CN113939653A

CN113939653A - Compressor

Info

Publication number: CN113939653A
Application number: CN201980097024.4A
Authority: CN
Inventors: 增本浩二; 小山修平; 达胁浩平
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2019-06-18
Filing date: 2019-06-18
Publication date: 2022-01-14
Also published as: WO2020255243A1; JPWO2020255243A1

Abstract

The compressor is provided with: a housing constituting a casing; a motor disposed inside the housing; a compression unit which is provided inside the casing and is driven by the motor to compress the refrigerant; and a shaft portion that connects the motor and the compression portion and transmits a rotational force of the motor to the compression portion, the motor including: a stator provided on an inner surface of the housing and having a plurality of divided cores arranged in a circumferential shape; and a rotor provided on an inner peripheral side of the plurality of divided cores of the stator and rotated by the stator, the plurality of divided cores having extending portions whose both end portions extend along the shaft portion.

Description

Compressor

Technical Field

The present invention relates to a compressor for compressing a refrigerant.

Background

In recent years, from the viewpoint of preventing global warming, the transition from HFC (hydrofluorocarbon) refrigerants used so far to low GWP refrigerants is advancing. As the refrigerant having a lower GWP than the HFC refrigerant, carbon dioxide or the like can be mentioned. Carbon dioxide has a high operating pressure in terms of physical properties, and the discharge temperature of the compressor tends to increase. Further, a compressor used in an ice chest, a refrigerator, or the like is operated at a high compression ratio in which the pressure ratio of the suction pressure to the discharge pressure is high, and therefore the discharge temperature is high. Since carbon dioxide has higher operating pressure than HFC refrigerant in terms of physical properties, it is necessary to secure the strength of a casing, which is a container constituting the outer contour of the compressor. The strength of the shell is increased by increasing the wall thickness. When the discharge temperature is high, a compressor of an injection type is generally used in which a high-pressure liquid refrigerant is introduced into the compressor at an appropriate position in the compression chamber.

Patent document 1 discloses a scroll compressor in which a jet port is formed in a platen of a fixed scroll, and a fixed scroll and an oscillating scroll each having a scroll body are fitted to each other to form a compression chamber. In the compressor of patent document 1, a motor having a stator and a rotor is disposed at a lower portion in a casing, and a compression chamber is disposed at an upper portion in the casing. In patent document 1, a high-pressure liquid refrigerant flows from an injection port into a compression chamber of an intermediate pressure. Thus, in patent document 1, the gas temperature in the compression chamber is lowered, and the discharge temperature of the refrigerant discharged from the compression chamber is lowered, so that the air conditioning efficiency is improved.

Patent document 1: japanese patent laid-open publication No. 2012-127222

However, in the scroll compressor disclosed in patent document 1, although the lower pressure is normally maintained in the shell, when the compressor is stopped, the high-pressure liquid refrigerant is introduced into the shell from the injection port, and therefore the pressure in the shell becomes high. Thus, the differential pressure between the high pressure and the low pressure of the casing of patent document 1 is large. Therefore, when the pressure in the casing is low, when the high-pressure liquid refrigerant is introduced into the casing from the injection port at the time of stopping the compressor, the pressure in the casing becomes high and the refrigerant expands, and there is a possibility that the stator held on the inner peripheral surface of the casing falls off.

Disclosure of Invention

The present invention has been made to solve the above-described problems, and provides a compressor in which the stator is prevented from falling off regardless of the pressure in the casing.

The compressor of the present invention comprises: a housing constituting a casing; a motor disposed inside the housing; a compression unit which is provided inside the casing and is driven by the motor to compress the refrigerant; and a shaft portion that connects the motor and the compression portion and transmits a rotational force of the motor to the compression portion, the motor including: a stator provided on an inner surface of the housing and having a plurality of divided cores arranged in a circumferential shape; and a rotor provided on an inner peripheral side of the plurality of divided cores of the stator and rotated by the stator, the plurality of divided cores having extending portions whose both end portions extend along the shaft portion.

According to the present invention, the plurality of divided cores of the stator have the extending portions whose both end portions extend along the shaft portion. Therefore, when the housing is expanded due to high pressure, the split cores extend in the radial direction of the housing by an amount corresponding to the amount of contraction of the tip of the extension portion. Therefore, even if the diameter of the housing is increased, the outer diameter of the stator having the plurality of divided cores follows the increased diameter. Therefore, the stator can be prevented from falling off regardless of the pressure in the case.

Drawings

Fig. 1 is a circuit diagram showing an air conditioner according to embodiment 1.

Fig. 2 is a sectional view showing a compressor according to embodiment 1.

Fig. 3 is a plan view showing a stator according to embodiment 1.

Fig. 4 is a plan view showing a stator of comparative example 1.

Fig. 5 is a plan view showing a stator according to embodiment 1.

Fig. 6 is a plan view showing a plurality of divided cores according to embodiment 1.

Fig. 7 is a plan view showing a stator of comparative example 2.

Fig. 8 is a plan view showing a division core according to embodiment 1.

Fig. 9 is a perspective view showing a division core according to embodiment 1.

Fig. 10 is a development view showing a plurality of divided cores according to embodiment 1.

Detailed Description

Hereinafter, an embodiment of a compressor according to the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments described below. In addition, in the following drawings, including fig. 1, the relationship between the sizes of the respective components may be different from the actual one. In the following description, terms indicating directions are used as appropriate for easy understanding of the present invention, and are terms for describing the present invention, and these terms do not limit the present invention. Examples of the terms indicating the direction include "up", "down", "right", "left", "front", and "rear".

Embodiment 1.

Fig. 1 is a circuit diagram showing an air conditioner 100 according to embodiment 1. The air conditioner 100 is a device for adjusting indoor air, and includes an outdoor unit 41, an indoor unit 42, and a control device 47, as shown in fig. 1. The outdoor unit 41 includes, for example, a compressor 43, an outdoor heat exchanger 44, an outdoor blower 44a, an expansion unit 45, and an intermediate injection circuit 50. The indoor unit 42 is provided with, for example, an indoor heat exchanger 46 and an indoor air-sending device 46a.

The compressor 43, the outdoor heat exchanger 44, the expansion unit 45, and the indoor heat exchanger 46 are connected by refrigerant pipes 48 to constitute the refrigerant circuit 40. The compressor 43 sucks the refrigerant in a low-temperature and low-pressure state, compresses the sucked refrigerant into a high-temperature and high-pressure refrigerant, and discharges the refrigerant. The outdoor heat exchanger 44 exchanges heat between outdoor air and refrigerant, for example. The outdoor heat exchanger 44 functions as a radiator. The outdoor blower 44a is a device that sends outdoor air to the outdoor heat exchanger 44.

The expansion unit 45 is a pressure reducing valve or an expansion valve that reduces the pressure of the refrigerant and expands the refrigerant. The expansion unit 45 is, for example, an electronic expansion valve whose opening degree is adjusted. The indoor heat exchanger 46 exchanges heat between, for example, indoor air and refrigerant. The indoor heat exchanger 46 functions as an evaporator. The indoor blower 46a is a device that sends indoor air to the indoor heat exchanger 46.

The intermediate injection circuit 50 connects the space between the outdoor heat exchanger 44 and the expansion unit 45 to the injection pipe 15 of the compressor 43. The refrigerant flowing out of the outdoor heat exchanger 44 flows through the intermediate injection circuit 50. The intermediate injection circuit 50 is provided with an injection expansion portion 51 and a solenoid valve 52. The injection expansion unit 51 is a pressure reducing valve or an expansion valve that reduces the pressure of the refrigerant flowing through the intermediate injection circuit 50 and expands the refrigerant. The injection expansion unit 51 is, for example, an electronic expansion valve whose opening degree is adjusted. The solenoid valve 52 allows or shuts off the flow of the refrigerant in the intermediate injection circuit 50, and is, for example, an on-off valve.

The control device 47 is composed of, for example, a microcomputer and a memory, and controls each device of the air conditioner 100. For example, the control device 47 adjusts the opening degree of the injection expansion unit 51 to adjust the amount of the refrigerant flowing through the intermediate injection circuit 50. In embodiment 1, carbon dioxide (CO) is used₂) As a refrigerant. The refrigerant pipe 48 is not limited to being filled with carbon dioxide (CO)₂) Optionally, carbon dioxide (CO) may be added₂) The mixed refrigerant of (3) may be further charged with another refrigerant.

Fig. 2 is a sectional view showing a compressor 43 according to embodiment 1. Next, the compressor 43 will be described in detail. The compressor 43 is, for example, a hermetic type scroll compressor that sucks and compresses a refrigerant circulating in a refrigeration cycle, and discharges the refrigerant in a high-temperature and high-pressure state. As shown in fig. 2, the compressor 43 includes a casing 8, a frame 3, an auxiliary frame 19, a shaft portion 4, a bearing portion 3b, a sub-bearing 19a, a suction pipe 5, a discharge pipe 13, an injection pipe 15, a compression portion 35, and a concave bearing 2d. The compressor 43 includes an eccentric pin portion 4a, the oldham ring 20, the valve 11, the valve pressing member 10, the oil pump 21, and the motor 36.

The casing 8 is a closed container constituting a housing of the compressor 43, and houses therein the compression section 35, the motor 36, and other components. A compression unit 35 is disposed at an upper portion and a motor 36 is disposed at a lower portion in the housing 8. Further, an oil reservoir 12 is formed at a lower portion of the casing 8.

The frame 3 is disposed above the motor 36 and between the motor 36 and the compression unit 35. The sub-frame 19 is disposed below the motor 36. The frame 3 and the sub-frame 19 are fixed to the inside of the housing 8 so as to face each other with the motor 36 interposed therebetween. The frame 3 and the auxiliary frame 19 are fixed to the inner peripheral surface of the housing 8 by shrink fitting, welding, or the like. The shaft portion 4 is a rod-shaped crank shaft extending in the vertical direction at the center of the housing 8, and connects the motor 36 and the compression portion 35. The shaft portion 4 connects the motor 36 and the compression portion 35, and transmits the rotational force of the motor 36 to the compression portion 35. An oil circuit 22 through which oil passes is formed inside the shaft portion 4. The bearing portion 3b is provided at the center of the frame 3 and rotatably supports the shaft portion 4. The sub-bearing 19a is provided at the center of the sub-frame 19 and rotatably supports the shaft 4.

The suction pipe 5 is connected to a low-pressure space 17 formed between the motor 36 and the compression part 35 in the casing 8 at a side of the casing 8. The suction pipe 5 sucks the low-pressure refrigerant flowing out of the refrigerant pipe 48 into the low-pressure space 17. The discharge pipe 13 is connected at an upper portion of the housing 8 with the high-pressure space 14 formed above the compression portion 35 in the housing 8. The discharge pipe 13 discharges the high-pressure refrigerant compressed by the compression portion 35 to a refrigerant pipe 48 outside the compressor 43. The injection pipe 15 is connected to the compression chamber 9 of the compression unit 35 at the upper portion of the casing 8. The injection pipe 15 introduces the refrigerant in a liquid state or a gas-liquid two-phase state flowing through the intermediate injection circuit 50 into the compression chamber 9. In this way, the injection pipe 15 is provided in the casing 8, and introduces the refrigerant in a liquid state or a gas-liquid two-phase state into the compression portion 35.

The compression portion 35 compresses the refrigerant sucked from the suction pipe 5 and discharges the compressed refrigerant to the high-pressure space 14 formed above the inside of the casing 8. The compression portion 35 includes a fixed scroll 1 and an oscillating scroll 2. The fixed scroll 1 is fixed to a housing 8 via a frame 3 above the orbiting scroll 2, and has a first platen 1c and a first scroll body 1b. The first platen 1c is a plate-like member, and constitutes an upper surface of the compression portion 35. The first vortex body 1b is a vortex-like projection extending downward from the lower surface of the first platen 1c.

The oscillating scroll 2 has a second platen 2c and a second scroll body 2b. The second platen 2c is a plate-like member disposed above the frame 3. The second vortex bodies 2b are spiral protrusions extending upward from the upper surface of the second platen 2c. The fixed scroll 1 and the oscillating scroll 2 are disposed in the housing 8 in a state where the first scroll 1b and the second scroll 2b are engaged with each other. The first scroll body 1b and the second scroll body 2b are formed following an involute curve, and the first scroll body 1b and the second scroll body 2b are combined in a meshed state, whereby a plurality of compression chambers 9 are formed between the first scroll body 1b and the second scroll body 2b.

A discharge port 1a is formed in the center of the fixed scroll 1, and the discharge port 1a is a space in which a refrigerant compressed to a high pressure is discharged. Further, an injection port 16 to which an injection pipe 15 is connected is formed in the first platen 1c of the fixed scroll 1. The injection port 16 is formed in each of a pair of compression chambers 9 which are point-symmetrical about the center of the first scroll 1b and the second scroll 2b. The liquid or gas-liquid two-phase refrigerant flowing in from the injection pipe 15 flows out through the injection port 16 into the compression chamber 9 in which the refrigerant is present in the middle of the compression process.

An injection distribution flow path 15a is formed in the fixed scroll 1. The injection distribution passage 15a is a passage for branching the refrigerant supplied from the injection pipe 15 into two paths and allowing the refrigerant to flow into two injection ports 16. In embodiment 1, the case where the injection distribution passage 15a is a hole formed in the fixed scroll 1 is exemplified, but the injection distribution passage 15a may be formed by a pipe independent from the fixed scroll 1. In this case, the compressor 43 has a pipe for guiding the refrigerant from the outside of the casing 8 to the injection port 16 located in the casing 8, and the outflow side of the pipe is branched in two directions and connected to the injection ports 16.

The lower portion of the second platen 2c of the orbiting scroll 2 is a concave bearing 2d. The recessed bearing 2d covers the shaft portion 4 and the eccentric pin portion 4a, and rotatably supports the shaft portion 4. An eccentric pin portion 4a is provided at the upper end of the shaft portion 4, and eccentrically rotates the orbiting scroll 2. The oldham ring 20 is disposed between the fixed scroll 1 and the orbiting scroll 2, and prevents the orbiting movement of the orbiting scroll 2 in the eccentric orbiting motion, thereby allowing the orbiting movement of the orbiting scroll 2.

The valve 11 is a plate spring member that covers the outlet opening of the discharge port 1a to prevent the refrigerant from flowing back. The valve pressing member 10 is provided at one end of the valve 11 to limit the amount of lifting of the valve 11. When the refrigerant is compressed to a predetermined pressure in the compression chamber 9, the refrigerant pushes the valve 11 against the elastic force of the valve 11. The compressed refrigerant is discharged from the discharge port 1a to the high-pressure space 14, and is discharged to the outside of the compressor 43 through the discharge pipe 13. The oil pump 21 is fixed to a lower portion of the shaft portion 4. The oil pump 21 is, for example, a displacement pump, and sucks the refrigerator oil stored in the oil reservoir 12 to an oil circuit 22 formed inside the shaft portion 4 by rotation of the shaft portion 4, and supplies the refrigerator oil to the bearing portion 3b and the concave bearing 2d through the oil circuit 22.

The motor 36 is provided in the low-pressure space 17 on the low-pressure side where the refrigerant is sucked, inside the casing 8. The motor 36 drives the orbiting scroll 2 constituting the compression portion 35. That is, the motor 36 rotates and drives the orbiting scroll 2 via the shaft portion 4, thereby compressing the refrigerant in the compression portion 35. The motor 36 has a rotor 6 and a stator 7. The rotor 6 is provided on the inner peripheral side of the stator 7. The rotor 6 is rotationally driven by energizing the stator 7, and rotates the shaft 4. The rotor 6 is fixed to the outer periphery of the shaft portion 4 and held with a slight gap from the stator 7.

Fig. 3 is a plan view showing stator 7 according to embodiment 1. The stator 7 is provided on an inner surface of the housing 8, and rotates the rotor 6 by being energized. In embodiment 1, the stator 7 is wound in a concentrated winding manner in which wires are concentrated. As shown in fig. 3, the stator 7 includes an annular core 61, a plurality of teeth 62 extending from the core 61 toward the inner peripheral side, and a coil including a winding 63 wound around each of the teeth 62. The windings 63 are spaced apart from each other by a space called a slot 64.

Fig. 4 is a plan view showing a stator 7a of comparative example 1. Here, as comparative example 1, a case where the stator 7a is wound in a distributed winding manner will be described. As shown in fig. 4, the stator 7a of comparative example 1 includes an annular core 61a, teeth 62a extending from the core 61a toward the inner peripheral side, and a coil including a winding 63a wound over the plurality of teeth 62 a. The inner peripheral side of the core 61a is a space called an insertion groove 64a. As shown in fig. 3 and 4, the core 61 of the concentrated winding type stator 7 is thinner than the core 61a of the distributed winding type stator 7 a.

Fig. 5 is a plan view showing stator 7 according to embodiment 1, and fig. 6 is a plan view showing a plurality of divided cores 70 according to embodiment 1. In embodiment 1, as shown in fig. 5 and 6, the core 61 and the teeth 62 of the stator 7 are formed of a plurality of divided cores 70 arranged in a circumferential shape. The plurality of divided cores 70 are welded and fixed, respectively. In this case, a wire is wound around each of the divided cores 70, and then the divided cores 70 are welded to each other. In this way, when the core 61 is formed of a plurality of divided cores 70, winding can be performed without using the winding nozzle 65. Both ends of the split core 70 become split portions 74. In embodiment 1, the number of the plurality of divided cores 70 is equal to the number of coils of the winding 63.

Fig. 7 is a plan view showing a stator 7b of comparative example 2. Here, a case where the stator 7b and the teeth 62b are integrated into the core 61b will be described as comparative example 2. As shown in fig. 7, the core of the stator 7b of comparative example 2 is not divided, and has an integral shape. In this case, the wire 63b is wound around each tooth 62 using the wire winding nozzle 65.

Fig. 8 is a plan view showing a divided core 70 according to embodiment 1, and fig. 9 is a perspective view showing the divided core 70 according to embodiment 1. As shown in fig. 8 and 9, the split core 70 is a T-shaped electromagnetic steel plate, and includes a core portion 71 in which a plurality of split cores 70 are arranged to form the core 61, and a tooth portion 72 extending from the core portion 71 to form the teeth 62. The portion where the divided cores 70 are in close contact with each other is referred to as a divided portion 74. Here, a plurality of cores 61 formed of a plurality of divided cores 70 are stacked in the axial direction of the shaft portion 4 (see fig. 10). The length of the iron core portion 71 in the radial direction is referred to as a yoke width W. Here, a process of fixing the stator 7 to the housing 8 will be described. Each of the divided cores 70 having the coil formed thereon is fixed by shrink fitting with the divided portions 74 closely disposed in the case 8. A value obtained by subtracting the inner diameter of the housing 8 from the outer diameter of the stator 7 is referred to as interference (shrink fit margin). The stator 7 is fixed to the housing 8 by using an interference of several 10 μm.

The stator 7 of the motor 36 is generally fixed to the housing 8 by press fitting, shrink fitting, or the like. In the case of fixing by press fitting or shrink fitting, an appropriate interference is set. The differential pressure between the pressure in the low-pressure space 17 inside the casing 8 of the compressor 43 and the pressure outside is about 1MPa during normal operation, but the high pressure and the low pressure are equalized at the time of stop, and is assumed to be about 10 MPa. Therefore, the thickness of the case 8 is set to be relatively large, and the interference between the case 8 and the stator 7 is set to be relatively large. When the casing 8 expands due to the differential pressure, the stator 7 may come off, and the interference is set to be large. Whereby the stator 7 and the housing 8 are reliably fixed.

Next, the manufacturing conditions of the compressor 43 will be explained. First, the thermal margin obtained by subtracting the inner diameter of the case 8 from the outer diameter (160mm) of the stator 7 before thermal charging is about 150 μm, for example, 125 μm to 175 μm. The thickness of the case 8 is about 9mm, for example, 8.5mm to 9.5 mm. Thus, the housing 8 is thick and therefore hard. The thickness of the divided core 70 is about 0.35mm, for example, 0.3mm to 0.4mm, and the yoke width W is about 10mm, for example, 9.5mm to 10.5 mm. The split core 70 is relatively thin and therefore flexible. This can strongly apply stress at the time of shrink fitting of the stator 7.

Fig. 10 is a development view showing a plurality of divided cores 70 according to embodiment 1. Fig. 10 is a view of the stator 7 in a state in which the housing 8 is cut approximately halfway in the height direction and fixed by shrink fitting, as viewed horizontally. As shown in fig. 10, the stator 7 of the compressor 43 manufactured under the above-described manufacturing conditions is not horizontal but undulated when viewed horizontally. That is, the plurality of divided cores 70 have extending portions 73 whose both end portions extend along the shaft portion 4. The extending portions 73 deform the vicinity of the boundaries between the split cores 70 in the axial direction due to stress when the split cores 70 are heat-fitted to the housing 8.

The extension 73 is not easily visually confirmed, but can be visually confirmed by enlarging it. In addition, the extension 73 can be confirmed by touching the surface with a finger or the like. In embodiment 1, the extension portion 73 extends toward the compression portion 35 and is recessed toward the auxiliary frame 19, but the extension portion 73 may extend along the auxiliary frame 19 and be recessed toward the compression portion 35. The extension portion 73 may be provided on either the compression portion 35 side or the auxiliary frame 19 side.

(operation of compressor 43)

Next, the operation of the compressor 43 will be described. When a power supply terminal (not shown) provided in the housing 8 is energized, the stator 7 and the rotor 6 generate torque, and the shaft 4 rotates. The shaft portion 4 rotates, and the orbiting scroll 2 eccentrically revolves while its rotation is restricted by the oldham ring 20. The refrigerant sucked into the low-pressure space 17 of the housing 8 from the suction pipe 5 is taken into the outer peripheral compression chamber 9 among the plurality of compression chambers 9 formed between the first scroll 1b of the fixed scroll 1 and the second scroll 2b of the orbiting scroll 2. Then, the compression chamber 9 into which the refrigerant is taken compresses the refrigerant by decreasing its volume while moving from the outer peripheral side to the center side in accordance with the eccentric rotation of the orbiting scroll 2. The compressed refrigerant is discharged from a discharge port 1a formed in the fixed scroll 1 into the high-pressure space 14 against the valve retainer 10, and is discharged from a discharge pipe 13 to the outside of the casing 8.

(operation of air conditioner 100)

Next, the operation of the air conditioner 100 will be described. The refrigerant sucked into the compressor 43 is compressed by the compressor 43 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure refrigerant in a gas state discharged from the compressor 43 flows into the outdoor heat exchanger 44 functioning as a condenser, and is condensed and liquefied in the outdoor heat exchanger 44 by heat exchange with the outdoor air sent by the outdoor air-sending device 44a. The condensed refrigerant in the liquid state flows into the expansion unit 45, and is expanded and decompressed in the expansion unit 45 to become a low-temperature, low-pressure refrigerant in a gas-liquid two-phase state. Then, the refrigerant in the gas-liquid two-phase state flows into the indoor heat exchanger 46 functioning as an evaporator, and exchanges heat with the indoor air sent by the indoor air-sending device 46a in the indoor heat exchanger 46, evaporates, and gasifies. At this time, the indoor air is cooled to perform cooling in the room. The evaporated refrigerant in a low-temperature and low-pressure gas state is sucked into the compressor 43.

Here, for example, in an operation in which the difference between the suction temperature and the discharge temperature of the refrigerant sucked into the compressor 43 is large, the refrigerant discharged from the discharge pipe 13 becomes high in temperature. Further, the operation in which the difference between the suction temperature and the discharge temperature is large is a high compression ratio operation in which the differential pressure between the high pressure and the low pressure is large. In this case, the refrigerant in a liquid state or a gas-liquid two-phase state flowing on the outlet side of the outdoor heat exchanger 44 is injected into the compression chamber 9 of the compressor 43, whereby the discharge temperature decreases. The high-pressure refrigerant flowing out of the outdoor heat exchanger 44 is decompressed to an intermediate pressure by controlling the throttle expansion coefficient and the flow rate by the ejector expansion unit 51 and the electromagnetic valve 52. The liquid refrigerant decompressed to the intermediate pressure flows into the compressor 43 from the injection pipe 15. The liquid refrigerant flowing into the compressor 43 passes through the injection distribution passage 15a formed in the fixed scroll 1 and is injected into the compression chamber 9 through the injection port 16. Thereby, the refrigerant in the liquid state cools the refrigerant in the gas state during compression in the compression chamber 9.

When the intermediate-pressure refrigerant is injected into the compression chamber 9, the pressure in the casing 8 is filled with a low pressure due to the low-pressure refrigerant flowing from the suction pipe 5 during operation. However, during the stop, the refrigerant in the intermediate pressure state is introduced from the injection port 16 to become the intermediate pressure. When the refrigerant is carbon dioxide, the pressure in the casing 8 varies over a wide range of 1MPa to 10 MPa. The housing 8 expands or contracts due to pressure fluctuations inside. This changes the apparent interference between the core 61 of the stator 7 and the inner surface of the housing 8. If the interference becomes small, the fixing force of the stator 7 becomes weak and cannot be held by the housing 8. Therefore, when the core 61 is thermally mounted to the housing 8, the initial interference is set large, and the stator 7 can be prevented from falling off after the housing 8 expands, but excessive stress is applied to the core 61.

According to embodiment 1, the plurality of divided cores 70 of the stator 7 have the extending portions 73 in which the divided portions 74 at both ends extend along the shaft portion 4. Therefore, when the housing 8 is expanded at a high pressure, the split core 70 extends in the radial direction of the housing 8 by the amount of contraction of the front end of the extension portion 73. Therefore, even if the inside of the housing 8 is expanded, the outer diameter of the stator 7 having the plurality of divided cores 70 follows the expanded diameter. Therefore, the stator 7 can be prevented from dropping out regardless of the pressure in the case 8, and the application of excessive stress to the divided core 70 can be prevented. This can realize the motor 36 and the compressor 43 with high efficiency and high reliability. Further, since the motor 36 is stably operated, it is possible to suppress unpleasant vibration, noise, and the like due to discontinuity of the motor 36.

Conventionally, when the initial interference is set large when the core 61 is thermally mounted on the housing 8, the magnetic characteristics of the core 61 of the stator 7 of the motor 36 are deteriorated, and a reduction in the rotational efficiency and a reduction in the reliability are caused. In contrast, in embodiment 1, since the core 61 of the stator 7 of the motor 36 includes the plurality of divided cores 70, even if the external interference is large in a state where the pressure in the housing 8 is low and the stator contracts, the extension portion 73 is deformed in the axial direction to relax the stress applied to the core 61. By relaxing the stress, the magnetic characteristics of the core 61 can be maintained. In a state where the pressure in the case 8 is high and the case is expanded, the degree of deformation of the extension portion 73 is small, and the interference of the appearance is increased. Thereby, the stator 7 can obtain an appropriate holding force.

In general, the strength of the core 61 of the concentrated winding type stator 7 is weaker than that of the core 61 of the distributed winding type stator 7 of comparative example 1. Therefore, an excessive stress may be applied to the core 61, which deteriorates the magnetic characteristics of the core 61, reduces the efficiency of the motor 36, and may cause damage to the winding wire 63 due to deformation of the core 61. As described above, embodiment 1 can alleviate the stress applied to the core 61 by having the extension portion 73. Therefore, even in the stator 7 of the concentrated winding system, the magnetic characteristics of the core 61 are maintained, and the efficiency of the motor 36 is maintained.

Further, although embodiment 1 exemplifies a case where the air conditioner 100 performs the cooling operation, a flow path switching device that switches the direction in which the refrigerant flows may be provided in the refrigerant circuit 40. This enables the air-conditioning apparatus 100 to perform a heating operation.

As described above, the number of the plurality of divided cores 70 is equal to the number of coils of the winding 63. In this way, in the annular core 61, the coil and the extending portion 73 are uniformly arranged in a circumferential shape. The excitation force of the motor 36 can be made uniform. Therefore, the vibration and noise of the motor 36 are made uniform. Therefore, noise and vibration due to pressure fluctuation can be reduced.

Description of the reference numerals

A fixed scroll; a discharge port; a first vortex body; a first platen; an oscillating scroll; a second vortex body; a second platen; a concave bearing; a frame; a bearing portion; a shaft portion; an eccentric pin portion; a suction tube; a rotor; 7. 7a, 7b. A housing; a compression chamber; 10.. a valve press; a valve; an oil reservoir; a discharge pipe; a plenum; injection piping; a jet dispensing flowpath; a jet port; a low pressure space; an auxiliary frame; a secondary bearing; a euro-ring; an oil pump; an oil circuit; a compression portion; a motor; a refrigerant circuit; an outdoor unit; an indoor unit; a compressor; an outdoor heat exchanger; an outdoor blower; 45.. an expansion portion; an indoor heat exchanger; an indoor blower; a control device; refrigerant tubing; an intermediate injection circuit; injecting an expansion part; a solenoid valve; 61. an iron core; a unitary core; 62.

teeth

62a, 62b.. tooth; 63. 63a, 63b.. winding; 64. a socket; 65.. a winding nozzle; segmenting the iron core; 71.. an iron core; a tooth portion; 73.. an extension; a partition; an air conditioning apparatus.

Claims

1. A compressor is characterized by comprising:

a housing constituting a casing;

a motor disposed inside the housing;

a compression unit that is provided inside the casing and is driven by the motor to compress a refrigerant; and

a shaft portion that connects the motor and the compression portion and transmits a rotational force of the motor to the compression portion,

the motor has:

a stator provided on an inner surface of the housing and having a plurality of divided cores arranged in a circumferential shape; and

a rotor provided on an inner peripheral side of the plurality of divided cores of the stator and rotated by the stator,

the plurality of divided cores have extending portions each having both ends extending along the shaft portion.

2. The compressor of claim 1,

the number of the plurality of divided cores is equal to the number of coils wound.

3. Compressor according to claim 1 or 2,

the motor is provided in a low-pressure space on a low-pressure side where the refrigerant is sucked in the casing.

4. A compressor according to any one of claims 1 to 3,

the plurality of divided cores are wound in a concentrated winding manner in which wires are wound in a concentrated manner.

5. The compressor according to any one of claims 1 to 4,

the refrigerant is CO₂Or comprises CO₂The refrigerant of (1).

6. The compressor according to any one of claims 1 to 5,

the compressor further includes an injection pipe provided in the casing and configured to introduce the refrigerant in a liquid state or a gas-liquid two-phase state into the compression portion.

7. The compressor according to any one of claims 1 to 6,

the stator is fixed to the housing by shrink fitting,

the thermal charging margin obtained by subtracting the inner diameter of the shell from the outer diameter of the stator is 125-175 μm.

8. The compressor according to any one of claims 1 to 7,

the wall thickness of the shell is 8.5 mm-9.5 mm.

9. The compressor according to any one of claims 1 to 8,

the thickness of the divided iron core is 0.3 mm-0.4 mm.

10. The compressor according to any one of claims 1 to 9,

the yoke width, which is the length in the radial direction of the core portion of the core formed by arranging the plurality of divided cores, is 9.5mm to 10.5 mm.