WO2017119075A1 - Compresseur à vis et dispositif à cycle de réfrigération - Google Patents

Compresseur à vis et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2017119075A1
WO2017119075A1 PCT/JP2016/050211 JP2016050211W WO2017119075A1 WO 2017119075 A1 WO2017119075 A1 WO 2017119075A1 JP 2016050211 W JP2016050211 W JP 2016050211W WO 2017119075 A1 WO2017119075 A1 WO 2017119075A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant flow
refrigerant
flow path
compression mechanism
motor
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PCT/JP2016/050211
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English (en)
Japanese (ja)
Inventor
伊藤　健
下地　美保子
英彰 永田
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/050211 priority Critical patent/WO2017119075A1/fr
Publication of WO2017119075A1 publication Critical patent/WO2017119075A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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

Definitions

  • the present invention relates to a screw compressor and a refrigeration cycle apparatus, and more particularly to cooling of a motor that drives a screw rotor.
  • a screw compressor including a casing in which a refrigerant circulates, a screw rotor that is accommodated in the casing and compresses the refrigerant, and a motor that rotationally drives the screw rotor.
  • the motor can be arranged on either the low pressure side or the high pressure side.
  • the generated motor can be cooled with a low-temperature and low-pressure gaseous refrigerant, so that the motor is often arranged on the low-pressure side.
  • a gap portion between the outer peripheral surface of the stator of the motor and the inner peripheral surface of the casing has an equal angular interval over the entire periphery.
  • a plurality of refrigerant flow paths are provided so as to have equal cross-sectional areas. The refrigerant passing through the plurality of refrigerant flow paths cools the motor, so that an increase in the coil temperature of the motor is suppressed and the motor is prevented from being burned (for example, see Patent Document 1).
  • a refrigerant suction passage through which refrigerant gas flows from the motor chamber to the compression mechanism is formed uniformly around the entire circumference between the centering guide and the main shaft (for example, see Patent Document 2).
  • Another single screw compressor is called a twin gate rotor system in which two gate rotors are arranged for one screw rotor (see, for example, Patent Document 3).
  • a double-sided operation is performed in which the same compression operation is performed on each half circumferential surface of the front and back of the screw rotor in a full load operation.
  • the compression operation on the half circumferential surface on one side is invalidated, and the one side operation is performed in which the compression operation is performed only on the half circumferential surface on one side. That is, in the one-side operation, an operation is performed in which the refrigerant gas is sucked only from the half circumferential surface of the screw rotor and the suction volume is reduced.
  • Another single screw compressor is called a mono gate rotor system in which one gate rotor is arranged for one screw rotor for common parts (see, for example, Patent Document 4).
  • the monogate rotor system constitutes a compressor with a small capacity.
  • the range of the screw rotor into which the refrigerant gas is sucked is generally determined by the rotation angle range from the start of compression of one groove formed in the screw rotor to the completion of discharge.
  • a plurality of refrigerant flow paths for passing the suction gas provided in the partition walls of the motor chamber and the compression mechanism section are arranged from the coil end of the motor in accordance with the full load operation of the twin gate rotor system.
  • the cross-sectional area in a cross-sectional view perpendicular to the axial direction of the rotating shaft is provided with an equal size around the rotating shaft of the screw rotor so that the flow resistance to the suction portion of the compression mechanism is substantially equal.
  • Japanese Patent No. 3684071 Japanese Patent No. 3622587 Japanese Patent Publication No. 1-35197 Japanese Patent No. 5178612
  • the suction gas is likely to flow from the refrigerant flow path on the screw rotor side performing the compression operation among the plurality of refrigerant flow paths provided around the rotation axis of the screw rotor. Further, the suction gas hardly flows in from the refrigerant flow path on the screw rotor side that is not performing compression operation among the plurality of refrigerant flow paths. For this reason, the refrigerant
  • the amount of refrigerant flowing in the refrigerant flow path between the outer peripheral surface of the stator of the motor and the inner peripheral surface of the casing decreases.
  • the temperature of the coil end of the stator on the screw rotor side where the compression operation is not performed around the rotation axis of the screw rotor tends to be high.
  • the cooling capacity by the refrigerant gas is lowered and the temperature of the coil end of the stator is likely to be high.
  • the present invention is for solving the above-described problems, and the cooling of the motor is made uniform, the local temperature rise of the motor is suppressed, and the operating range when the rotational speed is increased or decreased by the inverter drive is expanded.
  • An object of the present invention is to provide a screw compressor and a refrigeration cycle apparatus.
  • a screw compressor includes a casing in which a refrigerant circulates, a screw rotor that is housed in the casing, rotates around a rotating shaft, and compresses the refrigerant in a screw groove formed on an outer peripheral surface.
  • a compression mechanism composed of a gate rotor that meshes with the screw groove of the screw rotor, and a motor that is provided on the low-pressure side in the axial direction of the rotary shaft of the screw rotor, and that rotates the screw rotor.
  • a low-pressure refrigerant sucked from a suction port of a casing passes through a motor chamber that houses the motor and is compressed by the compression mechanism, and is around the rotation shaft of the screw rotor.
  • a refrigerant flow path for allowing the refrigerant to flow in a direction along the axial direction of the rotation shaft is provided between the motor chamber and the compression mechanism.
  • the provided refrigerant flow path includes a near refrigerant flow path that is closer to the compression mechanism, and a far refrigerant flow path that is farther from the compression mechanism than the near refrigerant flow path, and the rotation axis of the vicinity refrigerant flow path
  • a cross-sectional area in a cross-sectional view orthogonal to the axial direction is smaller than the cross-sectional area of the far refrigerant channel.
  • the refrigeration cycle apparatus includes the above screw compressor.
  • the cross-sectional area in a cross-sectional view perpendicular to the axial direction of the rotation axis of the near refrigerant flow path among the plurality of refrigerant flow paths is more small.
  • the amount of refrigerant flowing on the side closer to the compression mechanism around the rotating shaft of the screw rotor decreases, while the amount of refrigerant flowing on the side far from the compression mechanism increases. Therefore, the cooling of the motor is made uniform, insufficient cooling of the motor is suppressed, the local temperature rise of the motor is suppressed, and the operating range when the number of rotations by the inverter drive is increased or decreased can be expanded.
  • FIG. 1 It is a figure which shows schematic structure of the screw compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the AA line cross section of FIG. 1 of the screw compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the AA sectional view of FIG. 1 of the screw compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing which shows the AA line cross section of FIG. 1 of the screw compressor which concerns on Embodiment 3 of this invention. It is a refrigerant circuit figure which shows the refrigerating-cycle apparatus to which the screw compressor which concerns on Embodiment 4 of this invention is applied.
  • FIG. 1 is a diagram showing a schematic configuration of a screw compressor 100 according to Embodiment 1 of the present invention.
  • a monogate rotor type single screw compressor will be described as an example of the screw compressor 100.
  • the screw compressor 100 is used in a refrigeration cycle apparatus that is assumed to be operated in a wide range of compression ratios, such as an air conditioner, a refrigeration apparatus, and a water heater.
  • the screw compressor 100 includes a casing 1 in which a refrigerant flows.
  • the screw compressor 100 is housed in the casing 1, rotates around the rotary shaft 10, and compresses the refrigerant in the screw groove 2 a formed on the outer peripheral surface, and the screw groove 2 a of the screw rotor 2.
  • a housing groove 9 for a semi-cylindrical discharge port valve 8 that protrudes radially outward and extends in the axial direction of the rotary shaft 10 of the screw rotor 2 is formed on the inner cylinder surface of the casing 1 where the compression mechanism 4 is disposed.
  • a discharge port valve 8 forming a part of the discharge port 12 and the discharge flow path 13 is provided in the housing groove 9 so as to be slidable along the axial direction of the rotary shaft 10 of the screw rotor 2.
  • the discharge port valve 8 is driven by the drive mechanism 11 to adjust the discharge amount of the refrigerant compressed by the compression mechanism 4.
  • the screw compressor 100 includes a motor 5 that is provided on the low-pressure side that is upstream of the axial direction of the rotary shaft 10 of the screw rotor 2 in the refrigerant flow direction and that rotates the screw rotor 2.
  • the motor 5 is housed in a motor chamber 6 that is upstream of the compression mechanism 4 formed in the casing 1 in the direction of refrigerant flow in the axial direction of the rotary shaft 10.
  • the motor 5 is arranged on the upstream side in the refrigerant flow direction in the axial direction of the rotary shaft 10 of the screw rotor 2, so that the generated motor 5 is cooled by the low-temperature and low-pressure gaseous refrigerant.
  • the motor 5 includes a rotating rotor 5a connected to the screw rotor 2, and a stator 5b fixed to the casing 1 with an interval on the radially outer side of the rotor 5a.
  • the screw compressor 100 is formed with an inlet 7 for sucking low-temperature and low-pressure gaseous refrigerant upstream of the refrigerant flow direction in the axial direction of the rotary shaft 10 in the motor chamber 6.
  • the low-temperature and low-pressure gaseous refrigerant sucked from the suction port 7 of the casing 1 passes through the motor chamber 6 that houses the motor 5 and is compressed by the compression mechanism 4.
  • FIG. 2 is an explanatory diagram showing a cross section taken along line AA of FIG. 1 of the screw compressor 100 according to Embodiment 1 of the present invention.
  • the screw compressor 100 includes a plurality of refrigerant flow paths 21, 22 that circulate refrigerant in a direction along the axial direction of the rotary shaft 10 as shown by an arrow in FIG. 1 around the rotary shaft 10 of the screw rotor 2. 23a and 23b.
  • the plurality of refrigerant flow paths 21, 22, 23 a and 23 b are provided between the motor chamber 6 and the compression mechanism 4.
  • the eight refrigerant flow paths 21 are provided in the circumferential direction between the outer peripheral surface of the stator 5 b of the motor 5 and the inner peripheral surface of the casing 1, and supply refrigerant in a direction along the axial direction of the rotary shaft 10. Circulate.
  • the refrigerant flow path 22 is provided over the entire circumference between the outer peripheral surface of the rotor 5 a of the motor 5 and the inner peripheral surface of the stator 5 b of the motor 5, and distributes the refrigerant in a direction along the axial direction of the rotary shaft 10.
  • the refrigerant flow path 22 is a gap between the rotor 5 a that rotates the rotating shaft 10 of the motor 5 and the stator 5 b that is fixed to the casing 1.
  • the four refrigerant flow paths 23 a and 23 b are provided in a partition wall 14 that partitions the motor chamber 6 and the compression mechanism 4 in a direction orthogonal to the axial direction of the rotary shaft 10, and the motor chamber 6 and the compression mechanism 4 are separated from each other.
  • the refrigerant is circulated in a direction along the axial direction of the rotary shaft 10.
  • the four refrigerant flow paths 23 a and 23 b supply the refrigerant flowing through the eight refrigerant flow paths 21 and the refrigerant flow paths 22 to the compression mechanism 4.
  • the four refrigerant channels 23a and 23b include a near refrigerant channel 23a near the compression mechanism 4 and a far refrigerant channel 23b farther from the compression mechanism 4 than the near refrigerant channel 23a.
  • the number of refrigerant flow paths 23a and 23b is not limited to four, and a plurality of refrigerant flow paths 23a and 23b may be provided.
  • the four refrigerant channels 23a and 23b correspond to a plurality of first refrigerant channels of the present invention.
  • the cross-sectional area in a cross-sectional view perpendicular to the axial direction of the rotating shaft 10 of the two neighboring refrigerant flow paths 23 a close to the compression mechanism 4 is from the compression mechanism 4. It is smaller than the cross-sectional area in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the two distant refrigerant flow paths 23b.
  • sectional areas of the eight refrigerant channels 21 in the sectional view orthogonal to the axial direction of the rotating shaft 10 are all the same.
  • the four refrigerant flow paths 23a and 23b are divided into the sizes of the cross-sectional areas in the cross-sectional view orthogonal to the axial directions of the two types of the rotary shafts 10.
  • the present invention is not limited to this, and the cross-sectional area in a cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the near refrigerant flow path near the compression mechanism 4 among the plurality of refrigerant flow paths is that of the far refrigerant flow path far from the compression mechanism 4. It is only necessary to satisfy the relationship that it is smaller than the sectional area in the sectional view orthogonal to the axial direction of the rotating shaft 10. For this reason, each cross-sectional area may differ so that said relationship of the four refrigerant flow paths 23a and 23b may be satisfy
  • the flow resistance in the remote refrigerant flow path 23b far from the compression mechanism 4 out of the four refrigerant flow paths 23a and 23b is small, and the amount of refrigerant flowing through the compression mechanism 4 increases.
  • the flow path resistance in the vicinity refrigerant flow path 23a close to the compression mechanism 4 is large, and the amount of refrigerant flowing through the compression mechanism 4 decreases.
  • the screw compressor 100 can easily flow in the refrigerant that is the suction gas from the refrigerant flow path 23a near the compression mechanism 4 out of the four refrigerant flow paths 23a and 23b, and the refrigerant is far from the compression mechanism 4.
  • the amount of refrigerant flowing around the rotary shaft 10 of the screw rotor 2 can be increased or decreased.
  • circulates the motor chamber 6 flows uniformly over the perimeter around the rotating shaft 10 of the screw rotor 2.
  • the motor 5 will be in a uniform cooling state over the perimeter around the rotating shaft 10 of the screw rotor 2, and the temperature difference in the coil end of the stator 5b of the motor 5 can be suppressed.
  • the motor 5 is in a uniform cooling state over the entire circumference around the rotating shaft 10 of the screw rotor 2, and the temperature of the coil end of the stator 5 b can be locally suppressed from becoming high. Therefore, the operating range of the screw compressor 100 can be expanded.
  • the screw compressor 100 does not have a variable mechanism such as a variable flow rate mechanism in the motor chamber 6, the structure can be simplified, the manufacturing cost can be reduced, and the assembly workability can be improved.
  • FIG. 3 is an explanatory view showing a cross section along line AA of FIG. 1 of the screw compressor 100 according to Embodiment 2 of the present invention.
  • the screw compressor 100 includes a plurality of refrigerant flow paths 21 a, 21 b, 22, and 23 that circulate refrigerant in a direction along the axial direction of the rotary shaft 10 around the rotary shaft 10 of the screw rotor 2.
  • the eight refrigerant flow paths 21 a and 21 b are provided in the circumferential direction between the outer peripheral surface of the stator 5 b of the motor 5 and the inner peripheral surface of the casing 1, and extend in the direction along the axial direction of the rotary shaft 10. Circulate the refrigerant.
  • the eight refrigerant flow paths 21 a and 21 b include a near refrigerant flow path 21 a near the compression mechanism 4 and a far refrigerant flow path 21 b farther from the compression mechanism 4 than the near refrigerant flow path 21 a.
  • the number of the refrigerant flow paths 21a and 21b is not limited to eight, and a plurality of refrigerant flow paths may be provided.
  • the eight refrigerant flow paths 21a and 21b correspond to a plurality of second refrigerant flow paths of the present invention.
  • the four refrigerant channels 23 are provided in a partition wall 14 that partitions the motor chamber 6 and the compression mechanism 4 in a direction orthogonal to the axial direction of the rotary shaft 10, and communicates the motor chamber 6 and the compression mechanism 4.
  • the refrigerant is circulated in the direction along the axial direction of the rotating shaft 10.
  • the four refrigerant channels 23 supply the refrigerant flowing through the eight refrigerant channels 21 a and 21 b and the refrigerant channel 22 to the compression mechanism 4.
  • the cross-sectional area in the cross-sectional view perpendicular to the axial direction of the rotating shaft 10 of the four neighboring refrigerant flow paths 21 a close to the compression mechanism 4 is from the compression mechanism 4. It is smaller than the cross-sectional area in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the four distant refrigerant flow paths 21b.
  • the cross-sectional areas of the four refrigerant flow paths 23 in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 are all the same.
  • the eight refrigerant flow paths 21a and 21b are divided into cross-sectional area sizes in a cross-sectional view orthogonal to the axial directions of the two types of rotary shafts 10.
  • the present invention is not limited to this, and the cross-sectional area in a cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the near refrigerant flow path near the compression mechanism 4 among the plurality of refrigerant flow paths is that of the far refrigerant flow path far from the compression mechanism 4. It is only necessary to satisfy the relationship that it is smaller than the sectional area in the sectional view orthogonal to the axial direction of the rotating shaft 10. For this reason, each cross-sectional area may differ so that said relationship of the eight refrigerant flow paths 21a and 21b may be satisfy
  • the flow resistance in the far refrigerant flow path 21b far from the compression mechanism 4 out of the eight refrigerant flow paths 21a and 21b is small, and the amount of refrigerant flowing through the compression mechanism 4 is increased.
  • the channel resistance in the vicinity refrigerant channel 21a close to the compression mechanism 4 is large, and the amount of refrigerant flowing through the compression mechanism 4 decreases.
  • the refrigerant that is the suction gas by the screw compressor 100 can easily flow from the refrigerant flow path 21a in the vicinity of the compression mechanism 4 out of the eight refrigerant flow paths 21a and 21b, and the remote refrigerant flow path far from the compression mechanism 4 Contrary to having the property of not easily flowing in from 21b, the amount of refrigerant flowing around the rotating shaft 10 of the screw rotor 2 can be increased or decreased.
  • circulates the motor chamber 6 flows uniformly over the perimeter around the rotating shaft 10 of the screw rotor 2.
  • FIG. And the motor 5 will be in a uniform cooling state over the perimeter around the rotating shaft 10 of the screw rotor 2, and the temperature difference in the coil end of the stator 5b of the motor 5 can be suppressed.
  • the motor 5 is in a uniform cooling state over the entire circumference around the rotating shaft 10 of the screw rotor 2, and the temperature of the coil end of the stator 5 b can be locally suppressed from becoming high. Therefore, the operating range of the screw compressor 100 can be expanded.
  • the screw compressor 100 does not have a variable mechanism such as a variable flow rate mechanism in the motor chamber 6, the structure can be simplified, the manufacturing cost can be reduced, and the assembly workability can be improved.
  • FIG. 3 is a combination of the first embodiment and the second embodiment.
  • FIG. 4 is an explanatory view showing a cross section along line AA of FIG. 1 of the screw compressor 100 according to Embodiment 3 of the present invention.
  • the screw compressor 100 includes a plurality of refrigerant flow paths 21 a, 21 b, 22, 23 a, and 23 b that circulate refrigerant in a direction along the axial direction of the rotary shaft 10 around the rotary shaft 10 of the screw rotor 2. Yes.
  • the eight refrigerant flow paths 21 a and 21 b are provided in the circumferential direction between the outer peripheral surface of the stator 5 b of the motor 5 and the inner peripheral surface of the casing 1, and extend in the direction along the axial direction of the rotary shaft 10. Circulate the refrigerant.
  • the eight refrigerant flow paths 21 a and 21 b include a near refrigerant flow path 21 a near the compression mechanism 4 and a far refrigerant flow path 21 b farther from the compression mechanism 4 than the near refrigerant flow path 21 a.
  • the number of the refrigerant flow paths 21a and 21b is not limited to eight, and a plurality of refrigerant flow paths may be provided.
  • the eight refrigerant flow paths 21a and 21b correspond to a plurality of second refrigerant flow paths of the present invention.
  • the four refrigerant flow paths 23 a and 23 b are provided in a partition wall 14 that partitions the motor chamber 6 and the compression mechanism 4 in a direction orthogonal to the axial direction of the rotary shaft 10, and the motor chamber 6 and the compression mechanism 4 are separated from each other.
  • the refrigerant is circulated in a direction along the axial direction of the rotary shaft 10.
  • the four refrigerant flow paths 23 a and 23 b supply the refrigerant flowing through the eight refrigerant flow paths 21 and the refrigerant flow paths 22 to the compression mechanism 4.
  • the four refrigerant channels 23a and 23b include a near refrigerant channel 23a near the compression mechanism 4 and a far refrigerant channel 23b farther from the compression mechanism 4 than the near refrigerant channel 23a.
  • the number of refrigerant flow paths 23a and 23b is not limited to four, and a plurality of refrigerant flow paths 23a and 23b may be provided.
  • the four refrigerant channels 23a and 23b correspond to a plurality of first refrigerant channels of the present invention.
  • the cross-sectional area in the cross-sectional view perpendicular to the axial direction of the rotating shaft 10 of the four neighboring refrigerant flow paths 21 a close to the compression mechanism 4 is from the compression mechanism 4. It is smaller than the cross-sectional area in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the four distant refrigerant flow paths 21b.
  • the cross-sectional area of the four refrigerant flow paths 23a, 23b in the cross-sectional view perpendicular to the axial direction of the rotating shaft 10 of the two neighboring refrigerant flow paths 23a close to the compression mechanism 4 is two far-distance refrigerants far from the compression mechanism 4. It is smaller than the cross-sectional area in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the flow path 23b.
  • the eight refrigerant flow paths 21a and 21b are divided into the sizes of the cross-sectional areas in the cross-sectional view orthogonal to the axial directions of the two types of rotary shafts 10.
  • the present invention is not limited to this, and the cross-sectional area in a cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the near refrigerant flow path near the compression mechanism 4 among the plurality of refrigerant flow paths is that of the far refrigerant flow path far from the compression mechanism 4. It is only necessary to satisfy the relationship that it is smaller than the sectional area in the sectional view orthogonal to the axial direction of the rotating shaft 10.
  • each cross-sectional area may differ so that said relationship of the eight refrigerant flow paths 21a and 21b may be satisfy
  • the four refrigerant flow paths 23 a and 23 b are divided into the sizes of the cross-sectional areas in a cross-sectional view orthogonal to the axial directions of the two types of rotating shafts 10.
  • the present invention is not limited to this, and the cross-sectional area in a cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the near refrigerant flow path near the compression mechanism 4 among the plurality of refrigerant flow paths is that of the far refrigerant flow path far from the compression mechanism 4. It is only necessary to satisfy the relationship that it is smaller than the sectional area in the sectional view orthogonal to the axial direction of the rotating shaft 10. For this reason, each cross-sectional area may differ so that said relationship of the four refrigerant flow paths 23a and 23b may be satisfy
  • the flow resistance in the remote refrigerant flow path 23b far from the compression mechanism 4 out of the four refrigerant flow paths 23a and 23b is small, and the amount of refrigerant flowing through the compression mechanism 4 increases.
  • the flow path resistance in the vicinity refrigerant flow path 23a close to the compression mechanism 4 is large, and the amount of refrigerant flowing through the compression mechanism 4 decreases.
  • the flow resistance in the far refrigerant flow path 21b far from the compression mechanism 4 is small, and the amount of refrigerant flowing through the compression mechanism 4 increases.
  • the screw compressor 100 can easily flow in the refrigerant as the suction gas from the refrigerant flow paths 23a and 21a near the compression mechanism 4 out of the four refrigerant flow paths 23a and 23b and the eight refrigerant flow paths 21a and 21b.
  • the motor 5 is in a uniform cooling state over the entire circumference around the rotating shaft 10 of the screw rotor 2, and the temperature of the coil end of the stator 5 b can be locally suppressed from becoming high. Therefore, the operating range of the screw compressor 100 can be expanded.
  • the screw compressor 100 does not have a variable mechanism such as a variable flow rate mechanism in the motor chamber 6, the structure can be simplified, the manufacturing cost can be reduced, and the assembly workability can be improved.
  • FIG. 5 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which the screw compressor 100 according to Embodiment 5 of the present invention is applied.
  • the refrigeration cycle apparatus 200 includes a screw compressor 100, a condenser 80, an expansion valve 81, and an evaporator 82. These screw compressor 100, condenser 80, expansion valve 81 and evaporator 82 are connected by refrigerant piping to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 82 is sucked into the screw compressor 100 and becomes high temperature and pressure. The high-temperature and high-pressure refrigerant is condensed in the condenser 80 to become a liquid.
  • the refrigerant that has become liquid is decompressed and expanded by the expansion valve 81 to become a low-temperature and low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 82.
  • the screw compressor 100 according to the first to third embodiments can be applied to such a refrigeration cycle apparatus 200.
  • the refrigeration cycle apparatus 200 include an air conditioner, a refrigeration apparatus, and a water heater.
  • the screw compressor 100 includes the casing 1 in which the refrigerant flows.
  • the screw rotor 2 is housed in the casing 1 and rotates around the rotary shaft 10 to compress the refrigerant in the screw groove 2a formed on the outer peripheral surface.
  • the gate rotor 3 is engaged with the screw groove 2a of the screw rotor 2.
  • the compression mechanism 4 is provided.
  • a motor 5 is provided on the low-pressure side in the axial direction of the rotary shaft 10 of the screw rotor 2 and drives the screw rotor 2 to rotate.
  • the low-pressure refrigerant sucked from the suction port 7 of the casing 1 passes through the motor chamber 6 that houses the motor 5 and is compressed by the compression mechanism 4.
  • a plurality of refrigerant flow paths 21 a, 21 b, 23 a, and 23 b that circulate the refrigerant in the direction along the axial direction of the rotating shaft 10 are provided.
  • the plurality of refrigerant channels 21 a, 21 b, 23 a, 23 b provided between the motor chamber 6 and the compression mechanism 4 are based on the vicinity refrigerant channels 21 a, 23 a close to the compression mechanism 4 and the vicinity refrigerant channels 21 a, 23 a. Includes remote refrigerant channels 21b and 23b far from the compression mechanism 4.
  • the cross-sectional area in the cross-sectional view orthogonal to the axial direction of the rotating shaft 10 of the near refrigerant flow paths 21a and 23a is smaller than the cross-sectional area of the distant refrigerant flow paths 21b and 23b. According to this configuration, the amount of refrigerant flowing on the side closer to the compression mechanism 4 around the rotating shaft 10 of the screw rotor 2 decreases, while the amount of refrigerant flowing on the side farther from the compression mechanism 4 increases. Therefore, the cooling of the motor 5 is made uniform, insufficient cooling of the motor 5 is suppressed, the local temperature rise of the motor 5 is suppressed, and the operating range when the rotational speed by the inverter drive is increased or decreased can be expanded.
  • the cross-sectional area of the near refrigerant flow path 23a is smaller than the cross-sectional area of the distant refrigerant flow path 23b.
  • the motor 5 has a rotating rotor 5a connected to the screw rotor 2, and a stator 5b fixed at an interval on the radially outer side of the rotor 5a.
  • the plurality of refrigerant flow paths 21 a and 21 b provided between the motor chamber 6 and the compression mechanism 4 are provided between the outer peripheral surface of the stator 5 b of the motor 5 and the inner peripheral surface of the casing 1.
  • the cross-sectional area of the near refrigerant flow path 21a among the plurality of refrigerant flow paths 21a and 21b is smaller than the cross-sectional area of the distant refrigerant flow path 21b.
  • the amount of refrigerant flowing on the side closer to the compression mechanism 4 around the rotating shaft 10 of the screw rotor 2 decreases, while the amount of refrigerant flowing on the side farther from the compression mechanism 4 increases. Therefore, the cooling of the motor 5 is made uniform, insufficient cooling of the motor 5 is suppressed, the local temperature rise of the motor 5 is suppressed, and the operating range when the rotational speed by the inverter drive is increased or decreased can be expanded.
  • the refrigeration cycle apparatus 200 includes a screw compressor 100. According to this configuration, the cooling of the motor 5 is made uniform, the insufficient cooling of the motor 5 is suppressed, the local temperature rise of the motor 5 is suppressed, and the operating range when the rotational speed by the inverter drive is increased or decreased is reduced. Can be expanded.
  • the monogate rotor system has been described as the screw compressor.
  • the present invention is not limited to the mono-gate rotor system, and may be a twin-gate rotor system that has a structure in which the compression operation on one side is suspended and can perform one-side operation.
  • the twin gate rotor type screw compressor of the present invention the amount of refrigerant flowing on the side near the compression mechanism is reduced around the rotation axis of the screw rotor, even in partial load operation where the refrigerant circulation amount becomes very small.
  • the amount of refrigerant flowing on the side far from the mechanism increases. Therefore, it can suppress that the oil which flows with a refrigerant

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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Selon la présente invention, le refroidissement d'un moteur est rendu uniforme, des augmentations localisées de la température du moteur sont supprimés, et la plage de fonctionnement lors de l'augmentation ou la diminution de la vitesse de rotation à l'aide d'une commande d'onduleur est accrue. Des passages d'écoulement de réfrigérant dans lesquels un réfrigérant est amené à circuler dans une direction le long de la direction axiale d'un arbre rotatif d'un rotor à vis sont réalisés autour de l'arbre rotatif. Un passage d'écoulement de réfrigérant réalisé entre une chambre de moteur et un mécanisme de compression comprend un passage d'écoulement de réfrigérant proche qui est proche du mécanisme de compression, et un passage d'écoulement de réfrigérant distant qui est plus éloigné du mécanisme de compression que le passage d'écoulement de réfrigérant proche. La superficie de la section transversale du passage d'écoulement de réfrigérant proche, vue dans une section transversale orthogonale à la direction axiale de l'arbre rotatif, est inférieure à la superficie de la section transversale du passage d'écoulement de réfrigérant distant.
PCT/JP2016/050211 2016-01-06 2016-01-06 Compresseur à vis et dispositif à cycle de réfrigération WO2017119075A1 (fr)

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PCT/JP2016/050211 WO2017119075A1 (fr) 2016-01-06 2016-01-06 Compresseur à vis et dispositif à cycle de réfrigération

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PCT/JP2016/050211 WO2017119075A1 (fr) 2016-01-06 2016-01-06 Compresseur à vis et dispositif à cycle de réfrigération

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5095605U (fr) * 1973-12-28 1975-08-11
JPH0135197B2 (fr) * 1979-06-19 1989-07-24 Omphal Sa
JPH11351168A (ja) * 1998-06-05 1999-12-21 Kobe Steel Ltd スクリュ式冷凍装置
JP3622587B2 (ja) * 1999-08-26 2005-02-23 ダイキン工業株式会社 スクリュー圧縮機
JP5178612B2 (ja) * 2009-04-16 2013-04-10 三菱電機株式会社 スクリュー圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5095605U (fr) * 1973-12-28 1975-08-11
JPH0135197B2 (fr) * 1979-06-19 1989-07-24 Omphal Sa
JPH11351168A (ja) * 1998-06-05 1999-12-21 Kobe Steel Ltd スクリュ式冷凍装置
JP3622587B2 (ja) * 1999-08-26 2005-02-23 ダイキン工業株式会社 スクリュー圧縮機
JP5178612B2 (ja) * 2009-04-16 2013-04-10 三菱電機株式会社 スクリュー圧縮機

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