CN1488856A - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
CN1488856A
CN1488856A CNA031560067A CN03156006A CN1488856A CN 1488856 A CN1488856 A CN 1488856A CN A031560067 A CNA031560067 A CN A031560067A CN 03156006 A CN03156006 A CN 03156006A CN 1488856 A CN1488856 A CN 1488856A
Authority
CN
China
Prior art keywords
aforementioned
pedestal
disc spring
linearkompressor
disc
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
CNA031560067A
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Chinese (zh)
Other versions
CN100371591C (en
Inventor
寺床圭一郎
苅谷良一
赤泽辉行
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.)
SHINQUE CO Ltd
Panasonic Holdings Corp
Original Assignee
SHINQUE CO Ltd
Matsushita Electric Industrial Co Ltd
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 SHINQUE CO Ltd, Matsushita Electric Industrial Co Ltd filed Critical SHINQUE CO Ltd
Publication of CN1488856A publication Critical patent/CN1488856A/en
Application granted granted Critical
Publication of CN100371591C publication Critical patent/CN100371591C/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00Piston 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
    • F04B35/04Piston 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027Pulsation and noise damping means
    • F04B39/0044Pulsation and noise damping means with vibration damping supports
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10Adaptations or arrangements of distribution members

Abstract

A first and a second coil springs are disposed on one side and the other side respectively with a setting interlocking with a piston put between them. The first and second coil springs are different from each other in the winding direction.

Description

Linearkompressor
Technical field
The present invention relates to a kind of Linearkompressor, this Linearkompressor utilizes linear motor that the piston that can be configured in the cylinder central hole to free to-and-fro motion in the mode that forms pressing chamber is moved reciprocatingly, and carries out suction, compression, the discharge of fluid thus.
Background technique
Known in the past Linearkompressor possesses: have the cylinder body of the tube portion that is formed with central hole, can be inserted into piston in the central hole of this cylinder and the linear motor that makes this reciprocating motion of the pistons in the mode that marks off pressing chamber with in axial direction being free to slide, suck, compress, discharge fluid by making reciprocating motion of the pistons.
Linearkompressor in the past further possesses: with the pedestal of aforementioned piston interlock, clip this pedestal and be configured in a side of axial direction and first and second disc springs on the opposite side along same axis ground respectively.
In order to make the movable part that is made of piston and pedestal etc. do resonance motion, aforementioned first and second disc springs are constituted as pedestal are loaded to first direction that makes aforementioned pressing chamber compression and the second direction that makes it to expand.That is, when aforementioned piston to the first direction that makes the compression of this pressing chamber during toward moving finishing, except produce by linear motor to the Driving force of second direction, also utilize the loading force of compressed second disc spring to make this piston do double action to second direction.And, when making aforementioned piston to the second direction that makes the expansion of this pressing chamber during toward moving finishing, except produce by linear motor to the Driving force of first direction, also utilize the loading force of compressed first disc spring to make this piston do double action to first direction.
Like this, aforementioned first and second disc springs are used to provide the axial Driving force when making piston to-and-fro motion in axial direction to be configured.
That is, the Driving force that applies to piston from first and second disc springs is preferably as much as possible along axial direction, but do not take into full account this point in existing Linearkompressor.
Summary of the invention
The present invention is in view of the situation of aforementioned prior art, and the one purpose is, provides a kind of loading force of applying to piston from first and second disc springs of can making as far as possible along the Linearkompressor of axial direction.
The present invention provides a kind of Linearkompressor in order to realize aforementioned purpose, and this compressor possesses: the cylinder body with the tube portion that is formed with central hole; Can be inserted into the piston in the central hole of this cylinder body in the mode that marks off pressing chamber with in axial direction being free to slide; Pedestal with this piston interlock; Clip this pedestal be configured in a side of axial direction and opposite side respectively along same axis ground, along the first direction that makes aforementioned pressing chamber compression and first and second disc springs that the second direction of aforementioned pressing chamber expansion is loaded this pedestal; And make aforementioned pedestal to first direction and the reciprocating linear motor of second direction; Aforementioned first and second disc springs are formed in the state that can produce loading force separately when aforementioned linear motor is not worked, and the coiling direction of this first and second disc spring is different.
In addition, the present invention provides a kind of Linearkompressor in order to realize aforementioned purpose, and this Linearkompressor possesses: the cylinder body with the tube portion that is formed with central hole; Can be inserted into the piston in the central hole of this cylinder body in the mode that marks off pressing chamber with in axial direction being free to slide; Pedestal with this piston interlock; Clip this pedestal be configured in a side of axial direction and opposite side respectively along same axis ground, along the first direction that makes aforementioned pressing chamber compression and first and second disc springs that the second direction of aforementioned pressing chamber expansion is loaded this pedestal; And make aforementioned pedestal to first direction and the reciprocating linear motor of second direction; Aforementioned first and second disc springs are formed in the state that can produce its loading force separately when aforementioned linear motor is not worked, the coiling direction of this first and second disc spring is identical, this first and second disc spring, the end that clips the mutual subtend of aforementioned pedestal are configured in-58 °~+ 125 ° scope around the axis.
Preferably, at least one end in aforementioned first and second disc springs is extrapolated on the taper protuberance that is arranged on the parts that support this at least one end.The cardinal extremity diameter of this taper protuberance is bigger than the internal diameter of the disc spring of institute extrapolation, and its top end diameter is littler than the internal diameter of this disc spring.
Preferably, at least one end of aforementioned first and second disc springs, in be inserted in the tapered recess that is arranged on the parts that support this at least one end.The cardinal extremity diameter of this tapered recess is littler than the external diameter of the disc spring of institute interpolation, and its top end diameter is bigger than the external diameter of this disc spring.
More preferably, aforementioned first or the installing and locating circle face of at least one end of second disc spring, on the parts that a plurality of pins can not be connected to the relative rotation with this installing and locating circle face contacts via configuration around axis.
The simple declaration of accompanying drawing
Fig. 1 is the schematic sectional view of the Linearkompressor of a form of implementation of the present invention.
Fig. 2 is the schematic sectional view of the experimental setup of simulation Linearkompressor shown in Figure 1.
Fig. 3 is the plotted curve of the expression experimental result of carrying out with experimental setup shown in Figure 2, represents the relation at terminal position and pedestal angle of inclination.
Fig. 4 is to be the analytical model figure of the finite element method of model with Linearkompressor shown in Figure 1.
Fig. 5 is expression by the plotted curve that is the analysis result that obtains according to finite element method of model, the relation of expression terminal position and piston sidepiece load (transverse force) with Linearkompressor shown in Figure 1.
Fig. 6 be expression to Linearkompressor shown in Figure 1, with the identical Linearkompressor of the first and second disc spring coiling directions be model, according to the plotted curve of the analysis result that finite element method was obtained, represent the deflection in each terminal position and the relation of piston sidepiece load (transverse force).
Fig. 7 (a) reaches (b) schematic sectional view of the Linearkompressor of expression another embodiment of the present invention.
Label declaration
1 Linearkompressor, 10 cylinder bodies
11 11a of portion central holes
20 pistons, 30 pedestals
40 first disc springs, 50 second disc springs
60 linear motors
The working of an invention form
Form of implementation 1.
Below, describe with reference to the Linearkompressor of accompanying drawing form of implementation 1 of the present invention.
Fig. 1 is the schematic sectional view of the Linearkompressor 1 of the invention process form.
As shown in Figure 1, the Linearkompressor 1 of this form of implementation possesses: the cylinder body 10 with the tube portion 11 that is formed with central hole 11a; Can be inserted into the piston 20 in the central hole 11a of this cylinder body 10 in the mode that marks off pressing chamber P with in axial direction being free to slide; Pedestal 30 with these piston 20 interlocks; Clip this pedestal 30 and be configured in a side of axial direction and first and second disc springs 40,50 of opposite side along same axis ground respectively; And make aforementioned pedestal 30 reciprocating linear motors 60.
Aforementioned cylinder body 10 except aforementioned tube portion 11, also is furnished with the lip part 12 that extends to the radial outside direction from this one 11.
In addition, on another face (right flank among Fig. 1) of the axial direction of this cylinder body 10, be fixed with by the end cap portions (diagram is omitted) that covers the aforementioned pressing chamber P that central hole 11a and aforementioned piston 20 marked off.On this end cap portions, be furnished with the suction valve that makes fluid pass in and out aforementioned pressing chamber P and expulsion valve etc.
Aforementioned linear motor 60 possesses: can not be fixed in the fixing part 61 on the aforementioned cylinder body 10 with relatively moving, and for make aforementioned piston 20 with respect to aforementioned cylinder body 10 to-and-fro motion, be connected to the movable part 65 on this piston 20.
Particularly, aforementioned fixation portion 61 is furnished with: be connected to the perisporium parts 61a on this lip part 12 and be supported on coil component 61b on this surrounding wall portion 61a in the mode of extending to a side (being the left side Fig. 1) of axial direction from the lip part 12 of aforementioned cylinder body 10.
Aforementioned movable part 65 possesses the permanent magnet 65a that is connected on the aforementioned pedestal.
In this form of implementation, aforementioned movable part 65 possesses supporting part 66, this supporting part 66 comprises the little tube 66a of portion that extends to a side of axial direction from aforementioned pedestal 30, from this little tube 66a of portion to the lip part 66b of radial outside direction extension and from the big tube 66c of portion of the radial outer end portion of this lip part 66b to axial opposite side extension, aforementioned permanent magnet 65a is installed on the big tube 66c of portion of this supporting part 66.
In this form of implementation, Linearkompressor 1 further possesses cover 70, this cover 70 is connected on the aforementioned perisporium parts 61a, with with the fixing part 61 of aforementioned cylinder body 10 and aforementioned linear motor 60 in perisporium parts 61a acting in conjunction, mark off the holding space of aforementioned piston 20, pedestal 30, first and second disc springs 40,50.
Particularly, aforementioned cover parts 70 have: be connected on axial direction one end of aforementioned perisporium parts 61a surrounding wall portion 71 and around the end wall 72 of the axial direction the other end of this surrounding wall portion 71.
Aforementioned first disc spring 40 is by the end wall 72 of aforementioned cover parts 70 and aforementioned pedestal 30 clampings.
On the other hand, aforementioned second disc spring 50 is by the lip part 12 of aforementioned cylinder body 10 and aforementioned pedestal 30 clampings.
More specifically, aforementioned first and second disc springs 40,50, when aforementioned linear motor 60 is not worked (, be positioned at pedestal 30 under the situation in neutral position), be in the state that can produce its predetermined loading force.
More preferably, on the subtend face (supporting surface of first disc spring 40) of aforementioned end wall 72 and pedestal 30, can be provided with by the protuberance 80 of 40 extrapolations of aforementioned first disc spring.
Equally, on aforementioned pedestal 30 and subtend face said flange 10 (supporting surface of second disc spring 50), can be provided with by the protuberance 81 of 50 extrapolations of aforementioned second disc spring.In addition, in this form of implementation, insert in outside axial direction the other end of second disc spring 50 in the tube portion 11 of aforementioned cylinder body 10.
Owing to possess this structure, can effectively aforementioned first and second disc springs 40,50 be configured in together in the heart.
At this, the inventor proposes such hypothesis,, in the Linearkompressor 1 of this structure, by making the coiling direction difference of aforementioned first and second disc springs 40,50, can reduce to be carried in the transverse force on the aforementioned pedestal 30 that is.
At this, the inventor uses experimental setup shown in Figure 2 and experimentizes.
Experimental condition is as follows.
That is,, use the dextrorotation disc spring of material as spring steel, line footpath 7.1mm, coiling internal diameter 20.2mm, number of active coils 6.1, each one of the installing and locating number of turns, 9 ° of winding angles, natural length 72.4mm as first disc spring 40.
As second disc spring 50, use the dextrorotation disc spring of material as spring steel, line footpath 6mm, coiling internal diameter 25mm, number of active coils 4.1, each one of the installing and locating number of turns, 9 ° of winding angles, natural length 66mm.
Then, utilize the pedestal 30 of these first and second disc springs, 40,50 clamping thickness for 7.5mm.In addition, set aforementioned first and second disc springs 40,50, so that when intermediateness (displacement among Fig. 2 be zero state), respectively with compressive state (decrement of first disc spring 40 is that the decrement of 10.65mm, second disc spring 50 is 10.65mm) the aforementioned pedestal 30 of clamping of regulation.
Under this condition, the terminal position of aforementioned first and second disc springs 40,50 is changed becomes 0 °, 90 °, 180 °, 270 °, and utilizes the dial type indicator to measure pedestal inclination under each state.Measurement result is illustrated among Fig. 3.
In addition, the terminal position of so-called aforementioned first and second disc springs 40,50 is the circumferential direction separation angle of end that are illustrated in the subtend end of each disc spring.Promptly, each end of 0 ° of expression of terminal position, first and second disc springs is on the same position of circumferential direction, and 90 °, 180 °, 270 ° each end of representing first and second disc springs respectively of terminal position are separated 90 °, 180 °, 270 ° on the disc spring coiling direction.
Experiment carries out that both all adopt the experiment of dextrorotation disc spring to first and second disc springs as a comparison.Other condition is identical with previous experiments.This results of comparative experiment is illustrated among Fig. 3 in the lump.
In addition, the terminal position in the disc spring that coiling direction is identical is still represented the separation angle of coiling direction terminal in each disc spring.
As shown in Figure 3, under the different situation of the coiling direction of first and second disc springs 40,50, the situation identical with coiling direction compared, and on all terminal positions of this first and second disc spring 40,50, the pedestal angle of inclination all reduces.
Load to the proportional angle consideration of the transverse force of pedestal from aforementioned pedestal angle of inclination and by first and second disc springs, it is correct can judging aforementioned hypothesis.
Like this, in the Linearkompressor 1 of this form of implementation,, the transverse force that is carried on the pedestal 30 is reduced by making the coiling direction difference of first and second disc springs 40,50.Thereby, can make piston 20 to-and-fro motion in axial direction stably, can improve the mechanical efficiency of Linearkompressor.
Form of implementation 2.
Secondly, the Linearkompressor to the invention process form 2 describes.
Linearkompressor according to this form of implementation, identical and make specific these 2 of the terminal position in the subtend end of first and second disc springs 40,50 except the coiling direction that makes first and second disc springs 40,50, other Linearkompressor with aforementioned form of implementation 1 is identical.
Thereby, in this form of implementation, except with the difference of aforementioned form of implementation 1, omit its detailed description.
As previously described, in the Linearkompressor of this form of implementation, the coiling direction of first and second disc springs 40,50 is identical.
As the explanation of being done in aforementioned form of implementation 1, under the identical situation of the coiling direction of first and second disc springs 40,50, the situations different with the coiling direction of this first and second disc spring are compared, the transverse force that is carried on the aforementioned pedestal 30 increases, but the inventor has proposed following hypothesis again, promptly, by terminal position being set in the specific scope, can reduce to be carried in the transverse force on this pedestal 30.
Therefore, the inventor is a model with the Linearkompressor of form shown in Figure 1, utilizes finite element method to " terminal position-piston sidepiece load (transverse force) is resolved.
This analytical model of expression in Fig. 4.
In addition, for first and second disc springs 40,50, utilize experimental setup shown in Figure 2 to carry out identical experiment.
In addition, the joint between pedestal 30 and first and second disc spring 40,50 is made by the rigid body that can not produce deflection because of external force.This is because if this joint is an elastomer, then transverse force can be absorbed by this joint.
In addition, for first and second disc springs 40,50, piston 20 and pedestal 30 since must be in three dimensional space specific down, so by tiny hexahedral set of blocks body, be that entity (solid body) is made.
This analysis result is illustrated among Fig. 5.
As shown in Figure 5, the position is that piston sidepiece load is below 50N in the scope of 302 ° (58 °)~125 ° endways, and not needing provides lubricant oil to the sliding contact surface of piston and cylinder body.
And then as shown in Figure 5, the position is that piston sidepiece load is very low with respect to the increase ratio of terminal position in 0 °~90 ° the scope endways.
By this result as can be known, under the identical situation of the first and second disc spring coiling directions, the terminal position of subtend end is preferably set to-58 °~125 °, and then, more preferably be set at 0 °~90 °.
In addition, so-called terminal position is " (bearing) ", is that expression is separated (that is, terminal overlapping) along the direction opposite with the terminal coiling direction of each disc spring.Therefore, 302 ° of terminal positions and terminal position-58 ° synonym.
And then identical and terminal position is the parsing that the relation of " deflection-piston sidepiece load " under 0 °, 90 °, 180 °, 270 ° the situation has carried out utilizing finite element method to first and second disc springs, 40,50 coiling directions.
This analysis result is illustrated among Fig. 6.
In addition, analysis condition is identical with the parsing among Fig. 5.
In addition, so-called deflection is the amount of expression from middle position compression first disc spring.
As shown in Figure 6, even under the situation that the deflection that makes first and second disc springs 40,50 changes, the position is under the situation of 0 ° and 90 ° endways, compares with the situation of 180 ° and 270 °, and piston sidepiece load obviously reduces.
In addition, in aforementioned form of implementation 1 and form of implementation 2, as previously described, first and second disc springs the 40, the 50th constitute in the mode in the tube portion 11 that is inserted in corresponding protuberance 80,81 and cylinder body 10 simply outward, but, in addition, can also have structure as shown in Figure 7.
That is, can be via a plurality of pins 90 of configuration around the axis of disc spring, make the installing and locating circle face of first and/or second disc spring 40,50 and can not couple together with the relative rotation with parts that this installing and locating circle face touches.
By disposing this structure, can prevent first and/or second disc spring 40,50 around rotational, can be effectively the terminal position of disc spring be remained on the desired location.
And then, by the aforementioned protuberance 80,81 of disc spring 40,50 extrapolations, can form internal diameter big and its top end diameter than the internal diameter of this disc spring little taper protuberance 80 ' (Fig. 7 (b)) of cardinal extremity diameter than the disc spring of institute extrapolation.
By being equipped with this taper protuberance 80 ', can prevent the departing from of axial location of disc spring effectively.
In addition, replace aforementioned protuberance 80,80 ', can dispose the recess 81 of the disc spring of interpolation correspondence ".
More preferably, this recess 81 ", can form disc spring external diameter little and top end diameter than this disc spring external diameter big tapered recess (Fig. 7 (b)) of cardinal extremity diameter than institute interpolation, whereby, can prevent the departing from of axial location of disc spring effectively.
As mentioned above, the Linearkompressor of one form according to the present invention owing to make the coiling direction that is configured in the disc spring on axial direction one side and the opposite side different, can reduce to be carried in the transverse force on this pedestal with clipping pedestal effectively.
Thereby, can make piston to-and-fro motion in axial direction effectively, can improve the mechanical efficiency of Linearkompressor.
In addition, the Linearkompressor of another form according to the present invention, under the identical situation of the coiling direction that is configured in the disc spring on axial direction one side and the opposite side with clipping pedestal, owing to the end of this disc spring is configured in-58 °~+ 125 ° the scope, so can reduce to be carried in transverse force on this pedestal effectively.
Thereby, can make piston to-and-fro motion in axial direction effectively, can improve the mechanical efficiency of Linearkompressor.

Claims (5)

1, a kind of Linearkompressor is characterized in that possessing: the cylinder body with the tube portion that is formed with central hole; Can be inserted into the piston in the central hole of this cylinder body in the mode that marks off pressing chamber with in axial direction being free to slide; Pedestal with this piston interlock; Clip this pedestal be configured in a side of axial direction and opposite side respectively along same axis ground, along the first direction that makes aforementioned pressing chamber compression and first and second disc springs that the second direction of aforementioned pressing chamber expansion is loaded this pedestal; And make aforementioned pedestal to first direction and the reciprocating linear motor of second direction; Aforementioned first and second disc springs are formed in the state that can produce its loading force separately when aforementioned linear motor is not worked, and the Hand of spiral of this first and second disc spring is different.
2, a kind of Linearkompressor is characterized in that possessing: the cylinder body with the tube portion that is formed with central hole; Can be inserted into the piston in the central hole of this cylinder body in the mode that marks off pressing chamber with in axial direction being free to slide; Pedestal with this piston interlock; Clip this pedestal be configured in a side of axial direction and opposite side respectively along same axis ground, along the first direction that makes aforementioned pressing chamber compression and first and second disc springs that the second direction of aforementioned pressing chamber expansion is loaded this pedestal; Make aforementioned pedestal to first direction and the reciprocating linear motor of second direction; Aforementioned first and second disc springs are formed in the state that can produce its loading force separately when aforementioned linear motor is not worked, the Hand of spiral of this first and second disc spring is identical, this first and second disc spring, the end that clips the mutual subtend of aforementioned pedestal are configured in-58 °~+ 125 ° scope around the axis.
3, Linearkompressor as claimed in claim 1 or 2, it is characterized in that, at least one end in aforementioned first and second disc springs, be extrapolated on the taper protuberance that is arranged on the parts that support this at least one end, the cardinal extremity diameter of this taper protuberance is bigger than the internal diameter of the disc spring of institute extrapolation, and its top end diameter is littler than the internal diameter of this disc spring.
4, Linearkompressor as claimed in claim 1 or 2, it is characterized in that, at least one end of aforementioned first and second disc springs, in be inserted in the tapered recess that is arranged on the parts that support this at least one end, the cardinal extremity diameter of this tapered recess is littler than the external diameter of the disc spring of institute interpolation, and its top end diameter is bigger than the external diameter of this disc spring.
5, as any one described Linearkompressor in the claim 1 to 4, it is characterized in that, aforementioned first or the installing and locating circle face of at least one end of second disc spring, can not be connected to the relative rotation on the parts that touch with this installing and locating circle face via a plurality of pins of configuration around axis.
CNB031560067A 2002-08-28 2003-08-28 Linear compressor Expired - Fee Related CN100371591C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP249374/2002 2002-08-28
JP2002249374A JP4112313B2 (en) 2002-08-28 2002-08-28 Linear compressor

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Publication Number Publication Date
CN1488856A true CN1488856A (en) 2004-04-14
CN100371591C CN100371591C (en) 2008-02-27

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KR (1) KR100944738B1 (en)
CN (1) CN100371591C (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105781930A (en) * 2014-12-25 2016-07-20 珠海格力节能环保制冷技术研究中心有限公司 Linear compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103122837B (en) * 2013-03-07 2015-12-02 浙江大学 Adopt the Linearkompressor of three kinds of spring common support

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JPS61126385A (en) * 1984-11-22 1986-06-13 Sawafuji Electric Co Ltd Vibration type compressor
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JP2001123950A (en) 1999-10-26 2001-05-08 Matsushita Electric Ind Co Ltd Linear compressor
DE19983919B3 (en) * 1999-12-21 2012-04-05 Lg Electronics Inc. Piston support structure for a linear compressor
GB0005825D0 (en) 2000-03-11 2000-05-03 Archfact Ltd Compressor spring locator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105781930A (en) * 2014-12-25 2016-07-20 珠海格力节能环保制冷技术研究中心有限公司 Linear compressor

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KR20040019921A (en) 2004-03-06
JP4112313B2 (en) 2008-07-02
CN100371591C (en) 2008-02-27
JP2004084614A (en) 2004-03-18
KR100944738B1 (en) 2010-03-03

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