WO2014156679A1 - Multi-cylinder rotary compressor - Google Patents
Multi-cylinder rotary compressor Download PDFInfo
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- WO2014156679A1 WO2014156679A1 PCT/JP2014/056650 JP2014056650W WO2014156679A1 WO 2014156679 A1 WO2014156679 A1 WO 2014156679A1 JP 2014056650 W JP2014056650 W JP 2014056650W WO 2014156679 A1 WO2014156679 A1 WO 2014156679A1
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- cylinder
- rotary compressor
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- 238000005192 partition Methods 0.000 claims abstract description 41
- 238000007906 compression Methods 0.000 claims abstract description 37
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Classifications
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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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
Abstract
In this multi-cylinder rotary compressor, a motor, and a compression mechanism driven by the motor are provided inside a sealed container. The compression mechanism is formed from rotary compression mechanisms (6A, 6B) provided with: a plurality of cylinders (17, 18); a partition plate (21) which forms a partition between the plurality of cylinders (17, 18); blades which partition the insides of the cylinders (17, 18) into intake sides and discharge sides; and rotors (24, 25) which rotate inside the cylinders (17, 18). When ΦMo represents the core diameter of the motor, ΦDc represents the internal diameter of each of the cylinders (17, 18), Hc represents the width of each of the cylinders (17, 18), and Hs represents the width of the partition plate (21), Hs/Hc ≤ 0.35 is satisfied under conditions in which ΦDc/ΦMo ≥ 0.49.
Description
本発明は、モータコア径を大きくすることなく、圧縮機を大容量化（押し退け量ＵＰ）することができる密閉型の多気筒ロータリ圧縮機に関するものである。
The present invention relates to a hermetic multi-cylinder rotary compressor capable of increasing the capacity of a compressor (push-up amount UP) without increasing the motor core diameter.
密閉型のロータリ圧縮機を大容量化する場合、通常は単純に軸受面圧やブレードサイド面圧等のメカ負荷（機械的負荷）が大きくなることから、比例設計によりモータコア径（胴径）やジャーナル径を１ランクアップすることにより対応している。しかし、モータコア径（胴径）やジャーナル径のアップは、製造設備による制約を受けるため、限られたラインナップから選んで設計することになるが、１ランク上のモータコア径（胴径）を有する圧縮機を持っていない場合、大きな設備投資が必要になる。
When increasing the capacity of a hermetic rotary compressor, the mechanical load (mechanical load) such as bearing surface pressure and blade side surface pressure is usually increased, so the motor core diameter (body diameter) and This is achieved by increasing the journal diameter by one rank. However, the increase in the motor core diameter (body diameter) and journal diameter is limited by the manufacturing equipment, so it will be designed by selecting from a limited lineup. If you do not have a machine, a large capital investment is required.
そこで、モータコア径を変えずに、云い換えると、圧縮機の外形寸法を変えずに、圧縮機の押し退け量（容量）を大容量化可能としたものが、特許文献１に開示されている。これは、密閉型の多気筒ロータリ圧縮機において、クランク軸を複数連結構造となすことにより、複数のシリンダ間を仕切る仕切板に設けられている開口を小さくし、該開口部に連結部を支持するための軸受を設け、これによって、シリンダ内を回動するロータの外径を小さくし、偏心軸部の偏心量を大きく（ブレードストロークをロングストローク化）してシリンダ内の有効容量（押し退け量）を増大させ、大容量化したものである。
Therefore, Patent Document 1 discloses that the displacement (capacity) of the compressor can be increased without changing the motor core diameter, in other words, without changing the external dimensions of the compressor. This is because in a sealed multi-cylinder rotary compressor, a plurality of crankshafts are connected to each other, thereby reducing the opening provided in the partition plate that partitions the plurality of cylinders and supporting the connecting portion in the opening. To reduce the outer diameter of the rotor that rotates in the cylinder, and to increase the eccentric amount of the eccentric shaft (the blade stroke is made longer) to increase the effective capacity in the cylinder (push-away amount) ) To increase the capacity.
しかしながら、上記の特許文献１に開示されたものは、クランク軸を複数に分割して組み立てる構造としなければならないため、部品数が増加して加工工数や組み立て工数が増加し、構成の複雑化や高コスト化が避けられない等の課題があった。
However, since the structure disclosed in the above-mentioned Patent Document 1 has to be structured such that the crankshaft is divided into a plurality of parts, the number of parts increases, the number of processing steps and assembly steps increase, and the configuration becomes complicated. There were problems such as inevitable increase in cost.
一方、モータコア径を変更せずに、大容量化（押し退け量ＵＰ）する方法として、シリンダの内径を大きくすることにより、ブレードストロークをロングストローク化し、１ランク上の押し退け量の圧縮機を製造することが考えられる。しかし、この場合、上記の如く、軸受面圧やブレードサイド面圧等のメカ負荷（機械的負荷）が大きくなることから、それを抑える対策が必須となる等の技術的課題があった。
On the other hand, as a method of increasing the capacity (pushing-up amount UP) without changing the motor core diameter, the blade stroke is lengthened by increasing the inner diameter of the cylinder, and a compressor with a pushing-out amount that is one rank higher is manufactured. It is possible. However, in this case, as described above, the mechanical load (mechanical load) such as the bearing surface pressure and the blade side surface pressure is increased, and thus there is a technical problem that measures to suppress it are essential.
本発明は、このような事情に鑑みてなされたものであって、モータコア径を大きくすることなく、既存のモータコア径のままでシリンダ内径を大きくして大容量化しても、メカ負荷（機械的負荷）を抑えて１ランク上の押し退け量を持つ圧縮機を製造できる密閉型の多気筒ロータリ圧縮機を提供することを目的とする。
The present invention has been made in view of such circumstances. Even if the cylinder inner diameter is increased and the capacity is increased without increasing the motor core diameter, the mechanical load (mechanical load) is increased. It is an object of the present invention to provide a hermetic multi-cylinder rotary compressor capable of manufacturing a compressor having a displacement higher by one rank while suppressing the load).
上記した課題を解決するために、本発明の多気筒ロータリ圧縮機は、以下の手段を採用する。
すなわち、本発明の第１の態様にかかる多気筒ロータリ圧縮機は、密閉容器内にモータと、該モータにより駆動される圧縮機構とが設けられ、該圧縮機構が複数のシリンダと、該複数のシリンダ間を仕切る仕切板と、前記各シリンダ内を吸入側と吐出側とに仕切るブレードと、前記各シリンダ内を回動するロータとを備えたロータリ圧縮機構とされている多気筒ロータリ圧縮機であって、前記モータのコア径をΦＭｏ、前記各シリンダの内径をΦＤｃ、前記各シリンダの幅をＨｃ、前記仕切板の幅をＨｓとしたとき、
ΦＤｃ／ΦＭｏ≧０．４９の条件下において、
Ｈｓ／Ｈｃ≦０．３５を満たしている。 In order to solve the above-described problems, the multi-cylinder rotary compressor of the present invention employs the following means.
That is, the multi-cylinder rotary compressor according to the first aspect of the present invention is provided with a motor and a compression mechanism driven by the motor in a sealed container, and the compression mechanism includes a plurality of cylinders and the plurality of cylinders. A multi-cylinder rotary compressor that is a rotary compression mechanism that includes a partition plate that partitions cylinders, a blade that partitions each cylinder into a suction side and a discharge side, and a rotor that rotates within each cylinder. When the core diameter of the motor is ΦMo, the inner diameter of each cylinder is ΦDc, the width of each cylinder is Hc, and the width of the partition plate is Hs,
Under the condition of ΦDc / ΦMo ≧ 0.49,
Hs / Hc ≦ 0.35 is satisfied.
すなわち、本発明の第１の態様にかかる多気筒ロータリ圧縮機は、密閉容器内にモータと、該モータにより駆動される圧縮機構とが設けられ、該圧縮機構が複数のシリンダと、該複数のシリンダ間を仕切る仕切板と、前記各シリンダ内を吸入側と吐出側とに仕切るブレードと、前記各シリンダ内を回動するロータとを備えたロータリ圧縮機構とされている多気筒ロータリ圧縮機であって、前記モータのコア径をΦＭｏ、前記各シリンダの内径をΦＤｃ、前記各シリンダの幅をＨｃ、前記仕切板の幅をＨｓとしたとき、
ΦＤｃ／ΦＭｏ≧０．４９の条件下において、
Ｈｓ／Ｈｃ≦０．３５を満たしている。 In order to solve the above-described problems, the multi-cylinder rotary compressor of the present invention employs the following means.
That is, the multi-cylinder rotary compressor according to the first aspect of the present invention is provided with a motor and a compression mechanism driven by the motor in a sealed container, and the compression mechanism includes a plurality of cylinders and the plurality of cylinders. A multi-cylinder rotary compressor that is a rotary compression mechanism that includes a partition plate that partitions cylinders, a blade that partitions each cylinder into a suction side and a discharge side, and a rotor that rotates within each cylinder. When the core diameter of the motor is ΦMo, the inner diameter of each cylinder is ΦDc, the width of each cylinder is Hc, and the width of the partition plate is Hs,
Under the condition of ΦDc / ΦMo ≧ 0.49,
Hs / Hc ≦ 0.35 is satisfied.
本発明の第１の態様によれば、密閉型の多気筒ロータリ圧縮機にあって、モータのコア径ΦＭｏに対する各シリンダの内径ΦＤｃの比を、０．４９以上とした条件下で、各シリンダの幅Ｈｃに対する仕切板の幅Ｈｓの比を、０．３５以下とすることにより、モータコア径ΦＭｏを変更せずに、ガス負荷（圧縮負荷）を左程大きくすることなく、ブレードストロークをロングストローク化して、圧縮機の押し退け量を大容量化（押し退け量ＵＰ）することができるとともに、シリンダ幅Ｈｃに対する仕切板の幅Ｈｓを極力小さくし、上部軸受および下部軸受の支持点間距離を小さくすることにより、軸受面圧の上昇を抑制することができる。従って、既存のモータコア径のままで、１ランク上の押し退け量を持つ密閉型の多気筒ロータリ圧縮機を製造でき、大きな設備投資を行うことなく、製品ラインナップの拡充を図ることができる。
According to the first aspect of the present invention, in the sealed multi-cylinder rotary compressor, each cylinder has a ratio of 0.49 or more to the inner diameter ΦDc of each cylinder with respect to the motor core diameter ΦMo. By making the ratio of the width Hs of the partition plate to the width Hc of 0.35 or less, the blade stroke can be made a long stroke without changing the motor core diameter ΦMo and without increasing the gas load (compression load) to the left. Thus, the displacement amount of the compressor can be increased (the displacement amount UP), the width Hs of the partition plate with respect to the cylinder width Hc is made as small as possible, and the distance between the support points of the upper bearing and the lower bearing is reduced. As a result, an increase in bearing surface pressure can be suppressed. Therefore, it is possible to manufacture a sealed multi-cylinder rotary compressor having a displacement amount one rank higher with the existing motor core diameter, and it is possible to expand the product lineup without making a large capital investment.
さらに、本発明の第２の態様にかかる多気筒ロータリ圧縮機は、上記の多気筒ロータリ圧縮機において、前記仕切板は、ヤング率１６０［ＧＰａ］以上の素材で構成されている。
Furthermore, in the multi-cylinder rotary compressor according to the second aspect of the present invention, in the above-described multi-cylinder rotary compressor, the partition plate is made of a material having a Young's modulus of 160 [GPa] or more.
本発明の第２の態様によれば、仕切板が、ヤング率１６０［ＧＰａ］以上の素材で構成されているため、仕切板の幅Ｈｓをシリンダ幅Ｈｃの０．３５以下に薄幅化したとしても、ヤング率が１６０［ＧＰａ］以下の焼結合金や鋳鉄に比べて高い、１６０［ＧＰａ］以上の素材を用いることによって、その変形を抑えながら、軸受の支持点間距離を小さくすることができる。従って、軸受面圧等のメカ負荷の増大を抑制し、モータコア径を変えずに、簡易に圧縮機の押し退け量を１ランク上の容量に大容量化することができる。
According to the second aspect of the present invention, since the partition plate is made of a material having a Young's modulus of 160 [GPa] or more, the width Hs of the partition plate is reduced to 0.35 or less of the cylinder width Hc. Even so, by using a material with a Young's modulus of 160 [GPa] or lower, which is higher than that of a sintered alloy or cast iron, the distance between the support points of the bearing can be reduced while suppressing deformation. Can do. Therefore, an increase in mechanical load such as bearing surface pressure can be suppressed, and the displacement of the compressor can be easily increased to a capacity one rank higher without changing the motor core diameter.
さらに、本発明の第３の態様にかかる多気筒ロータリ圧縮機は、上記の多気筒ロータリ圧縮機において、前記仕切板は、炭素鋼もしくは合金鋼とされている。
Furthermore, the multi-cylinder rotary compressor according to the third aspect of the present invention is the above-described multi-cylinder rotary compressor, wherein the partition plate is made of carbon steel or alloy steel.
本発明の第３の態様によれば、仕切板が、ヤング率１６０［ＧＰａ］以上の炭素鋼もしくは合金鋼とされているため、焼結合金や鋳鉄に比べ剛性が高い炭素鋼や合金鋼を用いることにより、１６０［ＧＰａ］以上のヤング率を確保し、適正な材料の選択のみで仕切板を薄幅化しながら変形を抑えることができる。従って、軸受面圧等のメカ負荷の増大を抑制し、モータコア径を変えずに、簡易に圧縮機の押し退け量を１ランク上の容量に大容量化することができる。
According to the third aspect of the present invention, since the partition plate is carbon steel or alloy steel having a Young's modulus of 160 [GPa] or higher, carbon steel or alloy steel having higher rigidity than sintered alloy or cast iron is used. By using it, a Young's modulus of 160 [GPa] or more can be secured, and deformation can be suppressed while thinning the partition plate only by selecting an appropriate material. Therefore, an increase in mechanical load such as bearing surface pressure can be suppressed, and the displacement of the compressor can be easily increased to a capacity one rank higher without changing the motor core diameter.
さらに、本発明の第４の態様にかかる多気筒ロータリ圧縮機は、上述のいずれかの多気筒ロータリ圧縮機において、前記ブレードは、表面にＣｒＮ系等のＰＶＤ膜もしくはＤＬＣ膜等の硬質被膜が施されたブレードとされている。
Furthermore, the multi-cylinder rotary compressor according to the fourth aspect of the present invention is the above-mentioned multi-cylinder rotary compressor, wherein the blade has a hard coating such as a CrN-based PVD film or a DLC film on the surface. It is said that the blade has been applied.
本発明の第４の態様によれば、ブレードが、表面にＣｒＮ系等のＰＶＤ膜もしくはＤＬＣ膜等の硬質被膜が施されたブレードとされているため、ブレードストロークのロングストローク化によりブレードサイド面圧が上昇するが、ブレード表面に硬質被膜を施すことにより、面圧上昇による異常摩耗等にも十分対応することができる。従って、モータコア径を変えずにシリンダ内径を大きくし、設備投資を行わずに、簡易に圧縮機の押し退け量を１ランク上の容量に大容量化することができる。
According to the fourth aspect of the present invention, since the blade is a blade having a surface coated with a hard coating such as a CrN-based PVD film or a DLC film, the blade side surface is increased by increasing the blade stroke. Although the pressure rises, by applying a hard coating on the blade surface, it is possible to sufficiently cope with abnormal wear due to an increase in surface pressure. Therefore, the cylinder inner diameter can be increased without changing the motor core diameter, and the displacement of the compressor can be easily increased to a capacity one rank higher without making capital investment.
さらに、本発明の第５の態様にかかる多気筒ロータリ圧縮機は、上述のいずれかの多気筒ロータリ圧縮機において、前記密閉容器内の底部に充填される冷凍機油は、極圧剤を添加した冷凍機油とされている。
Furthermore, in the multi-cylinder rotary compressor according to the fifth aspect of the present invention, in any of the above-described multi-cylinder rotary compressors, the refrigerating machine oil filled in the bottom portion of the hermetic container is added with an extreme pressure agent. It is considered as refrigeration oil.
本発明の第５の態様によれば、密閉容器内の底部に充填される冷凍機油が、極圧剤を添加した冷凍機油とされているため、圧縮機の大容量化に伴って、軸受面圧やブレードサイド面圧等のメカ負荷が多少増大することは避けられず、それらの摺動部分において極圧潤滑状態が発生し易くなるものの、高荷重下で有効な極圧剤を冷凍機油に添加しておくことにより、摺動面での高潤滑性を維持し、焼き付きや摩耗、スカッフィングを防止することができる。従って、圧縮機の大容量化の伴うメカ負荷の増大にも有効に対応することができる。
According to the fifth aspect of the present invention, since the refrigerating machine oil filled in the bottom portion of the sealed container is a refrigerating machine oil to which an extreme pressure agent is added, the bearing surface is increased as the capacity of the compressor is increased. It is inevitable that mechanical loads such as pressure and blade side surface pressure increase somewhat, and although extreme pressure lubrication is likely to occur in those sliding parts, extreme pressure agent effective under high load is used as refrigerating machine oil. By adding it, high lubricity on the sliding surface can be maintained, and seizure, wear, and scuffing can be prevented. Therefore, it is possible to effectively cope with an increase in mechanical load accompanying an increase in capacity of the compressor.
本発明によると、モータコア径ΦＭｏを変更せずに、ガス負荷（圧縮負荷）をそれほど大きくすることなく、ブレードストロークをロングストローク化して、圧縮機の押し退け量を大容量化（押し退け量ＵＰ）することができるとともに、シリンダ幅Ｈｃに対する仕切板の幅Ｈｓを極力小さくし、上部軸受および下部軸受の支持点間距離を小さくすることにより、軸受面圧の上昇を抑制することができる。このため、既存のモータコア径のままで、１ランク上の押し退け量を持つ密閉型の多気筒ロータリ圧縮機を製造でき、大きな設備投資を行うことなく、製品ラインナップの拡充を図ることができる。
According to the present invention, without changing the motor core diameter ΦMo, without increasing the gas load (compression load) so much, the blade stroke is lengthened and the displacement of the compressor is increased (the displacement is increased). In addition, it is possible to suppress the increase in bearing surface pressure by reducing the width Hs of the partition plate with respect to the cylinder width Hc as much as possible and reducing the distance between the support points of the upper bearing and the lower bearing. For this reason, it is possible to manufacture a sealed multi-cylinder rotary compressor having a displacement amount one rank higher with the existing motor core diameter, and it is possible to expand the product lineup without making a large capital investment.
以下に、本発明の一実施形態について、図１ないし図６を参照して説明する。
図１には、本発明の一実施形態に係る多気筒ロータリ圧縮機の縦断面図が示され、図２には、その圧縮機構部分の諸元を表す横断面図、図３には、圧縮機構部分の諸元を表す縦断面図が示されている。
本実施形態に係る多気筒ロータリ圧縮機１は、上部および下部が上部カバー３および下部カバー４により密閉された円筒状の密閉容器２を備え、その内部の上方部位にモータ５が設置され、該モータ５により駆動される圧縮機構（ロータリ圧縮機構）６がその下方部位に設置された密閉型の多気筒ロータリ圧縮機１とされている。 Hereinafter, an embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a longitudinal sectional view of a multi-cylinder rotary compressor according to an embodiment of the present invention, FIG. 2 is a transverse sectional view showing specifications of a compression mechanism portion, and FIG. A longitudinal sectional view showing specifications of the mechanism portion is shown.
A multi-cylinder rotary compressor 1 according to the present embodiment includes a cylindrical sealed container 2 whose upper and lower portions are sealed by an upper cover 3 and a lower cover 4, and a motor 5 is installed in an upper portion inside the container. A compression mechanism (rotary compression mechanism) 6 driven by a motor 5 is a hermetic multi-cylinder rotary compressor 1 installed at a lower portion thereof.
図１には、本発明の一実施形態に係る多気筒ロータリ圧縮機の縦断面図が示され、図２には、その圧縮機構部分の諸元を表す横断面図、図３には、圧縮機構部分の諸元を表す縦断面図が示されている。
本実施形態に係る多気筒ロータリ圧縮機１は、上部および下部が上部カバー３および下部カバー４により密閉された円筒状の密閉容器２を備え、その内部の上方部位にモータ５が設置され、該モータ５により駆動される圧縮機構（ロータリ圧縮機構）６がその下方部位に設置された密閉型の多気筒ロータリ圧縮機１とされている。 Hereinafter, an embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a longitudinal sectional view of a multi-cylinder rotary compressor according to an embodiment of the present invention, FIG. 2 is a transverse sectional view showing specifications of a compression mechanism portion, and FIG. A longitudinal sectional view showing specifications of the mechanism portion is shown.
A multi-cylinder rotary compressor 1 according to the present embodiment includes a cylindrical sealed container 2 whose upper and lower portions are sealed by an upper cover 3 and a lower cover 4, and a motor 5 is installed in an upper portion inside the container. A compression mechanism (rotary compression mechanism) 6 driven by a motor 5 is a hermetic multi-cylinder rotary compressor 1 installed at a lower portion thereof.
密閉容器２の下部外周には、据え付け脚７が設けられている。また、密閉容器２の上部には、上部カバー３を貫通する吐出配管８が設けられ、多気筒ロータリ圧縮機１で圧縮された高圧の冷媒ガスを冷凍サイクル側へと吐き出す構成とされている。更に、密閉容器２の外周部には、アキュームレータ９が一体に組み付けられており、冷凍サイクル側からリターンする低圧の冷媒ガス中に含まれる油、液冷媒等の液分を分離し、ガス分のみを吸入配管１０，１１を介して圧縮機構６へと吸い込ませる構成とされている。
A mounting leg 7 is provided on the outer periphery of the lower portion of the sealed container 2. In addition, a discharge pipe 8 that penetrates the upper cover 3 is provided in the upper part of the sealed container 2, and the high-pressure refrigerant gas compressed by the multi-cylinder rotary compressor 1 is discharged to the refrigeration cycle side. Further, an accumulator 9 is integrally assembled on the outer peripheral portion of the sealed container 2 to separate liquid components such as oil and liquid refrigerant contained in the low-pressure refrigerant gas returning from the refrigeration cycle side, and only the gas component is separated. Is sucked into the compression mechanism 6 through the suction pipes 10 and 11.
モータ５は、ステータ１２とロータ１３とを備え、ステータ１２が密閉容器２の内周面に圧入等によって固定設置されている。ロータ１３には、クランク軸１４が一体に結合されることにより、その回転駆動力がクランク軸１４を介して圧縮機構６に伝達可能とされている。また、クランク軸１４の下方部位には、後述するロータリ圧縮機構６の第１ロータ２４および第２ロータ２５に対応して第１偏心部１５および第２偏心部１６が設けられている。
The motor 5 includes a stator 12 and a rotor 13, and the stator 12 is fixedly installed on the inner peripheral surface of the sealed container 2 by press fitting or the like. A crankshaft 14 is integrally coupled to the rotor 13 so that the rotational driving force can be transmitted to the compression mechanism 6 via the crankshaft 14. A first eccentric portion 15 and a second eccentric portion 16 are provided below the crankshaft 14 corresponding to a first rotor 24 and a second rotor 25 of the rotary compression mechanism 6 described later.
ロータリ圧縮機構６は、本実施形態では２気筒タイプとされている。その第１および第２ロータリ圧縮機構６Ａ，６Ｂは、第１シリンダ室１７および第２シリンダ室１８（以下、単にシリンダ１７，１８という場合もある。）が形成され、クランク軸１４の第１偏心部１５および第２偏心部１６に対応して密閉容器２内に固定設置された第１シリンダ本体１９および第２シリンダ本体２０と、第１シリンダ本体１９と第２シリンダ本体２０との間に介装され、第１シリンダ室１７および第２シリンダ室１８を区画する仕切板（セパレータプレート）２１と、第１シリンダ本体１９の上面に設けられ、第１シリンダ室１７を区画するとともに、クランク軸１４を支持する上部軸受２２と、第２シリンダ本体２０の下面に設けられ、第２シリンダ室１８を区画するとともに、クランク軸１４を支持する下部軸受２３と、を備えている。
The rotary compression mechanism 6 is a two-cylinder type in this embodiment. The first and second rotary compression mechanisms 6A and 6B are formed with a first cylinder chamber 17 and a second cylinder chamber 18 (hereinafter sometimes simply referred to as cylinders 17 and 18), and the first eccentricity of the crankshaft 14 is formed. The first cylinder main body 19 and the second cylinder main body 20 fixedly installed in the sealed container 2 corresponding to the portion 15 and the second eccentric portion 16, and between the first cylinder main body 19 and the second cylinder main body 20. The partition plate (separator plate) 21 that is mounted and partitions the first cylinder chamber 17 and the second cylinder chamber 18 and provided on the upper surface of the first cylinder body 19, partitions the first cylinder chamber 17, and the crankshaft 14 And a lower bearing 23 that is provided on the lower surface of the second cylinder body 20, defines the second cylinder chamber 18, and supports the crankshaft 14. , And a.
また、第１および第２ロータリ圧縮機構６Ａ，６Ｂは、第１偏心部１５および第２偏心部１６に回動自在に嵌合され、第１シリンダ室１７および第２シリンダ室１８内を回動される第１ロータ２４および第２ロータ２５と、第１シリンダ本体１９および第２シリンダ本体２０に設けられているブレード溝２６，２７（図２参照）に摺動自在に嵌合され、第１シリンダ室１７および第２シリンダ室１８内を吸入室側と吐出室側とに仕切るブレード２８，２９（図２参照）とを備えている。
Further, the first and second rotary compression mechanisms 6A and 6B are rotatably fitted to the first eccentric portion 15 and the second eccentric portion 16, and rotate in the first cylinder chamber 17 and the second cylinder chamber 18. The first rotor 24 and the second rotor 25 are slidably fitted into blade grooves 26 and 27 (see FIG. 2) provided in the first cylinder body 19 and the second cylinder body 20, respectively. Blades 28 and 29 (see FIG. 2) for partitioning the cylinder chamber 17 and the second cylinder chamber 18 into a suction chamber side and a discharge chamber side are provided.
第１および第２ロータリ圧縮機構６Ａ，６Ｂの第１シリンダ室１７および第２シリンダ室１８内には、吸入配管１０，１１から吸入ポート３０，３１を介して低圧の冷媒ガスが吸入され、第１ロータ２４および第２ロータ２５の回動により圧縮された後、吐出ポートおよび吐出弁（図示省略）を介して吐出チャンバー３２，３３内に吐出され、吐出チャンバー３２，３３から密閉容器２内に吐き出された後、吐出配管８を経て冷凍サイクルへと送り出されるように構成されている。
Low-pressure refrigerant gas is sucked into the first cylinder chamber 17 and the second cylinder chamber 18 of the first and second rotary compression mechanisms 6A and 6B from the suction pipes 10 and 11 through the suction ports 30 and 31, respectively. After being compressed by the rotation of the first rotor 24 and the second rotor 25, it is discharged into the discharge chambers 32 and 33 through a discharge port and a discharge valve (not shown), and is discharged from the discharge chambers 32 and 33 into the sealed container 2. After being discharged, it is configured to be sent to the refrigeration cycle via the discharge pipe 8.
ロータリ圧縮機構６を構成する第１シリンダ本体１９および第２シリンダ本体２０、仕切板２１、上部軸受２２および下部軸受２３は、ボルトを介して一体に締め付け固定されている。また、密閉容器２内の底部には、ＰＡＧ油、ＰＯＥ油等の冷凍機油３４が充填されており、クランク軸１４中に設けられている給油孔等を介して、公知の如く、圧縮機構６内の潤滑部位に給油可能とされている。この冷凍機油３４には、各々の油に適応する極圧剤が適量添加されているものとする。
The first cylinder body 19 and the second cylinder body 20, the partition plate 21, the upper bearing 22, and the lower bearing 23 constituting the rotary compression mechanism 6 are integrally tightened and fixed via bolts. The bottom of the sealed container 2 is filled with refrigerating machine oil 34 such as PAG oil or POE oil, and, as is well known, through the oil supply hole provided in the crankshaft 14, the compression mechanism 6. It is possible to supply oil to the lubricated part. It is assumed that an appropriate amount of extreme pressure agent suitable for each oil is added to the refrigerator oil 34.
上記の多気筒ロータリ圧縮機１において、既に生産中の圧縮機に使われているモータ５のコア径（胴径または外径）ΦＭｏを変えずに、第１シリンダ室１７および第２シリンダ室１８の内径、すなわちシリンダ内径ΦＤｃを大きくし、その押し退け量（容量）を１ランク上の容量に大容量化するため、モータコア径をΦＭｏ、第１シリンダ室１７および第２シリンダ室１８のシリンダ内径をΦＤｃとしたとき、シリンダ内径ΦＤｃを、
ΦＤｃ／ΦＭｏ≧０．４９
に設定している。 In the multi-cylinder rotary compressor 1 described above, the first cylinder chamber 17 and the second cylinder chamber 18 are not changed without changing the core diameter (body diameter or outer diameter) ΦMo of the motor 5 used in the compressor that is already in production. In order to increase the inner diameter of the cylinder, that is, the cylinder inner diameter ΦDc and increase the displacement (capacity) to a capacity one rank higher, the motor core diameter is ΦMo, and the cylinder inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18 are When ΦDc, the cylinder inner diameter ΦDc is
ΦDc / ΦMo ≧ 0.49
Is set.
ΦＤｃ／ΦＭｏ≧０．４９
に設定している。 In the multi-cylinder rotary compressor 1 described above, the first cylinder chamber 17 and the second cylinder chamber 18 are not changed without changing the core diameter (body diameter or outer diameter) ΦMo of the motor 5 used in the compressor that is already in production. In order to increase the inner diameter of the cylinder, that is, the cylinder inner diameter ΦDc and increase the displacement (capacity) to a capacity one rank higher, the motor core diameter is ΦMo, and the cylinder inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18 are When ΦDc, the cylinder inner diameter ΦDc is
ΦDc / ΦMo ≧ 0.49
Is set.
これは、現状生産中のロータリ圧縮機にあって、モータコア径ΦＭｏとシリンダ内径ΦＤｃとの比であるΦＤｃ／ΦＭｏは、図６に示されるように、一般に０．３５～０．４５の範囲に入るものがほとんどであり、最大でも０．４８であった。一方、ロータリ圧縮機のメカ負荷（機械的負荷）となるガス負荷（圧縮負荷）とΦＤｃ／ΦＭｏとの関係は、図４に示されるように、押し退け量を一定とした場合、右肩下がりのカーブとなっており、このため、シリンダ内径ΦＤｃを大きくすることにより、ΦＤｃ／ΦＭｏの値を大きくしても、ガス負荷（図３参照）は大きくならず、メカ負荷を増大することがないことが判った。
This is a rotary compressor currently in production, and ΦDc / ΦMo, which is the ratio of motor core diameter ΦMo and cylinder inner diameter ΦDc, is generally in the range of 0.35 to 0.45 as shown in FIG. Most of them entered, and the maximum was 0.48. On the other hand, the relationship between the gas load (compression load) that becomes the mechanical load (mechanical load) of the rotary compressor and ΦDc / ΦMo is shown in FIG. Therefore, even if the value of ΦDc / ΦMo is increased by increasing the cylinder inner diameter ΦDc, the gas load (see FIG. 3) does not increase and the mechanical load does not increase. I understood.
つまり、ロータリ圧縮機１の押し退け量をある値まで大容量化するために、モータコア径ΦＭｏを変えずにシリンダ内径ΦＤｃを大きくし、その比であるΦＤｃ／ΦＭｏを０．４９以上として、ブレードストローク（ブレード２８，２９の摺動ストローク）をロングストローク化させても、ロータ外径ΦＤｒとロータ幅Ｈｒの積であるロータの前映投影面積を抑えたまま、ロータの前映投影面積によって決まるガス負荷（圧縮負荷）を所定値以下に抑えられることが、図４および図６から明らかとなった。
That is, in order to increase the displacement amount of the rotary compressor 1 to a certain value, the cylinder inner diameter ΦDc is increased without changing the motor core diameter ΦMo, and the ratio ΦDc / ΦMo is set to 0.49 or more to increase the blade stroke. Even if the (sliding stroke of blades 28 and 29) is made longer, the gas determined by the projected area of the rotor while suppressing the projected area of the rotor, which is the product of the rotor outer diameter ΦDr and the rotor width Hr. It has become clear from FIGS. 4 and 6 that the load (compression load) can be suppressed to a predetermined value or less.
上記の条件下において、メカ負荷を決めるガス負荷を一定値以下に抑制することができれば、モータコア径ΦＭｏを変えずにシリンダ内径ΦＤｃを大きくすることで、押し退け量を大容量化できるとの知見が得られた。つまり、押し退け量を大容量化すると、図３に示されるように、メカ負荷であるガス負荷が大きくなってクランク軸１４の変形量が大きくなるため、クランク軸１４の変形を抑える必要が生じる。クランク軸１４の変形量が大きくなると、軸受に対する軸の片当たりの度合いが大きくなって、軸受面圧が大きくなる。クランク軸１４の変形量は、上部軸受２２と下部軸受２３との間の軸受支持点間距離Ｌによって左右されるので、軸受支持点間距離Ｌをできる限り小さくすることが軸受面圧を抑える上で有効であることが解る。
Under the above conditions, if the gas load that determines the mechanical load can be suppressed to a certain value or less, the knowledge that the displacement can be increased by increasing the cylinder inner diameter ΦDc without changing the motor core diameter ΦMo. Obtained. That is, when the displacement amount is increased, as shown in FIG. 3, the gas load, which is a mechanical load, is increased and the deformation amount of the crankshaft 14 is increased, so that it is necessary to suppress the deformation of the crankshaft 14. When the amount of deformation of the crankshaft 14 increases, the degree of contact of the shaft with respect to the bearing increases, and the bearing surface pressure increases. Since the amount of deformation of the crankshaft 14 depends on the distance L between the bearing support points between the upper bearing 22 and the lower bearing 23, reducing the distance L between the bearing support points as much as possible reduces the bearing surface pressure. It turns out that it is effective.
上記の軸受支持点間距離Ｌを小さくするには、第１シリンダ室１７および第２シリンダ室１８の幅Ｈｃ（以下、シリンダ幅Ｈｃという。）および仕切板（セパレータプレート）２１の幅Ｈｓ（以下、仕切板幅Ｈｓという。）を小さくすればよいが、押し退け量を大きくする上で、シリンダ幅Ｈｃを小さくすることは困難である。そこで、仕切板幅Ｈｓを小さくすることとなるが、この仕切板幅Ｈｓおよびシリンダ幅Ｈｃと軸受面圧との関係を分析の結果、図５に示されるように、Ｈｓ／Ｈｃを横軸、軸受面圧を縦軸にしてグラフ化したところ、右肩上がりのカーブとなり、Ｈｓ／Ｈｃを所定値以下とすれば、軸受面圧を許容値以下にできることが判明した。
In order to reduce the distance L between the bearing support points, the width Hc (hereinafter referred to as cylinder width Hc) of the first cylinder chamber 17 and the second cylinder chamber 18 and the width Hs (hereinafter referred to as separator plate) 21 of the partition plate (separator plate) 21 are used. However, it is difficult to reduce the cylinder width Hc in order to increase the displacement amount. Therefore, the partition plate width Hs is reduced. As a result of analysis of the relationship between the partition plate width Hs and the cylinder width Hc and the bearing surface pressure, as shown in FIG. When the bearing surface pressure is plotted on the vertical axis, it becomes a curve that rises to the right. It has been found that if Hs / Hc is set to a predetermined value or less, the bearing surface pressure can be set to an allowable value or less.
以上から、製造設備に影響を及ぼすモータコア径ΦＭｏ（モータコア径は製造設備による制限を受け、モータコア径を大きくすると、新たに設備投資が必要となる。）を変更することなく、シリンダ内径ΦＤｃを大きくして、ΦＤｃ／ΦＭｏ≧０．４９としても、Ｈｓ／Ｈｃを、Ｈｓ／Ｈｃ≦０．３５に制限すれば、メカ負荷である軸受面圧の増加を抑制してロータリ圧縮機１の押し退け量を大容量化することが可能となる。つまり、図６に示される斜線領域において、モータ５のコア径ΦＭｏを既存のコア径ΦＭｏのままで、１ランク上の押し退け量を持つロータリ圧縮機１を、新たに設備投資することなく、既存の設備を使用して簡易に製造することが可能となる。
From the above, it is possible to increase the cylinder inner diameter ΦDc without changing the motor core diameter ΦMo that affects the manufacturing equipment (the motor core diameter is limited by the manufacturing equipment, and if the motor core diameter is increased, new equipment investment is required). Even if ΦDc / ΦMo ≧ 0.49, if Hs / Hc is limited to Hs / Hc ≦ 0.35, the increase in the bearing surface pressure, which is a mechanical load, is suppressed, and the displacement of the rotary compressor 1 Can be increased in capacity. That is, in the shaded area shown in FIG. 6, the rotary compressor 1 having a displacement amount of one rank higher than the existing core diameter ΦMo while maintaining the core diameter ΦMo of the motor 5 without existing capital investment. It becomes possible to manufacture easily using this equipment.
なお、上記の如く、仕切板２１の幅Ｈｓを薄くすることによって、従来から仕切板２１に用いられていた焼結金属や鋳鉄製の仕切板をそのまま使用すると、これらの材料はヤング率が１６０［ＧＰａ］以下と低いことから、薄幅化による変形が問題となる可能性が出てくる。そこで、仕切板２１をヤング率が１６０［ＧＰａ］以上の素材で構成することが望ましく、例えばヤング率が２００［ＧＰａ］前後の炭素鋼や合金鋼を用いるとよい。
Note that, as described above, when the partition plate 21 is made thin by using a sintered metal or cast iron partition plate conventionally used for the partition plate 21 by reducing the width Hs, these materials have a Young's modulus of 160. Since it is as low as [GPa] or less, there is a possibility that deformation due to thinning becomes a problem. Therefore, it is desirable that the partition plate 21 is made of a material having a Young's modulus of 160 [GPa] or higher. For example, carbon steel or alloy steel having a Young's modulus of around 200 [GPa] may be used.
また、シリンダ内径ΦＤｃを大きくすると、それに相当してブレード２８，２９のストロークを大きくし、ロングストローク化しなければならなくなり、このブレードストロークのロングストローク化によって、ブレード２８，２９の側面に係る圧力が増加し、いわゆるブレードサイド面圧が上昇する。これに対応するため、ブレード２８，２９の両側面に対して、例えばＣｒＮ系等のＰＶＤ膜（Ｐｈｙｓｉｃａｌ Ｖａｐｏｒ Ｄｅｐｏｓｉｔｉｏｎ膜）もしくはＤＬＣ膜（ダイヤモンド・ライク・カーボン膜）等の硬質被膜を施し、面圧上昇による異常摩耗等に対応できるようにすることが望ましい。
Further, when the cylinder inner diameter ΦDc is increased, the strokes of the blades 28 and 29 correspondingly have to be increased and the strokes must be increased. By this increase in the stroke of the blades, the pressure applied to the side surfaces of the blades 28 and 29 is increased. It increases and the so-called blade side surface pressure increases. In order to cope with this, a hard coating such as a PVD film (Physical Vapor Deposition film) such as CrN or a DLC film (diamond-like carbon film) is applied to both side surfaces of the blades 28 and 29, and the surface pressure is increased. It is desirable to be able to cope with abnormal wear due to ascent.
さらに、圧縮機の押し退け量を大容量化することによるメカ負荷の増大を極力抑制するようにしてはいるものの、軸受面圧やブレードサイド面圧等のメカ負荷が多少増大することは避けられず、軸受２２，２３やブレード２８，２９、ロータ２４，２５等の摺動部分において極圧潤滑状態が発生し易くなる。これに対応するため、密閉容器２内の底部に充填されている冷凍機油３４に対して、前記したように、高荷重下で有効な極圧剤を適量添加しておくことが望ましい。
Furthermore, although the increase in the mechanical load due to the increased displacement of the compressor is suppressed as much as possible, it is inevitable that the mechanical load such as bearing surface pressure and blade side surface pressure will increase somewhat. The extreme pressure lubrication state is likely to occur in the sliding portions of the bearings 22 and 23, the blades 28 and 29, the rotors 24 and 25, and the like. In order to cope with this, as described above, it is desirable to add an appropriate amount of an extreme pressure agent effective under a high load to the refrigerating machine oil 34 filled in the bottom of the sealed container 2.
以上の説明の構成により、本実施形態によれば、以下の作用効果を奏する。
ロータリ圧縮機１において、第１シリンダ室１７および第２シリンダ室１８の内径、すなわちシリンダ内径ΦＤｃを大きくすれば、シリンダ容積が大きくなることから、第１偏心部１５および第２偏心部１６の偏心量を大きくしてブレード２８，２９のストロークを大きくすることにより、圧縮機の押し退け量を大容量化することができる。 With the configuration described above, according to the present embodiment, the following operational effects are obtained.
In the rotary compressor 1, if the inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18, that is, the cylinder inner diameter ΦDc is increased, the cylinder volume increases. Therefore, the eccentricity of the first eccentric portion 15 and the second eccentric portion 16 is increased. By increasing the amount to increase the stroke of the blades 28 and 29, the displacement of the compressor can be increased.
ロータリ圧縮機１において、第１シリンダ室１７および第２シリンダ室１８の内径、すなわちシリンダ内径ΦＤｃを大きくすれば、シリンダ容積が大きくなることから、第１偏心部１５および第２偏心部１６の偏心量を大きくしてブレード２８，２９のストロークを大きくすることにより、圧縮機の押し退け量を大容量化することができる。 With the configuration described above, according to the present embodiment, the following operational effects are obtained.
In the rotary compressor 1, if the inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18, that is, the cylinder inner diameter ΦDc is increased, the cylinder volume increases. Therefore, the eccentricity of the first eccentric portion 15 and the second eccentric portion 16 is increased. By increasing the amount to increase the stroke of the blades 28 and 29, the displacement of the compressor can be increased.
また、ロータリ圧縮機１の製造に際して、モータ５のコア径ΦＭｏは、製造設備による制限を受けることから、モータコア径ΦＭｏを大きくすると、新たに設備投資が必要となるが、モータコア径ΦＭｏを既存のロータリ圧縮機１のままとし、シリンダ内径ΦＤｃを大きくして大容量化すれば、設備投資を行うことなく、既存の設備を使って１ランク上の押し退け量を持つロータリ圧縮機１を製造することができることになる。
Further, when the rotary compressor 1 is manufactured, the core diameter ΦMo of the motor 5 is limited by the manufacturing equipment. Therefore, when the motor core diameter ΦMo is increased, capital investment is newly required. If the rotary compressor 1 is left as it is and the cylinder inner diameter ΦDc is increased to increase the capacity, the existing compressor can be used to manufacture the rotary compressor 1 having a higher displacement amount without using capital investment. Will be able to.
斯くして、本実施形態では、密閉容器２内にモータ５と、モータ５により駆動される圧縮機構６とが設けられ、その圧縮機構６が複数のシリンダ１７，１８と、複数のシリンダ１７，１８間を仕切る仕切板２１と、各シリンダ１７，１８内を吸入側と吐出側とに仕切るブレード２８，２９と、シリンダ１７，１８内を回動するロータ２４，２５とを備えたロータリ圧縮機構６Ａ，６Ｂとされている密閉型の多気筒ロータリ圧縮機１にあって、モータ５のコア径をΦＭｏ、各シリンダ１７，１８の内径をΦＤｃ、各シリンダ１７，１８の幅をＨｃ、仕切板２１の幅をＨｓとしたとき、ΦＤｃ／ΦＭｏ≧０．４９の条件下において、Ｈｓ／Ｈｃ≦０．３５を満たす構成としている。
Thus, in this embodiment, the motor 5 and the compression mechanism 6 driven by the motor 5 are provided in the sealed container 2, and the compression mechanism 6 includes a plurality of cylinders 17 and 18, a plurality of cylinders 17, A rotary compression mechanism provided with a partition plate 21 that partitions 18, blades 28 and 29 that partition the cylinders 17 and 18 into a suction side and a discharge side, and rotors 24 and 25 that rotate within the cylinders 17 and 18. 6A, 6B, a sealed multi-cylinder rotary compressor 1, wherein the motor 5 has a core diameter of ΦMo, the inner diameters of the cylinders 17 and 18 are ΦDc, the widths of the cylinders 17 and 18 are Hc, and a partition plate When the width of 21 is Hs, the structure satisfies Hs / Hc ≦ 0.35 under the condition of ΦDc / ΦMo ≧ 0.49.
これにより、モータコア径ΦＭｏを変更せずに、ガス負荷（圧縮負荷）を大きくすることなく、ブレード２８，２９ストロークをロングストローク化して、多気筒ロータリ圧縮機１の押し退け量を大容量化（押し退け量ＵＰ）することができるとともに、シリンダ幅Ｈｃに対する仕切板の幅Ｈｓを極力小さくし、上部軸受２２および下部軸受２３の支持点間距離Ｌを小さくすることにより、軸受面圧の上昇を抑制することができる。従って、既存のモータコア径ΦＭｏのままで、１ランク上の押し退け量を持つ密閉型の多気筒ロータリ圧縮機１を製造でき、大きな設備投資を行うことなく、製品ラインナップの拡充を図ることができる。
Thus, without changing the motor core diameter ΦMo, without increasing the gas load (compression load), the strokes of the blades 28 and 29 are lengthened, and the displacement amount of the multi-cylinder rotary compressor 1 is increased (pushing away). Amount), and the partition plate width Hs with respect to the cylinder width Hc is made as small as possible, and the distance L between the support points of the upper bearing 22 and the lower bearing 23 is made smaller, thereby suppressing an increase in bearing surface pressure. be able to. Therefore, the sealed multi-cylinder rotary compressor 1 having a displacement amount higher by one rank can be manufactured with the existing motor core diameter ΦMo, and the product lineup can be expanded without making a large capital investment.
また、仕切板２１の幅Ｈｓを、Ｈｓ／Ｈｃ≦０．３５として薄幅化することにより、仕切板２１の変形の可能性が生じるが、仕切板２１をヤング率が１６０［ＧＰａ］以上の例えば、炭素鋼もしくは合金鋼等の素材で構成することにより、仕切板２１の幅Ｈｓをシリンダ幅Ｈｃの０．３５以下に薄幅化したとしても、その変形を抑制することができる。従って、軸受面圧等のメカ負荷の増大を抑制し、モータコア径ΦＭｏを変更せずに、シリンダ内径ΦＤｃを大きくして簡易に多気筒ロータリ圧縮機１の押し退け量を１ランク上の容量に大容量化することができる。
Further, by reducing the width Hs of the partition plate 21 as Hs / Hc ≦ 0.35, the partition plate 21 may be deformed, but the partition plate 21 has a Young's modulus of 160 [GPa] or more. For example, even if the width Hs of the partition plate 21 is reduced to 0.35 or less of the cylinder width Hc by being made of a material such as carbon steel or alloy steel, the deformation can be suppressed. Therefore, an increase in mechanical load such as bearing surface pressure is suppressed, the cylinder inner diameter ΦDc is increased without changing the motor core diameter ΦMo, and the displacement amount of the multi-cylinder rotary compressor 1 is easily increased to a capacity one rank higher. Capacitance can be achieved.
さらに、シリンダ内径ΦＤｃを大きくして大容量化することにより、ブレード２８，２９のストロークがロングストローク化し、ブレードサイド面圧が上昇するが、ブレード表面にＣｒＮ系等のＰＶＤ膜もしくはＤＬＣ膜等の硬質被膜を施すことにより、ブレードサイド面圧の上昇による異常摩耗等にも十分対応することができる。このため、モータ５のコア径ΦＭｏを変えずにシリンダ内径ΦＤｃを大きくし、設備投資を行わずに、簡易に多気筒ロータリ圧縮機１の押し退け量を１ランク上の容量に大容量化することができる。
Furthermore, by increasing the cylinder inner diameter ΦDc to increase the capacity, the strokes of the blades 28 and 29 become longer and the blade side surface pressure rises. However, a CrN-based PVD film or DLC film or the like is formed on the blade surface. By applying a hard coating, it is possible to sufficiently cope with abnormal wear caused by an increase in blade side surface pressure. For this reason, the cylinder inner diameter ΦDc is increased without changing the core diameter ΦMo of the motor 5, and the displacement amount of the multi-cylinder rotary compressor 1 is simply increased to a capacity one rank higher without making capital investment. Can do.
また、密閉容器２の底部に充填される冷凍機油３４に極圧剤を添加しているため、圧縮機の大容量化に伴って、軸受面圧やブレードサイド面圧等のメカ負荷が多少増大することは避けられず、それらの摺動部分において極圧潤滑状態が発生し易くなるが、高荷重下で有効な極圧剤を冷凍機油に添加しておくことにより、摺動面での高潤滑性を維持し、焼き付きや摩耗、スカッフィングを防止することができる。これによって、ロータリ圧縮機１の大容量化に伴うメカ負荷の増大にも有効に対応することができる。
In addition, since extreme pressure agent is added to the refrigerating machine oil 34 filled in the bottom of the hermetic container 2, mechanical loads such as bearing surface pressure and blade side surface pressure increase somewhat as the compressor capacity increases. It is inevitable that extreme pressure lubrication is likely to occur in these sliding parts.However, by adding an extreme pressure agent effective under high load to the refrigerating machine oil, high pressure on the sliding surface can be obtained. Maintains lubricity and prevents seizure, wear and scuffing. Thereby, it is possible to effectively cope with an increase in mechanical load accompanying an increase in capacity of the rotary compressor 1.
なお、本発明は、上記実施形態にかかる発明に限定されるものではなく、その要旨を逸脱しない範囲において、適宜変形が可能である。例えば、上記実施形態において、第１ロータリ圧縮機構６Ａと第２ロータリ圧縮機構６Ｂとは、１８０度位相をずらして設けられることは云うまでもない。また、吐出チャンバー３２，３３は、吐出チャンバー３３に吐出された高圧ガスを吐出チャンバー３２で合流して密閉容器２内に吐き出す構成としてもよいことはもちろんである。さらに、第１シリンダ室１７と第２シリンダ室１８との幅Ｈｃは、必ずしも同一である必要はなく、異なる幅としてもよく、この場合、幅Ｈｃが大きい方を基準にすればよい。
In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, in the embodiment described above, it goes without saying that the first rotary compression mechanism 6A and the second rotary compression mechanism 6B are provided with a phase difference of 180 degrees. Of course, the discharge chambers 32 and 33 may be configured such that the high-pressure gas discharged into the discharge chamber 33 is merged in the discharge chamber 32 and discharged into the sealed container 2. Furthermore, the widths Hc of the first cylinder chamber 17 and the second cylinder chamber 18 are not necessarily the same, and may be different widths. In this case, the width Hc may be based on the larger one.
１ 多気筒ロータリ圧縮機
２ 密閉容器
５ モータ
６ 圧縮機構（ロータリ圧縮機構）
６Ａ 第１ロータリ圧縮機構
６Ｂ 第２ロータリ圧縮機構
１４ クランク軸
１５ 第１偏心部
１６ 第２偏心部
１７ 第１シリンダ室（シリンダ）
１８ 第２シリンダ室（シリンダ）
１９ 第１シリンダ本体
２０ 第２シリンダ本体
２１ 仕切板
２４ 第１ロータ
２５ 第２ロータ
２８，２９ ブレード
３４ 冷凍機油
ΦＭｏ モータコア径
ΦＤｃ シリンダ内径
Ｈｃ シリンダ幅
Ｈｓ 仕切板幅 1 Multi-cylinder rotary compressor 2 Sealed container 5 Motor 6 Compression mechanism (rotary compression mechanism)
6A First rotary compression mechanism 6B Second rotary compression mechanism 14 Crankshaft 15 First eccentric portion 16 Second eccentric portion 17 First cylinder chamber (cylinder)
18 Second cylinder chamber (cylinder)
19 First cylinder body 20 Second cylinder body 21 Partition plate 24 First rotor 25 Second rotor 28, 29 Blade 34 Refrigerating machine oil ΦMo Motor core diameter ΦDc Cylinder inner diameter Hc Cylinder width Hs Partition plate width
２ 密閉容器
５ モータ
６ 圧縮機構（ロータリ圧縮機構）
６Ａ 第１ロータリ圧縮機構
６Ｂ 第２ロータリ圧縮機構
１４ クランク軸
１５ 第１偏心部
１６ 第２偏心部
１７ 第１シリンダ室（シリンダ）
１８ 第２シリンダ室（シリンダ）
１９ 第１シリンダ本体
２０ 第２シリンダ本体
２１ 仕切板
２４ 第１ロータ
２５ 第２ロータ
２８，２９ ブレード
３４ 冷凍機油
ΦＭｏ モータコア径
ΦＤｃ シリンダ内径
Ｈｃ シリンダ幅
Ｈｓ 仕切板幅 1 Multi-cylinder rotary compressor 2 Sealed container 5 Motor 6 Compression mechanism (rotary compression mechanism)
6A First rotary compression mechanism 6B Second rotary compression mechanism 14 Crankshaft 15 First eccentric portion 16 Second eccentric portion 17 First cylinder chamber (cylinder)
18 Second cylinder chamber (cylinder)
19 First cylinder body 20 Second cylinder body 21 Partition plate 24 First rotor 25 Second rotor 28, 29 Blade 34 Refrigerating machine oil ΦMo Motor core diameter ΦDc Cylinder inner diameter Hc Cylinder width Hs Partition plate width
Claims (5)
- 密閉容器内にモータと、該モータにより駆動される圧縮機構とが設けられ、該圧縮機構が複数のシリンダと、該複数のシリンダ間を仕切る仕切板と、前記各シリンダ内を吸入側と吐出側とに仕切るブレードと、前記各シリンダ内を回動するロータとを備えたロータリ圧縮機構とされている多気筒ロータリ圧縮機であって、
前記モータのコア径をΦＭｏ、前記各シリンダの内径をΦＤｃ、前記各シリンダの幅をＨｃ、前記仕切板の幅をＨｓとしたとき、
ΦＤｃ／ΦＭｏ≧０．４９の条件下において、
Ｈｓ／Ｈｃ≦０．３５
を満たしている多気筒ロータリ圧縮機。 A motor and a compression mechanism driven by the motor are provided in the sealed container. The compression mechanism includes a plurality of cylinders, a partition plate for partitioning the plurality of cylinders, and a suction side and a discharge side in each cylinder. A multi-cylinder rotary compressor that is a rotary compression mechanism that includes a blade that divides the cylinder and a rotor that rotates in each cylinder,
When the core diameter of the motor is ΦMo, the inner diameter of each cylinder is ΦDc, the width of each cylinder is Hc, and the width of the partition plate is Hs,
Under the condition of ΦDc / ΦMo ≧ 0.49,
Hs / Hc ≦ 0.35
Meets the multi-cylinder rotary compressor. - 前記仕切板は、ヤング率１６０［ＧＰａ］以上の素材で構成されている請求項１に記載の多気筒ロータリ圧縮機。 The multi-cylinder rotary compressor according to claim 1, wherein the partition plate is made of a material having a Young's modulus of 160 [GPa] or more.
- 前記仕切板は、炭素鋼もしくは合金鋼とされている請求項２に記載の多気筒ロータリ圧縮機。 The multi-cylinder rotary compressor according to claim 2, wherein the partition plate is made of carbon steel or alloy steel.
- 前記ブレードは、表面にＣｒＮ系等のＰＶＤ膜もしくはＤＬＣ膜等の硬質被膜が施されたブレードとされている請求項１ないし３のいずれかに記載の多気筒ロータリ圧縮機。 The multi-cylinder rotary compressor according to any one of claims 1 to 3, wherein the blade is a blade having a surface coated with a hard coating such as a PVD film such as CrN or a DLC film.
- 前記密閉容器内の底部に充填される冷凍機油は、極圧剤を添加した冷凍機油とされている請求項１ないし４のいずれかに記載の多気筒ロータリ圧縮機。 The multi-cylinder rotary compressor according to any one of claims 1 to 4, wherein the refrigerating machine oil filled in the bottom of the sealed container is a refrigerating machine oil to which an extreme pressure agent is added.
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| WO2017138175A1 (en) * | 2016-02-12 | 2017-08-17 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
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| CN108788658A (en) * | 2018-06-08 | 2018-11-13 | 宁波甬微集团有限公司 | The production method of partition board in a kind of multicylinder compressor |
| CN109083843A (en) * | 2018-07-22 | 2018-12-25 | 宁波甬微集团有限公司 | The production method of partition in a kind of multicylinder compressor |
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| JPH03206387A (en) * | 1990-01-08 | 1991-09-09 | Hitachi Ltd | Rotary type compressor |
| JPH03258984A (en) * | 1990-03-06 | 1991-11-19 | Matsushita Refrig Co Ltd | Two-cylinder rotary compressor |
| JPH06159277A (en) * | 1992-11-26 | 1994-06-07 | Sanyo Electric Co Ltd | Multi-cylinder rotary compressor |
| JPH109168A (en) * | 1996-06-28 | 1998-01-13 | Hitachi Ltd | Rotary compressor |
| JP2005257240A (en) * | 2004-03-15 | 2005-09-22 | Sanyo Electric Co Ltd | Transition critical refrigerating device |
| JP2008101523A (en) * | 2006-10-18 | 2008-05-01 | Daikin Ind Ltd | Hermetic compressor |
| JP4365729B2 (en) | 2004-05-31 | 2009-11-18 | 三菱重工業株式会社 | Rotary compressor |
| WO2011148453A1 (en) * | 2010-05-24 | 2011-12-01 | 三菱電機株式会社 | Two-stage rotary compressor and heat pump apparatus |
| WO2012032765A1 (en) * | 2010-09-07 | 2012-03-15 | パナソニック株式会社 | Compressor and refrigeration cycle device using same |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4780971B2 (en) * | 2005-02-17 | 2011-09-28 | 三洋電機株式会社 | Rotary compressor |
-
2013
- 2013-03-29 JP JP2013073093A patent/JP2014196714A/en active Pending
-
2014
- 2014-03-13 WO PCT/JP2014/056650 patent/WO2014156679A1/en active Application Filing
- 2014-03-13 EP EP14774791.9A patent/EP2947321A4/en not_active Withdrawn
- 2014-03-13 CN CN201480008720.0A patent/CN105008722A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59165885A (en) * | 1983-03-09 | 1984-09-19 | Matsushita Refrig Co | Rotary compressor with multiple cylinders |
| JPS61126395A (en) * | 1984-11-22 | 1986-06-13 | Mitsubishi Electric Corp | 2-cylinder type rotary compressor |
| JPH03206387A (en) * | 1990-01-08 | 1991-09-09 | Hitachi Ltd | Rotary type compressor |
| JPH03258984A (en) * | 1990-03-06 | 1991-11-19 | Matsushita Refrig Co Ltd | Two-cylinder rotary compressor |
| JPH06159277A (en) * | 1992-11-26 | 1994-06-07 | Sanyo Electric Co Ltd | Multi-cylinder rotary compressor |
| JPH109168A (en) * | 1996-06-28 | 1998-01-13 | Hitachi Ltd | Rotary compressor |
| JP2005257240A (en) * | 2004-03-15 | 2005-09-22 | Sanyo Electric Co Ltd | Transition critical refrigerating device |
| JP4365729B2 (en) | 2004-05-31 | 2009-11-18 | 三菱重工業株式会社 | Rotary compressor |
| JP2008101523A (en) * | 2006-10-18 | 2008-05-01 | Daikin Ind Ltd | Hermetic compressor |
| WO2011148453A1 (en) * | 2010-05-24 | 2011-12-01 | 三菱電機株式会社 | Two-stage rotary compressor and heat pump apparatus |
| WO2012032765A1 (en) * | 2010-09-07 | 2012-03-15 | パナソニック株式会社 | Compressor and refrigeration cycle device using same |
Non-Patent Citations (1)
| Title |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105201845A (en) * | 2015-10-22 | 2015-12-30 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN105201845B (en) * | 2015-10-22 | 2017-11-07 | 广东美芝制冷设备有限公司 | Rotary compressor |
| WO2017138175A1 (en) * | 2016-02-12 | 2017-08-17 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2947321A1 (en) | 2015-11-25 |
| EP2947321A4 (en) | 2016-02-24 |
| JP2014196714A (en) | 2014-10-16 |
| CN105008722A (en) | 2015-10-28 |
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