WO2018142505A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
- Publication number
- WO2018142505A1 WO2018142505A1 PCT/JP2017/003598 JP2017003598W WO2018142505A1 WO 2018142505 A1 WO2018142505 A1 WO 2018142505A1 JP 2017003598 W JP2017003598 W JP 2017003598W WO 2018142505 A1 WO2018142505 A1 WO 2018142505A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- compressor
- r1234yf
- discharge pipe
- compression mechanism
- Prior art date
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 189
- 230000006835 compression Effects 0.000 claims abstract description 61
- 238000007906 compression Methods 0.000 claims abstract description 61
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 30
- 239000001294 propane Substances 0.000 claims description 15
- 238000005096 rolling process Methods 0.000 description 29
- 238000005192 partition Methods 0.000 description 8
- 238000005057 refrigeration Methods 0.000 description 6
- 239000002826 coolant Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 229930195733 hydrocarbon Natural products 0.000 description 5
- 150000002430 hydrocarbons Chemical class 0.000 description 5
- 239000003921 oil Substances 0.000 description 5
- 230000000704 physical effect Effects 0.000 description 4
- 239000004215 Carbon black (E152) Substances 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 238000010792 warming Methods 0.000 description 3
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- -1 R1234yf Substances 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Images
Classifications
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- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
-
- 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
- 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
-
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/263—HFO1234YF
-
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/266—Propane
-
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/268—R32
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
Definitions
- the present invention relates to a compressor that compresses and discharges a refrigerant.
- Hydrofluoroolefin or hydrocarbon has a smaller GWP (global warming potential) than R410A or R32 conventionally used as a refrigerant, and is a promising refrigerant as a refrigerant used for countermeasures against global warming.
- GWP global warming potential
- a compressor using an operating refrigerant mainly composed of hydrofluoroolefin has been proposed (see, for example, Patent Document 1).
- hydrofluoroolefin or hydrocarbon is a promising refrigerant as a refrigerant used for countermeasures against global warming because GWP is smaller than that of conventional refrigerant R410 or R32.
- hydrofluoroolefins or hydrocarbons have a lower refrigeration capacity per volume than conventional refrigerants such as R32. Therefore, when hydrofluoroolefin or hydrocarbon is used as the working refrigerant, it is necessary to increase the flow rate of the working refrigerant in order to achieve a refrigerating capacity equivalent to that of the conventional refrigerant. The pressure loss generated when discharging from the nozzle increases.
- the present invention has been made to solve the above-described problems, and provides a compressor that suppresses a pressure loss that occurs when an operating refrigerant is discharged from a sealed container of a compressor.
- a compressor according to the present invention includes a hermetically sealed container, a compression mechanism unit that is accommodated in the hermetic container and compresses the refrigerant flowing into the hermetic container, and the refrigerant that is attached to the hermetic container and compressed by the compression mechanism unit.
- the relationship of 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 is satisfied.
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism section is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇
- V st [m 3 ] of the compression mechanism section is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇
- FIG. 3 is a sectional view taken along line AA in FIG. 2.
- FIG. 3 is a sectional view taken along line BB in FIG.
- FIG. 3 illustrates a pipe friction coefficient ⁇ of a discharge pipe when the dimensions of the discharge pipe and the stroke volume capacity of the compressor according to Embodiment 1 of the present invention are changed.
- the discharge pressure loss (DELTA) P of the compressor which concerns on Embodiment 1 of this invention is illustrated with the contour line.
- coolant of the compressor which concerns on Embodiment 2 of this invention is illustrated with the contour line. It is a figure which shows the mixing ratio of R32 refrigerant
- FIG. 1 is an internal configuration diagram showing the inside of the compressor according to Embodiment 1 of the present invention.
- a twin rotary type compressor 100 having two cylindrical cylinders in the compression mechanism section will be described as an example of the compressor.
- the compressor 100 is a hermetic electric compressor including a hermetic container 1, and an electric motor unit 2 and a compression mechanism unit 3 inside the hermetic container 1.
- the sealed container 1 includes a bottomed cylindrical lower sealed container 13 and an upper sealed container 12 that closes an upper opening of the lower sealed container 13.
- the connecting portion between the lower sealed container 13 and the upper sealed container 12 is fixed by welding, and the sealed state is maintained.
- a suction pipe 15 is connected to the lower sealed container 13, and a suction muffler 14 is attached to the suction pipe 15.
- the suction pipe 15 is a connection pipe for sending the gas refrigerant flowing in via the suction muffler 14 into the compression mechanism unit 3.
- the lower airtight container 13 may be provided with an oil supply mechanism in which lubricating oil supplied to the compression mechanism unit 3 is stored.
- the discharge pipe 4 is connected to the upper sealed container 12 on the axis extension line of the rotating shaft 31.
- the discharge pipe 4 is a pipe that is attached to the sealed container 1 and discharges the refrigerant compressed by the compression mechanism unit 3 to the outside of the sealed container 1.
- the inner diameter of the discharge pipe is always formed at a constant size.
- the discharge pipe 4 should just be provided in the airtight container 1, and does not necessarily need to be arrange
- the upper sealed container 12 is further provided with an airtight terminal 16 for electrical connection with the electric motor unit 2 in the sealed container 1 and a rod 17 to which a cover for protecting the airtight terminal 16 is attached.
- the electric motor unit 2 includes a stator 21 fixed to the lower hermetic container 13 and a rotor 22 provided rotatably on the inner peripheral side of the stator 21.
- a rotation shaft 31 is fixed to the center of the rotor 22.
- the stator 21 is fixed to the lower sealed container 13 of the sealed container 1 by various fixing methods such as shrink fitting and welding.
- the stator 21 is electrically connected to the hermetic terminal 16 by a lead wire 18.
- FIG. 2 is a longitudinal sectional view showing a compression mechanism portion of the compressor according to Embodiment 1 of the present invention.
- 3 is a cross-sectional view taken along line AA in FIG. 4 is a cross-sectional view taken along line BB in FIG.
- the configuration of the compression mechanism unit 3 will be described with reference to FIGS. 3 and 4, the illustration of the eccentric shaft portion 31c and the eccentric shaft portion 31d is omitted.
- the compression mechanism section 3 is accommodated in the sealed container 1 and compresses the refrigerant flowing into the sealed container 1.
- the compression mechanism unit 3 is a twin rotary type compression mechanism having two cylindrical cylinders.
- the compression mechanism unit 3 is disposed below the electric motor unit 2 in the sealed container 1 and fixed to the lower sealed container 13. Yes.
- the compression mechanism unit 3 includes a rotary shaft 31, a main bearing 32, a sub bearing 33, a first cylindrical cylinder 34a, a first rolling piston 35a, a second cylindrical cylinder 34b, and a second rolling piston. 35b and a partition plate 36.
- the rotary shaft 31 is connected to the rotor 22 of the electric motor unit 2 and transmits the rotational force of the electric motor unit 2 to the compression mechanism unit 3.
- the rotating shaft 31 includes a main shaft portion 31a fixed to the rotor 22 of the electric motor unit 2, and a sub shaft portion 31b provided on the opposite side of the main shaft portion 31a in the axial direction.
- the rotating shaft 31 is provided between the main shaft portion 31a and the subshaft portion 31b, and an eccentric shaft portion 31c inserted into the first rolling piston 35a and an eccentric shaft inserted into the second rolling piston 35b. Part 31d.
- the eccentric shaft portion 31c and the eccentric shaft portion 31d are arranged with a predetermined phase difference (for example, 180 °).
- the rotary shaft 31 has a main shaft portion 31 a that is rotatably supported by a main bearing 32 and a sub shaft portion 31 b that is rotatably supported by a sub bearing 33.
- the main bearing 32 is a closing member that closes one end face (on the motor part 2 side) of both ends of the first cylindrical cylinder 34a.
- the main bearing 32 and the first cylindrical cylinder 34a are molded and assembled as separate articles.
- the sub-bearing 33 is a closing member that closes one end face of the both ends of the second cylindrical cylinder 34b (on the opposite side to the electric motor part 2 in the axial direction).
- the sub bearing 33 and the second cylindrical cylinder 34b are molded and assembled as separate articles.
- the first cylindrical cylinder 34a is formed in a substantially cylindrical shape, and both end surfaces of the substantially cylindrical shape are closed by the main bearing 32 and the partition plate 36 in the axial direction of the rotary shaft 31, as shown in FIG.
- a chamber 40a sealed in the internal space of the first cylindrical cylinder 34a is formed.
- the chamber 40a accommodates an eccentric shaft portion 31c of the rotating shaft 31 shown in FIG. 2 and a first rolling piston 35a that is rotatably fitted to the eccentric shaft portion 31c.
- the first cylindrical cylinder 34a is formed with a first vane sliding groove 41a in the radial direction.
- a first vane 37a is provided in the first vane sliding groove 41a.
- the first cylindrical cylinder 34a of the compression mechanism unit 3 is provided with a first suction port 42a for sucking the refrigerant.
- the first suction port 42a is formed in the radial direction of the first cylindrical cylinder 34a.
- the first suction port 42a is connected to the suction pipe 15 described above and serves as a path for guiding the refrigerant into the chamber 40a of the first cylindrical cylinder 34a.
- the first rolling piston 35a is mounted on the eccentric shaft portion 31c of the rotary shaft 31 shown in FIG. 2, and the first vane 37a that rotates eccentrically in the chamber 40a as the rotary shaft 31 rotates and is pressed against the outer periphery.
- a compression chamber is configured to perform a suction operation and a compression operation.
- the first vane 37a is pressed against the first rolling piston 35a by an urging means (not shown).
- the first vane 37a reciprocates in the first vane sliding groove 41a while contacting the first rolling piston 35a.
- the first vane 37a reciprocates in the first vane sliding groove 41a, and a space formed between the first cylindrical cylinder 34a and the first rolling piston 35a is defined as a suction chamber and a compression chamber. It is divided into.
- the second cylindrical cylinder 34b is formed in a substantially cylindrical shape, and both end surfaces of the substantially cylindrical shape are closed by the auxiliary bearing 33 and the partition plate 36 in the axial direction of the rotary shaft 31, as shown in FIG.
- a sealed chamber 40b is formed in the internal space of the second cylindrical cylinder 34b.
- the chamber 40b accommodates an eccentric shaft portion 31d of the rotary shaft 31 shown in FIG. 2 and a second rolling piston 35b that is rotatably fitted to the eccentric shaft portion 31d.
- the second cylindrical cylinder 34b has a second vane sliding groove 41b formed in the radial direction.
- a second vane 37b is provided in the second vane sliding groove 41b.
- the second cylindrical cylinder 34b of the compression mechanism unit 3 is provided with a second suction port 42b for sucking the refrigerant.
- the second suction port 42b is formed in the radial direction of the second cylindrical cylinder 34b.
- the second suction port 42b is connected to the suction pipe 15 described above and serves as a path for guiding the refrigerant into the chamber 40b of the second cylindrical cylinder 34b.
- the second rolling piston 35b is attached to the eccentric shaft portion 31d of the rotary shaft 31 shown in FIG. 2, and the second vane 37b is rotated eccentrically in the chamber 40b by the rotation of the rotary shaft 31 and pressed against the outer periphery.
- a compression chamber is configured to perform a suction operation and a compression operation.
- the second vane 37 b is pressed against the second rolling piston 35 b by urging means (not shown).
- the second vane 37b reciprocates in the second vane sliding groove 41b while being in contact with the second rolling piston 35b as the eccentric shaft portion 31d rotates.
- the second vane 37b reciprocates in the second vane sliding groove 41b, and a space formed between the second cylindrical cylinder 34b and the second rolling piston 35b is defined as a suction chamber and a compression chamber. It is divided into.
- the partition plate 36 is provided between the first cylindrical cylinder 34a and the second cylindrical cylinder 34b.
- the partition plate 36 has one end face (opposite to the electric motor section 2) of one end of the first cylindrical cylinder 34a and one end (electric motor section) of the second cylindrical cylinder 34b.
- 2 is a closing member that closes the end surface on the second side.
- the operating refrigerant of the compressor 100 uses R1234yf, which is a kind of hydrofluoroolefin, as a single refrigerant.
- Table 1 shows a comparison of physical property values of R1234yf and R32 used as a conventional refrigerant.
- the physical property value of each refrigerant is REFPROP ver. Of National Institute of Standards and Technology (NIST). Using 9.0, it was determined under the measurement conditions of a condensation temperature of 52 ° C., an evaporation temperature of 5 ° C., a subcool of 5 deg, and a superheat of 10 deg.
- R1234yf alone has a volume ratio capacity of about half that of R32 alone. Therefore, when R1234yf is used as a single refrigerant in a compressor, in order to achieve a refrigerating capacity equivalent to a compressor using R32 as a single refrigerant, the flow rate of refrigerant flowing through the compressor is compressed using R32 as a single refrigerant. It is necessary to make it about twice the machine. As a result, in the compressor using R1234yf as a single refrigerant, the flow rate of the refrigerant increases, so that the pressure loss generated when the operating refrigerant is discharged from the closed container of the compressor increases. Therefore, when R1234yf is used as a single refrigerant, it is necessary to suppress the pressure loss that occurs when the operating refrigerant is discharged from the closed container of the compressor.
- the rotating shaft 31 rotates when the electric motor unit 2 is driven.
- the eccentric shaft portion 31c and the eccentric shaft portion 31d of the rotating shaft 31 rotate.
- the first rolling piston 35a attached to the eccentric shaft portion 31c rotates eccentrically in the first cylindrical cylinder 34a
- the second rolling piston 35b attached to the eccentric shaft portion 31d serves as the second cylindrical cylinder. It rotates eccentrically within 34b.
- the first rolling piston 35a covering the eccentric shaft portion 31c of the rotating shaft 31 is eccentrically rotated in the first cylindrical cylinder 34a by the rotation of the rotating shaft 31, and is delimited by the first vane 37a.
- the compression chamber capacity in the first cylindrical cylinder 34a changes continuously. That is, as the first rolling piston 35a rotates, the volume of the space surrounded by the first cylindrical cylinder 34a, the first rolling piston 35a, and the first vane 37a is reduced in the chamber 40a. The refrigerant is compressed.
- the second rolling piston 35b covering the eccentric shaft portion 31d of the rotating shaft 31 is eccentrically rotated in the second cylindrical cylinder 34b by the rotation of the rotating shaft 31, thereby being separated by the second vane 37b.
- the compression chamber capacity in the second cylindrical cylinder 34b is continuously changed. That is, the rotation of the second rolling piston 35b reduces the volume of the space surrounded by the second cylindrical cylinder 34b, the second rolling piston 35b, and the second vane 37b in the chamber 40b.
- the refrigerant is compressed.
- the compression chamber is provided with a discharge valve (not shown) that is released when the pressure exceeds a predetermined pressure, and high-pressure refrigerant gas is discharged from the chamber 40a and the chamber 40b into the sealed container 1 when the pressure exceeds the predetermined pressure.
- the compressed refrigerant gas passes through the clearance of the electric motor unit 2 and is discharged from the discharge pipe 4 into the refrigerant circuit outside the compressor 100.
- Lubricating oil is stored in the lower part of the hermetic container 1, and the oil is supplied to each part by an oil supply mechanism (not shown) of the rotating shaft 31 to keep the compression mechanism part 3 lubricated.
- the compressor 100 according to Embodiment 1 of the present invention is a twin rotary type compressor and has two cylinders. Therefore, the compressor 100 sets a stroke volume for each cylinder.
- the stroke volume V1 [m 3 ] is a refrigerant constituted by the first cylindrical cylinder 34a, the main bearing 32, the partition plate 36, the first rolling piston 35a, and the first vane 37a. It is the volume of the space to be excluded.
- the stroke volume V2 [m 3 ] excludes the refrigerant composed of the second cylindrical cylinder 34b, the auxiliary bearing 33, the partition plate 36, the second rolling piston 35b, and the second vane 37b. It is the volume of the space to be.
- the compressor 100 uses a twin rotary type compressor, a single rotary type compressor may be used.
- the stroke volume is the volume of the space formed by the cylindrical cylinder, the main bearing, the auxiliary bearing, the rolling piston, and the vane.
- the stroke volume used in the present invention is intended for the stroke volume in any one cylinder, and does not represent the total stroke volume of a plurality of cylinders.
- the stroke volume V st [m 3 ] is used as a general term for the above stroke volume.
- the stroke volume V st [m 3 ] is the amount of refrigerant discharged from any one cylinder when the rotation shaft 31 makes one rotation.
- the stroke volume described above and the discharge pipe 4 have the following relationship.
- In-pipe friction loss (hereinafter referred to as discharge pressure loss) ⁇ P in the discharge pipe 4 is derived from the Darcy-Weissbach equation of the following equation (1).
- ⁇ P is the discharge pressure loss [Pa]
- ⁇ is the pipe friction coefficient
- l is the length [m] of the discharge pipe 4
- d is the diameter [m] of the discharge pipe 4
- ⁇ is the refrigerant density [kg / m 3 ]
- U represents the refrigerant flow rate [m / s].
- coolant flow velocity U [m / s] of Formula (1) can be represented by following formula (2).
- r represents the compressor rotation speed [rps]
- V st represents the stroke volume [m 3 ]
- d represents the diameter of the discharge pipe [m].
- ⁇ represents the viscosity [Pa ⁇ s] of the refrigerant.
- the pipe friction coefficient ⁇ is calculated from the repeated calculation of the Prandtl-Karman equation of the following equation (4). In the iterative calculation, the true pipe friction coefficient ⁇ is obtained by changing the pipe friction coefficient ⁇ on both sides little by little.
- the refrigerant density ⁇ [kg / m 3 ], the compressor rotation speed r [rps], and the refrigerant viscosity ⁇ [Pa ⁇ s] are also determined.
- the conditions in Table 2 are used as general cooling setting conditions.
- FIG. 5 illustrates the pipe friction coefficient ⁇ of the discharge pipe when the dimensions of the discharge pipe and the stroke volume capacity of the compressor according to Embodiment 1 of the present invention are changed.
- the dimension of the inner diameter d [m] of the discharge pipe 4 of the compressor is 4 ⁇ 10 ⁇ 3 [m] ⁇ d ⁇ 20 ⁇ 10 ⁇ 3 [m] and the stroke volume V st [m 3 ] is
- the tube friction coefficient ⁇ of the discharge tube 4 is obtained when the capacity is 5 ⁇ 10 ⁇ 6 [m 3 ] ⁇ V st ⁇ 130 ⁇ 10 ⁇ 6 [m 3 ].
- FIG. 5 shows a calculation result obtained by obtaining the pipe friction coefficient ⁇ .
- the Reynolds number Re is the inner diameter d [m] of the discharge pipe 4.
- the pipe friction coefficient ⁇ can be approximated by the inner diameter d [m] of the discharge pipe 4 and the stroke volume V st [m 3 ].
- a pipe friction coefficient ⁇ approximated by the inner diameter d [m] of the discharge pipe 4 and the stroke volume V st [m 3 ] is expressed by Expression (5).
- the relationship between the inner diameter d [m] of the discharge pipe 4 and the stroke volume V st [m 3 ] of the compression mechanism unit 3 is such that the discharge pressure loss ⁇ P does not rise sharply, V st ⁇ 9 ⁇ It is desirable to be configured to satisfy the relationship of (d-4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the stroke volume V st [m 3 ] of the compression mechanism unit 3 is 5 ⁇ 10 ⁇ 6 ⁇ V It is set within the range of st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the stroke volume V st [m 3 ] of the compressor using R32 as the refrigerant is generally set in the range of 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 55 ⁇ 10 ⁇ 6 .
- the refrigerant of R1234yf alone is the R32 single refrigerant.
- the refrigerant flow rate is 1.96 times that of the refrigerant.
- the refrigerant of R1234yf alone is used for the stroke volume V st [m 3 ] of the compressor using R32 whose capacity is generally set in the range of 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 55 ⁇ 10 ⁇ 6.
- the compressor to be used needs to set the capacity of the stroke volume V st [m 3 ] to 1.96 times. Therefore, when the single refrigerant of R1234yf is used as the working refrigerant, the stroke volume V st [m 3 ] of the compression mechanism unit 3 is within the range of 9.8 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 108 ⁇ 10 ⁇ 6 .
- the dimension of the inner diameter d [m] of the discharge pipe 4 of the compressor is set in the range of 0 ⁇ d ⁇ 20 ⁇ 10 ⁇ 3 .
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism section is 5 ⁇ 10 ⁇ . 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 is satisfied so that a hydrofluoroolefin refrigerant having a large refrigerant flow rate is used. It is possible to suppress a sudden increase in the discharge pressure loss ⁇ P of the compressor.
- the GWP of the refrigerant can be lowered, and the compressor efficiency of the compressor can be improved by suppressing the discharge pressure loss ⁇ P of the compressor from rising sharply.
- the stroke volume V st [m 3 ] of the compression mechanism section is 9.8 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 108 ⁇ 10 ⁇ 6
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 -3 ) ⁇ 10 -3 + 1 ⁇ 10 -5 satisfying the relationship, the discharge pressure loss ⁇ P of the compressor using the single refrigerant of R1234yf having a large refrigerant flow rate increases sharply. Can be suppressed.
- Embodiment 2 the operation refrigerant of the compressor 100 has been described using R1234yf, which is one type of hydrofluoroolefin, as a single refrigerant.
- R1234yf which is one type of hydrofluoroolefin
- FIG. 1 the operation refrigerant of the compressor 100 has been described using R1234yf, which is one type of hydrofluoroolefin, as a single refrigerant.
- R1234yf which is one type of hydrofluoroolefin
- the operating refrigerant is not limited to a single refrigerant of R1234yf, and other hydrofluoroolefins may be used as the operating refrigerant, or hydrocarbons such as propane may be used.
- the operating refrigerant may be a mixed refrigerant of two kinds of hydrofluoroolefins, or a mixed refrigerant of two or more kinds of refrigerants including a hydrofluoroolefin and a refrigerant other than hydrofluoroolefin (for example, R32). There may be.
- the GWP of the mixed refrigerant is desirably less than 500, and more desirably less than 100.
- Table 3 shows a comparison of physical property values of the refrigerant composition used in the compressor 100.
- the physical property value of each refrigerant is REFPROP ver. Of National Institute of Standards and Technology (NIST). Using 9.0, it was determined under the measurement conditions of a condensation temperature of 52 ° C., an evaporation temperature of 5 ° C., a subcool of 5 deg, and a superheat of 10 deg.
- the value of the discharge pressure loss ⁇ P changes (rises) due to the difference between the refrigerant density ⁇ and the refrigerant viscosity ⁇ , but V st > 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ ) as in the compressor 100 of the first embodiment.
- the compressor 100 has a relationship between the inner diameter d [m] of the discharge pipe 4 and the stroke volume V st [m 3 ] of the compression mechanism unit 3 such that the discharge pressure loss ⁇ P is It is desirable to be configured to satisfy the relationship of V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 that does not rise steeply.
- the stroke volume V st [m 3 ] of the compression mechanism unit 3 is 5 ⁇ 10 ⁇ 6 ⁇ V It is set within the range of st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the stroke volume V st [m 3 ] of the compressor using R32 as the refrigerant is generally set in the range of 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 55 ⁇ 10 ⁇ 6 .
- the propane simple refrigerant is an R32 simple refrigerant.
- the flow rate of the refrigerant is 1.68 times.
- a propane simple substance refrigerant is used for the stroke volume V st [m 3 ] of the compressor using R32 whose capacity is generally set in the range of 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 55 ⁇ 10 ⁇ 6.
- the compressor needs to set the capacity of the stroke volume V st [m 3 ] to 1.68 times. Therefore, when the propane simple refrigerant is used as the working refrigerant, the stroke volume V st [m 3 ] of the compression mechanism unit 3 is within the range of 8.4 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 92 ⁇ 10 ⁇ 6. Must be set.
- the dimension of the inner diameter d [m] of the discharge pipe 4 of the compressor is set in the range of 0 ⁇ d ⁇ 20 ⁇ 10 ⁇ 3 .
- the stroke volume V st [m 3 ] of the compression mechanism section is 8.4 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 92 ⁇ 10. -6
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 so that the discharge pressure loss ⁇ P of the compressor using propane with a large refrigerant flow rate increases sharply. Can be suppressed.
- the GWP of the refrigerant can be lowered by using a single propane refrigerant, and the compressor efficiency of the compressor can be improved by suppressing a sudden increase in the discharge pressure loss ⁇ P of the compressor. .
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism unit 3 is such that the discharge pressure loss ⁇ P does not rise steeply 5 ⁇ 10 ⁇ 6 ⁇ It is desirable to be configured to satisfy the relationship of V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the refrigerant flow rate required for the compressor changes.
- the stroke volume V st [m 3] is set in the range of 9.8 ⁇ 10 -6 [m 3] ⁇ V st ⁇ 86.8 ⁇ 10 -6 [m 3] .
- the stroke volume V st [m 3 ] with respect to the ratio of each refrigerant to the mass of the entire operating refrigerant is set within any one of the conditions (1) to (5) in Table 4 below. .
- the stroke volume V st [m 3 ] of the compression mechanism section is The range shown in Table 4 is set, and the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism section is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d -4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 so that the discharge pressure loss ⁇ P of the compressor using propane with a large refrigerant flow rate increases sharply. Can be suppressed. As a result, it is possible to reduce the GWP of the refrigerant by using the R1234yf refrigerant, and it is possible to improve the compressor efficiency of the compressor by suppressing the discharge pressure loss ⁇ P of the compressor from rising sharply.
- FIG. 8 is a diagram illustrating a mixing ratio of the R32 refrigerant, the R1234yf refrigerant, and the R1123 refrigerant. Furthermore, the present inventor also uses three types of mixed refrigerants including R32, R1234yf, and R1123 shown in Table 3 as the operating refrigerant, as in the compressor 100 of the first embodiment, V st > 9 ⁇ ( It was found that the discharge pressure loss ⁇ P increased sharply at d-4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism unit 3 is such that the discharge pressure loss ⁇ P does not rise steeply 5 ⁇ 10 ⁇ 6 ⁇ It is desirable to be configured to satisfy the relationship of V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 .
- the refrigerant flow rate required for the compressor changes.
- the stroke volume V st [ m 3 ] is set within the range shown in Table 5, and the relationship between the inner diameter d [m] of the discharge pipe and the stroke volume V st [m 3 ] of the compression mechanism is 5 ⁇ 10 ⁇ 6 ⁇ V st ⁇ 9 ⁇ (d ⁇ 4 ⁇ 10 ⁇ 3 ) ⁇ 10 ⁇ 3 + 1 ⁇ 10 ⁇ 5 to satisfy the relationship, compression using three mixed refrigerants including R32, R1234yf, and R1123 with a large refrigerant flow rate A sharp rise in the discharge pressure loss ⁇ P of the machine can be suppressed.
- FIG. FIG. 9 is a schematic view of a discharge pipe used in the compressor according to Embodiment 3 of the present invention. Parts having the same configuration as those of the compressors of FIGS. 1 to 8 are denoted by the same reference numerals and description thereof is omitted.
- the discharge pipe 4 used in the compressor 100 of the first embodiment is always formed with a constant inner diameter, but the discharge pipe 4A used in the compressor 100 according to the third embodiment of the present invention is The inner diameter r2 of the inlet portion 51 is formed to be larger than the inner diameter r1 of the path portion 50.
- the discharge pipe 4A is formed so that the inner diameter r2 of the inlet portion 51 is larger than the inner diameter r1 of the path portion 50.
- the pressure loss due to the rapid contraction of the refrigerant at the inlet of the discharge pipe 4A can be proposed.
- FIG. FIG. 10 is a schematic plan view of a compressor according to Embodiment 4 of the present invention.
- FIG. 11 is a schematic side view of the upper part of the sealed container. Parts having the same configuration as those of the compressors of FIGS. 1 to 9 are denoted by the same reference numerals and description thereof is omitted.
- the discharge pipe 4 used for the compressor 100 of Embodiment 1 is formed in a cylindrical shape
- the discharge pipe 4B used for the compressor 100 according to Embodiment 4 of the present invention has an upper end portion and a lower end portion. Are formed in different shapes.
- the discharge pipe 4 ⁇ / b> B is welded and connected to the sealed container 1 at the connection portion 1 b of the upper sealed container 12. As shown in FIGS.
- the first wall portion 43 a at the end connected to the sealed container 1 is formed in an oval or elliptical cross-sectional shape.
- the discharge pipe 4B has a second wall 43b at the other end formed in a circular cross-sectional shape. Further, the discharge pipe 4B is formed such that the cross-sectional area S1 of the discharge pipe 4B formed by the first wall 43a is larger than the cross-sectional area S2 of the discharge pipe 4B formed by the second wall 43b.
- the discharge pipe 4B is formed such that the first wall portion 43a at the end connected to the sealed container 1 has an oval or elliptical cross-sectional shape.
- the discharge pipe 4B has a second wall 43b at the other end formed in a circular cross-sectional shape.
- the internal diameter d [m] of the discharge pipe 4B can be formed large.
- the discharge pipe 4B is formed such that the cross-sectional area S1 of the discharge pipe 4B formed by the first wall 43a is larger than the cross-sectional area S2 of the discharge pipe 4B formed by the second wall 43b.
- the compressor 100 responds to an increase in the refrigerant flow rate and an increase in pressure loss when a new refrigerant (HFO refrigerant or HC refrigerant) having a small specific refrigeration capacity per volume is employed as the operating refrigerant, and the sealed container 1 The yield strength can be secured.
- HFO refrigerant or HC refrigerant HFO refrigerant or HC refrigerant
- the discharge pipe 4B does not have to have a non-circular (for example, oval shape or oval shape) cross section of the entire discharge pipe, and only the end portion on the side connected to the sealed container 1 has an oval shape or an oval shape. What is necessary is just to form in non-circular shapes, such as a shape.
- the embodiment of the present invention is not limited to the above-described Embodiments 1 to 4, and various modifications can be added.
- the compressor 100 according to the embodiment of the present invention is a twin rotary type compressor having two cylindrical cylinders in the compression mechanism unit 3, but may be a single rotary type compressor.
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Abstract
Description
図1は、本発明の実施の形態1に係る圧縮機の内部を示す内部構成図である。以下の説明において、圧縮機として、圧縮機構部に2つの円筒シリンダを有するツインロータリー式の圧縮機100を例に説明する。図1に示すように、圧縮機100は、密閉容器1と、密閉容器1の内部に、電動機部2と、圧縮機構部3とを備えた、密閉型の電動圧縮機である。
実施の形態1では、圧縮機100の動作冷媒は、ハイドロフルオロオレフィンの1種であるR1234yfを単体冷媒として用いることを説明した。本発明の実施の形態2に係る圧縮機では、圧縮機100に用いる他の動作冷媒について説明する。なお、図1~図6の圧縮機と同一の構成を有する部位には同一の符号を付してその説明を省略する。
図9は、本発明の実施の形態3に係る圧縮機に用いられる吐出管の概略図である。なお、図1~図8の圧縮機と同一の構成を有する部位には同一の符号を付してその説明を省略する。実施の形態1の圧縮機100に用いられる吐出管4は、内径が常に一定の大きさに形成されているが、本発明の実施の形態3に係る圧縮機100に用いられる吐出管4Aは、経路部50の内径r1より、入口部51の内径r2が大きくなるように形成されている。
図10は、本発明の実施の形態4に係る圧縮機の平面概略図である。図11は、密閉容器上部の側面概略図である。なお、図1~図9の圧縮機と同一の構成を有する部位には同一の符号を付してその説明を省略する。実施の形態1の圧縮機100に用いられる吐出管4は、円筒形状に形成されているが、本発明の実施の形態4に係る圧縮機100に用いられる吐出管4Bは、上端部と下端部が異なる形状に形成されているものである。吐出管4Bは、上部密閉容器12の接続部1bにおいて密閉容器1と溶接されて接続されている。図10及び図11に示すとおり、吐出管4Bは、密閉容器1と接続している側の端部の第1壁部43aが長円形または楕円形の断面形状に形成されている。また、吐出管4Bは、他端の第2壁部43bが円形の断面形状に形成されている。さらに、吐出管4Bは、第1壁部43aが形成する吐出管4Bの断面積S1が、第2壁部43bが形成する吐出管4Bの断面積S2よりも大きくなるように形成されている。
Claims (10)
- 密閉容器と、
前記密閉容器に収容され、前記密閉容器内に流入する冷媒を圧縮する圧縮機構部と、
前記密閉容器に取り付けられ、前記圧縮機構部によって圧縮された冷媒を前記密閉容器の外部に吐出するための吐出管と、
を備え、
前記吐出管の内径d[m]と、前記圧縮機構部のストロークボリュームVst[m3]との関係が、
5・10-6<Vst<9・(d-4・10-3)・10-3+1・10-5
の関係を満足する圧縮機。 - R1234yfの単体冷媒を動作冷媒とし、
前記圧縮機構部のストロークボリュームVst[m3]が、
9.8・10-6<Vst<108・10-6
の範囲内に設定されている請求項1に記載の圧縮機。 - プロパンの単体冷媒を動作冷媒とし、
前記圧縮機構部のストロークボリュームVst[m3]が、
8.4・10-6<Vst<92・10-6
の範囲内に設定されている請求項1に記載の圧縮機。 - R32とR1234yfとを含む2種の混合冷媒を動作冷媒とし、
前記圧縮機構部のストロークボリュームVst[m3]が、下記の条件(1)~(5)のいずれか1つの範囲内に設定されている請求項1に記載の圧縮機。
(1)R32冷媒及びR1234yf冷媒が、R32:R1234yf=1:99~20:80の割合[wt%]で含まれている場合に、
9.8・10-6<Vst<97.4・10-6
(2)R32冷媒及びR1234yf冷媒が、R32:R1234yf=21:79~40:60の割合[wt%]で含まれている場合に、
8.9・10-6<Vst<86.8・10-6
(3)R32冷媒及びR1234yf冷媒が、R32:R1234yf=41:59~60:40の割合[wt%]で含まれている場合に、
7.9・10-6<Vst<76.2・10-6
(4)R32冷媒及びR1234yf冷媒が、R32:R1234yf=61:39~80:20の割合[wt%]で含まれている場合に、
6.9・10-6<Vst<65.6・10-6
(5)R32冷媒及びR1234yf冷媒が、R32:R1234yf=81:19~99:1の割合[wt%]で含まれている場合に、
6.0・10-6<Vst<55.5・10-6 - R32とR1234yfとR1123とを含む3種の混合冷媒を動作冷媒とし、
R32冷媒と、R1234yf冷媒と、R1123冷媒とが、R32:R1234yf:R1123=50~70:20~40:1~20の割合[wt%]で含まれている場合に、
前記圧縮機構部のストロークボリュームVst[m3]が、
6.2・10-6<Vst<60.6・10-6
の範囲内に設定されている請求項1に記載の圧縮機。 - 前記吐出管の経路部の内径r1の寸法が、前記吐出管の経路部の入口部の内径r2よりも大きくなるように形成されている請求項1~5のいずれか1項に記載の圧縮機。
- 前記吐出管は、前記密閉容器と接続している側の端部の第1壁部が長円形または楕円形の断面形状に形成されており、他端の第2壁部が円形の断面形状に形成されている請求項1~5のいずれか1項に記載の圧縮機。
- 前記第1壁部が形成する前記吐出管の断面積S1が、前記第2壁部が形成する前記吐出管の断面積S2よりも大きくなるように形成されている請求項7に記載の圧縮機。
- 動作冷媒としてR32を含み、GWPが500未満である動作冷媒を用いた請求項1~8のいずれか1項に記載の圧縮機。
- GWPが100未満である動作冷媒を用いた請求項1~9のいずれか1項に記載の圧縮機。
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