WO2021106198A1 - Compressor and refrigeration cycle device - Google Patents

Compressor and refrigeration cycle device Download PDF

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Publication number
WO2021106198A1
WO2021106198A1 PCT/JP2019/046811 JP2019046811W WO2021106198A1 WO 2021106198 A1 WO2021106198 A1 WO 2021106198A1 JP 2019046811 W JP2019046811 W JP 2019046811W WO 2021106198 A1 WO2021106198 A1 WO 2021106198A1
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WO
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Prior art keywords
crankshaft
shaft portion
eccentric shaft
rotor
rolling piston
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PCT/JP2019/046811
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French (fr)
Japanese (ja)
Inventor
克樹 鈴木
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三菱電機株式会社
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Priority to PCT/JP2019/046811 priority Critical patent/WO2021106198A1/en
Publication of WO2021106198A1 publication Critical patent/WO2021106198A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member

Definitions

  • the present invention relates to a compressor and a refrigeration cycle device.
  • it relates to a rotary compressor.
  • compressors In refrigeration equipment, air conditioners, etc., compressors are used that suck in the gas refrigerant evaporated by the evaporator, compress it to the pressure required for condensation, and send out high-temperature and high-pressure gas refrigerant into the refrigerant circuit. ..
  • a rotary compressor is known as one of such compressors.
  • a rolling piston is provided between a cylinder that forms a compression space in a compression mechanism and an eccentric shaft that has an eccentric shaft whose central axis is deviated from the main axis of rotation in a crankshaft that is a rotation shaft.
  • a rotary compressor equipped with a cylindrical rotating component called.
  • the rotary compressor rotates the rolling piston attached to the eccentric shaft by fitting it into the eccentric shaft due to the eccentric movement of the eccentric shaft due to the rotation of the rotating shaft, thereby sliding between the cylinder and the eccentric shaft.
  • the dynamic resistance can be reduced.
  • the eccentric shaft portion protrudes from the shaft of the crankshaft on the entire circumference. Therefore, when the crankshaft is viewed from above, the circumference of the eccentric shaft portion seems to cover the circumference of the shaft.
  • the compressor usually has refrigerating machine oil to lubricate the equipment inside the compressor and prevent wear.
  • refrigerating machine oil to lubricate the equipment inside the compressor and prevent wear.
  • the difference between the inner diameter of the rolling piston and the diameter of the eccentric shaft portion is required to obtain the lubricating effect of the refrigerating machine oil.
  • Patent Document 1 does not solve the increase in the diameter of the eccentric shaft portion.
  • the diameter of the eccentric shaft portion is increased, the sliding distance is increased and the sliding loss is increased. Further, if the diameter of the eccentric shaft portion is increased, it causes the rotation of the rolling piston to be hindered. Further, since the moment of rotation in which the eccentric shaft portion and the rolling piston are integrally rotated increases, the rotation of the rolling piston decreases, and the effect is hindered. Therefore, even if the diameter of the eccentric shaft portion is reduced, there are restrictions on mounting the rolling piston as described above.
  • An object of the present invention is to obtain a compressor and a refrigeration cycle device capable of attaching a rolling piston to an eccentric shaft portion, regardless of the above-mentioned restrictions, in order to solve the above-mentioned problems.
  • a closed container as an outer shell, an electric motor portion having a stator and a rotor in the closed container, and a rolling piston are fitted in the closed container, respectively.
  • a crank shaft that has a plurality of eccentric shafts and is a rotating shaft that rotates with the rotation of the rotor, and a compression mechanism that is driven by the rotation of the crank shaft in a closed container to compress the fluid to be compressed.
  • the crank shaft supports a plurality of eccentric shaft portions, a long shaft portion that serves as an axis between the rotor and the plurality of eccentric shaft portions, and a plurality of eccentric shaft portions and the lower end side of the crank shaft. It is composed of a combination of parts divided into a short shaft portion that serves as a shaft between the cylinder head and the cylinder head.
  • a crankshaft that combines an eccentric shaft, a short shaft portion, and a long shaft portion is provided. Therefore, a rolling piston having an inner diameter corresponding to the diameter of the eccentric shaft can be fitted and attached without being disturbed by the short shaft portion and the long shaft portion. Therefore, the amount of eccentricity can be increased without expanding the entire circumference of the eccentric shaft portion to increase the diameter, and from the center of the eccentric shaft, which is a component of a force that hinders the rotation of the rolling piston. Radial distance can be reduced. Therefore, the rotation of the rolling piston can be improved, the sliding loss between the cylinder and the eccentric shaft portion can be reduced, and the compression performance can be improved with respect to the size of the container of the rotary compressor.
  • FIG. 2 is a diagram (No. 2) showing an outline of a positional relationship between a long shaft portion and an eccentric shaft portion of the crankshaft according to the first embodiment. It is a figure explaining the rotation drive part about the crankshaft in the compressor which concerns on Embodiment 2.
  • FIG. It is a figure which shows the structural example of the refrigerating cycle apparatus which concerns on Embodiment 3.
  • FIG. 1 is a diagram showing a configuration of a compressor according to the first embodiment.
  • FIG. 1 is a diagram showing an outline of a cross section in order to show the internal configuration of the rotary compressor 101.
  • hatching is attached to a portion mainly described, and hatching of other portions is omitted.
  • the rotary compressor 101 of the first embodiment is, for example, a main device of a refrigerating cycle device used in a refrigerator, a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, and the like. Then, the rotary compressor 101 sucks in a fluid to be compressed such as a refrigerant circulating in the refrigeration cycle device, compresses the fluid, and discharges the fluid in a high temperature and high pressure state. In the following, the fluid will be described as being a gaseous refrigerant.
  • the rotary compressor 101 is a two-cylinder type compressor having two cylinders 33, as will be described later. Therefore, as will be described later, the crankshaft 4 serving as the rotating shaft has a plurality of eccentric shaft portions 42. Further, the rotary compressor 101 of the first embodiment is a rolling piston type closed electric compressor.
  • a discharge pipe 6 penetrates and is fixed to the closed container 1 at the upper part of the closed container 1.
  • the discharge pipe 6 is a refrigerant pipe that discharges the compressed high-pressure gas refrigerant to the outside of the closed container 1.
  • a support leg 7 is installed in the lower part of the closed container 1.
  • the support legs 7 are legs for vertically installing the rotary compressor 101 on a horizontal surface such as a plateau.
  • the suction pipe 5 is a refrigerant pipe that allows a low-pressure gas refrigerant to flow into the closed container 1.
  • the suction muffler 51 is a muffler that reduces or eliminates noise generated by the refrigerant flowing in from the suction pipe 5.
  • the suction muffler 51 also functions as an accumulator, and has a refrigerant storage function for storing excess refrigerant and a gas-liquid separation function for retaining liquid refrigerant temporarily generated when the operating state changes. Since the suction muffler 51 has a gas-liquid separation function, it prevents a large amount of liquid refrigerant from flowing into the closed container 1 and prevents liquid compression from being performed in the rotary compressor 101.
  • the rotary compressor 101 of the first embodiment includes a compression mechanism unit 3 and an electric motor unit 2 having a motor for driving the compression mechanism unit 3 in a closed container 1 serving as an outer shell.
  • the refrigerating machine oil 8 is stored in the bottom of the closed container 1.
  • the refrigerating machine oil 8 is guided from the bottom of the closed container 1 to the inside of the rolling piston 32 via the inside of the crankshaft 4. Then, the refrigerating machine oil 8 becomes a lubricating oil that lubricates the equipment and members in the rotary compressor 101 and prevents wear due to sliding.
  • the motor unit 2 has a stator 21 and a rotor 22 that serve as motors.
  • the stator 21 generates a rotating magnetic field around the rotor 22 according to the applied voltage.
  • the rotor 22 is rotationally driven by the generated rotating magnetic field.
  • a crankshaft 4 serving as a rotation shaft is fitted into the rotor 22 and is shrink-fitted and fixed.
  • the crankshaft 4 rotates with the rotational drive of the rotor 22.
  • the crankshaft 4 has two eccentric shaft portions 42 that are opposite to each other and are eccentric with a phase shift of 180 degrees.
  • the configuration of the crankshaft 4 and the like will be described in detail later.
  • the oil separation plate 23 is fitted to the crankshaft 4 and adjusts the flow path of the refrigerant to promote the separation of the refrigerant and the refrigerating machine oil 8.
  • the compression mechanism unit 3 compresses the low-pressure refrigerant flowing into the low-pressure space of the closed container 1 from the suction pipe 5 by the rotational driving force supplied from the motor unit 2 to obtain a high-pressure refrigerant, and discharges the refrigerant upward.
  • the compression mechanism portion 3 includes a cylinder 33, a rolling piston 32, a cylinder head 34, a frame 35, a partition plate 36, and an eccentric shaft portion 42 of a crankshaft 4 described later.
  • the rolling piston 32 is fitted to the eccentric shaft portion 42 and slidably attached along the outer surface of the eccentric shaft portion 42.
  • the rolling piston 32 rotates with the rotation of the eccentric shaft of the eccentric shaft portion 42.
  • the outer surface of the hollow cylindrical cylinder 33 is fixed to the inner surface of the closed container 1.
  • the hollow portion inside the cylinder 33 is a space that serves as a compression chamber 31, and accommodates the eccentric shaft portion 42 and the rolling piston 32 of the crankshaft 4 described above.
  • the eccentric shaft portion 42 and the rolling piston 32 of the crankshaft 4 have a structure capable of eccentric rotation in the hollow portion in the cylinder 33 by the rotation of the crankshaft 4.
  • the cylinder 33 has a suction port 33a that communicates with the suction pipe 5 and allows a low-pressure refrigerant to flow in from the suction pipe 5.
  • the cylinder head 34 is a bearing that supports the lower end of the crankshaft 4. Then, the cylinder head 34 closes the end surface of the lower cylinder 33 from below and is fixed to the cylinder 33. Further, the frame 35 serves as an upper bearing that supports the side surface of the crankshaft 4. Then, the frame 35 closes the end surface of the upper cylinder 33 from above and is fixed to the cylinder 33.
  • the partition plate 36 is a plate that partitions between the two cylinders 33.
  • FIG. 2 is a diagram showing a configuration related to a compression chamber of the compressor according to the first embodiment.
  • the compression mechanism unit 3 of the first embodiment in the compression mechanism unit 3 of the first embodiment, the space surrounded by the cylinder 33, the rolling piston 32, the cylinder head 34, the frame 35, the partition plate 36, and the vane 37 becomes the compression chamber 31. ..
  • the cylinder head 34, the frame 35, and the partition plate 36 are not shown.
  • the vane 37 is pressed against the surface of the rolling piston 32 by the restoring force of an elastic body such as a spring 38 installed in the vane groove 33b of the cylinder 33. Then, the vane 37 reciprocates along the vane groove 33b following the eccentric movement due to the rotation of the rolling piston 32, and blocks the high-pressure space region and the low-pressure space region in the compression chamber 31.
  • the drive operation of the rotary compressor 101 of the first embodiment will be described.
  • the rotor 22 of the motor unit 2 rotates, so that the crankshaft 4 fitted in the rotor 22 rotates.
  • the two eccentric shaft portions 42 of the crankshaft 4 rotate.
  • each rolling piston 32 rotates while sliding along the inner wall of each cylinder inside each cylinder 33.
  • the low-pressure refrigerant flows in from the suction port 33a of the cylinder 33.
  • the refrigerant is compressed.
  • the compressed high-pressure refrigerant is discharged to the upper part in the closed container 1 and discharged to the outside of the closed container 1 from the discharge pipe 6 provided in the upper part of the closed container 1.
  • the radial component increases, so that the moment of rotation between the rolling piston 32 and the eccentric shaft portion 42 increases, and the rotation of the rolling piston 32 decreases.
  • the decrease in the rotation of the rolling piston 32 has a large effect, for example, under the condition that the supply of the refrigerating machine oil 8 is insufficient and the oil film is difficult to be formed when the compressor is driven at a low speed. Further, when the rotary compressor 101 becomes small, the efficiency is lowered under specific operating conditions.
  • FIG. 3 is a diagram illustrating a rotation drive portion centered on the crankshaft of the compressor according to the first embodiment.
  • the crankshaft 4 serving as a rotating shaft is divided into three parts, an eccentric shaft portion 42, a short shaft portion 41, and a long shaft portion 43. Will be done.
  • the rolling piston 32 is fitted to each eccentric shaft portion 42, the eccentric shaft portion 42, the short shaft portion 41, and the long shaft portion 43 are combined.
  • the short-axis portion 41 and the long-axis portion 43 have a short-axis coupling portion 41a and a long-axis coupling portion 43a, respectively, and can be coupled to the eccentric shaft portion 42.
  • FIG. 4 and 5 are diagrams showing an outline of the positional relationship between the long shaft portion and the eccentric shaft portion of the crankshaft according to the first embodiment.
  • FIG. 4 shows, as an example, the positional relationship between the long shaft portion 43 and the eccentric shaft portion 42 when viewed from the upper surface side of the rotary compressor 101.
  • the rolling piston 32 is fitted to the eccentric shaft portion 42 with respect to the integrated crankshaft 4 including the eccentric shaft portion 42.
  • the rolling piston 32 is passed through the long shaft portion 43 to perform the fitting.
  • the rolling piston 32 is passed through the short shaft portion 41 to perform the fitting.
  • FIGS. 4 and 5 The diameters of the eccentric shaft portions 42 are compared. As shown in FIG. 4, a part of the outer circumference of the eccentric shaft portion 42 protrudes from the long shaft portion 43, which is a rotating shaft, so that the eccentric shaft portion 42 protrudes from the long shaft portion 43 over the entire circumference as shown in FIG.
  • the diameter of the eccentric shaft portion 42 is smaller than that of the eccentric shaft portion 42 having restrictions. This also applies to the positional relationship between the short shaft portion 41 and the lower eccentric shaft portion 42.
  • the rotary compressor 101 includes a crankshaft 4 in which an eccentric shaft portion 42, a short shaft portion 41, and a long shaft portion 43, which are divided as parts, are combined.
  • the rolling pistons 32 are fitted to the two eccentric shaft portions 42, respectively.
  • the two eccentric shaft portions 42 are fitted with the rolling piston 32 having an inner diameter corresponding to the diameter of the eccentric shaft portion 42.
  • the two eccentric shaft portions 42, the short shaft portion 41, and the long shaft portion 43 are joined by fitting to assemble the crankshaft 4.
  • the short shaft portion 41 and the long shaft portion 43 are described as one component each, but may be further divided into a plurality of components.
  • the crankshaft 4 is provided by combining the eccentric shaft portion 42, the short shaft portion 41, and the long shaft portion 43. Therefore, the rolling piston 32 having an inner diameter corresponding to the diameter of the eccentric shaft portion 42 can be fitted and attached to the short shaft portion 41 and the long shaft portion 43 without being disturbed. Therefore, the amount of eccentricity r can be increased without increasing the diameter by projecting the entire circumference of the eccentric shaft portion 42, and the sliding loss is not hindered by the rotation of the rolling piston 32. It can be reduced and the compression performance can be improved with respect to the size of the closed container 1 of the rotary compressor 101.
  • FIG. 6 is a diagram illustrating a rotationally driven portion centered on a crankshaft in the compressor according to the second embodiment.
  • the crankshaft 4 of the rotary compressor 101 is divided into three parts, a short shaft portion 41, an eccentric shaft portion 42, and a long shaft portion 43, and is configured by combining them.
  • the rotor 22 has a cavity in the central portion. Then, in the rotary compressor 101 of the first embodiment, the long shaft portion 43 of the crankshaft 4 is inserted into the cavity of the rotor 22, and the crankshaft 4 and the rotor 22 are shrink-fitted and fixed.
  • the rotary compressor 101 of the second embodiment has a rotor coupling portion 24 in which the rotor 22 is coupled to the crankshaft 4 at the rotation center portion at the lower end portion. Then, the rotor 22 and the crankshaft 4 are fixed by fitting and coupling the rotor coupling portion 24 of the rotor 22 and the long shaft portion 43 of the crankshaft 4.
  • the long shaft portion 43 of the second embodiment is shorter than the long shaft portion 43 of the first embodiment.
  • the rotor 22 has a rotor coupling portion 24, and the rotor coupling portion 24 and the long shaft portion 43 of the crankshaft 4 are coupled to each other.
  • the rotor 22 and the crankshaft 4 are integrated so that they can rotate. Therefore, in the rotor 22, the cavity into which the crankshaft 4 is inserted can be eliminated. Then, the space for installing the permanent magnet (not shown) built in the rotor 22 can be expanded to the center side of the rotor 22. Therefore, the rotor 22 can be reduced in the radial direction, and the entire closed container 1 can be reduced in the radial direction.
  • FIG. 7 is a diagram showing a configuration example of the refrigeration cycle device according to the third embodiment.
  • FIG. 7 shows an air conditioner as a refrigeration cycle device.
  • the air conditioner of FIG. 7 connects the outdoor unit 100 and the indoor unit 200 with a refrigerant pipe 300 and a refrigerant pipe 400 to form a refrigerant circuit for circulating a refrigerant.
  • the outdoor unit 100 includes the rotary compressor 101 described in the first and second embodiments. Further, the outdoor unit 100 includes a four-way valve 102, an outdoor heat exchanger 103, an expansion valve 104, and an outdoor blower 105. Further, the indoor unit 200 has an indoor heat exchanger 201.
  • the rotary compressor 101 compresses and discharges the sucked refrigerant.
  • the rotary compressor 101 may be capable of arbitrarily changing the operating frequency by, for example, an inverter circuit or the like.
  • the four-way valve 102 is a valve that switches the flow of the refrigerant between the cooling operation and the heating operation.
  • the outdoor heat exchanger 103 exchanges heat between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation to evaporate and vaporize the refrigerant. In addition, it functions as a condenser during cooling operation to condense and liquefy the refrigerant. Further, the outdoor blower 105 sends outdoor air to the outdoor heat exchanger 103 to promote heat exchange between the outdoor air and the refrigerant.
  • the expansion valve 104 such as a throttle device serving as a pressure reducing device decompresses and expands the refrigerant.
  • the opening degree is adjusted based on an instruction from a control device (not shown) or the like.
  • the indoor heat exchanger 201 exchanges heat between, for example, air to be air-conditioned and a refrigerant. During heating operation, it functions as a condenser and condenses and liquefies the refrigerant. In addition, it functions as an evaporator during cooling operation to evaporate and vaporize the refrigerant.
  • the indoor blower 202 sends air to be air-conditioned to the indoor heat exchanger 201 to promote heat exchange between the air and the refrigerant.
  • the outdoor unit 100 and the like can be miniaturized by having the rotary compressor 101 described in the first embodiment and the second embodiment as an apparatus. Can be done.
  • the rotary compressor 101 has been described as compressing the refrigerant, but the present invention is not limited to this. It can be a compressor that compresses other fluids such as air.
  • the rotary compressor 101 has been described as an example, but the present invention is not limited to this, and the present invention can be applied to other closed electric compressors such as a scroll compressor.
  • the refrigerating cycle device using the air conditioner as an example has been described, but it can also be used for, for example, a refrigerating device or a hot water supply device.

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

Abstract

This compressor is provided with: a sealed container which serves as an outer shell; a motor having a stator and a rotor in the sealed container; a crankshaft which has, in the sealed container, a plurality of eccentric shafts having rolling pistons fitted thereto and which serves as a rotary shaft rotating along with rotation of the rotor; and a compression mechanism driven by rotation of the crankshaft so as to compress a fluid to be compressed in the sealed container. The crankshaft is configured by combining divisional components of a long shaft serving as a shaft between the rotor and the eccentric shafts, a short shaft serving as a shaft between the eccentric shafts and a cylinder head supporting the lower end side of the crankshaft, and the eccentric shafts.

Description

圧縮機および冷凍サイクル装置Compressor and refrigeration cycle equipment
　この発明は、圧縮機および冷凍サイクル装置に係るものである。特に、ロータリ圧縮機に関するものである。 The present invention relates to a compressor and a refrigeration cycle device. In particular, it relates to a rotary compressor.
　冷凍装置、空気調和装置などにおいては、蒸発器で蒸発したガス冷媒を吸入し、凝縮するために必要な圧力まで圧縮して冷媒回路中に高温高圧のガス冷媒を送り出す圧縮機が使用されている。このような圧縮機の１つとして、ロータリ圧縮機が知られている。 In refrigeration equipment, air conditioners, etc., compressors are used that suck in the gas refrigerant evaporated by the evaporator, compress it to the pressure required for condensation, and send out high-temperature and high-pressure gas refrigerant into the refrigerant circuit. .. A rotary compressor is known as one of such compressors.
　従来、圧縮機構部において圧縮空間を形成するシリンダと、回転軸となるクランクシャフトにおいて回転の主となる軸とは中心軸がずれた偏芯軸を有する偏芯軸部との間に、ローリングピストンと呼ばれる円筒状の自転部品を備えるロータリ圧縮機がある。ロータリ圧縮機は、回転軸の回転による偏芯軸部の偏芯運動により、偏芯軸部に嵌め合わせにより取り付けられたローリングピストンを自転させることで、シリンダと偏芯軸部との間の摺動抵抗を低減することができる。ここで、ローリングピストンの偏芯軸部への取り付けに係る制約上、偏芯軸部は、全周において、クランクシャフトの軸よりも突出している。このため、クランクシャフトを上部からみたときには、偏芯軸部の円周が軸の円周を覆うように見えることになる。 Conventionally, a rolling piston is provided between a cylinder that forms a compression space in a compression mechanism and an eccentric shaft that has an eccentric shaft whose central axis is deviated from the main axis of rotation in a crankshaft that is a rotation shaft. There is a rotary compressor equipped with a cylindrical rotating component called. The rotary compressor rotates the rolling piston attached to the eccentric shaft by fitting it into the eccentric shaft due to the eccentric movement of the eccentric shaft due to the rotation of the rotating shaft, thereby sliding between the cylinder and the eccentric shaft. The dynamic resistance can be reduced. Here, due to restrictions relating to the attachment of the rolling piston to the eccentric shaft portion, the eccentric shaft portion protrudes from the shaft of the crankshaft on the entire circumference. Therefore, when the crankshaft is viewed from above, the circumference of the eccentric shaft portion seems to cover the circumference of the shaft.
　また、通常、圧縮機は、圧縮機内の機器間を潤滑して、摩耗を防ぐため、冷凍機油を有する。複数のシリンダを有し、クランクシャフトが複数の偏芯軸部を有するロータリ圧縮機の場合、冷凍機油の潤滑効果を得るためには、ローリングピストンの内径と偏芯軸部の直径との差は、μｍ単位のオーダの隙間でならなければならない。 Also, the compressor usually has refrigerating machine oil to lubricate the equipment inside the compressor and prevent wear. In the case of a rotary compressor having a plurality of cylinders and a crankshaft having a plurality of eccentric shaft portions, the difference between the inner diameter of the rolling piston and the diameter of the eccentric shaft portion is required to obtain the lubricating effect of the refrigerating machine oil. , Must be on the order of μm.
　ロータリ圧縮機の容器の大きさに対して圧縮性能を上げるには、偏芯軸部を回転軸の中心からずらして偏芯量を大きくする。このため、偏芯軸部の全周を突出させて偏芯量を大きくすると、偏芯軸部の径が拡大する。ここで、２つの偏芯軸部を複数の部品に分離して構成し、偏芯軸部間に挟む仕切り板などの部材を挿入してから２つの偏芯軸部を連結する圧縮機が提案されている（たとえば、特許文献１参照）。このため、偏芯軸部の径の拡大に関係なく、部材が有する挿入に係る貫通穴は小さくなる。 To improve the compression performance with respect to the size of the container of the rotary compressor, shift the eccentric shaft from the center of the rotating shaft to increase the amount of eccentricity. Therefore, if the entire circumference of the eccentric shaft portion is projected to increase the amount of eccentricity, the diameter of the eccentric shaft portion is increased. Here, a compressor is proposed in which two eccentric shafts are separated into a plurality of parts, a member such as a partition plate sandwiched between the eccentric shafts is inserted, and then the two eccentric shafts are connected. (See, for example, Patent Document 1). Therefore, regardless of the increase in the diameter of the eccentric shaft portion, the through hole for insertion of the member becomes smaller.
特開２００５－３３７２１０号公報Japanese Unexamined Patent Publication No. 2005-337210
　しかしながら、上述した特許文献１の技術は、偏芯軸部の径が拡大することを解決するものではない。偏芯軸部の径が拡大すると、摺動距離が増大し、摺動損失が大きくなる。また、偏芯軸部の径が拡大すると、ローリングピストンの自転を阻害させる原因になる。さらに、偏芯軸部とローリングピストンとが一体となって回転するモーメントが増大するので、ローリングピストンの自転性が低下し、効果が阻害される。このため、偏芯軸部の径を小さくしようとしても、前述したように、ローリングピストンを取り付ける際の制約がある。 However, the technique of Patent Document 1 described above does not solve the increase in the diameter of the eccentric shaft portion. When the diameter of the eccentric shaft portion is increased, the sliding distance is increased and the sliding loss is increased. Further, if the diameter of the eccentric shaft portion is increased, it causes the rotation of the rolling piston to be hindered. Further, since the moment of rotation in which the eccentric shaft portion and the rolling piston are integrally rotated increases, the rotation of the rolling piston decreases, and the effect is hindered. Therefore, even if the diameter of the eccentric shaft portion is reduced, there are restrictions on mounting the rolling piston as described above.
　この発明は、上記のような課題を解決するため、上述した制約に関係なく、偏芯軸部にローリングピストンを取り付けることができる圧縮機および冷凍サイクル装置を得ることを目的とする。 An object of the present invention is to obtain a compressor and a refrigeration cycle device capable of attaching a rolling piston to an eccentric shaft portion, regardless of the above-mentioned restrictions, in order to solve the above-mentioned problems.
　上述した課題を解決するため、この発明の圧縮機は、外殻となる密閉容器と、密閉容器内において、固定子および回転子を有する電動機部と、密閉容器内において、ローリングピストンがそれぞれ嵌め合わされた複数の偏芯軸部を有し、回転子の回転とともに回転する回転軸となるクランクシャフトと、密閉容器内において、クランクシャフトの回転により駆動して、圧縮対象の流体を圧縮する圧縮機構部とを備え、クランクシャフトは、複数の偏芯軸部、回転子と複数の偏芯軸部との間の軸となる長軸部および複数の偏芯軸部とクランクシャフトの下端側を支持するシリンダヘッドとの間の軸となる短軸部に分かれた部品の組み合わせで構成されるものである。 In order to solve the above-mentioned problems, in the compressor of the present invention, a closed container as an outer shell, an electric motor portion having a stator and a rotor in the closed container, and a rolling piston are fitted in the closed container, respectively. A crank shaft that has a plurality of eccentric shafts and is a rotating shaft that rotates with the rotation of the rotor, and a compression mechanism that is driven by the rotation of the crank shaft in a closed container to compress the fluid to be compressed. The crank shaft supports a plurality of eccentric shaft portions, a long shaft portion that serves as an axis between the rotor and the plurality of eccentric shaft portions, and a plurality of eccentric shaft portions and the lower end side of the crank shaft. It is composed of a combination of parts divided into a short shaft portion that serves as a shaft between the cylinder head and the cylinder head.
　この発明の圧縮機によれば、偏芯軸、短軸部および長軸部を組み合わせたクランクシャフトを備えるようにした。このため、偏芯軸の径に対応した内径のローリングピストンを、短軸部および長軸部に邪魔されることなく、嵌め合わせて取り付けることができる。このため、偏芯軸部の全周を突出させて直径を拡大しなくても偏芯量を大きくすることができ、ローリングピストンの自転性を阻害する力の成分である偏芯軸の中心からの半径距離を縮小することができる。このため、ローリングピストンの自転性を向上させることができ、シリンダと偏芯軸部における摺動損失を低減し、ロータリ圧縮機の容器の大きさに対して圧縮性能を向上させることができる。 According to the compressor of the present invention, a crankshaft that combines an eccentric shaft, a short shaft portion, and a long shaft portion is provided. Therefore, a rolling piston having an inner diameter corresponding to the diameter of the eccentric shaft can be fitted and attached without being disturbed by the short shaft portion and the long shaft portion. Therefore, the amount of eccentricity can be increased without expanding the entire circumference of the eccentric shaft portion to increase the diameter, and from the center of the eccentric shaft, which is a component of a force that hinders the rotation of the rolling piston. Radial distance can be reduced. Therefore, the rotation of the rolling piston can be improved, the sliding loss between the cylinder and the eccentric shaft portion can be reduced, and the compression performance can be improved with respect to the size of the container of the rotary compressor.
実施の形態１に係る圧縮機の構成を示す図である。It is a figure which shows the structure of the compressor which concerns on Embodiment 1. FIG. 実施の形態１に係る圧縮機の圧縮室に係る構成を示す図である。It is a figure which shows the structure which concerns on the compression chamber of the compressor which concerns on Embodiment 1. FIG. 実施の形態１に係る圧縮機のクランクシャフトを中心とする回転駆動部分について説明する図である。It is a figure explaining the rotation drive part about the crankshaft of the compressor which concerns on Embodiment 1. FIG. 実施の形態１に係るクランクシャフトの長軸部と偏芯軸部との位置関係の概略を示す図（その１）である。It is a figure (the 1) which shows the outline of the positional relationship between the long shaft part and the eccentric shaft part of the crankshaft which concerns on Embodiment 1. FIG. 実施の形態１に係るクランクシャフトの長軸部と偏芯軸部との位置関係の概略を示す図（その２）である。FIG. 2 is a diagram (No. 2) showing an outline of a positional relationship between a long shaft portion and an eccentric shaft portion of the crankshaft according to the first embodiment. 実施の形態２に係る圧縮機におけるクランクシャフトを中心とする回転駆動部分について説明する図である。It is a figure explaining the rotation drive part about the crankshaft in the compressor which concerns on Embodiment 2. FIG. 実施の形態３に係る冷凍サイクル装置の構成例を表す図である。It is a figure which shows the structural example of the refrigerating cycle apparatus which concerns on Embodiment 3.
　以下、発明の実施の形態に係る圧縮機および冷凍サイクル装置について図面などを参照しながら説明する。以下の図面において、同一の符号を付したものは、同一またはこれに相当するものであり、以下に記載する実施の形態の全文において共通することとする。そして、明細書全文に表わされている構成要素の形態は、あくまでも例示であって、明細書に記載された形態に限定するものではない。特に構成要素の組み合わせは、各実施の形態における組み合わせのみに限定するものではなく、他の実施の形態に記載した構成要素を別の実施の形態に適用することができる。また、以下の説明において、図における上方を「上側」とし、下方を「下側」として説明する。さらに、理解を容易にするために、方向を表す用語（たとえば「右」、「左」、「前」、「後」など）などを適宜用いるが、説明のためのものであって、これらの用語は本願に係る発明を限定するものではない。そして、図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。 Hereinafter, the compressor and the refrigeration cycle apparatus according to the embodiment of the invention will be described with reference to drawings and the like. In the following drawings, those having the same reference numerals are the same or equivalent thereto, and are common to the whole texts of the embodiments described below. The form of the component represented in the entire specification is merely an example, and is not limited to the form described in the specification. In particular, the combination of components is not limited to the combination in each embodiment, and the components described in other embodiments can be applied to another embodiment. Further, in the following description, the upper side in the figure will be referred to as "upper side" and the lower side will be referred to as "lower side". Further, for ease of understanding, directional terms (eg, "right", "left", "front", "rear", etc.) are used as appropriate, but they are for illustration purposes only. The term does not limit the invention according to the present application. Then, in the drawings, the relationship between the sizes of the constituent members may differ from the actual one.
実施の形態１．
　図１は、実施の形態１に係る圧縮機の構成を示す図である。図１は、ロータリ圧縮機１０１の内部構成を示すため、断面の概略を示す図である。ここで、図１に示す実施の形態１のロータリ圧縮機１０１には、主に説明する部分に対してハッチングを付し、他の部分のハッチングを省略している。 Embodiment 1.
FIG. 1 is a diagram showing a configuration of a compressor according to the first embodiment. FIG. 1 is a diagram showing an outline of a cross section in order to show the internal configuration of the rotary compressor 101. Here, in the rotary compressor 101 of the first embodiment shown in FIG. 1, hatching is attached to a portion mainly described, and hatching of other portions is omitted.
　実施の形態１のロータリ圧縮機１０１は、たとえば、冷蔵庫、冷凍庫、自動販売機、空気調和装置、冷凍装置、給湯機などに用いられる冷凍サイクル装置の主要機器となる。そして、ロータリ圧縮機１０１は、冷凍サイクル装置を循環する冷媒などの圧縮対象となる流体を吸入し、その流体を圧縮して高温高圧の状態として吐出する。以下においては、流体が、気体の冷媒であるものとして説明する。ロータリ圧縮機１０１は、後述するように、２つのシリンダ３３を有する２シリンダ型の圧縮機である。このため、後述するように、回転軸となるクランクシャフト４は、偏芯軸部４２を複数有する。また、実施の形態１のロータリ圧縮機１０１は、ローリングピストン式の密閉型電動圧縮機である。 The rotary compressor 101 of the first embodiment is, for example, a main device of a refrigerating cycle device used in a refrigerator, a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, and the like. Then, the rotary compressor 101 sucks in a fluid to be compressed such as a refrigerant circulating in the refrigeration cycle device, compresses the fluid, and discharges the fluid in a high temperature and high pressure state. In the following, the fluid will be described as being a gaseous refrigerant. The rotary compressor 101 is a two-cylinder type compressor having two cylinders 33, as will be described later. Therefore, as will be described later, the crankshaft 4 serving as the rotating shaft has a plurality of eccentric shaft portions 42. Further, the rotary compressor 101 of the first embodiment is a rolling piston type closed electric compressor.
　密閉容器１の上部には、吐出管６が、密閉容器１に貫通して固定されている。吐出管６は、圧縮された高圧のガス冷媒を密閉容器１の外部に吐出させる冷媒配管である。また、密閉容器１の下部には、支持脚７が設置されている。支持脚７は、台地などの水平面上に、ロータリ圧縮機１０１を、縦置きにより設置する脚となる。 A discharge pipe 6 penetrates and is fixed to the closed container 1 at the upper part of the closed container 1. The discharge pipe 6 is a refrigerant pipe that discharges the compressed high-pressure gas refrigerant to the outside of the closed container 1. Further, a support leg 7 is installed in the lower part of the closed container 1. The support legs 7 are legs for vertically installing the rotary compressor 101 on a horizontal surface such as a plateau.
　吸入管５は、低圧のガス冷媒を密閉容器１の内部に流入させる冷媒配管である。また、吸入マフラ５１は、吸入管５から流入する冷媒により発生する騒音を低減または除去する消音器である。また、吸入マフラ５１は、アキュムレータとしても機能し、余剰冷媒を貯留する冷媒貯留機能と、運転状態が変化する際に一時的に発生する液冷媒を滞留させることによる気液分離機能とを有する。吸入マフラ５１が気液分離機能を有することにより、密閉容器１の内部に大量の液冷媒が流入されることを防ぎ、ロータリ圧縮機１０１において液圧縮が行われないようにする。 The suction pipe 5 is a refrigerant pipe that allows a low-pressure gas refrigerant to flow into the closed container 1. Further, the suction muffler 51 is a muffler that reduces or eliminates noise generated by the refrigerant flowing in from the suction pipe 5. Further, the suction muffler 51 also functions as an accumulator, and has a refrigerant storage function for storing excess refrigerant and a gas-liquid separation function for retaining liquid refrigerant temporarily generated when the operating state changes. Since the suction muffler 51 has a gas-liquid separation function, it prevents a large amount of liquid refrigerant from flowing into the closed container 1 and prevents liquid compression from being performed in the rotary compressor 101.
　また、図１に示すように、実施の形態１のロータリ圧縮機１０１は、外殻となる密閉容器１内に、圧縮機構部３と、圧縮機構部３を駆動するモータを有する電動機部２とを収容する。そして、密閉容器１内の底部には冷凍機油８が貯留されている。冷凍機油８は、密閉容器１内の底部からクランクシャフト４の内部を経由してローリングピストン３２の内部に導かれる。そして、冷凍機油８は、ロータリ圧縮機１０１内の機器および部材間を潤滑させ、摺動による摩耗を防ぐ潤滑油となる。 Further, as shown in FIG. 1, the rotary compressor 101 of the first embodiment includes a compression mechanism unit 3 and an electric motor unit 2 having a motor for driving the compression mechanism unit 3 in a closed container 1 serving as an outer shell. To accommodate. The refrigerating machine oil 8 is stored in the bottom of the closed container 1. The refrigerating machine oil 8 is guided from the bottom of the closed container 1 to the inside of the rolling piston 32 via the inside of the crankshaft 4. Then, the refrigerating machine oil 8 becomes a lubricating oil that lubricates the equipment and members in the rotary compressor 101 and prevents wear due to sliding.
　電動機部２は、モータとなる固定子２１と回転子２２とを有する。固定子２１は、印加される電圧にしたがって、回転子２２の周囲に回転磁界を発生させる。回転子２２は、発生した回転磁界により、回転駆動する。また、回転子２２には、回転軸となるクランクシャフト４が嵌入され、焼き嵌め固定される。クランクシャフト４は、回転子２２の回転駆動とともに回転する。クランクシャフト４は、後述するように、互いに反対向きになり、１８０度位相をずらして偏心した２つの偏芯軸部４２を上下に有する。クランクシャフト４の構成などについては、後に詳細に説明する。油分離板２３は、クランクシャフト４に嵌合し、冷媒の流路を調整して、冷媒と冷凍機油８との分離を促進する。 The motor unit 2 has a stator 21 and a rotor 22 that serve as motors. The stator 21 generates a rotating magnetic field around the rotor 22 according to the applied voltage. The rotor 22 is rotationally driven by the generated rotating magnetic field. Further, a crankshaft 4 serving as a rotation shaft is fitted into the rotor 22 and is shrink-fitted and fixed. The crankshaft 4 rotates with the rotational drive of the rotor 22. As will be described later, the crankshaft 4 has two eccentric shaft portions 42 that are opposite to each other and are eccentric with a phase shift of 180 degrees. The configuration of the crankshaft 4 and the like will be described in detail later. The oil separation plate 23 is fitted to the crankshaft 4 and adjusts the flow path of the refrigerant to promote the separation of the refrigerant and the refrigerating machine oil 8.
　また、圧縮機構部３は、電動機部２から供給された回転駆動力により、吸入管５から密閉容器１の低圧空間に流入した低圧冷媒を圧縮して高圧冷媒とし、上方に吐出する。圧縮機構部３は、シリンダ３３、ローリングピストン３２、シリンダヘッド３４、フレーム３５、仕切り板３６および後述するクランクシャフト４の偏芯軸部４２を有する。 Further, the compression mechanism unit 3 compresses the low-pressure refrigerant flowing into the low-pressure space of the closed container 1 from the suction pipe 5 by the rotational driving force supplied from the motor unit 2 to obtain a high-pressure refrigerant, and discharges the refrigerant upward. The compression mechanism portion 3 includes a cylinder 33, a rolling piston 32, a cylinder head 34, a frame 35, a partition plate 36, and an eccentric shaft portion 42 of a crankshaft 4 described later.
　ローリングピストン３２は、偏芯軸部４２の外側面に沿って、偏芯軸部４２に嵌合されて摺動自在に取り付けられている。ローリングピストン３２は、偏芯軸部４２の偏芯軸の回転とともに回転する。中空円筒形状のシリンダ３３の外側面は、密閉容器１内側面に固定されている。シリンダ３３内部の中空部分は、圧縮室３１となる空間となっており、前述したクランクシャフト４の偏芯軸部４２およびローリングピストン３２が収容されている。そして、クランクシャフト４の偏芯軸部４２およびローリングピストン３２が、クランクシャフト４の回転により、シリンダ３３内の中空部分において、偏芯回転できる構造となっている。シリンダ３３は、吸入管５と連通し、吸入管５から低圧冷媒が流入する吸入口３３ａを有する。 The rolling piston 32 is fitted to the eccentric shaft portion 42 and slidably attached along the outer surface of the eccentric shaft portion 42. The rolling piston 32 rotates with the rotation of the eccentric shaft of the eccentric shaft portion 42. The outer surface of the hollow cylindrical cylinder 33 is fixed to the inner surface of the closed container 1. The hollow portion inside the cylinder 33 is a space that serves as a compression chamber 31, and accommodates the eccentric shaft portion 42 and the rolling piston 32 of the crankshaft 4 described above. The eccentric shaft portion 42 and the rolling piston 32 of the crankshaft 4 have a structure capable of eccentric rotation in the hollow portion in the cylinder 33 by the rotation of the crankshaft 4. The cylinder 33 has a suction port 33a that communicates with the suction pipe 5 and allows a low-pressure refrigerant to flow in from the suction pipe 5.
　シリンダヘッド３４は、クランクシャフト４の下端部を支持する軸受となる。そして、シリンダヘッド３４は、下側のシリンダ３３の端面を下方から閉塞して、シリンダ３３に固定される。また、フレーム３５は、クランクシャフト４の側面を支える上方側の軸受けとなる。そして、フレーム３５は、上側のシリンダ３３の端面を上方から閉塞して、シリンダ３３に固定される。仕切り板３６は、２つのシリンダ３３の間を仕切る板である。 The cylinder head 34 is a bearing that supports the lower end of the crankshaft 4. Then, the cylinder head 34 closes the end surface of the lower cylinder 33 from below and is fixed to the cylinder 33. Further, the frame 35 serves as an upper bearing that supports the side surface of the crankshaft 4. Then, the frame 35 closes the end surface of the upper cylinder 33 from above and is fixed to the cylinder 33. The partition plate 36 is a plate that partitions between the two cylinders 33.
　図２は、実施の形態１に係る圧縮機の圧縮室に係る構成を示す図である。図２に示すように、実施の形態１の圧縮機構部３において、シリンダ３３、ローリングピストン３２、シリンダヘッド３４、フレーム３５、仕切り板３６およびベーン３７により囲まれた空間は、圧縮室３１となる。ここで、図２では、シリンダヘッド３４、フレーム３５および仕切り板３６は図示していない。ベーン３７は、シリンダ３３が有するベーン溝３３ｂに設置されたバネ３８などの弾性体の復元力によって、ローリングピストン３２の表面に押しつけられる。そして、ベーン３７は、ローリングピストン３２の回転による偏芯運動に追従して、ベーン溝３３ｂに沿って往復運動し、圧縮室３１内の高圧空間領域と低圧空間領域とを遮断する。 FIG. 2 is a diagram showing a configuration related to a compression chamber of the compressor according to the first embodiment. As shown in FIG. 2, in the compression mechanism unit 3 of the first embodiment, the space surrounded by the cylinder 33, the rolling piston 32, the cylinder head 34, the frame 35, the partition plate 36, and the vane 37 becomes the compression chamber 31. .. Here, in FIG. 2, the cylinder head 34, the frame 35, and the partition plate 36 are not shown. The vane 37 is pressed against the surface of the rolling piston 32 by the restoring force of an elastic body such as a spring 38 installed in the vane groove 33b of the cylinder 33. Then, the vane 37 reciprocates along the vane groove 33b following the eccentric movement due to the rotation of the rolling piston 32, and blocks the high-pressure space region and the low-pressure space region in the compression chamber 31.
　次に、実施の形態１のロータリ圧縮機１０１の駆動動作について説明する。実施の形態１のロータリ圧縮機１０１は、電動機部２の回転子２２が回転することで、回転子２２に嵌入されたクランクシャフト４が回転する。このとき、クランクシャフト４が有する２つの偏芯軸部４２が回転する。２つの偏芯軸部４２が回転することで、各シリンダ３３の内部で、それぞれのローリングピストン３２が、各シリンダの内壁に沿って摺動しながら回転する。 Next, the drive operation of the rotary compressor 101 of the first embodiment will be described. In the rotary compressor 101 of the first embodiment, the rotor 22 of the motor unit 2 rotates, so that the crankshaft 4 fitted in the rotor 22 rotates. At this time, the two eccentric shaft portions 42 of the crankshaft 4 rotate. As the two eccentric shaft portions 42 rotate, each rolling piston 32 rotates while sliding along the inner wall of each cylinder inside each cylinder 33.
　ローリングピストン３２の回転によって、圧縮室３１内の容積が広がる過程においては、シリンダ３３の吸入口３３ａから低圧冷媒が流入する。ローリングピストン３２がさらに回転を続け、圧縮室３１内の容積が狭まっていくと、冷媒が圧縮されていく。圧縮された高圧冷媒は、密閉容器１内の上部へ吐出され、密閉容器１の上部に設けられた吐出管６から密閉容器１の外部に吐出される。 In the process of expanding the volume in the compression chamber 31 due to the rotation of the rolling piston 32, the low-pressure refrigerant flows in from the suction port 33a of the cylinder 33. As the rolling piston 32 continues to rotate and the volume in the compression chamber 31 narrows, the refrigerant is compressed. The compressed high-pressure refrigerant is discharged to the upper part in the closed container 1 and discharged to the outside of the closed container 1 from the discharge pipe 6 provided in the upper part of the closed container 1.
　ここで、ローリングピストン３２の自転運動について説明する。ローリングピストン３２の自転運動において、運動に係る主となる力のうち、シリンダ３３とローリングピストン３２の接触による力が、偏芯軸部４２とローリングピストン３２との接触による力を上回るとき、クランクシャフト４から、直接、冷凍機油８が供給される。そして、ローリングピストン３２の自転運動により、冷凍機油８が潤沢で摩擦係数の低い偏芯軸部４２とローリングピストン３２との間で摺動が行われる。偏芯軸部４２とローリングピストン３２との摺動により、シリンダ３３とローリングピストン３２の摩擦係数の高い面での摺動の肩代わりをすることで損失を低減することができる。このため、偏芯軸部４２の径が大きくなると、半径成分が増大することで、ローリングピストン３２と偏芯軸部４２の間での回転のモーメントが増大し、ローリングピストン３２の自転性が低下する。ローリングピストン３２の自転性の低下は、たとえば、圧縮機を低速駆動させたときに、冷凍機油８の供給が不十分かつ油膜が形成されづらい条件において影響が大きい。また、ロータリ圧縮機１０１が小さくなると、特定の運転条件における効率低下を招く。 Here, the rotation motion of the rolling piston 32 will be described. In the rotating motion of the rolling piston 32, when the force due to the contact between the cylinder 33 and the rolling piston 32 exceeds the force due to the contact between the eccentric shaft portion 42 and the rolling piston 32 among the main forces related to the motion, the crankshaft Refrigerating machine oil 8 is directly supplied from 4. Then, the rotating motion of the rolling piston 32 causes the refrigerating machine oil 8 to slide between the eccentric shaft portion 42 having abundant and low friction coefficient and the rolling piston 32. By sliding the eccentric shaft portion 42 and the rolling piston 32, the loss can be reduced by taking over the sliding of the cylinder 33 and the rolling piston 32 on the surface having a high coefficient of friction. Therefore, as the diameter of the eccentric shaft portion 42 increases, the radial component increases, so that the moment of rotation between the rolling piston 32 and the eccentric shaft portion 42 increases, and the rotation of the rolling piston 32 decreases. To do. The decrease in the rotation of the rolling piston 32 has a large effect, for example, under the condition that the supply of the refrigerating machine oil 8 is insufficient and the oil film is difficult to be formed when the compressor is driven at a low speed. Further, when the rotary compressor 101 becomes small, the efficiency is lowered under specific operating conditions.
　図３は、実施の形態１に係る圧縮機のクランクシャフトを中心とする回転駆動部分について説明する図である。図３に示すように、実施の形態１のロータリ圧縮機１０１は、回転軸となるクランクシャフト４が、２つの偏芯軸部４２、短軸部４１および長軸部４３の３つの部品に分割される。そして、ローリングピストン３２を各偏芯軸部４２に嵌め合わせた後、偏芯軸部４２、短軸部４１および長軸部４３を組み合わせる。ここで、短軸部４１および長軸部４３は、それぞれ、短軸結合部４１ａおよび長軸結合部４３ａを有し、偏芯軸部４２と結合することができる。 FIG. 3 is a diagram illustrating a rotation drive portion centered on the crankshaft of the compressor according to the first embodiment. As shown in FIG. 3, in the rotary compressor 101 of the first embodiment, the crankshaft 4 serving as a rotating shaft is divided into three parts, an eccentric shaft portion 42, a short shaft portion 41, and a long shaft portion 43. Will be done. Then, after fitting the rolling piston 32 to each eccentric shaft portion 42, the eccentric shaft portion 42, the short shaft portion 41, and the long shaft portion 43 are combined. Here, the short-axis portion 41 and the long-axis portion 43 have a short-axis coupling portion 41a and a long-axis coupling portion 43a, respectively, and can be coupled to the eccentric shaft portion 42.
　図４および図５は、実施の形態１に係るクランクシャフトの長軸部と偏芯軸部との位置関係の概略を示す図である。図４は、ロータリ圧縮機１０１の上面側からみたときの長軸部４３と偏芯軸部４２との位置関係を、例として示している。 4 and 5 are diagrams showing an outline of the positional relationship between the long shaft portion and the eccentric shaft portion of the crankshaft according to the first embodiment. FIG. 4 shows, as an example, the positional relationship between the long shaft portion 43 and the eccentric shaft portion 42 when viewed from the upper surface side of the rotary compressor 101.
　たとえば、偏芯軸部４２を含め、一体化したクランクシャフト４に対し、ローリングピストン３２を偏芯軸部４２に嵌め合わせる場合について説明する。上側の偏芯軸部４２にローリングピストン３２を嵌め合わせるには、長軸部４３にローリングピストン３２を通過させて、嵌め合わせが行われる。また、下側の偏芯軸部４２にローリングピストン３２を嵌め合わせるには、短軸部４１にローリングピストン３２を通過させて、嵌め合わせが行われる。 For example, a case where the rolling piston 32 is fitted to the eccentric shaft portion 42 with respect to the integrated crankshaft 4 including the eccentric shaft portion 42 will be described. In order to fit the rolling piston 32 to the upper eccentric shaft portion 42, the rolling piston 32 is passed through the long shaft portion 43 to perform the fitting. Further, in order to fit the rolling piston 32 to the lower eccentric shaft portion 42, the rolling piston 32 is passed through the short shaft portion 41 to perform the fitting.
　ここで、偏芯軸部４２の偏芯軸が、クランクシャフト４が回転する軸の中心からのずれを示す偏芯量ｒについて、偏芯量ｒが同じときの、図４と図５との偏芯軸部４２の径を比較する。図４に示すように、偏芯軸部４２の外周の一部が、回転軸である長軸部４３からからはみ出すなどした方が、図５に示す、全周において長軸部４３から突出させる制約がある偏芯軸部４２よりも、偏芯軸部４２の径が小さくなる。これは、短軸部４１と下側の偏芯軸部４２との位置関係についても同様である。 Here, with respect to the eccentric amount r indicating that the eccentric shaft of the eccentric shaft portion 42 deviates from the center of the shaft on which the crankshaft 4 rotates, when the eccentric amount r is the same, FIGS. 4 and 5 The diameters of the eccentric shaft portions 42 are compared. As shown in FIG. 4, a part of the outer circumference of the eccentric shaft portion 42 protrudes from the long shaft portion 43, which is a rotating shaft, so that the eccentric shaft portion 42 protrudes from the long shaft portion 43 over the entire circumference as shown in FIG. The diameter of the eccentric shaft portion 42 is smaller than that of the eccentric shaft portion 42 having restrictions. This also applies to the positional relationship between the short shaft portion 41 and the lower eccentric shaft portion 42.
　しかしながら、長軸部４３と偏芯軸部４２とがあらかじめ一体で構成されているとき、図４の長軸部４３と偏芯軸部４２との位置関係では、ローリングピストン３２の内径は、偏芯軸部４２の径の長さだけでなく突出した長軸部４３分を加えることになる。このため、ローリングピストン３２と偏芯軸部４２との隙間が広くなってしまうことから、図４の位置関係が採用できなかった。 However, when the long shaft portion 43 and the eccentric shaft portion 42 are integrally formed in advance, the inner diameter of the rolling piston 32 is biased in the positional relationship between the long shaft portion 43 and the eccentric shaft portion 42 in FIG. Not only the length of the diameter of the core shaft portion 42 but also the protruding long shaft portion 43 minutes will be added. For this reason, the gap between the rolling piston 32 and the eccentric shaft portion 42 becomes wide, so that the positional relationship shown in FIG. 4 cannot be adopted.
　そこで、実施の形態１におけるロータリ圧縮機１０１は、部品として分割された偏芯軸部４２、短軸部４１および長軸部４３を組み合わせたクランクシャフト４を備える。クランクシャフト４を結合し、組み立てる際には、まず、２つの偏芯軸部４２に対し、それぞれローリングピストン３２を嵌め合わせる。このとき、短軸部４１および長軸部４３によってローリングピストン３２の挿入が邪魔されないので、２つの偏芯軸部４２には、偏芯軸部４２の直径に対応した内径のローリングピストン３２を嵌め合わせることができる。そして、ローリングピストン３２を嵌め合わせた後で、２つの偏芯軸部４２と短軸部４１および長軸部４３を嵌め合いにより結合し、クランクシャフト４を組み立てる。ここで、短軸部４１および長軸部４３は、それぞれ１つの部品として説明するが、さらに複数の部品に分割されていてもよい。 Therefore, the rotary compressor 101 according to the first embodiment includes a crankshaft 4 in which an eccentric shaft portion 42, a short shaft portion 41, and a long shaft portion 43, which are divided as parts, are combined. When connecting and assembling the crankshaft 4, first, the rolling pistons 32 are fitted to the two eccentric shaft portions 42, respectively. At this time, since the short shaft portion 41 and the long shaft portion 43 do not interfere with the insertion of the rolling piston 32, the two eccentric shaft portions 42 are fitted with the rolling piston 32 having an inner diameter corresponding to the diameter of the eccentric shaft portion 42. Can be matched. Then, after fitting the rolling piston 32, the two eccentric shaft portions 42, the short shaft portion 41, and the long shaft portion 43 are joined by fitting to assemble the crankshaft 4. Here, the short shaft portion 41 and the long shaft portion 43 are described as one component each, but may be further divided into a plurality of components.
　以上のように、実施の形態１のロータリ圧縮機１０１によれば、偏芯軸部４２、短軸部４１および長軸部４３を組み合わせたクランクシャフト４を備える。このため、偏芯軸部４２の直径に対応した内径のローリングピストン３２を、短軸部４１および長軸部４３に邪魔されることなく、嵌め合わせて取り付けることができる。このため、偏芯軸部４２の全周を突出させて直径を拡大しなくても、偏芯量ｒを大きくすることができ、ローリングピストン３２の自転が阻害されることなく、摺動損失を低減し、ロータリ圧縮機１０１の密閉容器１の大きさに対して圧縮性能を向上させることができる。 As described above, according to the rotary compressor 101 of the first embodiment, the crankshaft 4 is provided by combining the eccentric shaft portion 42, the short shaft portion 41, and the long shaft portion 43. Therefore, the rolling piston 32 having an inner diameter corresponding to the diameter of the eccentric shaft portion 42 can be fitted and attached to the short shaft portion 41 and the long shaft portion 43 without being disturbed. Therefore, the amount of eccentricity r can be increased without increasing the diameter by projecting the entire circumference of the eccentric shaft portion 42, and the sliding loss is not hindered by the rotation of the rolling piston 32. It can be reduced and the compression performance can be improved with respect to the size of the closed container 1 of the rotary compressor 101.
実施の形態２．
　図６は、実施の形態２に係る圧縮機におけるクランクシャフトを中心とする回転駆動部分について説明する図である。前述した実施の形態１では、ロータリ圧縮機１０１のクランクシャフト４を、短軸部４１、偏芯軸部４２および長軸部４３の３つの部品に分割し、組み合わせて構成するものであった。一方、回転子２２は、中心部分に空洞を有する。そして、実施の形態１のロータリ圧縮機１０１では、クランクシャフト４の長軸部４３を回転子２２の空洞に挿通し、クランクシャフト４と回転子２２とを焼き嵌めて固定した。 Embodiment 2.
FIG. 6 is a diagram illustrating a rotationally driven portion centered on a crankshaft in the compressor according to the second embodiment. In the first embodiment described above, the crankshaft 4 of the rotary compressor 101 is divided into three parts, a short shaft portion 41, an eccentric shaft portion 42, and a long shaft portion 43, and is configured by combining them. On the other hand, the rotor 22 has a cavity in the central portion. Then, in the rotary compressor 101 of the first embodiment, the long shaft portion 43 of the crankshaft 4 is inserted into the cavity of the rotor 22, and the crankshaft 4 and the rotor 22 are shrink-fitted and fixed.
　実施の形態２のロータリ圧縮機１０１は、回転子２２が、下端部における回転中心部分に、クランクシャフト４と結合する回転子結合部２４を有する。そして、回転子２２の回転子結合部２４とクランクシャフト４の長軸部４３とを嵌め合わせて結合することで、回転子２２とクランクシャフト４とを固定する。ここで、実施の形態２のロータリ圧縮機１０１では、回転子２２の空洞に長軸部４３を挿通する必要がない。このため、実施の形態２の長軸部４３は、実施の形態１の長軸部４３よりも短い。 The rotary compressor 101 of the second embodiment has a rotor coupling portion 24 in which the rotor 22 is coupled to the crankshaft 4 at the rotation center portion at the lower end portion. Then, the rotor 22 and the crankshaft 4 are fixed by fitting and coupling the rotor coupling portion 24 of the rotor 22 and the long shaft portion 43 of the crankshaft 4. Here, in the rotary compressor 101 of the second embodiment, it is not necessary to insert the long shaft portion 43 into the cavity of the rotor 22. Therefore, the long shaft portion 43 of the second embodiment is shorter than the long shaft portion 43 of the first embodiment.
　以上のように、実施の形態２のロータリ圧縮機１０１によれば、回転子２２は、回転子結合部２４を有し、回転子結合部２４とクランクシャフト４の長軸部４３とを結合させて、回転子２２とクランクシャフト４とを一体化して回転できるようにした。このため、回転子２２において、クランクシャフト４が挿入される空洞を廃止することができる。そして、回転子２２が内蔵する永久磁石（図示せず）を設置する空間を、回転子２２の中心側に拡張することができる。したがって、半径方向に回転子２２を縮小することができ、密閉容器１全体の径方向の縮小を行うことができる。 As described above, according to the rotary compressor 101 of the second embodiment, the rotor 22 has a rotor coupling portion 24, and the rotor coupling portion 24 and the long shaft portion 43 of the crankshaft 4 are coupled to each other. The rotor 22 and the crankshaft 4 are integrated so that they can rotate. Therefore, in the rotor 22, the cavity into which the crankshaft 4 is inserted can be eliminated. Then, the space for installing the permanent magnet (not shown) built in the rotor 22 can be expanded to the center side of the rotor 22. Therefore, the rotor 22 can be reduced in the radial direction, and the entire closed container 1 can be reduced in the radial direction.
実施の形態３．
　図７は、実施の形態３に係る冷凍サイクル装置の構成例を表す図である。ここで、図７では、冷凍サイクル装置として空気調和装置を示している。図７の空気調和装置は、室外機１００と室内機２００とを、冷媒配管３００および冷媒配管４００により配管接続し、冷媒を循環させる冷媒回路を構成する。室外機１００は、実施の形態１および実施の形態２において説明したロータリ圧縮機１０１を有する。また、室外機１００は、四方弁１０２、室外熱交換器１０３、膨張弁１０４および室外送風機１０５を有する。また、室内機２００は、室内熱交換器２０１を有する。 Embodiment 3.
FIG. 7 is a diagram showing a configuration example of the refrigeration cycle device according to the third embodiment. Here, FIG. 7 shows an air conditioner as a refrigeration cycle device. The air conditioner of FIG. 7 connects the outdoor unit 100 and the indoor unit 200 with a refrigerant pipe 300 and a refrigerant pipe 400 to form a refrigerant circuit for circulating a refrigerant. The outdoor unit 100 includes the rotary compressor 101 described in the first and second embodiments. Further, the outdoor unit 100 includes a four-way valve 102, an outdoor heat exchanger 103, an expansion valve 104, and an outdoor blower 105. Further, the indoor unit 200 has an indoor heat exchanger 201.
　ロータリ圧縮機１０１は、前述したように、吸入した冷媒を圧縮して吐出する。ここで、特に限定するものではないが、ロータリ圧縮機１０１を、たとえば、インバータ回路などにより、運転周波数を任意に変化できるようにしてもよい。四方弁１０２は、冷房運転時と暖房運転時とによって冷媒の流れを切り換える弁である。 As described above, the rotary compressor 101 compresses and discharges the sucked refrigerant. Here, although not particularly limited, the rotary compressor 101 may be capable of arbitrarily changing the operating frequency by, for example, an inverter circuit or the like. The four-way valve 102 is a valve that switches the flow of the refrigerant between the cooling operation and the heating operation.
　室外熱交換器１０３は、冷媒と空気（室外の空気）との熱交換を行う。たとえば、暖房運転時においては蒸発器として機能し、冷媒を蒸発させ、気化させる。また、冷房運転時においては凝縮器として機能し、冷媒を凝縮して液化させる。また、室外送風機１０５は、室外熱交換器１０３に室外の空気を送り込み、室外の空気と冷媒との熱交換を促す。 The outdoor heat exchanger 103 exchanges heat between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation to evaporate and vaporize the refrigerant. In addition, it functions as a condenser during cooling operation to condense and liquefy the refrigerant. Further, the outdoor blower 105 sends outdoor air to the outdoor heat exchanger 103 to promote heat exchange between the outdoor air and the refrigerant.
　減圧装置となる絞り装置などの膨張弁１０４は冷媒を減圧して膨張させるものである。たとえば電子式膨張弁などで構成した場合には、制御装置（図示せず）などの指示に基づいて開度調整を行う。室内熱交換器２０１は、たとえば空調対象となる空気と冷媒との熱交換を行う。暖房運転時においては凝縮器として機能し、冷媒を凝縮して液化させる。また、冷房運転時においては蒸発器として機能し、冷媒を蒸発させ、気化させる。室内送風機２０２は、空調対象となる空気を室内熱交換器２０１に送り込み、その空気と冷媒との熱交換を促す。 The expansion valve 104 such as a throttle device serving as a pressure reducing device decompresses and expands the refrigerant. For example, in the case of an electronic expansion valve or the like, the opening degree is adjusted based on an instruction from a control device (not shown) or the like. The indoor heat exchanger 201 exchanges heat between, for example, air to be air-conditioned and a refrigerant. During heating operation, it functions as a condenser and condenses and liquefies the refrigerant. In addition, it functions as an evaporator during cooling operation to evaporate and vaporize the refrigerant. The indoor blower 202 sends air to be air-conditioned to the indoor heat exchanger 201 to promote heat exchange between the air and the refrigerant.
　以上のように、実施の形態３の冷凍サイクル装置によれば、実施の形態１および実施の形態２で説明したロータリ圧縮機１０１を機器として有することで、室外機１００などの小型化をはかることができる。 As described above, according to the refrigeration cycle apparatus of the third embodiment, the outdoor unit 100 and the like can be miniaturized by having the rotary compressor 101 described in the first embodiment and the second embodiment as an apparatus. Can be done.
　前述した実施の形態１～実施の形態３においては、ロータリ圧縮機１０１が冷媒を圧縮するものとして説明したが、これに限定するものではない。空気など、他の流体を圧縮する圧縮機とすることができる。 In the above-described first to third embodiments, the rotary compressor 101 has been described as compressing the refrigerant, but the present invention is not limited to this. It can be a compressor that compresses other fluids such as air.
　また、前述した実施の形態２では、ロータリ圧縮機１０１を例に説明したが、これに限定するものではなく、スクロール圧縮機など、他の密閉型電動圧縮機にも適用することができる。 Further, in the above-described second embodiment, the rotary compressor 101 has been described as an example, but the present invention is not limited to this, and the present invention can be applied to other closed electric compressors such as a scroll compressor.
　また、前述した実施の形態３では、空気調和装置を例にした冷凍サイクル装置について説明したが、たとえば、冷凍装置または給湯装置などにも用いることができる。 Further, in the third embodiment described above, the refrigerating cycle device using the air conditioner as an example has been described, but it can also be used for, for example, a refrigerating device or a hot water supply device.
　１　密閉容器、２　電動機部、３　圧縮機構部、４　クランクシャフト、５　吸入管、６　吐出管、７　支持脚、８　冷凍機油、２１　固定子、２２　回転子、２３　油分離板、２４　回転子結合部、３１　圧縮室、３２　ローリングピストン、３３　シリンダ、３３ａ　吸入口、３３ｂ　ベーン溝、３４　シリンダヘッド、３５　フレーム、３６　仕切り板、３７　ベーン、３８　バネ、４１　短軸部、４１ａ　短軸結合部、４２　偏芯軸部、４３　長軸部、４３ａ　長軸結合部、５１　吸入マフラ、１００　室外機、１０１　ロータリ圧縮機、１０２　四方弁、１０３　室外熱交換器、１０４　膨張弁、１０５　室外送風機、２００　室内機、２０１　室内熱交換器、２０２　室内送風機、３００，４００　冷媒配管。 1 closed container, 2 electric motor, 3 compression mechanism, 4 crankshaft, 5 suction pipe, 6 discharge pipe, 7 support legs, 8 refrigerating machine oil, 21 stator, 22 rotor, 23 oil separator, 24 rotor coupling Part, 31 compression chamber, 32 rolling piston, 33 cylinder, 33a suction port, 33b vane groove, 34 cylinder head, 35 frame, 36 partition plate, 37 vane, 38 spring, 41 short shaft part, 41a short shaft joint part, 42 Eccentric shaft part, 43 long shaft part, 43a long shaft joint part, 51 suction muffler, 100 outdoor unit, 101 rotary compressor, 102 four-way valve, 103 outdoor heat exchanger, 104 expansion valve, 105 outdoor blower, 200 indoor unit , 201 indoor heat exchanger, 202 indoor blower, 300,400 refrigerant pipe.

Claims (4)

  1. 　外殻となる密閉容器と、
    　前記密閉容器内において、固定子および回転子を有する電動機部と、
    　前記密閉容器内において、ローリングピストンがそれぞれ嵌め合わされた複数の偏芯軸部を有し、前記回転子の回転とともに回転する回転軸となるクランクシャフトと、
    　前記密閉容器内において、前記クランクシャフトの回転により駆動して、圧縮対象の流体を圧縮する圧縮機構部とを備え、
    　前記クランクシャフトは、前記複数の偏芯軸部、前記回転子と前記複数の偏芯軸部との間の軸となる長軸部および前記複数の偏芯軸部と前記クランクシャフトの下端側を支持するシリンダヘッドとの間の軸となる短軸部に分かれた部品の組み合わせで構成される圧縮機。     A closed container that serves as the outer shell,
    In the closed container, a motor unit having a stator and a rotor, and
    In the closed container, a crankshaft having a plurality of eccentric shafts into which rolling pistons are fitted, and serving as a rotating shaft that rotates with the rotation of the rotor,
    In the closed container, a compression mechanism unit that is driven by the rotation of the crankshaft to compress the fluid to be compressed is provided.
    The crankshaft includes a plurality of eccentric shaft portions, a long shaft portion serving as an axis between the rotor and the plurality of eccentric shaft portions, and the plurality of eccentric shaft portions and the lower end side of the crankshaft. A compressor consisting of a combination of parts divided into short shafts that serve as the shaft between the crankhead and the supporting cylinder head.
  2. 　前記回転子は、回転中心部分に、前記クランクシャフトの前記長軸部と結合する結合部を有する請求項１に記載の圧縮機。 The compressor according to claim 1, wherein the rotor has a coupling portion that is coupled to the long shaft portion of the crankshaft at a rotation center portion.
  3. 　前記圧縮機構部は、
    　前記偏芯軸部の回転に伴って回転する前記ローリングピストンと、
    　前記偏芯軸部および前記ローリングピストンを収容するシリンダと、
    　前記シリンダの上端側で固定され、前記クランクシャフトを支持するフレームと、
    　前記シリンダ内に配置され、前記ローリングピストンに押圧されるベーンとを有し、
    　前記シリンダ、前記シリンダヘッド、前記フレーム、前記ベーンおよび前記ローリングピストンとで囲まれて前記流体を圧縮する圧縮室を有する請求項１または請求項２に記載の圧縮機。     The compression mechanism unit
    The rolling piston that rotates with the rotation of the eccentric shaft portion,
    A cylinder accommodating the eccentric shaft portion and the rolling piston,
    A frame fixed on the upper end side of the cylinder and supporting the crankshaft,
    It has a vane that is located in the cylinder and is pressed against the rolling piston.
    The compressor according to claim 1 or 2, further comprising a compression chamber that is surrounded by the cylinder, the cylinder head, the frame, the vane, and the rolling piston to compress the fluid.
  4. 　請求項１～請求項３のいずれか一項に記載の圧縮機、凝縮器、減圧装置および蒸発器が配管接続され、冷媒の循環が行われる冷媒回路を有する冷凍サイクル装置。 A refrigeration cycle device having a refrigerant circuit in which a compressor, a condenser, a decompression device, and an evaporator according to any one of claims 1 to 3 are connected by piping and a refrigerant is circulated.
PCT/JP2019/046811 2019-11-29 2019-11-29 Compressor and refrigeration cycle device WO2021106198A1 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63219890A (en) * 1986-11-05 1988-09-13 Riken Corp Combined crankshaft for rotary compressor
JPH01148474A (en) * 1987-12-03 1989-06-09 Toshiba Corp Manufacture of crank shaft
JP2012154266A (en) * 2011-01-27 2012-08-16 Sanyo Electric Co Ltd Rotary compressor and method of manufacturing the same

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63219890A (en) * 1986-11-05 1988-09-13 Riken Corp Combined crankshaft for rotary compressor
JPH01148474A (en) * 1987-12-03 1989-06-09 Toshiba Corp Manufacture of crank shaft
JP2012154266A (en) * 2011-01-27 2012-08-16 Sanyo Electric Co Ltd Rotary compressor and method of manufacturing the same

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