JP7170887B2 - scroll compressor - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to scroll compressors capable of suppressing temperature rises in compression chambers.

Patent Literature 1 discloses a scroll compressor capable of suppressing a temperature rise in a compression chamber by injecting refrigerant. In the scroll compressor of Patent Document 1, refrigerant is injected through an injection pipe provided in a closed container.

WO2016/199281

The scroll compressor includes a fixed scroll and an oscillating scroll each having spiral teeth, and two compression chambers are formed between the spiral teeth. The fixed scroll of the scroll compressor of Patent Document 1 is provided with two injection ports for evenly distributing the refrigerant injected through the injection pipe to the two compression chambers. However, since the two injection ports are formed at positions separated from each other, it is necessary to provide a separate hole in the fixed scroll for connecting the two injection ports. In addition, the hole needs to be formed by drilling the base plate of the fixed scroll, and a separate sealing member is required to close the hole. Therefore, in the scroll compressor of Patent Document 1, it is necessary to form a hole that connects the two injection ports and then additionally provide a sealing material that closes the hole. there were.

SUMMARY OF THE INVENTION It is an object of the present invention to solve the above-described problems and to provide a scroll compressor capable of reducing manufacturing man-hours.

の関係を満たすように形成されている。
また、本発明のスクロール圧縮機は、低圧の冷媒を圧縮し、高圧の冷媒として吐出させる圧縮ユニットと、前記圧縮ユニットを収容する密閉容器と、前記密閉容器を貫通するインジェクション管とを備え、前記圧縮ユニットは、第１台板と、前記第１台板に設けられた第１渦巻歯とを有する固定スクロールと、前記第１台板と対面した第２台板と、前記第２台板に設けられ、前記第１渦巻歯と噛み合うように配置された第２渦巻歯とを有する揺動スクロールとを備え、前記第１台板と前記第２台板と前記第１渦巻歯と前記第２渦巻歯との間に、一対の圧縮室が形成されるものであり、前記第１台板は、前記第１渦巻歯及び前記第２渦巻歯の位置よりも外側に設けられ、前記インジェクション管と前記一対の圧縮室との間を連通するインジェクション流路を有しており、前記インジェクション流路は、前記インジェクション管からの冷媒が流入する第１流路と、前記第１流路と接続され、前記一対の圧縮室の一方に前記第１流路に流入した冷媒を供給する第２流路と、前記第１流路及び前記第２流路のいずれか一方から分岐し、前記一対の圧縮室の他方に、前記第１流路及び前記第２流路のいずれか一方に流入した冷媒を供給する第３流路とを有しており、前記インジェクション流路は、前記第１渦巻歯の外周側への巻回方向における、前記第１渦巻歯の外周側の末端である巻き終わり部分と前記インジェクション流路との間の角度を変数θ［ｄｅｇｒｅｅ］とした場合、
９０≦θ≦１１０
となる位置に形成されており、前記第２流路は、前記第１渦巻歯の巻き終わり部分と前記第２渦巻歯との間の間隙に向けて、前記一対の圧縮室の一方で圧縮される冷媒を供給する流路であり、前記第３流路は、前記第２渦巻歯の巻き終わり部分と前記第１渦巻歯との間の間隙に向けて、前記一対の圧縮室の他方で圧縮される冷媒を供給する流路であり、前記インジェクション流路の形成位置が、前記一対の圧縮室に均等に冷媒を分配できる位置にある場合、前記第１渦巻歯の中心軸に対する前記第２流路及び前記第３流路の中心軸の角度は、それぞれ４５度であり、前記第１渦巻歯の中心軸に対する前記第２流路の中心軸の角度は、前記インジェクション流路の形成位置が、前記一対の圧縮室に均等に冷媒を分配できる位置よりも前記第１渦巻歯の巻き終わり部分に近い位置にある場合、４５度よりも小さくなり、前記インジェクション流路の形成位置が、前記一対の圧縮室に均等に冷媒を分配できる位置よりも前記第１渦巻歯の巻き終わり部分から遠い位置にある場合、４５度よりも大きくなるように形成されており、前記第１渦巻歯の中心軸に対する前記第３流路の中心軸の角度は、前記インジェクション流路の形成位置が、前記一対の圧縮室に均等に冷媒を分配できる位置よりも前記第２渦巻歯の巻き終わり部分に近い位置にある場合、４５度よりも小さくなり、前記インジェクション流路の形成位置が、前記一対の圧縮室に均等に冷媒を分配できる位置よりも前記第２渦巻歯の巻き終わり部分から遠い位置にある場合、４５度よりも大きくなるように形成されている。 A scroll compressor according to the present invention includes a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant, a closed container that houses the compression unit, and an injection pipe that penetrates the closed container, and the compression unit comprises a fixed scroll having a first base plate, a first spiral tooth provided on the first base plate, a second base plate facing the first base plate, and a second base plate provided on the second base plate. and a second spiral tooth arranged to mesh with the first spiral tooth, the first bed plate, the second bed plate, the first spiral tooth and the second spiral tooth. and a pair of compression chambers are formed between the injection pipe and the pair of compression chambers. The injection passage is connected to a first passage into which the refrigerant flows from the injection pipe and the first passage, and the pair of a second flow path that supplies the refrigerant that has flowed into the first flow path to one of the compression chambers of the pair of compression chambers; and a third flow path for supplying the coolant that has flowed into either the first flow path or the second flow path, and the injection flow path is viewed from the first flow path side. a center line of the second flow path extending in the direction of the first flow path from the center of the outlet of the second flow path on one side of the pair of compression chambers, and the other side of the pair of compression chambers. The centerline of the third channel extending in the direction of the first channel from the center of the outlet of the third channel at 1 is located inside the first channel.
Further, a scroll compressor of the present invention includes a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant, a closed container that houses the compression unit, and an injection pipe that penetrates the closed container, The compression unit includes: a fixed scroll having a first baseplate; a first spiral tooth provided on the first baseplate; a second baseplate facing the first baseplate; an oscillating scroll provided with a second spiral tooth disposed so as to mesh with the first spiral tooth, the first bed plate, the second bed plate, the first spiral tooth, and the second spiral tooth; A pair of compression chambers are formed between the spiral teeth, and the first bed plate is provided outside the positions of the first spiral teeth and the second spiral teeth, and is connected to the injection pipe. an injection flow path communicating with the pair of compression chambers, the injection flow path being connected to a first flow path into which refrigerant flows from the injection pipe, and the first flow path; a second flow path that supplies the refrigerant that has flowed into the first flow path to one of the pair of compression chambers; and a pair of compression chambers branched from either the first flow path or the second flow path and a third flow path for supplying the coolant that has flowed into either the first flow path or the second flow path, and the injection flow path is located on the outer circumference of the first spiral tooth. When the angle between the winding end portion, which is the end of the outer peripheral side of the first spiral tooth, and the injection flow path in the winding direction to the side is set as a variable θ [degree],
90≤θ≤110
and the second flow path is compressed toward one of the pair of compression chambers toward the gap between the winding end portion of the first spiral tooth and the second spiral tooth. and the third flow path is directed toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth, and is compressed in the other of the pair of compression chambers. The diameter of the second flow path is a variable Xf [mm], and the diameter of the third flow path is a variable Xo [mm]. mm], the ratio Xf/Xo of the diameter of the second flow path to the diameter of the third flow path is

is formed to satisfy the relationship of
Further, a scroll compressor of the present invention includes a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant, a closed container that houses the compression unit, and an injection pipe that penetrates the closed container, The compression unit includes: a fixed scroll having a first baseplate; a first spiral tooth provided on the first baseplate; a second baseplate facing the first baseplate; an oscillating scroll provided with a second spiral tooth disposed so as to mesh with the first spiral tooth, the first bed plate, the second bed plate, the first spiral tooth, and the second spiral tooth; A pair of compression chambers are formed between the spiral teeth, and the first bed plate is provided outside the positions of the first spiral teeth and the second spiral teeth, and is connected to the injection pipe. an injection flow path communicating with the pair of compression chambers, the injection flow path being connected to a first flow path into which refrigerant flows from the injection pipe, and the first flow path; a second flow path that supplies the refrigerant that has flowed into the first flow path to one of the pair of compression chambers; and a pair of compression chambers branched from either the first flow path or the second flow path and a third flow path for supplying the coolant that has flowed into either the first flow path or the second flow path, and the injection flow path is located on the outer circumference of the first spiral tooth. When the angle between the winding end portion, which is the end of the outer peripheral side of the first spiral tooth, and the injection flow path in the winding direction to the side is set as a variable θ [degree],
90≤θ≤110
and the second flow path is compressed toward one of the pair of compression chambers toward the gap between the winding end portion of the first spiral tooth and the second spiral tooth. and the third flow path is directed toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth, and is compressed in the other of the pair of compression chambers. is a flow path for supplying a refrigerant to be injected, and when the formation position of the injection flow path is located at a position where the refrigerant can be evenly distributed to the pair of compression chambers, the second flow with respect to the central axis of the first spiral tooth The angles of the central axes of the passage and the third passage are each 45 degrees, and the angle of the central axis of the second passage with respect to the central axis of the first spiral tooth is such that the position where the injection passage is formed is: When the position is closer to the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, the angle is smaller than 45 degrees, and the injection flow path is formed at the position where the injection flow path is formed in the pair of compression chambers. When the position is farther from the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the compression chamber, it is formed to be greater than 45 degrees with respect to the central axis of the first spiral tooth. The angle of the central axis of the third flow channel is such that the formation position of the injection flow channel is closer to the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers. is smaller than 45 degrees, and the formation position of the injection passage is located farther from the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers. It is formed to be larger than the degree.

In the scroll compressor of the present invention, the first base plate of the fixed scroll is provided with the first flow path, the second flow path, and the third flow path, thereby forming an injection flow path capable of supplying refrigerant to the pair of compressors. is formed. Therefore, in the scroll compressor of the present invention, there is no need to separately provide a refrigerant flow path for communicating the second flow path and the third flow path, and a seal member for blocking the refrigerant flow path can be omitted, thus reducing manufacturing man-hours. A scroll compressor that can be reduced can be provided.

1 is a schematic refrigerant circuit diagram of a refrigeration cycle device including a scroll compressor according to an embodiment; FIG. It is a longitudinal section showing an internal structure of a scroll compressor concerning an embodiment. FIG. 3 is a cross-sectional view taken along the line AA of FIG. 2; FIG. 3 is an enlarged view of the injection channel of FIG. 2; FIG. 3 is an enlarged view of a connecting portion of the injection pipe of FIG. 2;

Embodiment.
A scroll compressor 100 according to an embodiment will be described with reference to FIGS. 1 to 5. FIG. FIG. 1 is a schematic refrigerant circuit diagram of a refrigeration cycle device 1 including a scroll compressor 100 according to an embodiment. FIG. 2 is a longitudinal sectional view showing the internal structure of the scroll compressor 100 according to the embodiment. FIG. 3 is a cross-sectional view taken along line AA of FIG. FIG. 4 is an enlarged view of the injection channel 29 of FIG. FIG. 5 is an enlarged view of the connecting portion of the injection pipe 49 of FIG. In the drawings below, the dimensional relationship and shape of each component may differ from the actual one. Further, in the drawings below, the same reference numerals are assigned to the same members or portions or the members or portions having the same functions, or the reference numerals are omitted. In principle, the positional relationship between the constituent members of the scroll compressor 100, for example, the positional relationship in the vertical, horizontal, and longitudinal directions, is the positional relationship when the scroll compressor 100 is installed in a usable state.

FIG. 1 shows a minimum configuration of a refrigeration cycle device 1 including a scroll compressor 100 according to an embodiment. The refrigeration cycle device 1 includes a refrigerant circuit 500 in which a scroll compressor 100, a condenser 200, a first pressure reducing device 300, and an evaporator 400 are connected by refrigerant pipes, and refrigerant circulates inside the refrigerant pipes. In the refrigeration cycle device 1, for example, a fluorocarbon-based refrigerant such as R32 refrigerant or a natural refrigerant such as carbon dioxide is used as the refrigerant.

The scroll compressor 100 is a fluid machine that compresses sucked low-pressure refrigerant and discharges it as high-pressure refrigerant. Details of the scroll compressor 100 will be described later.

The condenser 200 is a heat exchanger that exchanges heat between a high-temperature, high-pressure gas refrigerant flowing inside the condenser 200 and a low-temperature medium passing through the condenser 200 . For example, the condenser 200 is configured as an air-cooled heat exchanger that exchanges heat between high-temperature, high-pressure gas refrigerant flowing inside the condenser 200 and low-temperature air passing through the condenser 200 .

The first decompression device 300 is an expansion device that expands and decompresses the high-pressure liquid refrigerant. As the first pressure reducing device 300, for example, an expander, a thermal automatic expansion valve, a linear electronic expansion valve, or the like is used.

The evaporator 400 is a heat exchanger that exchanges heat between a low-temperature, low-pressure liquid refrigerant or two-phase refrigerant flowing inside the evaporator 400 and a high-temperature medium passing through the evaporator 400 . For example, the evaporator 400 is configured as an air-cooled heat exchanger that exchanges heat between the low-temperature, low-pressure liquid refrigerant or two-phase refrigerant flowing inside the evaporator 400 and the high-temperature air passing through the evaporator 400. be.

In the refrigerant circuit 500 of the refrigeration cycle device 1 , the high-temperature, high-pressure gas refrigerant discharged from the scroll compressor 100 flows into the condenser 200 . The high-temperature and high-pressure gas refrigerant that has flowed into the condenser 200 is heat-exchanged by releasing heat to a low-temperature medium in the condenser 200, and becomes a high-pressure liquid refrigerant. The high pressure liquid refrigerant flows into the first pressure reducing device 300 . The high-pressure liquid refrigerant that has flowed into the first pressure reducing device 300 is expanded and decompressed to become a low-temperature low-pressure liquid refrigerant or a two-phase refrigerant. The low-temperature, low-pressure liquid refrigerant or two-phase refrigerant flows into the evaporator 400, absorbs heat from the high-temperature medium in the evaporator 400, and evaporates into a high-dryness two-phase refrigerant or a low-temperature, low-pressure gas refrigerant. The two-phase refrigerant with high dryness or the low-temperature, low-pressure gas refrigerant that has flowed out of the evaporator 400 is sucked into the scroll compressor 100 . The refrigerant sucked into the scroll compressor 100 is compressed into a high-temperature and high-pressure gas refrigerant, which is then discharged from the scroll compressor 100 .

The refrigeration cycle device 1 also has an injection circuit 800 that is branch-connected to the refrigerant pipe between the condenser 200 and the first pressure reducing device 300 and connected to the inside of the compression unit 10 of the scroll compressor 100. . The injection circuit 800 has a second pressure reducing device 600 . In the refrigeration cycle apparatus 1 of the embodiment, the injection circuit 800 is configured to cause the low-temperature, low-pressure liquid refrigerant or two-phase refrigerant to flow into the compression unit 10 of the scroll compressor 100 .

Like the first pressure reducing device 300, the second pressure reducing device 600 is an expansion device that expands and decompresses high-pressure liquid refrigerant and causes it to flow out as a low-temperature low-pressure liquid refrigerant or a two-phase refrigerant. For example, a linear electronic expansion valve or the like is used as the second pressure reducing device 600 .

Although injection circuit 800 has only second pressure reducing device 600 in FIG. 1 , it may have a cooler between second pressure reducing device 600 and scroll compressor 100 . A cooler is a heat exchanger that exchanges heat between a low-temperature, low-pressure liquid or two-phase refrigerant flowing inside the cooler and a high-temperature medium passing through the cooler. For example, the cooler is configured as an air-cooled heat exchanger that exchanges heat between a low-temperature, low-pressure two-phase refrigerant flowing inside the cooler and hot air passing through the cooler. The cooler exchanges heat between the low-temperature, low-pressure two-phase refrigerant that flows out of the second pressure reducing device 600 and flows inside the cooler, and the high-pressure liquid refrigerant or two-phase refrigerant that flows out of the condenser 200. It may be configured as a double-tube supercooling heat exchanger.

Next, the structure of the scroll compressor 100 according to the embodiment will be described with reference to FIGS. 2 and 3. FIG.

As shown in FIG. 2, the scroll compressor 100 includes a compression unit 10 that compresses low-pressure refrigerant and discharges it as high-pressure refrigerant, and an electric motor unit 30 that drives the compression unit 10 via a main shaft 33. there is Further, the scroll compressor 100 has a sealed container 40 that houses the compression unit 10 and the electric motor unit 30 and forms an outer shell of the scroll compressor 100 .

The sealed container 40 has a trunk portion 42 , a lid portion 41 provided on the upper portion of the trunk portion 42 , and a bottom portion 43 provided on the lower portion of the trunk portion 42 . The bottom portion 43 serves as an oil reservoir that stores lubricating oil. A suction pipe 44 for sucking the low-pressure refrigerant flowing out of the evaporator 400 is connected to the body portion 42 . A discharge pipe 45 for discharging high-pressure refrigerant is connected to the lid portion 41 .

The compression unit 10 has a fixed scroll 21 and an orbiting scroll 22 .

A frame 46 and a sub-frame 47 are further arranged inside the sealed container 40 so as to face each other with the electric motor unit 30 interposed therebetween in the axial direction of the main shaft 33 . Frame 46 is located between motor unit 30 and compression unit 10 . The subframe 47 is positioned below the electric motor unit 30 . The frame 46 and the sub-frame 47 are fixed to the inner peripheral surface of the body portion 42 of the sealed container 40 by shrink fitting or welding.

The fixed scroll 21 is fixed to the frame 46 with bolts or the like. The orbiting scroll 22 is accommodated in an internal space between the fixed scroll 21 and the frame 46. As shown in FIG.

The fixed scroll 21 has a first base plate 23 and a first spiral tooth 24 which is a spiral protrusion provided on one surface of the first base plate 23 . The orbiting scroll 22 has a second base plate 25 and a second spiral tooth 26 which is a spiral protrusion provided on one surface of the second base plate 25 . In the compression unit 10 , the second bedplate 25 faces the first bedplate 23 , and the second spiral teeth 26 are arranged to mesh with the first spiral teeth 24 . In the following description, the end of the first spiral tooth 24 on the outer peripheral side is referred to as a winding end portion 24a of the first spiral tooth 24. As shown in FIG. Further, the end of the second spiral tooth 26 on the outer peripheral side is referred to as a winding end portion 26 a of the second spiral tooth 26 .

In a state in which the second spiral tooth 26 is arranged to mesh with the first spiral tooth 24, the winding end portion 24a of the first spiral tooth 24 and the winding end portion 26a of the second spiral tooth 26 sandwich the central axis of the main shaft 33. are arranged point-symmetrically to each other. Between the first base plate 23, the second base plate 25, the first spiral tooth 24, and the second spiral tooth 26, a pair of compression chambers 11 with relatively varying volumes are formed. A pair of compression chambers 11 are formed in pairs at point-symmetrical positions with respect to the central axis of the main shaft 33 . In the compression unit 10 , a plurality of pairs of compression chambers 11 are formed.

A discharge port 3 is formed in the central portion of the first base plate 23 of the fixed scroll 21 to discharge the refrigerant gas that has been compressed to a high pressure. Around the discharge port 3, a discharge valve 5 for opening and closing the discharge port 3 and a valve guard 6 for controlling the movable range of the discharge valve 5 are provided. A discharge muffler 7 is fixed to the upper portion of the first base plate 23 of the fixed scroll 21 so as to cover the discharge port 3 .

A plurality of suction ports 36 are provided in the frame 46 . The plurality of suction ports 36 are connected to the space in the sealed container 40 between the frame 46 and the electric motor unit 30 and communicated with the suction pipe 44, and from the outer shell of the first spiral tooth 24 and the second spiral tooth 26 in the compression unit 10. is a through-hole that communicates with the space on the outside.

The orbiting scroll 22 is housed in a frame 46 and is restrained from rotating by an Oldham ring 22 a provided at the bottom of the orbiting scroll 22 . A hollow cylindrical boss portion 27 is formed at the center of the surface of the second base plate 25 opposite to the surface on which the second spiral teeth 26 are formed. A swing bearing 27 a is formed inside the boss portion 27 .

The electric motor unit 30 includes a stator 31 fixed to the inner peripheral surface of the closed container 40 by shrink fitting or the like, a rotor 32 rotatably accommodated on the inner peripheral side of the stator 31, and fixed to the rotor 32 by shrink fitting or the like. and a main shaft 33 . The rotor 32 is rotationally driven by applying a voltage to the stator 31 . Rotational drive of the rotor 32 is transmitted to the orbiting scroll 22 via the main shaft 33 . In the compression unit 10 , the refrigerant is compressed by the orbiting scroll 22 oscillating relative to the fixed scroll 21 .

The main shaft 33 has an eccentric shaft portion 33a, a main shaft portion 33b, and a sub shaft portion 33c. The eccentric shaft portion 33a is provided eccentrically with respect to the axis of the main shaft 33, and is rotatably accommodated in the swing bearing 27a. The main shaft portion 33b is supported by a main bearing 46a provided on the frame 46. As shown in FIG. A sleeve 34 is provided between the main bearing 46a and the main shaft portion 33b to smoothly rotate the main shaft portion 33b. The secondary shaft portion 33c is rotatably supported by a ball bearing 48. As shown in FIG. The ball bearing 48 is press-fitted and fixed to the central portion of the sub-frame 47 . An eccentric shaft portion 33a is inserted into the swing bearing 27a. The outer peripheral portion of the eccentric shaft portion 33a is in close contact with the inner peripheral portion of the swing bearing 27a via lubricating oil.

An injection pipe 49 is connected above the lid portion 41 . The injection pipe 49 is connected to an injection pipe insertion port 28 formed in the first base plate 23 of the fixed scroll 21 .

The first base plate 23 is formed with an injection passage 29 that communicates with the injection pipe 49 inserted into the injection pipe insertion port 28 and penetrates the surface on which the first spiral teeth 24 are formed. The injection channel 29 is provided on the first base plate 23 outside the positions of the first spiral tooth 24 and the second spiral tooth 26 . The low-temperature, low-pressure liquid refrigerant or two-phase refrigerant flowing from the injection circuit 800 flows into the compression unit 10 via the injection pipe 49 and the injection flow path 29 .

Next, the operation of scroll compressor 100 will be described.

When a voltage is applied to the stator 31 of the electric motor unit 30, current flows through the coils of the stator 31 and a magnetic field is generated. A magnetic field generated in the stator 31 causes the main shaft 33 passing through the rotor 32 to rotate. When the main shaft 33 rotates, the eccentric shaft portion 33 a rotates eccentrically, and the oscillating scroll 22 in the compression unit 10 oscillates. Due to the oscillating motion of the oscillating scroll 22 , the low-pressure refrigerant flowing out of the evaporator 400 is sucked into the sealed container 40 through the suction pipe 44 . The orbiting scroll 22 is restrained from rotating by the Oldham's ring 22a.

A part of the sucked refrigerant flows into the frame 46 through the suction port 36 of the frame 46 and is sucked into the compression unit 10 . Refrigerant flowing from the injection pipe 49 is sucked into the compression unit 10 through the injection flow path 29 , flows into the frame 46 , and is mixed with the refrigerant sucked into the compression unit 10 . The mixed refrigerant is sucked into the pair of suction chambers 12 to start the suction stroke. On the other hand, the rest of the coolant that has not flowed into the frame 46 cools the electric motor unit 30 and the lubricating oil.

By mixing the refrigerant sucked into the compression unit 10 with the refrigerant flowing from the injection pipe 49, the temperature of the refrigerant sucked into the compression unit 10 is lowered. Therefore, since the thermal expansion of the fixed scroll 21 and the orbiting scroll 22 can be suppressed, the behavior of the compression unit 10 can be stabilized.

In the suction stroke, the refrigerant sucked into the suction chamber 12 gradually moves toward the center of the orbiting scroll 22 due to the orbiting motion of the orbiting scroll 22, and is compressed by being reduced in volume. The compressed refrigerant is discharged from the pair of discharge chambers 13 , passes through the discharge port 3 of the fixed scroll 21 , and is discharged from the discharge valve 5 . The high-pressure refrigerant discharged from the discharge valve 5 is discharged from the discharge pipe 45 via the discharge muffler 7 . The high pressure refrigerant discharged from the discharge pipe 45 flows into the condenser 200 .

Next, the configuration of the injection flow path 29 will be described.

As shown in FIGS. 3 and 4, the injection channel 29 has a first channel 29a that communicates with the injection pipe 49 and into which the coolant from the injection pipe 49 flows. The injection flow path 29 also has a second flow path 29 b that is connected to the first flow path 29 a and supplies the refrigerant that has flowed into the first flow path 29 a to one of the pair of compression chambers 11 . The injection flow path 29 branches from the first flow path 29a and has a third flow path 29c that supplies the refrigerant that has flowed into the first flow path 29a to the other of the pair of compression chambers 11 . The first flow path 29a, the second flow path 29b, and the third flow path 29c are formed by boring the first base plate 23 with a boring tool such as a drill.

The second flow path 29 b can be, for example, a refrigerant flow path that supplies refrigerant to the suction chamber 12 formed between the winding end portion 24 a of the first spiral tooth 24 and the second spiral tooth 26 . Also, the third flow path 29 c can be a refrigerant flow path that supplies the refrigerant to the suction chamber 12 formed between the winding end portion 26 a of the second spiral tooth 26 and the first spiral tooth 24 , for example. Note that the relationship between the first spiral tooth 24 and the second spiral tooth 26 of the second flow path 29b and the third flow path 29c may be the reverse of the relationship described above. Also, the third flow path 29c may be a refrigerant flow path branched from the second flow path 29b.

The suction chamber 12 formed between the winding end portion 24 a of the first spiral tooth 24 and the second spiral tooth 26 opens toward the direction of the injection flow path 29 . On the other hand, the suction chamber 12 formed between the winding end portion 26 a of the second spiral tooth 26 and the first spiral tooth 24 opens in the direction opposite to the direction of the injection flow path 29 . Therefore, depending on the position of the injection channel 29, the refrigerant from the injection channel 29 may not be evenly distributed to the pair of compression chambers 11 in some cases. If the refrigerant from the injection channels 29 is not evenly distributed, the pressure between the pair of compression chambers 11 becomes unbalanced, and the behavior of the compression unit 10 may become unstable.

Therefore, the injection flow passage 29 defines the angle between the winding end portion 24a of the first spiral tooth 24 and the injection flow passage 29 in the winding direction of the first spiral tooth 24 to the outer peripheral side as a variable θ [degree]. , it is formed at a position where 90≤θ≤110. For example, the variable θ can be the angle between the winding end portion 24 a of the first spiral tooth 24 and the central axis of the first channel 29 a of the injection channel 29 .

When the injection flow path 29 is formed at a position where θ<90 or a position where θ>110, the refrigerant from the injection flow path 29 is not evenly distributed to the pair of compression chambers 11, and the pair of compression chambers 11 There is an imbalance in the temperature of the refrigerant compressed at .

For example, among the pair of compression chambers 11, the compression chamber 11 having a smaller amount of refrigerant from the injection passage 29 has a lower amount of refrigerant to be compressed than the compression chamber 11 having a large amount of refrigerant from the injection passage 29. temperature rises. In the compression chamber 11 where the temperature of the refrigerant to be compressed is higher, due to thermal expansion of the fixed scroll 21 and the orbiting scroll 22, contact between the first base plate 23 and the second spiral tooth 26 and contact between the second base plate 25 and Contact with the first spiral tooth 24 occurs. Therefore, when the injection passage 29 is formed at a position where θ<90 or a position where θ>110, the contact portion between the first spiral tooth 24 and the second spiral tooth 26 is worn or damaged, and the scroll compressor 100 is more likely to malfunction.

Further, in the compression chamber 11 in which the amount of refrigerant from the injection passage 29 is large among the pair of compression chambers 11, the concentration of lubricating oil with respect to the refrigerant decreases. When the concentration of the lubricating oil with respect to the refrigerant decreases, lubricating oil becomes insufficient at the contact portion of the second spiral tooth 26 with the first base plate 23 and the contact portion of the first spiral tooth 24 with the second base plate 25. Abrasion of the tip seal provided at the contact portion occurs. Therefore, if the injection passage 29 is formed at a position where θ<90 or a position where θ>110, the compression performance of the scroll compressor 100 may deteriorate due to wear of the tip seal.

On the other hand, if the injection flow path 29 is formed at a position where 90≦θ≦110, the position of the opening of the winding end portion 24a of the first spiral tooth 24 is the opening of the winding end portion 26a of the second spiral tooth 26. becomes farther than the position of Therefore, if the injection flow path 29 is formed at a position where 90≦θ≦110, the winding end portion 24a of the first spiral tooth 24 and the winding end portion 26a of the second spiral tooth 26 are opened. An imbalance in distribution of the refrigerant to the pair of compression chambers 11 can be suppressed. In addition, since the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11, the temperature of the refrigerant compressed in the pair of compression chambers 11 can be evenly lowered.

Therefore, if the injection flow path 29 is formed at a position where 90≦θ≦110, the imbalance in the distribution of the refrigerant to the pair of compression chambers 11 can be suppressed, so that the behavior of the compression unit 10 can be stabilized. can. Further, if the injection flow path 29 is formed at a position where 90≦θ≦110, it is possible to suppress the imbalance in the distribution of the refrigerant to the pair of compression chambers 11, which may cause problems in the scroll compressor 100. And the deterioration of the compression performance of the scroll compressor 100 can be suppressed.

Further, the diameter of the second flow path 29b is formed so as to decrease as the position of the second flow path 29b approaches the winding end portion 24a of the first spiral tooth 24. As shown in FIG. Further, the diameter of the third flow path 29c is formed to decrease as the position of the third flow path 29c approaches the winding end portion 26a of the second spiral tooth 26. As shown in FIG. For example, when the circumferential distance between the injection channel 29 and the winding end portion 24a of the first spiral tooth 24 is reduced, the diameter of the second channel 29b is made smaller than the diameter of the third channel 29c. be able to. Further, when the circumferential distance between the injection channel 29 and the winding end portion 24a of the first spiral tooth 24 increases, the diameter of the second channel 29b is made larger than the diameter of the third channel 29c. be able to.

By providing a difference in the diameters of the second flow path 29b and the third flow path 29c, the refrigerant from the injection flow path 29 can be evenly distributed to the pair of compression chambers 11, so that the behavior of the compression unit 10 can be stabilized. can be done. In addition, since the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11, the temperature of the refrigerant compressed in the pair of compression chambers 11 can be evenly lowered.

の関係を満たすように形成できる。For example, when the diameter of the second flow path 29b is the variable Xf [mm] and the diameter of the third flow path 29c is the variable Xo [mm], the third flow The diameter ratio Xf/Xo of the second channel 29b to the channel 29c is

can be formed to satisfy the relationship

If the diameters of the second flow path 29b and the third flow path 29c do not satisfy the above relationship, the refrigerant from the injection flow path 29 is not evenly distributed to the pair of compression chambers 11 and compressed in the pair of compression chambers 11. This creates an imbalance in the temperature of the coolant being supplied.

For example, among the pair of compression chambers 11, the compression chamber 11 having a smaller amount of refrigerant from the injection passage 29 has a lower amount of refrigerant to be compressed than the compression chamber 11 having a large amount of refrigerant from the injection passage 29. temperature rises. In the compression chamber 11 where the temperature of the refrigerant to be compressed is higher, due to thermal expansion of the fixed scroll 21 and the orbiting scroll 22, contact between the first base plate 23 and the second spiral tooth 26 and contact between the second base plate 25 and Contact with the first spiral tooth 24 occurs. Therefore, if the diameters of the second flow path 29b and the third flow path 29c do not satisfy the relationship of the above formula, the contact portions of the first spiral tooth 24 and the second spiral tooth 26 are worn or damaged, and the scroll compressor 100 more likely to cause problems.

Further, in the compression chamber 11 in which the amount of refrigerant from the injection passage 29 is large among the pair of compression chambers 11, the concentration of lubricating oil with respect to the refrigerant decreases. When the concentration of the lubricating oil with respect to the refrigerant decreases, lubricating oil becomes insufficient at the contact portion of the second spiral tooth 26 with the first base plate 23 and the contact portion of the first spiral tooth 24 with the second base plate 25. Abrasion of the tip seal provided at the contact portion occurs. Therefore, if the diameters of the second flow path 29b and the third flow path 29c do not satisfy the relationship of the above formula, the compression performance of the scroll compressor 100 may deteriorate due to wear of the tip seal.

On the other hand, when the diameters of the second flow path 29b and the third flow path 29c satisfy the above relationship, the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11. Therefore, the behavior of the compression unit 10 can be stabilized. In addition, since the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11, the temperature of the refrigerant compressed in the pair of compression chambers 11 can be evenly lowered.

Therefore, if the diameters of the second flow path 29b and the third flow path 29c satisfy the relationship of the above formula, the imbalance in the distribution of the refrigerant to the pair of compression chambers 11 can be suppressed, so the behavior of the compression unit 10 can be stabilized. Further, if the diameters of the second flow path 29b and the third flow path 29c satisfy the relationship of the above formula, the imbalance in the distribution of the refrigerant to the pair of compression chambers 11 can be suppressed. Possibility of malfunction and reduction in compression performance of the scroll compressor 100 can be suppressed.

Also, the angle of the central axis of the second flow path 29b with respect to the central axis of the first spiral tooth 24 is made smaller as the formation position of the injection flow path 29 approaches the winding end portion 24a of the first spiral tooth 24. formed. Also, the angle of the central axis of the third flow passage 29c with respect to the central axis of the first spiral tooth 24 is made smaller as the position where the injection passage 29 is formed approaches the winding end portion 26a of the second spiral tooth 26. formed.

For example, the angle φ1 [degree] of the central axis of the second flow path 29b with respect to the central axis of the first spiral tooth 24 can be 0≦φ1≦70. Also, the angle φ2 [degree] of the central axis of the third flow path 29c with respect to the central axis of the first spiral tooth 24 can be 0≦φ2≦70.

When φ1>70 or φ2>70, the outlets of the second flow path 29b and the third flow path 29c are formed on the fixed surface of the fixed scroll 21 with the frame 46. 29b and the outlet of the third channel 29c may be blocked. Further, as the angle φ1 or the angle φ2 approaches 90 [degree], depending on the shape of the fixed scroll 21 and the frame 46, the outlet of the second flow path 29b or the third flow path 29c may become a sealed container communicating with the discharge pipe 45. It may communicate with the high pressure space inside 40 . Therefore, if φ1>70 or φ2>70, the second flow path 29b and the third flow path 29c cannot function as the injection flow path 29, and the performance of the scroll compressor 100 may deteriorate. There is

On the other hand, when 0≤φ1≤70 and 0≤φ2≤70, the outlets of the second flow path 29b and the third flow path 29c may be blocked by the frame 46 or the high pressure inside the closed container 40 Communication with space can also be avoided. Therefore, by setting 0≦φ1≦70 and 0≦φ2≦70, the second flow path 29b and the third flow path 29c can function as the injection flow path 29, so that the scroll compressor 100 It can improve performance.

More specifically, when the injection channel 29 is formed at a position where the refrigerant can be evenly distributed to the pair of compression chambers 11, the second channel 29b and the third The angle of the central axis of the channel 29c can be set to 45 degrees. When the formation position of the injection flow path 29 is closer to the winding end portion 24a of the first spiral tooth 24 than the above-described formation position in the circumferential direction, the second flow path 29b with respect to the central axis of the first spiral tooth 24 can be less than 45 degrees. Further, when the formation position of the injection flow path 29 is further away from the winding end portion 24a of the first spiral tooth 24 than the above-described formation position in the circumferential direction, the second flow path 29b with respect to the central axis of the first spiral tooth 24 can be greater than 45 degrees. Further, when the formation position of the injection channel 29 is closer to the winding end portion 26a of the second spiral tooth 26 than the above-described formation position in the circumferential direction, the third flow relative to the central axis of the first spiral tooth 24 The angle of the central axis of channel 29c can be less than 45 degrees. Further, when the formation position of the injection flow path 29 is further away from the winding end portion 26a of the second spiral tooth 26 than the above-described formation position in the circumferential direction, the third flow path 29c with respect to the central axis of the first spiral tooth 24 can be greater than 45 degrees.

By providing a difference between the angles of the central axes of the second flow path 29b and the third flow path 29c, the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11, so that the behavior of the compression unit 10 can be changed. can be stabilized. In addition, since the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11, the temperature of the refrigerant compressed in the pair of compression chambers 11 can be evenly lowered.

Further, when the first base plate 23 is viewed from above, the central axes of the second flow path 29b and the third flow path 29c are arranged inside the first flow path 29a. According to this configuration, since the formation position of the injection flow path 29 can be limited to a part of the first base plate 23 , it is possible to prevent the rigidity of the first base plate 23 from decreasing due to the formation of the injection flow path 29 . Therefore, the stability of the compression unit 10 can be improved.

As described above, in the embodiment, the injection flow path 29 having the first flow path 29a, the second flow path 29b, and the third flow path 29c is provided in the first base plate 23 of the fixed scroll 21. there is With this configuration, the refrigerant flowing from the injection pipe 49 can be evenly distributed to the pair of compression chambers 11 . In addition, there is no need to separately provide a coolant flow path for communicating the second flow path 29b and the third flow path 29c, and a sealing member for blocking the coolant flow path can be omitted, so that manufacturing man-hours can be reduced. Therefore, in the embodiment, it is possible to provide the scroll compressor 100 capable of evenly distributing the refrigerant flowing from the injection pipe 49 and reducing the manufacturing cost.

Further, as shown in FIG. 5, the axial clearance C between the first flow path 29a of the injection flow path 29 and the injection tube insertion port 28 can be set to 1 to 2 [mm]. By setting the clearance C to 1 to 2 [mm], the depth of the injection flow path 29, the length of the injection pipe 49, or the size of the joint of the sealed container 40, etc. are processed to the JIS standard ordinary tolerance medium grade. be able to. In addition, it is possible to prevent a part of the first flow path 29a of the injection flow path 29 from being blocked by the injection pipe 49 due to the processing.

When an upward load, for example, a counter pressure acts on the frame 46 and the orbiting scroll 22, the frame 46 and the orbiting scroll 22 move upward. On the other hand, since the main shaft 33 is not affected by the upward load, it does not move upward. Therefore, when an upward load acts on the frame 46 and the oscillating scroll 22, the area of the portion where the main bearing 46a faces the main shaft 33 and the area of the portion where the oscillating bearing 27a faces the main shaft 33 decrease. At this time, when the clearance C is 2 [mm] or more, the degree of decrease in the area of the portion where the main bearing 46a and the swing bearing 27a face the main shaft 33 increases. When the scroll compressor 100 operates in a state where the areas of the main bearing 46a and the rocking bearing 27a facing the main shaft 33 are reduced, the load acting on the main bearing 46a and the rocking bearing 27a increases. 100 can go wrong.

On the other hand, when the clearance C is less than 2 [mm], the degree of decrease in the area of the portion where the main bearing 46a and the rocking bearing 27a face the main shaft 33 can be reduced. can be suppressed from increasing. In addition, even if an upward load acts on the fixed scroll 21, by limiting the clearance C to 1 to 2 [mm], the floating amount can be regulated, so damage to the compression unit 10 can be prevented. can be suppressed. Therefore, by limiting the clearance C to 1 to 2 [mm], it is possible to prevent problems from occurring in the scroll compressor 100 .

Also, the injection pipe 49 can be attached by penetrating the flat surface 41 a of the lid portion 41 . For example, as shown in FIG. 5, the inner diameter of the lid portion 41 is a variable DA, the width of the bent portion 41b of the lid portion 41 is a variable R, and the inner diameter of the injection pipe 49 is a variable DB. can be installed at a position X that satisfies
X<DA/2-R-DB/2
Note that the position X is the distance between the vertical center of the scroll compressor 100 and the central axis of the injection pipe 49 . According to the above configuration, the injection pipe 49 is not fixed to the bent portion 41b of the lid portion 41, so that the mounting hole for the injection pipe 49 can be easily processed, and the injection pipe 49 can be easily brazed. can reduce manufacturing costs.

In addition, in the embodiment, the injection flow path 29 is provided outside the positions of the first spiral tooth 24 and the second spiral tooth 26 on the first base plate 23 . In addition, the refrigerant flowing from the injection passage 29 joins and mixes with the refrigerant sucked from the suction pipe 44 before being sucked into the suction chamber 12 . That is, the refrigerant flowing from the injection channel 29 flows into the low pressure space of the compression unit 10 .

Conventionally, a method of injecting a refrigerant into the compression chamber 11 of medium pressure space is known. In this case, since refrigerants with different pressures flow into the compression chamber 11 of the intermediate pressure space, the refrigerants with different pressures are mixed in the compression chamber 11, resulting in mixing loss, and the performance of the scroll compressor 100 is lowered. there was a case. Further, when adopting a method of injecting the refrigerant into the compression chamber 11 of the intermediate pressure space, the injection port for injecting the refrigerant is arranged so as to communicate with the compression chamber 11 of the intermediate pressure space. Therefore, under operating conditions in which injection is not required, the refrigerant flows backward from the compression chamber 11 of the intermediate pressure space to the injection port, and the compressed refrigerant expands, resulting in compression loss.

On the other hand, in the case of the formation position of the injection flow path 29 of the embodiment, the refrigerant flowing from the injection flow path 29 joins with the refrigerant sucked from the suction pipe 44 before being sucked into the suction chamber 12. mixed. Therefore, since refrigerants having different pressures do not mix in the compression chamber 11, there is no mixing loss or compression loss. .

Moreover, in the embodiment, the temperature of the pair of compression chambers 11 can be lowered. Therefore, the gap between the tip of the first spiral tooth 24 and the second base plate 25 and the gap between the tip of the second spiral tooth 26 and the first base plate 23 shrink due to thermal expansion and come into contact with each other. Since this can be suppressed, failure of the scroll compressor 100 can be suppressed. For example, when a refrigerant with a high discharge temperature, such as R32, is used as the refrigerant, the inside of the compression unit 10 becomes hot due to compression operation at a high compression ratio, and the degree of contraction of the tips of the first spiral teeth 24 and the second spiral teeth 26 also increases. It is particularly effective because it increases in size.

In addition, since the injection passage 29 is formed in the first base plate 23 of the fixed scroll 21 and not formed in the frame 46, the frame 46 is not cooled by the inflow of the coolant from the injection pipe 49. Therefore, by reducing the axial dimension of the frame 46, the gap between the tip of the first spiral tooth 24 and the second base plate 25 and the gap between the tip of the second spiral tooth 26 and the first base plate 23 are reduced. Since it is possible to suppress contact due to a reduction in the gap between them, failure of the scroll compressor 100 can be suppressed.

Other embodiments.
The present invention is not limited to the above-described embodiments, and various modifications are possible. For example, although one compression unit 10 is provided in the scroll compressor 100 in the above-described embodiment, a plurality of compression units may be provided. Further, although the scroll compressor 100 is described as a hermetic compressor in FIG. 2, it may be an open compressor or a semi-hermetic compressor.

Also, the configurations of the above-described embodiments can be combined with each other.

1 refrigeration cycle device 3 discharge port 5 discharge valve 6 valve retainer 7 discharge muffler 10 compression unit 11 compression chamber 12 suction chamber 13 discharge chamber 21 fixed scroll 22 orbiting scroll 22a Oldham ring, 23 first bed plate 24 first spiral tooth 24a winding end portion of first spiral tooth 25 second bed plate 26 second spiral tooth 26a winding end portion of second spiral tooth 27 boss portion 27a swing dynamic bearing, 28 injection pipe insertion port, 29 injection flow path, 29a first flow path, 29b second flow path, 29c third flow path, 30 electric motor unit, 31 stator, 32 rotor, 33 main shaft, 33a eccentric shaft portion, 33b main shaft portion, 33c sub shaft portion, 34 sleeve, 36 suction port, 40 sealed container, 41 lid portion, 41a flat surface, 41b bent portion, 42 body portion, 43 bottom portion, 44 suction pipe, 45 discharge pipe, 46 frame, 46a main bearing, 47 subframe, 48 ball bearing, 49 injection pipe, 100 scroll compressor, 200 condenser, 300 first pressure reducing device, 400 evaporator, 500 refrigerant circuit, 600 second pressure reducing device, 800 injection circuit.

Claims (11)

a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant;
A closed container containing the compression unit;
and an injection pipe that penetrates the closed container,
The compression unit is
a fixed scroll having a first base plate and a first spiral tooth provided on the first base plate;
an orbiting scroll having a second base plate facing the first base plate and a second spiral tooth provided on the second base plate and arranged to mesh with the first spiral tooth,
A pair of compression chambers are formed between the first base plate, the second base plate, the first spiral tooth, and the second spiral tooth,
The first base plate is
an injection passage provided outside the positions of the first spiral tooth and the second spiral tooth and communicating between the injection pipe and the pair of compression chambers,
The injection channel is
a first flow path into which the coolant from the injection pipe flows;
a second flow path that is connected to the first flow path and supplies the refrigerant that has flowed into the first flow path to one of the pair of compression chambers;
One of the first flow path and the second flow path is branched to supply the refrigerant flowing into either the first flow path or the second flow path to the other of the pair of compression chambers. and a third flow path,
When the injection flow path is viewed from the first flow path side, the second flow extends from the center of the outlet of the second flow path on one side of the pair of compression chambers in the direction of the first flow path. The centerline of the channel and the centerline of the third channel extending in the direction of the first channel from the center of the outlet of the third channel on the other side of the pair of compression chambers A scroll compressor located inside the channel. The injection channel is
When the angle between the winding end portion, which is the end of the outer peripheral side of the first spiral tooth, and the injection flow path in the winding direction of the first spiral tooth to the outer peripheral side is set as a variable θ [degree],
90≤θ≤110
2. The scroll compressor according to claim 1, which is formed at a position where The second flow path is a flow path that supplies refrigerant to be compressed in one of the pair of compression chambers toward a gap between the winding end portion of the first spiral tooth and the second spiral tooth. ,
The third flow path is a flow path that supplies the refrigerant compressed in the other of the pair of compression chambers toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth. ,
The second flow path and the third flow path are
When the diameter of the second flow path is a variable Xf [mm] and the diameter of the third flow path is a variable Xo [mm],
The ratio Xf/Xo of the diameter of the second flow path to the diameter of the third flow path is

3. The scroll compressor according to claim 2, which is formed so as to satisfy the relationship of a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant;
A closed container containing the compression unit;
and an injection pipe that penetrates the closed container,
The compression unit is
a fixed scroll having a first base plate and a first spiral tooth provided on the first base plate;
an orbiting scroll having a second base plate facing the first base plate and a second spiral tooth provided on the second base plate and arranged to mesh with the first spiral tooth,
A pair of compression chambers are formed between the first base plate, the second base plate, the first spiral tooth, and the second spiral tooth,
The first base plate is
an injection passage provided outside the positions of the first spiral tooth and the second spiral tooth and communicating between the injection pipe and the pair of compression chambers,
The injection channel is
a first flow path into which the coolant from the injection pipe flows;
a second flow path that is connected to the first flow path and supplies the refrigerant that has flowed into the first flow path to one of the pair of compression chambers;
One of the first flow path and the second flow path is branched to supply the refrigerant flowing into either the first flow path or the second flow path to the other of the pair of compression chambers. and a third flow path,
The injection channel is
When the angle between the winding end portion, which is the end of the outer peripheral side of the first spiral tooth, and the injection flow path in the winding direction of the first spiral tooth to the outer peripheral side is set as a variable θ [degree],
90≤θ≤110
It is formed at a position where
The second flow path is a flow path that supplies refrigerant to be compressed in one of the pair of compression chambers toward a gap between the winding end portion of the first spiral tooth and the second spiral tooth. ,
The third flow path is a flow path that supplies the refrigerant compressed in the other of the pair of compression chambers toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth. ,
The second flow path and the third flow path are
When the diameter of the second flow path is a variable Xf [mm] and the diameter of the third flow path is a variable Xo [mm],
The ratio Xf/Xo of the diameter of the second flow path to the diameter of the third flow path is

A scroll compressor formed to satisfy the relationship of The second flow path is a flow path that supplies refrigerant to be compressed in one of the pair of compression chambers toward a gap between the winding end portion of the first spiral tooth and the second spiral tooth. ,
The third flow path is a flow path that supplies the refrigerant compressed in the other of the pair of compression chambers toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth. ,
When the formation position of the injection passage is at a position where the refrigerant can be evenly distributed to the pair of compression chambers, the central axis of the second passage and the third passage with respect to the central axis of the first spiral tooth is The angles are each 45 degrees,
The angle of the central axis of the second flow path with respect to the central axis of the first spiral tooth is
When the formation position of the injection passage is closer to the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, the angle is smaller than 45 degrees,
When the formation position of the injection passage is farther from the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, it is formed to be larger than 45 degrees. and
The angle of the central axis of the third flow path with respect to the central axis of the first spiral tooth is
When the formation position of the injection passage is closer to the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, it is formed to be smaller than 45 degrees. ,
When the formation position of the injection passage is farther from the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, it is formed to be larger than 45 degrees. The scroll compressor according to any one of claims 2 to 4. a compression unit that compresses a low-pressure refrigerant and discharges it as a high-pressure refrigerant;
A closed container containing the compression unit;
and an injection pipe that penetrates the closed container,
The compression unit is
a fixed scroll having a first base plate and a first spiral tooth provided on the first base plate;
an orbiting scroll having a second base plate facing the first base plate and a second spiral tooth provided on the second base plate and arranged to mesh with the first spiral tooth,
A pair of compression chambers are formed between the first base plate, the second base plate, the first spiral tooth, and the second spiral tooth,
The first base plate is
an injection passage provided outside the positions of the first spiral tooth and the second spiral tooth and communicating between the injection pipe and the pair of compression chambers,
The injection channel is
a first flow path into which the coolant from the injection pipe flows;
a second flow path that is connected to the first flow path and supplies the refrigerant that has flowed into the first flow path to one of the pair of compression chambers;
One of the first flow path and the second flow path is branched to supply the refrigerant flowing into either the first flow path or the second flow path to the other of the pair of compression chambers. and a third flow path,
The injection channel is
When the angle between the winding end portion, which is the end of the outer peripheral side of the first spiral tooth, and the injection flow path in the winding direction of the first spiral tooth to the outer peripheral side is set as a variable θ [degree],
90≤θ≤110
It is formed at a position where
The second flow path is a flow path that supplies refrigerant to be compressed in one of the pair of compression chambers toward a gap between the winding end portion of the first spiral tooth and the second spiral tooth. ,
The third flow path is a flow path that supplies the refrigerant compressed in the other of the pair of compression chambers toward the gap between the winding end portion of the second spiral tooth and the first spiral tooth. ,
When the formation position of the injection passage is at a position where the refrigerant can be evenly distributed to the pair of compression chambers, the central axis of the second passage and the third passage with respect to the central axis of the first spiral tooth is The angles are each 45 degrees,
The angle of the central axis of the second flow path with respect to the central axis of the first spiral tooth is
When the formation position of the injection passage is closer to the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, the angle is smaller than 45 degrees,
When the formation position of the injection passage is farther from the winding end portion of the first spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, it is formed to be larger than 45 degrees. and
The angle of the central axis of the third flow path with respect to the central axis of the first spiral tooth is
When the formation position of the injection passage is closer to the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, the angle is smaller than 45 degrees,
When the formation position of the injection passage is farther from the winding end portion of the second spiral tooth than the position where the refrigerant can be evenly distributed to the pair of compression chambers, it is formed to be larger than 45 degrees. scroll compressor. The scroll compressor according to claim 5 or 6, wherein the angle of the central axis of the second flow path with respect to the central axis of the first spiral tooth is 0 degrees or more and 70 degrees or less. The scroll compressor according to any one of claims 5 to 7, wherein the angle of the central axis of the third flow path with respect to the central axis of the first spiral tooth is 0 degrees or more and 70 degrees or less. . The scroll compressor according to any one of claims 1 to 8, wherein the injection pipe is fixed to the first bed plate. The closed container is
The scroll compressor according to any one of claims 1 to 9, comprising a lid portion having a flat surface through which the injection pipe penetrates. The closed container is
A bent portion forming a corner of the closed container,
The injection tube is
Assuming that the inner diameter of the lid portion is a variable DA, the width of the bent portion is a variable R, and the inner diameter of the injection pipe is a variable DB,
The position X between the vertical center of the scroll compressor and the central axis of the injection pipe is
X<DA/2-R-DB/2
11. The scroll compressor of claim 10 arranged to satisfy:

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