AU2023282649B2

AU2023282649B2 - Compressor and method for designing the same

Info

Publication number: AU2023282649B2
Application number: AU2023282649A
Authority: AU
Inventors: Hirofumi SHIMAYA; Shohei TERASAKI
Original assignee: Mitsubishi Heavy Industries Thermal Systems Ltd
Current assignee: Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date: 2022-06-09
Filing date: 2023-05-26
Publication date: 2025-10-02
Anticipated expiration: 2043-05-26
Also published as: CN118318105A; WO2023238709A1; JP2023180460A; EP4417814A1; EP4417814A4; JP7467531B2; AU2023282649A1

Abstract

Provided is a compressor capable of reducing vibration even when a compressor body is reduced in size. The compressor comprises a compressor body (10) having a compression unit (6) that compresses a refrigerant in a cylindrical housing (2), and a cylindrical accumulator (12) connected to a refrigerant intake side of the compressor body, wherein the relationship 3≤(m1/D1)/(m2/(D2)≤7 is satisfied, where m1 is the mass of the compressor body (10), m2 is the mass of the accumulator (12), D1 is the outer diameter of the compressor body (10), and D2 is the outer diameter of the accumulator (12).

Description

COMPRESSOR AND METHOD FOR DESIGNING THE SAME 27 Aug 2025

Technical Field

[0001] 5 The present disclosure relates to a compressor and a method for designing the compressor.

Background Art 2023282649

[0002] The discussion of the background to the invention herein is intended to 10 facilitate an understanding of the invention. However, it should be appreciated that the discussion is not an acknowledgement or admission that any aspect of the discussion was part of the common general knowledge as at the priority date of the application.

[0002a] 15 A rotary compressor is known as one of compressors used in refrigeration devices, air-conditioning devices, and the like.

[0003] As described in Patent Document 1, propagation of vibration of a rotary compressor to an inlet tube of an accumulator is problematic. When a refrigerant 20 pipe is broken due to the vibration propagated to the inlet tube of the accumulator, a refrigerant inside the pipe may leak to the outside. In particular, when a flammable refrigerant (as an example of a flammability class, a mildly flammable refrigerant (A2L), a flammable refrigerant (A2), or a strongly flammable refrigerant (A3)) is used as the refrigerant, it is more necessary to 25 avoid leakage of the refrigerant. In addition, when the rotary compressor vibrates, mountability to a product can be deteriorated.

Citation List Patent Literature 30 [0004] Patent Document 1: JP 2011-185123 A

Summary of Invention Technical Problem

[0005] 35 In a related-art rotary compressor having a relatively large weight, the moment of inertia of a static system is large, and thus vibration caused by driving of a rotary compression unit (for example, rotation of a piston rotor), which is a 11 Sep 2025 rotating system, tends to be suppressed. However, due to miniaturization of the rotary compressor, the moment of inertia of the static system may decrease and a problem related to vibration may become apparent. 5 [0006] The present disclosure has been made in view of such circumstances, and it is desirable to provide a compressor capable of reducing vibration even when a compressor main body is miniaturized and a method for designing the 2023282649 compressor.

10 Solution to Problem

[0007] A compressor (1) according to a first form of the present disclosure is a compressor including a compressor main body (10) including, in a tubular housing (2), a compression unit (6) compressing a refrigerant, and a tubular 15 accumulator (12) coupled to a refrigerant suction portion of the compressor main body, in which 3 ≤ (m1/D1)/(m2/D2) ≤ 7, where m1 is a mass of the compressor main body, m2 is a mass of the accumulator, D1 is an outside diameter of the compressor main body, and D2 is an outside diameter of the accumulator, wherein a moment of inertia Js of the static system (total) is more than 0.006 20 [kg·m 2 ] and less than 0.011 [kg·m 2 ], wherein the moment of inertia Js of the static system (total): Js = Jc + Ja + m2 × Rg 2 [kg·m 2 ], a moment of inertia (compressor main body (10)): Jc = {(m1 - mr - m0) × D1 2 }/8 [kg·m 2 ], a moment of inertia (accumulator (12)): Ja = (m2 × D2 2 )/8 [kg·m 2 ] and wherein a distance between an axis of rotation (CL) of a rotor shaft body in the compressor main 25 body and a center axis (CL2) of an inlet tube in the accumulator through which the refrigerant is introduced: Rg [m], a mass of a refrigeration oil: m0 [kg], and a mass of a rotating system comprising the rotor shaft body, a rotor of an electric motor, and a piston rotor of the compression unit: mr [kg].

[0008] 30 A method for designing a compressor according to another form of the present disclosure is a method for designing a compressor, the compressor including a compressor main body including, in a tubular housing, a compression unit compressing a refrigerant, and a tubular accumulator coupled to a refrigerant suction portion of the compressor main body, in which 3 ≤ (m1/D1)/(m2/D2) ≤ 35 7, where m1 is a mass of the compressor main body, m2 is a mass of the accumulator, D1 is an outside diameter of the compressor main body, and D2 is an outside diameter of the accumulator, wherein a moment of inertia Js of the static system (total) is more than 0.006 [kg·m 2 ] and less than 0.011 [kg·m 2 ], 11 Sep 2025 wherein the moment of inertia Js of the static system (total): Js = Jc + Ja + m2 × Rg2 [kg·m 2 ], a moment of inertia (compressor main body (10)): Jc = {(m1 - mr - m0) × D1 2 }/8 [kg·m 2 ], a moment of inertia (accumulator (12)): Ja = (m2 × D2 2 )/8 5 [kg·m 2 ] and wherein a distance between an axis of rotation (CL) of a rotor shaft body in the compressor main body and a center axis (CL2) of an inlet tube in the accumulator through which the refrigerant is introduced: Rg [m], a mass of a refrigeration oil: m0 [kg], and a mass of a rotating system comprising the rotor 2023282649 shaft body, a rotor of an electric motor, and a piston rotor of the compression 10 unit: mr [kg].

Advantageous Effects of Invention

[0009] It is possible to reduce vibration even when a compressor is miniaturized.

Brief Description of Drawings 15 [0010] FIG. 1 is a vertical cross-sectional view illustrating a rotary compressor according to an embodiment of the present disclosure. FIG. 2 is a side view illustrating a state in which the rotary compressor of FIG. 1 is provided at an installation surface. 20 FIG. 3 is a graph showing a vibration reduction effect when the compressor of the present disclosure is miniaturized. FIG. 4A is a graph of a comparative example of FIG. 3 when the horizontal axis is D1/m2. FIG. 4B is a graph of a comparative example of FIG. 3 when the horizontal 25 axis is m1/m2.

Description of Embodiments

[0011] An embodiment according to the present disclosure will be described below with reference to the drawings. 30 As illustrated in FIG. 1, a rotary compressor (hereinafter simply referred to as a "compressor") 1 according to the present embodiment is a hermetically sealed electric rotary compressor used in, for example, an air conditioner or a refrigeration device. The compressor 1 includes a compressor main body 10 and an accumulator 12. The accumulator 12 is coupled to the compressor main body 35 10 via a suction tube 11.

[0012] 27 Aug 2025

The compressor main body 10 includes a housing 2 having a substantially cylindrical shape, a rotor shaft body 3, an electric motor 5, and a rotary compression unit 6. An axis of rotation CL of the rotor shaft body 3 coincides 5 with the center axis of the housing 2. The rotor shaft body 3 is disposed so as to extend in the vertical direction and rotates about the axis of rotation CL in the housing 2.

[0013] 2023282649

The housing 2 is hermetically sealed and extends in the vertical direction. 10 The housing 2 includes a cylindrical main body portion 21, and an upper lid portion 22 and a lower lid portion 23 that close upper and lower openings of the main body portion 21.

[0014] A plurality of leg portions 7 are fixed to a lower portion of the main body 15 portion 21. The leg portions 7 are disposed in the circumferential direction of the main body portion 21 at predetermined angular intervals. As illustrated in FIG. 2, each leg portion 7 is fixed to an installation surface FL via a vibration-proof rubber 8.

[0015] 20 An opening 24 is formed at a position facing the outside surface of a cylinder 60 in a lower portion of the side wall of the housing 2. In the cylinder 60, a suction port 25 that communicates to a predetermined position in the cylinder is formed at a position facing the opening 24.

[0016] 25 An oil sump for storing lubricating oil is formed at a bottom portion of the housing 2. The liquid level of the oil sump when the oil is initially sealed is located above the rotary compression unit 6. Thus, the rotary compression unit 6 is driven in the oil sump.

[0017] 30 The upper lid portion 22 is provided with a discharge tube 13 and a terminal block 30. The discharge tube 13 penetrates the upper lid portion 22 in the thickness direction and includes a lower portion disposed inside the housing 2 and an upper portion disposed outside the housing 2. The discharge tube 13 discharges a compressed refrigerant to the outside of the housing 2. The terminal 35 block 30 is provided with three power supply terminals 31 for supplying electric power to the electric motor 5. Three-phase electric power is supplied to the power supply terminals 31 from an inverter device (not illustrated).

[0018] 27 Aug 2025

The accumulator 12 is used to separate a refrigerant into gas and liquid before supplying the refrigerant to the compressor main body 10. The accumulator 12 has a substantially cylindrical shape and is fixed to the outside 5 surface of the housing 2 via a bracket 14. An inlet tube 15 for introducing a refrigerant guided from an evaporator (not illustrated) is provided at an upper portion of the accumulator 12. The suction tube 11 for causing the refrigerant inside the accumulator 12 to be sucked into the compressor main body 10 is 2023282649

coupled to a lower portion of the accumulator 12. The suction tube 11 is coupled 10 to the suction port 25 through the opening 24 of the housing 2. The accumulator 12 supplies the gas-phase refrigerant to the rotary compression unit 6 through the suction tube 11.

[0019] As the refrigerant, a flammable refrigerant, that is, a refrigerant in a 15 flammability class of a mildly flammable refrigerant (A2L), a flammable refrigerant (A2), or a strongly flammable refrigerant (A3) such as propane, is used.

[0020] The electric motor 5 is accommodated at a central portion of the housing 20 2 in the vertical direction. The electric motor 5 includes a rotor 51 and a stator 52. The rotor 51 is fixed to the outside surface of the rotor shaft body 3 and is disposed above the rotary compression unit 6. The stator 52 is disposed so as to surround the outside surface of the rotor 51 and is fixed to an inner surface 21a of the main body portion 21 of the housing 2. 25 Electric power is supplied to the stator 52 from each power supply terminal 31 through a wiring line 32. The electric motor 5 rotates the rotor shaft body 3 by electric power supplied from each power supply terminal 31.

[0021] The rotary compression unit 6 is disposed in a state of being vertically 30 interposed between an upper bearing 4A and a lower bearing 4B. The upper bearing 4A and the lower bearing 4B are each formed of a metal material and are fixed to the cylinder 60 constituting the rotary compression unit 6 with a bolt 61. The rotor shaft body 3 is supported by the upper bearing 4A and the lower bearing 4B in a rotatable manner about the axis of rotation CL. 35 [0022] The rotary compression unit 6 is disposed at a bottom portion in the housing 2 below the electric motor 5. The rotary compression unit 6 includes the cylinder 60, an eccentric shaft portion 62, and a piston rotor 63.

5a

[0023] 27 Aug 2025

A compression chamber 60A, a suction hole 60B, and a discharge hole (not illustrated) are formed in the cylinder 60. The compression chamber 60A is formed inside the cylinder 60. The piston rotor 63 is accommodated in the 5 compression chamber 60A.

[0024] The rotary compression unit 6 is fixed to the inner surface 21a of the main body portion 21 of the housing 2. Specifically, the upper bearing 4A sandwiching 2023282649

the cylinder 60 is fixed to the inner surface 21a of the main body portion 21 of 10 the housing 2. The upper bearing 4A is fixed by plug-welding at a plurality of positions in the circumferential direction of the housing 2. Note that instead of plug welding, shrink fitting, cold fitting, or the like may be performed.

[0025] The eccentric shaft portion 62 is provided at a lower end portion of the 15 rotor shaft body 3 and is provided inside the piston rotor 63 in a state of being offset in an orthogonal direction from the central axis of the rotor shaft body 3.

5a

Thepiston The pistonrotor rotor6363has hasa acylindrical cylindricalshape shape having having an outside an outside diameter diameter

smaller than smaller thanthe theinside insidediameter diameterof of thethe cylinder cylinder 60,60, is is disposed disposed inside inside the the cylinder 60, cylinder 60, and andisisfixed fixedininaa state state of of being beingmounted mounted at the at the outside outside periphery periphery of of the eccentric the eccentric shaft shaft portion portion62. 62.The Thepiston piston rotor rotor 63 63 eccentrically eccentrically rotates rotates about about

the axis the axis of of rotation rotation CL CLalong alongwith with thethe rotation rotation of of thethe rotor rotor shaft shaft body body 3. 3.

[0026]

[0026] Thesuction The suctionhole hole60B60B is is a hole a hole forfor guiding guiding the the refrigerant refrigerant to the to the inside inside of of the cylinder the cylinder 60 60and andisisformed formedin in a direction a direction orthogonal orthogonal to the to the axisaxis of rotation of rotation

CL. CL.

Thehigh-pressure The high-pressure refrigerant refrigerant discharged discharged fromfrom the discharge the discharge hole hole (not (not illustrated) formed illustrated) inthe formed in thecylinder cylinder6060isisguided guided into into a space a space formed formed between between a a dischargecover discharge cover6565andand thethe upper upper bearing bearing 4Athen 4A and and guided then guided into into the the internal internal

spaceof space of the the housing housing2.2.

[0027]

Theabove-described The above-described compressor compressor 1 operates 1 operates as follows. as follows.

A refrigerant A refrigerant guided guidedfrom from thethe evaporator evaporator (not(not illustrated) illustrated) is taken is taken intointo

the accumulator the accumulator1212 through through the the inlet inlet tube tube 15. 15. The The refrigerant refrigerant is separated is separated into into gas and gas andliquid liquidininthe theaccumulator accumulator12,12, andand the the gas-phase gas-phase refrigerant refrigerant is guided is guided to to the rotary the rotary compression compression unit unit 6 through 6 through the the suction suction tubetube 11.the 11. In In rotary the rotary

compression compression unit unit 6, 6, therefrigerant the refrigerant is is guided guided to to thethe compression compression chamber chamber 60A 60A throughthe through thesuction suctionhole hole60B. 60B. Then, Then, eccentric eccentric rotation rotation of piston of the the piston rotorrotor 63 63 gradually decreases gradually decreases the the volume volume of of the thecompression compression chamber 60Aand chamber 60A and compresses compresses the the refrigerant.TheThe refrigerant. compressed compressed refrigerant refrigerant passespasses through through the the spaceinside space insidethe thedischarge dischargecover cover 65 65 through through the discharge the discharge holeisand hole and is then then

guidedtotothe guided theinternal internalspace spaceofofthe thehousing housing2. 2. TheThe refrigerant refrigerant discharged discharged into into the internal the internal space spaceof of the the housing housing2 2isisguided guidedto to a condenser a condenser (not(not illustrated) illustrated)

throughthe through thedischarge discharge tube tube 13 13 provided provided at the at the upper upper portion portion ofhousing of the the housing 2. 2.

[0028]

[0028] Next, vibration Next, vibrationwhen whenthethe compressor compressor 1 operates 1 operates will will be be described. described.

Vibrationcaused Vibration causedbyby thethe operation operation of the of the compressor compressor 1 is generated 1 is generated from from a drive a unit of drive unit of aa rotating systemsuch rotating system suchasasthethepiston piston rotor rotor 63 63 andand propagated propagated

from the from the compressor mainbody compressor main body1010toto the the accumulator accumulator 12. 12.

[0029]

[0029] Thespecifications The specificationsused used forvibration for vibration calculation calculation areare as as follows. follows.

Massof Mass of the the compressor mainbody compressor main body10: 10:ml m1[kg]

[kg] Massof Mass of the the accumulator 12: m2 accumulator 12: [kg] m2 [kg]

Outside diameter Outside diameter of of the the compressor compressor main body 10: main body 10: D1 D1(see (see FIG. FIG. 2) 2) [m]

[m]

Outsidediameter Outside diameterof of the the accumulator accumulator 12:(see 12: D2 D2 FIG. (see 2) FIG.

[m]2) [m]

6

Distancebetween Distance betweenthethe axis axis of of rotation rotation CL CL and and a center a center axis axis CL2 CL2 of theof the inlet tube inlet tube 15: Rg(see 15: Rg (seeFIG. FIG.2)2)[m]

[m] Displacement Displacement amount amount of rotary of the the rotary compression compression unit 6:unit 6: V [cc/rev] V [cc/rev]

Mass Mass ofofthe therefrigeration refrigerationoil: oil:m0m0[kg]:

[kg]:

Massofofthe Mass therotating rotatingsystem: system:mr mr [kg]

[kg]

Here, the Here, the rotating rotatingsystem systemrefers referstotorotating rotatingmembers, members, thatthat is, is, thethe rotor rotor

shaft body shaft body3,3,the therotor rotor51, 51,and andthe thepiston pistonrotor rotor63. 63.Thus, Thus, thethe staticsystem static system refers refers

to aa configuration to otherthan configuration other thanthe therotating rotatingsystem, system, that that is,is,the thecompressor compressor mainmain

body1010and body andthetheaccumulator accumulator 12 exclusive 12 exclusive of theofrotating the rotating system. system.

[0030]

[0030] Thenumerical The numerical values values of of m1,m1, ml, m2, m2, D1D2and D1 and areD2 in are the in the following following ranges. ranges. 4 kg 4 kg ≤ kg m1 ml <≤666kg < ml kg kg 0.3 0.3 kg kg<≤ m2 0.3 kg m2 m2< ≤0.7 0.7kgkg 0.7 kg 80 80 mm 80 mm <≤ D1 mm D1 <≤95 D1 95 mm 95 mm mm

50 50 mm 50 mm <≤ D2 mm D2 <≤75 D2 75 mm 75 mm mm

[0031]

[0031] Themoment The moment of inertia of inertia of of thethe static static system system and and the moment the moment of inertia of inertia of of the rotating the rotating system systemare areasasfollows. follows. Static Static System System

Momentofofinertia Moment inertia (compressor (compressor main mainbody): body): 2 Jc === {(m1 Jc Jc {(m1 {(m1- --mrmr mr- -- m0) X × m0) m0) X D1 [kg·m 2 ] }/8 [kg:m²] D1²}/8

Moment Moment of of inertia inertia (accumulator): (accumulator): 2 2 Ja == (m2 Ja × D2 (m2 X )/8 [kgm2] D2²)/8 [kg·m

[kg:m²] ] Moment Moment of of inertia inertia (total): (total): 2 [kgm2]

Js Js = Js == Jc Jc + Jc JaJa++ +m2 ++Ja m2 X ×Rg² m2 X Rg [kg·m 2 ]

[kg:m²] Rg2

Rotating system Rotating system 2 Moment Moment Moment ofof of inertia:JrJr inertia: inertia: [kg·m

[kg:m²] Jr [kgm2] ]

[0032]

[0032] When When vibration vibration of of an an inlet inlet tube tube 15 15 of of an an accumulator accumulator 12 of 12 of a reference a reference

compressor compressor (related-artcompressor) (related-art compressor) at aattime a time of design of design is A is A [m],

[m], vibration vibration A' A′

[m] of the

[m] of the inlet inlet tube tube 15 15of of the the compressor compressor 1 of 1 of thethe present present embodiment embodiment in in comparison with comparison with thethe reference reference compressor compressor is simply is simply represented represented by the by the

following equations. following equations.

A′ A' = A' == αA aA [m]

[m] A [m]

α===(V/V') a (V/V′)XX× (V/V') (Jr′/Jr)XX×(Js'/Js) (Jr'/Jr) (Jr'/Jr) (Js′/Js) X×X(Rg/Rg') (Js'/Js) (Rg/Rg′) (Rg/Rg')

[0033]

[0033] Theterms The termsofofthe theabove above equation equation of aof α have have have the following thefollowing the following physical physical physical

meanings: meanings:

Excitationforce Excitation force(proportional (proportionaltotothethedisplacement displacement amount): amount): (V/V′) (V/V') times times - 1 (Jr'/Jr) times Rotationspeed Rotation speedvariation variation (proportional (proportional to Jr to Jr ¹): 1): ): (Jr′/Jr) times Angularspeed Angular speed of of thethe rotary rotary compression compression unit unit 6 (proportional 6 (proportional ¹):Js - 1 ): Js to to Js-1):

(Js′/Js) times (Js'/Js) times

Rotationaldirection Rotational directionacceleration accelerationof of theinlet the inlettube tube1515 (proportional (proportional to to Rg): (Rg/Rg') Rg): (Rg/Rg′)times times

[0034]

[0034] FIG.33shows FIG. shows a graph a graph obtained obtained by plotting by plotting results results of above of the the above calculations. calculations.

In the In the figure, figure, the the vertical vertical axis axis represents the moment represents the moment of of inertia inertia Js Js of of thethe

static system static (total), and system (total), the horizontal and the horizontalaxis axisrepresents represents(m1/D1)/(m2/D2). (m1/D1)/(m2/D2). A larger A larger moment moment of of inertia inertia Js Js of of thethe staticsystem static system on on the the vertical vertical axis axis

meanssmaller means smaller vibration. vibration.

[0035]

As can As can be be seen seen from FIG. 3, from FIG. 3, by by designing designing the the range range of of(m1/D1)/(m2/D2) (m1/D1)/(m2/D2)

to be to equal to be equal to or or more morethan than3 3andand equal equal to or to or less less than than 7, 7, thethe moment moment of inertia of inertia

Js of Js of the the static static system is smaller system is thanthat smaller than that of of aa related-art related-art machine machine (reference (reference

compressor)(the compressor) (themaximum maximum momentmoment of inertia of inertia Js static Js of the of the system static system is 0.011is 0.011 2 which

[kg·m

[kgm2],

[kg·m²],], which whichisis is inin in anan an allowable allowable allowable range range range ofaaof of a vibration vibration vibration reduction reduction reduction effect). effect). effect).In In In

addition, it addition, it is is possible possible to to obtain obtain the the moment moment of of inertiaJsJsofofthe inertia thestatic staticsystem system 2 is equal to equal to or or more morethan thana apredetermined predetermined value value (0.006 (0.006 [kg·m

[kgm2]),

[kg·m²]), ]), which which which is is allowableasasa avalue allowable valuefor forvibration vibrationreduction. reduction. Further, as Further, as can can be beseen seenfrom fromthethe figure, figure, by by using using thethe parameter parameter

(m1/D1)/(m2/D2), (m1/D1)/(m2/D2), the the compressor compressor 1 can 1becan be evaluated evaluated in distinction in distinction from thefrom the

related-art machine related-art (reference machine (reference compressor). compressor). ThisThis serves serves as anas an effective effective

indicator for indicator for evaluating evaluatingminiaturization miniaturizationof of thethe compressor compressor main main body body 10. 10.

[0036]

[0036] For example, For example,when when parameters parameters areassetinasrespective are set in respective comparative comparative

examplesdescribed examples described below, below, the the compressor compressor 1 cannot 1 cannot be distinguished be distinguished from thefrom the

related-art machine, related-art andminiaturization machine, and miniaturization and and vibration vibration reduction reduction cannot cannot be be evaluatedatat the evaluated thesame sametime. time.

[0037]

[0037] In FIG. In FIG. 4A, 4A,D1/m2, D1/m2, that that is,is, a value a value obtained obtained by dividing by dividing the outside the outside

diameter D1 diameter D1 of of the the compressor mainbody compressor main body1010bybythe the mass massm2 m2ofofthe the

accumulator1212 accumulator is is used used as as a parameter a parameter of the of the horizontal horizontal axis.axis. As be As can can be seen seen fromthe from thefigure, figure,plotted plottedpoints pointsofofthe thepresent presentembodiment embodiment are overlapped are overlapped with with values of values of the the related-art related-art machine machine (reference (reference compressor) compressor) onhorizontal on the the horizontal axis, axis, and they and theycannot cannotbebedistinguished distinguished from from eacheach other. other.

[0038]

[0038] In FIG. In FIG.4B, 4B,ml/m2, m1/m2, m1/m2, that that is,is, a value a value obtained obtained by dividing by dividing the mass the mass ml of m1 of the compressor the main body compressor main body1010bybythe the mass massm2 m2ofofthe the accumulator accumulator1212isis used used as as a parameter a parameter ofofthe thehorizontal horizontalaxis. axis.AsAs cancan be be seen seen fromfrom the figure, the figure, plotted plotted

points of points of the the present presentembodiment embodimentare are overlapped overlapped with values with values of the of the related-art related-art

machine(reference machine (reference compressor) compressor) onhorizontal on the the horizontal axis, axis, andcannot and they they cannot be be distinguishedfrom distinguished fromeach each other. other.

[0039]

[0039] As can As canbebeunderstood understood with with reference reference to FIGS. to FIGS. 3, 4A 3, 4A4B,and and by 4B, by

appropriatelyselecting appropriately selectinga aparameter parameteras as illustrated illustrated in in FIG. FIG. 3, 3, it it isispossible possibletoto evaluate the evaluate the compressor compressorin in distinction distinction from from the the related-art related-art machine machine (reference (reference

compressor). compressor).

[0040]

Theoperational The operationaleffects effectsofofthe thepresent present embodiment embodiment described described above above are are

as follows. as follows. Miniaturizationofofthe Miniaturization thecompressor compressormainmain body body 10 decreases 10 decreases the the mass. mass. Thus,the Thus, themoment moment of inertia of inertia of of thethe static static system system decreases decreases and vibration and vibration duringduring

operationtends operation tendstotoincrease. increase.OnOn thethe other other hand, hand, asresult as a a result of of studies studies conducted conducted

by the by the present presentinventors inventorsand and thethe like,itithas like, hasbeen been found found that that there there is is a range a range in in

whichvibration which vibrationcancan be be reduced reduced in terms in terms of relationship of the the relationship between between the the mass mass m1and ml andthe the outside outside diameter diameter D1 of the D1 of the compressor main body compressor main body10 10and andthe the mass mass m2and m2 andthe theoutside outside diameter diameter D2the D2 of of accumulator the accumulator 12. 12. That is, That is, even when even when the the compressor compressor main main body body 10 10 is miniaturized, is miniaturized, the the vibration vibration can vibrationcan be canbe reduced reduced be in in reduced inthe the range range the of of range <3(m1/D1)/(m2/D2) 3 of ≤3 (m1/D1)/(m2/D2) < 7. (m1/D1)/(m2/D2) ≤7.7.

[0041]

Even when Even whena amildly mildlyflammable flammablerefrigerant refrigerant (A2L), (A2L), aa flammable flammable refrigerant (A2), refrigerant (A2), or or aa strongly stronglyflammable flammable refrigerant refrigerant (A3)(A3) is used is used as as the the refrigerant, since refrigerant, the compressor since the compressor 1 with 1 with less less vibration vibration during during operation operation is is provided,itit is provided, is possible to reduce possible to reducethe thepossibility possibilitythat thatthe therefrigerant refrigerantleaks leaksdue duetoto

breakageofofa apipe breakage pipecoupled coupled to to thethe inlet inlet tube tube 15 15 as as much much as possible. as possible.

[0042]

[0042] A weight A weight adding adding member membermay may be be attached attached totothe theaccumulator accumulator1212SO sosoas asto to adjust the adjust themass mass m2 m2 of of the the accumulator accumulator 12. 12. The The weight weight adding adding member is mainly member is mainly used to used to increase increasethe themass massm2 m2 of the of the accumulator accumulator 12isand 12 and is irrelevant irrelevant to theto the

essential function essential functionofofthe theaccumulator accumulator12.12. ForFor example, example, rubber rubber (particularly, (particularly,

butyl rubber butyl rubberhaving havinga high a high specific specific weight) weight) is used. is used. WhenWhen rubberrubber is used, is used, the the rubberisis attached rubber attachedtotothe theoutside outsidesurface surfaceofofthetheaccumulator accumulator 12, 12, for for example. example.

[0043]

9

Thecompressor The compressorandand the the design design method method therefor therefor described described in the in the above- above - describedembodiment described embodiment canunderstood, can be be understood, for example, for example, as follows. as follows.

[0044]

[0044] A compressor A compressor(1)(1) according according to atofirst a first aspect aspect of of thethe present present disclosure disclosure is a is a

compressor compressor including including a compressor a compressor main main bodyincluding, body (10) (10) including, in a tubular in a tubular

housing(2), housing (2),aacompression compression unit unit (6)(6) compressing compressing a refrigerant, a refrigerant, and aand a tubular tubular

accumulator(12) accumulator (12) coupled coupled to atorefrigerant a refrigerant suction suction portion portion of compressor of the the compressor main body, main body, in in which which 33 < ≤(m1/D1)/(m2/D2) (m1/D1)/(m2/D2) < ≤7, (m1/D1)/(m2/D2) 7, 7,where where where m1 mlml is aisa is amass massmass ofthe ofof thethe compressor compressor main main body, body, m2a is m2 is a mass mass of theofaccumulator, the accumulator, D1outside D1 is an is an outside

diameterofofthe diameter thecompressor compressor main main body, body, and and D2 is D2 is an outside an outside diameter diameter of the of the accumulator. accumulator.

[0045]

[0045] Miniaturizationofofthe Miniaturization thecompressor compressormainmain body body decreases decreases the Thus, the mass. mass. Thus, the moment the moment of of inertia inertia ofof thestatic the staticsystem system decrease decrease and and vibration vibration during during

by the by the present presentinventors inventorsand and thethe like,itithas like, hasbeen beenfound found that that there there is is a range a range in in whichvibration which vibrationcancan be be reduced reduced in terms in terms of the of the relationship relationship between between the the mass mass and the and the outside outsidediameter diameterof of the the compressor compressor main main body body and theand theandmass mass the and the outside diameter outside diameterofofthe theaccumulator. accumulator. That That is, is, eveneven whenwhen the compressor the compressor main main

bodyisis miniaturized, body miniaturized,vibration vibration can can be be reduced reduced in the in the range range of 3 of < 3≤ (m1/D1)/(m2/D2) (m1/D1)/(m2/D2) (m1/D1)/(m2/D2) <7,≤ 7,where where 7,where m1 mlmlis isthe isthe the mass mass mass ofthe ofofthethe compressor compressor compressor main main main body, m2m2m2 body, body, is the is the mass of the mass of the accumulator, accumulator,D1 D1 is the is the outside outside diameter diameter of compressor of the the compressor mainbody, main body,and and D2 D2 is the is the outside outside diameter diameter of accumulator. of the the accumulator.

[0046]

A compressor A compressor according according to ato a second second aspect aspect ofpresent of the the present disclosure disclosure is is the compressor the compressor according according to the to the first first aspect, aspect, in in which which

4 kg 4 4 kg kg<≤ ml m1< ≤666kg, m1 kg, kg, 0.3 0.3 kg kg <≤ m2 0.3 kg m2< 0.7 m2 ≤0.70.7kg, kg, kg, 80 80 mm 80 mm <≤ D1 mm D1 <≤95 D1 95 mm, 95 mm, and mm, and

50 50 mm 50 mm <≤ D2 mm D2 <≤75 D2 75 mm. 75 mm. mm.

[0047]

[0047] When When the the masses masses and and the the outside outside diameters diameters are within are within the above - the above above-

describedranges, described ranges,a aminiaturized miniaturized compressor compressor can can be be achieved. achieved.

[0048]

A compressor A compressor according according to ato a third third aspect aspect of the of the present present disclosure disclosure is is the the compressor compressor according according to the to the first first aspect aspect or or thethe second second aspect, aspect, in which in which a mildly a mildly

flammable flammable refrigerant,a flammable refrigerant, a flammable refrigerant, refrigerant, or aor a strongly strongly flammable flammable

refrigerant is refrigerant is used as the used as the refrigerant. refrigerant.

10

[0049] 27 Aug 2025

Even when the mildly flammable refrigerant (A2L), the flammable refrigerant (A2), or the strongly flammable refrigerant (A3) is used, since the compressor with less vibration during operation is provided, it is possible to 5 reduce the possibility that the refrigerant leaks due to breakage of a pipe or the like.

[0050] A compressor according to a fourth aspect of the present disclosure is the 2023282649

compressor according to any of the first aspect to the third aspect, in which a 10 weight adding member adjusting the m2 is attached to the accumulator.

[0051] The above relationship for achieving vibration reduction may be satisfied by adjusting the mass m2 of the accumulator. The weight adding member is mainly used to increase the weight of the accumulator and is irrelevant to the 15 essential function of the accumulator. For example, rubber (specifically, butyl rubber having a large specific gravity) is used. When rubber is used, the rubber is attached to the outside surface of the accumulator, for example.

[0052] A method for designing a compressor according to a fifth aspect of the 20 present disclosure is a method for designing a compressor, the compressor including a compressor main body including, in a tubular housing, a compression unit compressing a refrigerant, and a tubular accumulator coupled to a refrigerant suction portion of the compressor main body, in which 3 ≤ (m1/D1)/(m2/D2) ≤ 7, where m1 is a mass of the compressor main body, m2 is a mass of the 25 accumulator, D1 is an outside diameter of the compressor main body, and D2 is an outside diameter of the accumulator.

[0053] Unless the context requires otherwise, where the terms “comprise”, “comprises”, “comprised” or “comprising” are used in this specification (including the claims) they 30 are to be interpreted as specifying the presence of the stated features, integers, steps or components, but not precluding the presence of one or more other features, integers, steps or components, or group thereof.

Reference Signs List

[0054] 35 1 Compressor (rotary compressor) 2 Housing 3 Rotor shaft body

4A Upper bearing 27 Aug 2025

4B Lower bearing 5 Electric motor 6 Rotary compression unit (compression unit) 5 7 Leg portion 8 Vibration-proof rubber 10 Compressor main body 11 Suction tube 2023282649

12 Accumulator 10 13 Discharge tube 14 Bracket 15 Inlet tube 21 Main body portion 21a Inner surface 15 22 Upper lid portion 23 Lower lid portion 24 Opening 25 Suction port 30 Terminal block 20 31 Power supply terminal 32 Wiring line 51 Rotor 52 Stator 60 Cylinder 25 60A Compression chamber 60B Suction hole 61 Bolt 62 Eccentric shaft portion 63 Piston rotor 30 65 Discharge cover CL Axis of rotation CL2 Center axis of the inlet tube FL Installation surface

Claims

The claims defining the invention are as follows: 11 Sep 2025

[Claim 1] A compressor comprising: 5 a compressor main body including, in a tubular housing, a compression unit configured to compress a refrigerant; and a tubular accumulator coupled to a refrigerant suction portion of the compressor main body, wherein 2023282649

3 ≤ (m1/D1)/(m2/D2) ≤ 7, where m1 is a mass of the compressor main 10 body, m2 is a mass of the accumulator, D1 is an outside diameter of the compressor main body, and D2 is an outside diameter of the accumulator, wherein a moment of inertia Js of the static system (total) is more than 0.006 [kg·m 2 ] and less than 0.011 [kg·m 2 ], wherein the moment of inertia Js of the static system (total): 15 Js = Jc + Ja + m2 × Rg 2 [kg·m 2 ], a moment of inertia (compressor main body (10)): Jc = {(m1 - mr - m0) × D1 2 }/8 [kg·m 2 ], a moment of inertia (accumulator (12)): Ja = (m2 × D2 2 )/8 [kg·m 2 ] and 20 wherein a distance between an axis of rotation (CL) of a rotor shaft body in the compressor main body and a center axis (CL2) of an inlet tube in the accumulator through which the refrigerant is introduced: Rg [m], a mass of a refrigeration oil: m0 [kg], and a mass of a rotating system comprising the rotor shaft body, a rotor of 25 an electric motor, and a piston rotor of the compression unit: mr [kg] .
[Claim 2] The compressor according to claim 1, wherein 4 kg ≤ m1 ≤ 6 kg, 30 0.3 kg ≤ m2 ≤ 0.7 kg, 80 mm ≤ D1 ≤ 95 mm, and 50 mm ≤ D2 ≤ 75 mm.
[Claim 3] 35 The compressor according to claim 1 or 2, wherein a mildly flammable refrigerant, a flammable refrigerant, or a strongly flammable refrigerant is used as the refrigerant.
[Claim 4] 11 Sep 2025

The compressor according to claim 1 or 2, wherein a weight adding member configured to adjust the m2 is attached to the accumulator. 5
[Claim 5] A method for designing a compressor, the compressor including a compressor main body including, in a tubular housing, a compression unit 2023282649

configured to compress a refrigerant, and a tubular accumulator coupled to a 10 refrigerant suction portion of the compressor main body, wherein 3 ≤ (m1/D1)/(m2/D2) ≤ 7, where m1 is a mass of the compressor main body, m2 is a mass of the accumulator, D1 is an outside diameter of the compressor main body, and D2 is an outside diameter of the accumulator, wherein a moment of inertia Js of the static system (total) is more than 15 0.006 [kg·m 2 ] and less than 0.011 [kg·m 2 ], wherein the moment of inertia Js of the static system (total): Js = Jc + Ja + m2 × Rg 2 [kg·m 2 ], a moment of inertia (compressor main body (10)): Jc = {(m1 - mr - m0) × D1 2 }/8 [kg·m 2 ], 20 a moment of inertia (accumulator (12)): Ja = (m2 × D2 2 )/8 [kg·m 2 ] and wherein a distance between an axis of rotation (CL) of a rotor shaft body in the compressor main body and a center axis (CL2) of an inlet tube in the accumulator through which the refrigerant is introduced: Rg [m], 25 a mass of a refrigeration oil: m0 [kg], and a mass of a rotating system comprising the rotor shaft body, a rotor of an electric motor, and a piston rotor of the compression unit: mr [kg] .