JP7308986B2 - Scroll compressor and refrigeration cycle equipment - Google Patents

Description

The present disclosure relates to a scroll compressor and a refrigeration cycle device including the same.

The scroll compressor includes a fixed scroll having involute-shaped spiral teeth protruding from a fixed base plate, and an oscillating scroll having involute-shaped spiral teeth protruding from an oscillating base plate. It is provided so that the spiral teeth mesh with each other. At this time, the fixed scroll and the orbiting scroll are in contact with each other at their spiral side surfaces with the phases of their spiral teeth relatively shifted by 180°. Then, the orbiting scroll is caused to revolve with respect to the fixed scroll, and the plurality of compression chambers formed by the fixed scroll and the orbiting scroll are gradually decreased from the outer side to the inner side, whereby the compressor is Compress the refrigerant gas inside. As a result, the scroll compressor discharges the compressed refrigerant gas inside the compression chamber from the central discharge port.

In such a scroll compressor, the fixed scroll and the orbiting scroll have their spiral teeth brought into close contact with each other's base plate for the purpose of suppressing leakage of compressed refrigerant gas into adjacent compression chambers. are interlocked in a state of Therefore, the spiral teeth of the fixed scroll and the oscillating scroll receive a load from the refrigerant gas compressed during the compression process, and thus, the root portions located on the fixed bed plate side and the oscillating bed plate side, which are the base plates, respectively, are deformed. Stress is generated. Therefore, in such a scroll compressor, the corners of the root portion at the center of the spiral and the tip of the spiral tooth on the opposite side are each formed into a curved shape, that is, a process of adding a radius. had been applied.

Here, scroll compressors mounted in air conditioners, refrigerators, water heaters, etc. include a high-pressure shell in which a space in contact with the shell outer cover is filled with high-pressure refrigerant after the compression process, and a low-pressure refrigerant before the compression process. There are two types: a low pressure shell filled with refrigerant; Conventionally, it is necessary to provide a sealing material at the tips of the spiral teeth of a scroll compressor having a low-pressure shell in order to prevent leakage between compression chambers. Therefore, in such a scroll compressor, in order to prevent the seal material from slipping down from the tip of the spiral tooth during operation, a seal material fall prevention wall is provided on both sides of the seal material. However, in this case, the thickness of the sealing material fall prevention wall must be ensured in order to hold the sealing material, and the provision of the sealing material fall prevention wall has been a limitation in reducing the thickness of the spiral tooth.

Therefore, in order to reduce the tooth thickness of the spiral tooth, it has been proposed to form a sealing material drop prevention wall only on one side of the sealing material (see, for example, Patent Document 1). In the scroll compressor of Patent Document 1, by providing the seal material drop prevention wall only on one side of the seal material, the tooth thickness of the spiral tooth is reduced to form a large compression chamber, which is compared to a compressor of the same size. It was intended to increase the intake volume.

JP-A-11-230064

However, in the compressor described in Patent Document 1, since the seal material drop prevention wall is constructed only from one side of the seal material, the sealing material may be caught by the opposing tooth bottom surface, or the reversal of the high and low pressure leakage direction in an overcompressed state may cause the seal to fail. The material could fall out of the groove. As described above, the compressor described in Patent Document 1 has a reliability problem.

The present disclosure is intended to solve the above-described problems, and an object thereof is to provide a scroll compressor and a refrigeration cycle device including the scroll compressor capable of improving performance while ensuring reliability. It is something to do.

A scroll compressor according to the present disclosure includes: a fixed scroll having an involute-shaped fixed-side spiral tooth formed to protrude from a fixed base plate; and a sealing material provided at the tip of the fixed-side spiral tooth; an oscillating scroll having an involute-shaped oscillating-side spiral tooth protruding from an oscillating base plate; The scroll and the orbiting scroll are combined so that the fixed side spiral teeth and the orbiting side spiral teeth are meshed with each other, and a compression chamber for compressing the refrigerant is provided between the fixed scroll and the orbiting scroll. In the scroll compressor, the fixed scroll and the orbiting scroll have seal grooves for holding the sealing material formed at the tips of the fixed-side spiral teeth and the orbiting-side spiral teeth, respectively. The seal groove has a bottom portion serving as a bottom portion, and a sealant fall prevention wall serving as a side wall portion continuously from the bottom portion, and the sealant fall prevention wall includes the fixed side spiral tooth and the The bottom portion of the fixed-side spiral tooth is formed only on the outward surface side of the swing-side spiral tooth, and the bottom portion of the fixed-side spiral tooth extends from the tooth bottom located on the fixed base plate side to the inward-surface-side end of the fixed-side spiral tooth. is higher than the height from the tooth bottom to the end of the seal groove on the outward surface side of the bottom surface portion, and the height from the tooth bottom to the end of the outward surface of the fixed-side spiral tooth height, and the bottom portion of the rocking-side spiral tooth is the height from the tooth bottom located on the rocking base plate side to the end of the rocking-side spiral tooth on the inward surface side is higher than the height from the tooth bottom to the end of the bottom surface of the seal groove on the outward surface side and lower than the height from the tooth bottom to the end of the outward surface of the oscillation-side spiral tooth It is set.

A refrigeration cycle apparatus according to the present disclosure includes a refrigerant circuit having at least a compressor, a condenser, an expansion valve, and an evaporator, and uses the above scroll compressor as the compressor.

According to the present disclosure, by providing the sealing material drop prevention wall only on the outward surface side of the seal grooves of the fixed-side spiral tooth and the oscillating-side spiral tooth, the tooth thickness of the spiral tooth is reduced, thereby reducing the spiral intake volume. can be expanded to extend the upper limit of compressor capacity. In addition, in the bottom portion, the height from the tooth bottom located on the fixed base plate and rocking base plate side to the end of the inward surface side of the fixed side spiral tooth and the rocking side spiral tooth of the bottom portion is It is set higher than the height to the end of the outward surface side of the fixed-side spiral tooth and the swing-side spiral tooth of the bottom portion. That is, by increasing the height of the high-pressure side of the bottom surface where the sealing material is arranged, it is possible to prevent the sealing material from falling during operation. Thus, according to the scroll compressor and the refrigeration cycle apparatus including the same according to the present disclosure, it is possible to improve performance while ensuring reliability.

1 is an explanatory diagram schematically showing a longitudinal section of a scroll compressor according to Embodiment 1; FIG. FIG. 2 is an explanatory view schematically showing a cross section of a compression chamber in the scroll compressor of FIG. 1; FIG. 2 is a longitudinal sectional view schematically showing an enlarged portion of a compression chamber in the scroll compressor of FIG. 1; FIG. 4 is an enlarged cross-sectional view showing a main part in the compression chamber of FIG. 3; FIG. 2 is a longitudinal sectional view schematically showing a fixed scroll in the scroll compressor of FIG. 1; FIG. 6 is an enlarged cross-sectional view showing a main part of the fixed scroll of FIG. 5; FIG. 2 is a longitudinal sectional view schematically showing an orbiting scroll in the scroll compressor of FIG. 1; FIG. 8 is an enlarged cross-sectional view showing a main part of the orbiting scroll of FIG. 7; FIG. 5 is an explanatory diagram showing, as a comparative example, changes in state of compression chambers in a conventional scroll compressor every 90°. FIG. 4 is an explanatory diagram showing state changes every 90° in a compression chamber of the scroll compressor according to Embodiment 1; FIG. 3 is a schematic cross-sectional view showing the shape of a seal groove formed on a tooth tip located on the center side of an oscillation-side spiral tooth in the scroll compressor of FIG. 2 ; 4 is a graph showing a comparison of swirl intake volumes of scroll compressors according to Embodiments 1 and 2. FIG. 4 is a graph showing the correlation between the rotation speed and capacity of the scroll compressors according to Embodiments 1 and 2. FIG. FIG. 7 is a schematic cross-sectional view showing the shape of a seal groove at the tip of the swing-side spiral tooth of the scroll compressor according to the modification of Embodiment 1; FIG. 6 is a longitudinal sectional view schematically showing a fixed scroll of a scroll compressor according to Embodiment 2; FIG. 8 is a longitudinal sectional view schematically showing an orbiting scroll of a scroll compressor according to Embodiment 2; FIG. 11 is a schematic cross-sectional view showing the shape of a seal groove at the tip of an oscillation-side spiral tooth of a scroll compressor according to Embodiment 3; FIG. 11 is a refrigerant circuit diagram showing an example of a refrigeration cycle apparatus according to Embodiment 4;

Hereinafter, embodiments of a scroll compressor and a refrigeration cycle device according to the present disclosure will be described with reference to the accompanying drawings. It should be noted that the configurations of the components shown in the entire specification and drawings are merely examples and are not limited to these descriptions. In other words, the present disclosure can be modified as appropriate within a range not contrary to the gist or idea that can be read from the scope of claims and the entire specification. Further, the technical idea of the present disclosure also includes a scroll compressor and a refrigerating cycle device that involve such changes. Furthermore, in each figure, the same reference numerals are assigned to the same or equivalent items, which are common throughout the specification .

Embodiment 1.
<Configuration of Scroll Compressor 1>
A scroll compressor 1 according to Embodiment 1 will be described with reference to FIGS. 1 to 3. FIG. FIG. 1 is an explanatory diagram schematically showing a longitudinal section of a scroll compressor 1 according to Embodiment 1. FIG. FIG. 2 is an explanatory view schematically showing a cross section of the compression chamber 31 in the scroll compressor 1 of FIG. 1. As shown in FIG. FIG. 3 is a longitudinal sectional view schematically showing an enlarged portion of the compression chamber 31 in the scroll compressor 1 of FIG.

As shown in FIG. 1 , the scroll compressor 1 includes a compression mechanism section 10 and a motor 20 as an electric mechanism for driving the compression mechanism section 10 inside a shell 2 that is an airtight container. In the case of the first embodiment, the scroll compressor 1 is a so-called low-pressure shell type compressor in which the inside of the shell 2 is filled with refrigerant before being compressed by the compression mechanism section 10 . Carbon dioxide, for example, is used as the refrigerant compressed by the scroll compressor 1 . Note that the refrigerant is not limited to carbon dioxide, and other refrigerants can be widely applied.

The shell 2 has an upper shell 2a, a lower shell 2b, and a body shell 2c to constitute the outer shell of the scroll compressor 1, and has an oil reservoir 9 at its lower portion. The shell 2 has a cylindrical shape with a bottom, and a dome-shaped upper shell 2a closes an upper portion of the trunk shell 2c, and a lower shell 2b closes a lower portion of the trunk shell 2c.

The compression mechanism section 10 includes a fixed scroll 11 and an orbiting scroll 12 . As shown in FIG. 1 , the fixed scroll 11 includes a fixed base plate 110 and involute-shaped fixed spiral teeth 111 provided on the fixed base plate 110 . The oscillating scroll 12 includes an oscillating base plate 120 and an involute-shaped oscillating-side spiral tooth 121 provided on the oscillating base plate 120 . Further, as shown in FIGS. 2 and 3, a sealing material 3, which will be described later, is arranged on the tooth tips 111a and 121a of the fixed-side spiral tooth 111 and the oscillation-side spiral tooth 121, respectively. The compression mechanism 10 has a symmetrical spiral shape in which the fixed-side spiral teeth 111 of the fixed scroll 11 and the orbiting-side spiral teeth 121 of the orbiting scroll 12 are meshed in opposite phases with respect to the rotation center of the main shaft 8. is arranged in the shell 2 in the state of

Compression mechanism 10 is supported by frame 6 . The frame 6 is fixed to the inner peripheral surface of the shell 2 by shrink fitting, welding, or the like. The frame 6 is arranged within the shell 2 between the compression mechanism section 10 and the motor 20 . A shaft hole 6a is formed in the central portion of the frame 6, and the main shaft 8 is passed through the shaft hole 6a. A subframe 7 is provided below the motor 20 in the shell 2 . The subframe 7 is fixed to the inner peripheral surface of the shell 2 by shrink fitting, welding, or the like.

The motor 20 includes a rotor 21 as a rotor and a stator 22 as a stator. The compression mechanism section 10 is driven via. The rotor 21 is provided on the inner peripheral side of the stator 22 and attached to the main shaft 8 . The stator 22 is connected to a glass terminal (not shown) between the frame 6 and the stator 22 by a lead wire (not shown) in order to obtain electric power from the outside. The stator 22 rotates the rotor 21 with electric power supplied from the outside. The rotor 21 rotates the main shaft 8 by rotating.

The rotor 21 of the motor 20 is fixed to the main shaft 8 by a technique such as shrink fitting, and the main shaft 8 drives the compression mechanism section 10 by rotating with the rotation of the rotor 21 . Refrigerating machine oil 9 a is stored in an oil reservoir 9 positioned below the scroll compressor 1 . An oil pump 81 as an oil supply mechanism is fixed to the lower end of the main shaft 8 . The oil pump 81 is, for example, a positive displacement pump such as a trochoid pump. As the main shaft 8 rotates, the oil pump 81 pumps up the refrigerating machine oil 9 a stored in the oil reservoir 9 through an oil supply passage 82 formed inside the main shaft 8 . The pumped refrigerating machine oil 9 a is supplied to the swing bearing 123 and the compression chamber 31 for the purpose of lubricating the swing bearing 123 and sealing the gap of the compression chamber 31 .

A main shaft portion 84 is provided below the eccentric shaft portion 83 in the main shaft 8 . The eccentric shaft portion 83 is arranged at a position eccentric to the main shaft portion 84 . The main shaft portion 84 is fitted in the main bearing 15 via the sleeve 14, and slides on the main bearing 15 via an oil film of the refrigerator oil 9a. The main bearing 15 is fixed to the frame 6 by press-fitting a bearing material such as a copper-lead alloy used for slide bearings.

The sleeve 14 is a tubular member provided between the frame 6 and the main bearing 15 . The sleeve 14 absorbs tilting between the frame 6 and the main shaft 8 .

The slider 4 a is a cylindrical member attached to the outer peripheral surface of the upper portion of the main shaft 8 . The slider 4 a is positioned on the inner side surface of the lower portion of the orbiting scroll 12 . That is, the orbiting scroll 12 is attached to the main shaft 8 via the slider 4a. As a result, the orbiting scroll 12 rotates as the main shaft 8 rotates. A swing bearing 123 is provided between the swing scroll 12 and the slider 4a.

The first balancer 4 b is attached to the main shaft 8 . A first balancer 4 b is positioned between the frame 6 and the rotor 21 . The first balancer 4b offsets the imbalance caused by the orbiting scroll 12 and the slider 4a.

A second balancer 8 a is attached to the main shaft 8 . The second balancer 8 a is positioned between the rotor 21 and the subframe 7 and attached to the lower surface of the rotor 21 . The second balancer 8a offsets the imbalance caused by the orbiting scroll 12 and the slider 4a.

The subframe 7 is provided below the motor 20 inside the shell 2 and rotatably supports the main shaft 8 via a subbearing 16 . A central portion of the sub-frame 7 is provided with a sub-bearing 16 consisting of a ball bearing, which radially supports the main shaft 8 below the motor 20 . In addition, the sub-bearing 16 may have another bearing configuration other than the ball bearing. A sub-shaft portion 85 of the main shaft 8 below the motor 20 is fitted with the sub-bearing 16 and slides on the sub-bearing 16 via an oil film of the refrigerating machine oil 9a. The axial centers of the main shaft portion 84 and the sub-shaft portion 85 are aligned with the axial center of the main shaft 8 .

The shell 2 is provided with a suction pipe 101 for sucking the refrigerant and a discharge pipe 102 for discharging the refrigerant. A suction pipe 101 is provided on the side wall of the shell 2 . The intake pipe 101 is a pipe for sucking gaseous refrigerant into the shell 2 . Below the frame 6 in the shell 2, a low-pressure suction space 70 filled with refrigerant drawn from the suction pipe 101 is formed.

A discharge pipe 102 is provided in the upper portion of the shell 2 . The discharge pipe 102 is a pipe that discharges the compressed refrigerant to the outside of the shell 2 . In the shell 2 , a high-pressure discharge space 71 filled with refrigerant discharged from the compression mechanism 10 is provided on the side of the discharge pipe 102 positioned above the fixed base plate 110 of the fixed scroll 11 of the compression mechanism 10 . is formed. Above the shell 2, there is an injection mechanism 40 that injects the refrigerant introduced from the outside into a refrigerant suction space 73 located on the outer peripheral side of the oscillation-side spiral tooth 12b, which will be described later, or into the compression chamber 31, which will be described later. It is preferable that the injection pipe 103 is connected.

<Compression Mechanism Section 10>
Next, the compression mechanism section 10 of the scroll compressor 1 according to the first embodiment will be described with reference to FIGS. 4 to 8 in addition to FIGS. 1 to 3 described above. 4 is an enlarged cross-sectional view showing a main portion A in the compression chamber 31 of FIG. 3. FIG. FIG. 5 is a longitudinal sectional view schematically showing the fixed scroll 11 in the scroll compressor 1 of FIG. 1. FIG. 6 is an enlarged cross-sectional view showing a main portion B of the fixed scroll 11 of FIG. 5. FIG. FIG. 7 is a longitudinal sectional view schematically showing the orbiting scroll 12 in the scroll compressor 1 of FIG. 1. As shown in FIG. FIG. 8 is an enlarged cross-sectional view showing essential parts of the orbiting scroll 12 of FIG. In the following description, the fixed-side spiral tooth 111 and the rocking-side spiral tooth 121 may be referred to as the spiral teeth 111 and 121 for convenience.

As shown in FIG. 1 , the compression mechanism section 10 of the scroll compressor 1 includes a fixed scroll 11 and an orbiting scroll 12 . The fixed scroll 11 is fixedly arranged with respect to the frame 6 . The orbiting scroll 12 is arranged in the space between the fixed scroll 11 and the frame 6 . An Oldham ring 13 is arranged between the orbiting scroll 12 and the frame 6 to prevent the orbiting scroll 12 from rotating.

The Oldham ring 13 is arranged on the thrust surface opposite to the upper surface of the orbiting scroll 12 on which the orbiting spiral teeth 121 are formed, and prevents the orbiting scroll 12 from rotating. That is, the Oldham ring 13 functions to prevent the orbiting scroll 12 from rotating on its axis and to allow the orbiting scroll 12 to pivot. The upper and lower surfaces of the Oldham ring 13 are formed with claws (not shown) projecting perpendicularly to each other. The claws of the Oldham ring 13 are fitted into Oldham grooves (not shown) formed in the orbiting scroll 12 and the frame 6, respectively.

The fixed scroll 11 and the orbiting scroll 12 are arranged so that the fixed side spiral tooth 111 and the orbiting side spiral tooth 121 are opposed to each other so that the fixed side spiral tooth 111 and the orbiting side spiral tooth 121 are engaged with each other. A compression chamber 31 is formed in a space where the spiral teeth 121 are meshed. When the orbiting scroll 12 is oscillatingly moved by the main shaft 8 , the gaseous refrigerant is compressed in the compression chamber 31 . Details of the compression chamber 31 will be described later.

Specifically, as shown in FIG. 1 , the fixed spiral tooth 111 is arranged to extend downward on the lower surface side of the fixed base plate 110 in the assembled state of the fixed scroll 11 . A discharge port 11a is formed through the central portion of the fixed scroll 11 for discharging compressed gas as a heating medium. Further, a reed valve 50 is installed at the outlet of the discharge port 11a of the fixed scroll 11 so as to cover the outlet. The reed valve 50 opens and closes the discharge port 11a to prevent backflow of the fluid. The valve guard 51 is a long plate-like member thicker than the reed valve 50, and supports the reed valve 50 from the rear side when the reed valve 50 is opened, thereby restricting the movable range of the reed valve 50. , to protect the reed valve 50 from deformation.

Further, the swing-side spiral tooth 121 is arranged to extend upward on the upper surface side of the swing base plate 120 in the assembled state of the swing scroll 12 . The orbiting scroll 12 performs a revolving motion, in other words, an oscillating motion with respect to the fixed scroll 11 , and its rotation motion is restricted by the Oldham ring 13 .

A cylindrical boss portion 122 is formed at the center of the back surface of the rocking base plate 120 of the rocking scroll 12 on the side opposite to the surface on which the rocking-side spiral teeth 121 are formed. A swing bearing 123 is fixed inside the boss portion 122 . The swing bearing 123 is made of a bearing material such as a copper-lead alloy used for sliding bearings, and the bearing material is press-fitted inside the boss portion 122 and fixed.

A slider 4 with a balancer is rotatably arranged inside the swing bearing 123 . The balancer-equipped slider 4 includes a cylindrical slider 4a and a first balancer 4b, which are joined using a technique such as shrink fitting. The slider 4a is fitted to an eccentric shaft portion 83, which will be described later, provided at the upper end of the main shaft 8 so as to be relatively movable, and automatically adjusts the swing radius of the swing scroll 12. As shown in FIG. The slider 4a is provided so that the fixed-side spiral tooth 111 and the swing-side spiral tooth 121 are always in contact with each other when the swing scroll 12 swings. The first balancer 4b is located on the side of the slider 4a and is provided to cancel the centrifugal force of the orbiting scroll 12 and suppress the vibration of the compression element.

In this way, the orbiting scroll 12 is connected to the eccentric shaft portion 83 of the main shaft 8 via the slider with balancer 4 , and the slider with balancer 4 automatically adjusts the oscillation radius while rotating the main shaft 8 . oscillating motion with A cylindrical bearing operation space 72 is formed between the back surface of the swing bed plate 120 of the swing scroll 12 and the frame 6 . The swing bearing 123 rotates within the bearing motion space 72 together with the balancer-equipped slider 4 during the swing motion of the swing scroll 12 . A slider without a balancer function may be mounted instead of the slider with balancer 4 .

Since the orbiting scroll 12 revolves according to the number of revolutions of the main shaft 8, the centrifugal force applied to the eccentric shaft portion 83 of the main shaft 8 increases under high-speed operation conditions. For this reason, it is preferable that the orbiting scroll 12 is made of a lightweight material such as aluminum instead of casting. That is, if the orbiting scroll 12 is light, the weight of the first balancer 4b and the balancer-equipped slider 4 can be reduced, and the cost and the size of the scroll compressor 1 can be reduced. Further, by reducing the centrifugal force generated by the orbiting scroll 12 during operation, the load applied to the orbiting bearing 123 can be reduced, and the slidability can be improved. In addition, the material of the orbiting scroll 12 is not limited to the aluminum material, and a casting material, a resin material, or the like can also be applied.

As shown in FIGS. 1 and 2, between the fixed side spiral tooth 111 and the oscillating side spiral tooth 121, as the main shaft 8 rotates, from the radially outer side toward the inner side of the spiral center side, Therefore, a plurality of compression chambers 31 with reduced volumes are formed. Each compression chamber 31 has a crescent-shaped cross section, and the refrigerant taken in from the outer peripheral side is continuously and smoothly compressed toward the center of the spiral to increase the pressure, and the closer to the center of the spiral, the higher the temperature. Become.

That is, the plurality of compression chambers 31 have a high-pressure side compression chamber 31a on the spiral center side of the fixed side spiral tooth 111 and the swinging side spiral tooth 121, and a low pressure side compression chamber 31b on the outer peripheral side where the refrigerant is taken in. With such a compression process, the internal temperature of the compression chamber 31 rises, and the fixed-side spiral tooth 111 and the oscillating-side spiral tooth 121 thermally expand. tooth height increases.

Here, in the case of the fixed side spiral tooth 111, the tooth height means the height from the tooth bottom 112 located on the fixed base plate 110 side to the tooth tip 111a of the fixed side spiral tooth 111 of the fixed scroll 11, which will be described later. . In the case of the oscillation-side spiral tooth 121, the tooth height is the height from the tooth bottom 124 located on the oscillation bed plate 120 side of the oscillation-side spiral tooth 121 of the oscillation scroll 12, which will be described later, to the tooth tip 121a. means

As described above, since the tooth heights of the fixed side spiral tooth 111 and the oscillating side spiral tooth 121 increase due to thermal expansion, as shown in FIGS. A gap is provided between the tooth tops 111a and 121a. Specifically, when the fixed scroll 11 and the orbiting scroll 12 mesh the fixed side spiral tooth 111 and the orbiting side spiral tooth 121, these tooth tops 111a and 121a and the tooth bottom 124 facing them , and 112, a minute tip clearance 33 is formed.

The tip clearance 33 is provided for the purpose of preventing contact between the tip 111a and the tooth bottom 124 and contact between the tip 121a and the tooth bottom 112 due to thermal expansion. In this case, refrigerant leakage from the high-pressure side compression chamber 31a to the low-pressure side compression chamber 31b, as shown in FIG. Circumferential direction leakage (indicated by the dashed arrow in FIG. 2) due to minute circumferential gaps 34 generated when the side surfaces of the tooth 111 and the swing-side spiral tooth 121 are in contact with each other.

Therefore, in the compression mechanism portion 10 of Embodiment 1, as shown in FIGS. A sealing material 3 is provided to The sealing material 3 is generally a molded product made of a resin-based material, and for example, a PPS (polyphenylene sulfide)-based resin is used. The material of the sealing material 3 is not limited to PPS, and is formed using one selected from the group including polyetheretherketone-based resins and polyimide-based resins as appropriate according to the intended use. The optimum resin material can be applied. Moreover, since the sealing material 3 is a resin molded product, the cross-sectional shape, the total length and the number of turns can be arbitrarily set, and a material suitable for the application of the mounted compressor can be used. Sealing material 3 is arranged and held in seal grooves 113 and 125 formed in tooth tips 111a and 121a of fixed-side spiral tooth 111 and oscillating-side spiral tooth 121, respectively.

Here, the seal grooves 113 and 125 formed in the addendums 111a and 121a of the fixed side spiral tooth 111 and the oscillation side spiral tooth 121 will be described with reference to FIGS. 4 to 8. FIG.

As shown in FIGS. 4 to 6, the seal groove 113 formed in the tip 111a of the fixed-side spiral tooth 111 has a bottom portion 115 as a bottom portion and a side wall portion continuous from the bottom portion 115 for preventing the sealing material from falling. a wall 114; In this case, the sealing material drop prevention wall 114 is formed only on the outward surface side of the fixed spiral tooth 111 . In addition, the seal groove 113 has a side surface portion 116 which is a contact surface with the seal material 3 located on the inner peripheral side of the seal material drop prevention wall 114 continuous from the bottom surface portion 115 and is formed perpendicular to the fixed base plate 110 . It is

As shown in FIGS. 4, 7 and 8, the seal groove 125 formed in the tooth tip 121a of the swing-side spiral tooth 121 has a bottom surface portion 127 which is a bottom portion and a side wall portion continuing from the bottom surface portion 127. and a sealing material fall prevention wall 126 having a In this case, the sealing material drop prevention wall 126 is formed only on the outward surface side of the swing-side spiral tooth 121 . In addition, the seal groove 125 has a side surface portion 128 which is a surface in contact with the seal material 3 located on the inner peripheral side of the seal material fall prevention wall 126 continuous from the bottom surface portion 127 and is perpendicular to the rocking base plate 120 . formed.

As shown in FIG. 4, the bottom portion 115 of the fixed-side spiral tooth 111 has a height h1 from the tooth bottom 112 located on the fixed base plate 110 side to the end of the fixed-side spiral tooth 111 on the inward surface side. It is set higher than the height h2 from the bottom 112 to the end of the fixed-side spiral tooth 111 on the outward surface side.

As shown in FIG. 4, the bottom portion 127 of the oscillating-side spiral tooth 121 has a height h3 from the tooth bottom 124 located on the oscillating base plate 120 side to the end of the oscillating-side spiral tooth 121 on the inward surface side. is set higher than the height h4 from the tooth bottom 124 to the end of the swinging side spiral tooth 121 on the outward surface side.

In other words, the bottom surface portions 115 and 127 are inclined toward the tooth bottoms 112 and 124 as they progress from the inward surface side to the outward surface side of the fixed side spiral tooth 111 and the oscillating side spiral tooth 121 .

The sealing material 3 installed on the tooth tip 111a of the fixed side spiral tooth 111 floats due to the pressure difference between the compression chambers 31 adjacent in the radial direction and the circumferential direction, and as shown in FIG. , and the sealing material fall prevention wall 114 . The seal material 3 installed on the tooth tip 121a of the swing-side spiral tooth 121 floats due to the pressure difference between the compression chambers 31 adjacent in the radial direction and the circumferential direction, and faces each other as shown in FIG. It is pressed against the tooth bottom 112 and the sealing material fall prevention wall 126 . This prevents refrigerant leakage between high and low pressures between the compression chambers 31 adjacent in the radial direction and the circumferential direction as shown in FIG.

Here, although not shown, in the tooth tip, the seal groove has sealing material drop prevention walls on both sides of the outward surface side and the inward surface side. It was necessary to avoid contact with the tip of the tooth. In order to secure the strength of the spiral tooth, the root portion is generally connected in a curved shape toward the tooth bottom. That is, so-called R processing is applied to the root portion of the spiral tooth. For this reason, conventionally, the tip of the spiral tooth is rounded and chamfered with a radius of curvature larger than that of the root of the spiral tooth.

In contrast, in the fixed-side spiral tooth 111 and the rocking-side spiral tooth 121 of Embodiment 1, the sealing material 3 is formed by the tooth roots 124 and the tooth roots 124 and 124 of the rocking-side spiral tooth 121 and the fixed-side spiral tooth 111, respectively. It slides in contact with 112 . In other words, in the case of the first embodiment, the sealing material 3 provided on the addendums 111a and 121a is applied to the bottoms 124 and 112 of the oscillation-side spiral tooth 121 and the fixed-side spiral tooth 111 facing them. It slides along the root. Therefore, it is not necessary to perform rounding and chamfering on the tip of the tooth with a radius of curvature larger than the radius of curvature for rounding the root portion of the spiral tooth as in the conventional art. Moreover, compared with the conventional scroll compressor, it is possible to reduce refrigerant leakage from the high-pressure side compression chamber 31a to the low-pressure side compression chamber 31b in the compression process.

FIG. 9 is an explanatory diagram showing, as a comparative example, changes in the state of the compression chamber 330 at every 90° in a conventional scroll compressor. 10A and 10B are explanatory diagrams showing state changes at every 90° in the compression chamber 31 of the scroll compressor 1 according to Embodiment 1. FIG. 9 and 10 show how the compression chamber 330 or 31 changes state by rotating the spiral tooth 320 or 121 with respect to the spiral tooth 310 or 111 at every 90° from the top. there is

As shown in FIG. 9, conventionally, the seal grooves 310a and 320a of the spiral teeth 310 and 320 have sealing material drop prevention walls 311 and 321 on the outward surface side of the spiral teeth 310 and 320, and seal the seal material fall prevention walls 311 and 321 on the inward surface side of the spiral teeth 310 and 320, respectively. It had material fall prevention walls 312 and 322 . As a result, the seal grooves 310a and 320a hold the seal material 3 from both the outward surface side and the inward surface side of the spiral teeth 310 and 320, thereby preventing the seal material 3 from falling during operation. was Here, if the conventional sealing material fall prevention walls 311, 312 and 321, 322 are simply replaced with only the seal material fall prevention walls 311 and 321 on one side on the outward surface side, the seal material fall prevention wall 312 on the inward surface side and 322 is just removed. Therefore, the contact surfaces of the sealing material fall prevention walls 311 and 321 that hold the sealing material 3 are only the flat bottom surface (not shown) of the sealing groove and the side surface (not shown) following it. Therefore, there is a possibility that the seal material 3 may fall from the seal grooves 310a and 320a due to being caught by the opposing tooth roots, or due to reversal of high and low pressure leakage directions in an over-compressed state, or the like. In addition, if the sealing material 3 falls, there is a concern that the spiral teeth and the discharge port bearing surface will be damaged due to foreign matter being caught, resulting in deterioration in performance, damage to the compressor, and the like.

On the other hand, as shown in FIG. 4, in the seal groove 113 of the fixed-side spiral tooth 111 of the first embodiment, the height h1 from the tooth bottom 112 to the end of the bottom surface 115 on the inward surface side is It is set higher than the height h2 from the bottom 112 to the end of the bottom surface portion 115 on the outward surface side. Further, the seal groove 125 of the swing-side spiral tooth 121 has a height h3 from the tooth bottom 124 to the end of the bottom surface 127 on the inward surface side, and the height h3 from the tooth bottom 124 to the end of the bottom surface 127 on the outward surface side is is set higher than the height h4 of . That is, in the seal grooves 113 and 125 of the first embodiment, the bottom surfaces 115 and 127 are inclined toward the tooth bottoms 112 and 124 as they progress from the inward surface side end to the outward surface side end. ing. Therefore, the bottom surface portions 115 and 127, which are part of the shape of contact surfaces of the sealing material fall prevention walls 114 and 126 that hold the sealing material 3, have heights between the ends on the inward surface side and the ends on the outward surface side. It has a shape with differences h1-h2 and h3-h4.

As a result, even if the sealing material fall prevention walls 114 and 126 are provided only on one side of the spiral teeth 111 and 121 on the outward surface side, the sealing material 3 is prevented from falling due to being caught by the opposing tooth roots 124 and 112. It can be prevented. In addition, it is possible to prevent the sealing member 3 from dropping due to reversal of the high and low pressure leakage directions in the overcompressed state. Therefore, in the scroll compressor 1 of Embodiment 1, reliability can be improved. In addition, by providing seal material fall prevention walls 114 and 126 only on one side of each spiral tooth 111 and 121 on the outward surface side, each spiral tooth 111 and The tooth thickness, which is the thickness of 121, can be reduced by one side of the sealing material drop prevention wall. As a result, in the scroll compressor 1 of Embodiment 1 shown in FIG. 10, compared with the conventional shape shown in FIG. As a result, the intake volume can be increased.

As shown in FIG. 4 , a gap 35 is formed between the bottom surface portions 115 and 127 of the seal grooves 113 and 125 and the sealing material 3 . The dimension d of this gap 35 is determined by the distance between the lowest portion of one spiral tooth 121 located on the center side of the sealing material fall prevention wall 126 and the other base plate (fixed base plate 110). It is the length obtained by subtracting the longest part of the material 3. The height differences h1-h2 and h3-h4 of the bottom surfaces 115 and 127 in the seal grooves 113 and 125 correspond to the gaps 35 formed between the sealing material 3 and the ends of the bottom surfaces 115 and 127 on the outward surface side. is preferably larger than the dimension d of

In other words, in the fixed-side spiral tooth 111, the seal groove 113 has a height h1 from the tooth bottom 112 to the inward-facing end of the bottom surface portion 115, and a height h1 from the tooth bottom 112 to the outward-facing end of the bottom surface portion 115. It is desirable that the difference h1-h2 between the height h2 to the bottom portion 115 and the seal member 3 at the end of the bottom portion 115 on the outward surface side is set larger than the dimension d of the gap 35. In the swing-side spiral tooth 121, the seal groove 125 has a height h3 from the tooth bottom 124 to the end of the bottom surface portion 127 on the inward surface side, and a height h3 from the tooth bottom 124 to the end of the bottom surface portion 127 on the outward surface side. It is desirable that the difference h3-h4 between the height h4 up to the bottom portion 127 and the seal member 3 at the end of the bottom portion 127 on the outward surface side be set larger than the dimension d of the gap 35.

The sealing material 3 floats due to the pressure difference between the compression chambers 31, and when the amount of floating of the sealing material 3 becomes equal to or greater than the height differences h1-h2 and h3-h4 of the bottom surfaces 115 and 127, the sealing material 3 , on the inward surfaces of the seal grooves 113 and 125. Therefore, there is a possibility that the sealing material 3 may drop due to being caught by the opposing tooth bottoms 112 and 124 and due to reversal of the high and low pressure leak directions in the overcompressed state.

On the other hand, in the scroll compressor 1 of Embodiment 1, the height differences h1-h2 and h3-h4 are replaced by the dimension d By setting it to be larger than , it is possible to prevent the sealing material from falling. Since the sealing material 3 thermally expands and contracts, the dimension d of the gap 35 may increase as the temperature decreases. Also, the dimension d of the gap 35 may increase due to wear. Therefore, it is more desirable that the height differences h1-h2 and h3-h4 are several times larger than the dimension d of the gap 35. FIG.

Further, although not shown, when the sealing material fall prevention walls are provided on both the outward surface side and the inward surface side of the seal material, the end portion of the seal material fall prevention wall, the root portion of the opposing spiral tooth, come into contact with each other, and spiral damage occurs due to abnormal temperature rise and seizure due to metal contact. Therefore, when the sealing material fall prevention walls are provided on both sides of the sealing material, the tip of the tooth is chamfered, or the root is rounded and chamfered. However, there is a concern that a gap is generated in the chamfered portion, and refrigerant leaks from the gap in the circumferential direction of the spiral teeth, degrading the performance of the compressor.

On the other hand, in the spiral teeth 111 and 121 of Embodiment 1, since the inward surfaces of the tooth tips 111a and 121a are formed of the sealing material 3, the sealing material 3 is in contact with the opposing root portions. operation becomes possible. As a result, it is possible to eliminate leakage gaps on the inward surface side of the spiral teeth of the conventional shape, so that the performance of the scroll compressor 1 can be improved. In particular, under conditions where refrigerant leakage between high and low pressures during low-speed operation has a large impact on the compressor, in addition to the capacity increase due to the increased volume, leakage loss can be greatly reduced, resulting in a significant improvement in performance under low-speed conditions. can be achieved.

In addition, in the sealing material 3, the portion that contacts the root portion of the facing spiral tooth 111 or 121 may be rounded or chamfered with the same radius of curvature as the root portion.

Here, the shapes of the seal grooves 113 and 125 on the spiral center side of the spiral teeth 111 and 121 will be described with reference to FIGS. 2 and 11. FIG. FIG. 11 is a schematic cross-sectional view showing the shape of the seal groove 125 formed in the tip 121a positioned on the center side of the swing-side spiral tooth 121 in the scroll compressor 1 of FIG. Since the seal grooves 113 and 125 on the spiral center side of the spiral teeth 111 and 121 have the same shape, in the following description related to FIG. Description and illustration of 111 are omitted.

As shown in FIGS. 2 and 11, in the case of the scroll compressor 1 of Embodiment 1, the seal groove 125 arranged on the spiral center side of the swing-side spiral tooth 121 is located on the inward surface side of the tooth tip 121a. It is desirable that a sealing material drop prevention wall 129 is also formed. In other words, the sealant drop prevention wall 126 is formed only on the outward surface side of the seal groove 125 in the region where the end portion of the sealant drop prevention wall described above and the root portion of the opposing spiral tooth are likely to come into contact with each other. Sealing material drop prevention walls 126 and 129 are formed on both the outward surface side and the inward surface side of the seal groove 125 on the spiral center side where the possibility of such contact is low. With such a configuration, in the seal groove 125 arranged on the spiral center side of the swing-side spiral tooth 121, the seal material 3 can be reliably held from both the outward surface side and the inward surface side. It can effectively prevent falling.

5 and 7, and FIGS. 12 and 13 will be used to explain the increase in refrigerant intake volume and performance improvement in the spiral teeth 111 and 121 in the scroll compressor 1 and the increase in the spiral strength. to explain. FIG. 12 is a graph showing a comparison of the swirl intake volumes of the scroll compressors 1 according to the first and second embodiments. FIG. 13 is a graph showing the correlation between the rotational speed and capacity of the scroll compressor 1 according to Embodiments 1 and 2. In FIG. For the sake of convenience, FIG. 12 shows a swirl intake volume of a scroll compressor 1 according to Embodiment 2, which will be described later, as a comparative example, but detailed description is omitted here.

As shown in FIG. 5 , the fixed scroll 11 is inclined such that the inward surface of the fixed-side spiral tooth 111 toward the spiral center is tapered toward the tip 111 a of the fixed base plate 110 . In other words, the fixed side spiral tooth 111 is inclined with respect to the tooth bottom 112 on the inward surface side. Further, as shown in FIG. 7, the orbiting scroll 12 is inclined so that the outward surface of the orbiting spiral tooth 121 on the refrigerant suction side tapers toward the tip of the tooth with respect to the orbiting base plate 120 . are doing. That is, the outward surface side of the swing-side spiral tooth 121 is inclined with respect to the tooth bottom 124 . In this case, the inclination angle θ of each spiral tooth 111 and 121 is preferably set within a range of 4° or less. As a result, the tooth thickness of the spiral teeth 111 and 121 on the side of the roots 112 and 124 can be increased, and the strength of the spiral teeth 111 and 121 can be improved. In each spiral tooth 111 and 121 , the outward surface side and the inward surface side opposite to the inclined inward surface side and the outward surface side are preferably formed perpendicular to the tooth bottoms 112 and 124 .

Here, when one side of each spiral tooth 111 and 121 is inclined as described above for the purpose of improving the strength, the tooth thickness on the tooth bottom 112 and 124 side of each spiral tooth 111 and 121, which was conventionally vertical, increases. be done. At this time, if the inclination angle θ is 4° or less, the amount of increase in the tooth thickness is very small, and the degree of contribution of volume reduction to the intake volume increase due to the one-sided sealing material fall prevention walls 114 and 126 is small. Further, the actual increase in tooth thickness of the compression chamber 31 due to the overlapping of the spiral teeth 121 and 111 facing each other is only one side of the increased tooth thickness on the tooth roots 112 and 124 side. Therefore, by making the sealing material drop prevention walls 114 and 126 one-sided and the spiral teeth 111 and 121 tapered on one side, the spiral pitch is increased even if the involute range and base circle forming the spiral are the same. Therefore, as shown in Embodiments 1 and 2 of FIG. 12, the intake volume of compression chamber 31 can be increased. Moreover, there is no need to improve other parts or add additional components, and it is possible to increase the intake volume with the same involute. Therefore, as shown in Embodiments 1 and 2 of FIG. 13, it is possible to improve the maximum capacity of the scroll compressor 1 alone without increasing the manufacturing cost.

When the operating range required for the scroll compressor 1 is expanded and the operating condition is a high compression ratio state in which the difference between the suction pressure and the discharge pressure is large, the pressure difference between adjacent compression chambers 31 increases. Due to this pressure difference, if the stress generated at the base of each spiral tooth 111 and 121 exceeds the proof stress of the material, or if the stress is repeatedly applied, each spiral tooth 111 and 121 may be damaged and the scroll compressor 1 may stop. There is As described above, in the conventional spiral tooth that simply has a seal material fall prevention wall on only one side, the shape of the spiral tooth is simply thinned by making the seal material fall prevention wall on one side, so it is difficult to take in the refrigerant. Although the volume is increased, the vortex strength is reduced. This reduces the reliability of the compressor. Therefore, in order to improve the strength of the spiral, it is necessary to ensure reliability in terms of strength by enlarging the radius of curvature of the root of the spiral tooth in order to avoid stress concentration on the root of the spiral tooth. However, the expansion of the radius of curvature of the root portion of the spiral tooth in the radius of curvature of the root portion of the spiral tooth leads to the need to increase the radius processing or chamfering of the tooth tip of the opposing spiral tooth. A gap is formed between the R processed portion or the chamfered portion of . Since this gap causes circumferential leakage between the compression chambers, the compressed refrigerant leaks from the high-pressure side to the low-pressure side, causing loss in the compressor, which is a major factor in deteriorating performance.

Therefore, in the scroll compressor 1 of Embodiment 1, as described above, by tapering one side of each of the spiral teeth 111 and 121, the strength of the root portion of each of the spiral teeth 111 and 121 can be improved. and In particular, in the scroll compressor 1 of Embodiment 1, as the weight of the material of the orbiting scroll 12 is reduced, the outward surface side of the orbiting side spiral tooth 121 whose material rigidity is reduced is inclined so that the height difference is reduced. The stress generated in the root portion of the swing-side spiral tooth 121 due to pressure can be reduced more efficiently.

In addition, by adding an inclination angle θ to one side of each spiral tooth 111 and 121, even with the same tooth height, compared to a spiral tooth having a conventional shape, the cross-sectional area at the base of each spiral tooth 111 and 121 is larger than that of a conventional spiral tooth. The second moment increases. Therefore, when the base portions of the spiral teeth 111 and 121 are rounded, sufficient strength can be ensured even if the radius of curvature of the rounded teeth is small. In this case, since the radius of curvature of the R-processed portion at the base of each spiral tooth 111 and 121 is small, the shape of the R-processed portion and the chamfered portion of the tooth tip 121a and 111a of the opposing spiral teeth 121 and 111 is also small. Can be configured. Therefore, since the circumferential leakage gap can be made smaller, leakage in the compression process is reduced, leading to improved performance. Note that the fixed scroll 11 and the orbiting scroll 12 may not have the same tooth thickness.

<Operation of Scroll Compressor 1>
Next, operation of the scroll compressor 1 will be described. When electric power is supplied to the stator 22, the rotor 21 generates torque, and the main shaft 8 supported by the main bearing 15 of the frame 6 and the sub-bearing 16 of the sub-frame 7 rotates. The orbiting scroll 12 whose boss portion is driven by the eccentric shaft portion 83 of the main shaft 8 is restricted from rotating by the Oldham ring 13 and revolves. That is, the boss portion of the orbiting scroll 12 is driven by the eccentric shaft portion 83 of the main shaft 8 in a state where the rotation is restricted by the Oldham ring 13 that reciprocates in the Oldham groove direction of the frame 6, thereby causing the orbiting scroll 12 to rotate. eccentrically orbits with respect to the fixed scroll 11 . As a result, the volumes of the plurality of compression chambers 31 formed by the combination of the fixed-side spiral teeth 111 of the fixed scroll 11 and the orbiting-side spiral teeth 121 of the orbiting scroll 12 are sequentially reduced.

As the orbiting scroll 12 eccentrically orbits, gaseous refrigerant sucked into the shell 2 from the suction pipe 101 is compressed between the spiral teeth 111 and 121 of the fixed scroll 11 and the orbiting scroll 12 . It is taken into chamber 31 and compressed toward the center. The compressed refrigerant is discharged from the discharge port 11a of the fixed scroll 11 by opening the reed valve 50, and discharged from the discharge pipe 102 to the outside of the scroll compressor 1, that is, to the refrigerant circuit.

The imbalance due to the movement of the orbiting scroll 12 and the Oldham ring 13 is balanced and stabilized by the first balancer 4b attached to the main shaft 8 and the second balancer 8a attached to the rotor 21 side. . The refrigerating machine oil 9a stored in the oil reservoir 9 in the lower portion of the shell 2 passes through the oil supply passage 82 provided in the main shaft 8 and reaches the main bearing 15, the sub-bearing 16, and the sliding parts such as the thrust surface. supplied.

<Effect of Embodiment 1>
As described above, in the scroll compressor 1 of Embodiment 1, the seal material drop prevention walls 114 and 126 are arranged on the outward surface side of the seal grooves 113 and 125 of the fixed side spiral tooth 111 and the swing side spiral tooth 121. set only to At this time, in the seal groove 113, the height h1 from the tooth bottom 112 to the end of the bottom surface portion 115 on the inward surface side is greater than the height h2 from the tooth bottom 112 to the end of the bottom surface portion 115 on the outward surface side. set high. Further, the seal groove 125 of the swing-side spiral tooth 121 has a height h3 from the tooth bottom 124 to the end of the bottom surface 127 on the inward surface side, and the height h3 from the tooth bottom 124 to the end of the bottom surface 127 on the outward surface side is is set higher than the height h4 of . That is, the seal grooves 113 and 125 incline toward the tooth roots 112 and 124 as the bottom surfaces 115 and 127 on which the sealing material 3 is placed respectively advance from the end on the inward surface side to the end on the outward surface side. It is set so that the high pressure side is higher than the low pressure side.

Therefore, according to the scroll compressor 1 of Embodiment 1, the seal material drop prevention walls 114 and 126 are provided only on the outward surface side of the seal grooves 113 and 125, so that the tooth thickness of the spiral teeth 111 and 121 is reduced to The wall thickness can be reduced and the swirl uptake volume can be increased to extend the upper limit of compressor capacity. In addition, by raising the high pressure side of the bottom surfaces 115 and 127 where the sealing material 3 is arranged, it is possible to prevent the sealing material 3 from falling during operation. Thus, according to the scroll compressor 1 of Embodiment 1, it is possible to improve performance while ensuring reliability.

Furthermore, according to the scroll compressor 1 of Embodiment 1, the spiral teeth 111 and 121 are given the inclination angle θ so that the stress applied to the base portions of the spiral teeth 111 and 121 can be counteracted. , the strength of each spiral tooth 111 and 121 can be improved.

<Modification of Embodiment 1>
Here, a modification of Embodiment 1 will be described with reference to FIG. 14 . FIG. 14 is a schematic cross-sectional view showing the shape of the seal groove 125 in the tip 121a of the swing-side spiral tooth 121 of the scroll compressor 1 according to the modification of the first embodiment. Here, since the seal grooves 113 and 125 of the fixed side spiral tooth 111 and the rocking side spiral tooth 121 have substantially the same shape, only the rocking side spiral tooth 121 is used as a modified example for convenience. As shown in FIG. 14 and described, the fixed-side spiral tooth 111 is similarly configured.

In the case of the first embodiment described above, as shown in FIGS. 5 and 6, the seal groove 113 has a contact surface with the seal material 3 located on the inner peripheral side of the seal material drop prevention wall 114 continuous from the bottom surface portion 115. is formed perpendicular to the fixed base plate 110 . In addition, as shown in FIGS. 7 and 8, the seal groove 125 has a side surface portion 128 which is a contact surface with the seal material 3 located on the inner peripheral side of the seal material fall prevention wall 126 continuous from the bottom surface portion 127. A case in which it is formed perpendicular to the rocking base plate 120 has been described. However, these side portions 116 and 128 are not limited to being formed perpendicular to the fixed base plate 110 and the rocking base plate 120 .

That is, for example, as shown in FIG. 14, in which the same reference numerals are given to the parts corresponding to those in FIG. 3 may be perpendicular to the bottom surface portion 127 . That is, in this case, the side surface portion 128 is not perpendicular to the rocking plate 120, but is inclined. In this way, the side surface portion 128, which is a part of the contact surface shape of the sealing material fall prevention wall 126 that holds the sealing material 3, is inclined with respect to the rocking base plate 120, so that the side surface portion 128 is tilted toward the rocking table. As compared with the case of being perpendicular to the plate 120, the holding force of the sealing material 3 can be improved. Therefore, the ability to prevent the sealing material 3 from coming off during operation can be significantly improved.

Embodiment 2.
Next, a scroll compressor 1 according to Embodiment 2 of the present disclosure will be described with reference to FIGS. 15 and 16. FIG. FIG. 15 is a longitudinal sectional view schematically showing fixed scroll 11 of scroll compressor 1 according to Embodiment 2. As shown in FIG. FIG. 16 is a longitudinal sectional view schematically showing the orbiting scroll 12 of the scroll compressor 1 according to Embodiment 2. As shown in FIG. In FIGS. 15 and 16, parts corresponding to those in FIGS. 5 and 7 described above are denoted by the same reference numerals. Hereinafter, detailed description of the same components as in the first embodiment described above will be given. omitted.

As shown in FIG. 15 , in the second embodiment, the fixed scroll 11 is arranged such that not only the inward surface, which is the spiral center side of the fixed-side spiral tooth 111 , but also the outward surface on the rear side thereof It is inclined so as to be tapered as it progresses to the tip 111a. In other words, the fixed side spiral tooth 111 is inclined with respect to the tooth bottom 112 on the inward surface side and the outward surface side. Further, as shown in FIG. 16 , the orbiting scroll 12 has not only the outward surface of the orbiting spiral teeth 121 on the refrigerant suction side, but also the inward surface on the back side of the orbiting scroll tooth 121 , which is toothed against the oscillation base plate 120 . It slopes to taper as it goes forward. That is, the swing-side spiral tooth 121 is inclined with respect to the tooth bottom 124 on the outward surface side and the inward surface side.

<Effect in Embodiment 2>
As described above, in the scroll compressor 1 of the second embodiment, both the inward and outward surfaces of the spiral teeth 111 and 121 are tapered. can increase the strength of each spiral tooth 111 and 121. Therefore, the reliability of the scroll compressor 1 is also improved.

In this case, the inclination angle θ of each spiral tooth 111 and 121 is preferably set within a range of 4° or less. As a result, the tooth thickness of the spiral teeth 111 and 121 on the side of the roots 112 and 124 can be further increased, and the strength of the spiral teeth 111 and 121 can be further improved. Although the inclination angles .theta. of the inward and outward surfaces of the spiral teeth 111 and 121 are assumed to be the same here, the magnitude relationship between them can be arbitrarily set.

Embodiment 3.
Next, a scroll compressor 1 according to Embodiment 3 of the present disclosure will be described with reference to FIG. 17 . FIG. 17 is a schematic cross-sectional view showing the shape of the seal groove 125 in the tooth tip 121a of the swing-side spiral tooth 121 of the scroll compressor 1 according to Embodiment 3. As shown in FIG. 17, the same reference numerals are given to the parts corresponding to those in FIG. 8 described above, and detailed description of the same components as those in the first embodiment described above will be omitted below. Further, although only the swing-side spiral tooth 121 will be illustrated and described here, the fixed-side spiral tooth 111 may also have the same configuration as in FIG. 17 .

In the case of Embodiment 3, the sealing material 3 is arranged over the entire area of the tooth tip 121a of the swing-side spiral tooth 121 so as to cover the entire tooth tip 121a.

In the conventional shape, since the sealing material drop prevention walls 311, 312 and 321, 322 are present on both the inward and outward surfaces of the spiral teeth 310 and 320, the tips of the teeth are made of metal. (See Figure 9). Therefore, the tip and bottom of the tooth are subjected to optional R processing and chamfering, respectively, for the purpose of preventing metallic contact with the bottom of spiral teeth 320 and 310 facing each other. However, a minute circumferential gap 34 (see FIG. 4) generated when this R processing and chamfering processing overlap becomes a circumferential leakage path in each spiral tooth 310 and 320, and becomes a factor of deterioration of compressor performance. there is Therefore, in Embodiment 3, the sealing material 3 is arranged so as to exist over the entire area of the tooth tip 121a.

<Effects in Embodiment 3>
As described above, in the scroll compressor 1 of Embodiment 3, the sealing material 3 is arranged so as to exist over the entire tooth tip 121a, and the end located at the tip of the swing-side spiral tooth 121 The part becomes the resin of the sealing material 3 instead of metal. For this reason, it is possible to operate in a state of contact with the root portion of the opposed fixed-side spiral tooth 111 (see FIG. 4), and loss due to circumferential leakage can be reduced.

Embodiment 4.
<Configuration of refrigeration cycle device 200>
Next, Embodiment 4 will be described with reference to FIG. 18 is a refrigerant circuit diagram showing an example of a refrigeration cycle apparatus according to Embodiment 4. FIG. The refrigerating cycle device 200 functions as an air conditioner that performs cooling or heating operation to condition the indoor air, for example, by transferring heat between the outside air and the indoor air via a refrigerant.

As shown in FIG. 18 , a refrigeration cycle device 200 includes a scroll compressor 1 , a condenser 201 , an expansion valve 202 as a decompression device, and an evaporator 203 . The refrigeration cycle device 200 also includes an injection circuit 204 branched from between the condenser 201 and the expansion valve 202 and connected to the scroll compressor 1 . A flow control valve 205 is provided in the injection circuit 204 . For the scroll compressor 1, the scroll compressors 1 of the first to third embodiments described above can be applied.

<Operation example of refrigeration cycle device 200>
In the refrigeration cycle apparatus 200 configured as described above, the gas refrigerant discharged from the scroll compressor 1 flows into the condenser 201, exchanges heat with the air passing through the condenser 201, and flows out as a high-pressure liquid refrigerant. . The high-pressure liquid refrigerant that has flowed out of the condenser 201 is decompressed by the expansion valve 202 to become a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 203 . The low-pressure gas-liquid two-phase refrigerant that has flowed into the evaporator 203 exchanges heat with the air passing through the evaporator 203 to become low-pressure gas refrigerant, which is sucked into the scroll compressor 1 again.

In addition, the injection refrigerant, which is a part of the refrigerant discharged from the scroll compressor 1 and passed through the condenser 201, flows into the injection circuit 204, and flows into the injection pipe 103 of the scroll compressor 1 via the flow control valve 205. . The liquid or gas-liquid two-phase injection refrigerant that has flowed into the injection pipe 103 is injected into the spiral side suction space 73 or the compression chamber 31 .

The refrigeration cycle apparatus 200 configured in this way can further improve the compression function force in synergy with the increase in the swirl intake volume by including the scroll compressor 1 described above.

The refrigerating cycle device 200 equipped with the scroll compressor 1 can be applied to refrigerators, freezers, vending machines, air conditioners, refrigerating devices, water heaters, and the like.

REFERENCE SIGNS LIST 1 scroll compressor 2 shell 2a upper shell 2b lower shell 2c trunk shell 3 sealing material 4 slider with balancer 4a slider 4b first balancer 6 frame 6a shaft hole 7 subframe 8 main shaft , 8a Second balancer 9 Oil reservoir 9a Refrigerant oil 10 Compression mechanism 11 Fixed scroll 11a Discharge port 12 Oscillating scroll 12b Oscillating side spiral tooth 13 Oldham ring 14 Sleeve 15 Main bearing , 16 auxiliary bearing, 20 motor, 21 rotor, 22 stator, 31 compression chamber, 31a high-pressure side compression chamber, 31b low-pressure side compression chamber, 33 tip clearance, 34 circumferential clearance, 35 clearance, 40 injection mechanism, 50 reed valve , 51 valve retainer, 70 suction space, 71 discharge space, 72 bearing operation space, 73 spiral side suction space, 81 oil pump, 82 oil supply passage, 83 eccentric shaft portion, 84 main shaft portion, 85 auxiliary shaft portion, 101 suction pipe, 102 discharge pipe, 103 injection pipe, 110 fixed base plate, 111 fixed side spiral tooth, 111a tooth tip, 112 tooth bottom, 113 seal groove, 114 sealing material fall prevention wall, 115 bottom surface portion, 116 side surface portion, 120 swing table Plate 121 swing-side spiral tooth 121a tooth tip 122 boss portion 123 swing bearing 124 tooth bottom 125 seal groove 126 seal material fall prevention wall 127 bottom portion 128 side portion 129 seal material fall prevention wall, 200 refrigeration cycle device, 201 condenser, 202 expansion valve, 203 evaporator, 204 injection circuit, 205 flow control valve, 310 spiral tooth, 310a seal groove, 311 seal material fall prevention wall, 312 seal material fall prevention wall, 320 spiral tooth, 330 compression chamber, d dimension, h1 height, h2 height, h3 height, h4 height, θ inclination angle.

Claims (11)

a fixed scroll having involute-shaped fixed-side spiral teeth formed to protrude from a fixed base plate; and sealing material provided at the tip of the fixed-side spiral teeth;
an oscillating scroll having an involute-shaped oscillating-side spiral tooth protruding from an oscillating base plate; and a sealing material provided at the tip of the oscillating-side spiral tooth
The fixed scroll and the orbiting scroll are combined so that the fixed-side spiral teeth and the orbiting-side spiral teeth are meshed with each other, and the compression mechanism compresses the refrigerant between the fixed scroll and the orbiting scroll. A scroll compressor having chambers formed therein,
The fixed scroll and the orbiting scroll are
Seal grooves for holding the sealing material are formed in the tooth tips of the fixed-side spiral teeth and the rocking-side spiral teeth, respectively;
The seal groove is
having a bottom portion serving as a bottom portion and a sealing material fall prevention wall serving as a side wall portion continuously from the bottom portion;
The sealing material fall prevention wall is
formed only on the outward surface side of the fixed-side spiral tooth and the rocking-side spiral tooth,
The bottom portion of the fixed-side spiral tooth,
The height from the tooth bottom located on the fixed base plate side to the end on the inward surface side of the fixed side spiral tooth is the height from the tooth bottom to the end on the outward surface side of the bottom surface of the seal groove. height and lower than the height from the tooth bottom to the end of the outward surface of the stationary spiral tooth ,
The bottom portion of the swing-side spiral tooth is
The height from the tooth bottom located on the rocking base plate side to the end of the rocking-side spiral tooth on the inward surface side is the height from the tooth bottom to the end of the bottom surface on the outward surface side of the seal groove. and lower than the height from the tooth bottom to the end of the outward surface of the swing-side spiral tooth . A gap is formed between the bottom surface portion of the seal groove and the seal material,
The seal groove is provided in each of the fixed-side spiral tooth and the rocking-side spiral tooth,
a height from the tooth bottom to the end of the bottom surface on the inward surface side;
The difference between the height from the tooth bottom to the end of the bottom surface on the outward surface side is
2. The scroll compressor according to claim 1, wherein the dimension of said gap between said seal member and said seal member at the end of said bottom surface portion on the outward surface side is larger than the size of said gap. The fixed scroll is
an inward surface of the fixed-side spiral tooth is inclined with respect to the fixed base plate so as to taper toward the tip of the tooth;
The orbiting scroll is
3. The scroll compressor according to claim 1, wherein the outward surface of said swing-side spiral tooth is inclined with respect to said swing bed plate so as to taper toward said tooth tip. The fixed scroll is
the inward and outward surfaces of the fixed-side spiral tooth are inclined with respect to the fixed base plate so as to taper toward the tip of the tooth;
The orbiting scroll is
3. The scroll compressor according to claim 1, wherein the inward and outward surfaces of said swing-side spiral tooth are inclined with respect to said swing bed plate so as to taper off toward said tooth tip. 5. The scroll compressor according to claim 3, wherein an inclination angle of said inclined inward and outward surfaces of said fixed-side spiral tooth and said rocking-side spiral tooth is 4[deg.] or less. The seal groove is
6. The sealing material fall prevention wall according to any one of claims 1 to 5, wherein a surface in contact with the sealing material located on the inner peripheral side of the sealing material fall prevention wall is perpendicular to the fixed base plate and the rocking base plate. Scroll compressor as described. The seal groove is
The scroll compressor according to any one of claims 1 to 5, wherein a surface in contact with the seal material located on the inner peripheral side of the seal material fall prevention wall is perpendicular to the bottom surface portion. The sealing material is
The scroll compressor according to any one of claims 1 to 7, which is formed using one selected from the group including polyphenylene sulfide-based resin, polyetheretherketone-based resin and polyimide-based resin. The sealing material is
The scroll compressor according to any one of claims 1 to 8, wherein the tooth tip of the fixed-side spiral tooth and the oscillation-side spiral tooth is arranged over the entire area of the tooth tip. further comprising a sealed container that houses the fixed scroll and the orbiting scroll;
The closed container is
The scroll compressor according to any one of claims 1 to 9 , further comprising an injection mechanism that injects the refrigerant into the refrigerant suction space on the outer peripheral side of the swing-side spiral teeth or into the compression chamber that is being compressed. . A refrigeration cycle apparatus comprising a refrigerant circuit having at least a compressor, a condenser, an expansion valve and an evaporator, and using the scroll compressor according to any one of claims 1 to 10 as the compressor.

Images