WO2018168345A1 - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- WO2018168345A1 WO2018168345A1 PCT/JP2018/005745 JP2018005745W WO2018168345A1 WO 2018168345 A1 WO2018168345 A1 WO 2018168345A1 JP 2018005745 W JP2018005745 W JP 2018005745W WO 2018168345 A1 WO2018168345 A1 WO 2018168345A1
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- Prior art keywords
- shell
- discharge pipe
- rotary compressor
- compression mechanism
- pipe
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Definitions
- the present invention relates to a rotary compressor used in an outdoor unit or refrigerator of an air conditioner.
- a rotary compressor used in an outdoor unit or a refrigerator of an air conditioner includes an electric motor part and a compression mechanism part in a sealed container, and the electric motor part and the compression mechanism part are connected by a shaft, and the shaft is eccentric. The piston attached to the part is revolved by the rotation of the shaft.
- positions a shaft to a perpendicular direction what does not arrange
- Patent Document 1 and Patent Document 2 a terminal is arranged on the shell for the purpose of reducing the overall height of the rotary compressor.
- Patent Documents 3 to 7 a rotary compressor of the type in which the electric mechanism portion and the compression mechanism portion are arranged in the vertical direction and the shaft is arranged in the vertical direction has been proposed in which the discharge pipe is arranged at a position other than the central portion of the upper shell.
- Patent Documents 3 to 6 are not clearly described, since the discharge pipe and the terminal are arranged on the upper shell, the discharge pipe is arranged at a position other than the central portion in relation to the terminal. is doing.
- Patent Document 7 there is no description of the terminal, but the discharge pipe is arranged at a position other than the central portion.
- the discharge pipe is placed at the center of the upper shell unless there is any restriction such as terminal placement.
- the center of gravity of the rotary compressor is not the central portion of the upper shell due to the accumulator, if the discharge pipe is arranged at the central portion of the upper shell, the vibration of the discharge pipe increases.
- the vibration of the discharge pipe increases, the vibration is transmitted to the pipe connected to the discharge pipe, the stress applied to the pipe also increases, and the pipe may be damaged.
- an object of the present invention is to provide a rotary compressor that can reduce vibration transmitted to a pipe connected to the discharge pipe by reducing vibration of the discharge pipe.
- a rotary compressor includes an electric motor section and a compression mechanism section in a sealed container, and the sealed container is formed as a cylindrical shell extending in a vertical direction, The upper shell for closing the upper opening of the shell shell, and the lower shell for closing the lower opening of the shell shell, the suction shell for introducing the suction refrigerant into the compression mechanism portion, the motor shell portion
- a rotary compressor having an accumulator provided upstream of the suction pipe, connected to a terminal for feeding power, connected to the upper shell, and a discharge pipe for leading the discharge refrigerant compressed by the compression mechanism.
- a rotary compressor according to a second aspect of the present invention is the rotary compressor according to the first aspect, wherein the discharge pipe is arranged at the gravity center position G.
- the vibration of the discharge pipe can be reduced, and the vibration transmitted to the pipe connected to the discharge pipe can be reduced.
- FIG. 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention.
- Top view conceptual diagram showing the position of the discharge pipe of the rotary compressor
- the discharge pipe when the diameter of the trunk shell is D and the center of gravity position of the upper shell that is on the vertical line of the center of gravity including the accumulator is the center of gravity position G, the discharge pipe has a radius D / 10 around G. It is arranged within the range. According to the first aspect, the vibration of the discharge pipe can be reduced, the vibration transmitted to the pipe connected to the discharge pipe can be reduced, and the pipe stress can be reduced.
- the discharge pipe is arranged at the gravity center position G. According to the second aspect, the vibration of the discharge pipe can be reduced most.
- FIG. 1 is a sectional view of a rotary compressor according to this embodiment.
- the rotary compressor according to this embodiment includes an electric motor unit 20 and a compression mechanism unit 30 in the hermetic container 10.
- the electric motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40.
- the sealed container 10 includes a cylindrical shell 10a that extends in the vertical direction, an upper shell 10b that closes an upper opening of the shell 10a, and a lower shell 10c that closes a lower opening of the shell 10a.
- the electric motor unit 20 includes a stator 21 that is fixed to the inner surface of the sealed container 10 and a rotor 22 that rotates within the stator 21.
- the rotary compressor according to the present embodiment includes a first compression mechanism unit 30 ⁇ / b> A and a second compression mechanism unit 30 ⁇ / b> B as the compression mechanism unit 30.
- the first compression mechanism 30A includes a first cylinder 31A, a first piston 32A disposed in the first cylinder 31A, and a vane (not shown) that partitions the first cylinder 31A.
- 32A revolves in the first cylinder 31A, and sucks and compresses the low-pressure refrigerant gas.
- the second compression mechanism 30B includes a second cylinder 31B, a second piston 32B disposed in the second cylinder 31B, and a vane that partitions the second cylinder 31B (not shown). 2), and the second piston 32B revolves in the second cylinder 31B to suck in and compress the low-pressure refrigerant gas.
- a main bearing 51 is disposed on one surface of the first cylinder 31A, and an intermediate plate 52 is disposed on the other surface of the first cylinder 31A.
- An intermediate plate 52 is disposed on one surface of the second cylinder 31B, and a sub-bearing 53 is disposed on the other surface of the second cylinder 31B. That is, the intermediate plate 52 partitions the first cylinder 31A and the second cylinder 31B.
- the middle plate 52 has an opening larger than the diameter of the shaft 40.
- the shaft 40 includes a main shaft portion 41 to which the rotor 22 is attached and supported by the main bearing 51, a first eccentric portion 42 to which the first piston 32A is attached, a second eccentric portion 43 to which the second piston 32B is attached, and a sub-bearing. And a countershaft portion 44 supported by 53.
- the first eccentric part 42 and the second eccentric part 43 are formed with a phase difference of 180 degrees, and a connecting shaft part 45 is formed between the first eccentric part 42 and the second eccentric part 43. .
- the first compression chamber 34A is formed between the main bearing 51 and the intermediate plate 52 between the inner peripheral surface of the first cylinder 31A and the outer peripheral surface of the first piston 32A.
- the second compression chamber 34B is formed between the inner peripheral surface of the second cylinder 31B and the outer peripheral surface of the second piston 32B between the intermediate plate 52 and the auxiliary bearing 53.
- the first compression chamber 34A and the second compression chamber 34B have the same volume. That is, the inner diameter of the first cylinder 31A and the inner diameter of the second cylinder 31B are the same, and the outer diameter of the first piston 32A and the outer diameter of the second piston 32B are the same.
- the inner circumferential height of the first cylinder 31A and the inner circumferential height of the second cylinder 31B are the same, and the first piston 32A height and the second piston 32B height are the same.
- An oil sump 11 is formed at the bottom of the sealed container 10, and an oil pickup 12 is provided at the lower end of the shaft 40.
- an oil supply passage is formed in the shaft 40 in the axial direction, and a communication passage for supplying oil to the sliding surface of the compression mechanism unit 30 is formed in the oil supply passage.
- first suction pipe 13A and a second suction pipe 13B Connected to the shell 10a are a first suction pipe 13A and a second suction pipe 13B for introducing the suction refrigerant into the compression mechanism section 30, and a terminal 50 for supplying power to the motor section 20.
- a discharge pipe 14 is connected to the upper shell 10b.
- the terminal 50 is disposed above the electric motor unit 20.
- the first suction pipe 13A is connected to the first compression chamber 34A
- the second suction pipe 13B is connected to the second compression chamber 34B.
- An accumulator 15 is provided on the upstream side of the first suction pipe 13A and the second suction pipe 13B. The accumulator 15 separates the refrigerant returned from the refrigeration cycle into a liquid refrigerant and a gas refrigerant.
- Gas refrigerant flows through the first suction pipe 13A and the second suction pipe 13B.
- the accumulator 15 and the terminal 50 are disposed at symmetrical positions with respect to the center of the shell 10a. Due to the rotation of the shaft 40, the first piston 32A and the second piston 32B revolve in the first compression chamber 34A and the second compression chamber 34B. The gas refrigerant sucked into the first compression chamber 34A and the second compression chamber 34B from the first suction pipe 13A and the second suction pipe 13B by the revolving motion of the first piston 32A and the second piston 32B is converted into the first compression chamber 34A.
- FIG. 2 is a top conceptual view showing the position of the discharge pipe of the rotary compressor according to this embodiment.
- the discharge pipe 14 when the diameter of the trunk shell 10a is D and the center of gravity position of the upper shell 10b on the vertical line of the center of gravity including the accumulator 15 is G, the discharge pipe 14 has a radius D / It arrange
- the vibration of the discharge pipe 14 can be reduced, and the vibration transmitted to the pipe connected to the discharge pipe 14 can be reduced. Pipe stress can be reduced. Further, by arranging the discharge pipe 14 at the center of gravity position G, the vibration of the discharge pipe 14 can be reduced most.
- the present invention can also be applied to a single cylinder rotary compressor.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Provided is a rotary compressor, wherein: a sealed container 10 is composed of a barrel shell 10a that extends in the vertical direction and is cylindrically formed, an upper shell 10b that closes the upper opening of the barrel shell 10a, and a lower shell 10c that closes the lower opening of the barrel shell 10a; suction pipes 13A, 13B through which an intake refrigerant is introduced to a compression mechanism part 30 and a terminal 50 through which power is fed to an electric motor part 20 are connected to the barrel shell 10a; a discharge pipe 14, through which a discharge refrigerant compressed at the compression mechanism part 30 is discharged, is connected to the upper shell 10b; an accumulator 15 is provided on the upstream side of the suction pipes 13A, 13B; and, in the case where the diameter of the barrel shell 10a is D and the center of gravity position at the upper shell 10b on a vertical line of the center of gravity including the accumulator 15 is G, by disposing the discharge pipe 14 in the range of a radius D/10 around G, vibration of the discharge pipe 14 can be reduced and thus vibration transmitted to a pipe connected to the discharge pipe 14 can be reduced.
Description
本発明は空気調和機の室外機や冷凍機に用いられるロータリー式圧縮機に関するものである。
The present invention relates to a rotary compressor used in an outdoor unit or refrigerator of an air conditioner.
一般に、空気調和機の室外機や冷凍機に用いられるロータリー式圧縮機は、密閉容器内に電動機部と圧縮機構部とを備え、電動機部と圧縮機構部とをシャフトによって連結し、シャフトの偏心部に取り付けたピストンを、シャフトの回転によって公転運動させる。
そして、電動機構部と圧縮機構部とを上下方向に配置し、シャフトを鉛直方向に配置するタイプのロータリー式圧縮機において、ターミナルを上シェル上部に配置しないものが提案されている（特許文献１、特許文献２）。
特許文献１及び特許文献２は、ロータリー式圧縮機の全高を低減する目的でターミナルを胴シェルに配置している。
また、電動機構部と圧縮機構部とを上下方向に配置し、シャフトを鉛直方向に配置するタイプのロータリー式圧縮機において、吐出管を上シェルの中央部でない位置に配置するものが提案されている（特許文献３～特許文献７）。
特許文献３～特許文献６は、明らかに記載されていないものもあるが、上シェルに吐出管とターミナルとを配置しているために、ターミナルとの関係で吐出管を中央部でない位置に配置している。
特許文献７は、ターミナルの記載はないが、吐出管を中央部でない位置に配置している。 Generally, a rotary compressor used in an outdoor unit or a refrigerator of an air conditioner includes an electric motor part and a compression mechanism part in a sealed container, and the electric motor part and the compression mechanism part are connected by a shaft, and the shaft is eccentric. The piston attached to the part is revolved by the rotation of the shaft.
And in the rotary compressor of the type which arrange | positions an electric mechanism part and a compression mechanism part to an up-down direction, and arrange | positions a shaft to a perpendicular direction, what does not arrange | position a terminal to the upper shell upper part is proposed (patent document 1). Patent Document 2).
In Patent Document 1 and Patent Document 2, a terminal is arranged on the shell for the purpose of reducing the overall height of the rotary compressor.
In addition, a rotary compressor of the type in which the electric mechanism portion and the compression mechanism portion are arranged in the vertical direction and the shaft is arranged in the vertical direction has been proposed in which the discharge pipe is arranged at a position other than the central portion of the upper shell. (Patent Documents 3 to 7).
Although Patent Documents 3 to 6 are not clearly described, since the discharge pipe and the terminal are arranged on the upper shell, the discharge pipe is arranged at a position other than the central portion in relation to the terminal. is doing.
In Patent Document 7, there is no description of the terminal, but the discharge pipe is arranged at a position other than the central portion.
そして、電動機構部と圧縮機構部とを上下方向に配置し、シャフトを鉛直方向に配置するタイプのロータリー式圧縮機において、ターミナルを上シェル上部に配置しないものが提案されている（特許文献１、特許文献２）。
特許文献１及び特許文献２は、ロータリー式圧縮機の全高を低減する目的でターミナルを胴シェルに配置している。
また、電動機構部と圧縮機構部とを上下方向に配置し、シャフトを鉛直方向に配置するタイプのロータリー式圧縮機において、吐出管を上シェルの中央部でない位置に配置するものが提案されている（特許文献３～特許文献７）。
特許文献３～特許文献６は、明らかに記載されていないものもあるが、上シェルに吐出管とターミナルとを配置しているために、ターミナルとの関係で吐出管を中央部でない位置に配置している。
特許文献７は、ターミナルの記載はないが、吐出管を中央部でない位置に配置している。 Generally, a rotary compressor used in an outdoor unit or a refrigerator of an air conditioner includes an electric motor part and a compression mechanism part in a sealed container, and the electric motor part and the compression mechanism part are connected by a shaft, and the shaft is eccentric. The piston attached to the part is revolved by the rotation of the shaft.
And in the rotary compressor of the type which arrange | positions an electric mechanism part and a compression mechanism part to an up-down direction, and arrange | positions a shaft to a perpendicular direction, what does not arrange | position a terminal to the upper shell upper part is proposed (patent document 1). Patent Document 2).
In Patent Document 1 and Patent Document 2, a terminal is arranged on the shell for the purpose of reducing the overall height of the rotary compressor.
In addition, a rotary compressor of the type in which the electric mechanism portion and the compression mechanism portion are arranged in the vertical direction and the shaft is arranged in the vertical direction has been proposed in which the discharge pipe is arranged at a position other than the central portion of the upper shell. (Patent Documents 3 to 7).
Although Patent Documents 3 to 6 are not clearly described, since the discharge pipe and the terminal are arranged on the upper shell, the discharge pipe is arranged at a position other than the central portion in relation to the terminal. is doing.
In Patent Document 7, there is no description of the terminal, but the discharge pipe is arranged at a position other than the central portion.
特許文献１及び特許文献２では、ロータリー式圧縮機の全高を低減する目的でターミナルを胴シェルに配置しているため、吐出管についても上シェルに配置していない。
特許文献２～特許文献７では、吐出管を中央部でない位置に配置しているが、吐出管の振動を課題としておらず、従って、中央部からどの方向にずらすかについては何ら記載されていない。
ロータリー式圧縮機では、特許文献３、特許文献５、特許文献６、及び特許文献７に記載の通り、吐出管を上シェルの中央部からずらすと、吐出冷媒にオイルが多く混入してしまうという技術常識により、ターミナルの配置などの制約が無い限り吐出管を上シェルの中央部に配置する。
しかし、ロータリー式圧縮機の重心は、アキュムレータによって上シェルの中央部ではないため、吐出管を上シェルの中央部に配置すると、吐出管の振動が大きくなる。
吐出管の振動が大きくなると、吐出管に接続される配管に振動が伝達し、配管にかかる応力も大きくなり、配管が破損する可能性が生じてしまう。 In patent document 1 and patent document 2, since the terminal is arrange | positioned in the trunk | drum shell in order to reduce the total height of a rotary compressor, it is not arrange | positioned also about a discharge pipe in the upper shell.
In Patent Document 2 to Patent Document 7, the discharge pipe is arranged at a position other than the central part, but vibration of the discharge pipe is not a problem, and therefore, there is no description about which direction to shift from the central part. .
In the rotary compressor, as described in Patent Document 3, Patent Document 5, Patent Document 6, and Patent Document 7, if the discharge pipe is shifted from the center portion of the upper shell, a large amount of oil is mixed in the discharge refrigerant. According to the common general knowledge, the discharge pipe is placed at the center of the upper shell unless there is any restriction such as terminal placement.
However, since the center of gravity of the rotary compressor is not the central portion of the upper shell due to the accumulator, if the discharge pipe is arranged at the central portion of the upper shell, the vibration of the discharge pipe increases.
When the vibration of the discharge pipe increases, the vibration is transmitted to the pipe connected to the discharge pipe, the stress applied to the pipe also increases, and the pipe may be damaged.
特許文献２～特許文献７では、吐出管を中央部でない位置に配置しているが、吐出管の振動を課題としておらず、従って、中央部からどの方向にずらすかについては何ら記載されていない。
ロータリー式圧縮機では、特許文献３、特許文献５、特許文献６、及び特許文献７に記載の通り、吐出管を上シェルの中央部からずらすと、吐出冷媒にオイルが多く混入してしまうという技術常識により、ターミナルの配置などの制約が無い限り吐出管を上シェルの中央部に配置する。
しかし、ロータリー式圧縮機の重心は、アキュムレータによって上シェルの中央部ではないため、吐出管を上シェルの中央部に配置すると、吐出管の振動が大きくなる。
吐出管の振動が大きくなると、吐出管に接続される配管に振動が伝達し、配管にかかる応力も大きくなり、配管が破損する可能性が生じてしまう。 In patent document 1 and patent document 2, since the terminal is arrange | positioned in the trunk | drum shell in order to reduce the total height of a rotary compressor, it is not arrange | positioned also about a discharge pipe in the upper shell.
In Patent Document 2 to Patent Document 7, the discharge pipe is arranged at a position other than the central part, but vibration of the discharge pipe is not a problem, and therefore, there is no description about which direction to shift from the central part. .
In the rotary compressor, as described in Patent Document 3, Patent Document 5, Patent Document 6, and Patent Document 7, if the discharge pipe is shifted from the center portion of the upper shell, a large amount of oil is mixed in the discharge refrigerant. According to the common general knowledge, the discharge pipe is placed at the center of the upper shell unless there is any restriction such as terminal placement.
However, since the center of gravity of the rotary compressor is not the central portion of the upper shell due to the accumulator, if the discharge pipe is arranged at the central portion of the upper shell, the vibration of the discharge pipe increases.
When the vibration of the discharge pipe increases, the vibration is transmitted to the pipe connected to the discharge pipe, the stress applied to the pipe also increases, and the pipe may be damaged.
そこで本発明は、吐出管の振動を低減することで、吐出管に接続される配管に伝達する振動を低減できるロータリー式圧縮機を提供することを目的とする。
Therefore, an object of the present invention is to provide a rotary compressor that can reduce vibration transmitted to a pipe connected to the discharge pipe by reducing vibration of the discharge pipe.
請求項１記載の本発明のロータリー式圧縮機は、密閉容器内に電動機部と圧縮機構部とを備え、前記密閉容器は、上下方向に沿って延びる円筒状に形成された胴シェルと、前記胴シェルの上部開口を塞ぐ上シェルと、前記胴シェルの下部開口を塞ぐ下シェルとで構成され、前記胴シェルには、前記圧縮機構部に吸入冷媒を導入する吸入管と、前記電動機部に給電するターミナルとが接続され、前記上シェルには、前記圧縮機構部で圧縮された吐出冷媒を導出する吐出管が接続され、前記吸入管の上流側にはアキュムレータを設けたロータリー式圧縮機であって、前記胴シェルの直径をＤ、前記アキュムレータを含む重心の鉛直線上となる前記上シェルでの重心位置をＧとした時、前記吐出管を、前記重心位置Ｇを中心として半径Ｄ／１０の範囲内に配置したことを特徴とする。
請求項２記載の本発明のロータリー式圧縮機は、請求項１に記載のロータリー式圧縮機において、前記吐出管を、前記重心位置Ｇに配置したことを特徴とする。 A rotary compressor according to a first aspect of the present invention includes an electric motor section and a compression mechanism section in a sealed container, and the sealed container is formed as a cylindrical shell extending in a vertical direction, The upper shell for closing the upper opening of the shell shell, and the lower shell for closing the lower opening of the shell shell, the suction shell for introducing the suction refrigerant into the compression mechanism portion, the motor shell portion A rotary compressor having an accumulator provided upstream of the suction pipe, connected to a terminal for feeding power, connected to the upper shell, and a discharge pipe for leading the discharge refrigerant compressed by the compression mechanism. When the diameter of the trunk shell is D and the center of gravity position of the upper shell, which is on the vertical line of the center of gravity including the accumulator, is G, the discharge pipe has a radius D / 10 around the center of gravity position G. Range of Characterized in that arranged within.
A rotary compressor according to a second aspect of the present invention is the rotary compressor according to the first aspect, wherein the discharge pipe is arranged at the gravity center position G.
請求項２記載の本発明のロータリー式圧縮機は、請求項１に記載のロータリー式圧縮機において、前記吐出管を、前記重心位置Ｇに配置したことを特徴とする。 A rotary compressor according to a first aspect of the present invention includes an electric motor section and a compression mechanism section in a sealed container, and the sealed container is formed as a cylindrical shell extending in a vertical direction, The upper shell for closing the upper opening of the shell shell, and the lower shell for closing the lower opening of the shell shell, the suction shell for introducing the suction refrigerant into the compression mechanism portion, the motor shell portion A rotary compressor having an accumulator provided upstream of the suction pipe, connected to a terminal for feeding power, connected to the upper shell, and a discharge pipe for leading the discharge refrigerant compressed by the compression mechanism. When the diameter of the trunk shell is D and the center of gravity position of the upper shell, which is on the vertical line of the center of gravity including the accumulator, is G, the discharge pipe has a radius D / 10 around the center of gravity position G. Range of Characterized in that arranged within.
A rotary compressor according to a second aspect of the present invention is the rotary compressor according to the first aspect, wherein the discharge pipe is arranged at the gravity center position G.
本発明によれば、吐出管の振動を低減でき、吐出管に接続される配管に伝達する振動を低減できる。
According to the present invention, the vibration of the discharge pipe can be reduced, and the vibration transmitted to the pipe connected to the discharge pipe can be reduced.
本発明の第１態様は、胴シェルの直径をＤ、アキュムレータを含む重心の鉛直線上となる上シェルでの重心位置を重心位置Ｇとした時、吐出管を、Ｇを中心として半径Ｄ／１０の範囲内に配置したものである。第１態様によれば、吐出管の振動を低減でき、吐出管に接続される配管に伝達する振動を低減し、配管応力の低減を図ることができる。
In the first aspect of the present invention, when the diameter of the trunk shell is D and the center of gravity position of the upper shell that is on the vertical line of the center of gravity including the accumulator is the center of gravity position G, the discharge pipe has a radius D / 10 around G. It is arranged within the range. According to the first aspect, the vibration of the discharge pipe can be reduced, the vibration transmitted to the pipe connected to the discharge pipe can be reduced, and the pipe stress can be reduced.
本発明の第２態様は、第１態様に加え、吐出管を、重心位置Ｇに配置したものである。第２態様によれば、吐出管の振動を最も低減できる。
In the second aspect of the present invention, in addition to the first aspect, the discharge pipe is arranged at the gravity center position G. According to the second aspect, the vibration of the discharge pipe can be reduced most.
以下、本発明の一実施例について図面を参照しながら説明する。
図１は、本実施例によるロータリー式圧縮機の断面図である。
本実施例によるロータリー式圧縮機は、密閉容器１０内に電動機部２０と圧縮機構部３０とを備えている。電動機部２０と圧縮機構部３０とはシャフト４０によって連結されている。
密閉容器１０は、上下方向に沿って延びる円筒状に形成された胴シェル１０ａと、胴シェル１０ａの上部開口を塞ぐ上シェル１０ｂと、胴シェル１０ａの下部開口を塞ぐ下シェル１０ｃとで構成されている。
電動機部２０は、密閉容器１０内面に固定される固定子２１と、固定子２１内で回転する回転子２２とから構成される。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a sectional view of a rotary compressor according to this embodiment.
The rotary compressor according to this embodiment includes anelectric motor unit 20 and a compression mechanism unit 30 in the hermetic container 10. The electric motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40.
The sealedcontainer 10 includes a cylindrical shell 10a that extends in the vertical direction, an upper shell 10b that closes an upper opening of the shell 10a, and a lower shell 10c that closes a lower opening of the shell 10a. ing.
Theelectric motor unit 20 includes a stator 21 that is fixed to the inner surface of the sealed container 10 and a rotor 22 that rotates within the stator 21.
図１は、本実施例によるロータリー式圧縮機の断面図である。
本実施例によるロータリー式圧縮機は、密閉容器１０内に電動機部２０と圧縮機構部３０とを備えている。電動機部２０と圧縮機構部３０とはシャフト４０によって連結されている。
密閉容器１０は、上下方向に沿って延びる円筒状に形成された胴シェル１０ａと、胴シェル１０ａの上部開口を塞ぐ上シェル１０ｂと、胴シェル１０ａの下部開口を塞ぐ下シェル１０ｃとで構成されている。
電動機部２０は、密閉容器１０内面に固定される固定子２１と、固定子２１内で回転する回転子２２とから構成される。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a sectional view of a rotary compressor according to this embodiment.
The rotary compressor according to this embodiment includes an
The sealed
The
本実施例によるロータリー式圧縮機は、圧縮機構部３０として、第１圧縮機構部３０Ａと第２圧縮機構部３０Ｂとを有している。
第１圧縮機構部３０Ａは、第１シリンダ３１Ａと、第１シリンダ３１Ａ内に配置される第１ピストン３２Ａと、第１シリンダ３１Ａ内を仕切るベーン（図示せず）とを有し、第１ピストン３２Ａが第１シリンダ３１Ａ内で公転運動することで、低圧の冷媒ガスを吸入して圧縮する。
第１圧縮機構部３０Ａと同様に、第２圧縮機構部３０Ｂは、第２シリンダ３１Ｂと、第２シリンダ３１Ｂ内に配置される第２ピストン３２Ｂと、第２シリンダ３１Ｂ内を仕切るベーン（図示せず）とを有し、第２ピストン３２Ｂが第２シリンダ３１Ｂ内で公転運動することで、低圧の冷媒ガスを吸入して圧縮する。 The rotary compressor according to the present embodiment includes a firstcompression mechanism unit 30 </ b> A and a second compression mechanism unit 30 </ b> B as the compression mechanism unit 30.
Thefirst compression mechanism 30A includes a first cylinder 31A, a first piston 32A disposed in the first cylinder 31A, and a vane (not shown) that partitions the first cylinder 31A. 32A revolves in the first cylinder 31A, and sucks and compresses the low-pressure refrigerant gas.
Similar to thefirst compression mechanism 30A, the second compression mechanism 30B includes a second cylinder 31B, a second piston 32B disposed in the second cylinder 31B, and a vane that partitions the second cylinder 31B (not shown). 2), and the second piston 32B revolves in the second cylinder 31B to suck in and compress the low-pressure refrigerant gas.
第１圧縮機構部３０Ａは、第１シリンダ３１Ａと、第１シリンダ３１Ａ内に配置される第１ピストン３２Ａと、第１シリンダ３１Ａ内を仕切るベーン（図示せず）とを有し、第１ピストン３２Ａが第１シリンダ３１Ａ内で公転運動することで、低圧の冷媒ガスを吸入して圧縮する。
第１圧縮機構部３０Ａと同様に、第２圧縮機構部３０Ｂは、第２シリンダ３１Ｂと、第２シリンダ３１Ｂ内に配置される第２ピストン３２Ｂと、第２シリンダ３１Ｂ内を仕切るベーン（図示せず）とを有し、第２ピストン３２Ｂが第２シリンダ３１Ｂ内で公転運動することで、低圧の冷媒ガスを吸入して圧縮する。 The rotary compressor according to the present embodiment includes a first
The
Similar to the
第１シリンダ３１Ａの一方の面には主軸受５１を配置し、第１シリンダ３１Ａの他方の面には中板５２を配置している。
また、第２シリンダ３１Ｂの一方の面には中板５２を配置し、第２シリンダ３１Ｂの他方の面には副軸受５３を配置している。
すなわち、中板５２は第１シリンダ３１Ａと第２シリンダ３１Ｂとを仕切る。中板５２は、シャフト４０の径よりも大きな開口部を有する。
シャフト４０は、回転子２２を取り付けて主軸受５１で支持される主軸部４１と、第１ピストン３２Ａを取り付ける第１偏心部４２と、第２ピストン３２Ｂを取り付ける第２偏心部４３と、副軸受５３で支持される副軸部４４とで構成される。
第１偏心部４２と第２偏心部４３とは１８０度の位相差を持って形成され、第１偏心部４２と第２偏心部４３との間には、連結軸部４５を形成している。 Amain bearing 51 is disposed on one surface of the first cylinder 31A, and an intermediate plate 52 is disposed on the other surface of the first cylinder 31A.
Anintermediate plate 52 is disposed on one surface of the second cylinder 31B, and a sub-bearing 53 is disposed on the other surface of the second cylinder 31B.
That is, theintermediate plate 52 partitions the first cylinder 31A and the second cylinder 31B. The middle plate 52 has an opening larger than the diameter of the shaft 40.
The shaft 40 includes amain shaft portion 41 to which the rotor 22 is attached and supported by the main bearing 51, a first eccentric portion 42 to which the first piston 32A is attached, a second eccentric portion 43 to which the second piston 32B is attached, and a sub-bearing. And a countershaft portion 44 supported by 53.
The firsteccentric part 42 and the second eccentric part 43 are formed with a phase difference of 180 degrees, and a connecting shaft part 45 is formed between the first eccentric part 42 and the second eccentric part 43. .
また、第２シリンダ３１Ｂの一方の面には中板５２を配置し、第２シリンダ３１Ｂの他方の面には副軸受５３を配置している。
すなわち、中板５２は第１シリンダ３１Ａと第２シリンダ３１Ｂとを仕切る。中板５２は、シャフト４０の径よりも大きな開口部を有する。
シャフト４０は、回転子２２を取り付けて主軸受５１で支持される主軸部４１と、第１ピストン３２Ａを取り付ける第１偏心部４２と、第２ピストン３２Ｂを取り付ける第２偏心部４３と、副軸受５３で支持される副軸部４４とで構成される。
第１偏心部４２と第２偏心部４３とは１８０度の位相差を持って形成され、第１偏心部４２と第２偏心部４３との間には、連結軸部４５を形成している。 A
An
That is, the
The shaft 40 includes a
The first
第１圧縮室３４Ａは、主軸受５１と中板５２との間で、第１シリンダ３１Ａ内周面と第１ピストン３２Ａ外周面との間に形成される。また、第２圧縮室３４Ｂは、中板５２と副軸受５３との間で、第２シリンダ３１Ｂ内周面と第２ピストン３２Ｂ外周面との間に形成される。
第１圧縮室３４Ａと第２圧縮室３４Ｂとの容積は同一である。すなわち、第１シリンダ３１Ａ内径と、第２シリンダ３１Ｂ内径とは同一であり、第１ピストン３２Ａ外径と第２ピストン３２Ｂ外径とは同一である。また、第１シリンダ３１Ａ内周高さと、第２シリンダ３１Ｂ内周高さとは同一であり、第１ピストン３２Ａ高さと第２ピストン３２Ｂ高さとは同一である。
密閉容器１０内の底部にはオイル溜め１１が形成され、シャフト４０の下端部にはオイルピックアップ１２を設けている。
また、図示はしないが、シャフト４０の内部には軸方向に給油路が形成され、給油路には、圧縮機構部３０の摺動面にオイルを供給するための連通路が形成されている。 Thefirst compression chamber 34A is formed between the main bearing 51 and the intermediate plate 52 between the inner peripheral surface of the first cylinder 31A and the outer peripheral surface of the first piston 32A. The second compression chamber 34B is formed between the inner peripheral surface of the second cylinder 31B and the outer peripheral surface of the second piston 32B between the intermediate plate 52 and the auxiliary bearing 53.
Thefirst compression chamber 34A and the second compression chamber 34B have the same volume. That is, the inner diameter of the first cylinder 31A and the inner diameter of the second cylinder 31B are the same, and the outer diameter of the first piston 32A and the outer diameter of the second piston 32B are the same. Further, the inner circumferential height of the first cylinder 31A and the inner circumferential height of the second cylinder 31B are the same, and the first piston 32A height and the second piston 32B height are the same.
Anoil sump 11 is formed at the bottom of the sealed container 10, and an oil pickup 12 is provided at the lower end of the shaft 40.
Although not shown, an oil supply passage is formed in the shaft 40 in the axial direction, and a communication passage for supplying oil to the sliding surface of thecompression mechanism unit 30 is formed in the oil supply passage.
第１圧縮室３４Ａと第２圧縮室３４Ｂとの容積は同一である。すなわち、第１シリンダ３１Ａ内径と、第２シリンダ３１Ｂ内径とは同一であり、第１ピストン３２Ａ外径と第２ピストン３２Ｂ外径とは同一である。また、第１シリンダ３１Ａ内周高さと、第２シリンダ３１Ｂ内周高さとは同一であり、第１ピストン３２Ａ高さと第２ピストン３２Ｂ高さとは同一である。
密閉容器１０内の底部にはオイル溜め１１が形成され、シャフト４０の下端部にはオイルピックアップ１２を設けている。
また、図示はしないが、シャフト４０の内部には軸方向に給油路が形成され、給油路には、圧縮機構部３０の摺動面にオイルを供給するための連通路が形成されている。 The
The
An
Although not shown, an oil supply passage is formed in the shaft 40 in the axial direction, and a communication passage for supplying oil to the sliding surface of the
胴シェル１０ａには、圧縮機構部３０に吸入冷媒を導入する第１吸入管１３Ａ及び第２吸入管１３Ｂと、電動機部２０に給電するターミナル５０とが接続されている。上シェル１０ｂには吐出管１４が接続されている。ターミナル５０は、電動機部２０よりも上方位置に配置している。
第１吸入管１３Ａは第１圧縮室３４Ａに、第２吸入管１３Ｂは第２圧縮室３４Ｂに、それぞれ接続されている。第１吸入管１３Ａ及び第２吸入管１３Ｂの上流側には、アキュムレータ１５を設けている。アキュムレータ１５は、冷凍サイクルから戻ってきた冷媒を、液冷媒とガス冷媒に分離する。第１吸入管１３Ａ及び第２吸入管１３Ｂにはガス冷媒が流れる。アキュムレータ１５とターミナル５０とは、胴シェル１０ａの中心に対して対称の位置に配置している。
シャフト４０の回転によって、第１ピストン３２Ａ及び第２ピストン３２Ｂは、第１圧縮室３４Ａ及び第２圧縮室３４Ｂ内で公転運動を行う。
第１ピストン３２Ａ及び第２ピストン３２Ｂの公転運動によって、第１吸入管１３Ａ及び第２吸入管１３Ｂから第１圧縮室３４Ａ及び第２圧縮室３４Ｂに吸入されたガス冷媒は、第１圧縮室３４Ａ及び第２圧縮室３４Ｂで圧縮された後に密閉容器１０内に吐出され、電動機部２０を通過して上昇する間にオイルを分離し、吐出管１４から密閉容器１０外に吐出される。
また、シャフト４０の回転によって、オイル溜め１１から吸い上げたオイルは、連通路から圧縮機構部３０に供給され、圧縮機構部３０の摺動面の潤滑を行う。 Connected to theshell 10a are a first suction pipe 13A and a second suction pipe 13B for introducing the suction refrigerant into the compression mechanism section 30, and a terminal 50 for supplying power to the motor section 20. A discharge pipe 14 is connected to the upper shell 10b. The terminal 50 is disposed above the electric motor unit 20.
Thefirst suction pipe 13A is connected to the first compression chamber 34A, and the second suction pipe 13B is connected to the second compression chamber 34B. An accumulator 15 is provided on the upstream side of the first suction pipe 13A and the second suction pipe 13B. The accumulator 15 separates the refrigerant returned from the refrigeration cycle into a liquid refrigerant and a gas refrigerant. Gas refrigerant flows through the first suction pipe 13A and the second suction pipe 13B. The accumulator 15 and the terminal 50 are disposed at symmetrical positions with respect to the center of the shell 10a.
Due to the rotation of the shaft 40, thefirst piston 32A and the second piston 32B revolve in the first compression chamber 34A and the second compression chamber 34B.
The gas refrigerant sucked into thefirst compression chamber 34A and the second compression chamber 34B from the first suction pipe 13A and the second suction pipe 13B by the revolving motion of the first piston 32A and the second piston 32B is converted into the first compression chamber 34A. After being compressed in the second compression chamber 34 </ b> B, it is discharged into the sealed container 10, oil is separated while rising through the electric motor unit 20, and discharged from the discharge pipe 14 to the outside of the sealed container 10.
Further, the oil sucked from theoil reservoir 11 by the rotation of the shaft 40 is supplied to the compression mechanism unit 30 from the communication path, and lubricates the sliding surface of the compression mechanism unit 30.
第１吸入管１３Ａは第１圧縮室３４Ａに、第２吸入管１３Ｂは第２圧縮室３４Ｂに、それぞれ接続されている。第１吸入管１３Ａ及び第２吸入管１３Ｂの上流側には、アキュムレータ１５を設けている。アキュムレータ１５は、冷凍サイクルから戻ってきた冷媒を、液冷媒とガス冷媒に分離する。第１吸入管１３Ａ及び第２吸入管１３Ｂにはガス冷媒が流れる。アキュムレータ１５とターミナル５０とは、胴シェル１０ａの中心に対して対称の位置に配置している。
シャフト４０の回転によって、第１ピストン３２Ａ及び第２ピストン３２Ｂは、第１圧縮室３４Ａ及び第２圧縮室３４Ｂ内で公転運動を行う。
第１ピストン３２Ａ及び第２ピストン３２Ｂの公転運動によって、第１吸入管１３Ａ及び第２吸入管１３Ｂから第１圧縮室３４Ａ及び第２圧縮室３４Ｂに吸入されたガス冷媒は、第１圧縮室３４Ａ及び第２圧縮室３４Ｂで圧縮された後に密閉容器１０内に吐出され、電動機部２０を通過して上昇する間にオイルを分離し、吐出管１４から密閉容器１０外に吐出される。
また、シャフト４０の回転によって、オイル溜め１１から吸い上げたオイルは、連通路から圧縮機構部３０に供給され、圧縮機構部３０の摺動面の潤滑を行う。 Connected to the
The
Due to the rotation of the shaft 40, the
The gas refrigerant sucked into the
Further, the oil sucked from the
図２は、本実施例によるロータリー式圧縮機の吐出管の位置を示す上面概念図である。
本実施例は、胴シェル１０ａの直径をＤ、アキュムレータ１５を含む重心の鉛直線上となる上シェル１０ｂでの重心位置をＧとした時、吐出管１４を、重心位置Ｇを中心として半径Ｄ／１０の範囲内に配置する。
吐出管１４を、重心位置Ｇを中心とした半径Ｄ／１０の範囲内に配置することで、吐出管１４の振動を低減でき、吐出管１４に接続される配管に伝達する振動を低減し、配管応力の低減を図ることができる。
また、吐出管１４を、重心位置Ｇに配置することで、吐出管１４の振動を最も低減できる。 FIG. 2 is a top conceptual view showing the position of the discharge pipe of the rotary compressor according to this embodiment.
In this embodiment, when the diameter of thetrunk shell 10a is D and the center of gravity position of the upper shell 10b on the vertical line of the center of gravity including the accumulator 15 is G, the discharge pipe 14 has a radius D / It arrange | positions in the range of 10.
By arranging thedischarge pipe 14 within a radius D / 10 centered on the center of gravity G, the vibration of the discharge pipe 14 can be reduced, and the vibration transmitted to the pipe connected to the discharge pipe 14 can be reduced. Pipe stress can be reduced.
Further, by arranging thedischarge pipe 14 at the center of gravity position G, the vibration of the discharge pipe 14 can be reduced most.
本実施例は、胴シェル１０ａの直径をＤ、アキュムレータ１５を含む重心の鉛直線上となる上シェル１０ｂでの重心位置をＧとした時、吐出管１４を、重心位置Ｇを中心として半径Ｄ／１０の範囲内に配置する。
吐出管１４を、重心位置Ｇを中心とした半径Ｄ／１０の範囲内に配置することで、吐出管１４の振動を低減でき、吐出管１４に接続される配管に伝達する振動を低減し、配管応力の低減を図ることができる。
また、吐出管１４を、重心位置Ｇに配置することで、吐出管１４の振動を最も低減できる。 FIG. 2 is a top conceptual view showing the position of the discharge pipe of the rotary compressor according to this embodiment.
In this embodiment, when the diameter of the
By arranging the
Further, by arranging the
本発明は、１シリンダのロータリー式圧縮機でも適用可能である。
The present invention can also be applied to a single cylinder rotary compressor.
１０ 密閉容器
１０ａ 胴シェル
１０ｂ 上シェル
１０ｃ 下シェル
２０ 電動機部
２１ 固定子
２２ 回転子
３０ 圧縮機構部
３１ シリンダ
３２Ａ 第１ピストン
３２Ｂ 第２ピストン
４０ シャフト
４１ 主軸部
４２ 第１偏心部
４３ 第２偏心部
４４ 副軸部
５０ ターミナル DESCRIPTION OFSYMBOLS 10 Airtight container 10a Body shell 10b Upper shell 10c Lower shell 20 Electric motor part 21 Stator 22 Rotor 30 Compression mechanism part 31 Cylinder 32A 1st piston 32B 2nd piston 40 Shaft 41 Main shaft part 42 1st eccentric part 43 2nd eccentric part 44 Countershaft 50 Terminal
１０ａ 胴シェル
１０ｂ 上シェル
１０ｃ 下シェル
２０ 電動機部
２１ 固定子
２２ 回転子
３０ 圧縮機構部
３１ シリンダ
３２Ａ 第１ピストン
３２Ｂ 第２ピストン
４０ シャフト
４１ 主軸部
４２ 第１偏心部
４３ 第２偏心部
４４ 副軸部
５０ ターミナル DESCRIPTION OF
Claims (2)
- 密閉容器内に電動機部と圧縮機構部とを備え、
前記密閉容器は、上下方向に沿って延びる円筒状に形成された胴シェルと、前記胴シェルの上部開口を塞ぐ上シェルと、前記胴シェルの下部開口を塞ぐ下シェルとで構成され、
前記胴シェルには、前記圧縮機構部に吸入冷媒を導入する吸入管と、前記電動機部に給電するターミナルとが接続され、
前記上シェルには、前記圧縮機構部で圧縮された吐出冷媒を導出する吐出管が接続され、
前記吸入管の上流側にはアキュムレータを設けたロータリー式圧縮機であって、
前記胴シェルの直径をＤ、前記アキュムレータを含む重心の鉛直線上となる前記上シェルでの重心位置をＧとした時、
前記吐出管を、前記重心位置Ｇを中心として半径Ｄ／１０の範囲内に配置した
ことを特徴とするロータリー式圧縮機。 An electric motor part and a compression mechanism part are provided in the sealed container,
The sealed container is constituted by a cylindrical shell formed in a cylindrical shape extending in the vertical direction, an upper shell that closes an upper opening of the trunk shell, and a lower shell that closes a lower opening of the trunk shell,
The barrel shell is connected to a suction pipe that introduces suction refrigerant into the compression mechanism portion and a terminal that feeds power to the motor portion.
The upper shell is connected to a discharge pipe that leads out the discharged refrigerant compressed by the compression mechanism section,
A rotary compressor provided with an accumulator on the upstream side of the suction pipe,
When the diameter of the shell is D and the position of the center of gravity in the upper shell that is on the vertical line of the center of gravity including the accumulator is G,
A rotary compressor, wherein the discharge pipe is disposed within a radius D / 10 centered on the gravity center position G. - 前記吐出管を、前記重心位置Ｇに配置した
ことを特徴とする請求項１に記載のロータリー式圧縮機。 The rotary compressor according to claim 1, wherein the discharge pipe is disposed at the gravity center position G.
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| CN201880010583.2A CN110268166B (en) | 2017-03-17 | 2018-02-19 | Rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7227530B1 (en) | 2021-09-30 | 2023-02-22 | ダイキン工業株式会社 | Compressor unit and refrigeration equipment |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113931843B (en) * | 2021-10-13 | 2023-05-09 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
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| JPS5991484U (en) * | 1982-12-13 | 1984-06-21 | 三洋電機株式会社 | Closed rotary compressor |
| JPH04187887A (en) * | 1990-11-21 | 1992-07-06 | Matsushita Electric Ind Co Ltd | Rotary type multistage gas compressor |
| JPH0666258A (en) * | 1992-08-14 | 1994-03-08 | Mitsubishi Heavy Ind Ltd | Refrigerating unit |
| US6372993B1 (en) * | 1995-06-13 | 2002-04-16 | Copeland Corporation | Sealed terminal assembly for hermetic compressor |
| JP2005061348A (en) * | 2003-08-18 | 2005-03-10 | Matsushita Electric Ind Co Ltd | Sealed compressor |
| JP2006177226A (en) * | 2004-12-22 | 2006-07-06 | Hitachi Home & Life Solutions Inc | Rotary compressor and air conditioner using the same |
| JP2008248717A (en) * | 2007-03-29 | 2008-10-16 | Mitsubishi Electric Corp | Refrigerant compression device |
| US20100278675A1 (en) * | 2007-11-08 | 2010-11-04 | Jeong-Min Han | 2 stage rotary compressor |
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| JPS5991484A (en) * | 1982-11-17 | 1984-05-26 | 三菱電機株式会社 | Display unit for industrial computer system |
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- 2017-03-17 JP JP2017052416A patent/JP6671052B2/en active Active
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- 2018-02-19 WO PCT/JP2018/005745 patent/WO2018168345A1/en active Application Filing
- 2018-02-19 CN CN201880010583.2A patent/CN110268166B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5991484U (en) * | 1982-12-13 | 1984-06-21 | 三洋電機株式会社 | Closed rotary compressor |
| JPH04187887A (en) * | 1990-11-21 | 1992-07-06 | Matsushita Electric Ind Co Ltd | Rotary type multistage gas compressor |
| JPH0666258A (en) * | 1992-08-14 | 1994-03-08 | Mitsubishi Heavy Ind Ltd | Refrigerating unit |
| US6372993B1 (en) * | 1995-06-13 | 2002-04-16 | Copeland Corporation | Sealed terminal assembly for hermetic compressor |
| JP2005061348A (en) * | 2003-08-18 | 2005-03-10 | Matsushita Electric Ind Co Ltd | Sealed compressor |
| JP2006177226A (en) * | 2004-12-22 | 2006-07-06 | Hitachi Home & Life Solutions Inc | Rotary compressor and air conditioner using the same |
| JP2008248717A (en) * | 2007-03-29 | 2008-10-16 | Mitsubishi Electric Corp | Refrigerant compression device |
| US20100278675A1 (en) * | 2007-11-08 | 2010-11-04 | Jeong-Min Han | 2 stage rotary compressor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7227530B1 (en) | 2021-09-30 | 2023-02-22 | ダイキン工業株式会社 | Compressor unit and refrigeration equipment |
| WO2023053672A1 (en) * | 2021-09-30 | 2023-04-06 | ダイキン工業株式会社 | Compressor unit and refrigeration device |
| JP2023051659A (en) * | 2021-09-30 | 2023-04-11 | ダイキン工業株式会社 | Compressor unit and freezer |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2018155169A (en) | 2018-10-04 |
| CN110268166B (en) | 2021-08-03 |
| CN110268166A (en) | 2019-09-20 |
| JP6671052B2 (en) | 2020-03-25 |
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