WO2022249274A1

WO2022249274A1 - Compressor

Info

Publication number: WO2022249274A1
Application number: PCT/JP2021/019768
Authority: WO
Inventors: 雷人河村; 一喜小林; 渉岩竹
Original assignee: 三菱電機株式会社
Priority date: 2021-05-25
Filing date: 2021-05-25
Publication date: 2022-12-01
Also published as: JPWO2022249274A1

Abstract

This compressor comprises: a container constituting the outline of the compressor; an electrically operated mechanism provided inside the container; a main shaft that is attached to the electrically operated mechanism and transmits rotational force of the electrically operated mechanism; a fixed scroll having a fixed base plate fixed to inside the container, and fixed spiral teeth provided to the fixed base plate and flattened in one direction; an orbiting scroll having an orbiting base plate connected to an upper end of the main shaft, and orbiting spiral teeth that orbit by means of the rotational force of the electrically operated mechanism and form a compression chamber together with the fixed spiral teeth, the orbiting spiral teeth being flattened in one direction; and a tip seal which is provided on the upper portion of the fixed spiral teeth and the upper portion of the orbiting spiral teeth, and which seals the space between the fixed spiral teeth and the orbiting base plate, and the space between the orbiting spiral teeth and the fixed base plate, wherein a thick-walled portion that overlaps with a major axis on the fixed spiral teeth and overlaps with a major axis on the orbiting spiral teeth has a thick outer wall provided to an outer end in the width direction on the upper end surface of the thick-walled portion, the thick outer wall and extending in a direction away from the upper end surface, and a thick inner wall provided to an inner end in the width direction on the upper end surface of the thick-walled portion, extending in a direction away from the upper end surface, and forming a thick groove into which the tip seal is inserted between the thick outer wall and the thick inner wall.

Description

compressor

The present disclosure relates to a compressor that compresses refrigerant.

Conventionally, a scroll compressor is known as a compressor used in air conditioners, refrigerators, etc. to compress refrigerant. A scroll compressor has a container, and a compression mechanism portion that is housed in the container and compresses a refrigerant in a compression chamber that is formed by combining a fixed scroll and an orbiting scroll. The fixed scroll is provided with fixed spiral teeth on a fixed base plate, and the oscillating scroll is provided with oscillating spiral teeth on an oscillating base plate. The compression chamber is formed by meshing fixed spiral teeth and oscillating spiral teeth. In the scroll compressor, the oscillating movement of the oscillating scroll reduces the volume of the compression chamber and changes the position of the compression chamber, thereby sucking and compressing the refrigerant. In such a scroll compressor, a technique has been proposed in which the suction volume of the compression chamber is increased as much as possible without changing the diameter of the container, thereby increasing the compression capacity while reducing the size and cost. By devising the spiral shapes of the fixed spiral tooth and the oscillating spiral tooth, the suction volume of the compression chamber can be increased without changing the diameter of the container.

A scroll compressor generally contacts the tip of one spiral tooth and the bottom of the other spiral tooth. However, in the compression process, a difference in the amount of thermal expansion of the spiral tooth occurs due to the temperature difference between the winding start and the winding end of the spiral tooth. In addition, the spiral tooth deforms due to a change in the load acting on the back surface of the spiral tooth. As a result, minute gaps are formed at the tips of the spiral teeth, and compressed gas such as refrigerant may leak in the compression chamber. For the purpose of solving this problem, Patent Literature 1 discloses a scroll compressor in which spiral teeth are processed in advance so that the height of the spiral teeth becomes lower toward the center. Patent document 1 attempts to align the heights of the spiral teeth after thermal expansion.

However, in the scroll compressor according to Patent Document 1, when the temperature difference between the winding end and the winding start of the spiral teeth is lower than the assumed value, the amount of thermal expansion is small and deformation is difficult. In this case, since a gap remains between the tip and bottom of the spiral tooth, the refrigerant may leak from the compression chamber, degrading the performance of the compressor. In addition, if the temperature difference between the winding end and the winding start of the spiral tooth is higher than an assumed value, the amount of thermal expansion is large and deformation is likely to occur. In this case, the height of the central spiral tooth is too high, and a gap is generated between the tooth tip and the tooth bottom of the outer peripheral spiral tooth. As a result, the refrigerant may leak from the compression chamber, degrading the performance of the compressor.

For the purpose of solving the problem described in Patent Document 1, there are cases where a tip seal is generally installed to suppress leakage of refrigerant from the tips of the spiral teeth. However, since grooves need to be formed in the spiral teeth to install the tip seal, the contact area of the tip of the tooth decreases and the contact surface pressure increases, reducing the reliability of the compressor. There is a risk. On the other hand, if an attempt is made to increase the tooth thickness of the spiral teeth to secure the contact area, the ratio of the spiral teeth occupying the effective space in the horizontal direction increases. For this reason, the suction volume, which is the effective compression chamber volume, is reduced, and there is a risk that the performance of the compressor will be reduced.

In order to solve this problem, Patent Document 2 discloses a scroll compressor in which side walls forming grooves for holding tip seals are provided only on the outside of spiral teeth. Patent document 2 attempts to secure a contact area by reducing the tooth thickness.

JP-A-58-133491 JP-A-11-230064

However, in the scroll compressor disclosed in Patent Document 2, there is a risk that the tip seal will deform or come off due to sliding of the tooth tips or fluctuations in the pressure inside the compression chamber. That is, Patent Document 2 has a problem with the retention of the tip seal.

The present disclosure has been made to solve the above problems, and aims to provide a compressor that improves the retention of the tip seal while ensuring the contact area.

A compressor according to the present disclosure includes a container forming an outer shell, an electric mechanism provided inside the container, a main shaft attached to the electric mechanism and transmitting a rotational force of the electric mechanism, and fixed inside the container. a fixed scroll provided on the fixed base plate and having fixed spiral teeth flattened in one direction; a rocking base plate connected to the upper end of the main shaft; and an oscillating scroll having an oscillating spiral tooth flattened in one direction to form a compression chamber together with the fixed spiral tooth, and a fixed chip seals for sealing between the spiral tooth and the oscillating bedplate and between the oscillating spiral tooth and the fixed bedplate, overlapping the major axis at the stationary spiral tooth and overlapping the major axis at the oscillating spiral tooth. The thick portion is provided at the outer end in the width direction of the upper end face and extends away from the upper end face, and the thick outer wall is provided at the inner end in the width direction of the upper end face and extends away from the upper end face. and a thick inner wall forming a thick groove between the thick outer wall and into which the tip seal is inserted.

According to the present disclosure, the fixed spiral tooth and the oscillating spiral tooth are flattened in one direction, and the portion of the fixed spiral tooth that overlaps with the major axis and the portion of the oscillating spiral tooth that overlaps with the major axis becomes the thick portion. there is Here, a sufficient contact area can be secured in the thick portion. A tip seal is inserted into a thick groove formed between a thick outer wall and a thick inner wall of the thick portion. That is, since the thick outer wall and the thick inner wall are provided on both sides of the tip seal, the tip seal is highly retainable. In this way, it is possible to improve the retention of the tip seal while ensuring the contact area.

1 is a circuit diagram showing a refrigeration cycle apparatus according to Embodiment 1; FIG. 1 is an axial sectional view showing a compressor according to Embodiment 1; FIG. 1 is a circumferential cross-sectional view showing a compressor according to Embodiment 1; FIG. 4 is a diagram showing rotation phases of an orbiting scroll of the compressor according to Embodiment 1. FIG. FIG. 5 is a diagram showing the state of the oscillating spiral tooth according to Embodiment 1; 1 is an axial sectional view showing a compressor according to Embodiment 1; FIG. FIG. 4 is a schematic diagram showing a thick portion and a thin portion according to Embodiment 1; FIG. 7 is a circumferential cross-sectional view showing a compressor according to Embodiment 2; FIG. 10 is a diagram showing a state of an oscillating spiral tooth according to Embodiment 2; FIG. 11 is a circumferential cross-sectional view showing a compressor according to Embodiment 3;

Hereinafter, embodiments of the compressor of the present disclosure will be described with reference to the drawings. It should be noted that the present disclosure is not limited by the embodiments described below. In addition, in the following drawings, including FIG. 1, the size relationship of each constituent member may differ from the actual one. In addition, in the following description, directional terms are used as appropriate to facilitate understanding of the present disclosure, but this is for the purpose of describing the present disclosure, and these terms are intended to limit the present disclosure. is not. Directional terms include, for example, "up", "down", "right", "left", "front" or "back".

Embodiment 1.
FIG. 1 is a circuit diagram showing a refrigeration cycle apparatus 100 according to Embodiment 1. FIG. The refrigeration cycle device 100 is, for example, an air conditioner that adjusts air in an indoor space, and includes an outdoor unit 102 and an indoor unit 103 as shown in FIG. The outdoor unit 102 is provided with, for example, a compressor 1 , a channel switching device 107 , an outdoor heat exchanger 108 , an outdoor fan 109 and an expansion section 110 . The indoor unit 103 is provided with, for example, an indoor heat exchanger 111 and an indoor fan 112 . Note that the refrigeration cycle device 100 is not limited to an air conditioner, and may be a refrigerator.

A refrigerant circuit 104 is configured by connecting the compressor 1 , the flow switching device 107 , the outdoor heat exchanger 108 , the expansion section 110 and the indoor heat exchanger 111 by refrigerant pipes 105 . The compressor 1 sucks a low-temperature, low-pressure refrigerant, compresses the sucked refrigerant, converts it into a high-temperature, high-pressure refrigerant, and discharges it. The compressor 1 is, for example, a capacity-controllable inverter compressor. The channel switching device 107 switches the direction in which the refrigerant flows in the refrigerant circuit 104, and is, for example, a four-way valve. The outdoor heat exchanger 108 exchanges heat, for example, between outdoor air and refrigerant. The outdoor heat exchanger 108 acts as a condenser during cooling operation and acts as an evaporator during heating operation. The expansion unit 110 is a pressure reducing valve or an expansion valve that reduces the pressure of the refrigerant to expand it. The expansion part 110 is, for example, an electronic expansion valve whose opening is adjusted.

The indoor heat exchanger 111 exchanges heat, for example, between indoor air and refrigerant. The indoor heat exchanger 111 acts as an evaporator during cooling operation, and acts as a condenser during heating operation. The indoor fan 112 is a device that sends indoor air to the indoor heat exchanger 111 .

(Operating mode, cooling operation)
Next, operation modes of the refrigeration cycle apparatus 100 will be described. First, the cooling operation will be explained. In the cooling operation, the refrigerant sucked into the compressor 1 is compressed by the compressor 1 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 passes through the flow switching device 107 and flows into the outdoor heat exchanger 108 acting as a condenser. It is heat-exchanged with outdoor air sent by 109 to condense and liquefy. The condensed liquid refrigerant flows into the expansion section 110 and is expanded and decompressed in the expansion section 110 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. Then, the gas-liquid two-phase refrigerant flows into the indoor heat exchanger 111 acting as an evaporator, and in the indoor heat exchanger 111, heat is exchanged with the indoor air sent by the indoor blower 112 to evaporate and gasify. do. At this time, the indoor air is cooled, and cooling is performed in the room. The vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching device 107 and is sucked into the compressor 1 .

(Operating mode, heating operation)
Next, the heating operation will be explained. In the heating operation, the refrigerant sucked into the compressor 1 is compressed by the compressor 1 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 passes through the flow path switching device 107 and flows into the indoor heat exchanger 111 acting as a condenser. It is heat-exchanged with the room air sent by 112 to condense and liquefy. At this time, the indoor air is warmed, and heating is performed in the room. The condensed liquid refrigerant flows into the expansion section 110 and is expanded and decompressed in the expansion section 110 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. Then, the gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 108 acting as an evaporator, where it is heat-exchanged with the outdoor air sent by the outdoor blower 109 to evaporate and gasify. do. The vaporized low-temperature, low-pressure gaseous refrigerant passes through the flow path switching device 107 and is sucked into the compressor 1 .

Note that the refrigeration cycle device 100 does not have to have the channel switching device 107 . In this case, the refrigeration cycle device 100 becomes a dedicated cooling machine or a dedicated heating machine.

FIG. 2 is an axial sectional view showing the compressor 1 according to Embodiment 1. FIG. Next, the compressor 1 will be explained in detail. The compressor 1 sucks and compresses the refrigerant circulating in the refrigerant circuit 104, for example, and discharges the refrigerant in a high-temperature and high-pressure state, and is, for example, a hermetic scroll compressor. As shown in FIG. 2, the compressor 1 includes a container 2, a frame 14, a sub-frame 16, a main shaft 30, a main bearing 17, a sub-bearing 18, a suction pipe 51, a discharge pipe 52, a compression and a mechanism section 10 . The compressor 1 also includes an Oldham ring 40 , an oil pump 19 , and an electric mechanism section 20 .

The container 2 is a closed container that constitutes the outer shell of the compressor 1 and has a cylindrical shape. Inside the container 2, the compression mechanism section 10, the electric mechanism section 20, and other parts are accommodated. Inside the container 2, the compression mechanism section 10 is arranged above and the electric mechanism section 20 is arranged below. A bottom portion 43 of the container 2 is formed with an oil reservoir portion 2a that stores refrigerating machine oil.

The frame 14 is fixed to the container 2 and accommodates the compression mechanism section 10, and rotatably supports the main shaft 30 via main bearings 17, for example. The frame 14 is arranged above the electric mechanism portion 20 and positioned between the electric mechanism portion 20 and the compression mechanism portion 10 . A discharge pipe 52 is connected to the inside of the frame 14 . The compressed refrigerant passes through the frame 14 and is discharged from the discharge pipe 52 .

The subframe 16 is arranged below the electric mechanism section 20 inside the container 2 . The subframe 16 rotatably supports the main shaft 30 via the subbearing 18 . The frame 14 and the sub-frame 16 are fixed inside the container 2 so as to face each other with the electric mechanism section 20 interposed therebetween. The frame 14 and subframe 16 are fixed to the inner peripheral surface of the container 2 by shrink fitting, welding, or the like. The main shaft 30 is supported by the frame 14 at the center of the container 2 and is a rod-shaped crankshaft extending vertically, and connects the electric mechanism section 20 and the compression mechanism section 10 .

The main shaft 30 connects the electric mechanism portion 20 and the compression mechanism portion 10 to transmit the rotational force of the electric mechanism portion 20 to the compression mechanism portion 10 . A rocking bed plate 12 a of the rocking scroll 12 is provided at the upper end of the main shaft 30 . The main shaft 30 has an eccentric shaft portion 31 and a main shaft portion 30a. The eccentric shaft portion 31 is eccentric with respect to the axis of the main shaft 30 and is rotatably accommodated in the rocking bearing 15 . The outer peripheral portion of the eccentric shaft portion 31 is in close contact with the inner peripheral portion of the swing bearing 15 via the refrigerator oil. The main shaft portion 30 a is supported by a main bearing 17 provided on the frame 14 . A rotor of the electric mechanism portion 20 is fixed to the main shaft portion 30a by shrink fitting or the like. An oil passage 32 through which oil passes is formed inside the main shaft 30 . The main bearing 17 is provided in the central portion of the frame 14 and supports the upper portion of the main shaft 30 so as to be rotatable. The sub-bearing 18 is press-fitted into the central portion of the sub-frame 16 and supports the lower portion of the main shaft 30 so as to be rotatable.

The suction pipe 51 is connected to the first space 72 formed in the fixed scroll 11 of the compression mechanism section 10 on the side of the container 2 . The suction pipe 44 sucks the low-pressure refrigerant flowing from the refrigerant pipe 105 into the first space 72 . The discharge pipe 52 is connected to the space formed in the frame 14 on the side of the container 2 . The discharge pipe 52 discharges the high-pressure refrigerant compressed by the compression mechanism section 10 to the refrigerant pipe 105 outside the compressor 1 .

The compression mechanism section 10 compresses the refrigerant sucked from the suction pipe 51 and discharges it outside the compression mechanism section 10 inside the container 2 . The compression mechanism section 10 has a fixed scroll 11 and an orbiting scroll 12 . The fixed scroll 11 is fixed to the container 2 above the orbiting scroll 12, and has a fixed base plate 11a and fixed spiral teeth 11b. The fixed base plate 11 a is a plate-like member and constitutes the upper surface of the compression mechanism section 10 . A discharge port 13 is formed in the central portion of the fixed base plate 11a, and a first space 72 is formed on the side of the fixed base plate 11a. The fixed spiral tooth 11b is a spiral protrusion extending downward from the lower surface of the fixed base plate 11a.

The orbiting scroll 12 has an orbiting base plate 12a and an orbiting spiral tooth 12b. The rocking plate 12 a is a plate-like member arranged above the frame 14 . The oscillating spiral tooth 12b is a spiral projection extending upward from the upper surface of the oscillating base plate 12a. The fixed scroll 11 and the orbiting scroll 12 are provided inside the container 2 with the fixed spiral teeth 11b and the orbiting spiral teeth 12b meshing with each other. The fixed spiral tooth 11b and the oscillating spiral tooth 12b are formed following an involute curve. A plurality of compression chambers 60 are formed between the teeth 12b. When the orbiting scroll 12 is oscillating, the oscillating spiral teeth 12b float in the axial direction, so that the fixed spiral teeth 11b and the oscillating spiral teeth 12b mesh with each other to form compression chambers 60. As shown in FIG.

A swing bearing 15 is provided between the swing scroll 12 and the eccentric shaft portion 31 . The swing bearing 15 covers the main shaft 30 and the eccentric shaft portion 31 and supports the main shaft 30 rotatably. The eccentric shaft portion 31 is provided at the upper end of the main shaft 30 and eccentrically rotates the orbiting scroll 12 . The Oldham ring 40 is provided on the thrust surface of the orbiting scroll 12 opposite to the surface on which the orbiting spiral teeth 12b are formed. The Oldham ring 40 prevents the orbiting scroll 12 from rotating during the eccentric orbiting motion, and allows the orbiting scroll 12 to revolve. The upper and lower surfaces of the Oldham's ring 40 are provided with claws (not shown) projecting perpendicularly to each other. The claws of the Oldham ring 40 are inserted into Oldham grooves 41 (see FIG. 3) formed in the orbiting scroll 12 and frame 14 .

The oil pump 19 is accommodated in the bottom portion 43 of the container 2 and sucks up oil from the oil reservoir portion 2a. The oil pump 19 is fixed to the lower portion of the main shaft 30 . The oil pump 19 sucks up the oil stored in the oil reservoir 2 a into an oil passage 32 formed inside the main shaft 30 and supplies the oil to the auxiliary bearing 18 , the main bearing 17 and the oscillating bearing 15 through the oil passage 32 . Note that the oil pump 19 may be omitted. In this case, for example, a configuration is adopted in which oil is sucked up from the oil reservoir portion 2a using differential pressure.

The electric mechanism part 20 is provided in the lower part inside the container 2 . The electric mechanism section 20 drives the orbiting scroll 12 that constitutes the compression mechanism section 10 . That is, the motor-driven mechanism section 20 rotates the orbiting scroll 12 via the main shaft 30 , thereby compressing the refrigerant in the compression mechanism section 10 . The electric mechanism section 20 has a rotor 21 and a stator 22 . The rotor 21 is provided inside the stator 22 . The rotor 21 is rotationally driven by energizing the stator 22 to rotate the main shaft 30 . The rotor 21 is fixed to the outer periphery of the main shaft 30 and held with a small gap from the stator 22 .

(Operation of compressor 1)
Next, operation of the compressor 1 will be described. When a power supply terminal (not shown) provided on the container 2 is energized, current flows through the coils of the stator 22 to generate a magnetic field. Due to the magnetic field generated in the stator 22, the main shaft portion 30a passing through the rotor 21 rotates. When the main shaft portion 30a rotates, the eccentric shaft portion 31 rotates eccentrically, and the orbiting scroll 12 eccentrically orbits with the oscillation radius while its rotation is restricted by the Oldham ring 40. FIG. Here, the swing radius refers to the amount of eccentricity of the eccentric shaft portion 31 with respect to the main shaft portion 30a.

The low-pressure refrigerant flowing out of the indoor heat exchanger 111 is sucked into the first space 72 of the fixed base plate 11 a of the container 2 through the suction pipe 51 . The low-pressure refrigerant that has flowed into the first space 72 flows into the second space 73 through two openings (not shown) provided in the frame 14 . The low-pressure refrigerant that has flowed into the second space 73 is sucked into the compression chamber 60 as the oscillating spiral tooth 12b oscillates relative to the fixed spiral tooth 11b. As the orbiting scroll 12 eccentrically revolves, the compression chamber 60 that has taken in the refrigerant decreases in volume while moving from the outer circumference to the center, thereby compressing the refrigerant.

At that time, the refrigerant is boosted from a low pressure to a high pressure due to the geometric volume change of the compression chamber 60 caused by the relative oscillating motion of the oscillating spiral tooth 12b with respect to the fixed spiral tooth 11b. The compressed high-pressure refrigerant passes through the discharge port 13 of the fixed scroll 11 and the through hole 61 a of the baffle 61 , pushes the discharge valve 62 open, and is discharged into the discharge muffler 63 . The high-pressure refrigerant discharged into the discharge muffler 63 flows into the third space 74 and is discharged from the compressor 1 through the discharge pipe 52 . The third space 74 and the discharge pipe 52 communicate with each other through the frame 14 and the like.

FIG. 3 is a circumferential cross-sectional view showing the compressor 1 according to Embodiment 1. FIG. As shown in FIG. 3 , the container 2 has a circular cross section in the circumferential direction, and inside the container 2 , the outer peripheral surface of the frame 14 is fixed in contact with the inner peripheral surface of the container 2 . Thus, the outer peripheral surface of the frame 14 is also perfectly circular. A fixed scroll 11 and an orbiting scroll 12 are arranged in the second space 73 of the frame 14 . An Oldham groove 41 in which the Oldham ring 40 is provided is formed in the second space 73 . Here, the rocking plate 12a is flattened in one direction. Here, the term "flat" includes an oval shape and an elliptical shape, and refers to a shape that is flatter than a circular shape. The Oldham's groove 41 is arranged on the short axis side of the rocking plate 12a. Therefore, the rocking rocking plate 12a and the Oldham's groove 41 do not interfere with each other.

As shown in FIG. 3, the fixed spiral tooth 11b and the oscillating spiral tooth 12b are flattened in one direction. As described above, since the rocking bed plate 12a is also flat, the space on the rocking bed plate 12a can be effectively utilized by flattening the rocking spiral teeth 12b provided on the rocking bed plate 12a. be able to. Thus, by increasing space efficiency, the volume of the compression chamber 60 can be increased without changing the size of the container 2 . Therefore, the performance of the compressor 1 can be improved. Further, the size of the container 2 can be reduced while maintaining the performance of the compressor 1 . In the following description, when both the fixed spiral tooth 11b and the oscillating spiral tooth 12b are shown without distinction, they are collectively referred to as spiral teeth. In addition, in the following description, when both the fixed base plate 11a and the rocking base plate 12a are shown without distinction, they are collectively referred to as base plates.

Here, tip seals 50 are provided above the fixed spiral teeth 11b and above the oscillating spiral teeth 12b. Here, the upper portion of the fixed spiral tooth 11b and the upper portion of the oscillating spiral tooth 12b are the tip of the fixed spiral tooth 11b and the tip of the oscillating spiral tooth 12b, respectively. The tip seal 50 seals between the fixed spiral tooth 11b and the oscillating base plate 12a and between the oscillating spiral tooth 12b and the fixed base plate 11a. The tip seal 50 is inserted into grooves formed in the upper end faces of the fixed spiral tooth 11b and the oscillating spiral tooth 12b. That is, the tip seal 50 is also flattened in one direction like the fixed spiral tooth 11b and the oscillating spiral tooth 12b. The degree of flatness of the tip seal 50 may be different from the degree of flatness of the fixed spiral tooth 11b and the oscillating spiral tooth 12b.

FIG. 4 is a diagram showing the rotational phases of the orbiting scroll 12 of the compressor 1 according to Embodiment 1. FIG. FIG. 4(a) shows the positions of spiral teeth at a rotational phase of 0 (2π) [rad], and FIG. 4(b) shows the positions of spiral teeth at a rotational phase of π/2 [rad]. FIG. 4(c) shows the positions of the spiral teeth at the rotational phase of π [rad], and FIG. 4(d) shows the positions of the spiral teeth at the rotational phase of 3π/2 [rad]. In this way, when the spiral shape of the spiral tooth is flat, when the oscillating spiral tooth 12b operates with a constant oscillating radius, the outward surface and the inward surface of the oscillating spiral tooth 12b face each other. It contacts the inward and outward surfaces of 11b.

At this time, the compression mechanism section 10 takes in low-temperature gas from the outer peripheral portion of the container 2, gradually compresses it into high-temperature and high-pressure gas, and discharges it from the central portion. For this reason, a temperature difference and a pressure difference occur between the outer peripheral portion at the end of the winding of the fixed spiral tooth 11b and the oscillating spiral tooth 12b and the central portion at the start of winding. As a result, the deformation amounts of the fixed spiral tooth 11b and the oscillating spiral tooth 12b change between the outer peripheral portion and the central portion. Therefore, there is a difference in height between the fixed spiral tooth 11b and the oscillating spiral tooth 12b.

FIG. 5 is a diagram showing the state of the oscillating spiral tooth 12b according to Embodiment 1. FIG. Next, shape changes due to temperature changes and load changes acting on the oscillating spiral tooth 12b will be described. FIG. 5(a) is a diagram showing a state in which the oscillating spiral tooth 12b is not deformed, and FIG. 5(b) is a diagram showing a state in which the oscillating spiral tooth 12b is deformed by thermal expansion. 5(c) is a diagram showing a state in which the rocking base plate 12a supporting the rocking spiral tooth 12b is curved and deformed. As shown in FIG. 5A, when the oscillating spiral tooth 12b is not deformed, or when the amount of deformation of the oscillating spiral tooth 12b is small, the tip of one spiral tooth and the other spiral tooth A concave gap that widens toward the center is formed between it and the tooth root. At this time, the tip seal 50 floats up to fill the gap, thereby suppressing gas leakage from the compression chamber 60 .

On the other hand, as shown in FIGS. 5(b) and 5(c), when the oscillating spiral tooth 12b is deformed, the tip of the spiral tooth in the central portion and the tip of the spiral tooth in the outer peripheral portion The distance in the height direction becomes closer. As a result, the tip of one spiral tooth comes into full contact with the bottom of the other spiral tooth. At this time, the tip seal 50 is inserted inside the groove.

FIG. 6 is an axial sectional view showing the compressor 1 according to Embodiment 1. FIG. As shown in FIG. 6, the fixed spiral tooth 11b and the oscillating spiral tooth 12b have a thickness that increases or decreases, and have a thick portion 81 and a thin portion 91. As shown in FIG. The wall thickness when the rotational phase (extension angle) of the spiral tooth is π/2 [rad] and 3π/2 [rad] than the wall thickness when 0 (2π) [rad] and π [rad] is thicker. That is, the thick portion 81 is a portion that overlaps the major axis of the fixed spiral tooth 11b and overlaps the major axis of the oscillating spiral tooth 12b. Specifically, the thick portion 81 is a portion whose extension angle is in the range of N×π±π/4 [rad]. Here, N is a natural number including 0. The thin portion 91 is a portion that overlaps the minor axis of the fixed spiral tooth 11b and the minor axis of the oscillating spiral tooth 12b. Specifically, the thin portion 91 is a portion whose extension angle is in the range of N×π+π/2±π/4 [rad].

The thick portion 81 has a thick outer wall 82 and a thick inner wall 83 . The thick outer wall 82 is provided at the outer end portion in the width direction of the upper end surface of the thick portion 81 and extends in a direction away from the upper end surface. The thick inner wall 83 is provided at the inner end portion in the width direction of the upper end surface of the thick portion 81 and extends away from the upper end surface. A thick groove 84 into which the tip seal 50 is inserted is formed between the thick outer wall 82 and the thick inner wall 83 . That is, the thick portion 81 has outer walls on both sides of the tip seal 50 .

The thin portion 91 has a thin outer wall 92 . The thin outer wall 92 is provided at the outer end portion in the width direction of the upper end surface and extends in a direction away from the upper end surface. A thin groove 94 into which the tip seal 50 is inserted is formed between the thin outer wall 92 and the inner end in the width direction. That is, the outer wall is provided only on the outside of the tip seal 50 in the thin portion 91 .

FIG. 7 is a schematic diagram showing the thick portion 81 and thin portion 91 according to the first embodiment. FIG. 7 is a schematic diagram representing the oscillating spiral tooth 12b in a straight line. As shown in FIG. 7, the thick outer wall 82 and the thin outer wall 92 have the same height, but the thick inner wall 83 draws a smooth curved surface toward the thin portion 91 and becomes lower. becomes 0. Thus, the height of the thick inner wall 83 changes in a constant cycle with respect to the extension angles of the fixed spiral tooth 11b and the oscillating spiral tooth 12b. The thick outer wall 82 and the thick inner wall 83 have the same height. As a result, it is possible to reduce the leakage loss of gas through the gap between the tip of the spiral tooth on the inner peripheral side where the pressure difference in the compression chamber 60 across the spiral tooth is large. Therefore, the performance of the compressor 1 can be improved. Of the thick outer wall 82 and the thick outer wall 82 , the thicker one may be thicker than the thin outer wall 92 .

Here, the circumferential end of the tip seal 50 is installed in the thin portion 91 . Thereby, the rigidity of the end portion of the groove that holds the tip seal 50 can be ensured. Therefore, it is possible to suppress the deterioration of the reliability of the compressor 1 .

According to the first embodiment, the fixed spiral tooth 11b and the oscillating spiral tooth 12b are flattened in one direction. , and the thick portion 81 . Here, a sufficient contact area can be secured in the thick portion 81 . A chip seal 50 is inserted into a thick groove 84 formed between a thick outer wall 82 and a thick inner wall 83 of the thick portion 81 . That is, since the thick outer wall 82 and the thick inner wall 83 are provided on both sides of the tip seal 50, the tip seal 50 can be highly retained. In this way, it is possible to improve the retention of the tip seal 50 while ensuring the contact area.

Although the first embodiment exemplifies the case where the thin portion 91 has the thin outer wall 92, the thin portion 91 may have a thin inner wall. The thin inner wall is provided at the inner end portion in the width direction of the upper end surface of the thin portion 91, extends away from the upper end surface, and is between the outer end portion in the width direction and the thin groove into which the tip seal 50 is inserted. 94. In this case, the thicker one of the thick outer wall 82 and the thick outer wall 82 may be thicker than the thin inner wall.

Embodiment 2.
FIG. 8 is a circumferential cross-sectional view showing compressor 1 according to Embodiment 2. As shown in FIG. Embodiment 2 is different from Embodiment 1 in that a tip seal 50 is provided at the central portion of fixed spiral tooth 11b and oscillating spiral tooth 12b. In the second embodiment, the same reference numerals are assigned to the same parts as in the first embodiment, and the description thereof is omitted.

As shown in FIG. 8, the tip seal 50 is provided only at the central portion of the fixed spiral tooth 11b and the oscillating spiral tooth 12b, and is not provided at the outer peripheral portion of the fixed spiral tooth 11b and the oscillating spiral tooth 12b. do not have. Here, the central portion refers to the portion in which the extension angle is smaller than 3π [rad], and the outer peripheral portion refers to the portion in which the extension angle is greater than 3π [rad].

FIG. 9 is a diagram showing the state of the oscillating spiral tooth 12b according to the second embodiment. Next, shape changes due to temperature changes and load changes acting on the oscillating spiral tooth 12b will be described. FIG. 9(a) is a diagram showing a state in which the oscillating spiral tooth 12b is not deformed, and FIG. 9(b) is a diagram showing a state in which the oscillating spiral tooth 12b is deformed by thermal expansion. 9(c) is a diagram showing a state in which the rocking base plate 12a supporting the rocking spiral tooth 12b is curved and deformed. As shown in FIG. 9A, when the oscillating spiral tooth 12b is not deformed, or when the amount of deformation of the oscillating spiral tooth 12b is small, the tip of one spiral tooth and the other spiral tooth A concave gap that widens toward the center is formed between it and the tooth root. At this time, the tip seal 50 floats up to fill the gap, thereby suppressing gas leakage from the compression chamber 60 .

On the other hand, as shown in FIGS. 9B and 9C, when the oscillating spiral tooth 12b is deformed, the tip of the spiral tooth in the central portion and the tip of the spiral tooth in the outer peripheral portion The distance in the height direction becomes closer. As a result, the tip of one spiral tooth comes into full contact with the bottom of the other spiral tooth. At this time, the tip seal 50 is inserted inside the groove.

According to the second embodiment, the tip seal 50 is provided at the central portion of the fixed spiral tooth 11b and the oscillating spiral tooth 12b. Therefore, the entire surfaces of the tooth tips of the outer peripheral portions of the fixed spiral tooth 11b and the oscillating spiral tooth 12b can be brought into contact with each other. Therefore, the contact surface pressure acting on the tips of the outer peripheral portions of the fixed spiral tooth 11b and the oscillating spiral tooth 12b can be reduced, so that the reliability of the compressor 1 can be further enhanced. Here, the circumferential end portion of the tip seal 50 is installed in the thin portion 91 . Thereby, the rigidity of the end portion of the groove that holds the tip seal 50 can be ensured. Therefore, it is possible to suppress the deterioration of the reliability of the compressor 1 .

Embodiment 3.
FIG. 10 is a circumferential cross-sectional view showing compressor 1 according to Embodiment 3. As shown in FIG. Embodiment 3 differs from

Embodiments

1 and 2 in that the tip seal 50 is not provided in the thin portion 91 . In the third embodiment, the same reference numerals are given to the parts that are common to the first and second embodiments, and the description thereof is omitted.

As shown in FIG. 10 , the tip seal 50 is provided only on the thick portion 81 and not on the thin portion 91 . As described above, the thick portion 81 has an extension angle of N×π±π/4 [rad], and the thin portion 91 has an extension angle of N×π+π/2±π/4 [rad]. rad].

According to the third embodiment, the tip seal 50 is not provided on the thin portion 91 . Therefore, the amount of tip seal 50 used can be reduced. Therefore, the reliability of the compressor 1 can be improved with less material.

1 Compressor 2 Container 2a Oil reservoir 10 Compression mechanism 11 Fixed scroll 11a Fixed base plate 11b Fixed spiral tooth 12 Oscillating scroll 12a Oscillating bedplate 12b Oscillating spiral tooth 13 Discharge Outlet, 14 frame, 15 rocking bearing, 16 sub-frame, 17 main bearing, 18 sub-bearing, 19 oil pump, 20 electric mechanism, 21 rotor, 22 stator, 30 main shaft, 30a main shaft, 31 eccentric shaft , 32 oil passage, 40 Oldham ring, 41 Oldham groove, 50 chip seal, 51 suction pipe, 52 discharge pipe, 60 compression chamber, 61 baffle, 61a through hole, 62 discharge valve, 63 discharge muffler, 72 first space, 73 Second space 74 Third space 81 Thick part 82 Thick outer wall 83 Thick inner wall 84 Thick groove 91 Thin part 92 Thin outer wall 94 Thin groove 100 Refrigeration cycle device 102 Outdoor unit 103 Indoor unit, 104 Refrigerant circuit, 105 Refrigerant pipe, 107 Flow path switching device, 108 Outdoor heat exchanger, 109 Outdoor blower, 110 Expansion unit, 111 Indoor heat exchanger, 112 Indoor blower.

Claims

a container forming an outer shell;
an electric mechanism provided inside the container;
a main shaft that is attached to the electric mechanism and transmits the rotational force of the electric mechanism;
a fixed scroll having a fixed base plate fixed inside the container and a fixed spiral tooth provided on the fixed base plate and flattened in one direction;
an oscillating bed plate connected to the upper end of the main shaft; and an oscillating spiral tooth that is flattened in one direction and forms a compression chamber together with the fixed spiral tooth by being oscillated by the rotational force of the electric mechanism. an oscillating scroll having
Chip seals provided on the upper portion of the fixed spiral tooth and the upper portion of the oscillating spiral tooth for sealing between the fixed spiral tooth and the oscillating bedplate and between the oscillating spiral tooth and the fixed bedplate. and
The thick portion that overlaps the long axis of the fixed spiral tooth and overlaps the long axis of the oscillating spiral tooth,
a thick outer wall provided at the outer end in the width direction of the upper end surface and extending in a direction away from the upper end surface;
a thick inner wall provided at the inner end in the width direction of the upper end face, extending in a direction away from the upper end face, and forming a thick groove between the thick outer wall and the thick outer wall into which the tip seal is inserted; have a compressor.
The thin portion overlapping the minor axis of the fixed spiral tooth and the minor axis of the oscillating spiral tooth,
The upper end face has a thin outer wall provided at the outer end in the width direction, extending in a direction away from the upper end face, and forming a thin groove between the upper end face and the inner end in the width direction, into which the tip seal is inserted. Item 1. The compressor according to item 1.
The compressor according to claim 2, wherein the thick outer wall and the thick outer wall have a thicker thickness than the thin outer wall.
The thin portion overlapping the minor axis of the fixed spiral tooth and the minor axis of the oscillating spiral tooth,
The upper end face has a thin inner wall provided at the inner end in the width direction, extending in a direction away from the upper end face, and forming a thin groove between the upper end face and the outer end in the width direction, into which the tip seal is inserted. Item 1. The compressor according to item 1.
5. The compressor according to claim 4, wherein a thickness of the thicker one of the thick outer wall and the thick outer wall is thicker than the thin inner wall.
The compressor according to any one of claims 2 to 5, wherein a circumferential end portion of the tip seal is installed in the thin portion.
The compressor according to any one of claims 1 to 6, wherein the flatness of the tip seal is different from the flatness of the fixed spiral tooth and the oscillating spiral tooth.
The tip seal is
The compressor according to any one of claims 1 to 7, wherein the compressor is provided at the central portion of the fixed spiral tooth and the oscillating spiral tooth.
The height of the thick inner wall is
The compressor according to any one of claims 1 to 8, wherein the extension and opening angles of the fixed spiral teeth and the oscillating spiral teeth change at a constant cycle.
The compressor according to any one of claims 1 to 9, wherein the oscillating spiral teeth float in the axial direction so that the fixed spiral teeth and the oscillating spiral teeth mesh with each other to form the compression chambers. .