KR20090012841A - Two stage rotary compressor - Google Patents

Two stage rotary compressor Download PDF

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Publication number
KR20090012841A
KR20090012841A KR1020070077023A KR20070077023A KR20090012841A KR 20090012841 A KR20090012841 A KR 20090012841A KR 1020070077023 A KR1020070077023 A KR 1020070077023A KR 20070077023 A KR20070077023 A KR 20070077023A KR 20090012841 A KR20090012841 A KR 20090012841A
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KR
South Korea
Prior art keywords
low pressure
bearing
high pressure
pressure cylinder
cover
Prior art date
Application number
KR1020070077023A
Other languages
Korean (ko)
Inventor
변상명
이승준
이윤희
최윤성
Original Assignee
엘지전자 주식회사
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 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to KR1020070077023A priority Critical patent/KR20090012841A/en
Publication of KR20090012841A publication Critical patent/KR20090012841A/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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
    • F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
    • 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
    • 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
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts
    • 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
    • Y10S417/902—Hermetically sealed motor pump unit

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A 2-stage rotary compressor is provided to simplify the coupling structure of main parts by carrying out coupling thereof once coaxially by using an elongated bolt. A cover(171), a lower bearing(161), a low pressure cylinder(121), an intermediate plate(140), a high pressure cylinder(131) and an upper baring(162) are coupled in sequence from the bottom by an elongated bolt(B) coaxially.

Description

Rotary two stage compressor {TWO STAGE ROTARY COMPRESSOR}

1 is a view showing an example of a conventional rotary twin compressor.

2 is a view showing an example of a conventional rotary two-stage compressor.

Figure 3 is a schematic diagram showing an example of a cycle comprising a rotary two-stage compressor according to the present invention.

4 is a view showing an example of a rotary two-stage compressor according to the present invention.

5 is a view showing an example of a low pressure compression assembly of a rotary two-stage compressor according to the present invention.

6 and 7 are a view of a portion of the rotary two stage compressor according to the present invention from above and below.

8 is a view showing a part of the rotary two-stage compressor according to the present invention cut away.

9 is a view showing an example of a rotary shaft of a rotary two-stage compressor according to the present invention.

10 is a view showing an example of an internal flow path of a rotary two-stage compressor according to the present invention.

11 is a view showing a first embodiment of a fastening structure of a rotary two-stage compressor according to the present invention.

12 is a view showing a second embodiment of the fastening structure of the rotary two-stage compressor according to the present invention.

<Explanation of symbols on main parts of the drawings>

100: rotary compressor 110: electric motor

120: low pressure compression assembly 130: high pressure compression assembly

140: intermediate plate 161: lower bearing

162: upper bearing 171: lower cover

B: long bolt

The present invention relates to a rotary compressor, and more particularly to a rotary two stage compressor that can simplify the fastening structure of the compression mechanism parts.

In general, a compressor is a mechanical device that increases pressure by receiving power from a power generator such as an electric motor or a turbine to compress air, refrigerant, or various other working gases. It is widely used throughout.

These compressors can be classified into reciprocating compressors for compressing refrigerant while linearly reciprocating inside the cylinders by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder. Rotary compressor that compresses the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder so that a compression space for absorbing and discharging the working gas is formed between the roller and the eccentric rotating roller and the cylinder. And a scroll compressor for compressing the refrigerant while the turning scroll is rotated along the fixed scroll to form a compressed space in which the working gas is sucked and discharged between the orbiting scroll and the fixed scroll. Divided into

Particularly, the rotary compressor includes two rollers and two cylinders at the upper and lower portions, and a rotary twin compressor at the upper and lower rollers and the cylinder pair compresses part of the total compression capacity and the other and the upper and lower portions. Rotary two-stage with two rollers and two cylinders, two cylinders in communication, one pair compresses relatively low pressure refrigerant, and the other pair compresses relatively high pressure refrigerant after low pressure compression More advanced, such as a compressor.

In the Republic of Korea Patent Publication No. 1994-001001 a rotary compressor is disclosed. The motor is located inside the shell, and a rotating shaft is installed to penetrate the motor. In addition, a cylinder is located under the electric motor, and an eccentric portion fitted to the rotating shaft and a roller fitted to the eccentric portion are located inside the cylinder. The cylinder has a coolant discharge hole and a coolant inlet hole, and a vane is provided between the coolant discharge hole and the coolant inlet hole to prevent the uncompressed low pressure refrigerant from mixing with the compressed high pressure refrigerant. In addition, a spring is installed at one end of the vane to maintain the eccentric and rotating roller and the vane in contact. When the rotating shaft is rotated by the motor, the eccentric portion and the roller rotate along the inner circumference of the cylinder to compress the refrigerant gas, and the compressed refrigerant gas is discharged through the refrigerant discharge hole.

Republic of Korea Patent Publication No. 10-2005-0062995 discloses a rotary twin compressor. Referring to FIG. 1, two cylinders 1035 and 1045 and an intermediate plate 1030 which compress the same capacity are provided, and the compression capacity is improved by twice compared to the first stage compressor.

Republic of Korea Patent Publication No. 10-2007-0009958 discloses a rotary two-stage compressor. Referring to FIG. 2, the compressor 2001 includes an electric motor 2014 having a stator 2007 and a rotor 2008 above an inside of a sealed container 2013, and two rotary shafts 2002 connected to the electric motor are provided. Eccentricity is provided. The main bearing 2009, the high pressure compression element 2020b, the intermediate plate 2015, the low pressure compression element 2020a and the sub bearing 2019 are laminated in order from the electric motor 2014 side with respect to the rotating shaft 2002. . Also disclosed is an intermediate tube 2040 for introducing refrigerant compressed in the low pressure compression element 2020a into the high pressure compression element 2020b.

However, the rotary two-stage compressor according to the prior art is the main bearing, the high pressure compression element, the intermediate plate, the low pressure compression element is integrally bolted, the sub-bearing, gasket, cover additional bolt connection to form an intermediate pressure chamber Therefore, as the fastening is made twice, there is a problem that not only the productivity is lowered but also the production cost is increased.

The present invention has been made to solve the above problems of the prior art, to provide a rotary two-stage compressor that can simplify the fastening structure of the compression mechanism components, such as low pressure cylinder, high pressure cylinder, intermediate plate, bearing and cover. The purpose is.

In addition, the present invention provides a rotary two-stage compressor capable of fastening compression mechanism parts such as a low pressure cylinder, a high pressure cylinder, an intermediate plate, a bearing and a cover, and at the same time forming an internal flow path through which refrigerant flows. The purpose is to provide.

The present invention for solving the above problems is a sealed container; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; A bearing and a cover defining a low pressure compression assembly and an intermediate pressure chamber in communication with the high pressure compression assembly; And, it provides a rotary two-stage compressor comprising a; low-pressure cylinder, high-pressure cylinder, intermediate plate, long bolt for fastening the bearing and cover on the coaxial.

In addition, the long bolt provides a rotary two-stage compressor, characterized in that fastened along the cover, bearing, low pressure cylinder, intermediate plate, high pressure cylinder from the lower side.

In addition, the upper bearing and the upper cover is fixed to the inside of the sealed container so as to be located above the high pressure compression assembly, and having a space for temporarily passing through the refrigerant discharged from the high pressure compression assembly; the long bolt extends to the upper bearing It provides a rotary two-stage compressor, characterized in that fastened.

The present invention also provides a rotary two-stage compressor, which is provided between the bearing and the cover and includes a gasket for preventing leakage of the intermediate pressure chamber.

In addition, the bearing includes a shaft insertion portion protruding in one direction to the center so that the rotation shaft is inserted, and a fastening portion protruding in the same direction as one direction around the cover so that the cover is long bolted, the cover is inserted / It is formed in a flat plate shape provided with a support hole, the gasket provides a rotary two-stage compressor, characterized in that formed in a flat plate shape corresponding to the cover.

In addition, the bearing includes a shaft insertion portion protruding in one direction to the center so that the rotation shaft is inserted, and a fastening portion that is flat around the cover so that the cover is fastened to the long bolt, and the cover includes a hole into which the shaft insertion portion of the bearing is inserted / supported. And a periphery stepped to protrude in one direction and the opposite direction around the center, wherein the gasket includes a first gasket installed between the shaft insert of the bearing and the center of the cover, and between the fastening portion of the bearing and the periphery of the cover. It provides a rotary two-stage compressor, including; a second gasket installed in.

In addition, the bearing, the low pressure cylinder, the intermediate plate, the inner passage through which the refrigerant flows by the intermediate pressure communication holes formed in the high pressure cylinder, respectively; further comprising a long bolt, bearing, low pressure cylinder, intermediate plate, It provides a rotary two-stage compressor, characterized in that installed at regular intervals in the circumferential direction of the high pressure cylinder.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

3 is a schematic diagram showing an example of a cycle including a rotary two-stage compressor according to the present invention. The heating cycle includes components such as rotary two stage compressor 100, condenser 300, evaporator 400, phase separator 500, and four-way valve 600. Among them, the condenser 300 constitutes an indoor unit, and the compressor 100, the evaporator 400, and the phase separator 500 constitute an outdoor unit. The refrigerant compressed by the compressor 100 is introduced into the condenser 300 of the indoor unit through the four-way valve 600, and the compressed refrigerant gas is condensed by exchanging heat with the surroundings. The condensed refrigerant passes through the expansion valve to low pressure. The refrigerant passing through the expansion valve is separated into gas and liquid in the phase separator 500, and the liquid flows into the evaporator 400. The liquid is evaporated by heat exchange in the evaporator 400 and flows into the accumulator 200 in a gas state, and flows into the low pressure compression assembly (not shown) through the refrigerant inlet pipe 151 of the compressor 100 in the accumulator 200. do. In addition, the gas separated from the phase separator 500 is introduced into the compressor 100 through the injection pipe 153. The medium pressure refrigerant compressed by the low pressure compression assembly of the compressor 100 and the refrigerant introduced through the injection tube 153 are introduced into the high pressure compression assembly (not shown) of the compressor 100 and compressed to high pressure. The discharge pipe 152 is discharged to the outside of the compressor 100 again.

4 is a view showing an example of a rotary two-stage compressor according to the present invention. Rotary two-stage compressor 100 according to an embodiment of the present invention, the lower pressure compression assembly 120, the intermediate plate 140, the high pressure compression assembly 130 and the electric motor 110 from the bottom in the sealed container 101 It includes. In addition, it includes a refrigerant inlet pipe 151 penetrating through the sealed container 101 and connected to the accumulator 200 and a refrigerant discharge pipe 152 for discharging the compressed refrigerant to the outside of the sealed container.

The motor 110 includes a stator 111, a rotor 112, and a rotation shaft 113. The stator 111 includes a lamination of a ring-shaped electrical steel sheet and a coil wound on the lamination. The rotor 112 also has a lamination in which an electronic steel sheet is laminated. The rotating shaft 113 penetrates the center of the rotor 112 and is fixed to the rotor 112. When a current is applied to the motor 110, the rotor 112 rotates by the mutual electromagnetic force between the stator 111 and the rotor 112, and the rotating shaft 113 fixed to the rotor 112 also rotates with the rotor 112. Rotate together. The rotating shaft 113 extends from the rotor 112 to the low pressure compression assembly 120 so as to penetrate the center portion of the low pressure compression assembly 120, the intermediate plate 140, and the high pressure compression assembly 130.

The low pressure compression assembly 120 and the high pressure compression assembly 130 are stacked in the order of the low pressure compression assembly 120-the middle plate 140-the high pressure compression assembly 130 from the bottom with the intermediate plate 140 interposed therebetween. Can be. Conversely, the high pressure compression assembly 120, the middle plate 140, and the high pressure compression assembly 130 may be stacked in the order from the bottom. In addition, regardless of the stacking order of the low pressure compression assembly 120, the middle plate 140 and the high pressure compression assembly 130, the lower bearing and the upper bearing 161 and the upper bearing 162 are respectively installed It helps the rotation of the rotary shaft 113, and supports the load of each component of the two-stage compression assembly stacked vertically. The upper bearing 162 is three-point welded to the hermetic container 101 to support the load of the two-stage compression assembly and fix it to the hermetic container 101.

The low pressure compression assembly 120 is connected to the refrigerant inlet pipe 151 introduced through the sealed container 101 from the outside. In addition, a lower bearing 161 and a lower cover 171 are positioned below the low pressure compression assembly 120, and an intermediate pressure chamber Pm is formed between the lower bearing 161 and the lower cover 171. The intermediate pressure chamber Pm is a space in which the refrigerant compressed in the low pressure compression assembly 120 is discharged, and is a space in which the refrigerant is temporarily stored before the refrigerant is introduced into the high pressure compression assembly 130, from the low pressure compression assembly 120. The high pressure compression assembly 130 serves as a buffer space on the flow path through which the refrigerant flows.

Looking at the structure in which the intermediate pressure chamber (Pm) is formed in the lower bearing 161, for example, the lower bearing 161 is protruded downward, the center portion in which the rotary shaft 131 is inserted / installed and the peripheral portion of the lower cover 171 abuts The lower cover 171 has a hole through which the rotating shaft 131 passes, and is formed in a flat shape in close contact with the lower bearing 161. In this case, the downwardly protruding peripheral portion of the lower bearing 161 and the flat peripheral portion of the lower cover 171 are bolted to the low pressure cylinder 121 at once. As another example, the lower bearing 161 may protrude downward only at the center of which the rotation shaft 113 is inserted / installed, and at the same time, other portions thereof may be formed flat, and the lower cover 171 may have a hole through which the rotation shaft 113 penetrates. The provided central portion may be formed flat, and at the same time, the periphery thereof may be stepped up to protrude upward. At this time, the flat peripheral portion of the lower bearing 161 and the peripheral portion protruding upwardly of the lower cover 171 are installed to be bolted to the low pressure cylinder 121 at once. In this case, the shape of the lower bearing 161 can be simplified to reduce the number of work, and the shape of the lower cover 171 can also be easily manufactured by pressing. Furthermore, the shape and the fastening method of the lower bearing 161 and the lower cover 171 are not limited to the above-mentioned method, and will be described an example in which the intermediate pressure chamber Pm is formed in the lower bearing 161. However, the intermediate pressure chamber Pm may be formed in any one of the upper bearing 162 and the intermediate plate 140.

A discharge port (not shown) is installed on an upper portion of the upper bearing 162 positioned above the high pressure compression assembly 130. The high pressure refrigerant discharged from the high pressure compression assembly 130 through the discharge port of the upper bearing 162 is discharged to the outside through the refrigerant discharge pipe 152 located on the top of the sealed container 101.

The lower bearing 161, the low pressure compression assembly 120, the intermediate plate 140, and the high pressure compression assembly 130 have an internal flow path 180 connecting refrigerant from the low pressure compression assembly 120 to the high pressure compression assembly 130. ) Is formed. The inner flow passage 180 is formed vertically so as to be substantially parallel to the axial direction of the compressor.

Since the inner passage 180 is not a separate tube, the injection tube 153 (shown in FIG. 3) into which the refrigerant gas separated from the above-described phase separator 500 (shown in FIG. 3) flows into the inner passage 180. It can be installed anywhere. For example, a through hole (not shown) is formed in any one of the lower bearing 161, the intermediate plate 140, and the high pressure cylinder 131 forming the intermediate pressure chamber Pm, and the injection tube 153 is formed in the through hole. ), The refrigerant gas can be introduced, and the compression efficiency can be increased.

5 is a view showing an example of a low pressure compression assembly of a rotary two-stage compressor according to the present invention. The low pressure compression assembly 120 includes a low pressure cylinder 121, a low pressure eccentric 122, a low pressure roller 123, a low pressure vane 124, a low pressure elastic member 125, a low pressure inlet hole 126, and an intermediate pressure discharge hole. 127. The rotating shaft 113 passes through the center of the low pressure cylinder 121, and the low pressure eccentric portion 122 is fixed to the rotating shaft 113. In this case, the low pressure eccentric portion 122 may be integrally formed with the rotation shaft 113. In addition, the low pressure roller 123 is rotatably installed in the low pressure eccentric part 122, and the low pressure roller 123 rotates while rolling along the inner diameter of the low pressure cylinder 121 as the rotary shaft 113 rotates. The low pressure inlet hole 126 and the intermediate pressure discharge hole 127 are formed at both sides of the low pressure vane 124. In addition, the space in the low pressure cylinder 121 is partitioned by the low pressure vane 124 and the low pressure roller 123, and the refrigerant before and after compression coexists in the low pressure cylinder 121. As shown in FIG. It is partitioned by the low pressure vane 124 and the low pressure roller 123, and the portion including the low pressure refrigerant inlet hole 126 is the low pressure refrigerant inlet (S l ), the middle portion containing the intermediate pressure discharge hole 127 in the middle It is called a pressurized refrigerant discharge part D m . Here, the low pressure elastic member 125 is a means for applying a force to the low pressure vane 124 so that the low pressure vane 124 maintains contact with the low pressure roller 123. The vane hole 124h formed in the low pressure cylinder 121 is formed to penetrate the low pressure cylinder 121 laterally so that the low pressure vane 124 can be located. Through the vane hole 124, the low pressure vane 124 is guided, and the low pressure elastic member 125 that applies the force to the low pressure vane 124 extends through the low pressure cylinder 121 to the sealed container 101. . One end of the low pressure elastic member 125 is in contact with the low pressure vane 124, the other end is in contact with the closed container 101, so that the low pressure vane 124 maintains contact with the low pressure roller 123. To push.

In addition, the low pressure cylinder 121 has an intermediate pressure communication hole so that the refrigerant compressed in the low pressure compression assembly 120 may flow into the high pressure compression assembly 130 through the intermediate pressure chamber Pm formed by the lower bearing 161. 120a) is formed. The intermediate pressure communication hole 120a does not overlap the refrigerant inlet pipe 151 inserted into the low pressure inlet hole 126, that is, the internal flow path 180 and the refrigerant inlet pipe 151 do not overlap with each other. ) Is formed. Although partially overlapped with the refrigerant inlet pipe 151, the medium pressure refrigerant is formed to flow into the high pressure compression assembly 130 from the intermediate pressure chamber Pm. However, in this case, since the internal flow path 180 can see the loss by the cross-sectional area overlapping the refrigerant inlet pipe 151, it is not preferable. In addition, as the refrigerant bypasses the vicinity of the refrigerant inlet pipe 151, the pressure may decrease.

As shown in FIG. 5, when the low pressure eccentric portion 122 rotates by the rotation of the rotary shaft 113, and the low pressure roller 123 rolls along the low pressure cylinder 121, the volume of the low pressure inflow portion S 1 is reduced. Since the low pressure inlet S 1 becomes low as it is increased, the refrigerant flows through the low pressure inlet hole 126. On the other hand, the intermediate pressure discharge portion (D m), the volume is filled with the refrigerant in the intermediate pressure discharge portion (D m) compression, it loses of, and is discharged through the intermediate pressure discharge holes (127). As the low pressure eccentric part 122 and the low pressure roller 123 rotate, the volume of the low pressure inlet part S 1 and the intermediate pressure discharge part D m continuously changes, and discharges the compressed refrigerant every one revolution.

6 to 8 is a view showing a part of a rotary two-stage compressor according to an embodiment of the present invention. In order from the bottom, the lower bearing 161, the low pressure compression assembly 120, the intermediate plate 140, and the high pressure compression assembly 130 are stacked. As described above, the low pressure refrigerant is introduced into the low pressure cylinder 121 through the refrigerant inlet pipe 151 and the low pressure inlet hole 126 and compressed, and then the low pressure compression assembly 120 through the intermediate pressure discharge hole 127. ) Is discharged into the intermediate pressure chamber Pm, which is a space restricted by the lower surface of the bottom surface, the lower bearing 161, and the lower cover 171. The intermediate pressure discharge hole 161h is formed in the lower bearing 161 so that the intermediate pressure discharge hole 127 and the intermediate pressure discharge hole 161h of the lower bearing 161 overlap each other. A valve (not shown) is installed below the intermediate pressure discharge hole 161h, and when the refrigerant compressed in the intermediate pressure discharge part Dm of the low pressure compression assembly 120 is compressed to a predetermined pressure, the pressure is discharged into the intermediate pressure chamber Pm. Be sure to The refrigerant discharged into the intermediate pressure chamber Pm is formed in the intermediate pressure communication hole 120a and the intermediate plate 140 formed in the low pressure cylinder 121 through the intermediate pressure communication hole 161a formed in the lower bearing 161. It passes through the intermediate pressure communication hole 140a and flows into the high pressure compression assembly 130 through the intermediate pressure inlet groove 130a of the high pressure cylinder 131. Intermediate pressure communication hole 161a of the lower bearing 161, intermediate pressure communication hole 120a of the low pressure compression assembly, intermediate pressure communication hole 140a of the intermediate plate 140, and intermediate pressure inflow of the high pressure compression assembly 130 The groove 130a forms an internal flow path 180 through which the medium pressure refrigerant compressed by the low pressure compression assembly 120 passes. At this time, the intermediate pressure inlet groove 130a of the high pressure compression assembly 130 is formed in the form of an inclined groove so as to communicate with the internal space of the high pressure cylinder 131. A lower portion of the intermediate pressure inlet groove 130a is formed to contact the intermediate pressure communication hole 140a of the intermediate plate 140 to form a part of the internal flow path 180, and the compressed medium pressure refrigerant is medium pressure inlet. It is introduced into the high pressure cylinder 131 through the groove 130a. When the medium pressure refrigerant flows into the high pressure compression assembly 130 through the internal flow path 180, the high pressure compression assembly 130 compresses the medium pressure refrigerant to the high pressure in the same operating principle as the low pressure compression assembly 120. do.

As described above, when the internal flow path 180 through which the medium pressure refrigerant passes is not formed by a separate pipe, but formed inside the sealed container 101, noise can be reduced, and the length of the internal flow path 180 is increased. Can be shortened, and the loss of the refrigerant pressure due to the resistance can be reduced. In addition, in the above, an example in which the intermediate pressure chamber Pm is formed in the lower bearing 161 has been described, but the intermediate pressure chamber Pm may be formed in any one of the upper bearing 162 and the intermediate plate 140. . Accordingly, although the specific structure may vary slightly, in any case, the internal flow path 180 is formed inside the two-stage compression assembly, so that the medium pressure refrigerant compressed in the low pressure compression assembly 120 through the internal flow path 180 is formed. Guided to the high pressure compression assembly 130. Through this configuration, it is possible to shorten the length of the flow path through which the medium pressure refrigerant is guided, to minimize the flow loss, and to reduce noise and vibration without passing through the connection pipe passing through the hermetic container 101.

At this time, the intermediate pressure communication hole 120a of the low pressure compression assembly 120 constituting the internal flow path 180 to prevent the internal flow path 180 from being blocked by the refrigerant inlet pipe 151, and the intermediate pressure of the intermediate plate 140. The communication hole 140a and the intermediate pressure inlet groove 130a of the high pressure compression assembly 130 are formed to be spaced apart from the refrigerant inlet pipe 151 when viewed in the axial direction of the compressor 100.

The intermediate pressure communication hole 161a of the lower bearing 161 is formed to avoid the position where the refrigerant inlet pipe 151 is inserted so as not to overlap with the refrigerant inlet pipe 151 connected to the low pressure cylinder 121. The refrigerant inlet pipe 151 is inserted into the low pressure inlet hole 126 formed in the low pressure cylinder 121. The low pressure inlet hole 126 is formed close to the low pressure vane insertion hole 124h into which the low pressure vane 124 (shown in FIG. 5) is inserted. This is because, as the low pressure inlet hole 126 moves away from the low pressure vane 124 (shown in FIG. 5), a dead volume that does not contribute to the compression of the refrigerant in the inner space of the low pressure cylinder 121 increases.

In addition, the intermediate pressure inlet groove 130a of the high pressure cylinder 131 is not formed to penetrate from the lower part to the upper part of the high pressure cylinder 131, and communicates with the internal space of the high pressure cylinder 131 from the lower part of the high pressure cylinder 131. It is formed obliquely. At this time, the intermediate pressure inlet groove 130a is formed close to the high pressure vane hole 134h into which the high pressure vane (not shown) is inserted. As in the low pressure compression assembly, since the intermediate pressure inlet groove 130a is formed close to the high pressure vane (not shown), it is possible to reduce the dead volume in the space inside the high pressure cylinder 131.

The low pressure vanes 124 and the high pressure vanes (not shown) are located on the same axis. Therefore, the intermediate pressure communication hole 161a formed in the lower bearing 161 and the intermediate pressure inflow groove 130a formed in the high pressure cylinder 131 are not formed on the same axis, and horizontal positions are formed to be spaced apart from each other. In the third embodiment of the present invention, in order to connect the intermediate pressure communication hole 161a of the lower bearing 161 and the intermediate pressure communication hole 130a of the high pressure cylinder 131, the intermediate pressure communication hole of the low pressure cylinder 121 is connected. The intermediate pressure communication hole 140a of the 120a and the intermediate plate 140 is formed in a substantially spiral shape. The intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed to overlap each other in a spiral. That is, the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 overlap to form a spiral communication hole. At this time, one end of the spiral communication hole overlaps the intermediate pressure communication hole 161a of the lower bearing 161, and the other end overlaps the intermediate pressure inlet groove 130a of the high pressure cylinder 131. Here, one end of the intermediate pressure communication hole 120a of the low pressure cylinder 121 penetrates to be connected to the intermediate rolling communication hole 161a of the lower bearing 161. That is, the intermediate pressure communication hole 120a of the low pressure cylinder 121 is formed such that one end contacting the intermediate pressure communication hole 161a of the lower bearing 161 penetrates in the vertical direction of the low pressure cylinder 121, and intermediate pressure communication is performed. The remaining portion of the hole 120a is formed in a spiral shape as the lower portion of the intermediate pressure communication hole 120a gradually increases from one end to the other end. In addition, the intermediate pressure communication hole 140a of the intermediate plate 140, on the other hand, the other end of the spiral communication hole, that is, the other end overlapping the intermediate pressure inlet groove 130a of the upper cylinder 130 is perpendicular to the intermediate plate 140. It is formed to penetrate in the direction. In addition, as the upper end portion of the intermediate pressure communication hole 120a gradually increases from one end overlapping with the intermediate pressure communication hole 161a of the lower bearing 161 to the other end, it is formed in a spiral shape as a whole.

When the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral shape, the refrigerant is formed in the intermediate pressure communication hole 120a and the middle of the low pressure cylinder 121. The resistance received along the intermediate pressure communication hole 140a of the plate 140 is reduced. Of course, the intermediate pressure communication hole (120a) of the low pressure cylinder 121 and the intermediate pressure communication hole (140a) of the intermediate plate 140 is not only a spiral, but also a circular arc-like shape that does not change the height of the top or bottom. It may be formed as.

Further, when the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral or arc shape, the intermediate pressure communication holes 120a and 140a of the spiral or arc shape are formed. Fastening holes 120b and 140b may be formed in the central portion of the. The lower bearing 161, the low pressure cylinder 121, the intermediate plate 140, the high pressure cylinder 131, and the upper bearing 162 are generally fastened through bolts. At this time, the fastening holes 161b, 120b, 130b, 140b, and 162b to which the bolts are fastened are the refrigerant inlet pipe 151, the medium pressure communication hole 161a, 120a, 130a, and 162a, the medium pressure inlet groove 140a, and the middle. Various members such as the pressure discharge hole 127 and the internal flow path should be avoided. In addition, the fastening holes 161b, 120b, 130b, 140b, and 162b should be formed in at least three places, and should be able to evenly distribute the fastening force to the entire compressor assembly 105. In this case, the intermediate pressure communication hole 120a of the low pressure cylinder 121 and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed of the intermediate pressure communication hole 161a of the lower bearing 161 and the high pressure cylinder 131. Since the length is longer than that of the intermediate pressure inlet groove 130a, it prevents the formation of a plurality of fastening holes 161b, 120b, 130b, 140b and 162b. Therefore, when the intermediate pressure communication hole 120a of the low pressure cylinder and the intermediate pressure communication hole 140a of the intermediate plate 140 are formed in a spiral or arc shape, the fastening hole 161b, 120b, 130b, 140b, 162b can be formed, which is advantageous for distributing a plurality of fastening holes 161b, 120b, 130b, 140b, 162b in the entire compressor assembly 105.

9 is a view showing an example of a rotary shaft provided in a rotary two-stage compressor according to the present invention. The low pressure eccentric portion 122 and the high pressure eccentric portion 132 are coupled to the rotary shaft 113. The low pressure eccentric 122 and the high pressure eccentric 132 are coupled to the rotating shaft 113 with a phase difference of generally 180 kHz to reduce vibration. In addition, the rotating shaft 113 is a hollow shaft having an empty inside, and has an oil communication hole 113a at the lower portion of the low pressure eccentric portion 122 and the upper portion of the high pressure eccentric portion 132. In addition, the rotating shaft 113 is formed of a hollow shaft, the inner portion (113h) is inserted into the stirrer (113b) of the thin plate bent in a spiral. The stirrer 113b is fitted to the inside 113h of the rotating shaft 113, and rotates together with the rotating shaft 113 when the rotating shaft 113 rotates. As the stirrer 113b rotates together by the rotation of the rotary shaft 113, oil filled in the lower portion of the airtight container 101 (shown in FIG. 4) rises along the inside of the rotary shaft 113 along the stirrer 113b. A portion of the low pressure roller 121, the intermediate plate 140 and the high pressure cylinder 131 through the oil communication hole 113a formed in the rotating shaft 113, and the low pressure roller 123 (shown in FIG. 5). And a high pressure roller (not shown).

10 is a view showing an example of the installation structure of the intermediate pressure chamber of the rotary two-stage compressor according to the present invention. The intermediate pressure chamber Pm of the rotary two-stage compressor according to the present invention includes a lower bearing 161 and a lower cover 171 positioned below the low pressure compression assembly 120, and a gasket installed therebetween to prevent leakage of refrigerant. (G), but the intermediate pressure chamber (Pm) is the lower bearing 161, the low pressure cylinder 121, the intermediate pressure communication holes (161a, 120a, 140a) and high pressure cylinder 131 provided in the intermediate plate 140, respectively It is installed to communicate with the inner flow path 180 made of the intermediate pressure inlet groove (130a) provided in the. Of course, the first compressed refrigerant in the low pressure compression assembly 120 flows along the intermediate pressure chamber Pm and the internal flow path 180 and merges with the medium pressure refrigerant introduced through the injection tube 153, and then the high pressure. It is introduced into the compression assembly 130 and is second compressed.

11 is a view illustrating a fastening structure of a rotary two-stage compressor according to the present invention, the lower cover 171, the lower bearing 161, the low pressure cylinder 121, the intermediate plate 140, The high-pressure cylinder 131, the upper bearing 162 is fastened to the long bolt (B) in the axial direction, the long bolt (B) is installed so as not to interfere with the inner flow path 180 located in the axial direction. That is, as mentioned above: each of the fastening holes 161b, 120b, 140b, 130b, 162b of the lower bearing 161, the low pressure cylinder 121, the intermediate plate 140, the high pressure cylinder 131: The lower cover 171 is provided with a fastening hole (not shown), and the fastening holes 161b, 120b, 140b, 130b, and 162b of such components are provided at a predetermined interval in the circumferential direction. Five bolts are formed at the same time and five long bolts B are also provided to provide fastening force uniformly in the circumferential direction to each part.

At this time, the lower bearing 161 is based on the flat disk 161A, the cylindrical shaft insertion portion 161B, which is inserted / installed in the center of the rotation shaft 113 protrudes downward, the long bolt (B) is fastened around The fastening part 161C is projected downward, and is cast. In addition, the lower cover 171 is formed in a flat plate shape formed in the center of the hole in which the shaft insertion portion 161B of the lower bearing 161 is fitted, and the gasket G is also formed in a shape corresponding to the lower cover 171. do.

Therefore, when the upper bearing 162 is welded and fixed inside the sealed container 101, the high pressure cylinder 131, the middle plate 140, the low pressure cylinder 121, and the lower bearing 161 in the lower direction of the upper bearing 162. , Stacking the gasket (G) and the lower cover 171, the flat upper surface of the lower bearing 161 abuts the lower surface of the low-pressure cylinder 121, the shaft insertion portion 161B of the lower bearing 161 is gasket (G) and each hole of the lower cover 171, and then the long bolt (B) is a lower pressure cylinder 121 at the periphery of the lower cover 171, the fastening portion (161C) of the lower bearing 161 at once. , To be coupled to the intermediate plate 140, the high pressure cylinder 131, the upper bearing 162.

11 is a view showing a second embodiment of the fastening structure of the rotary two-stage compressor according to the present invention, the second embodiment of the lower cover 171, the lower bearing 161, from the bottom as in the first embodiment The low pressure cylinder 121, the intermediate plate 140, the high pressure cylinder 131, the upper bearing 162 is fastened to the long bolt (B) in the axial direction, but the shape of the lower bearing 161 is simple to work Is reduced and at the same time the shape of the lower cover 171 becomes complicated, it is changed to a structure that can be easily press fabricated.

At this time, the lower bearing 161 is projected downward only in the cylindrical shaft insertion portion 161B in which the rotating shaft 113 is inserted / installed at the center based on the flat disc 161A. The size of the product can also be reduced. In addition, the lower cover 171 has a central portion 171B formed in the center of the hole in which the shaft insertion portion 161B of the lower bearing 161 is fitted is formed flat, the fastening of the long bolt (B) around the fastening The portion 171B is formed stepped so as to protrude upward from the central portion 171A.

Furthermore, in order to prevent leakage between the lower bearing 161 and the lower cover 171, the gaskets G1 and G2 are inserted in contact with each other, and the shaft inserting portion 161B of the lower bearing 161 and the lower cover ( A first gasket G1, such as an O-ring, is provided at a portion where the central portion 171A of the 171 abuts each other, and the peripheral portion of the lower bearing 161 and the fastening portion 171B of the lower cover 171 are mutually provided. A second gasket G2 in the shape of a flat plate ring is provided at an abutting portion.

Therefore, when the upper bearing 162 is welded and fixed inside the sealed container 101, the high pressure cylinder 131, the middle plate 140, the low pressure cylinder 121, and the lower bearing 161 in the lower direction of the upper bearing 162. , Stacking the gasket (G) and the lower cover 171, the flat upper surface of the lower bearing 161 is in contact with the lower surface of the low-pressure cylinder 121, the shaft insertion portion 161B of the lower bearing 161 The gasket G and the lower cover 171 are inserted into the central hole 171A side hole, and then the long bolt B is fastened to the fastening portion 171B of the lower cover 171 and the periphery of the lower bearing 161. The low pressure cylinder 121, the intermediate plate 140, the high pressure cylinder 131, the upper bearing 162 to be fastened at once.

In the above, the present invention has been described in detail by way of examples based on the embodiments of the present invention and the accompanying drawings. However, the scope of the present invention is not limited by the above embodiments and drawings, and the scope of the present invention will be limited only by the contents described in the claims below.

The rotary two-stage compressor according to the present invention configured as described above is fastening each part because the upper bearing, the high pressure cylinder, the intermediate plate, the low pressure cylinder, the lower bearing, the lower cover are fastened at a time using a long bolt on the coaxial shaft. The structure can be simplified to increase productivity and reduce production costs.

In addition, the rotary two-stage compressor according to the present invention includes a medium pressure communication groove or a medium pressure communication hole in the high pressure cylinder, the intermediate plate, the low pressure cylinder, and the lower bearing, and is formed separately from the intermediate pressure communication groove or the intermediate pressure communication hole. When the upper bearing, the high pressure cylinder, the intermediate plate, the low pressure cylinder, the lower bearing, and the lower cover are fastened with long bolts through the sphere, the intermediate pressure communication grooves or the intermediate pressure communication holes of the parts communicate with each other at the same time. There is an advantage that the internal flow path can be easily formed.

Claims (7)

chest; A rotating shaft provided in the sealed container and transmitting a rotational force; A low pressure compression assembly in which primary compression of the refrigerant is performed inside the low pressure cylinder according to the rotation of the rotary shaft; A high pressure compression assembly in which secondary compression of the refrigerant compressed first in the high pressure cylinder is performed according to the rotation of the rotary shaft; An intermediate plate partitioning between the low pressure cylinder and the high pressure cylinder; A bearing and a cover defining a low pressure compression assembly and an intermediate pressure chamber in communication with the high pressure compression assembly; And, And a long bolt for fastening the low pressure cylinder, the high pressure cylinder, the intermediate plate, the bearing and the cover coaxially. The method of claim 1, Long bolt is a rotary two-stage compressor, characterized in that fastened along the cover, bearing, low pressure cylinder, intermediate plate, high pressure cylinder from the lower side. The method of claim 2, An upper bearing and an upper cover fixed inside the sealed container so as to be positioned above the high pressure compression assembly and having a space for temporarily passing through the refrigerant discharged from the high pressure compression assembly; The long bolt is a rotary two-stage compressor characterized in that it is extended to the upper bearing. The method of claim 1, A rotary two-stage compressor, provided between the bearing and the cover, comprising a gasket for preventing leakage of the intermediate pressure chamber. The method of claim 4, wherein The bearing includes a shaft insertion portion protruding in one direction to the center so that the rotation shaft is inserted, and a fastening portion protruding in the same direction as one direction around the cover so that the cover is fastened to the long bolt; The cover is formed into a flat plate shape having a hole into which the shaft insertion portion of the bearing is inserted / supported. The gasket is a rotary two-stage compressor, characterized in that formed in a flat plate shape corresponding to the cover. The method of claim 4, wherein The bearing includes a shaft insertion portion protruding in one direction to the center so that the rotation shaft is inserted, and a fastening portion that is flat around the bolt to fasten the cover. The cover includes a central portion having a hole into which the shaft insertion portion of the bearing is inserted / supported, and a periphery stepped to protrude in a direction opposite to the one direction around the central portion. The gasket includes a first gasket installed between the shaft insertion portion of the bearing and the central portion of the cover, and a second gasket installed between the fastening portion of the bearing and the periphery of the cover. The method according to any one of claims 1 to 6, And an internal flow path through which the refrigerant flows by an intermediate pressure communication hole formed in the bearing, the low pressure cylinder, the intermediate plate, and the high pressure cylinder, respectively. Long bolt is a rotary two-stage compressor, characterized in that installed at regular intervals in the circumferential direction of the bearing, low pressure cylinder, intermediate plate, high pressure cylinder so as not to interfere with the internal flow path.
KR1020070077023A 2007-07-31 2007-07-31 Two stage rotary compressor KR20090012841A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103362816A (en) * 2012-03-30 2013-10-23 三菱电机株式会社 Rotary compressor
KR101369053B1 (en) * 2011-10-27 2014-02-28 미쓰비시덴키 가부시키가이샤 Rotary compressor
KR20190142568A (en) * 2018-06-18 2019-12-27 엘지전자 주식회사 Compressor
US11306719B2 (en) 2018-06-18 2022-04-19 Lg Electronics Inc. Compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101369053B1 (en) * 2011-10-27 2014-02-28 미쓰비시덴키 가부시키가이샤 Rotary compressor
CN103362816A (en) * 2012-03-30 2013-10-23 三菱电机株式会社 Rotary compressor
KR20190142568A (en) * 2018-06-18 2019-12-27 엘지전자 주식회사 Compressor
US11306719B2 (en) 2018-06-18 2022-04-19 Lg Electronics Inc. Compressor

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