l'une des revendications précédentes, caractérisé par au moins un ressort auxiliaire (16, 17) agissant parallèlement au mouvement du corps oscillant (5).
  15. Groupe d'entraînement selon la revendication 17, caractérisé en ce que la raideur du ressort à diaphragme (6, 7) parallèlement audit mouvement est inférieure à celle du ressort auxiliaire (16, 17).
  16. Groupe d'entraînement selon la revendication 14 ou 15, caractérisé en ce que le ressort auxiliaire (16, 17) est un ressort hélicoïdal, et en ce que le centre de gravité du corps oscillant (5) est mobile le long de l'axe longitudinal du ressort hélicoïdal (16, 17).
  17. Groupe d'entraînement selon l'une des revendications 14 à 16, caractérisé en ce qu'il comprend deux ressorts auxiliaires (16, 17) qui sont reliés entre eux et au corps oscillant (5) à deux premières extrémités et s'étendent en sens contraire par rapport au sens du mouvement.
  18. Compresseur linéaire comprenant un piston guidé de manière mobile dans une chambre de compresseur (12) et relié au corps oscillant (5) par une tige de piston (11), caractérisé par un groupe d'entraînement selon l'une des revendications précédentes.
  19. Compresseur linéaire selon la revendication 18, caractérisé en ce que la tige de piston (11) est entouré au moins par portions dudit au moins un ressort auxiliaire (16, 17).
  20. Compresseur linéaire selon la revendication 18 ou 19, caractérisé en ce que la tige de piston (11) porte une bride (18) contre laquelle se serrent deux ressorts auxiliaires (16, 17) venant de directions opposées.
  21. Appareil frigorifique comprenant un compresseur linéaire selon l'une des revendications 18 à 20.
EP08852620A 2007-11-19 2008-10-21 Compresseur linéaire et groupe d'entraînement pour celui-ci Not-in-force EP2212556B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007055166A DE102007055166A1 (de) 2007-11-19 2007-11-19 Linearverdichter und Antriebsaggregat dafür
PCT/EP2008/064194 WO2009065684A1 (fr) 2007-11-19 2008-10-21 Compresseur linéaire et groupe d'entraînement pour celui-ci

Publications (2)

Publication Number Publication Date
EP2212556A1 EP2212556A1 (fr) 2010-08-04
EP2212556B1 true EP2212556B1 (fr) 2012-02-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08852620A Not-in-force EP2212556B1 (fr) 2007-11-19 2008-10-21 Compresseur linéaire et groupe d'entraînement pour celui-ci

Country Status (5)

Country Link
EP (1) EP2212556B1 (fr)
AT (1) ATE547628T1 (fr)
DE (1) DE102007055166A1 (fr)
ES (1) ES2380647T3 (fr)
WO (1) WO2009065684A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009047743A1 (de) * 2009-12-09 2011-06-16 BSH Bosch und Siemens Hausgeräte GmbH Verdichter mit einem Tragegestell

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6056519A (en) * 1997-10-15 2000-05-02 Matsushita Refrigeration Company Structure of vibrating compressor
DE102004062307A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
DE102004062301A1 (de) 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür
DE102006009232A1 (de) 2006-02-28 2007-08-30 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter und Antriebsaggregat dafür

Also Published As

Publication number Publication date
WO2009065684A1 (fr) 2009-05-28
DE102007055166A1 (de) 2009-05-20
ES2380647T3 (es) 2012-05-17
ATE547628T1 (de) 2012-03-15
EP2212556A1 (fr) 2010-08-04

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