EP3364130A1 - Akkumulator mit mehreren rohren und verdichter - Google Patents

Akkumulator mit mehreren rohren und verdichter Download PDF

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Publication number
EP3364130A1
EP3364130A1 EP17744146.6A EP17744146A EP3364130A1 EP 3364130 A1 EP3364130 A1 EP 3364130A1 EP 17744146 A EP17744146 A EP 17744146A EP 3364130 A1 EP3364130 A1 EP 3364130A1
Authority
EP
European Patent Office
Prior art keywords
pipes
vessel
accumulator
compressor
bracket
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP17744146.6A
Other languages
English (en)
French (fr)
Other versions
EP3364130A4 (de
EP3364130B1 (de
Inventor
Shunsuke Yakushiji
Makoto Ogawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3364130A1 publication Critical patent/EP3364130A1/de
Publication of EP3364130A4 publication Critical patent/EP3364130A4/de
Application granted granted Critical
Publication of EP3364130B1 publication Critical patent/EP3364130B1/de
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Classifications

    • 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0033—Pulsation and noise damping means with encapsulations
    • F04B39/0038—Pulsation and noise damping means with encapsulations of inlet or outlet channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/804—Accumulators for refrigerant circuits
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type

Definitions

  • the present invention relates to an accumulator provided with a plurality of pipes, and to a compressor to which the plurality of pipes of the accumulator are connected.
  • a compressor which is provided with two rotary-type compression mechanisms and a motor, and which takes a gas refrigerant from an accumulator (gas-liquid separator) into a cylinder of each of the rotary-type compression mechanisms, is used in an air conditioner, a chiller, and the like.
  • the accumulator used in the twin rotary compressor is provided with a vessel that separates a refrigerant into gas and liquid phases, and two pipes that introduce the gas refrigerant inside the vessel into the compressor.
  • Patent Document 1 a stay, which fixes the two pipes to an inner wall of the vessel, is installed inside the vessel in an intermediate portion thereof with respect to the vertical direction.
  • Patent Document 1 JP 5531891 B
  • Vibrations are transmitted to an accumulator from a compressor via piping.
  • an excitation source such as torque ripples or a cogging torque of a motor and flow ripples of a refrigerant discharged from a compression mechanism
  • the piping vibrates inside a vessel of the accumulator.
  • the vibration amplitude is large in the vicinity of a free end (upper end) of the piping, which is disposed away from a fixed end disposed in a bottom portion of the vessel.
  • the entire accumulator including the vessel, vibrates at the same time.
  • the accumulator emits noise as a result of the vibrations.
  • Patent Document 1 In order to reduce the noise emitted from the accumulator, the vibrations of the piping excited by the compressor need to be suppressed. In order to achieve that, the piping on the free end side, at which the vibration amplitude is large, may be fixed to the vessel. In Patent Document 1 also, two pipes are fixed, inside the vessel, to an inner wall of the vessel on the free end side thereof by a stay.
  • An object of the present invention is to provide an accumulator capable of sufficiently reducing vibrations of the accumulator excited via piping, and a compressor provided with the accumulator.
  • An accumulator of the present invention includes: a vessel that separates a fluid into gas and liquid phases in an interior of the vessel; a plurality of pipes that extract the gas phase inside the vessel to the outside of the vessel; and a holding portion that holds together the plurality of pipes extending in parallel inside the vessel.
  • the holding portion is separated from the vessel, and holds together respective sections of the plurality of pipes inside the vessel.
  • the accumulator of the present invention is preferably provided with the holding portions in at least two different locations in the vertical direction.
  • the holding portions are preferably disposed in a range including a first height of 0.5 and the vicinity thereof, and in a range including a second height of 0.8 and the vicinity thereof.
  • the first height correspond to a position of a first node of a tertiary mode of vibrations of the pipes
  • the second height correspond to a position of a node of a secondary mode of the vibrations of the pipes and to a position of a second node of the tertiary mode.
  • a reference pipe which is the pipe including the reference lower end portion, is preferably provided with a straight portion passing through a bottom portion of the vessel and extending from the interior of the vessel to the outside of the vessel along the vertical direction, and a curved portion that is curved with respect to the straight portion, and the base end position is preferably an upper end of the curved portion of the reference pipe.
  • the holding portion preferably includes a plurality of retaining portions that each respectively retain one of the plurality of pipes, and a connecting portion that connects the plurality of retaining portions with each other.
  • the connecting portion preferably includes a spring portion.
  • a compressor of the present invention which includes the above-described accumulator and to which the pipes are connected, is provided with a compression mechanism that compresses a fluid taken in via the pipes; a motor that drives the compression mechanism; and a housing that houses the compression mechanism and the motor and supports the accumulator.
  • the compression mechanism is preferably a rotary compression mechanism that includes a cylinder and a piston rotor, the piston rotor being rotated, inside the cylinder, eccentrically with respect to an axial center of the cylinder.
  • each of the two compression mechanisms include the cylinder and the piston rotor.
  • the holding portion holding together the plurality of pipes of the accumulator, which vibrate inside the vessel of the accumulator as a result of being excited from the outside, the vibrations of the pipes are dampened due to deformation of the pipes and the holding portion, and also due to friction between the pipes and the holding portion.
  • the holding portion Since the holding portion is separated from the vessel of the accumulator, the vibrations of the pipes disposed inside the vessel are not directly input to the vessel via the holding portion.
  • the vessel is prevented from being excited by the vibrations of the pipes inside the vessel, and the entire accumulator, including the vessel, can be prevented from vibrating.
  • a compressor 10 of a first embodiment which is illustrated in FIG. 1 , is provided with a rotary-type compression mechanism 11, a motor 12 that drives the compression mechanism 11, a cylindrical housing 13 that houses the compression mechanism 11 and the motor 12, and an accumulator 20 (gas-liquid separator).
  • the compressor 10 takes in a low-pressure gas refrigerant present inside the accumulator 20 via pipes 21 and 22, and compresses the refrigerant using the compression mechanism 11 to which a rotational driving force output from the motor 12 is transmitted via a crank shaft 14.
  • the compressor 10 and the accumulator 20 configure an air conditioner, a refrigerator, and the like, and are connected to a refrigerant circuit (not illustrated) in which the refrigerant is circulated.
  • the compression mechanism 11 which is a so-called twin rotary-type compression mechanism, is provided with an upper compression mechanism 110, a lower compression mechanism 120, a separator plate 11A, and an upper bearing 11B and a lower bearing 11C that rotatably support the crank shaft 14.
  • the upper compression mechanism 110 is provided with an upper crank pin 111 that is offset with respect to an axial center of the crank shaft 14, an upper piston rotor 112, an upper cylinder 113, and an upper muffler 114.
  • the upper piston rotor 112 is fitted to an outer circumferential portion of the upper crank pin 111, and revolves inside the upper cylinder 113.
  • An intake port 113A into which the gas refrigerant is taken via the pipe 21 of the accumulator 20, is formed in the upper cylinder 113 so as to penetrate a side wall of the upper cylinder 113 in the radial direction.
  • the interior of the upper cylinder 113 and the interior of a lower cylinder 123 are partitioned by the separator plate 11A.
  • the refrigerant which has been taken into the upper cylinder 113 and which has been compressed in a space located further forward, in the rotational direction, than a blade (not illustrated) that is pressed against an outer circumferential portion of the upper piston rotor 112, is discharged into the housing 13 via a discharge port (not illustrated) formed in the upper bearing 11B and an opening (not illustrated) formed in the upper muffler 114.
  • the lower compression mechanism 120 is also provided with a lower crank pin 121, a lower piston rotor 122, the lower cylinder 123, and a lower muffler 124.
  • An intake port 123A into which the gas refrigerant is taken via the pipe 22 of the accumulator 20, is formed in the lower cylinder 123 so as to penetrate a side wall of the lower cylinder 123 in the radial direction.
  • the lower crank pin 121 is offset with respect to the axial center of the crank shaft 14 in a direction that causes the lower crank pin 121 to have an opposite phase (180 degrees) to that of the upper crank pin 111.
  • the refrigerant that has been taken into the lower cylinder 123 is compressed as a result of the rotation of the lower piston rotor 122 and is discharged into the housing 13 via a discharge port (not illustrated) formed in the lower bearing 11C and an opening (not illustrated) formed in the lower muffler 124.
  • the refrigerant which has been discharged into the housing 13 from the upper compression mechanism 110 and the lower compression mechanism 120, is discharged into the refrigerant circuit via a discharge pipe 131 provided in an upper portion of the housing 13.
  • the accumulator 20 is provided with a vessel 20A that separates the refrigerant into gas and liquid phases in the interior thereof, two pipes 21 and 22 that extract the gas refrigerant of the gas phase inside the vessel 20A to the outside of the vessel 20A and cause the compressor 10 to take in the gas refrigerant, and a bracket 30 (holding portion) that holds together the two pipes 21 and 22 inside the vessel 20A.
  • the vessel 20A is formed in a cylindrical shape and supported by a side wall 13A of the housing 13 of the compressor 10.
  • a strap 25 is wound and tightened around an outer circumferential portion of the vessel 20A, and is fixed to an accumulator bracket 26 provided on the side wall 13A. Via the accumulator bracket 26 and the strap 25, the vessel 20A is supported by the side wall 13A of the housing 13 in a cantilevered manner.
  • an intake pipe 20B is provided that takes the low-pressure refrigerant from the refrigerant circuit (not illustrated) into the vessel 20A.
  • the pipes 21 and 22 extend in parallel inside the vessel 20A.
  • the pipes 21 and 22 are separated from an inner wall 20W of the vessel 20A.
  • the pipe 21 is connected to the upper compression mechanism 110, and the pipe 22 is connected to the lower compression mechanism 120.
  • the pipe 21 is provided with a straight portion 21A that extends in the vertical direction (perpendicular direction) downwardly from a position separated by a predetermined distance from the upper end portion of the vessel 20A, and a curved portion 21B that is curved with respect to the straight portion 21A and extends toward the intake port 113A of the upper cylinder 113.
  • the straight portion 21A penetrates a bottom portion 23 of the vessel 20A from the interior of the vessel 20A, reaches the outside of the vessel 20A, and is formed contiguously to the curved portion 21B.
  • the straight portion 21A is fixed to the bottom portion 23 of the vessel 20A by causing a circumferential edge of a hole, through which the straight portion 21A passes, to be crimped.
  • the curved portion 21B is fixed to the side wall 13A of the housing 13 by a joint 133. A leading end portion of the curved portion 21B penetrates the side wall 13A and is inserted into the intake port 113A.
  • the pipes 21 and 22 can be formed of an appropriate copper-based or iron-based metallic material.
  • the pipe 22 is also provided with a straight portion 22A that extends along the vertical direction, and a curved portion 21B that is curved with respect to the straight portion 22A and extends toward the intake port 123A of the lower cylinder 123.
  • the straight portion 22A extends in parallel with the straight portion 21A of the pipe 21.
  • the curved portion 22B is provided below the curved portion 21B of the above-described pipe 21, and extends horizontally and in parallel with the curved portion 21B. A leading end portion of the curved portion 21B penetrates the side wall 13A and is inserted into the intake port 123A.
  • a bent section 22C of the pipe 22 is positioned further to the outer circumferential side than a bent section 21C of the pipe 21.
  • an upper end portion 21U of the straight portion 21A of the pipe 21 and an upper end portion 22U of the straight portion 22A of the pipe 22 are arranged side by side at the same height from the bottom portion 23.
  • a partition member 24 is provided that vertically partitions the interior of the vessel 20A.
  • the partition member 24 prevents the refrigerant, which flows into the vessel 20A from the intake pipe 20B, from directly entering into the pipes 21 and 22.
  • the refrigerant, which flows into the vessel 20A passes through an opening (not illustrated) formed in the partition member 24.
  • the refrigerant inside the vessel 20A is separated into the gas refrigerant of the gas phase and a liquid refrigerant of the liquid phase, on the basis of density differences in the refrigerant.
  • the gas refrigerant which is present in an upper part of the interior of the vessel 20A, flows into the pipes 21 and 22 via the upper end portions 21U and 22U, flows through each of the pipes 21 and 22, and is taken into the compression mechanisms 110 and 120.
  • vibrations are transmitted to the accumulator 20 from the compressor 10 via the pipes 21 and 22.
  • the pipes 21 and 22, which are excited by an excitation source, such as torque ripples or a cogging torque of the motor 12 and flow ripples of the refrigerant discharged from the compression mechanism 11, vibrate inside the vessel 20A.
  • FIG. 2A is a schematic view illustrating an example of a vibration analysis result of pipes 91 and 92 of a known accumulator.
  • FIG. 2A schematically illustrates an outer shape of the housing 13 of a rotary compressor.
  • the pipes 91 and 92, which are connected to the compressor, are each schematically illustrated by one line.
  • an axis line of the housing 13 of the compressor while the operation is stopped (when there are no vibrations) is illustrated by a long dashed short dashed line
  • the axis line of the housing 13 of the compressor 10 during the operation (when there are vibrations) is illustrated by a solid line.
  • respective axis lines of the pipes 91 and 92 while the operation is stopped (when there are no vibrations) are illustrated by long dashed short dashed lines, and the respective axis lines of the pipes 91 and 92 during the operation are illustrated by solid lines.
  • the compressor vibrates as a result of a magnetic vibrating force of the motor 12 or the flow ripples of the discharged refrigerant
  • the pipes 91 and 92 to which vibrations are transmitted from the compressor via the cylinder of the compression mechanism or the housing 13, vibrate even more than the compressor.
  • the vibration amplitude is large.
  • the bracket 30 is provided that holds together the pipe 21 and the pipe 22 inside the vessel 20A in a state of being separated from the vessel 20A.
  • the straight portions 21A and 22A of the pipes 21 and 22 that extend inside the vessel 20A can be held together by one or more of the brackets 30.
  • the bracket 30 is provided at one location in the length direction (vertical direction) of the straight portions 21A and 22A.
  • the bracket 30 is separated from the inner wall 20W of the vessel 20A, is not fixed to the vessel 20A, and holds together the straight portions 21A and 22A that extend inside the vessel 20A.
  • the bracket 30 is provided with a cylindrical retaining portion 31 that retains an outer circumferential portion of the straight portion 21A that is inserted thereinto, a cylindrical retaining portion 32 that retains an outer circumferential portion of the straight portion 22A that is inserted thereinto in the same manner as the straight portion 21A, and a planar connecting portion 33 that connects the retaining portion 31 and the retaining portion 32.
  • the bracket 30 is formed of an appropriate resin-based material or an appropriate metallic material, such that the retaining portion 31, the retaining portion 32, and the connecting portion 33 are integrally formed.
  • the bracket 30 preferably possesses moderate elasticity.
  • the retaining portion 31 is fixed to a predetermined section of the straight portion 21A in the vertical direction.
  • the retaining portion 32 is also fixed to a predetermined section of the straight portion 22A in the vertical direction.
  • the retaining portions 31 and 32 are positioned at the same height from the bottom portion 23 of the vessel 20A.
  • the connecting portion 33 extends between the retaining portion 31 and the retaining portion 32.
  • the connecting portion 33 is disposed along the vertical direction, and since the rigidity of the connecting portion 33 is greater in the vertical direction, a vibration damping effect, which is obtained as a result of deformation of the connecting portion 33, is greater when the vibrations are generated in the vertical direction.
  • the retaining portion 31 is preferably fixed, in a state of being in close contact with the outer circumferential portion of the straight portion 21A, as a result of the straight portion 21A being press-fitted into the retaining portion 31, for example.
  • an elastic member may be interposed between an inner circumferential portion of the retaining portion 31 and the outer circumferential portion of the straight portion 21A, and the inner circumferential portion of the retaining portion 31, the elastic member, and the outer circumferential portion of the straight portion 21A may be caused to be in close contact with each other.
  • bracket 30 illustrated in the present embodiment is merely an example, and as long as the bracket 30 holds together the pipes 21 and 22 inside the vessel 20A in a state of being separated from the vessel 20A, any appropriate configuration of the bracket 30 can be adopted.
  • ring members 34 which are illustrated by long dashed double-short dashed lines in FIG. 3A , can be provided on the respective outer circumferential portions of the straight portions 21A and 22A. Since the retaining portions 31 and 32 are supported by the ring members 34, the retaining portions 31 and 32 can be prevented from slipping down.
  • the straight portions 21A and 22A are relatively displaced in the length direction.
  • the straight portion 21A of the pipe 21 is displaced downward, and the straight portion 22A of the pipe 22 is displaced upward.
  • the straight portions 21A and 22A are held together by the bracket 30, as illustrated in FIG. 4B , the straight portions 21A and 22A and the bracket 30 are deformed as a result of the straight portions 21A and 22A respectively sliding inside the retaining portions 31 and 32.
  • the vibrations of the pipes 21 and 22 are dampened.
  • the bracket 30 is separated from the vessel 20A, unlike when the bracket 30 is in contact with the vessel 20A, the vibrations of the pipes 21 and 22 inside the vessel 20A are not directly input to the vessel 20A via the bracket 30. In other words, since the vessel 20A is prevented from being excited by the vibrations of pipes 21 and 22 inside the vessel 20A, the entire accumulator 20, including the vessel 20A, can be prevented from vibrating.
  • the bracket 30 since the bracket 30 is provided that holds together the pipes 21 and 22 in a state of being separated from the vessel 20A, the vibrations of the accumulator 20 can be reduced. As a result, a level of an acoustic pressure emitted from the accumulator 20 decreases, and noise emitted from the accumulator 20 can thus be suppressed.
  • a system that transmits vibrations from the compressor 10, which is an excitation source, to the accumulator 20 is fixed to the pipes 21 and 22 inside the vessel 20A, and the vibrations of the pipes 21 and 22 can be inhibited from being transmitted to the vessel 20A or the outside of the vessel 20A as much as possible.
  • respective sections of the pipes 21 and 22, in which a distance of a relative displacement, due to relative vibrations between the pipes 21 and 22, becomes large, are preferably held together by the bracket 30.
  • an elastic body such as rubber, may be provided so as to completely cover the outer circumferential portions of the pipes 21 and 22 that extend inside the vessel 20A.
  • the weight of the accumulator 20 increases, and further, a sufficient vibration damping effect may not be necessarily obtained.
  • the vibration damping can be efficiently achieved.
  • bracket 30 of the present embodiment a bracket illustrated in FIG. 3B or FIG. 3C can be used.
  • a bracket 35 illustrated in FIG. 3B is provided with retaining portions 351 and 352 that are each formed in a C-shape when viewed from the vertical direction, and the connecting portion 33 that connects the retaining portions 351 and 352.
  • the bracket 35 is formed by stamping a sheet metal material and bending both ends thereof into point-symmetrical C-shapes. Sections that are bent at both ends of the connecting portion 33 correspond to the retaining portions 351 and 352.
  • the retaining portions 351 and 352 are each formed in a C-shape and each provided with a gap Sp in a section thereof adjacent to the connecting portion 33. Thus, when the pipes 21 and 22 held by the retaining portions 351 and 352 vibrate, the retaining portions 351 and 352 can open and close.
  • bracket 35 illustrated in FIG. 3B is easily manufactured, and further, since the retaining portions 351 and 352 deform as a result of opening and closing, the vibration damping effect is high.
  • a bracket 36 illustrated in FIG. 3C is provided with a connecting portion 361 that is disposed along the horizontal direction, and the retaining portions 31 and 32 that are connected by the connecting portion 361.
  • the bracket 36 Since the rigidity of the connecting portion 361 is greater in the horizontal direction, the bracket 36 is effective in reducing the vibrations of the pipes 21 and 22 in the horizontal direction, as illustrated in FIG. 2B , for example. Further, as a result of the improved rigidity in the horizontal direction, an eigenfrequency can be adjusted from a view point of avoiding resonance.
  • Brackets 37 to 39 illustrated in FIGS. 5A to 5C are respectively the brackets 30, 35, and 36 illustrated in FIGS. 3A to 3C , in each of which a spring member is additionally provided.
  • a spring portion 101 which is provided in each of the bracket 37 illustrated in FIG. 5A and the bracket 38 illustrated in FIG. 5B , is formed by performing bending processing on the connecting portion 33 so as to have a bellows-shape.
  • a spring portion 102 which is provided in the bracket 39 illustrated in FIG. 5C , is also formed by performing the bending processing on the connecting portion 361 so as to have a bellows-shape. As a result of the spring portion 102 elastically deforming, the vibration damping effect by the bracket 39 is improved.
  • FIGS. 6 to 9 A second embodiment of the present invention will be described with reference to FIGS. 6 to 9 .
  • the accumulator 40 of the second embodiment is provided with brackets 41 and 42 that are disposed at two different locations in the length direction of the straight portions 21A and 22A of the pipes 21 and 22.
  • Each of the brackets 41 and 42 can be configured in the same manner as the bracket 30 ( FIG. 3A ) described in the first embodiment.
  • Each of the brackets 41 and 42 may also be configured in the same manner as the brackets 37 to 39 illustrated in FIGS. 3B, 3C , and FIGS. 5A to 5C .
  • the brackets 41 and 42 are disposed at predetermined heights.
  • bracket 41 is positioned at a height of approximately 0.5 (first height HI)
  • bracket 42 is positioned at a height of approximately 0.8 (second height H2).
  • the bracket 41 holds together a first section 211 of the pipe 21 and a first section 221 of the pipe 22.
  • the first section 211 and the first section 221 are positioned at the same height.
  • the bracket 42 holds together a second section 212 of the pipe 21 and a second section 222 of the pipe 22.
  • the second section 212 and the second section 222 are positioned at the same height.
  • a dimension of each of the brackets 41 and 42 in the vertical direction can be determined to be an appropriate dimension of 1 mm or greater in order to cause a holding force to act on the pipes 21 and 22.
  • the base end position P1 is an upper end of the curved portion 21B of the pipe 21 (reference pipe), the curved portion 21B having the reference lower end portion 21L that is located in a higher position, of the lower end portions 21L and 22L of the pipes 21 and 22.
  • this configuration conforms well to a vibration model of a beam ( FIG. 8 and FIG. 9 ), which will be described later.
  • the bracket 41 When the height from the base end position P1 to the leading end position P2 is "1", the bracket 41 is disposed over a range including the height H1 equivalent to 0.5 and the vicinity of the height H1.
  • the bracket 42 is disposed over a range including the height H2 equivalent to 0.8 and the vicinity of the height H2.
  • a center portion of the bracket 41 in a vertical direction D 1, in which the straight portion 21A extends is preferably positioned at the height H1 of approximately 0.5.
  • a center portion of the bracket 42 in the vertical direction D1 is preferably positioned at the height H2 of approximately 0.8.
  • brackets 41 and 42 are disposed at the predetermined heights.
  • FIGS. 7A to 7C illustrate a vibration analysis result of the pipes 91 and 92 of a conventional accumulator (provided with no bracket for the pipes) connected to the rotary compressor.
  • FIG. 7A illustrates a primary vibration mode component
  • FIG. 7B illustrates a secondary vibration mode component
  • FIG. 7C illustrates a tertiary vibration mode component.
  • the respective sections of the pipes 21 and 22, in which the distance of the relative displacement caused by the relative vibrations between the pipes 21 and 22 becomes large, are preferably held together by the bracket 30.
  • Each of the pipes 21 and 22 includes a fixed end 201, which is crimped to the bottom portion 23 ( FIG. 6 ) of the vessel 20A, and a free end 202.
  • FIGS. 8A to 8C respectively illustrate the primary, secondary, and tertiary vibration mode components.
  • the vibration amplitude gradually increases toward the free end 202, and as the vibration amplitude increases, a relative displacement between a section of the pipe 21 and a section of the pipe 22, which are positioned at the same height from the fixed end 201, increases.
  • an arrow illustrated in FIG. 8B indicates a direction in which a section of the node B of the pipe 22 is relatively displaced with respect to a section of the node B of the pipe 21.
  • arrows illustrated in FIG. 8C indicate directions in which respective sections of the pipe 22 corresponding to the nodes B1 and B2 are relatively displaced with respect to respective sections of the pipe 21 corresponding to the nodes B1 and B2.
  • the position of the node B of the secondary vibration mode and the positions of the nodes B1 and B2 of the tertiary vibration mode are calculated on the basis of a basic equation.
  • FIGS. 9A to 9C respectively illustrate the primary, secondary, and tertiary vibration mode components.
  • FIG. 9B illustrates an example of a value calculated using a vibration formula of a beam having a fixed end and a free end. As illustrated in FIG. 9B , when the length from the fixed end 201 to the free end 202 is "1", the node B of the secondary vibration mode is positioned at "0.774".
  • FIG. 9C illustrates examples of values calculated using the vibration equation of the beam having the fixed end and the free end.
  • the node B1 of the tertiary vibration mode is positioned at "0.500” and the node B2 of the tertiary vibration mode is positioned at "0.868".
  • the vibration amplitude becomes largest at the free end 202, namely, at the position of "1". Accordingly, it can be considered that the relative displacement of the pipes 21 and 22 becomes largest at this position.
  • the two locations at the height H1 of 0.5 and at the height H2 of 0.8 are selected as the locations at which the pipes 21 and 22 are held together.
  • the brackets 41 and 42 are preferably disposed at the heights H1 and H2, respectively.
  • the vibrations of the pipes 21 and 22 can be efficiently dampened.
  • the vibration damping effect described in the first embodiment can be obtained more sufficiently.
  • the accumulator 40 of the second embodiment may be provided with other brackets that hold together the pipes 21 and 22 inside the vessel 20A, in addition to the brackets 41 and 42.
  • the pipes 21 and 22 can be held together by one bracket 45 across a range including both the height H1 of 0.5 and the height H2 of 0.8.
  • the vibrations can be dampened more sufficiently.
  • a basic concept of the present invention is that two or more of the pipes are held together inside the vessel 20A by the bracket that is separated from the vessel 20A.
  • the position and the number of the bracket are not limited.
  • the pipe 21 and 22 can also be held together inside the vessel 20A by three brackets 46 to 48 that are positioned separately at three locations in the vertical direction so as to be separated from the vessel 20A.
  • the present invention is suitable for the accumulators 20 and 40 that are provided with the two pipes 21 and 22 corresponding to the two cylinders 113 and 123 of the twin rotary-type compression mechanism 11.
  • the present invention is not necessarily limited to this configuration.
  • the present invention can be applied to a rotary compressor provided with one cylinder and one piston rotor.
  • the accumulator of the present invention can also be applied to another compressor, such as a scroll compressor, other than the rotary compressor.
  • the accumulator of the present invention need not be supported by the housing 13 of the compressor. According to the vibration damping configuration of the accumulator of the present invention, vibrations transmitted from any of the excitation sources to the pipes 21 and 22 inside the vessel 20A can be dampened. As a result, vibrations of the accumulator can be reduced.
  • Shapes of the pipes 21 and 22 of the accumulator of the present invention can be determined as appropriate.
  • the pipes 21 and 22 need not be provided with the curved portions 21B and 22B.
  • a reference height that determines the respective sections of the pipes to be held can be determined as appropriate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP17744146.6A 2016-01-26 2017-01-23 Akkumulator mit mehreren rohren und verdichter Active EP3364130B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016012394A JP6645845B2 (ja) 2016-01-26 2016-01-26 複数の配管を有するアキュムレータおよび圧縮機
PCT/JP2017/002177 WO2017130916A1 (ja) 2016-01-26 2017-01-23 複数の配管を有するアキュムレータおよび圧縮機

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EP3364130A1 true EP3364130A1 (de) 2018-08-22
EP3364130A4 EP3364130A4 (de) 2018-11-21
EP3364130B1 EP3364130B1 (de) 2023-02-15

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JP (1) JP6645845B2 (de)
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Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP3567250A1 (de) * 2018-05-11 2019-11-13 Mitsubishi Heavy Industries Thermal Systems, Ltd. Verdichtersystem

Families Citing this family (5)

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JP7080092B2 (ja) * 2018-04-05 2022-06-03 三菱重工サーマルシステムズ株式会社 圧縮機システム
JP7295414B2 (ja) * 2019-07-24 2023-06-21 ダイキン工業株式会社 圧縮機ユニット
WO2022004597A1 (ja) * 2020-07-01 2022-01-06 ダイキン工業株式会社 熱源ユニットおよびスクロール圧縮機
JP7206506B2 (ja) * 2020-10-30 2023-01-18 ダイキン工業株式会社 回転式圧縮機
JP2023130738A (ja) 2022-03-08 2023-09-21 オムロン株式会社 シール貼付システム

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JPH02128061U (de) * 1989-03-30 1990-10-22
JPH0363475A (ja) * 1989-07-31 1991-03-19 Daikin Ind Ltd アキュムレータ
JP2911193B2 (ja) * 1990-08-21 1999-06-23 三洋電機株式会社 ２気筒回転式圧縮機用のアキュムレータ
JP3064545B2 (ja) * 1991-08-30 2000-07-12 松下電器産業株式会社 ２気筒回転式圧縮機
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KR100664295B1 (ko) * 2005-05-19 2007-01-04 엘지전자 주식회사 압축기용 어큐뮬레이터의 진동소음 저감 장치
CN2821494Y (zh) * 2005-07-12 2006-09-27 乐金电子(天津)电器有限公司 复式旋转式压缩机用储液罐
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CN103348203B (zh) * 2011-02-08 2015-12-09 松下电器产业株式会社 气液分离器及制冷循环装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3567250A1 (de) * 2018-05-11 2019-11-13 Mitsubishi Heavy Industries Thermal Systems, Ltd. Verdichtersystem

Also Published As

Publication number Publication date
CN108351135A (zh) 2018-07-31
WO2017130916A1 (ja) 2017-08-03
JP2017133725A (ja) 2017-08-03
EP3364130A4 (de) 2018-11-21
EP3364130B1 (de) 2023-02-15
JP6645845B2 (ja) 2020-02-14

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