WO2014156679A1 - Compresseur rotatif multicylindre - Google Patents

Compresseur rotatif multicylindre Download PDF

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Publication number
WO2014156679A1
WO2014156679A1 PCT/JP2014/056650 JP2014056650W WO2014156679A1 WO 2014156679 A1 WO2014156679 A1 WO 2014156679A1 JP 2014056650 W JP2014056650 W JP 2014056650W WO 2014156679 A1 WO2014156679 A1 WO 2014156679A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
rotary compressor
partition plate
motor
φmo
Prior art date
Application number
PCT/JP2014/056650
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English (en)
Japanese (ja)
Inventor
郁男 江崎
茂樹 三浦
小川　真
将成 宇野
章浩 野口
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to EP14774791.9A priority Critical patent/EP2947321A4/fr
Priority to CN201480008720.0A priority patent/CN105008722A/zh
Publication of WO2014156679A1 publication Critical patent/WO2014156679A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry

Definitions

  • the present invention relates to a hermetic multi-cylinder rotary compressor capable of increasing the capacity of a compressor (push-up amount UP) without increasing the motor core diameter.
  • the mechanical load such as bearing surface pressure and blade side surface pressure
  • the motor core diameter body diameter
  • This is achieved by increasing the journal diameter by one rank.
  • the increase in the motor core diameter (body diameter) and journal diameter is limited by the manufacturing equipment, so it will be designed by selecting from a limited lineup. If you do not have a machine, a large capital investment is required.
  • Patent Document 1 discloses that the displacement (capacity) of the compressor can be increased without changing the motor core diameter, in other words, without changing the external dimensions of the compressor. This is because in a sealed multi-cylinder rotary compressor, a plurality of crankshafts are connected to each other, thereby reducing the opening provided in the partition plate that partitions the plurality of cylinders and supporting the connecting portion in the opening. To reduce the outer diameter of the rotor that rotates in the cylinder, and to increase the eccentric amount of the eccentric shaft (the blade stroke is made longer) to increase the effective capacity in the cylinder (push-away amount) ) To increase the capacity.
  • Patent Document 1 since the structure disclosed in the above-mentioned Patent Document 1 has to be structured such that the crankshaft is divided into a plurality of parts, the number of parts increases, the number of processing steps and assembly steps increase, and the configuration becomes complicated. There were problems such as inevitable increase in cost.
  • the blade stroke is lengthened by increasing the inner diameter of the cylinder, and a compressor with a pushing-out amount that is one rank higher is manufactured. It is possible.
  • the mechanical load such as the bearing surface pressure and the blade side surface pressure is increased, and thus there is a technical problem that measures to suppress it are essential.
  • the present invention has been made in view of such circumstances. Even if the cylinder inner diameter is increased and the capacity is increased without increasing the motor core diameter, the mechanical load (mechanical load) is increased. It is an object of the present invention to provide a hermetic multi-cylinder rotary compressor capable of manufacturing a compressor having a displacement higher by one rank while suppressing the load).
  • the multi-cylinder rotary compressor of the present invention employs the following means. That is, the multi-cylinder rotary compressor according to the first aspect of the present invention is provided with a motor and a compression mechanism driven by the motor in a sealed container, and the compression mechanism includes a plurality of cylinders and the plurality of cylinders.
  • a multi-cylinder rotary compressor that is a rotary compression mechanism that includes a partition plate that partitions cylinders, a blade that partitions each cylinder into a suction side and a discharge side, and a rotor that rotates within each cylinder.
  • each cylinder has a ratio of 0.49 or more to the inner diameter ⁇ Dc of each cylinder with respect to the motor core diameter ⁇ Mo.
  • the blade stroke can be made a long stroke without changing the motor core diameter ⁇ Mo and without increasing the gas load (compression load) to the left.
  • the displacement amount of the compressor can be increased (the displacement amount UP)
  • the width Hs of the partition plate with respect to the cylinder width Hc is made as small as possible, and the distance between the support points of the upper bearing and the lower bearing is reduced.
  • an increase in bearing surface pressure can be suppressed. Therefore, it is possible to manufacture a sealed multi-cylinder rotary compressor having a displacement amount one rank higher with the existing motor core diameter, and it is possible to expand the product lineup without making a large capital investment.
  • the partition plate is made of a material having a Young's modulus of 160 [GPa] or more.
  • the partition plate is made of a material having a Young's modulus of 160 [GPa] or more, the width Hs of the partition plate is reduced to 0.35 or less of the cylinder width Hc. Even so, by using a material with a Young's modulus of 160 [GPa] or lower, which is higher than that of a sintered alloy or cast iron, the distance between the support points of the bearing can be reduced while suppressing deformation. Can do. Therefore, an increase in mechanical load such as bearing surface pressure can be suppressed, and the displacement of the compressor can be easily increased to a capacity one rank higher without changing the motor core diameter.
  • the multi-cylinder rotary compressor according to the third aspect of the present invention is the above-described multi-cylinder rotary compressor, wherein the partition plate is made of carbon steel or alloy steel.
  • the partition plate is carbon steel or alloy steel having a Young's modulus of 160 [GPa] or higher, carbon steel or alloy steel having higher rigidity than sintered alloy or cast iron is used. By using it, a Young's modulus of 160 [GPa] or more can be secured, and deformation can be suppressed while thinning the partition plate only by selecting an appropriate material. Therefore, an increase in mechanical load such as bearing surface pressure can be suppressed, and the displacement of the compressor can be easily increased to a capacity one rank higher without changing the motor core diameter.
  • the multi-cylinder rotary compressor according to the fourth aspect of the present invention is the above-mentioned multi-cylinder rotary compressor, wherein the blade has a hard coating such as a CrN-based PVD film or a DLC film on the surface. It is said that the blade has been applied.
  • the blade is a blade having a surface coated with a hard coating such as a CrN-based PVD film or a DLC film
  • the blade side surface is increased by increasing the blade stroke.
  • the pressure rises by applying a hard coating on the blade surface, it is possible to sufficiently cope with abnormal wear due to an increase in surface pressure. Therefore, the cylinder inner diameter can be increased without changing the motor core diameter, and the displacement of the compressor can be easily increased to a capacity one rank higher without making capital investment.
  • the refrigerating machine oil filled in the bottom portion of the hermetic container is added with an extreme pressure agent. It is considered as refrigeration oil.
  • the bearing surface is increased as the capacity of the compressor is increased. It is inevitable that mechanical loads such as pressure and blade side surface pressure increase somewhat, and although extreme pressure lubrication is likely to occur in those sliding parts, extreme pressure agent effective under high load is used as refrigerating machine oil. By adding it, high lubricity on the sliding surface can be maintained, and seizure, wear, and scuffing can be prevented. Therefore, it is possible to effectively cope with an increase in mechanical load accompanying an increase in capacity of the compressor.
  • the blade stroke is lengthened and the displacement of the compressor is increased (the displacement is increased).
  • FIG. 1 is a longitudinal sectional view of a multi-cylinder rotary compressor according to an embodiment of the present invention. It is a cross-sectional view showing the specification of the compression mechanism part of the said multi-cylinder rotary compressor. It is a longitudinal cross-sectional view showing the specification of the compression mechanism part of the said multi-cylinder rotary compressor. It is a graph which shows the relationship between the ratio of the motor core diameter of a multi-cylinder rotary compressor, and a cylinder internal diameter, and gas load. It is a graph which shows the relationship between the ratio of the partition plate width
  • FIG. 1 is a longitudinal sectional view of a multi-cylinder rotary compressor according to an embodiment of the present invention
  • FIG. 2 is a transverse sectional view showing specifications of a compression mechanism portion
  • FIG. A longitudinal sectional view showing specifications of the mechanism portion is shown.
  • a multi-cylinder rotary compressor 1 according to the present embodiment includes a cylindrical sealed container 2 whose upper and lower portions are sealed by an upper cover 3 and a lower cover 4, and a motor 5 is installed in an upper portion inside the container.
  • a compression mechanism (rotary compression mechanism) 6 driven by a motor 5 is a hermetic multi-cylinder rotary compressor 1 installed at a lower portion thereof.
  • a mounting leg 7 is provided on the outer periphery of the lower portion of the sealed container 2.
  • a discharge pipe 8 that penetrates the upper cover 3 is provided in the upper part of the sealed container 2, and the high-pressure refrigerant gas compressed by the multi-cylinder rotary compressor 1 is discharged to the refrigeration cycle side.
  • an accumulator 9 is integrally assembled on the outer peripheral portion of the sealed container 2 to separate liquid components such as oil and liquid refrigerant contained in the low-pressure refrigerant gas returning from the refrigeration cycle side, and only the gas component is separated. Is sucked into the compression mechanism 6 through the suction pipes 10 and 11.
  • the motor 5 includes a stator 12 and a rotor 13, and the stator 12 is fixedly installed on the inner peripheral surface of the sealed container 2 by press fitting or the like.
  • a crankshaft 14 is integrally coupled to the rotor 13 so that the rotational driving force can be transmitted to the compression mechanism 6 via the crankshaft 14.
  • a first eccentric portion 15 and a second eccentric portion 16 are provided below the crankshaft 14 corresponding to a first rotor 24 and a second rotor 25 of the rotary compression mechanism 6 described later.
  • the rotary compression mechanism 6 is a two-cylinder type in this embodiment.
  • the first and second rotary compression mechanisms 6A and 6B are formed with a first cylinder chamber 17 and a second cylinder chamber 18 (hereinafter sometimes simply referred to as cylinders 17 and 18), and the first eccentricity of the crankshaft 14 is formed.
  • the first cylinder main body 19 and the second cylinder main body 20 fixedly installed in the sealed container 2 corresponding to the portion 15 and the second eccentric portion 16, and between the first cylinder main body 19 and the second cylinder main body 20.
  • the partition plate (separator plate) 21 that is mounted and partitions the first cylinder chamber 17 and the second cylinder chamber 18 and provided on the upper surface of the first cylinder body 19, partitions the first cylinder chamber 17, and the crankshaft 14 And a lower bearing 23 that is provided on the lower surface of the second cylinder body 20, defines the second cylinder chamber 18, and supports the crankshaft 14. , And a.
  • first and second rotary compression mechanisms 6A and 6B are rotatably fitted to the first eccentric portion 15 and the second eccentric portion 16, and rotate in the first cylinder chamber 17 and the second cylinder chamber 18.
  • the first rotor 24 and the second rotor 25 are slidably fitted into blade grooves 26 and 27 (see FIG. 2) provided in the first cylinder body 19 and the second cylinder body 20, respectively.
  • Blades 28 and 29 for partitioning the cylinder chamber 17 and the second cylinder chamber 18 into a suction chamber side and a discharge chamber side are provided.
  • Low-pressure refrigerant gas is sucked into the first cylinder chamber 17 and the second cylinder chamber 18 of the first and second rotary compression mechanisms 6A and 6B from the suction pipes 10 and 11 through the suction ports 30 and 31, respectively. After being compressed by the rotation of the first rotor 24 and the second rotor 25, it is discharged into the discharge chambers 32 and 33 through a discharge port and a discharge valve (not shown), and is discharged from the discharge chambers 32 and 33 into the sealed container 2. After being discharged, it is configured to be sent to the refrigeration cycle via the discharge pipe 8.
  • the first cylinder body 19 and the second cylinder body 20, the partition plate 21, the upper bearing 22, and the lower bearing 23 constituting the rotary compression mechanism 6 are integrally tightened and fixed via bolts.
  • the bottom of the sealed container 2 is filled with refrigerating machine oil 34 such as PAG oil or POE oil, and, as is well known, through the oil supply hole provided in the crankshaft 14, the compression mechanism 6. It is possible to supply oil to the lubricated part. It is assumed that an appropriate amount of extreme pressure agent suitable for each oil is added to the refrigerator oil 34.
  • the first cylinder chamber 17 and the second cylinder chamber 18 are not changed without changing the core diameter (body diameter or outer diameter) ⁇ Mo of the motor 5 used in the compressor that is already in production.
  • the motor core diameter is ⁇ Mo
  • the cylinder inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18 are When ⁇ Dc, the cylinder inner diameter ⁇ Dc is ⁇ Dc / ⁇ Mo ⁇ 0.49 Is set.
  • the cylinder inner diameter ⁇ Dc is increased without changing the motor core diameter ⁇ Mo, and the ratio ⁇ Dc / ⁇ Mo is set to 0.49 or more to increase the blade stroke. Even if the (sliding stroke of blades 28 and 29) is made longer, the gas determined by the projected area of the rotor while suppressing the projected area of the rotor, which is the product of the rotor outer diameter ⁇ Dr and the rotor width Hr. It has become clear from FIGS. 4 and 6 that the load (compression load) can be suppressed to a predetermined value or less.
  • the gas load that determines the mechanical load can be suppressed to a certain value or less, the knowledge that the displacement can be increased by increasing the cylinder inner diameter ⁇ Dc without changing the motor core diameter ⁇ Mo. Obtained. That is, when the displacement amount is increased, as shown in FIG. 3, the gas load, which is a mechanical load, is increased and the deformation amount of the crankshaft 14 is increased, so that it is necessary to suppress the deformation of the crankshaft 14.
  • the amount of deformation of the crankshaft 14 increases, the degree of contact of the shaft with respect to the bearing increases, and the bearing surface pressure increases. Since the amount of deformation of the crankshaft 14 depends on the distance L between the bearing support points between the upper bearing 22 and the lower bearing 23, reducing the distance L between the bearing support points as much as possible reduces the bearing surface pressure. It turns out that it is effective.
  • the width Hc (hereinafter referred to as cylinder width Hc) of the first cylinder chamber 17 and the second cylinder chamber 18 and the width Hs (hereinafter referred to as separator plate) 21 of the partition plate (separator plate) 21 are used.
  • separator plate the width Hs in order to increase the displacement amount. Therefore, the partition plate width Hs is reduced.
  • FIG. When the bearing surface pressure is plotted on the vertical axis, it becomes a curve that rises to the right. It has been found that if Hs / Hc is set to a predetermined value or less, the bearing surface pressure can be set to an allowable value or less.
  • the partition plate 21 when the partition plate 21 is made thin by using a sintered metal or cast iron partition plate conventionally used for the partition plate 21 by reducing the width Hs, these materials have a Young's modulus of 160. Since it is as low as [GPa] or less, there is a possibility that deformation due to thinning becomes a problem. Therefore, it is desirable that the partition plate 21 is made of a material having a Young's modulus of 160 [GPa] or higher. For example, carbon steel or alloy steel having a Young's modulus of around 200 [GPa] may be used.
  • the strokes of the blades 28 and 29 correspondingly have to be increased and the strokes must be increased.
  • the pressure applied to the side surfaces of the blades 28 and 29 is increased. It increases and the so-called blade side surface pressure increases.
  • a hard coating such as a PVD film (Physical Vapor Deposition film) such as CrN or a DLC film (diamond-like carbon film) is applied to both side surfaces of the blades 28 and 29, and the surface pressure is increased. It is desirable to be able to cope with abnormal wear due to ascent.
  • the following operational effects are obtained.
  • the rotary compressor 1 if the inner diameters of the first cylinder chamber 17 and the second cylinder chamber 18, that is, the cylinder inner diameter ⁇ Dc is increased, the cylinder volume increases. Therefore, the eccentricity of the first eccentric portion 15 and the second eccentric portion 16 is increased. By increasing the amount to increase the stroke of the blades 28 and 29, the displacement of the compressor can be increased.
  • the core diameter ⁇ Mo of the motor 5 is limited by the manufacturing equipment. Therefore, when the motor core diameter ⁇ Mo is increased, capital investment is newly required. If the rotary compressor 1 is left as it is and the cylinder inner diameter ⁇ Dc is increased to increase the capacity, the existing compressor can be used to manufacture the rotary compressor 1 having a higher displacement amount without using capital investment. Will be able to.
  • the motor 5 and the compression mechanism 6 driven by the motor 5 are provided in the sealed container 2, and the compression mechanism 6 includes a plurality of cylinders 17 and 18, a plurality of cylinders 17, A rotary compression mechanism provided with a partition plate 21 that partitions 18, blades 28 and 29 that partition the cylinders 17 and 18 into a suction side and a discharge side, and rotors 24 and 25 that rotate within the cylinders 17 and 18.
  • a sealed multi-cylinder rotary compressor 1 wherein the motor 5 has a core diameter of ⁇ Mo, the inner diameters of the cylinders 17 and 18 are ⁇ Dc, the widths of the cylinders 17 and 18 are Hc, and a partition plate When the width of 21 is Hs, the structure satisfies Hs / Hc ⁇ 0.35 under the condition of ⁇ Dc / ⁇ Mo ⁇ 0.49.
  • the strokes of the blades 28 and 29 are lengthened, and the displacement amount of the multi-cylinder rotary compressor 1 is increased (pushing away). Amount), and the partition plate width Hs with respect to the cylinder width Hc is made as small as possible, and the distance L between the support points of the upper bearing 22 and the lower bearing 23 is made smaller, thereby suppressing an increase in bearing surface pressure. be able to. Therefore, the sealed multi-cylinder rotary compressor 1 having a displacement amount higher by one rank can be manufactured with the existing motor core diameter ⁇ Mo, and the product lineup can be expanded without making a large capital investment.
  • the partition plate 21 may be deformed, but the partition plate 21 has a Young's modulus of 160 [GPa] or more.
  • the width Hs of the partition plate 21 is reduced to 0.35 or less of the cylinder width Hc by being made of a material such as carbon steel or alloy steel, the deformation can be suppressed. Therefore, an increase in mechanical load such as bearing surface pressure is suppressed, the cylinder inner diameter ⁇ Dc is increased without changing the motor core diameter ⁇ Mo, and the displacement amount of the multi-cylinder rotary compressor 1 is easily increased to a capacity one rank higher. Capacitance can be achieved.
  • the strokes of the blades 28 and 29 become longer and the blade side surface pressure rises.
  • a CrN-based PVD film or DLC film or the like is formed on the blade surface.
  • the cylinder inner diameter ⁇ Dc is increased without changing the core diameter ⁇ Mo of the motor 5, and the displacement amount of the multi-cylinder rotary compressor 1 is simply increased to a capacity one rank higher without making capital investment. Can do.
  • this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably.
  • the first rotary compression mechanism 6A and the second rotary compression mechanism 6B are provided with a phase difference of 180 degrees.
  • the discharge chambers 32 and 33 may be configured such that the high-pressure gas discharged into the discharge chamber 33 is merged in the discharge chamber 32 and discharged into the sealed container 2.
  • the widths Hc of the first cylinder chamber 17 and the second cylinder chamber 18 are not necessarily the same, and may be different widths. In this case, the width Hc may be based on the larger one.
  • Multi-cylinder rotary compressor 1 Sealed container 5 Motor 6 Compression mechanism (rotary compression mechanism) 6A First rotary compression mechanism 6B Second rotary compression mechanism 14 Crankshaft 15 First eccentric portion 16 Second eccentric portion 17 First cylinder chamber (cylinder) 18 Second cylinder chamber (cylinder) 19 First cylinder body 20 Second cylinder body 21 Partition plate 24 First rotor 25 Second rotor 28, 29 Blade 34 Refrigerating machine oil ⁇ Mo Motor core diameter ⁇ Dc Cylinder inner diameter Hc Cylinder width Hs Partition plate width

Abstract

L'invention porte, dans un compresseur rotatif multicylindre, sur un moteur et un mécanisme de compression entraîné par le moteur qui sont placés à l'intérieur d'une enveloppe hermétique. Le mécanisme de compression est formé de mécanismes de compression rotatifs (6A, 6B) comprenant : une pluralité de cylindres (17, 18) ; une plaque de séparation (21) qui forme une cloison entre la pluralité de cylindres (17, 18) ; des lames qui séparent les volumes intérieurs des cylindres (17, 18) en côtés admission et côtés décharge ; et des rotors (24, 25) qui tournent à l'intérieur des cylindres (17, 18). Lorsque ΦMo représente le diamètre de noyau du moteur, ΦDc représente le diamètre interne de chacun des cylindres (17, 18), Hc représente la largeur de chacun des cylindres (17, 18) et Hs représente la largeur de la plaque de séparation (21), la relation Hs/Hc ≤ 0,35 est satisfaite dans les conditions dans lesquelles ΦDc/ΦMo ≥ 0,49.
PCT/JP2014/056650 2013-03-29 2014-03-13 Compresseur rotatif multicylindre WO2014156679A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP14774791.9A EP2947321A4 (fr) 2013-03-29 2014-03-13 Compresseur rotatif multicylindre
CN201480008720.0A CN105008722A (zh) 2013-03-29 2014-03-13 多气缸旋转压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013073093A JP2014196714A (ja) 2013-03-29 2013-03-29 多気筒ロータリ圧縮機
JP2013-073093 2013-03-29

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WO2014156679A1 true WO2014156679A1 (fr) 2014-10-02

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JP (1) JP2014196714A (fr)
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CN105201845A (zh) * 2015-10-22 2015-12-30 广东美芝制冷设备有限公司 旋转式压缩机
WO2017138175A1 (fr) * 2016-02-12 2017-08-17 東芝キヤリア株式会社 Compresseur rotatif et dispositif à cycle de réfrigération

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CN105840508A (zh) * 2016-05-17 2016-08-10 广东美芝制冷设备有限公司 旋转式压缩机及具有其的冷冻循环装置
CN109958622B (zh) * 2017-12-25 2021-06-08 上海海立电器有限公司 一种滚动转子式压缩机
CN108788658A (zh) * 2018-06-08 2018-11-13 宁波甬微集团有限公司 一种多缸压缩机中隔板的制作方法
CN109083843A (zh) * 2018-07-22 2018-12-25 宁波甬微集团有限公司 一种多缸压缩机中隔板的制作方法
CN109113999A (zh) * 2018-09-06 2019-01-01 宁波甬微集团有限公司 一种多缸压缩机中隔板的制作方法

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CN105201845B (zh) * 2015-10-22 2017-11-07 广东美芝制冷设备有限公司 旋转式压缩机
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EP2947321A4 (fr) 2016-02-24

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