JP2006200542A - Hermetic electric compressor - Google Patents
Hermetic electric compressor Download PDFInfo
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- JP2006200542A JP2006200542A JP2006081974A JP2006081974A JP2006200542A JP 2006200542 A JP2006200542 A JP 2006200542A JP 2006081974 A JP2006081974 A JP 2006081974A JP 2006081974 A JP2006081974 A JP 2006081974A JP 2006200542 A JP2006200542 A JP 2006200542A
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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
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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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
- 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
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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
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Motor Or Generator Frames (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
本発明は、密閉容器内に電動要素と、この電動要素にて駆動される圧縮要素を設けて成る密閉式電動圧縮機に関するものである。 The present invention relates to a hermetic electric compressor in which an electric element and a compression element driven by the electric element are provided in a hermetic container.
従来のこの種密閉式電動圧縮機、特に、内部中間圧型多段圧縮式のロータリコンプレッサでは、第1の回転圧縮要素の吸込ポートから冷媒ガスがシリンダの低圧室側に吸入され、ローラとベーンの動作により圧縮されて中間圧となりシリンダの高圧室側より吐出ポート、吐出消音室を経て密閉容器内に吐出される。そして、この密閉容器内の中間圧の冷媒ガスは第2の回転圧縮要素の吸込ポートからシリンダの低圧室側に吸入され、ローラとベーンの動作により2段目の圧縮が行なわれて高温高圧の冷媒ガスとなり、高圧室側より吐出ポート、吐出消音室を経て放熱器に流入し、放熱した後、膨張弁で絞られて蒸発器で吸熱し、第1の回転圧縮要素に吸入されるサイクルを繰り返す。 In a conventional hermetic electric compressor of this type, particularly an internal intermediate pressure type multistage compression rotary compressor, refrigerant gas is drawn into the low pressure chamber side of the cylinder from the suction port of the first rotary compression element, and the operation of the rollers and vanes Is compressed to an intermediate pressure and discharged from the high pressure chamber side of the cylinder into the sealed container through the discharge port and the discharge silencer chamber. The intermediate-pressure refrigerant gas in the sealed container is sucked into the low-pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second stage compression is performed by the operation of the roller and the vane, so The refrigerant gas flows from the high-pressure chamber side through the discharge port and discharge silencer chamber, flows into the radiator, radiates heat, is throttled by the expansion valve, absorbs heat by the evaporator, and is sucked into the first rotary compression element. repeat.
係るロータリコンプレッサに、高低圧差の大きい冷媒、例えば炭酸ガスの一例としての二酸化炭素(CO2)を冷媒として用いた場合、冷媒圧力は高圧となる第2の回転圧縮要素で12MPaGに達し、一方、低段側となる第1の回転圧縮要素で8MPaGとなり、これが密閉容器内の圧力となる。 When a refrigerant having a large high-low pressure difference, for example, carbon dioxide (CO 2 ) as an example of carbon dioxide gas is used as the refrigerant for the rotary compressor, the refrigerant pressure reaches 12 MPaG in the second rotary compression element having a high pressure, The first rotary compression element on the lower stage side becomes 8 MPaG, which is the pressure in the sealed container.
また、このようなロータリコンプレッサでは、電動要素に給電を行うためのターミナルが密閉容器に取り付けられる。図20は係る従来のロータリコンプレッサのターミナル300部分の断面図を示す。ターミナル300は、電気的端子301が設けられる円形のガラス部302と、その周囲に形成された金属製の取付部303とから構成されており、この取付部303が密閉容器304に形成された取付孔306の周縁部に溶接により固定されていた。このようなロータリコンプレッサは、例えば、特許文献1に開示されている。
ここで、ターミナル300の取付部303の厚さ寸法については、薄すぎると上述した密閉容器304内の冷媒ガスの高い圧力に対する強度(耐圧性能)が不足し、取付部303に亀裂が発生するなどの故障の原因となる。一方、厚すぎると、今度は密閉容器304に溶接する際に多量の熱量が必要となって来るため、この熱によってガラス部302に損傷が発生し、ガスリークや破壊の危険性が出てくる問題があった。 Here, if the thickness dimension of the attachment portion 303 of the terminal 300 is too thin, the above-described strength (pressure resistance performance) of the refrigerant gas in the sealed container 304 against a high pressure is insufficient, and the attachment portion 303 is cracked. Cause malfunction. On the other hand, if it is too thick, a large amount of heat is required when welding to the sealed container 304, and this heat causes damage to the glass portion 302, resulting in a risk of gas leakage and destruction. was there.
本発明は、係る従来技術の課題を解決するために成されたものであり、電動要素に給電するためのターミナル部分に発生する不都合を未然に回避することができる密閉式電動圧縮機を提供することを目的とする。 The present invention has been made to solve the problems of the related art, and provides a hermetic electric compressor capable of avoiding inconveniences occurring in a terminal portion for supplying power to an electric element. For the purpose.
即ち、請求項1の発明の密閉式電動圧縮機は、密閉容器内に電動要素と、この電動要素にて駆動される圧縮要素とを備え、この圧縮要素によりCO2冷媒を圧縮して密閉容器内に吐出するものであって、密閉容器に取り付けられたターミナルを備え、このターミナルは、電気的端子が貫通して取り付けられる円形のガラス部と、このガラス部の周囲に形成され、密閉容器の取付孔周縁部に溶接固定される鍔状の金属製取付部とを有しており、この取付部の厚さ寸法を2.4±0.5mmの範囲とし、S25C〜S45Cの鉄を用いたことを特徴とする。 That is, the sealed type electric compressor of the first aspect of the invention, the motor element in a sealed container, and a compression element driven by the electric element, hermetic container and compressing the CO 2 refrigerant by the compression element The terminal is attached to a sealed container, and the terminal is formed around the glass part with a circular glass part through which the electrical terminal is attached. It has a hook-shaped metal mounting portion that is welded and fixed to the peripheral portion of the mounting hole. The thickness of the mounting portion is in the range of 2.4 ± 0.5 mm, and iron of S25C to S45C is used. It is characterized by that.
請求項2の発明の密閉式電動圧縮機は、密閉容器内に電動要素と、この電動要素にて駆動される第1及び第2の回転圧縮要素を備え、第1の回転圧縮要素で圧縮されたCO2冷媒ガスを密閉容器内に吐出し、更にこの吐出された中間圧の冷媒ガスを第2の回転圧縮要素で圧縮するものであって、密閉容器に取り付けられたターミナルを備え、このターミナルは、電気的端子が貫通して取り付けられる円形のガラス部と、このガラス部の周囲に形成され、密閉容器の取付孔周縁部に溶接固定される鍔状の金属製取付部とを有し、この取付部の厚さ寸法を2.4±0.5mmの範囲とし、S25C〜S45Cの鉄を用いたことを特徴とする。 According to a second aspect of the present invention, there is provided a hermetic electric compressor including an electric element in a hermetic container and first and second rotary compression elements driven by the electric element, and the first electric compression element is compressed by the first rotary compression element. CO 2 refrigerant gas is discharged into a sealed container, and the discharged intermediate-pressure refrigerant gas is compressed by a second rotary compression element, comprising a terminal attached to the sealed container. Has a circular glass part through which the electrical terminal is attached, and a bowl-shaped metal attachment part formed around the glass part and welded to the peripheral part of the attachment hole of the sealed container, A thickness dimension of the mounting portion is in a range of 2.4 ± 0.5 mm, and iron of S25C to S45C is used.
本発明によれば、密閉式電動圧縮機の密閉容器に取り付けられたターミナルを備え、このターミナルは、電気的端子が貫通して取り付けられる円形のガラス部と、このガラス部の周囲に形成され、密閉容器の取付孔周縁部に溶接固定される鍔状の金属製取付部とを有しており、この取付部の厚さ寸法を2.4±0.5mmの範囲とし、S25C〜S45Cの鉄を用いたので、密閉容器内の圧力が高くなるCO2冷媒を使用した密閉式電動圧縮機において、ターミナルの耐圧性能を十分に確保しながら、溶接固定に必要となる熱量の増大も抑制することが可能となる。 According to the present invention, it is provided with a terminal attached to a hermetic container of a hermetic electric compressor, and this terminal is formed around a circular glass part through which an electrical terminal is attached, and this glass part, It has a bowl-shaped metal attachment part that is welded and fixed to the peripheral part of the attachment hole of the closed container. The thickness dimension of this attachment part is in the range of 2.4 ± 0.5 mm, and the iron of S25C to S45C Therefore, in a sealed electric compressor using a CO 2 refrigerant that increases the pressure in the sealed container, it is possible to suppress the increase in the amount of heat required for welding fixation while ensuring sufficient pressure resistance of the terminal. Is possible.
これにより、ターミナルの取付部に亀裂が発生し、或いは、ガラス部に損傷が生じることによって発生するガスリークやターミナル破壊を未然に回避することができるようになるものである。 As a result, it is possible to avoid a gas leak or a terminal breakage that occurs when a crack occurs in the terminal mounting portion or the glass portion is damaged.
次に、図面に基づき本発明の実施形態を詳述する。図1は本発明の密閉式電動圧縮機の実施例として、第1及び第2の回転圧縮要素32、34を備えた内部中間圧型多段(2段)圧縮式のロータリコンプレッサ10の縦断面図、図2はロータリコンプレッサ10の正面図、図3ロータリコンプレッサ10の側面図、図4はロータリコンプレッサ10のもう一つの縦断面図、図5はロータリコンプレッサ10の更にもう一つの縦断面図、図6はロータリコンプレッサ10の電動要素14部分の平断面図、図7はロータリコンプレッサ10の回転圧縮機構部18の拡大断面図をそれぞれ示している。 Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view of an internal intermediate pressure type multi-stage (two-stage) rotary compressor 10 having first and second rotary compression elements 32 and 34 as an embodiment of a hermetic electric compressor of the present invention. 2 is a front view of the rotary compressor 10, FIG. 3 is a side view of the rotary compressor 10, FIG. 4 is another longitudinal sectional view of the rotary compressor 10, and FIG. 5 is yet another longitudinal sectional view of the rotary compressor 10. FIG. Fig. 7 is a plan sectional view of the electric element 14 portion of the rotary compressor 10, and Fig. 7 is an enlarged sectional view of the rotary compression mechanism portion 18 of the rotary compressor 10.
各図において、10は二酸化炭素(CO2)を冷媒として使用する内部中間圧型多段圧縮式のロータリコンプレッサで、このロータリコンプレッサ10は鋼板からなる円筒状の密閉容器12と、この密閉容器12の内部空間の上側に配置収納された電動要素14及びこの電動要素14の下側に配置され、電動要素14の回転軸16により駆動される第1の回転圧縮要素32(1段目)及び第2の回転圧縮要素34(2段目)からなる回転圧縮機構部18にて構成されている。実施例のロータリコンプレッサ10の高さ寸法は220mm(外径120mm)、電動要素14の高さ寸法は約80mm(外径110mm)、回転圧縮機構部18の高さ寸法は約70mm(外径110mm)で、電動要素14と回転圧縮機構部18との間隔は約5mmとなっている。また、第2の回転圧縮要素34の排除容積は第1の回転圧縮要素32の排除容積よりも小さく設定されている。 In each figure, reference numeral 10 denotes an internal intermediate pressure multistage compression rotary compressor that uses carbon dioxide (CO 2 ) as a refrigerant. The rotary compressor 10 includes a cylindrical sealed container 12 made of a steel plate, and an interior of the sealed container 12. The electric element 14 arranged and housed on the upper side of the space, and the first rotary compression element 32 (first stage) and the second electric element 14 arranged below the electric element 14 and driven by the rotating shaft 16 of the electric element 14. The rotary compression mechanism section 18 is composed of a rotary compression element 34 (second stage). The height dimension of the rotary compressor 10 of the embodiment is 220 mm (outer diameter 120 mm), the height dimension of the electric element 14 is about 80 mm (outer diameter 110 mm), and the height dimension of the rotary compression mechanism 18 is about 70 mm (outer diameter 110 mm). ), The distance between the electric element 14 and the rotary compression mechanism 18 is about 5 mm. Further, the excluded volume of the second rotary compression element 34 is set smaller than the excluded volume of the first rotary compression element 32.
密閉容器12は実施例では厚さ4.5mmの鋼板より構成され、底部をオイル溜とし、電動要素14と回転圧縮機構部18を収納する容器本体12Aと、この容器本体12Aの上部開口を閉塞する略椀状のエンドキャップ(蓋体)12Bとで構成され、且つ、このエンドキャップ12Bの上面中心には円形の取付孔12Dが形成されており、この取付孔12Dには電動要素14に電力を供給するためのターミナル(配線を省略)20が取り付けられている。 In the embodiment, the sealed container 12 is made of a steel plate having a thickness of 4.5 mm, the bottom is an oil reservoir, the container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and the upper opening of the container body 12A is closed. And a circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B. The mounting element 12D has a power supply to the electric element 14. A terminal (wiring is omitted) 20 is attached.
この場合、ターミナル20の周囲のエンドキャップ12Bには、座押成形によって所定曲率の段差部12Cが、エンドキャップ12Bの中心軸を中心に軸対称の形状で環状に形成されている。また、ターミナル20は図19に示す如く電気的端子139が貫通して取り付けられた円形のガラス部20Aと、このガラス部20Aの周囲に形成され、斜め外下方に鍔状に張り出した鉄製(S25C〜S45C)の取付部20Bとから構成され、エンドキャップ12Bの中心軸を中心に軸対称の形状を呈している。取付部20Bの厚さ寸法は2.4±0.5mmの範囲(1.9mm以上2.9mm以下)とされている。そして、ターミナル20は、そのガラス部20Aを下側から取付孔12Dに挿入して上側に臨ませ、取付部20Bを取付孔12Dの周縁に当接させた状態でエンドキャップ12Bの取付孔12D周縁に取付部20Bを溶接することで、エンドキャップ12Bに固定されている。 In this case, a stepped portion 12C having a predetermined curvature is annularly formed on the end cap 12B around the terminal 20 in a shape symmetrical with respect to the center axis of the end cap 12B. Further, as shown in FIG. 19, the terminal 20 is formed of a circular glass portion 20A through which an electrical terminal 139 penetrates, and is made of iron (S25C) formed around the glass portion 20A and projecting in a bowl shape obliquely outward and downward. To S45C) and has an axisymmetric shape around the central axis of the end cap 12B. The thickness dimension of the mounting portion 20B is in the range of 2.4 ± 0.5 mm (1.9 mm or more and 2.9 mm or less). And the terminal 20 inserts the glass part 20A into the mounting hole 12D from the lower side and faces the upper side, and attaches the mounting part 20B to the peripheral edge of the mounting hole 12D, and the peripheral edge of the mounting hole 12D of the end cap 12B. The attachment portion 20B is welded to the end cap 12B.
ここで、密閉容器12内の圧力を後述する中間圧としてターミナル20の取付部20Bの厚さを薄くしていった場合、試験では1.9mmよりも薄くなった時点で密閉容器12内の冷媒ガスの高い圧力(中間圧)に対する強度(耐圧性能)が不足し、取付部20B自体に亀裂が発生した。一方、取付部20Bの厚さを2.9mmよりも厚くした場合、今度は密閉容器304に溶接する際に多量の熱量が必要となり、ガラス部20Aへの悪影響が懸念される試験結果となった。 Here, when the thickness of the mounting portion 20B of the terminal 20 is reduced by using the pressure in the sealed container 12 as an intermediate pressure, which will be described later, the refrigerant in the sealed container 12 becomes less than 1.9 mm in the test. The strength (pressure resistance performance) against the high gas pressure (intermediate pressure) was insufficient, and a crack occurred in the mounting portion 20B itself. On the other hand, when the thickness of the mounting portion 20B is made thicker than 2.9 mm, a large amount of heat is required this time when welding to the sealed container 304, resulting in a test result that may cause adverse effects on the glass portion 20A. .
本発明ではこれを踏まえて、ターミナル20の取付部20Bの厚さ寸法を2.4±0.5mmとしたことにより、ターミナル20の耐圧性能を十分に確保しながら、溶接固定に必要となる熱量の増大も抑制することができた。 In the present invention, based on this, the thickness of the mounting portion 20B of the terminal 20 is set to 2.4 ± 0.5 mm, so that the heat amount necessary for welding and fixing is ensured while sufficiently ensuring the pressure resistance performance of the terminal 20. It was also possible to suppress the increase of.
電動要素14は、密閉容器12の上部空間の内周面に沿って環状に取り付けられたステータ22と、このステータ22の内側に若干の間隙を設けて挿入配置されたロータ24とからなる。このロータ24は中心を通り鉛直方向に延びる回転軸16に固定されている。 The electric element 14 includes a stator 22 attached in an annular shape along the inner peripheral surface of the upper space of the hermetic container 12, and a rotor 24 inserted and arranged with a slight gap inside the stator 22. The rotor 24 is fixed to a rotating shaft 16 that passes through the center and extends in the vertical direction.
ステータ22は、ドーナッツ状の電磁鋼板を積層した積層体26と、この積層体26の歯部に直巻き(集中巻き)方式により巻装されたステータコイル28を有している(図6)。また、ロータ24もステータ22と同様に電磁鋼板の積層体30で形成され、この積層体30内に永久磁石MGを挿入して構成されている。 The stator 22 includes a laminated body 26 in which donut-shaped electromagnetic steel plates are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method (FIG. 6). Similarly to the stator 22, the rotor 24 is also formed by a laminated body 30 of electromagnetic steel plates, and a permanent magnet MG is inserted into the laminated body 30.
前記第1の回転圧縮要素32と第2の回転圧縮要素34との間には中間仕切板36が挟持されている。即ち、第1の回転圧縮要素32と第2の回転圧縮要素34は、中間仕切板36と、この中間仕切板36の上下に配置されたシリンダ38、シリンダ40と、この上下シリンダ38、40内を180度の位相差を有して回転軸16に設けた上下偏心部42、44に嵌合されて偏心回転する上下ローラ46、48と、この上下ローラ46、48に当接して上下シリンダ38、40内をそれぞれ低圧室側と高圧室側に区画する後述する上下ベーン50(下側のベーンは図示せず)と、上シリンダ38の上側の開口面及び下シリンダ40の下側の開口面を閉塞して回転軸16の軸受けを兼用する支持部材としての上部支持部材54及び下部支持部材56にて構成される。 An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, a cylinder 38 and a cylinder 40 disposed above and below the intermediate partition plate 36, and the inside of the upper and lower cylinders 38 and 40. The upper and lower rollers 46 and 48 are fitted to the upper and lower eccentric portions 42 and 44 provided on the rotating shaft 16 with a phase difference of 180 degrees and rotate eccentrically, and the upper and lower cylinders 38 are in contact with the upper and lower rollers 46 and 48. , 40 are divided into a low pressure chamber side and a high pressure chamber side, respectively, and upper and lower vanes 50 (lower vanes are not shown), an upper opening surface of the upper cylinder 38 and an opening surface of the lower cylinder 40 below. And an upper support member 54 and a lower support member 56 as support members that also serve as bearings for the rotary shaft 16.
上部支持部材54および下部支持部材56には、吸込ポート161、162にて上下シリンダ38、40の内部とそれぞれ連通する吸込通路58、60と、凹陥した吐出消音室62、64が形成されると共に、これら両吐出消音室62、64の開口部はそれぞれカバーにより閉塞される。即ち、吐出消音室62はカバーとしての上部カバー66、吐出消音室64はカバーとしての下部カバー68にて閉塞される。 The upper support member 54 and the lower support member 56 are formed with suction passages 58 and 60 that communicate with the inside of the upper and lower cylinders 38 and 40 through suction ports 161 and 162, and recessed discharge silencer chambers 62 and 64, respectively. The openings of both the discharge silencing chambers 62 and 64 are respectively closed by covers. That is, the discharge silence chamber 62 is closed by an upper cover 66 as a cover, and the discharge silence chamber 64 is closed by a lower cover 68 as a cover.
この場合、上部支持部材54の中央には軸受け54Aが起立形成されており、この軸受け54A内面には筒状のブッシュ122が装着されている。また、下部支持部材56の中央には軸受け56Aが貫通形成されており、この軸受け56A内面にも筒状のブッシュ123が装着されている。これらブッシュ122、123は後述する如き摺動性の良い材料にて構成されており、回転軸16はこれらブッシュ122、123を介して上部支持部材54の軸受け54Aと下部支持部材56の軸受け56Aに保持される。 In this case, a bearing 54A is erected at the center of the upper support member 54, and a cylindrical bush 122 is mounted on the inner surface of the bearing 54A. Further, a bearing 56A is formed through the center of the lower support member 56, and a cylindrical bush 123 is mounted on the inner surface of the bearing 56A. The bushes 122 and 123 are made of a material having good slidability as will be described later, and the rotating shaft 16 is connected to the bearing 54A of the upper support member 54 and the bearing 56A of the lower support member 56 through the bushes 122 and 123. Retained.
この場合、下部カバー68はドーナッツ状の円形鋼板から構成されており、周辺部の4カ所を主ボルト129・・・によって下から下部支持部材56に固定され、吐出ポート41にて第1の回転圧縮要素32の下シリンダ40内部と連通する吐出消音室64の下面開口部を閉塞する。この主ボルト129・・・の先端は上部支持部材54に螺合する。下部カバー68の内周縁は下部支持部材56の軸受け56A内面より内方に突出しており、これによって、ブッシュ123の下端面は下部カバー68によって保持され、脱落が防止されている(図9)。図10は下部支持部材56の下面を示しており、128は吐出消音室64内において吐出ポート41を開閉する第1の回転圧縮要素32の吐出弁である。 In this case, the lower cover 68 is made of a donut-shaped circular steel plate, and is fixed to the lower support member 56 from below by main bolts 129... The lower surface opening of the discharge silencing chamber 64 communicating with the inside of the lower cylinder 40 of the compression element 32 is closed. The front ends of the main bolts 129 are screwed into the upper support member 54. The inner peripheral edge of the lower cover 68 protrudes inward from the inner surface of the bearing 56A of the lower support member 56, whereby the lower end surface of the bush 123 is held by the lower cover 68 and is prevented from falling off (FIG. 9). FIG. 10 shows the lower surface of the lower support member 56, and 128 is a discharge valve of the first rotary compression element 32 that opens and closes the discharge port 41 in the discharge silencing chamber 64.
ここで、下部支持部材56は鉄系の焼結材料(鋳物でも可)により構成されており、下部カバー68を取り付ける側の面(下面)は、平面度0.1mm以下に加工された後、スチーム処理が加えられている。このスチーム処理によって下部カバー68を取り付ける側の面は酸化鉄となるため、焼結材料内部の孔が塞がれてシール性が向上する。これにより、下部カバー68と下部支持部材56間にガスケットを介設する必要が無くなる。 Here, the lower support member 56 is made of an iron-based sintered material (which may be cast), and the surface (lower surface) on which the lower cover 68 is attached is processed to have a flatness of 0.1 mm or less, Steam processing has been added. Since the surface on which the lower cover 68 is attached by this steam treatment is made of iron oxide, the hole inside the sintered material is blocked and the sealing performance is improved. This eliminates the need for a gasket between the lower cover 68 and the lower support member 56.
尚、吐出消音室64と密閉容器12内における上部カバー66の電動要素14側は、上下シリンダ38、40や中間仕切板36を貫通する孔である連通路63にて連通されている(図4)。この場合、連通路63の上端には中間吐出管121が立設されており、この中間吐出管121は上方の電動要素14のステータ22に巻装された相隣接するステータコイル28、28間の隙間に指向している(図6)。 In addition, the electric element 14 side of the upper cover 66 in the discharge silencer chamber 64 and the sealed container 12 is communicated with a communication passage 63 that is a hole penetrating the upper and lower cylinders 38 and 40 and the intermediate partition plate 36 (FIG. 4). ). In this case, an intermediate discharge pipe 121 is erected at the upper end of the communication path 63, and this intermediate discharge pipe 121 is between the adjacent stator coils 28, 28 wound around the stator 22 of the upper electric element 14. It is directed to the gap (FIG. 6).
また、上部カバー66は吐出ポート39にて第2の回転圧縮要素34の上シリンダ38内部と連通する吐出消音室62の上面開口部を閉塞し、密閉容器12内を吐出消音室62と電動要素14側とに仕切る。この上部カバー66は図11に示す如く厚さ2mm以上10mm以下(実施例では最も望ましい6mmとされている)であって、前記上部支持部材45の軸受け45Aが貫通する孔が形成された略ドーナッツ状の円形鋼板から構成されており、上部支持部材54との間にビード付きのガスケット124を挟み込んだ状態で、当該ガスケット124を介して周辺部が4本の主ボルト78・・・により、上から上部支持部材54に固定されている。この主ボルト78・・・の先端は下部支持部材56に螺合する。 Further, the upper cover 66 closes the upper opening of the discharge silencer chamber 62 communicating with the inside of the upper cylinder 38 of the second rotary compression element 34 at the discharge port 39, and the discharge silencer chamber 62 and the electric element inside the sealed container 12. Divide into 14 sides. As shown in FIG. 11, the upper cover 66 has a thickness of 2 mm or more and 10 mm or less (6 mm is the most desirable in the embodiment), and is a substantially donut having a hole through which the bearing 45A of the upper support member 45 passes. In the state in which a gasket 124 with a bead is sandwiched between the upper support member 54 and the upper support member 54, the peripheral portion is surrounded by four main bolts 78. To the upper support member 54. The front ends of the main bolts 78 are screwed into the lower support member 56.
上部カバー66を係る厚さ寸法とすることで、密閉容器12内よりも高圧となる吐出消音室62の圧力に十分に耐えながら、小型化を達成し、電動要素14との絶縁距離を確保することもできるようになる。更に、この上部カバー66の内周縁と軸受け54Aの外面間にはOリング126が設けられている(図12)。係るOリング126により軸受け54A側のシールを行うことで、上部カバー66の内周縁で十分にシールを行い、ガスリークを防ぐことができるようになり、吐出消音室62の容積拡大が図れると共に、Cリングにより上部カバー66の内周縁側を軸受け54Aに固定する必要も無くなる。ここで、図11において127は吐出消音室62内において吐出ポート39を開閉する第2の回転圧縮要素34の吐出弁である。 By setting the upper cover 66 to have such a thickness dimension, it is possible to achieve downsizing and secure an insulation distance from the electric element 14 while sufficiently withstanding the pressure of the discharge silencer chamber 62 that is higher than that in the sealed container 12. You can also do that. Further, an O-ring 126 is provided between the inner peripheral edge of the upper cover 66 and the outer surface of the bearing 54A (FIG. 12). By sealing the bearing 54A side with the O-ring 126, it becomes possible to sufficiently seal the inner periphery of the upper cover 66 and prevent gas leakage, and the volume of the discharge silencer chamber 62 can be increased. The ring eliminates the need to fix the inner peripheral edge of the upper cover 66 to the bearing 54A. Here, in FIG. 11, 127 is a discharge valve of the second rotary compression element 34 that opens and closes the discharge port 39 in the discharge silencer chamber 62.
次に、上シリンダ38の下側の開口面及び下シリンダ40の上側の開口面を閉塞する中間仕切板36内には、上シリンダ38内の吸込側に対応する位置に、図13、図14に示す如く外周面から内周面に至り、外周面と内周面とを連通して給油路を構成する貫通孔131が穿設されており、この貫通路131の外周面側の封止材132を圧入して外周面側の開口を封止している。また、この貫通孔131の中途部には上側に延在する連通孔133が穿設されている。 Next, in the intermediate partition plate 36 that closes the lower opening surface of the upper cylinder 38 and the upper opening surface of the lower cylinder 40, a position corresponding to the suction side in the upper cylinder 38 is shown in FIGS. 13 and 14. As shown in FIG. 2, a through hole 131 is formed from the outer peripheral surface to the inner peripheral surface, and the outer peripheral surface communicates with the inner peripheral surface to form an oil supply passage. A sealing material on the outer peripheral surface side of the through passage 131 is formed. 132 is press-fitted to seal the opening on the outer peripheral surface side. A communication hole 133 extending upward is formed in the middle of the through hole 131.
一方、上シリンダ38の吸込ポート161(吸込側)には中間仕切板36の連通孔133に連通する連通孔134が穿設されている。また、回転軸16内には図7に示す如く軸中心に鉛直方向のオイル孔80と、このオイル孔80に連通する横方向の給油孔82、84(上下偏心部42、44にも形成されている)が形成されており、中間仕切板36の貫通孔131の内周面側の開口は、これらの給油孔82、84を介してオイル孔80に連通している。 On the other hand, a communication hole 134 communicating with the communication hole 133 of the intermediate partition plate 36 is formed in the suction port 161 (suction side) of the upper cylinder 38. Further, as shown in FIG. 7, a vertical oil hole 80 is formed in the rotating shaft 16 at the center of the shaft, and lateral oil supply holes 82 and 84 (upper and lower eccentric portions 42 and 44) communicating with the oil hole 80 are also formed. The opening on the inner peripheral surface side of the through hole 131 of the intermediate partition plate 36 communicates with the oil hole 80 through these oil supply holes 82 and 84.
後述する如く密閉容器12内は中間圧となるため、2段目で高圧となる上シリンダ38内にはオイルの供給が困難となるが、中間仕切板36を係る構成としたことにより、密閉容器12内底部のオイル溜めから汲み上げられてオイル孔80を上昇し、給油孔82、84から出たオイルは、中間仕切板36の貫通孔131に入り、連通孔133、134から上シリンダ38の吸込側(吸込ポート161)に供給されるようになる。 As will be described later, since the inside of the sealed container 12 is at an intermediate pressure, it is difficult to supply oil into the upper cylinder 38, which is at a high pressure in the second stage. The oil that has been pumped up from the oil sump at the inner bottom of the cylinder 12 and moved up through the oil hole 80 enters the through hole 131 of the intermediate partition plate 36 and is sucked into the upper cylinder 38 through the communication holes 133 and 134. To the side (suction port 161).
図16中Lは上シリンダ38の吸入側の圧力変動を示し、図中P1は中間仕切板36の内周面の圧力を示す。この図にL1で示す如く上シリンダ38の吸込側の圧力(吸入圧力)は、吸入過程においては吸入圧損により中間仕切板36の内周面側の圧力よりも低下する。この期間に中間仕切板36の貫通孔131、連通孔133から上シリンダ38の連通孔134を介して上シリンダ38内に給油が成されることになる。 In FIG. 16, L indicates the pressure fluctuation on the suction side of the upper cylinder 38, and P1 in the drawing indicates the pressure on the inner peripheral surface of the intermediate partition plate 36. As indicated by L1 in this figure, the suction side pressure (suction pressure) of the upper cylinder 38 is lower than the pressure on the inner peripheral surface side of the intermediate partition plate 36 due to suction pressure loss during the suction process. During this period, oil is supplied from the through hole 131 and the communication hole 133 of the intermediate partition plate 36 to the upper cylinder 38 through the communication hole 134 of the upper cylinder 38.
上述の如く上下シリンダ38、40、中間仕切板36、上下支持部材54、56及び上下カバー66、68はそれぞれ4本の主ボルト78・・・と主ボルト129・・・にて上下から締結されるが、更に、上下シリンダ38、40、中間仕切板36、上下支持部材54、56は、これら主ボルト78、129の外側に位置する補助ボルト136、136により締結される(図4)。この補助ボルト136は上部支持部材54側から挿入され、先端は下支持部材56に螺合している。 As described above, the upper and lower cylinders 38 and 40, the intermediate partition plate 36, the upper and lower support members 54 and 56, and the upper and lower covers 66 and 68 are fastened from above and below by the four main bolts 78. However, the upper and lower cylinders 38, 40, the intermediate partition plate 36, and the upper and lower support members 54, 56 are fastened by auxiliary bolts 136, 136 positioned outside the main bolts 78, 129 (FIG. 4). The auxiliary bolt 136 is inserted from the upper support member 54 side, and the tip thereof is screwed to the lower support member 56.
また、この補助ボルト136は前述したベーン50の後述する案内溝70の近傍に位置している。このように補助ボルト136、136を追加して回転圧縮機構部18を一体化することで、内部が極めて高圧となることに対するシール性の確保が成されると共に、ベーン50の案内溝70の近傍を締め付けるので、案内溝70からの背圧ガスリークも防止できるようになる。 The auxiliary bolt 136 is positioned in the vicinity of the guide groove 70 described later of the vane 50 described later. Thus, by adding the auxiliary bolts 136 and 136 and integrating the rotary compression mechanism 18, the sealing performance against the extremely high pressure inside is ensured, and the vicinity of the guide groove 70 of the vane 50. As a result, the back pressure gas leak from the guide groove 70 can be prevented.
一方、上シリンダ38内には前述したベーン50を収納する案内溝70と、この案内溝70の外側に位置してバネ部材としてのスプリング76を収納する収納部70Aが形成されており、この収納部70Aは案内溝70側と密閉容器12(容器本体12A)側に開口している(図8)。前記スプリング76はベーン50の外側端部に当接し、常時ベーン50をローラ46側に付勢する。そして、このスプリング76の密閉容器12側の収納部70A内には金属製のプラグ137が設けられ、スプリング76の抜け止めの役目を果たす。案内溝70には図示しない背圧室が形成されており、この背圧室には第2の回転圧縮要素34の吐出圧力(高圧)が加えられるため、プラグ137のスプリング76側は高圧、密閉容器12側は中間圧となる。 On the other hand, a guide groove 70 for storing the vane 50 described above and a storage portion 70A for storing a spring 76 as a spring member located outside the guide groove 70 are formed in the upper cylinder 38. The portion 70A is open to the guide groove 70 side and the closed container 12 (container body 12A) side (FIG. 8). The spring 76 is in contact with the outer end of the vane 50 and constantly urges the vane 50 toward the roller 46. A metal plug 137 is provided in the housing portion 70A of the spring 76 on the closed container 12 side, and serves to prevent the spring 76 from coming off. A back pressure chamber (not shown) is formed in the guide groove 70, and the discharge pressure (high pressure) of the second rotary compression element 34 is applied to the back pressure chamber. The container 12 side has an intermediate pressure.
この場合、プラグ137の外寸は収納部70Aの内寸よりも小さく設定され、プラグ137は収納部70A内に隙間嵌めにより挿入される。また、プラグ137の周面には当該プラグ137と収納部70Aの内面間をシールするためのOリング138が取り付けられている。そして、上シリンダ38の外端、即ち、収納部70Aの外端と密閉容器12の容器本体12A間の間隔は、Oリング138からプラグ137の密閉容器12側の端部までの距離よりも小さく設定されている。 In this case, the outer dimension of the plug 137 is set smaller than the inner dimension of the storage portion 70A, and the plug 137 is inserted into the storage portion 70A by a clearance fit. An O-ring 138 is attached to the peripheral surface of the plug 137 for sealing between the plug 137 and the inner surface of the storage portion 70A. The distance between the outer end of the upper cylinder 38, that is, the outer end of the storage portion 70A, and the container body 12A of the sealed container 12 is smaller than the distance from the O-ring 138 to the end of the plug 137 on the sealed container 12 side. Is set.
係る寸法関係としたことにより、プラグ137を収納部70A内に圧入固定する場合の如く、上シリンダ38が変形して上部支持部材54との間のシール性が低下し、性能悪化を来す不都合を未然に回避することができるようになる。また、係る隙間嵌めであっても、上シリンダ38と密閉容器12間の間隔をOリング138からプラグ137の密閉容器12側の端部までの距離よりも小さく設定しているので、プラグ137が収納部70Aから押し出される方向に移動しても、密閉容器12に当接して移動が阻止された時点で依然Oリング138は収納部70A内に位置してシールするので、プラグ138の機能には何ら問題は生じない。 Due to such a dimensional relationship, as in the case where the plug 137 is press-fitted and fixed in the housing portion 70A, the upper cylinder 38 is deformed and the sealing performance with the upper support member 54 is deteriorated, resulting in a deterioration in performance. Can be avoided in advance. Even with such a clearance fit, the distance between the upper cylinder 38 and the sealed container 12 is set to be smaller than the distance from the O-ring 138 to the end of the plug 137 on the sealed container 12 side. Even if it moves in the direction pushed out from the storage portion 70A, the O-ring 138 is still positioned and sealed in the storage portion 70A when the movement is prevented by coming into contact with the hermetic container 12; There is no problem.
ところで、回転軸16と一体に180度の位相差を持って形成される上下偏心部42、44の相互間を連結する連結部90は、その断面形状を回転軸16の円形断面より断面積を大きくして剛性を持たせるために非円形状の例えばラグビーボール状とされている(図17)。即ち、回転軸16に設けた上下偏心部42、44を連結する連結部90の断面形状は上下偏心部42、44の偏心方向に直交する方向でその肉厚を大きくしている(図中ハッチングの部分)。 By the way, the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 formed integrally with the rotating shaft 16 with a phase difference of 180 degrees has a cross-sectional shape that is larger than the circular cross section of the rotating shaft 16. In order to enlarge and give rigidity, it is made into a non-circular shape such as a rugby ball (FIG. 17). That is, the cross-sectional shape of the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 provided on the rotating shaft 16 is increased in thickness in the direction perpendicular to the eccentric direction of the upper and lower eccentric portions 42 and 44 (hatching in the figure). Part).
これにより、回転軸16に一体に設けられた上下偏心部42、44を連結する連結部90の断面積が大きくし、断面2次モーメントを増加させて強度(剛性)を増し、耐久性と信頼性を向上させている。特に使用圧力の高い冷媒を2段圧縮する場合、高低圧の圧力差が大きいために回転軸16にかかる荷重も大きくなるが、連結部90の断面積を大きくしてその強度(剛性)を増し、回転軸16が弾性変形してしまうのを防止している。 As a result, the cross-sectional area of the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 provided integrally with the rotating shaft 16 is increased, the second moment is increased, and the strength (rigidity) is increased. Improves sex. In particular, when a refrigerant having a high working pressure is compressed in two stages, the load applied to the rotary shaft 16 increases due to the large pressure difference between the high and low pressures. However, the strength (rigidity) is increased by increasing the cross-sectional area of the connecting portion 90. The rotation shaft 16 is prevented from being elastically deformed.
この場合、上側の偏心部42の中心をO1とし、下側の偏心部44の中心をO2とすると、偏心部42の偏心方向側の連結部90の面の円弧の中心はO1、偏心部44の偏心方向側の連結部90の面の円弧の中心はO2としている。これにより、回転軸16を切削加工機にチャックして上下偏心部42、44と連結部90を切削加工する際、偏心部42を加工した後、半径のみを変更して連結部90の一面を加工し、チャック位置を変更して連結部90の他面を加工し、半径のみを変更して偏心部44を加工すると云う作業が可能となる。これにより、回転軸16をチャックし直す回数が減少して生産性が著しく改善されるようになる。 In this case, if the center of the upper eccentric portion 42 is O1, and the center of the lower eccentric portion 44 is O2, the center of the arc of the surface of the connecting portion 90 on the eccentric direction side of the eccentric portion 42 is O1, and the eccentric portion 44. The center of the arc of the surface of the connecting portion 90 on the eccentric direction side is O2. Thus, when the rotary shaft 16 is chucked to the cutting machine to cut the upper and lower eccentric portions 42 and 44 and the connecting portion 90, after machining the eccentric portion 42, only the radius is changed and one surface of the connecting portion 90 is changed. It is possible to perform an operation of machining, changing the chuck position, machining the other surface of the connecting portion 90, and machining the eccentric portion 44 by changing only the radius. As a result, the number of times of rechucking the rotating shaft 16 is reduced and the productivity is remarkably improved.
そして、この場合冷媒としては地球環境にやさしく、可燃性および毒性等を考慮して自然冷媒である炭酸ガスの一例としての前記二酸化炭素(CO2)を使用し、潤滑油としてのオイルは、例えば鉱物油(ミネラルオイル)、アルキルベンゼン油、エーテル油、エステル油等既存のオイルが使用される。 In this case, the carbon dioxide (CO 2 ) is used as an example of carbon dioxide gas which is a natural refrigerant in consideration of flammability and toxicity as the refrigerant, and the oil as the lubricating oil is, for example, Existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil and ester oil are used.
密閉容器12の容器本体12Aの側面には、上部支持部材54と下部支持部材56の吸込通路58、60、吐出消音室62及び上部カバー66の上側(電動要素14の下端に略対応する位置)に対応する位置に、スリーブ141、142、143及び144がそれぞれ溶接固定されている。スリーブ141と142は上下に隣接すると共に、スリーブ143はスリーブ141の略対角線上にある。また、スリーブ144はスリーブ141と略90度ずれた位置にある。 On the side surface of the container main body 12A of the sealed container 12, the suction passages 58, 60 of the upper support member 54 and the lower support member 56, the upper side of the discharge silencer chamber 62, and the upper cover 66 (position substantially corresponding to the lower end of the electric element 14). The sleeves 141, 142, 143, and 144 are fixed by welding at positions corresponding to. The sleeves 141 and 142 are adjacent to each other vertically, and the sleeve 143 is substantially diagonal to the sleeve 141. Further, the sleeve 144 is located at a position shifted by approximately 90 degrees from the sleeve 141.
そして、スリーブ141内には上シリンダ38に冷媒ガスを導入するための冷媒導入管92の一端が挿入接続され、この冷媒導入管92の一端は上シリンダ38の吸込通路58に連通される。この冷媒導入管92は密閉容器12の上側を通過してスリーブ144に至り、他端はスリーブ144内に挿入接続されて密閉容器12内に連通する。 One end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the upper cylinder 38 is inserted and connected into the sleeve 141, and one end of the refrigerant introduction pipe 92 is communicated with the suction passage 58 of the upper cylinder 38. The refrigerant introduction pipe 92 passes through the upper side of the sealed container 12 to reach the sleeve 144, and the other end is inserted and connected into the sleeve 144 to communicate with the sealed container 12.
また、スリーブ142内には下シリンダ40に冷媒ガスを導入するための冷媒導入管94の一端が挿入接続され、この冷媒導入管94の一端は下シリンダ40の吸込通路60に連通される。この冷媒導入管94の他端はアキュムレータ146の下端に接続されている。また、スリーブ143内には冷媒吐出管96が挿入接続され、この冷媒吐出管96の一端は吐出消音室62に連通される。 Also, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the lower cylinder 40 is inserted and connected into the sleeve 142, and one end of the refrigerant introduction pipe 94 is communicated with the suction passage 60 of the lower cylinder 40. The other end of the refrigerant introduction tube 94 is connected to the lower end of the accumulator 146. A refrigerant discharge pipe 96 is inserted and connected into the sleeve 143, and one end of the refrigerant discharge pipe 96 is communicated with the discharge silencer chamber 62.
上記アキュムレータ146は吸込冷媒の気液分離を行うタンクであり、密閉容器12の容器本体12Aの上部側面に溶接固定された密閉容器側のブラケット147にアキュムレータ側のブラケット148を介して取り付けられている。このブラケット148はブラケット147から上方に延在し、アキュムレータ146の上下方向の略中央部を保持しており、その状態でアキュムレータ146は密閉容器12の側方に沿うかたちで配置される。冷媒導入管92はスリーブ141から出た後、実施例では右方に屈曲した後、上昇しており、アキュムレータ146の下端はこの冷媒導入管92に近接するかたちとなる。そこで、アキュムレータ146の下端から降下する冷媒導入管94は、スリーブ141から見て冷媒導入管92の屈曲方向とは反対の左側を迂回してスリーブ142に至るように引き回されている(図3)。 The accumulator 146 is a tank that performs gas-liquid separation of the suction refrigerant, and is attached to a bracket 147 on the hermetic container side welded to the upper side surface of the container body 12A of the hermetic container 12 via a bracket 148 on the accumulator side. . The bracket 148 extends upward from the bracket 147 and holds a substantially central portion of the accumulator 146 in the vertical direction. In this state, the accumulator 146 is arranged along the side of the sealed container 12. The refrigerant introduction pipe 92 rises after exiting from the sleeve 141, bent in the right direction in the embodiment, and then rises, and the lower end of the accumulator 146 becomes close to the refrigerant introduction pipe 92. Therefore, the refrigerant introduction pipe 94 descending from the lower end of the accumulator 146 is routed around the left side opposite to the bending direction of the refrigerant introduction pipe 92 when viewed from the sleeve 141 so as to reach the sleeve 142 (FIG. 3). ).
即ち、上部支持部材38と下部支持部材40の吸込通路58、60にそれぞれ連通する冷媒導入管92、94は密閉容器12から見て水平方向で反対の方向に屈曲されたかたちとされており、これにより、アキュムレータ146の上下寸法を拡大して容積を増やしても、各冷媒導入管92、94が相互に干渉しないように配慮されている。 That is, the refrigerant introduction pipes 92 and 94 respectively communicating with the suction passages 58 and 60 of the upper support member 38 and the lower support member 40 are bent in the opposite direction in the horizontal direction when viewed from the sealed container 12. Thereby, even if the vertical dimension of the accumulator 146 is enlarged to increase the volume, consideration is given so that the refrigerant introduction pipes 92 and 94 do not interfere with each other.
また、スリーブ141、143、144の外面周囲には配管接続用のカプラが係合可能な鍔部151が形成されており、スリーブ142の内面には配管接続用のネジ溝152が形成されている。これにより、スリーブ141、143、144にはロータリコンプレッサ10の製造工程における完成検査で気密試験を行う場合に試験用配管のカプラを鍔部151に容易に接続できるようになると共に、スリーブ142にはネジ溝152を使用して試験用配管を容易にネジ止めできるようになる。特に、上下で隣接するスリーブ141と142は、一方のスリーブ141に鍔部151が、他方のスリーブ142にネジ溝152が形成されていることで、狭い空間で試験用配管を各スリーブ141、142に接続可能となる。 Further, a flange 151 that can be engaged with a coupler for pipe connection is formed around the outer surfaces of the sleeves 141, 143, and 144, and a thread groove 152 for pipe connection is formed on the inner surface of the sleeve 142. . As a result, the sleeves 141, 143, 144 can be easily connected to the coupler 151 of the test pipe when the airtight test is performed in the completion inspection in the manufacturing process of the rotary compressor 10. It becomes possible to easily screw the test pipe using the screw groove 152. In particular, the sleeves 141 and 142 that are adjacent in the vertical direction are formed with a flange 151 on one sleeve 141 and a thread groove 152 on the other sleeve 142, so that the test pipes can be connected to the sleeves 141 and 142 in a narrow space. Can be connected.
そして、実施例のロータリコンプレッサ10は図18に示すような給湯装置153の冷媒回路に使用される。即ち、ロータリコンプレッサ10の冷媒吐出管96は水加熱用のガスクーラ154の入口に接続される。このガスクーラ154が給湯装置153の図示しない貯湯タンクに設けられる。ガスクーラ154を出た配管は減圧装置としての膨張弁156を経て蒸発器157の入口に至り、蒸発器157の出口は冷媒導入管94に接続される。また、冷媒導入管92の中途部からは図2、図3では図示していないが除霜回路を構成するデフロスト管158が分岐し、流路制御装置としての電磁弁159を介してガスクーラ154の入口に至る冷媒吐出管96に接続されている。尚、図18ではアキュムレータ146は省略されている。 And the rotary compressor 10 of an Example is used for the refrigerant circuit of the hot-water supply apparatus 153 as shown in FIG. That is, the refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the gas cooler 154 for water heating. This gas cooler 154 is provided in a hot water storage tank (not shown) of the hot water supply device 153. The pipe exiting the gas cooler 154 reaches the inlet of the evaporator 157 through an expansion valve 156 as a decompression device, and the outlet of the evaporator 157 is connected to the refrigerant introduction pipe 94. Further, although not shown in FIGS. 2 and 3, a defrost pipe 158 constituting a defrosting circuit branches off from the middle of the refrigerant introduction pipe 92, and the gas cooler 154 is connected via an electromagnetic valve 159 as a flow path control device. It is connected to a refrigerant discharge pipe 96 that reaches the inlet. In FIG. 18, the accumulator 146 is omitted.
以上の構成で次に動作を説明する。尚、加熱運転では電磁弁159は閉じているものとする。ターミナル20および図示されない配線を介して電動要素14のステータコイル28に通電されると、電動要素14が起動してロータ24が回転する。この回転により回転軸16と一体に設けた上下偏心部42、44に嵌合された上下ローラ46、48が上下シリンダ38、40内を偏心回転する。 Next, the operation of the above configuration will be described. In the heating operation, the solenoid valve 159 is closed. When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted to the upper and lower eccentric parts 42 and 44 provided integrally with the rotary shaft 16 rotate eccentrically in the upper and lower cylinders 38 and 40.
これにより、冷媒導入管94および下部支持部材56に形成された吸込通路60を経由して吸込ポート162から下シリンダ40の低圧室側に吸入された低圧(一段目吸入圧LP:4MPaG)の冷媒ガスは、ローラ48とベーンの動作により圧縮されて中間圧(MP1:8MPaG)となり下シリンダ40の高圧室側より吐出ポート41、下部支持部材56に形成された吐出消音室64から連通路63を経て中間吐出管121から密閉容器12内に吐出される。 As a result, the low-pressure refrigerant (first-stage suction pressure LP: 4 MPaG) is sucked from the suction port 162 to the low-pressure chamber side of the lower cylinder 40 via the refrigerant introduction pipe 94 and the suction passage 60 formed in the lower support member 56. The gas is compressed by the operation of the roller 48 and the vane to become an intermediate pressure (MP1: 8 MPaG), and from the high pressure chamber side of the lower cylinder 40 to the discharge port 41 and the discharge silencer chamber 64 formed in the lower support member 56, through the communication path 63. Then, it is discharged from the intermediate discharge pipe 121 into the sealed container 12.
このとき、中間吐出管121は上方の電動要素14のステータ22に巻装された相隣接するステータコイル28、28間の隙間に指向しているので、未だ比較的温度の低い冷媒ガスを電動要素14方向に積極的に供給できるようになり、電動要素14の温度上昇が抑制されるようになる。また、これによって、密閉容器12内は中間圧(MP1)となる。 At this time, since the intermediate discharge pipe 121 is directed to the gap between the adjacent stator coils 28 and 28 wound around the stator 22 of the upper electric element 14, the refrigerant gas still having a relatively low temperature is supplied to the electric element. It becomes possible to actively supply in the 14 directions, and the temperature rise of the electric element 14 is suppressed. Moreover, the inside of the airtight container 12 becomes intermediate pressure (MP1) by this.
そして、密閉容器12内の中間圧の冷媒ガスは、スリーブ144から出て(中間吐出圧は前記MP1)冷媒導入管92及び上部支持部材54に形成された吸込通路58を経由して吸込ポート161から上シリンダ38の低圧室側に吸入される(2段目吸入圧MP2)。吸入された中間圧の冷媒ガスは、ローラ46とベーン50の動作により2段目の圧縮が行なわれて高温高圧の冷媒ガスとなり(2段目吐出圧HP:12MPaG)、高圧室側から吐出ポート39を通り上部支持部材54に形成された吐出消音室62、冷媒吐出管96を経由してガスクーラ154内に流入する。このときの冷媒温度は略+100℃まで上昇しており、係る高温高圧の冷媒ガスは放熱して、貯湯タンク内の水を加熱し、約+90℃の温水を生成する。 Then, the intermediate pressure refrigerant gas in the sealed container 12 exits from the sleeve 144 (intermediate discharge pressure is MP1), and the suction port 161 passes through the refrigerant introduction pipe 92 and the suction passage 58 formed in the upper support member 54. To the low pressure chamber side of the upper cylinder 38 (second-stage suction pressure MP2). The suctioned intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vane 50 to become a high-temperature and high-pressure refrigerant gas (second-stage discharge pressure HP: 12 MPaG), and is discharged from the high-pressure chamber side. The gas flows into the gas cooler 154 through the discharge silencer chamber 62 formed in the upper support member 54 and the refrigerant discharge pipe 96. The refrigerant temperature at this time has risen to approximately + 100 ° C., and the high-temperature and high-pressure refrigerant gas dissipates heat to heat the water in the hot water storage tank and generate hot water of about + 90 ° C.
一方、ガスクーラ154において冷媒自体は冷却され、ガスクーラ154を出る。そして、膨張弁156で減圧された後、蒸発器157に流入して蒸発し、アキュムレータ146(図18では示していない)を経て冷媒導入管94から第1の回転圧縮要素32内に吸い込まれるサイクルを繰り返す。 On the other hand, the refrigerant itself is cooled in the gas cooler 154 and exits the gas cooler 154. Then, after the pressure is reduced by the expansion valve 156, the refrigerant flows into the evaporator 157 to evaporate, and is sucked into the first rotary compression element 32 from the refrigerant introduction pipe 94 through the accumulator 146 (not shown in FIG. 18). repeat.
特に、低外気温の環境ではこのような加熱運転で蒸発器157には着霜が成長する。その場合には電磁弁159を開放し、膨張弁156は全開状態として蒸発器157の除霜運転を実行する。これにより、密閉容器12内の中間圧の冷媒(第2の回転圧縮要素34から吐出された少量の高圧冷媒を含む)は、デフロスト管158を通ってガスクーラ154に至る。この冷媒の温度は+50〜+60℃程であり、ガスクーラ154では放熱せず、当初は逆に冷媒が熱を吸収するかたちとなる。そして、ガスクーラ154から出た冷媒は膨張弁156を通過し、蒸発器157に至るようになる。即ち、蒸発器157には略中間圧の比較的温度の高い冷媒が減圧されずに実質的に直接供給されるかたちとなり、これによって、蒸発器157は加熱され、除霜されることになる。 In particular, in an environment of low outside air temperature, frost forms on the evaporator 157 by such heating operation. In that case, the electromagnetic valve 159 is opened, the expansion valve 156 is fully opened, and the defrosting operation of the evaporator 157 is executed. As a result, the intermediate-pressure refrigerant in the sealed container 12 (including a small amount of high-pressure refrigerant discharged from the second rotary compression element 34) reaches the gas cooler 154 through the defrost pipe 158. The temperature of this refrigerant is about +50 to + 60 ° C., and the gas cooler 154 does not radiate heat, but initially the refrigerant absorbs heat. Then, the refrigerant discharged from the gas cooler 154 passes through the expansion valve 156 and reaches the evaporator 157. That is, the refrigerant having a relatively high intermediate pressure is supplied directly to the evaporator 157 without being depressurized, whereby the evaporator 157 is heated and defrosted.
このように、第1の回転圧縮要素32から吐出された中間圧の冷媒ガスを密閉容器12から取り出して蒸発器157の除霜を行うようにしているので、第2の回転圧縮要素34から吐出された高圧冷媒を蒸発器157に減圧せずに供給する場合に発生する第2の回転圧縮要素34の吐出(高圧)と吸込(中間圧)における圧力の逆転現象を防止することができるようになる。 In this way, the intermediate pressure refrigerant gas discharged from the first rotary compression element 32 is taken out from the hermetic container 12 and the evaporator 157 is defrosted, so that it is discharged from the second rotary compression element 34. So as to prevent the reverse phenomenon of the pressure in the discharge (high pressure) and suction (intermediate pressure) of the second rotary compression element 34 that occurs when supplying the high-pressure refrigerant to the evaporator 157 without reducing the pressure. Become.
尚、密閉式電動圧縮機としては実施例の如き内部中間圧型多段圧縮式のロータリコンプレッサに限らず、単一シリンダのロータリコンプレッサなどにも本発明は有効である。更に、実施例ではロータリコンプレッサ10を給湯装置153の冷媒回路に用いたが、これに限らず、室内の暖房用などに用いても本発明は有効である。 Note that the hermetic type electric compressor is not limited to the internal intermediate pressure type multistage compression type rotary compressor as in the embodiment, and the present invention is also effective for a single cylinder rotary compressor and the like. Furthermore, although the rotary compressor 10 was used for the refrigerant circuit of the hot water supply device 153 in the embodiments, the present invention is not limited to this, and the present invention is effective when used for indoor heating.
10 ロータリコンプレッサ
12 密閉容器
12A エンドキャップ
12D 取付孔
14 電動要素
16 回転軸
18 回転圧縮機構部
20 ターミナル
20A ガラス部
20B 取付部
32 第1の回転圧縮要素
34 第2の回転圧縮要素
36 中間仕切板
38、40 シリンダ
39、41 吐出ポート
42 偏心部
44 偏心部
46 ローラ
48 ローラ
50 ベーン
54 上部支持部材
56 下部支持部材
62 吐出消音室
64 吐出消音室
66 上部カバー
68 下部カバー
70 案内溝
70A 収納部
76 スプリング(バネ部材)
78、129 主ボルト
90 連結部
92、94 冷媒導入管
96 冷媒吐出管
131 貫通孔(給油路)
132 封止材
133、134 連通孔
137 プラグ
138 Oリング
141、142、143、144 スリーブ
146 アキュムレータ
147、148 ブラケット
151 鍔部
153 給湯装置
154 ガスクーラ
156 膨張弁
157 蒸発器
158 デフロスト管
159 電磁弁
DESCRIPTION OF SYMBOLS 10 Rotary compressor 12 Airtight container 12A End cap 12D Mounting hole 14 Electric element 16 Rotating shaft 18 Rotation compression mechanism part 20 Terminal 20A Glass part 20B Attachment part 32 1st rotation compression element 34 2nd rotation compression element 36 Intermediate partition plate 38 , 40 Cylinder 39, 41 Discharge port 42 Eccentric part 44 Eccentric part 46 Roller 48 Roller 50 Vane 54 Upper support member 56 Lower support member 62 Discharge silencer chamber 64 Discharge silencer chamber 66 Upper cover 68 Lower cover 70 Guide groove 70A Storage part 76 Spring (Spring member)
78, 129 Main bolt 90 Connecting portion 92, 94 Refrigerant introduction pipe 96 Refrigerant discharge pipe 131 Through hole (oil supply passage)
132 Sealant 133, 134 Communication hole 137 Plug 138 O-ring 141, 142, 143, 144 Sleeve 146 Accumulator 147, 148 Bracket 151 Hook 153 Hot water supply device 154 Gas cooler 156 Expansion valve 157 Evaporator 158 Defrost tube 159 Solenoid valve
Claims (2)
前記密閉容器に取り付けられたターミナルを備え、
該ターミナルは、電気的端子が貫通して取り付けられる円形のガラス部と、該ガラス部の周囲に形成され、前記密閉容器の取付孔周縁部に溶接固定される鍔状の金属製取付部とを有し、
該取付部の厚さ寸法を2.4±0.5mmの範囲とし、S25C〜S45Cの鉄を用いたことを特徴とする密閉式電動圧縮機。 In a hermetic electric compressor comprising an electric element in a hermetic container and a compression element driven by the electric element, and compressing the CO 2 refrigerant by the compression element and discharging it into the hermetic container,
Comprising a terminal attached to the sealed container;
The terminal includes a circular glass portion through which an electrical terminal is attached, and a bowl-shaped metal attachment portion formed around the glass portion and welded to the periphery of the attachment hole of the sealed container. Have
A hermetic electric compressor characterized in that the thickness of the mounting portion is in a range of 2.4 ± 0.5 mm and iron of S25C to S45C is used.
前記密閉容器に取り付けられたターミナルを備え、
該ターミナルは、電気的端子が貫通して取り付けられる円形のガラス部と、該ガラス部の周囲に形成され、前記密閉容器の取付孔周縁部に溶接固定される鍔状の金属製取付部とを有し、
該取付部の厚さ寸法を2.4±0.5mmの範囲とし、S25C〜S45Cの鉄を用いたことを特徴とする密閉式電動圧縮機。 An electric element and first and second rotary compression elements driven by the electric element are provided in the sealed container, and CO 2 refrigerant gas compressed by the first rotary compression element is discharged into the sealed container. Further, in the hermetic electric compressor for compressing the discharged intermediate pressure refrigerant gas by the second rotary compression element,
Comprising a terminal attached to the sealed container;
The terminal includes a circular glass portion through which an electrical terminal is attached, and a bowl-shaped metal attachment portion formed around the glass portion and welded to the periphery of the attachment hole of the sealed container. Have
A hermetic electric compressor characterized in that the thickness of the mounting portion is in a range of 2.4 ± 0.5 mm and iron of S25C to S45C is used.
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JP2006081974A JP2006200542A (en) | 2006-03-24 | 2006-03-24 | Hermetic electric compressor |
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JP2006081974A JP2006200542A (en) | 2006-03-24 | 2006-03-24 | Hermetic electric compressor |
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JP2001295663A Division JP2003097434A (en) | 2001-09-27 | 2001-09-27 | Hermetic electric compressor |
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Cited By (1)
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JP2008274844A (en) * | 2007-04-27 | 2008-11-13 | Fujitsu General Ltd | Rotary compressor |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2008274844A (en) * | 2007-04-27 | 2008-11-13 | Fujitsu General Ltd | Rotary compressor |
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