KR20160026121A - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
KR20160026121A
KR20160026121A KR1020140114050A KR20140114050A KR20160026121A KR 20160026121 A KR20160026121 A KR 20160026121A KR 1020140114050 A KR1020140114050 A KR 1020140114050A KR 20140114050 A KR20140114050 A KR 20140114050A KR 20160026121 A KR20160026121 A KR 20160026121A
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KR
South Korea
Prior art keywords
scroll
orbiting scroll
ball
fixed
orbiting
Prior art date
Application number
KR1020140114050A
Other languages
Korean (ko)
Other versions
KR102008940B1 (en
Inventor
박일영
신지 타가미
Original Assignee
한온시스템 주식회사
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Priority to KR1020140114050A priority Critical patent/KR102008940B1/en
Publication of KR20160026121A publication Critical patent/KR20160026121A/en
Application granted granted Critical
Publication of KR102008940B1 publication Critical patent/KR102008940B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

According to an aspect of the present invention, there is provided a scroll compressor including: a fixed scroll having a spiral fixed lap and a hard plate; A orbiting scroll including a revolving wrap and a hard plate forming a compression chamber together with the fixed lap; And a rotating shaft which is eccentrically rotated with respect to the orbiting scroll and is rotatably mounted on an end portion of the rotating scroll, wherein a ball engaging groove And the orbiting scroll is disposed between the fixed scroll and the rotary shaft.

Description

[0001] SCROLL COMPRESSOR [0002]

The present invention relates to a scroll compressor, and more particularly to a scroll compressor having a structure for coupling a rotary shaft and an orbiting scroll.

The scroll compressor has a pair of opposing scrolls, and the refrigerant in the compression space is compressed as the volume of the compression space formed by the pair of scrolls changes. The pair of scrolls comprises a fixed scroll fixed to the compressor and a orbiting scroll which eccentrically rotates with respect to the fixed scroll.

Wherein the driving unit for rotating the orbiting scroll includes a driving shaft that receives rotational power from a rotor rotating by an induction current of the stator, a scroll bushing eccentrically connected to the driving shaft and seated on a rear surface of the orbiting scroll, And a balance weight disposed between the scroll bushings.

A bushing protrusion is formed at a position deviated from the center of the scroll bushing. As the bushing protrusion penetrates the balance weight and is inserted into the center hole of the drive shaft, the scroll bushing, the balance weight, and the drive shaft are assembled and connected to each other.

In the prior art, the diameter of the center hole is formed to be finer than the diameter of the bushing protrusion in order to buffer the tangential force generated when the drive shaft rotates at a high speed. As a result, the scroll bushing has a clearance with respect to the radial direction of the orbiting scroll, and the orbiting scroll can be brought into close contact with the fixed scroll.

In addition, the orbiting scroll has a clearance in the up-and-down direction with respect to the fixed scroll. 1, a gap is formed between the fixed lap 102 formed on the fixed scroll 100 and the surface of the orbiting scroll 110 and between the orbiting lap 112 of the orbiting scroll 110 and the fixed scroll 100, And the tip chambers 104 and 114 are respectively installed at the ends of the fixed lap and the orbiting lap to prevent the leakage of the refrigerant through the clearance. The orbiting scroll is configured to be pressed toward the fixed scroll by the back pressure acting on the back surface of the orbiting scroll during operation of the scroll compressor. However, since it is not easy to push the orbiting scroll to an appropriate degree with respect to the fixed scroll, Thereby allowing the tip thread to function as a buffer.

Therefore, the orbiting scroll is installed to be movable by a predetermined distance with respect to the fixed scroll in order to prevent leakage. In short, in the scroll compressor, a radial clearance is required between the rotary shaft and the orbiting scroll, and a clearance in the axial direction is required between the orbiting scroll and the fixed scroll. Due to this, the scroll bush must be precisely machined, There is a risk of degradation. In addition, since the tip chamber is additionally required, not only the number of parts is increased but also the life of the product is adversely affected due to the tip chamber being worn relatively quickly.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll compressor capable of providing axial and radial clearances in a more simplified structure.

According to an aspect of the present invention, there is provided a fixed scroll including a spiral fixed lap and a hard plate. A orbiting scroll including a revolving wrap and a hard plate forming a compression chamber together with the fixed lap; And a rotating shaft which is eccentrically rotated with respect to the orbiting scroll and is rotatably mounted on an end portion of the rotating scroll, wherein a ball engaging groove And the orbiting scroll is disposed between the fixed scroll and the rotary shaft.

In the above aspect of the present invention, when the rotating shaft is stopped, the orbiting scroll and the rotating shaft are not mechanically constrained, but only when the driving force is applied to the rotating shaft, the driving force is transmitted to the orbiting scroll. Therefore, sufficient clearance can be imparted in the radial direction and the axial direction. This clearance is extinguished when the driving force transmitted by the ball reaches an appropriate level, so that the orbiting scroll is swiveled to drive the radial and axial clearance in a simple configuration . ≪ / RTI >

Here, a flange may be formed at an end of the rotary shaft, and a thrust bearing may be provided between the flange and the end plate of the orbiting scroll.

Here, the thrust bearing may have a disk shape, and a through hole may be formed in the center of the thrust bearing to allow the ball to be inserted therethrough.

Also, the depth of the ball engagement groove may be smaller than the radius of the ball.

In addition, the cross section of the ball engagement groove may be formed to have an arc shape.

In addition, a tip chamber may be provided at an end of the fixed lap or the orbiting lap.

The protrusion may be formed at an end of the rotating shaft to fix the ball so as not to be detached.

According to aspects of the present invention having the above-described structure, since the orbiting scroll and the rotating shaft are mechanically unrestricted, radial and axial clearance can be easily imparted.

In addition, even if the suction pressure or the discharge pressure suddenly changes during operation, a sufficient clearance can be given, so that occurrence of noise and vibration can be minimized.

In addition, since the orbiting scroll and the rotating shaft are substantially separated from each other, clearance in an arbitrary direction can be easily provided.

1 is a cross-sectional view schematically showing an example of a conventional scroll compressor.
2 is a cross-sectional view for explaining the operation of a conventional scroll compressor.
3 is a cross-sectional view schematically showing an embodiment of a scroll compressor according to the present invention.
FIG. 4 is a plan view schematically showing a state where a ball is inserted in the embodiment shown in FIG. 3. FIG.

Hereinafter, an embodiment of a scroll compressor according to the present invention will be described in detail with reference to the accompanying drawings.

Before describing the embodiment of the present invention, the structure and operation of a conventional scroll compressor will be described first. Referring to FIG. 2, the scroll compressor 1 mainly includes a driving unit 3, a control unit 5, and a compression unit 7. 2, the driving unit 3 includes a driving unit housing 31, an intermediate housing unit 32, a driving unit housing 31, and a driving unit housing 31, A stator 33 provided in the intermediate housing 32 and a rotor 34 rotating inside the stator 33. [

In this case, the driving unit housing 31 is a cylindrical portion of the driving unit 3, and the middle unit 32 is interposed between the driving unit housing 31 and the control unit 5, A bearing housing 35 protrudes from the bottom surface of the housing 32 and a bearing 36 for rotatably supporting the rotary shaft 37 of the drive unit 3 rotor 34 is provided in the bearing housing 35 And is fixedly installed. In addition, a suction port 38 for sucking the refrigerant is formed in the intermediate housing 32 at one side of the circumferential surface.

The stator 33 includes a stator core 33a fixedly mounted on the inner circumferential surface of the drive housing 31 as a kind of electromagnet by press-fitting or the like, and a rotor 34 mounted coaxially on the inside, And a bundle of coils 33b wound on the stator core 33a.

The rotor 34 is rotatably driven by being mounted coaxially inside the stator 33 as described above and rotatably inserted into the through hole at the center of the stator core 33a of the stator 33 A rotating shaft 37 disposed long along the center axis, and a permanent magnet (not shown) attached to the outer circumferential surface of the rotating shaft 37.

Therefore, the rotor 34 is driven to rotate by the interaction with the stator 33 when the stator 33 is energized, and the rotating shaft 37 is driven through the bearing 36 31 so as to rotate together with the rotor 34. As shown in Fig.

The control unit 5 controls the operation of the driving unit 3 and is electrically connected to the stator 33 of the driving unit 3 to rotate the rotor 34 by removing the stator 33. [ The control unit 5 includes a head housing 51 coupled to one side of the intermediate housing 32, a PCB 52 mounted inside the head housing 51, And various electronic components such as a plurality of elements mounted on the printed circuit board.

The compression section 7 is a section for compressing the refrigerant by rotating by the rotational driving force generated in the driving section 3 and is connected to the rear end of the rotary shaft 37 of the driving section 3 as shown in FIG.

At this time, the compression section 7 includes an orbiting scroll 71 which is rotatably mounted on the inner rear end of the drive housing 31, and a fixed scroll 72 which is paired with the orbiting scroll 71 and compresses the refrigerant. And the refrigerant flowing into the compression chamber (73) formed therebetween is compressed by the relative rotation of the orbiting scroll (71) and the fixed scroll (72).

The orbiting scroll 71 is protruded from the rear surface of the orbiting scroll 71 so as to converge toward the center and the orbiting scroll 71 is curved in a spiral shape. So as to rotate relative to the fixed scroll (72) in synchronism with the rotor (34). Although not shown, the orbiting scroll is restrained not to be rotated by a bearing or a pin. When the eccentric driving force is transmitted by the rotating shaft, the orbiting scroll rotates around the rotating shaft.

The fixed scroll 72 is fixed to the inner rear end of the drive housing 31 and is fixed to the orbiting scroll 71a of the orbiting scroll 71 by a fixed wrap 72a curved in a spiral shape Respectively.

Therefore, when the revolving scroll 71 revolves, the mutually-aligned orbiting scroll 71 and the fixed scroll 72 are swung in the drive unit 3 by the interaction of the respective revolving and fixed wraps 71a and 72a, And the refrigerant sucked into the outer periphery of the fixed wraps 71a and 72a is compressed to a central portion thereof and the refrigerant compressed at a high pressure is discharged through the discharge port 72c formed through the fixed scroll 72 into the cover housing 74 And is discharged to the chamber 75.

The cover housing 74 is coupled to the rear end of the drive housing 31 so that one opening of the cover housing 74 faces the rear side of the fixed scroll 72. The cover housing 74 is provided at one side thereof with a discharge A port 76 is formed through.

That is, the refrigerant compressed in the compression chamber 73 is discharged to the high-pressure chamber 75 through the discharge port 72c, and the high-pressure refrigerant discharged into the high-pressure chamber 75 is finally discharged to the outside through the discharge port 76 Is supplied.

At this time, in order to minimize the friction generated between the orbiting scroll (71) and the fixed scroll (72) while the relative rotation thereof is minimized and the leakage of the refrigerant is reduced, the surface of the orbiting scroll (71b) A sealing plate 77 is provided on the surface of the fixed end plate 72b of the scroll 72, respectively. The sealing plate 77 is made of steel and has a smooth surface.

A tip chamber 78 is coupled to the tip of the orbiting wrap 71a and the stationary wrap 72a so as to correspond to the sealing plate 77.

The tip chamber 78 is made of Teflon and has a spiral shape corresponding to the shape of the swirling and stationary wraps 71a and 72a and is in contact with the sealing plate 77 so as to be in contact with the orbiting scroll 71 and the stationary scroll 72 Minimize tip clearance to minimize leakage.

As described above, the orbiting scroll is provided so as to be able to advance or retreat relative to the fixed scroll, and the contact pressure to the fixed scroll is adjusted by the back pressure applied to the back surface of the orbiting scroll. Therefore, as described in the background section, the orbiting scroll and the rotary shaft must be coupled to each other so that they can flow in the radial direction and the axial direction. However, such a conventional fastening structure is complicated and difficult to manufacture.

3, an embodiment of a scroll compressor according to the present invention will be described in detail. Referring to FIG. 3, the embodiment 200 is basically the same as the conventional scroll compressor in that it includes the fixed scroll 210 and the orbiting scroll 220. The fixed scroll 210 includes a fixed lap 212 formed in a spiral shape on a fixed end plate and the fixed lap 212 meshes with a orbiting wrap 222 formed on a rotating end plate of the orbiting scroll 220, .

The orbiting scroll 220 is installed so as not to be rotatable by an articulation or a guide pin or the like, and a ball engagement groove 224 having an arc-shaped cross section is formed at the center of the orbiting scroll 220.

A rotating shaft 230 is disposed on the back surface of the orbiting scroll 220. The rotation shaft 230 is coupled to the rotor as described above, and is rotated by the electromagnetic force between the rotor and the stator when electric power is supplied. However, the rotary shaft 230 is configured to rotate eccentrically with respect to the orbiting scroll.

A flange 232 extending in a radial direction of the rotating shaft 230 is provided at an end of the rotating shaft 230 and a ball fixing portion 234 is formed at a substantially central portion of the flange 232. A ball 240 is rotatably mounted in the ball fixing portion 234. Here, a protrusion 236 is formed on the outer periphery of the ball fixing portion 234 to prevent the ball 240 from being detached. The protrusion 236 may be omitted by increasing the depth of the ball fixing portion 234. FIG.

Here, the radius r of the ball 240 is smaller than the radius of curvature R of the ball engagement groove 224. The radial clearance of the orbiting scroll is determined by the difference between the radius of curvature (R) and the radius (r). Also, the depth of the ball engagement groove 224 is smaller than the radius r of the ball 240. The axial clearance of the orbiting scroll is determined by the difference between the depth and the radius r.

A disc-shaped thrust bearing 250 is provided between the back surface of the orbiting scroll 220 and the flange 232 of the rotating shaft. A through hole 252 is formed in the center of the thrust bearing 250 to allow the ball to pass therethrough. The thrust bearing 250 is installed to smoothly move between the flange 232 and the rear surface of the orbiting scroll 220.

Now, with reference to Figs. 3 and 4, the operation of the above embodiment will be described. As shown, the orbiting scroll 220 and the rotary shaft 230 are only interposed between the two, and are not mechanically constrained at all. Accordingly, the orbiting scroll can freely move in the radial direction (the left-right direction in Fig. 3) and the axial direction (the up-down direction in Fig. 3) with respect to the rotation shaft.

However, since the fixed scroll 210 is disposed above the orbiting scroll, the movement in the axial direction is limited until it comes into contact with the fixed scroll. The movement in the radial direction is also restricted to a distance corresponding to the difference between the radius r of the ball 240 and the radius of curvature R of the ball engagement groove 224. It is needless to say that the orbiting scroll can freely move in the radial direction and the axial direction within a range that does not deviate from the limitation, but the rotation is prevented by the above-mentioned bearing or the like.

In this state, when the driving force is applied to the rotating shaft 230, the orbiting scroll remains stopped until the ball 240 comes into contact with the inner wall surface of the ball catching groove 224, Rotation.

When the rotation of the rotation shaft further progresses and the ball 240 contacts the inner wall surface of the ball engagement groove 224, the driving force transmitted to the rotation shaft causes the ball 240 to apply a force F s to the orbiting scroll do. The force F s can be divided into a radial component F r and an axial component F h and the radial component F r moves the orbiting scroll radially, So that the wrap and the orbiting scroll of the orbiting scroll are in close contact with each other. In addition, the axial component force (F h) is to prevent leakage between the raising push the orbiting scroll toward the fixed scroll end plate and fixed between the orbiting wrap and the orbiting end plate and a stationary wrap.

Here, since the ball 240 is rotatably mounted on the rotary shaft 230, when the excessive force is exerted on the orbiting scroll, the ball is prevented from being rotated by an excessive force.

Referring to FIG. 4, the force F s caused by the driving force can be divided into a radial component F r and a component F c in a direction perpendicular to the radial component F r , The force F c causes a torque that causes the orbiting scroll to pivot relative to the fixed scroll.

As described above, in the above-described embodiment, the driving force is transmitted by the ball, and since the rotary shaft and the orbiting scroll are not mechanically constrained, clearance in any direction of the orbiting scroll relative to the rotary shaft can be easily provided. In addition, when excessive force is applied, it can be solved by rotating the ball, so that wear due to friction between parts can also be minimized. Particularly, even if the tip chamber provided at the end of the orbiting wrap and the fixed lap is omitted, a superior leakage preventing effect can be obtained.

However, in the case of operation at a high compression ratio, a tip chamber can be additionally provided in order to obtain a more satisfactory leakage preventing performance. In this case, however, durability of the tip chamber can be improved because a proper degree of pressure is applied to the tip chamber.

Claims (7)

A fixed scroll having a spiral fixed lap and a hard plate;
A orbiting scroll including a revolving wrap and a hard plate forming a compression chamber together with the fixed lap; And
And a rotating shaft which eccentrically rotates with respect to the orbiting scroll and is freely rotatably mounted at an end thereof,
Wherein a ball engagement groove having a radius of curvature larger than a radius of the ball is formed on an inner peripheral surface of a back plate of the orbiting scroll, and the orbiting scroll is disposed between the fixed scroll and the rotation shaft. The method according to claim 1,
Wherein a flange is formed at an end of the rotary shaft, and a thrust bearing is provided between the flange and the end plate of the orbiting scroll. 3. The method of claim 2,
Wherein the thrust bearing has a disk shape, and a through hole is formed in a center portion of the thrust bearing to allow the ball to be inserted therethrough. The method according to claim 1,
And the depth of the ball engagement groove is smaller than the radius of the ball. The method according to claim 1,
Wherein a cross section of the ball engagement groove has an arc shape. The method according to claim 1,
And a tip chamber is provided at an end of the fixed lap or the orbiting lap. The method according to claim 1,
And a protrusion is formed at an end of the rotating shaft to fix the ball so that the ball does not come off.
KR1020140114050A 2014-08-29 2014-08-29 Scroll compressor KR102008940B1 (en)

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Application Number Priority Date Filing Date Title
KR1020140114050A KR102008940B1 (en) 2014-08-29 2014-08-29 Scroll compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020140114050A KR102008940B1 (en) 2014-08-29 2014-08-29 Scroll compressor

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KR20160026121A true KR20160026121A (en) 2016-03-09
KR102008940B1 KR102008940B1 (en) 2019-08-08

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018056634A1 (en) * 2016-09-21 2018-03-29 엘지전자 주식회사 Mutual rotation type scroll compressor having position-changeable bearing applied thereto

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR950014590A (en) * 1993-11-08 1995-06-16 김광호 Scroll compressor
KR950033094A (en) * 1994-05-17 1995-12-22 이헌조 Axial Leakage Prevention Device of Scroll Compressor
KR20010007167A (en) * 1999-06-08 2001-01-26 마스다 노부유키 Thrust rolling bearing and open type scroll compressor
KR20020066967A (en) * 2001-02-13 2002-08-21 스크롤 테크놀로지스 Oil supply cross-hole in orbiting scroll member

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR950014590A (en) * 1993-11-08 1995-06-16 김광호 Scroll compressor
KR950033094A (en) * 1994-05-17 1995-12-22 이헌조 Axial Leakage Prevention Device of Scroll Compressor
KR20010007167A (en) * 1999-06-08 2001-01-26 마스다 노부유키 Thrust rolling bearing and open type scroll compressor
KR20020066967A (en) * 2001-02-13 2002-08-21 스크롤 테크놀로지스 Oil supply cross-hole in orbiting scroll member

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018056634A1 (en) * 2016-09-21 2018-03-29 엘지전자 주식회사 Mutual rotation type scroll compressor having position-changeable bearing applied thereto
US10883500B2 (en) 2016-09-21 2021-01-05 Lg Electronics Inc. Co-rotating scroll compressor having displacement bearing

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