JP2005146987A - Heat exchanger integral type horizontal compressor with built-in accumulator - Google Patents

Heat exchanger integral type horizontal compressor with built-in accumulator Download PDF

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JP2005146987A
JP2005146987A JP2003385646A JP2003385646A JP2005146987A JP 2005146987 A JP2005146987 A JP 2005146987A JP 2003385646 A JP2003385646 A JP 2003385646A JP 2003385646 A JP2003385646 A JP 2003385646A JP 2005146987 A JP2005146987 A JP 2005146987A
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heat exchanger
refrigerant gas
rotary compression
sealed container
accumulator
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Yoshiaki Kurosawa
美暁 黒澤
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger integral type horizontal compressor with built-in accumulator in which a function of accumulator is added and a heat exchanger is integrally provided. <P>SOLUTION: This compressor has a double structure in which an inside closed vessel 1 is provided within a horizontal outside closed vessel 16. In the inside closed vessel 1, an electric motor part 2 and a rotary compression part 3 comprised of a first-stage rotary compression part 3a and a second-stage rotary compression part 3b driven by the electric motor part 2 are provided. An intake pipe 13 is arranged to an upper part of a space S between the outside closed vessel 16 and the inside closed vessel 1, and is connected to the first-stage rotary compression part 3a, and an oil reservoir 19A including a liquefied refrigerant is arranged to a bottom of the outside closed vessel 16. A small-sized intake pipe 13a and an delivery pipe 14 for delivering a coolant gas to an outside are arranged to the second-stage rotary compression part 3b. A return pipe 18 is connected to a side end part of the outside closed vessel 16, and the heat exchanger 21 is arranged to the upper part of the space S. An end of the return pipe 18 is connected to an outlet of an evaporator, an end of the delivery pipe 14 is connected to an inlet of a gas cooler, an inlet of the heat exchanger 21 is connected to an outlet of the gas cooler, and an outlet of the heat exchanger 21 is connected to an expansion valve. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、アキュームレータの機能を付加すると共に、熱交換器を一体型に設けた構造のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサに関する。   The present invention relates to a built-in accumulator and a heat exchanger integrated horizontal compressor having a structure in which an accumulator function is added and a heat exchanger is provided integrally.

一般に２段圧縮回転式コンプレッサは、密閉容器内にステータとロータとからなる電動機部と、この電動機部のロータに取り付けた回転軸によって駆動される回転圧縮部とが設けられ、回転圧縮部は第１段回転圧縮部と第２段回転圧縮部とから構成され、これらは共にシリンダとこのシリンダ内を偏心回転するローラとを備えており、密閉容器の外部から吸入管を介して第１段回転圧縮部に吸入される冷媒ガスは、中間圧（１段目吐出圧力）まで圧縮された後に密閉容器内に吐出され、この中間圧の冷媒ガスは第２段回転圧縮部に吸入され、高圧（２段目吐出圧力）に圧縮された後に吐出管を介して密閉容器外部に吐出される（例えば、特許文献１）。   In general, a two-stage compression rotary compressor is provided with an electric motor unit including a stator and a rotor and a rotary compression unit driven by a rotary shaft attached to the rotor of the electric motor unit. The first stage rotary compression part and the second stage rotary compression part are composed of a cylinder and a roller that rotates eccentrically in the cylinder, and the first stage rotation is made from the outside of the sealed container via the suction pipe. The refrigerant gas sucked into the compression unit is compressed to an intermediate pressure (first-stage discharge pressure) and then discharged into the hermetic container. The intermediate-pressure refrigerant gas is sucked into the second-stage rotary compression unit, and the high-pressure ( After being compressed to (second stage discharge pressure), it is discharged to the outside of the sealed container through the discharge pipe (for example, Patent Document 1).

上記構成の２段圧縮回転式コンプレッサは、例えば図５に示すように自動車用空調機の冷凍サイクルに組み込まれて使用される。この冷凍サイクルにおいて、冷媒ガスとしてＣＯ２ガスが用いられ、２段圧縮回転式コンプレッサＣで高圧に圧縮された冷媒ガスは、ガスクーラＡで放熱した後に熱交換器Ｂで冷やされ、次いで膨張弁Ｄで気液混合状態にされてエバポレータＥで蒸発する。この後、冷媒ガスはアキュームレータＦで気液分離され、前記熱交換器Ｂにて温められた後に前記２段圧縮回転式コンプレッサＣに戻される。このようなサイクルが繰り返して行われる。
特許第２５０７０４７号公報 The two-stage compression rotary compressor having the above configuration is used by being incorporated in a refrigeration cycle of an automotive air conditioner, for example, as shown in FIG. In this refrigeration cycle, CO 2 gas is used as the refrigerant gas. The refrigerant gas compressed to a high pressure by the two-stage compression rotary compressor C is radiated by the gas cooler A, cooled by the heat exchanger B, and then expanded by the expansion valve D. Then, it is brought into a gas-liquid mixed state and evaporated by the evaporator E. Thereafter, the refrigerant gas is separated into gas and liquid by the accumulator F, warmed by the heat exchanger B, and then returned to the two-stage compression rotary compressor C. Such a cycle is repeated.
Japanese Patent No. 25007047

上記従来の冷凍サイクルでは、比較的形状の大きい熱交換器Ｂ及びアキュームレータＦはそれぞれ別個独立した機器であって自動車のエンジンルームに配設するのに場所をとり、エンジンルームが狭い場合には設置し難くなり、又は設置できないといった問題があった。   In the conventional refrigeration cycle, the heat exchanger B and the accumulator F, which are relatively large in shape, are separate and independent devices and take up space for installation in the engine room of an automobile, and are installed when the engine room is small. It was difficult to install or could not be installed.

本発明は、このような従来技術の問題を解決するためになされ、２段圧縮回転式コンプレッサにアキュームレータの機能を付加すると共に、熱交換器を一体型に設けた構造のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサを提供することを目的とする。   The present invention has been made to solve the above-described problems of the prior art. The accumulator function is added to the two-stage compression / rotation compressor, and the heat exchanger is built in and integrated with the heat exchanger. An object is to provide an integrated horizontal compressor.

上記の目的を達成するための手段として、本発明の請求項１は、横置き外側密閉容器の内部に内側密閉容器を設けて二重構造とし、前記内側密閉容器内には電動機部と、この電動機部により駆動される第１段回転圧縮部及び第２段回転圧縮部とからなる回転圧縮部を設け、前記外側密閉容器の側部には冷媒ガスの戻し管を接続すると共に、この外側密閉容器内の上部空間に吸入管を設けて前記第１段回転圧縮部に接続し、外側密閉容器内の下部空間にオイル溜めを設け、前記第２段回転圧縮部には第１段回転圧縮部で圧縮され内側密閉容器内に吐出される中間圧の冷媒ガスを吸入する吸入管と、圧縮後の高圧冷媒ガスを外部に吐出するための吐出管を接続し、更に前記外側密閉容器内の上部空間に熱交換器を設けてなるアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサを特徴とする。   As means for achieving the above object, claim 1 of the present invention provides a double structure by providing an inner sealed container inside a laterally placed outer sealed container, and an electric motor part is provided in the inner sealed container. A rotary compression section comprising a first stage rotary compression section and a second stage rotary compression section driven by an electric motor section is provided, and a refrigerant gas return pipe is connected to the side of the outer sealed container, and the outer sealed section is sealed. A suction pipe is provided in the upper space in the container and connected to the first stage rotary compression part, an oil sump is provided in the lower space in the outer sealed container, and the first stage rotary compression part is provided in the second stage rotary compression part. A suction pipe that sucks in an intermediate pressure refrigerant gas that is compressed in and discharged into the inner sealed container, and a discharge pipe that discharges the compressed high-pressure refrigerant gas to the outside, and further connects the upper part in the outer sealed container Built-in accumulator with heat exchanger in space Wherein the compressor every fine heat exchanger-integrated horizontal.

本発明の請求項２は、請求項１記載のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサにおいて、前記熱交換器は、熱伝導率の高い材料からなるチューブで構成されていることを特徴とする。   Claim 2 of the present invention is the horizontal compressor with a built-in accumulator and integrated heat exchanger according to claim 1, wherein the heat exchanger is formed of a tube made of a material having high heat conductivity. To do.

本発明の請求項３は、請求項１記載のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサにおいて、前記熱交換器は、熱伝導率の高い材料からなる帯状体と、この帯状体の一方の端部に接続した入口側ヘッダ及び他方の端部に接続した出口側ヘッダとから構成され、前記帯状体の内部には複数の第１冷媒ガス流路と第２冷媒ガス流路とが隣接して並列状態に設けられ、前記第１冷媒ガス流路は前記入口側ヘッダ及び出口側ヘッダに連通し、前記第２冷媒ガス流路は前記外側密閉容器内の上部空間に開口していることを特徴とする。   According to a third aspect of the present invention, in the horizontal compressor with a built-in accumulator and an integrated heat exchanger according to the first aspect, the heat exchanger includes a strip made of a material having a high thermal conductivity, and one of the strips. An inlet-side header connected to the end and an outlet-side header connected to the other end, and a plurality of first refrigerant gas flow paths and second refrigerant gas flow paths are adjacent to each other inside the strip. The first refrigerant gas flow path communicates with the inlet-side header and the outlet-side header, and the second refrigerant gas flow path opens into an upper space in the outer sealed container. Features.

上記請求項１の発明によれば、外側密閉容器と内側密閉容器との間の空間部によりエバポレータから戻される気液混合状態の冷媒ガス（ＣＯ２冷媒ガス）を気液分離する機能（アキュームレータの機能）を行うことができ、外側密閉容器内の上部空間に設けた熱交換器によりガスクーラからの冷媒ガスを冷やすと共に、冷却後の冷媒ガスを膨張弁に供給することができる。これにより、２段圧縮回転式コンプレッサにアキュームレータが内蔵され、且つ熱交換器が内部に一体型となっているため、高さに余裕のない狭いエンジンルームであっても設置し易くなる。 According to the first aspect of the invention, the function (gas accumulator function) of separating the gas-liquid mixed refrigerant gas (CO 2 refrigerant gas) returned from the evaporator by the space between the outer sealed container and the inner sealed container is returned. Function), the refrigerant gas from the gas cooler can be cooled by the heat exchanger provided in the upper space in the outer sealed container, and the refrigerant gas after cooling can be supplied to the expansion valve. Thereby, since the accumulator is built in the two-stage compression rotary compressor and the heat exchanger is integrated in the inside, it is easy to install even in a narrow engine room having no height.

請求項２の発明によれば、外側密閉容器内の上部空間に熱伝導率の高い材料からなるチューブを設けることで熱交換器を容易に構成することができる。   According to invention of Claim 2, a heat exchanger can be easily comprised by providing the tube which consists of material with high heat conductivity in the upper space in an outer side airtight container.

請求項３の発明によれば、熱伝導率の高い材料からなる帯状体の内部に第１冷媒ガス流路（ガスクーラから出た冷媒ガスが通る）と、第２冷媒ガス流路（エバポレータからの戻し冷媒ガスが通る）とを隣接して設け、第１冷媒ガス流路に連通する入口側ヘッダ及び出口側ヘッダを帯状体の両端部に取り付けることで熱交換器を一体化した２段圧縮回転式コンプレッサを容易に構成することができる。   According to the invention of claim 3, the first refrigerant gas flow path (the refrigerant gas exiting from the gas cooler passes) and the second refrigerant gas flow path (from the evaporator) pass through the band made of a material having high thermal conductivity. Two-stage compression rotation in which the heat exchanger is integrated by attaching the inlet side header and the outlet side header communicating with the first refrigerant gas flow path to both ends of the belt-like body. A type compressor can be easily configured.

次に、本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの実施形態を添付図面に基づいて説明する。   Next, an embodiment of a horizontal compressor with a built-in accumulator and an integrated heat exchanger according to the present invention will be described with reference to the accompanying drawings.

添付図面中、図１は本発明に用いる２段圧縮回転式コンプレッサの概略断面図である。
図２は本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの実施形態を示すもので、（ａ）は模式的概略図、（ｂ）は（ａ）のＹ−Ｙ線概略断面図である。
図３は本発明に係るアキュームレータ内蔵及び熱交換器一体型コンプレッサを自動車用空調機の冷凍サイクルに組み込んだ例を示す回路図である。図４は本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの他の実施形態を示すもので、（ａ）は一部の概略断面図、（ｂ）は組み込まれる熱交換器の概略分解斜視図である。図５は従来のコンプレッサを自動車用空調機の冷凍サイクルに組み込んだ例を示す回路図である。 FIG. 1 is a schematic sectional view of a two-stage compression rotary compressor used in the present invention.
2A and 2B show an embodiment of a horizontal compressor with a built-in accumulator and a heat exchanger according to the present invention. FIG. 2A is a schematic schematic view, and FIG. 2B is a schematic cross-sectional view along line YY of FIG. It is.
FIG. 3 is a circuit diagram showing an example in which an accumulator built-in and heat exchanger integrated compressor according to the present invention is incorporated in a refrigeration cycle of an automotive air conditioner. FIG. 4 shows another embodiment of a horizontal compressor with a built-in accumulator and a heat exchanger according to the present invention, wherein (a) is a schematic sectional view of a part, and (b) is a schematic of a heat exchanger to be incorporated. It is a disassembled perspective view. FIG. 5 is a circuit diagram showing an example in which a conventional compressor is incorporated in a refrigeration cycle of an automotive air conditioner.

図１において、１は金属製の内側密閉容器であり、一端壁を有する円筒状の容器１ａとこの容器１ａの開口端部に溶接された椀状の蓋体１ｂとから構成されている。容器１ａ内の左方部には電動機部２が設けられ、右方部には回転圧縮部３が配設されている。   In FIG. 1, reference numeral 1 denotes a metal inner sealed container, which is composed of a cylindrical container 1a having one end wall and a bowl-shaped lid 1b welded to the open end of the container 1a. An electric motor unit 2 is provided on the left side in the container 1a, and a rotary compression unit 3 is provided on the right side.

上記電動機部２は、容器１ａの内壁に固定されたステータ２ａと、このステータ２ａの中心部に配置されたロータ２ｂとから構成され、ロータ２ｂの軸心部には回転軸４が固定されて右方に延設されている。又、上記蓋体１ｂの左端部にはターミナル５が貫通して固定され、このターミナル５とステータ２ａとがリード線５ａによって電気的に接続され、ステータ２ａに電力を供給してロータ２ｂを回転できるようにしてある。   The electric motor unit 2 includes a stator 2a fixed to the inner wall of the container 1a, and a rotor 2b disposed at the center of the stator 2a. A rotating shaft 4 is fixed to the axial center of the rotor 2b. It extends to the right. Further, a terminal 5 is fixed through the left end of the lid 1b. The terminal 5 and the stator 2a are electrically connected by a lead wire 5a, and power is supplied to the stator 2a to rotate the rotor 2b. I can do it.

上記回転圧縮部３は、第１段回転圧縮部３ａとその左側に配設されている第２段回転圧縮部３ｂとを有し、これらの間には仕切板６が介在しており、第１段回転圧縮部３ａの右側には第１支持部材７が添えられると共に、第２段回転圧縮部３ｂの左側には第２支持部材８が添えられ、これらの構成部材を貫通する通しボルト３ｃと、この通しボルト３ｃに螺合するナット３ｄとで締着することにより一体化されている。そして、前記回転軸４の延部は回転圧縮部３を貫通し、上記第１支持部材７と第２支持部材８とによって軸支持され、且つ第１段回転圧縮部３ａと第２段回転圧縮部３ｂにそれぞれ対応させて円形の第１偏心部４ａと第２偏心部４ｂとが設けられている。この第１偏心部４ａと第２偏心部４ｂとは、回転軸４を中心にして１８０°位相をずらしてある。   The rotary compression unit 3 includes a first-stage rotary compression unit 3a and a second-stage rotary compression unit 3b disposed on the left side of which a partition plate 6 is interposed, A first support member 7 is attached to the right side of the first-stage rotary compression unit 3a, and a second support member 8 is attached to the left side of the second-stage rotary compression unit 3b, and through bolts 3c penetrating these components. And a nut 3d that is screwed to the through bolt 3c. The extending portion of the rotary shaft 4 passes through the rotary compression portion 3 and is axially supported by the first support member 7 and the second support member 8, and the first stage rotary compression portion 3 a and the second stage rotary compression. A circular first eccentric portion 4a and a second eccentric portion 4b are provided corresponding to the portions 3b, respectively. The first eccentric portion 4a and the second eccentric portion 4b are shifted in phase by 180 ° about the rotating shaft 4.

上記第１段回転圧縮部３ａは、容器１ａの内壁に固定されている第１シリンダ９と、この第１シリンダ９の円形孔９ａの内周壁面に沿って偏心回転する環状の第１ローラ１０とを備え、この第１ローラ１０は前記回転軸４における第１偏心部４ａの外周壁面に嵌装されている。又、図示は省略したが、第１ローラ１０の外周壁面にはバネで付勢されている第１ベーンが常時当接し、第１シリンダ９の円形孔９ａ内を低圧室と高圧室とに区分している。   The first-stage rotary compression unit 3a includes a first cylinder 9 fixed to the inner wall of the container 1a and an annular first roller 10 that rotates eccentrically along the inner peripheral wall surface of the circular hole 9a of the first cylinder 9. The first roller 10 is fitted on the outer peripheral wall surface of the first eccentric portion 4 a of the rotating shaft 4. Although not shown, the first vane urged by a spring is always in contact with the outer peripheral wall surface of the first roller 10, and the inside of the circular hole 9a of the first cylinder 9 is divided into a low pressure chamber and a high pressure chamber. doing.

上記第２段回転圧縮部３ｂは、第１段回転圧縮部３ａと同様に、容器１ａの内壁に固定されている第２シリンダ１１と、この第２シリンダ１１の円形孔１１ａの内周壁面に沿って偏心回転する環状の第２ローラ１２とを備え、この第２ローラ１２は前記回転軸４における第２偏心部４ｂの外周壁面に嵌装されている。又、図示は省略したが、第２ローラ１２の外周壁面にはバネで付勢されている第２ベーンが常時当接し、第２シリンダ１１の円形孔１１ａ内を低圧室と高圧室とに区分している。   Similar to the first stage rotary compression part 3a, the second stage rotary compression part 3b is provided on the inner wall surface of the second cylinder 11 fixed to the inner wall of the container 1a and the circular hole 11a of the second cylinder 11. And an annular second roller 12 that rotates eccentrically along the outer circumferential wall surface of the second eccentric portion 4 b of the rotating shaft 4. Although not shown, the second vane 12 urged by a spring is always in contact with the outer peripheral wall surface of the second roller 12, and the circular hole 11a of the second cylinder 11 is divided into a low pressure chamber and a high pressure chamber. doing.

１３は第１段回転圧縮部３ａに冷媒ガス（本実施例ではＣＯ２冷媒ガス）を供給するための吸入管であり、前記容器１ａの上壁に溶接され、前記第１シリンダ９の吸入ポート９ｂに連通している。この吸入ポート９ｂは前記円形孔９ａ内の低圧室入口に連通している。又、図示は省略したが、第１シリンダ９には第１段回転圧縮部３ａで圧縮した中間圧の冷媒ガスを内側密閉容器１内に吐出するための吐出ポートが設けられている。 Reference numeral 13 denotes a suction pipe for supplying refrigerant gas (CO 2 refrigerant gas in the present embodiment) to the first stage rotary compression unit 3a, which is welded to the upper wall of the container 1a and is connected to the suction port of the first cylinder 9. It communicates with 9b. The suction port 9b communicates with the low pressure chamber inlet in the circular hole 9a. Although not shown, the first cylinder 9 is provided with a discharge port for discharging the intermediate-pressure refrigerant gas compressed by the first stage rotary compression unit 3a into the inner sealed container 1.

１４は第２段回転圧縮部３ｂで圧縮した高圧の冷媒ガスを外部に吐出するための吐出管であり、容器１ａの上壁を貫通して溶接固定されているスリーブ１５に挿着され、前記第２シリンダ１１の吐出ポート１１ｃに連通している。この吐出ポート１１ｃは前記円形孔１１ａの高圧室出口に連通している。又、第２シリンダ１１には前記内側密閉容器１内に吐出された中間圧の冷媒ガスを吸入するための小形吸入管１３ａを設けて吸入ポート１１ｂに接続し、この吸入ポート１１ｂは前記円形孔１１ａの低圧室入口に連通している。   14 is a discharge pipe for discharging the high-pressure refrigerant gas compressed by the second-stage rotary compression unit 3b to the outside, and is inserted into a sleeve 15 that is welded and fixed through the upper wall of the container 1a. The second cylinder 11 communicates with the discharge port 11c. The discharge port 11c communicates with the high pressure chamber outlet of the circular hole 11a. The second cylinder 11 is provided with a small suction pipe 13a for sucking the intermediate pressure refrigerant gas discharged into the inner sealed container 1, and is connected to the suction port 11b. The suction port 11b is connected to the circular hole. 11a communicates with the low pressure chamber inlet.

上記構成の２段回転圧縮式のコンプレッサは、図２（ａ）、（ｂ）に示すように金属製の外側密閉容器１６の内部に複数のステー又はリブ等の取付部材１７を介して装着される。外側密閉容器１６は、一端壁を有する円筒状の容器１６ａとこの容器１６ａの開口端部に溶接される蓋体１６ｂとから構成されており、蓋体１６ｂには戻し管１８が接続され、容器１６ａの底部には液化冷媒を含むオイル溜め１９Ａが設けられている。このオイル溜め１９Ａには前記第１段回転圧縮部３ａに設けたオイル吸入口３ｅが開口しており、このオイル吸入口３ｅは前記第１シリンダ９に設けたオイル通路（図略）を介して前記吸入管１３に連通している。この吸入管１３による冷媒ガスの吸入に伴って、オイル溜め１９Ａのオイルの一部がオイル吸入口３ｅより吸入され、オイル通路を通って冷媒ガスと共に第１段回転圧縮部３ａに供給される。又、前記内側密閉容器１内には公知のオイル汲み上げ手段２０を取り付けて、内側密閉容器１の底部のオイル溜め１９Ｂからオイルを汲み上げて前記回転軸４に供給できるようにする。尚、前記吐出管１４は容器１６ａの上壁を貫通して外部に突出させ、図示はされていないが前記ターミナル５は蓋体１６ｂを貫通して外部に突出させておく。   As shown in FIGS. 2A and 2B, the two-stage rotary compression compressor configured as described above is mounted inside a metal outer sealed container 16 via a plurality of mounting members 17 such as stays or ribs. The The outer sealed container 16 includes a cylindrical container 16a having one end wall and a lid body 16b welded to the open end of the container 16a, and a return pipe 18 is connected to the lid body 16b. An oil sump 19A containing a liquefied refrigerant is provided at the bottom of 16a. The oil sump 19A has an oil suction port 3e provided in the first stage rotary compression portion 3a. The oil suction port 3e is connected to an oil passage (not shown) provided in the first cylinder 9. It communicates with the suction pipe 13. Along with the suction of the refrigerant gas through the suction pipe 13, a part of the oil in the oil reservoir 19A is sucked from the oil suction port 3e and supplied to the first stage rotary compression unit 3a along with the refrigerant gas through the oil passage. A known oil pumping means 20 is installed in the inner sealed container 1 so that oil can be pumped from the oil reservoir 19B at the bottom of the inner sealed container 1 and supplied to the rotary shaft 4. The discharge pipe 14 passes through the upper wall of the container 16a and protrudes to the outside. Although not shown, the terminal 5 passes through the lid body 16b and protrudes to the outside.

上記外側密閉容器１６と内側密閉容器との間の空間Ｓの上部には、熱交換器２１が一体的に設けられている。この熱交換器２１は屈曲形成したマイクロチューブ２１ａを空間Ｓ上部に配設し、その両端部を容器１６ａの外部に突出させて一端側を入口１６ｂ、他端側を出口１６ｃとした構成のものである。マイクロチューブ２１ａはアルミニウム又は銅等の熱伝導率の高い材料で形成され、通過する冷媒ガスの流速を速めるために内径は小さく（例えば０．７〜１．５ｍｍ）してある。   A heat exchanger 21 is integrally provided in the upper part of the space S between the outer sealed container 16 and the inner sealed container. This heat exchanger 21 has a configuration in which a bent microtube 21a is disposed in the upper portion of the space S, and both end portions thereof are projected to the outside of the container 16a so that one end side is an inlet 16b and the other end side is an outlet 16c. It is. The microtube 21a is formed of a material having high thermal conductivity such as aluminum or copper, and has a small inner diameter (for example, 0.7 to 1.5 mm) in order to increase the flow rate of the refrigerant gas passing therethrough.

以上の構成によって、アキュームレータ内蔵及び熱交換器一体型横置きコンプレッサＣ１が形成される。このアキュームレータ内蔵及び熱交換器一体型コンプレッサＣ１は、前記ターミナル５を介して電動機部２のステータ２ａに通電するとロータ２ｂが回転し、この回転により回転軸４の第１偏心部４ａに嵌装された第１ローラ１０及び第２偏心部４ｂに嵌装された第２ローラ１２が、第１シリンダ９と第２シリンダ１１内をそれぞれ偏心回転することでガス圧縮が行われる。   With the above configuration, a horizontal compressor C1 with a built-in accumulator and a heat exchanger is formed. In this accumulator-integrated and heat exchanger-integrated compressor C1, when the stator 2a of the electric motor unit 2 is energized through the terminal 5, the rotor 2b rotates, and this rotation is fitted into the first eccentric portion 4a of the rotating shaft 4. The second roller 12 fitted to the first roller 10 and the second eccentric portion 4b rotates eccentrically in the first cylinder 9 and the second cylinder 11, respectively, so that gas compression is performed.

上記アキュームレータ内蔵及び熱交換器一体型コンプレッサＣ１は、図３に示すように自動車用空調機の冷凍サイクルに組み込んで使用される。前記吐出管１４の端部はガスクーラＡの入口に接続され、戻し管１８の端部はエバポレータＥの出口に接続され、熱交換器２１の入口（マイクロチューブ２１ａの入口２１ｂ）は連結管２２を介してガスクーラＡの出口に接続されると共に、出口（マイクロチューブ２１ａの出口２１ｃ）は連結管２３を介して膨張弁Ｄの入口に接続される。   The accumulator built-in and heat exchanger integrated compressor C1 is used by being incorporated in a refrigeration cycle of an automotive air conditioner as shown in FIG. The end of the discharge pipe 14 is connected to the inlet of the gas cooler A, the end of the return pipe 18 is connected to the outlet of the evaporator E, and the inlet of the heat exchanger 21 (the inlet 21b of the microtube 21a) is connected to the connecting pipe 22. And the outlet (the outlet 21 c of the microtube 21 a) is connected to the inlet of the expansion valve D via the connecting pipe 23.

前記内側密閉容器１内の回転圧縮部３にて２段圧縮された冷媒ガスは、吐出管１４を通ってガスクーラＡに流入し、ここで放熱して外気温近くまで冷却される。ガスクーラＡで冷却された冷媒ガスは、連結管２２を通って前記熱交換器２１のマイクロチューブ２１ａ内に流入し、後記するエバポレータＥから戻される冷媒ガスとの間で熱交換して約３５℃に冷やされる。熱交換器２１で冷却された冷媒ガスは、連結管２３を通って膨張弁Ｄに流入し、ここで冷やされて気液混合状態にされた後、エバポレータＥで蒸発する。エバポレータＥで蒸発した冷媒ガスは、戻し管１８を通って内側密閉容器１と外側密閉容器１６との間の空間Ｓ部に戻される。   The refrigerant gas compressed in two stages by the rotary compression unit 3 in the inner sealed container 1 flows into the gas cooler A through the discharge pipe 14, where it dissipates heat and is cooled to near ambient temperature. The refrigerant gas cooled by the gas cooler A flows into the microtube 21a of the heat exchanger 21 through the connecting pipe 22, and exchanges heat with the refrigerant gas returned from the evaporator E, which will be described later. Chilled. The refrigerant gas cooled by the heat exchanger 21 flows into the expansion valve D through the connecting pipe 23, where it is cooled to a gas-liquid mixed state, and then evaporated by the evaporator E. The refrigerant gas evaporated by the evaporator E is returned to the space S between the inner sealed container 1 and the outer sealed container 16 through the return pipe 18.

この空間Ｓ部に戻された冷媒ガスは約５℃になっており、ここで気液分離され戻り冷媒ガス中に含まれているオイル及び蒸発しきれない冷媒は液化して前記オイル溜め１９Ａに落下し、冷媒ガスはオイル溜め１９Ａより上方の領域に溜まる。即ち、空間Ｓ部はアキュームレータＦ１の機能を果たすことになる。更に、この空間Ｓ部の戻り冷媒ガスは、前記熱交換器２１と接しているため、前記のようにマイクロチューブ２１ａを通過する冷媒ガスとの間で熱交換が行われる。その結果、マイクロチューブ２１ａを通過する冷媒ガスは前記のように約３５℃に冷やされ、空間Ｓ部の戻り冷媒ガスは約１５℃に温められる。このようにして、戻り冷媒ガスを温めるのは冷媒ガス中に僅かに残存する液分を乾燥させるためであり、マイクロガスチューブ２１ａの冷媒ガスを冷やすのは冷媒ガス（ＣＯ２冷媒ガス）の臨界温度約３１℃に近付けて冷凍サイクルの性能を高めるためである。 The refrigerant gas returned to the space S is about 5 ° C., and the oil contained in the return refrigerant gas that has been gas-liquid separated and the refrigerant that cannot be evaporated are liquefied and stored in the oil reservoir 19A. The refrigerant gas falls and accumulates in an area above the oil reservoir 19A. That is, the space S portion fulfills the function of the accumulator F1. Further, since the return refrigerant gas in the space S is in contact with the heat exchanger 21, heat exchange is performed with the refrigerant gas passing through the microtube 21a as described above. As a result, the refrigerant gas passing through the microtube 21a is cooled to about 35 ° C. as described above, and the return refrigerant gas in the space S is warmed to about 15 ° C. In this way, the return refrigerant gas is warmed in order to dry the liquid that remains slightly in the refrigerant gas, and the refrigerant gas in the micro gas tube 21a is cooled by the criticality of the refrigerant gas (CO 2 refrigerant gas). This is to increase the performance of the refrigeration cycle by bringing the temperature close to about 31 ° C.

熱交換器２１により温められた冷媒ガスは、前記吸入管１３により吸入されて第１段回転圧縮部３ａに供給される。この第１段回転圧縮部３ａに供給された冷媒ガスは、前記第１シリンダ９の吸入ポート９ｂから円形孔９ａの低圧室に吸入され、この円形孔９ａ内を偏心回転する第１ローラ１０により圧縮され、高圧室から吐出ポートを経て内側密閉容器１内に吐出される。第１段回転圧縮部３ａで圧縮された冷媒ガスは、中間圧（３〜４ＭＰａ）まで昇圧される。   The refrigerant gas warmed by the heat exchanger 21 is sucked through the suction pipe 13 and supplied to the first stage rotary compression unit 3a. The refrigerant gas supplied to the first stage rotary compression unit 3a is sucked into the low pressure chamber of the circular hole 9a from the suction port 9b of the first cylinder 9, and is eccentrically rotated in the circular hole 9a by the first roller 10. It is compressed and discharged from the high-pressure chamber into the inner sealed container 1 through the discharge port. The refrigerant gas compressed by the first stage rotary compression unit 3a is increased to an intermediate pressure (3-4 MPa).

内側密閉容器１内に吐出された中間圧の冷媒ガスは、前記小形吸入管１３ａから吸入されて第２段回転圧縮部３ｂに供給される。小形吸入管１３ａから吸入された中間圧の冷媒ガスは、前記第２シリンダ１１の吸入ポート１１ｂから円形孔１１ａの低圧室に吸入され、この円形孔１１ａ内を偏心回転する第２ローラ１２により圧縮されて高圧室から吐出ポート１１ｃに吐出される。第２段回転圧縮部３ｂで圧縮された冷媒ガスは、高圧（１０〜１２ＭＰａ）まで昇圧される。そして、吐出ポート１１ｃに吐出された高圧の冷媒ガスは、前記吐出管１４内に流入して外部に吐出されガスクーラＡに供給される。   The intermediate-pressure refrigerant gas discharged into the inner sealed container 1 is sucked from the small suction pipe 13a and supplied to the second stage rotary compression unit 3b. The intermediate-pressure refrigerant gas sucked from the small suction pipe 13a is sucked into the low pressure chamber of the circular hole 11a from the suction port 11b of the second cylinder 11, and is compressed by the second roller 12 that rotates eccentrically in the circular hole 11a. Then, it is discharged from the high pressure chamber to the discharge port 11c. The refrigerant gas compressed by the second stage rotary compression unit 3b is pressurized to a high pressure (10 to 12 MPa). The high-pressure refrigerant gas discharged to the discharge port 11 c flows into the discharge pipe 14 and is discharged to the outside and supplied to the gas cooler A.

前記回転圧縮部３での冷媒ガス圧縮中に、前記オイル汲み上げ手段２０により内側密閉容器１内のオイル溜め１９Ｂからオイルが汲み上げられて回転軸４に供給される。この回転軸４にはオイル通路（図略）が設けられていてオイルを移行させ、回転軸４の軸受け部である前記第１支持部材７と第２支持部材８、及び回転圧縮部３の回転部にオイルを供給して潤滑する。潤滑後のオイルは回転圧縮部３から排出されてオイル溜め１９Ｂに落下する。オイル溜め１９ｂのオイル量を調整するために、底部にオイル戻し孔（図略）を設けて前記オイル溜め１９Ａに適量戻すようにすると好ましい。   During the compression of the refrigerant gas in the rotary compression unit 3, the oil is drawn up from the oil reservoir 19 </ b> B in the inner sealed container 1 by the oil pumping means 20 and supplied to the rotary shaft 4. The rotation shaft 4 is provided with an oil passage (not shown) to transfer oil, and the first support member 7 and the second support member 8 that are bearing portions of the rotation shaft 4 and the rotation compression portion 3 rotate. Lubricate by supplying oil to the part. The lubricated oil is discharged from the rotary compression unit 3 and falls into the oil reservoir 19B. In order to adjust the amount of oil in the oil reservoir 19b, it is preferable to provide an oil return hole (not shown) at the bottom so as to return an appropriate amount to the oil reservoir 19A.

図４（ａ）、（ｂ）は、本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの他の実施形態を示すものであり、前記実施形態と同じ構成部材は同一符号を付けてそれらの詳しい説明は省略する。本実施形態では、外側密閉容器１６の空間Ｓ上部に配設する熱交換器２４に特徴を有するものである。   4 (a) and 4 (b) show another embodiment of a horizontal compressor with a built-in accumulator and a heat exchanger according to the present invention, and the same components as those in the above embodiment are given the same reference numerals. Detailed description thereof will be omitted. In the present embodiment, the heat exchanger 24 disposed in the upper portion of the space S of the outer sealed container 16 is characterized.

この熱交換器２４は、外側密閉容器１６と内側密閉容器１との間の上部空間の断面形状に合致させて断面湾曲状に形成したアルミニウム等の熱伝導率の高い材料からなる帯状体２５と、この帯状体２５の端部に取り付けられる湾曲状の入口側ヘッダ２６及び出口側ヘッダ２７とから構成され、帯状体２５の内部には複数の第１冷媒ガス流路２５ａと第２冷媒ガス流路２５ｂとが隣接して並列状態に設けられ、前記第１冷媒ガス流路２５ａは前記入口側ヘッダ２６及び出口側ヘッダ２７に連通し、前記第２冷媒ガス流路２５ｂは前記空間Ｓ上部に開口している。冷媒ガス流路２５ａ、２５ｂは、通過する冷媒ガスの流速を速めるために内径を小さく（例えば、０．７〜１．５ｍｍ）形成してある。   The heat exchanger 24 includes a belt-like body 25 made of a material having high thermal conductivity such as aluminum, which is formed in a curved cross section so as to match the cross sectional shape of the upper space between the outer sealed container 16 and the inner sealed container 1. In addition, the belt-like body 25 includes a curved inlet-side header 26 and an outlet-side header 27 attached to the end of the belt-like body 25, and a plurality of first refrigerant gas flow paths 25 a and second refrigerant gas flows are formed inside the belt-like body 25. The first refrigerant gas flow path 25a communicates with the inlet side header 26 and the outlet side header 27, and the second refrigerant gas flow path 25b is formed above the space S. It is open. The refrigerant gas flow paths 25a and 25b are formed with a small inner diameter (for example, 0.7 to 1.5 mm) in order to increase the flow velocity of the refrigerant gas that passes therethrough.

上記入口側ヘッダ２６及び出口側ヘッダ２７は、いずれも両端が閉塞された円筒状を呈しており、前記帯状体２５の第１冷媒ガス流路２５ａに対応する複数の小孔２６ａ、２７ａが側部にそれぞれ設けられている。この入口側ヘッダ２６及び出口側ヘッダ２７は、複数の小孔２６ａ、２７ａがそれぞれ帯状体２５の第１冷媒ガス流路２５ａの開口端部に合致するようにして帯状体２５の端部にそれぞれ溶接等により固定される。又、前記外側密閉容器１６の容器１６ａの上壁に供給管２６ｂと排出管２７ｂを取り付け、供給管２６ｂの下端部は入口側ヘッダ２６に接続して連通させ、排出管２７ｂの下端部は出口側ヘッダ２７に接続して連通させてある。これにより、供給管２６ａから冷媒ガスを供給すると、入口側ヘッダ２６内に流入すると共に第１冷媒ガス流路２５ａに分流し、この第１冷媒ガス流路２５ａを通過して出口側ヘッダ２７内に合流すると共に、排出管２７ｂから外部に排出される。   Each of the inlet side header 26 and the outlet side header 27 has a cylindrical shape with both ends closed, and a plurality of small holes 26a, 27a corresponding to the first refrigerant gas flow path 25a of the strip 25 are on the side. Provided in each part. The inlet-side header 26 and the outlet-side header 27 are respectively provided at the end portions of the strip-shaped body 25 such that the plurality of small holes 26 a, 27 a respectively match the opening end portions of the first refrigerant gas flow paths 25 a of the strip-shaped body 25. It is fixed by welding or the like. Further, a supply pipe 26b and a discharge pipe 27b are attached to the upper wall of the container 16a of the outer sealed container 16, the lower end of the supply pipe 26b is connected to and communicated with the inlet side header 26, and the lower end of the discharge pipe 27b is the outlet. It is connected to the side header 27 for communication. Thus, when the refrigerant gas is supplied from the supply pipe 26a, the refrigerant gas flows into the inlet header 26 and is diverted to the first refrigerant gas channel 25a, passes through the first refrigerant gas channel 25a, and enters the outlet header 27. And discharged to the outside through the discharge pipe 27b.

以上の構成によって、アキュームレータ内蔵及び熱交換器一体型横置きコンプレッサＣ２が形成される。このアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサＣ２は、前記と同様に自動車用空調機の冷凍サイクルに組み込んで使用される。冷凍サイクルの回路構成は前記実施形態の場合（図３）と同じであるからその詳しい説明は省略する。   With the above configuration, a horizontal compressor C2 with a built-in accumulator and an integrated heat exchanger is formed. The accumulator built-in and heat exchanger integrated horizontal compressor C2 is used by being incorporated in a refrigeration cycle of an automotive air conditioner, as described above. Since the circuit configuration of the refrigeration cycle is the same as that in the above embodiment (FIG. 3), detailed description thereof is omitted.

前記回転圧縮部３にて２段圧縮された冷媒ガスは、吐出管１４から吐出されてガスクーラＡに流入し、このガスクーラＡから熱交換器２４、膨張弁Ｄ、エバポレータＥを経て戻し管１８から内側密閉容器１と外側密閉容器１６との間の空間Ｓ部に戻される。そして、ガスクーラＡからの冷媒ガスは、前記供給管２６ｂを介して熱交換器２４の入口側ヘッダ２６内に流入し、第１冷媒ガス流路２５ａを流れる際に、エバポレータＥからの戻り冷媒ガスが第２冷媒ガス流路２５ｂを流れることから熱交換して冷却される。冷却された冷媒ガスは、出口側ヘッダ２７内に流入し、この出口側ヘッダ２７から排出管２７ｂを介して外部に排出され膨張弁Ｄに供給される。   The refrigerant gas compressed in two stages by the rotary compression unit 3 is discharged from the discharge pipe 14 and flows into the gas cooler A. From the gas cooler A, the heat exchanger 24, the expansion valve D, and the evaporator E are passed through the return pipe 18. The space S between the inner sealed container 1 and the outer sealed container 16 is returned. Then, the refrigerant gas from the gas cooler A flows into the inlet header 26 of the heat exchanger 24 through the supply pipe 26b, and returns to the refrigerant gas from the evaporator E when flowing through the first refrigerant gas passage 25a. Since it flows through the second refrigerant gas flow path 25b, it is cooled by exchanging heat. The cooled refrigerant gas flows into the outlet header 27 and is discharged from the outlet header 27 to the outside via the discharge pipe 27 b and supplied to the expansion valve D.

又、エバポレータＥからの戻り冷媒ガスは、前記と同様に内側密閉容器１と外側密閉容器１６との間の空間Ｓ部で気液分離され、液化オイルは液化冷媒と共にオイル溜め１９Ａに落下し、冷媒ガスはオイル溜め１９Ａより上方の領域に溜まる。即ち、空間Ｓ部はアキュームレータＦ１の機能を果たすことになる。更に、この空間Ｓ部の戻り冷媒ガスは、前記のように熱交換器２４の帯状体２５における第２冷媒ガス流路２５ｂ内に流入し、前記第１冷媒ガス流路２５ａ内を通過する冷媒ガスとの間で熱交換が行われる。その結果、前記と同様に熱交換器２４を通過する冷媒ガスは約３５℃に冷やされ、空間Ｓ部の戻り冷媒ガスは約１５℃に温められる。   In addition, the return refrigerant gas from the evaporator E is gas-liquid separated in the space S between the inner sealed container 1 and the outer sealed container 16 in the same manner as described above, and the liquefied oil falls into the oil reservoir 19A together with the liquefied refrigerant, The refrigerant gas collects in a region above the oil reservoir 19A. That is, the space S portion fulfills the function of the accumulator F1. Further, the return refrigerant gas in the space S part flows into the second refrigerant gas passage 25b in the strip 25 of the heat exchanger 24 as described above, and passes through the first refrigerant gas passage 25a. Heat exchange is performed with the gas. As a result, similarly to the above, the refrigerant gas passing through the heat exchanger 24 is cooled to about 35 ° C., and the return refrigerant gas in the space S is warmed to about 15 ° C.

温められた戻り冷媒ガスは、熱交換器２４の帯状体２５から空間Ｓの後方上部に排出され、前記吸入管１３により吸入されて第１段回転圧縮部３ａに供給される。第１段回転圧縮部３ａに供給された冷媒ガスは、前記第１シリンダ９の吸入ポート９ｂから円形孔９ａの低圧室に吸入され、この円形孔９ａ内を偏心回転する第１ローラ１０により圧縮され、高圧室から吐出ポートを経て内側密閉容器１内に吐出される。この第１段回転圧縮部３ａで圧縮された冷媒ガスは、中間圧（３〜４ＭＰａ）まで昇圧される。   The warmed return refrigerant gas is discharged from the strip 25 of the heat exchanger 24 to the upper rear part of the space S, is sucked in by the suction pipe 13, and is supplied to the first stage rotary compression unit 3a. The refrigerant gas supplied to the first stage rotary compression unit 3a is sucked into the low pressure chamber of the circular hole 9a from the suction port 9b of the first cylinder 9, and is compressed by the first roller 10 that rotates eccentrically in the circular hole 9a. Then, it is discharged from the high-pressure chamber through the discharge port into the inner sealed container 1. The refrigerant gas compressed by the first stage rotary compression unit 3a is increased to an intermediate pressure (3-4 MPa).

内側密閉容器１内に吐出された中間圧の冷媒ガスは、前記小形吸入管１３ａから吸入されて第２段回転圧縮部３ｂに供給される。小形吸入管１３ａから吸入された中間圧の冷媒ガスは、前記第２シリンダ１１の吸入ポート１１ｂから円形孔１１ａの低圧室に吸入され、この円形孔１１ａ内を偏心回転する第２ローラ１２により圧縮されて高圧室から吐出ポート１１ｃに吐出される。この第２段回転圧縮部３ｂで圧縮された冷媒ガスは、高圧（１０〜１２ＭＰａ）まで昇圧される。そして、吐出ポート１１ｃに吐出された高圧の冷媒ガスは、前記吐出管１４内に流入して外部に吐出されガスクーラＡに供給される。   The intermediate-pressure refrigerant gas discharged into the inner sealed container 1 is sucked from the small suction pipe 13a and supplied to the second stage rotary compression unit 3b. The intermediate-pressure refrigerant gas sucked from the small suction pipe 13a is sucked into the low pressure chamber of the circular hole 11a from the suction port 11b of the second cylinder 11, and is compressed by the second roller 12 that rotates eccentrically in the circular hole 11a. Then, it is discharged from the high pressure chamber to the discharge port 11c. The refrigerant gas compressed by the second stage rotary compression unit 3b is increased to a high pressure (10 to 12 MPa). The high-pressure refrigerant gas discharged to the discharge port 11 c flows into the discharge pipe 14 and is discharged to the outside and supplied to the gas cooler A.

本発明によるアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサは、特に自動車用空調機に適したものであるが、これに限定されずに一般の空調機、冷凍・冷蔵装置の冷凍サイクル用コンプレッサとして十分適用できるものである。   The horizontal compressor with a built-in accumulator and a heat exchanger according to the present invention is particularly suitable for an automotive air conditioner, but is not limited thereto, and is used as a compressor for a refrigeration cycle of a general air conditioner or a refrigeration / refrigeration apparatus. It can be applied sufficiently.

本発明に用いる２段圧縮回転式コンプレッサの概略断面図である。It is a schematic sectional drawing of the two-stage compression rotation type compressor used for this invention. 本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの実施形態を示すもので、（ａ）は模式的概略図、（ｂ）は（ａ）のＹ−Ｙ線概略断面図である。BRIEF DESCRIPTION OF THE DRAWINGS Embodiment of the horizontal compressor with a built-in accumulator and a heat exchanger which concerns on this invention is shown, (a) is typical schematic, (b) is a YY line schematic sectional drawing of (a). 本発明に係るアキュームレータ内蔵及び熱交換器一体型コンプレッサを自動車用空調機の冷凍サイクルに組み込んだ例を示す回路図である。1 is a circuit diagram showing an example in which an accumulator built-in and heat exchanger integrated compressor according to the present invention is incorporated in a refrigeration cycle of an automotive air conditioner. 本発明に係るアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサの他の実施形態を示すもので、（ａ）は一部の概略断面図、（ｂ）は組み込まれる熱交換器の概略分解斜視図である。The other embodiment of a horizontal compressor with a built-in accumulator and a heat exchanger according to the present invention is shown, (a) is a schematic sectional view of a part, (b) is a schematic exploded perspective view of a heat exchanger to be incorporated. It is. 従来のコンプレッサを自動車用空調機の冷凍サイクルに組み込んだ例を示す回路図である。It is a circuit diagram which shows the example which integrated the conventional compressor in the refrigerating cycle of the air conditioner for motor vehicles.

符号の説明Explanation of symbols

１ 内側密閉容器
２ 電動機部
３ 回転圧縮部
３ａ 第１段回転圧縮部
３ｂ 第２段回転圧縮部
４ 回転軸
５ ターミナル
９ 第１シリンダ
１０ 第１ローラ
１１ 第２シリンダ
１２ 第２ローラ
１３ 吸入管
１４ 吐出管
１６ 外側密閉容器
１８ 戻し管
１９Ａ、１９Ｂ オイル溜め
２１ 熱交換器
２４ 熱交換器
２５ 帯状体
２５ａ 第１冷媒ガス流路
２５ｂ 第２冷媒ガス流路
２６ 入口側ヘッダ
２７ 出口側ヘッダ DESCRIPTION OF SYMBOLS 1 Inner airtight container 2 Electric motor part 3 Rotation compression part 3a 1st stage rotation compression part 3b 2nd stage rotation compression part 4 Rotating shaft 5 Terminal 9 1st cylinder 10 1st roller 11 2nd cylinder 12 2nd roller 13 Intake pipe 14 Discharge pipe 16 Outer airtight container 18 Return pipes 19A and 19B Oil reservoir 21 Heat exchanger 24 Heat exchanger 25 Strip 25a First refrigerant gas flow path 25b Second refrigerant gas flow path 26 Inlet side header 27 Outlet side header

Claims (3)

横置き外側密閉容器の内部に内側密閉容器を設けて二重構造とし、前記内側密閉容器内には電動機部と、この電動機部により駆動される第１段回転圧縮部及び第２段回転圧縮部とからなる回転圧縮部を設け、前記外側密閉容器の側部には冷媒ガスの戻し管を接続すると共に、この外側密閉容器内の上部空間に吸入管を設けて前記第１段回転圧縮部に接続し、外側密閉容器内の下部空間に液化冷媒を含むオイル溜めを設け、前記第２段回転圧縮部には第１段回転圧縮部で圧縮され内側密閉容器内に吐出される中間圧の冷媒ガスを吸入する吸入管と、圧縮後の高圧冷媒ガスを外部に吐出するための吐出管を接続し、更に前記外側密閉容器内の上部空間に熱交換器を設けてなることを特徴とするアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサ。   An inner airtight container is provided inside the horizontally placed outer airtight container to form a double structure, and an electric motor part, a first stage rotary compression part and a second stage rotary compression part driven by the electric motor part are provided in the inner airtight container. And a refrigerant gas return pipe is connected to the side portion of the outer sealed container, and a suction pipe is provided in the upper space in the outer sealed container to provide the first stage rotary compression section. An oil reservoir containing a liquefied refrigerant is provided in the lower space in the outer sealed container, and the second-stage rotary compression section is compressed by the first-stage rotary compression section and is discharged into the inner sealed container. An accumulator comprising: a suction pipe for sucking gas; a discharge pipe for discharging compressed high-pressure refrigerant gas to the outside; and a heat exchanger provided in an upper space in the outer sealed container Built-in and heat exchanger integrated horizontal installation Suppressor. 前記熱交換器は、熱伝導率の高い材料からなるチューブで構成されていることを特徴とする請求項１記載のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサ。   2. The horizontal compressor with a built-in accumulator and a heat exchanger according to claim 1, wherein the heat exchanger comprises a tube made of a material having high thermal conductivity. 前記熱交換器は、熱伝導率の高い材料からなる帯状体と、この帯状体の一方の端部に接続した入口側ヘッダ及び他方の端部に接続した出口側ヘッダとから構成され、前記帯状体の内部には複数の第１冷媒ガス流路と第２冷媒ガス流路とが隣接して並列状態に設けられ、前記第１冷媒ガス流路は前記入口側ヘッダ及び出口側ヘッダに連通し、前記第２冷媒ガス流路は前記外側密閉容器内の上部空間に開口していることを特徴とする請求項１記載のアキュームレータ内蔵及び熱交換器一体型横置きコンプレッサ。   The heat exchanger is composed of a band-shaped body made of a material having high thermal conductivity, an inlet-side header connected to one end of the band-shaped body, and an outlet-side header connected to the other end. A plurality of first refrigerant gas passages and second refrigerant gas passages are provided adjacent to each other in parallel in the body, and the first refrigerant gas passages communicate with the inlet side header and the outlet side header. 2. The horizontal compressor with a built-in accumulator and a heat exchanger according to claim 1, wherein the second refrigerant gas flow path opens into an upper space in the outer sealed container.
JP2003385646A 2003-11-14 2003-11-14 Heat exchanger integral type horizontal compressor with built-in accumulator Pending JP2005146987A (en)

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USD917036S1 (en) 2018-02-20 2021-04-20 Dometic Sweden Ab Air distribution box
USD1006977S1 (en) 2018-02-20 2023-12-05 Dometic Sweden Ab Air distribution box
US11376925B2 (en) 2018-04-16 2022-07-05 Dometic Sweden Ab Air distribution apparatus
US11760167B2 (en) 2018-04-16 2023-09-19 Dometic Sweden Ab Air distribution apparatus
WO2019229706A1 (en) * 2018-05-31 2019-12-05 Dometic Sweden Ab Air conditioner for a vehicle
CN112203881A (en) * 2018-05-31 2021-01-08 多美达瑞典有限公司 Air conditioner for vehicle
CN108916006B (en) * 2018-08-01 2023-08-15 珠海格力电器股份有限公司 Compressor
CN108916006A (en) * 2018-08-01 2018-11-30 珠海格力电器股份有限公司 Compressor with a compressor housing having a plurality of compressor blades
CN109113993A (en) * 2018-09-04 2019-01-01 珠海凌达压缩机有限公司 Horizontal compressor
CN112145434A (en) * 2019-06-26 2020-12-29 Bsh家用电器有限公司 Compressor and household appliance
EP3757482A1 (en) * 2019-06-26 2020-12-30 BSH Hausgeräte GmbH Compressor and household appliance
US20220307500A1 (en) * 2019-09-17 2022-09-29 Hanon Systems Compressor module
JP2022548720A (en) * 2019-09-17 2022-11-21 ハンオン システムズ compressor module
WO2021117141A1 (en) * 2019-12-10 2021-06-17 三菱電機株式会社 Heat pump apparatus
WO2023054841A1 (en) * 2021-09-29 2023-04-06 삼성전자주식회사 Horizontal compressor
WO2024085065A1 (en) * 2022-10-21 2024-04-25 株式会社デンソー Electric compressor

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