WO2023188422A1

WO2023188422A1 - Compressor and upper shell

Info

Publication number: WO2023188422A1
Application number: PCT/JP2022/016982
Authority: WO
Inventors: 鉄郎平見; 浩平達脇
Original assignee: 三菱電機株式会社
Priority date: 2022-04-01
Filing date: 2022-04-01
Publication date: 2023-10-05

Abstract

A compressor comprising: a bottomed cylindrical shell forming an outer shell; a frame housed inside the shell; an oscillating scroll slidably held by the frame; and a fixed scroll that, together with the oscillating scroll, forms a compression chamber in which to compress a refrigerant, wherein the shell has a cylindrical main shell housing the frame, the oscillating scroll, and the fixed scroll and an upper shell sealing an opening at one end of the main shell, the fixed scroll has a first board fixed to a first inner wall of the main shell, a lower end of the upper shell has a tab to be inserted inside the opening at one end of the main shell, the first board is caught between the tab and the first inner wall in an axial direction of the shell, the first board has a first engaging part, the tab has a second engaging part, and the first and second engaging parts are engaged with each other to form a rotation suppression mechanism that suppresses circumferential rotation of the fixed scroll.

Description

Compressor and upper shell

The present disclosure relates to a compressor that compresses refrigerant, and more specifically relates to a compressor equipped with a fixed scroll and an upper shell.

In a conventional general scroll compressor, an oscillating scroll is supported by a frame fixed inside a main shell, and a fixed scroll is provided opposite the oscillating scroll. In the conventional frame, the peripheral wall of the frame extends to the fixed scroll, and the fixed scroll is fixed at the tip of the peripheral wall with bolts or the like. Further, a crankshaft is attached to the orbiting scroll. By rotating the crankshaft, the oscillating scroll oscillates relative to the fixed scroll, and the refrigerant is compressed in a compression chamber formed by the oscillating scroll and the fixed scroll.

Furthermore, in order to increase the capacity of the compressor, there is a technique in which the peripheral wall of the frame is eliminated and the space for arranging the spiral bodies provided in the oscillating scroll and the fixed scroll is expanded (see, for example, Patent Document 1). In scroll compressors that do not have a peripheral wall of the frame, bolts cannot be used to fix the fixed scroll, so shrink fitting of the fixed scroll and main shell or arc spot welding of the fixed scroll is used. There is.

Patent No. 6678762

In the conventional general scroll compressor described above, the peripheral wall of the frame that supports the oscillating scroll extends in the direction of the fixed scroll, and the fixed scroll is fixed with bolts at the tip of the peripheral wall. Since a compression chamber for compressing refrigerant is formed between the fixed scroll and the orbiting scroll, the positional accuracy of the fixed scroll with respect to the orbiting scroll is important. In conventional general scroll compressors, it has been possible to ensure the positional accuracy of the fixed scroll by fixing the fixed scroll to the tip of the peripheral wall of the frame.

However, in the scroll compressor described in Patent Document 1, since there is no peripheral wall of the frame, the frame and the fixed scroll cannot be bolted together. Patent Document 1 discloses performing shrink fitting and arc spot welding as a fixed scroll fixing method instead of bolt fastening. However, the gaps between the tips of the spiral bodies of the fixed scroll and the spiral body of the oscillating scroll are on the order of several tens of μm, and excessive shrink fitting and fixing by welding cause distortion in the fixed scroll. When distortion occurs in the fixed scroll, there may be areas where the gap between the tooth tips expands, increasing the gap through which refrigerant leaks. In that case, the compression performance of the compressor may deteriorate, or the compressor itself may be damaged due to contact between the tooth tips of the spiral body. Therefore, the method of fixing the fixed scroll must be a method that does not cause distortion to the fixed scroll by fixing the fixed scroll to the shell. In other words, shrink fitting or welding that provides the minimum necessary holding force to prevent the fixed scroll from floating is necessary. It is desirable to do so.

Therefore, in Patent Document 1, in addition to shrink fitting, the fixed scroll is sandwiched between an upper shell installed on the upper part of the main shell and a positioning step provided on the main shell, thereby preventing the fixed scroll from lifting up. . This makes it possible to prevent the fixed scroll from lifting even if the pressure inside the compression chamber is abnormally increased due to liquid compression, such as when the refrigerant is started in a state where it is stagnant, such as during startup in winter.

However, when abnormal pressure rise occurs in the compression chamber, a force that lifts the fixed scroll in the axial direction of the compressor and a force that rotates the fixed scroll in the circumferential direction are generated. Although it is possible to prevent the fixed scroll from lifting by using the minimum necessary shrink fitting to prevent lifting and fixing by sandwiching the main shell and the upper shell, it is not possible to prevent the fixed scroll from rotating in the circumferential direction.

The present disclosure has been made in order to solve such problems, and without forming a peripheral wall for fixing the fixed scroll in the frame, the lifting of the fixed scroll and the circumferential direction of the fixed scroll due to abnormal pressure increase during operation can be prevented. The purpose of the present invention is to provide a compressor and an upper shell that can prevent both the rotation of the compressor and the upper shell.

A compressor according to the present disclosure includes a bottomed cylindrical shell constituting an outer shell, a frame housed inside the shell, an oscillating scroll slidably held by the frame, and an oscillating scroll that is slidably held in the frame. a fixed scroll that, together with the scroll, forms a compression chamber for compressing refrigerant; the shell includes a cylindrical main shell that houses the frame, the swinging scroll, and the fixed scroll; an upper shell that seals an opening at one end of the shell, the fixed scroll having a first substrate fixed to a first inner wall surface of the main shell, and a lower end of the upper shell a claw portion inserted into the opening on the one end side of the main shell; the first substrate is held between the claw portion and the first inner wall surface in the axial direction of the compressor; The first substrate has a first locking portion, the claw portion has a second locking portion, and the first locking portion and the second locking portion are engaged with each other. , constitutes a rotation suppression mechanism section that suppresses rotation of the fixed scroll in the circumferential direction.

The upper shell according to the present disclosure is an upper shell having an open lower end, and the lower end of the upper shell has a claw portion formed in a circumferential direction, and the claw portion is An upper shell rotation suppressing convex portion is provided at at least one location in the circumferential direction and protrudes downward from the claw portion, and the upper shell rotation suppressing convex portion is disposed below the upper shell and extends around the circumferential direction. It is inserted into a portion of the object whose rotation in the direction is to be suppressed.

According to the compressor and upper shell according to the present disclosure, the rotation suppressing mechanism prevents rotation of the fixed scroll due to abnormal pressure increase during operation, without forming a peripheral wall for fixing the fixed scroll to the frame. are doing. Therefore, the fixed scroll can be arranged within the shell with high positional accuracy, and the positional accuracy of the fixed scroll can be maintained even when abnormal pressure rise occurs in the compression chamber. Further, since the first substrate of the fixed scroll is sandwiched between the upper shell and the main shell, lifting of the fixed scroll in the axial direction can be prevented.

1 is a schematic longitudinal cross-sectional view showing the configuration of a compressor 1 according to a first embodiment. FIG. 2 is an exploded perspective view showing the structure of a frame 5, an Oldham ring 7, etc. provided in the compressor 1 according to the first embodiment. FIG. 2 is a partially enlarged sectional view of the compressor 1 shown in FIG. 1. FIG. FIG. 2 is a partially enlarged sectional view showing a region surrounded by a dashed line A in FIG. 1; FIG. 2 is a cross-sectional view showing the configuration of an upper shell 2b provided in the compressor 1 according to the first embodiment. FIG. 2 is a perspective view schematically showing the configuration of an upper shell 2b provided in the compressor 1 according to the first embodiment. FIG. 3 is a plan view showing the configuration of an upper shell 2b provided in the compressor 1 according to the first embodiment from the back side. FIG. 3 is a plan view showing the configuration of a fixed scroll 3 provided in the compressor 1 according to the first embodiment. FIG. 3 is a cross-sectional view showing the configuration of a fixed scroll 3 provided in the compressor 1 according to the first embodiment. 1 is a schematic perspective view showing a schematic configuration of a fixed scroll 3 provided in a compressor 1 according to Embodiment 1. FIG. FIG. 3 is a partial perspective view showing a rotation suppressing mechanism section 50 of the upper shell 2b and the fixed scroll 3 in the compressor 1 according to the first embodiment. FIG. 4 is a partially enlarged sectional view showing the configuration of a region surrounded by a dashed line F in FIG. 3; FIG. 4 is a partially enlarged cross-sectional view showing the configuration of a region surrounded by a dashed line G in FIG. 3. FIG. FIG. 4 is a partially enlarged sectional view showing a configuration in which a cutout portion 25c is provided in a region surrounded by a dashed line F in FIG. 3. FIG. FIG. 2 is a plan view schematically showing the configuration of an upper shell 2b provided in the compressor 1 according to the first embodiment. 3 is a diagram showing an example of the shape of an upper shell rotation suppressing convex portion 211 formed on an upper shell 2b provided in the compressor 1 according to the first embodiment. FIG. FIG. 3 is a cross-sectional view showing the configuration of an upper shell 2b provided in the compressor 1 according to the second embodiment. FIG. 3 is a partial perspective view showing a rotation suppressing mechanism section 50A of an upper shell 2b and a fixed scroll 3 in a compressor 1 according to a second embodiment. 7 is a configuration diagram showing an example of the configuration of a refrigeration cycle device 601 according to Embodiment 3. FIG.

Hereinafter, embodiments of a compressor, a refrigeration cycle device, and an upper shell of a compressor according to the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the following embodiments, and can be variously modified without departing from the gist of the present disclosure. Furthermore, the present disclosure includes all combinations of configurations that can be combined among the configurations shown in the following embodiments and modifications thereof. Further, in each figure, the same reference numerals are the same or equivalent, and this is common throughout the entire specification. Furthermore, descriptions of items with the same reference numerals will be omitted or simplified as appropriate. Furthermore, the shape, size, arrangement, etc. of the configurations shown in each figure can be changed as appropriate within the scope of the present disclosure. In the following description, with reference to the frame 5, the side where the compression mechanism section 1a is provided (upper side) is oriented as one end side U, and the side where the drive mechanism section 1b is provided (lower side) is oriented as the other end side L. do. Moreover, in each drawing, the Z direction indicates the axial direction of the main shaft 13 of the compressor 1, and is, for example, the vertical direction. Further, the XY plane is a plane that intersects the Z direction, and is, for example, a horizontal direction. Further, for the sake of explanation, the Z direction is sometimes called the up-down direction, the X direction is sometimes called the left-right direction, and the Y direction is sometimes called the depth direction.

Embodiment 1.
<Configuration of compressor 1>
The configuration of the compressor 1 according to the first embodiment will be described below with reference to FIGS. 1 and 2. FIG. 1 is a schematic vertical sectional view showing the configuration of a compressor 1 according to the first embodiment. FIG. 2 is an exploded perspective view showing the structure of the frame 5, Oldham ring 7, etc. provided in the compressor 1 according to the first embodiment. The compressor 1 shown in FIG. 1 is a so-called vertical scroll compressor that is used with the central axis of the main shaft 13 substantially perpendicular to the ground.

As shown in FIG. 1, the compressor 1 includes a compression mechanism section 1a that compresses refrigerant and a drive mechanism as an electric mechanism that drives the compression mechanism section 1a, inside a bottomed cylindrical shell 2 that is an airtight container. A portion 1b is provided. In the case of the first embodiment, the 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 1a.

The refrigerant is composed of, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a hydrocarbon, or a mixture thereof. Halogenated hydrocarbons having carbon double bonds are HFC (Hydrofluorocarbon) refrigerants and fluorocarbon-based low GWP (Global Warming Potential) refrigerants, which have zero ozone depletion potential. Examples of low GWP refrigerants include HFO (hydrofluoroolefin) refrigerants, and examples thereof include tetrafluoropropenes such as HFO1234yf, HFO1234ze, and HFO1243zf, each of which has a chemical formula of C ₃ H ₂ F ₄ . Examples of halogenated hydrocarbons that do not have carbon double bonds include refrigerants in which R32 (difluoromethane), R41, and the like represented by CH ₂ F ₂ are mixed. Examples of hydrocarbons include natural refrigerants such as propane and propylene. An example of the mixture is a mixed refrigerant in which R32, R41, etc. are mixed with HFO1234yf, HFO1234ze, HFO1243zf, etc.

The shell 2 includes a main shell 2a, an upper shell 2b, and a lower shell 2c, and constitutes the outer shell of the compressor 1. The shell 2 is thus composed of three or more parts. The shell 2 also has an oil reservoir 40 at the bottom. The shell 2 has a cylindrical shape with a bottom. The main shell 2a has a cylindrical shape with both upper and lower ends open. The opening at one end U of the main shell 2a is closed and sealed by the dome-shaped upper shell 2b, and the opening at the other end L of the main shell 2a is closed and sealed by the lower shell 2c. . The lower shell 2c is supported by a fixing base 2d having a plurality of through holes. By screwing screws into through holes provided in the fixing base 2d, the compressor 1 can be fixed to other members such as the casing of the outdoor unit.

Since a detailed description of the compression mechanism section 1a will be given later, only the general configuration of the compressor 1 will be described here.

The compression mechanism section 1a is arranged toward one end side U from a frame 5 arranged in the main shell 2a, and is composed of a fixed scroll 3, an oscillating scroll 4, an Oldham ring 7, a thrust plate 8, and the like.

The frame 5 is housed inside the shell 2. The frame 5 is fixed to the inner peripheral surface of the main shell 2a by shrink fitting, welding, or the like. The frame 5 is disposed within the shell 2 between the compression mechanism section 1a and the drive mechanism section 1b. As shown in FIG. 2, a cylindrical frame boss portion 5b is formed in the center of the frame 5, and the main shaft 13 is passed through the frame boss portion 5b. As shown in FIG. 2, the main body portion 5a of the frame 5 is provided above the frame boss portion 5b. The frame 5 holds the swinging scroll 4 slidably relative to the fixed scroll 3 within the shell 2 .

Inside the shell 2, the drive mechanism section 1b is arranged at the other end L with respect to the frame 5. Furthermore, as shown in FIG. 1, a subframe 18 is provided below the drive mechanism section 1b. The subframe 18 is fixed to the inner peripheral surface of the shell 2 by shrink fitting, welding, or the like.

The drive mechanism section 1b includes a rotor 15 as a rotor and a stator 17 as a stator. The drive mechanism section 1b is installed inside the shell 2 between the frame 5 and the subframe 18, and drives the compression mechanism section 1a via the main shaft 13. The rotor 15 is provided on the inner peripheral side of the stator 17 and attached to the main shaft 13 by shrink fitting or the like. The stator 17 is connected to a glass terminal 26 located between the frame 5 and the stator 17 with a lead wire (not shown) in order to obtain electric power from the outside. Then, the stator 17 rotates the rotor 15 using electric power supplied from the outside. As the rotor 15 rotates, the main shaft 13 is rotated and the compression mechanism section 1a is driven.

Further, refrigerating machine oil 21 is stored in an oil reservoir 40 located at the lower part of the compressor 1, that is, the lower shell 2c. Refrigerating machine oil 21 is, for example, oil containing ester-based synthetic oil. An oil pump 20 serving as an oil supply mechanism is fixed to the lower end of the main shaft 13. The oil pump 20 is, for example, a positive displacement pump such as a trochoid pump. As the main shaft 13 rotates, the oil pump 20 pumps up refrigerating machine oil 21 stored in an oil reservoir 40 through an oil supply passage 13c formed inside the main shaft 13. The pumped-up refrigerating machine oil 21 passes through the oil supply passage 13c in the main shaft 13 and constitutes the compression mechanism section 1a, etc., reducing wear between mechanically contacting parts, controlling the temperature of sliding parts, and improving sealing performance. . As the refrigerating machine oil 21, an oil having excellent lubricating properties, electrical insulation, stability, refrigerant solubility, low-temperature fluidity, etc., and a suitable viscosity is suitable.

The main shaft 13 has an eccentric shaft part 13a and a main shaft part 13b arranged below the eccentric shaft part 13a. The eccentric shaft portion 13a is arranged at an eccentric position with respect to the main shaft portion 13b. The main shaft portion 13b is fitted into the main bearing 5c via the sleeve 12, and slides on the main bearing 5c via an oil film formed by the refrigerating machine oil 21. The main bearing 5c is fixed to the frame 5 by press-fitting a bearing material used for sliding bearings, such as a copper-lead alloy.

The sleeve 12 is a cylindrical member provided between the main shaft 13 and the main bearing 5c. The sleeve 12 absorbs the inclination of the main shaft 13 with respect to the frame 5.

As shown in FIG. 2, the slider with balancer 11 has a cylindrical slider portion 11a and a balancer portion 11b. The cylindrical slider portion 11a and the balancer portion 11b are joined by shrink fitting or the like. The slider portion 11a is fitted to be movable relative to the eccentric shaft portion 13a provided at the upper end of the main shaft 13, and automatically adjusts the swing radius of the swing scroll 4. The slider portion 11a is provided so that the first spiral body 3b of the fixed scroll 3 and the second spiral body 4b of the orbiting scroll 4 are always in contact with each other when the orbiting scroll 4 swings. . As shown in FIG. 2, the balancer section 11b is located on the side of the slider section 11a, and is provided to cancel the centrifugal force of the swinging scroll 4 and suppress vibrations of the compression element. The balancer section 11b is arranged along a part of the side surface of the cylindrical slider section 11a.

In this way, the swinging scroll 4 is connected to the eccentric shaft portion 13a of the main shaft 13 via the slider 11 with a balancer, and the swing radius is automatically adjusted by the slider 11 with a balancer, and the rotation of the main shaft 13 is controlled. It oscillates along with the movement. As shown in FIG. 3, which will be described later, a cylindrical swing bearing operating space 5e is formed between the swing scroll thrust surface 4f of the second substrate 4a of the swing scroll 4 and the main body portion 5a of the frame 5. ing. During the swing motion of the swing scroll 4, the swing bearing 4e rotates together with the balancer-equipped slider 11 within the swing bearing operating space 5e.

The first balancer 14 is attached to the main shaft 13, as shown in FIG. The first balancer 14 is located between the frame 5 and the rotor 15. The first balancer 14 cancels out the unbalance caused by the swinging scroll 4 and the slider 11 with a balancer.

As shown in FIG. 1, the second balancer 16 is located between the rotor 15 and the subframe 18, and is attached to the lower surface of the rotor 15. The second balancer 16 cancels out the unbalance caused by the swinging scroll 4 and the slider 11 with a balancer.

Inside the shell 2, a subframe 18 is provided below the drive mechanism section 1b. The subframe 18 is fixed to the inner peripheral surface of the main shell 2a by shrink fitting, welding, or the like. A sub-bearing 19 made of a ball bearing is provided at the center of the sub-frame 18. The sub-bearing 19 supports the main shaft 13 in the radial direction below the drive mechanism section 1b. The sub-frame 18 rotatably supports the main shaft 13 via a sub-bearing 19. Note that the secondary bearing 19 may have a bearing configuration other than a ball bearing. In the main shaft 13, a portion below the drive mechanism portion 1b is referred to as a sub-bearing portion 13e. The sub-bearing portion 13e is fitted into the sub-bearing 19 and slides on the sub-bearing 19 via an oil film formed by the refrigerating machine oil 21. The axes of the main shaft portion 13b, the main bearing portion 13d, and the sub-bearing portion 13e coincide with the axis of the main shaft 13.

As shown in FIG. 1, the shell 2 is provided with a suction pipe 22 for sucking refrigerant and a discharge pipe 23 for discharging the refrigerant. The suction pipe 22 is provided on the side wall of the shell 2. The suction pipe 22 is a pipe that sucks gaseous refrigerant into the interior of the shell 2 . A low-pressure suction space 41 filled with suction refrigerant flowing from the suction pipe 22 is formed below the frame 5 in the shell 2 .

The discharge pipe 23 is provided at the top of the upper shell 2b. The discharge pipe 23 is a pipe that discharges the refrigerant compressed by the compression mechanism part 1a to the outside of the shell 2. In addition, in the shell 2, the discharge pipe 23 side located above the first substrate 3a (see FIG. 3) of the fixed scroll 3 of the compression mechanism section 1a is filled with the discharge refrigerant discharged from the compression mechanism section 1a. A high pressure discharge space 42 is formed. It is preferable that an injection pipe 24 of an injection mechanism 1c that injects refrigerant introduced from the outside is connected above the main shell 2a. The injection pipe 24 injects a refrigerant introduced from the outside into a refrigerant intake space 44 located on the outer peripheral side of the second spiral body 4b of the orbiting scroll 4 or into a compression chamber 43, which will be described later.

<Compression mechanism section 1a>
Next, using FIGS. 3 to 4 in addition to FIGS. 1 to 2 described above, the configuration of the compression mechanism section 1a of the compressor 1 according to the first embodiment and the holding of the fixed scroll 3 and the swinging scroll 4 will be explained. The form will be explained. FIG. 3 is a partially enlarged sectional view of the compressor 1 shown in FIG. 1. FIG. 3 shows only the structure of the upper part of the compressor 1 shown in FIG. FIG. 4 is a partially enlarged sectional view showing a region surrounded by a dashed line A in FIG.

The compression mechanism section 1a of the compressor 1 is arranged from the frame 5 toward one end side U, and is composed of a fixed scroll 3, an oscillating scroll 4, a thrust plate 8, an Oldham ring 7, and the like.

The fixed scroll 3 is made of metal such as cast iron, and includes a first substrate 3a (see, for example, FIG. 10) and a first spiral body 3b (see, for example, FIG. 10). FIG. 10, which will be described later, is a schematic diagram schematically showing the configuration of the fixed scroll 3, and is different from the fixed scroll 3 according to Embodiment 1 in the spiral shape of the first spiral body 3b, the number of turns, etc. .

The first substrate 3a has a disk shape, and as shown in FIG. 3, a discharge hole 3c is formed in the center thereof to penetrate in the vertical direction. The first substrate 3a has one surface (hereinafter referred to as a first surface 312) on which the first spiral body 3b is formed, and the other surface located on the opposite side of the first surface 312 (hereinafter referred to as a second surface 313). ) and a side surface 314. The side surface 314 is located at the outermost part of the first substrate 3a in the radial direction, and is a surface that connects the first surface 312 and the second surface 313. The first spiral body 3b formed on the first surface 312 protrudes toward the other end side L of the first substrate 3a, forming a spiral wall. Furthermore, a sealing material for preventing leakage between the first spiral body 3b and the compression chamber 43 is provided at the tip of the first spiral body 3b. A discharge valve 9 is installed at the outlet of the discharge hole 3c of the fixed scroll 3 so as to cover the outlet. The discharge valve 9 is constituted by, for example, a reed valve. The discharge valve 9 opens and closes the discharge hole 3c to prevent backflow of fluid. The discharge valve holder 10 is a long plate-shaped member that is thicker than the discharge valve 9, and supports the discharge valve 9 from the back side (that is, the upper side) when the discharge valve 9 is opened. To protect a discharge valve 9 from deformation while restricting a movable range.

The swinging scroll 4 is made of metal such as aluminum, and includes a second substrate 4a, a second spiral body 4b, a cylindrical swinging scroll boss portion 4c, and a second Oldham groove 4d. Further, a sealing material for preventing leakage between the second spiral body 4b and the compression chamber 43 is provided at the tip of the second spiral body 4b. The second substrate 4a has one surface on which the second spiral body 4b is formed (hereinafter referred to as the first surface 412) and the other surface located on the opposite side of the first surface (hereinafter referred to as the second surface 413). ) and a side surface 414. The first surface 412 is arranged to face the first surface 312 of the fixed scroll 3 . At least a portion of the outer peripheral region of the second surface 413 becomes a sliding surface. Further, the side surface 414 is located at the outermost portion of the second substrate 4a in the radial direction, and is a surface that connects the first surface 412 and the second surface 413. The second substrate 4a is supported by the frame 5 such that the sliding surface of the second surface 413 of the second substrate 4a can slide on the thrust plate 8 (see FIG. 1). The second spiral body 4b projects from the first surface 412 toward one end side U, and forms a spiral wall. In the second substrate 4a of the swing scroll 4, a cylindrical swing scroll boss portion 4c is formed at the center of the second surface 413. A swing bearing 4e is fixed inside the swing scroll boss portion 4c. The rocking bearing 4e is made of a bearing material used for sliding bearings, such as copper-lead alloy. The swing bearing 4e is formed by press-fitting and fixing a bearing material inside the swing scroll boss portion 4c.

The frame 5 is a hollow metal frame with a cavity formed therein, and is provided inside the shell 2. As shown in FIG. 2, the frame 5 has a cylindrical main body part 5a with a step formed therein, and a cylindrical frame boss part 5b arranged below the main body part 5a. As shown in FIG. 1, an oil return pipe 6 for returning oil accumulated inside the frame 5 to the low pressure space is connected to the main body portion 5a. The oil return pipe 6 is a pipe for returning the lubricating oil accumulated in the frame 5 to the oil reservoir part 40 inside the lower shell 2c, and is inserted and fixed into the oil drain hole 5i formed on the side surface of the main body part 5a. ing. The oil drain hole 5i is a through hole that penetrates the side surface of the main body portion 5a. Therefore, the oil drain hole 5i penetrates inside and outside of the frame 5.

Furthermore, as shown in FIGS. 1 to 3, a main bearing 5c is fixed inside the frame boss portion 5b. The main bearing 5c is made of a bearing material used for sliding bearings, such as copper-lead alloy. The main bearing 5c is formed by press-fitting and fixing a bearing material inside the frame boss portion 5b. The main body portion 5a is fixed to the inner wall surface of one end side U of the shell 2. A frame thrust surface 5f for supporting the swinging scroll 4 is formed on one end side U of the frame 5. The frame thrust surface 5f is arranged parallel to the XY plane. As shown in FIG. 2, the frame thrust surface 5f has a donut shape in plan view. A ring-shaped thrust plate 8 (see FIGS. 1 and 2) made of a steel sheet material such as valve steel is arranged on the frame thrust surface 5f. Therefore, in the first embodiment, the thrust plate 8 functions as a thrust bearing. Further, as shown in FIG. 3, a suction port 5d is formed at a position on the outer end side of the frame thrust surface 5f that does not overlap with the thrust plate 8. That is, as shown in FIG. 2, the annular thrust plate 8 has a notch 8a formed at one location on the outer end side. The suction port 5d is arranged at a position corresponding to the notch 8a of the thrust plate 8. The suction port 5d is a space that penetrates the main body portion 5a in the vertical direction, that is, one end side U and the other end side L. The number of suction ports 5d is not limited to one, and a plurality of suction ports may be formed.

As shown in FIG. 2, an Oldham housing portion 5g is formed in a stepped portion of the frame 5 below the frame thrust surface 5f. The Oldham storage portion 5g is arranged parallel to the XY plane and has a donut shape when viewed from above. The Oldham ring 7 is placed in the Oldham housing portion 5g. A first Oldham groove 5h is formed in the Oldham housing portion 5g. In the example of FIG. 2, two first Oldham grooves 5h are formed. The first Oldham groove 5h is formed from the lower part of the inner wall of the main body portion 5a to the Oldham housing portion 5g. The first Oldham groove 5h is recessed toward the other end L from the Oldham housing portion 5g. The first key portion 7b of the Oldham ring 7 is inserted into the first Oldham groove 5h.

As shown in FIG. 2, the Oldham ring 7 includes a ring portion 7a, a first key portion 7b, and a second key portion 7c. The ring portion 7a has an annular shape. In the example of FIG. 2, two first key parts 7b are provided on the ring part 7a. The two first key parts 7b are arranged on the surface of the other end side L of the ring part 7a so as to face each other in the radial direction. The two first key parts 7b each have a rectangular parallelepiped shape. The two first key portions 7b are accommodated in a pair of first Oldham grooves 5h of the frame 5, respectively. Furthermore, in the example of FIG. 2, two second key parts 7c are provided on the ring part 7a. The two second key parts 7c are arranged on the surface of one end side U of the ring part 7a so as to face each other in the radial direction. The two second key parts 7c are arranged with a phase shift of 90 degrees with respect to the two first key parts 7b. That is, the imaginary line extending in the radial direction connecting the two second key parts 7c and the imaginary line extending in the radial direction connecting the two first key parts 7b are orthogonal to each other. The two second key parts 7c each have a rectangular parallelepiped shape. The two second key portions 7c are accommodated in a pair of second Oldham grooves 4d (see FIG. 3) of the swinging scroll 4. When the oscillating scroll 4 revolves due to the rotation of the main shaft 13, the first key part 7b slides in the first Oldham groove 5h, and the second key part 7c slides in the second Oldham groove 4d. 7 prevents the swinging scroll 4 from rotating. That is, the Oldham ring 7 functions to prevent the rotation of the swinging scroll 4 and to enable the swinging motion of the swinging scroll 4.

The first surface 312 of the fixed scroll 3 and the first surface 412 of the swinging scroll 4 are arranged to face each other. The compression chamber 43 is formed by meshing the first spiral body 3b of the fixed scroll 3 and the second spiral body 4b of the swinging scroll 4 with each other. The compression chamber 43 has a volume that decreases from the outside toward the inside in the radial direction. Therefore, the refrigerant is gradually compressed by taking in the refrigerant from the outer ends of the first spiral body 3b and the second spiral body 4b and moving it toward the center. The compression chamber 43 communicates with the discharge hole 3c at the center of the fixed scroll 3. A discharge valve 9 is attached to a second surface 313, which is a surface on one end side U of the fixed scroll 3, to prevent backflow of the refrigerant. The discharge valve 9 is attached to open and close the discharge hole 3c provided in the fixed scroll 3 within a preset opening range. As described above, the discharge valve holder 10 is provided above the discharge valve 9. The discharge valve holder 10 protects the discharge valve 9 from deformation while restricting the movable range of the discharge valve 9 by supporting the discharge valve 9 from the back side when the discharge valve 9 is opened. Moreover, as shown in FIG. 3, a muffler 25 having discharge holes 3c may be further provided.

As shown in FIG. 2 or 4, the main shell 2a includes a first inner wall surface 111, a first protrusion 112 that protrudes from the first inner wall surface 111 and positions the fixed scroll 3, and one end of the first protrusion 112. and a first positioning surface 113 facing toward side U. That is, the first positioning surface 113 is the upper end surface portion of the first protrusion 112 . Furthermore, as shown in FIG. 2 or FIG. A second positioning surface 116 facing the one end side U. That is, the second positioning surface 116 is the upper end surface portion of the second protrusion 115. In this way, the inner wall of the main shell 2a is provided with two steps in the Z direction. The inner diameter of the main shell 2a decreases in two steps toward the other end L in the Z direction. This will be explained in detail below. First, a first step is formed by providing a first protrusion 112 on the first inner wall surface 111 . The inner wall of the main shell 2a below the first protrusion 112 is a second inner wall surface 114. The inner diameter of the second inner wall surface 114 is smaller than the first inner wall surface 111 by the amount of the first protrusion 112 . Next, a second protrusion 115 is provided on the second inner wall surface 114, thereby forming a second step. The fixed scroll 3 is housed in the main shell 2a so that the outermost edge of the first surface 312 in the radial direction is disposed on the first positioning surface 113, as shown in FIG. Thereby, the position of the fixed scroll 3 in the Z direction is determined. The first substrate 3a of the fixed scroll 3 is fixed to the first inner wall surface 111 by shrink fitting or the like while being positioned by the first positioning surface 113. The frame 5 is housed within the main shell 2a such that the lower end surface portion 511 of the main body portion 5a is disposed on the second positioning surface 116. Thereby, the position of the frame 5 in the Z direction is determined. The frame 5 is fixed to the second inner wall surface 114 by shrink fitting or the like while being positioned by the second positioning surface 116 .

As shown in FIGS. 1 and 3, the upper shell 2b is inserted from one end side U of the main shell 2a and fixed by welding, arc spot welding, or the like. At this time, as shown in FIG. 4, the upper shell positioning surface 213 provided at the lower end of the upper shell 2b presses the fixed scroll 3 against the first positioning surface 113 of the main shell 2a. Thereby, the position of the fixed scroll 3 in the Z direction is determined. Furthermore, while maintaining the pressed state, the fixed scroll 3 is fixed to the main shell 2a by shrink fitting. This suppresses variations in the height of the refrigerant intake space 44 for each product of the compressor 1, improves the positional accuracy of the fixed scroll 3, and prevents the fixed scroll 3 from shifting in the vertical direction when the compressor 1 is driven. suppress. As a result, lifting of the fixed scroll 3 in the axial direction can be prevented.

<Method for manufacturing compressor 1>
Next, a method for manufacturing the compressor 1 according to the first embodiment will be described. The method for manufacturing the compressor 1 includes, for example, the following steps (a) to (d). (a): Frame fixing step of fixing the frame 5 to the inner wall surface of the main shell 2a; (b): After the frame fixing step, the fixed scroll 3 and the frame are fixed using pins (not shown) protruding from the frame 5. (c): After the phase determining step, a first substrate fixing step of fixing the first substrate 3a of the fixed scroll 3 to the inner wall surface of the main shell 2a, (d): 1 After the board fixing process, the extraction process involves removing the pins used for phase determination.

Specifically, in step (a), among the outer circumferential surfaces of the frame 5, the outermost outer circumferential surface in the radial direction is fixed to the inner wall surface of the main shell 2a by shrink fitting or the like. Then, in step (b), rod-shaped pins are inserted into the recesses formed in the frame 5 and the fixed scroll 3 to determine the phase between the fixed scroll 3 and the frame 5. The recess formed in the frame 5 is recessed downward in the Z direction. Further, the recess formed in the fixed scroll 3 is recessed upward in the Z direction, or is a through hole penetrating the first substrate 3a. A recess formed in the frame 5 and a recess formed in the fixed scroll 3 are arranged to face each other in the Z direction, and a rod-shaped pin is inserted into these recesses. Thereby, the fixed scroll 3 and frame 5 are phased. Then, in step (c), the outer peripheral surface of the first substrate 3a of the fixed scroll 3 is fixed to the inner wall surface of the main shell 2a by shrink fitting or the like. In this way, the rotational phases of the fixed scroll 3 and the frame 5 are determined. Next, in step (d), the pin is extracted from the recess formed in the frame 5 and the recess formed in the fixed scroll 3. By removing the pin, interference between the pin and the swinging scroll 4 can be eliminated. Note that if there is no possibility of interference between the pin and the swinging scroll 4, the pin may remain inserted in the recess formed in the frame 5 and the recess formed in the fixed scroll 3.

<Rotation suppression mechanism of fixed scroll 3>
Next, the rotation suppressing mechanism 50 that prevents deviation in the rotational phase of the fixed scroll 3, which is the main feature of the first embodiment, will be explained using FIGS. 5 to 11. The rotation suppressing mechanism 50 of the fixed scroll 3 includes the fixed scroll 3 and the upper shell 2b.

FIG. 5 is a sectional view showing the configuration of the upper shell 2b provided in the compressor 1 according to the first embodiment. In FIG. 5, a sectional view taken along line AA in FIG. 7 is shown. FIG. 6 is a perspective view schematically showing the configuration of the upper shell 2b provided in the compressor 1 according to the first embodiment. FIG. 7 is a plan view showing the configuration of the upper shell 2b provided in the compressor 1 according to the first embodiment from the back side. In FIG. 7, the state where the upper shell 2b is viewed from the other end side L is shown.

On the other hand, FIG. 8 is a plan view showing the configuration of the fixed scroll 3 provided in the compressor 1 according to the first embodiment. In FIG. 8, the fixed scroll 3 is shown viewed from one end side U. FIG. 9 is a sectional view showing the configuration of the fixed scroll 3 provided in the compressor 1 according to the first embodiment. In FIG. 9, a cross-sectional view taken along the line DD in FIG. 8 is shown. FIG. 10 is a schematic perspective view showing a schematic configuration of the fixed scroll 3 provided in the compressor 1 according to the first embodiment. In FIG. 10, the fixed scroll 3 is shown viewed from the other end L. As mentioned above, FIG. 10 is a schematic diagram schematically showing the configuration of the fixed scroll 3, and the fixed scroll 3 according to the first embodiment is different from the spiral shape and the number of turns of the first spiral body 3b. etc. are different.

FIG. 11 is a partial perspective view showing the rotation suppression mechanism 50 of the upper shell 2b and fixed scroll 3 in the compressor 1 according to the first embodiment. FIG. 11 shows a perspective view of the upper shell 2b cut along the two-dot chain line C in FIG. 7, and the fixed scroll 3 cut along the two-dot chain line E in FIG.

As shown in FIGS. 5 to 7, the upper shell 2b has a dome shape. Alternatively, the upper shell 2b has a cylindrical shape with a bottom. The lower end of the upper shell 2b is open. As shown in FIGS. 5 and 6, a claw portion 214 is provided at the lower end of the upper shell 2b. As shown in FIGS. 1 and 3, the claw portion 214 is a portion inserted into the opening at one end U of the main shell 2a. The plate thickness _T2 of the claw portion 214 is the same as that of the other portions of the upper shell 2b. In a conventional general compressor, a step is provided in the upper shell 2b by thinning the lower part of the upper shell 2b corresponding to the claw portion 214, and the step is formed in the main shell 2a of the upper shell 2b. It was a positioning part for the In contrast, in the first embodiment, the upper shell positioning surface 213 is used to position the upper shell 2b, so there is no need to reduce the thickness of the claw portion 214. Therefore, in the manufacturing process, the step of thinning the claw portion 214 is not necessary, so the number of processing steps is reduced accordingly, and the cost can be reduced.

The claw portion 214 has an upper shell positioning surface 213 and an upper shell rotation suppressing convex portion 211. The upper shell positioning surface 213 is provided on the lower end surface of the claw portion 214, and has a ring shape in plan view, as shown in FIG. Upper shell positioning surface 213 is arranged parallel to the XY plane. More specifically, the upper shell positioning surface 213 is composed of the "lower end surface of the claw portion 214" other than the upper shell rotation suppressing convex portion 211. The radial size (that is, the thickness) of the upper shell positioning surface 213 is the thickness T ₂ of the claw portion 214 . As shown in FIGS. 5 and 6, the upper shell rotation suppressing convex portion 211 is provided to protrude from the upper shell positioning surface 213 toward the other end side L. As shown in FIG. 5, the upper shell rotation suppressing convex portion 211 has a rectangular or substantially rectangular shape when viewed from the side. The thickness of the upper shell rotation suppressing convex portion 211 is the same as the thickness T ₂ of the upper shell positioning surface 213 . Therefore, the upper shell rotation suppressing convex portion 211 has a rectangular parallelepiped shape. However, the tip of the upper shell rotation suppressing convex portion 211 may be chamfered as shown in FIG. Similarly, the tip of the upper shell positioning surface 213 may also be chamfered, as shown in FIG. Note that in the examples shown in FIGS. 5 to 7, three upper shell rotation suppressing convex portions 211 are provided, but the present invention is not limited thereto. The number of upper shell rotation suppressing convex portions 211 may be any number greater than or equal to one. Further, the three upper shell rotation suppressing convex portions 211 are arranged at intervals in the circumferential direction. Note that the intervals may or may not be equal intervals.

As shown in FIGS. 8 to 10, the fixed scroll 3 includes a first substrate 3a and a first spiral body 3b. The first substrate 3a has a disk shape.

A fixed scroll rotation suppression recess 311 is provided in the first substrate 3a. The fixed scroll rotation suppression recess 311 is arranged at the outermost part of the second surface 313 in the radial direction, as shown in FIG. The fixed scroll rotation suppression recess 311 is recessed from the second surface 313 toward the other end side L, as shown in FIGS. 9 and 10. The fixed scroll rotation suppression recess 311 is recessed in the thickness direction of the first substrate 3a of the fixed scroll 3. The fixed scroll rotation suppressing recess 311 opens from the second surface 313 of the first substrate 3a toward one end side U, and opens from the side surface 314 toward the outside in the radial direction. The upper shell rotation suppressing convex portion 211 of the upper shell 2 b is inserted into the fixed scroll rotation suppressing recess 311 . The internal shape of the fixed scroll rotation suppression recess 311 is a rectangular parallelepiped, as shown in FIG. 11 . The internal shape of the fixed scroll rotation suppression concave portion 311 is complementary to the upper shell rotation suppression convex portion 211 . Note that in the examples shown in FIGS. 8 to 10, three fixed scroll rotation suppression recesses 311 are provided, but the present invention is not limited thereto. The number of fixed scroll rotation suppressing recesses 311 may be any number greater than or equal to one, but is preferably the same number as the upper shell rotation suppressing protrusions 211. However, it is desirable that the fixed scroll rotation suppressing recess 311 be provided in the first substrate 3a, avoiding the location where the injection horizontal hole 27 (see FIGS. 1 and 8) is formed. The injection horizontal hole 27 is formed in the first substrate 3a of the fixed scroll 3, as shown in FIG. For example, as shown in FIG. 8, the injection horizontal hole 27 extends from the injection installation hole in which the injection tube 24 is installed in the first substrate 3a toward the side surface 314 of the first substrate 3a.

When assembling the compressor 1, when inserting the upper shell 2b into the main shell 2a, the upper shell rotation suppressing convex portion 211 and the fixed scroll rotation suppressing recess 311 are combined. That is, the upper shell rotation suppressing convex portion 211 is inserted into the fixed scroll rotation suppressing recess 311. As a result, the upper shell rotation suppressing convex portion 211 and the fixed scroll rotation suppressing recess 311 are combined. When the fixed scroll 3 attempts to rotate in the circumferential direction, the circumferential side surface of the upper shell rotation suppressing convex portion 211 comes into contact with the circumferential side wall inside the fixed scroll rotation suppressing recess 311 . Therefore, rotation of the fixed scroll 3 in the circumferential direction due to abnormal pressure increase during operation is suppressed. Note that the fixed scroll rotation suppressing recess 311 does not penetrate through the thickness of the first substrate 3a in order to prevent communication between high and low pressures inside the compressor 1. Therefore, as shown in FIG. 9, when the thickness of the first substrate 3a is "thickness _T3 " and the depth of the fixed scroll rotation suppressing recess 311 is "depth _D3 ", _T3 > _D3. The relationship holds true.

At this time, as shown in FIG. 9, the "thickness H ₃ " of the first substrate 3a in the part where the fixed scroll rotation suppressing recess 311 is provided is naturally thinner than the "thickness T ₃ " in the other parts. become. Hereinafter, the thinned portion will be referred to as a thinned portion 315. If the "plate thickness _H3 " of the thin portion 315 is insufficiently secured, there is a concern that the first substrate 3a may be damaged due to the differential pressure between the high pressure space and the low pressure space. Therefore, the depth _D3 of the fixed scroll rotation suppressing recess 311 is desirably a value equal to or less than 3/4 of the thickness _T3 of the first substrate 3a. That is, it is desirable that the relationship 3/4×T ₃ ≧D ₃ holds true.

Furthermore, as described using FIG. 4, the fixed scroll 3 is sandwiched between the upper shell positioning surface 213 of the upper shell 2b and the first positioning surface 113 of the main shell 2a. Therefore, the height H ₂ of the upper shell rotation suppression convex portion 211 must be shorter than the depth D ₃ of the fixed scroll rotation suppression recess 311 . That is, the relationship D ₃ >H ₂ holds true. If the height _H2 of the upper shell rotation suppressing convex part 211 is longer than the depth _D3 of the fixed scroll rotation suppressing recess 311, the upper shell positioning surface 213 of the upper shell 2b and the second surface 313 of the fixed scroll 3 There will be a gap between the two. Therefore, the height H ₂ of the upper shell rotation suppression convex portion 211 is set to be shorter than the depth D ₃ of the fixed scroll rotation suppression recess 311 .

FIG. 12 is a partially enlarged cross-sectional view showing the configuration of the area surrounded by the dashed line F in FIG. In FIG. 12, the upper shell rotation suppressing convex portion 211 is inserted into the fixed scroll rotation suppressing recess 311. At this time, in the X direction, the upper shell rotation suppressing convex portion 211 is arranged between the side surface of the fixed scroll rotation suppressing recess 311 and the first inner wall surface 111 of the main shell 2a. At this time, there are spaces between the upper shell rotation suppressing convex part 211 and the side surface of the fixed scroll rotation suppressing recess 311, and between the upper shell rotation suppressing convex part 211 and the first inner wall surface 111 of the main shell 2a, respectively. There is a small gap. This is because if the upper shell rotation suppressing convex portion 211 is completely sandwiched, assembly cannot be performed. In the assembly process of the compressor 1, after the fixed scroll 3 is shrink-fitted to the main shell 2a, the upper shell 2b is inserted into the main shell 2a, and while the upper shell 2b is pressed down from above, the upper shell 2b and the main shell are Assembly is performed by welding 2a.
Furthermore, since the relationship D ₃ >H ₂ holds true, there is a gap between the top surface of the thin portion 315 of the first substrate 3a of the fixed scroll 3 having a thickness H ₃ and the tip surface 211a of the upper shell rotation suppressing convex portion 211. There is a small gap.

As described above, in the first embodiment, when inserting the upper shell 2b into the main shell 2a, the upper shell rotation suppressing convex portion 211 is fitted into the fixed scroll rotation suppressing recess 311. This restricts movement of the fixed scroll 3 in the circumferential direction. Therefore, rotation of the fixed scroll 3 in the circumferential direction can be prevented. In this manner, the upper shell rotation suppressing convex portion 211 is inserted into a portion of the fixed scroll 3, which is the object to be suppressed from rotating in the circumferential direction, and suppresses the circumferential rotation of the object to be suppressed.

In the first embodiment, as described above, the fixed scroll rotation suppressing recess 311 formed on the first substrate 3a of the fixed scroll 3, and the upper shell rotation suppressing protrusion 211 formed on the claw portion 214 of the upper shell 2b. constitutes the rotation suppression mechanism section 50. The fixed scroll rotation suppressing recess 311 is sometimes called a "first locking part" or a "first recess". Further, the upper shell rotation suppressing convex portion 211 is sometimes referred to as a “second locking portion” or a “convex portion”. When the "first locking part" and the "second locking part" are engaged, that is, the "convex part" is fitted into the "first recess", the claw part of the upper shell 2b 214 and the first substrate 3a of the fixed scroll 3 are engaged with each other.

When a phase shift occurs between the fixed scroll 3 and the oscillating scroll 4, symmetrical contact is not possible in the compression chamber 43, and a leakage gap occurs in the compression chamber 43 on one side in the X direction or the Y direction, resulting in a decrease in performance. . Therefore, it is desirable that the clearance in the circumferential direction between the upper shell rotation suppressing convex portion 211 that prevents rotation of the fixed scroll 3 and the fixed scroll rotation suppressing recess 311 is smaller. The circumferential clearance will be explained below using FIG. 11. Here, the circumferential size of the upper shell rotation suppressing convex portion 211 is defined as “distance L ₂ ”, and the circumferential size of the fixed scroll rotation suppressing concave portion 311 is defined as “distance W ₃ ”. At this time, the difference between "distance W ₃ " and "distance L ₂ " is called circumferential clearance (=W ₃ -L ₂ ). The clearance may be expressed as a difference in distance as described above, but it may also be expressed as a central angle with respect to the axial center of the main shaft 13 of the compressor 1. However, if the circumferential clearance is made too small, the upper shell 2b may not fit properly when the compressor 1 is assembled, or the processing cost may increase, resulting in a decrease in product productivity. Therefore, in the compressor 1 of the first embodiment, the clearance in the circumferential direction between the upper shell rotation suppressing convex portion 211 and the fixed scroll rotation suppressing recess 311 is set at a center with respect to the axial center of the main shaft 13 of the compressor 1. It is desirable to set the angle within 1.5 degrees. When the circumferential clearance is within 1.5 degrees, when a rotational phase shift occurs due to the rotation of the second spiral body 4b due to abnormal pressure increase in the compression chamber 43 during operation of the compressor 1, the compressor 1 It is possible to keep the impact on the product within the permissible range for the performance specified by. In this way, it is desirable that the clearance be appropriately set for each model of the compressor 1 so that the performance determined by the compressor 1 has no effect on the product within an allowable range.

The number of upper shell rotation suppression protrusions 211 and fixed scroll rotation suppression recesses 311 that constitute the rotation suppression mechanism may be at least one or more. As described above, the side surface 314 of the fixed scroll 3 and the first inner wall surface 111 of the main shell 2a are fixed by shrink fitting. Therefore, the rotation of the fixed scroll 3 only occurs with respect to the axial center of the fixed scroll 3, and the effect is the same even if there are two or more upper shell rotation suppressing convex portions 211. However, it is also possible to reduce the length L of the entire circumference of the claw portion 214 or the height H of the claw portion 214 (see FIG. 5) and increase the number of upper shell rotation suppression convex portions 211 and fixed scroll rotation suppression recesses 311. , a similar effect can be obtained. Therefore, a plurality of upper shell rotation suppressing protrusions 211 and fixed scroll rotation suppressing recesses 311 may be provided as long as they are four or less. When the number is 5 or more, the cost increases due to an increase in the machining time of the upper shell rotation suppressing convex portion 211 and the fixed scroll rotation suppressing concave portion 311, or the incidence of unassembled products increases due to the accumulation of tolerances of the claw portion 214. Therefore, it is undesirable. Therefore, in the first embodiment, it is desirable that the numbers of upper shell rotation suppressing convex portions 211 and fixed scroll rotation suppressing recesses 311 be 1 or more and 4 or less, respectively. Here, the length L of the entire circumference of the claw portion 214 is the total length in the circumferential direction of the inner circle of the ring-shaped upper shell positioning surface 213 shown in FIG. Therefore, the length L of the entire circumference of the claw portion 214 is a value that can be calculated based on the inner diameter of the upper shell positioning surface 213. Further, the height H of the claw portion 214 is the length of the entire claw portion 214 including the upper shell rotation suppressing convex portion 211 in the Z direction.

In order to prevent the upper shell rotation suppressing convex part 211 from being destroyed by the rotational force of the fixed scroll 3 due to abnormal pressure increase, the length _L2 in the circumferential direction of the upper shell rotation suppressing convex part 211 can be set as follows. desirable. That is, the length _L2 in the circumferential direction of the upper shell rotation suppressing convex portion 211 is 0.015 times or more the length L of the entire inner circle of the claw portion 214 of the upper shell 2b. is desirable. Further, as the circumferential length W ₃ of the fixed scroll rotation suppressing recess 311 becomes longer, the area of the thin portion 315 having the plate thickness H ₃ increases, and therefore reliability with respect to strength decreases. Therefore, the length _L2 in the circumferential direction of the upper shell rotation suppressing convex portion 211 should be 0.035 times or less the length L of the entire inner circle of the claw portion 214 of the upper shell 2b. is desirable. Therefore, in the first embodiment, the length L ₂ in the circumferential direction of the upper shell rotation suppressing convex portion 211 is 0.015 times or more and 0.035 times or less of the total circumferential length L of the claw portion 214. Preferably long.

In the conventional general scroll compressor described above, the peripheral wall of the frame extends to the fixed scroll, and the fixed scroll is fixed at the tip of the peripheral wall with bolts or the like. In this frame, the rotational phases of the frame, the swinging scroll, and the fixed scroll are ensured by using an Oldham ring and a highly accurate positioning component such as a reamer pin. However, in a frame without a peripheral wall, such as the frame 5 of Embodiment 1, a reamer pin cannot be used, and maintaining the phase of the fixed scroll 3 is a problem. Therefore, in the first embodiment, by having the following two configurations (A) and (B), the fixed scroll 3 can be installed in the compressor 1 equipped with the frame 5 without a peripheral wall without increasing the number of parts. Lifting up in the axial direction and rotation in the circumferential direction can be prevented.

(A) The first substrate 3a of the fixed scroll 3 has a first locking portion, and the claw portion 214 of the upper shell 2b has a second locking portion. The first locking portion and the second locking portion engage with each other to constitute a rotation suppression mechanism portion 50 that suppresses rotation of the fixed scroll 3 in the circumferential direction due to abnormal pressure increase during operation. .
(B) The first substrate 3a of the fixed scroll 3 is held between the claw portion 214 and the first inner wall surface 111 of the main shell 2a in the axial direction of the main shaft 13 of the compressor 1. More specifically, the first substrate 3a of the fixed scroll 3 has a first protrusion formed on the upper shell positioning surface 213 and the first inner wall surface 111 of the main shell 2a in the axial direction of the main shaft 13 of the compressor 1. 112.

As described above, in the first embodiment, in preparation for an abnormal pressure increase in the compression chamber 43, the mechanism that suppresses the fixed scroll 3 on a plane restricts the positional deviation in the height direction (configuration (B)), and the upper shell rotation suppressing convex part 211 and the fixed scroll rotation suppression recess 311 to restrict positional deviation in the circumferential direction (configuration (A)). By these regulations, it is possible to provide the compressor 1 with improved reliability against abnormal pressure increase in the compression chamber 43.

The circumferential positional deviation of the fixed scroll 3 will be explained using FIG. 15. FIG. 15 is a plan view schematically showing the configuration of the upper shell 2b provided in the compressor 1 according to the first embodiment. In FIG. 15, illustration of some structures such as the discharge pipe 23 and the injection pipe 24 is omitted for the sake of explanation. Moreover, in FIG. 15, for explanation, the first spiral body 3b of the fixed scroll 3 and the second spiral body 4b of the swinging scroll 4 are shown by broken lines. When the main shaft 13 rotates in the rotation direction R1 shown in FIG. 1, the rotation direction of the orbiting scroll 4 becomes the rotation direction R2. At this time, due to the oscillating motion of the compressor 1, the direction in which the positional deviation of the fixed scroll 3 in the circumferential direction occurs is in the opposite rotation direction (hereinafter referred to as the deviation direction) with respect to the rotation direction R2 of the oscillating scroll 4. R3). That is, the fixed scroll 3 is shifted in a rotation direction opposite to the rotation direction R2 of the oscillating scroll 4. At this time, the direction of the force by which the upper shell 2b supports the fixed scroll 3 is opposite to the displacement direction R3, and becomes a rotation direction R4 shown in FIG. 15. In this way, in each direction R1 to R4, the rotation directions R1, R2, and R4 are the same direction (for example, counterclockwise in FIG. 15), and only the displacement direction R3 of the fixed scroll 3 is in the opposite direction (for example, 15 clockwise).

Here, the clearance in the circumferential direction between the upper shell rotation suppressing convex portion 211 and the fixed scroll rotation suppressing recess 311 that prevent the rotation of the fixed scroll 3, which was explained using FIG. 11, is as shown in FIG. Consider the rear clearance S1 and the front clearance S2. The rear clearance S1 is a clearance arranged on the rear side in the displacement direction R3 of the fixed scroll 3. Further, the front clearance S2 is a clearance disposed on the front side in the displacement direction R3 of the fixed scroll 3.

Considering the displacement direction R3 of the fixed scroll 3, in order to reduce the amount of displacement of the fixed scroll 3, it is desirable to make the rear clearance S1 smaller than the front clearance S2. That is, when the circumferential size of the rear clearance S1 is "distance L _S1 " and the circumferential size of the front clearance S2 is "distance L _S2 ", the rear clearance is adjusted so that L _S1 < L _S2 . S1 and front clearance S2 are set. Ideally, it is desirable that the rear clearance S1=0.

FIG. 16 is a diagram showing an example of the shape of the upper shell rotation suppressing convex portion 211 formed on the upper shell 2b provided in the compressor 1 according to the first embodiment. In FIGS. 16(a) to (c), the side surface of the upper shell rotation suppressing convex portion 211 on the rear clearance S1 side is referred to as a side surface portion 211b, and the side surface of the upper shell rotation suppressing convex portion 211 on the front clearance S2 side is referred to as a side surface portion 211b. 211c.

The example shown in FIG. 16(a) shows a shape conforming to the configuration shown in FIG. 11. The shape of the upper shell rotation suppressing convex portion 211 is a rectangular parallelepiped. The shape of the upper shell rotation suppressing convex portion 211 when viewed from the radial direction is a rectangular shape, and the side surface portion 211b on the rear clearance S1 side and the side surface portion 211c on the front clearance S2 side of the upper shell rotation suppressing convex portion 211 are mutually It extends downward in parallel from the upper shell positioning surface 213, which is the lower end surface of the claw portion 214. In the example of FIG. 16(a), the force indicated by the arrow P is received by the side surface portion 211b. The example shown in FIG. 16(a) has the best workability among FIGS. 16(a) to 16(c). The fixed scroll rotation suppressing recess 311 has a complementary shape to the upper shell rotation suppressing convex 211, and therefore has a rectangular parallelepiped shape.

In the example shown in FIG. 16(b), the shape of the upper shell rotation suppressing convex portion 211 when viewed from the radial direction is as follows: It has a thick trapezoidal shape. This point differs from FIG. 16(a). In FIG. 16(b), the side surface portion 211c of the upper shell rotation suppressing convex portion 211 on the front clearance S2 side extends downward in the Z direction from the upper shell positioning surface 213. On the other hand, the side surface portion 211b of the upper shell rotation suppressing convex portion 211 on the rear clearance S1 side is inclined outwardly with respect to the downward direction as it goes downward in the Z direction from the upper shell positioning surface 213. In this way, in the example shown in FIG. 16(b), the upper shell rotation suppressing convex portion 211 basically has a rectangular parallelepiped shape, but is tapered at the end. In FIG. 16(b), the "distance _L2 " (see FIG. 11), which is the circumferential size of the upper shell rotation suppressing convex portion 211, gradually increases toward the lower side in the Z direction. In the example of FIG. 16(b), the force indicated by the arrow P is received at the upper end of the side surface portion 211b. In the example shown in FIG. 16(b), rotation of the fixed scroll 3 in the circumferential direction is suppressed the most among FIGS. 16(a) to 16(c). The shape of the fixed scroll rotation suppressing recess 311 is complementary to the upper shell rotation suppressing convex 211, and is therefore basically a rectangular parallelepiped, and tapers toward the upper side in the Z direction. There is. That is, the “distance W ₃ ” (see FIG. 11), which is the circumferential size of the fixed scroll rotation suppressing recess 311, gradually decreases toward the upper side in the Z direction.

In the example shown in FIG. 16(c), the shape of the upper shell rotation suppressing convex portion 211 when viewed from the radial direction is tapered downward from the upper shell positioning surface 213, which is the lower end surface of the claw portion 214. It has a trapezoidal shape. This point differs from FIG. 16(a). In FIG. 16C, the side surface portion 211c of the upper shell rotation suppressing convex portion 211 on the front clearance S2 side extends downward in the Z direction from the upper shell positioning surface 213. On the other hand, the side surface portion 211b of the upper shell rotation suppressing convex portion 211 on the rear clearance S1 side is inclined inwardly with respect to the downward direction as it goes downward in the Z direction from the upper shell positioning surface 213. In this way, in the example shown in FIG. 16(c), the upper shell rotation suppressing convex portion 211 basically has a rectangular parallelepiped shape, but is tapered. In FIG. 16(c), the "distance _L2 " (see FIG. 11), which is the circumferential size of the upper shell rotation suppressing convex portion 211, gradually decreases toward the lower side in the Z direction. In the example of FIG. 16(c), the force indicated by the arrow P is received at the lower end of the side surface portion 211b. In the example shown in FIG. 16(c), the amount of upward movement of the fixed scroll 3 is suppressed the most among FIGS. 16(a) to 16(c). The shape of the fixed scroll rotation suppression concave portion 311 is complementary to the upper shell rotation suppression convex portion 211, and is therefore basically a rectangular parallelepiped, and the tip becomes thicker toward the upper side in the Z direction. ing. That is, the “distance W ₃ ” (see FIG. 11), which is the circumferential size of the fixed scroll rotation suppressing recess 311, gradually increases toward the upper side in the Z direction.

In the first embodiment, only the upper shell rotation suppressing convex portion 211 is formed on the upper shell 2b and the fixed scroll rotation suppressing recess 311 is formed on the fixed scroll 3. Therefore, in any model of the compressor 1, Easy to configure.

When assembling the compressor 1, it is necessary to use a jig in the manufacturing process to position the upper shell 2b. In the first embodiment, the positional relationship between the discharge pipe 23 of the upper shell 2b and the upper shell rotation suppressing protrusion 211 is reduced by reducing the clearance between the fixed scroll rotation suppressing recess 311 and the upper shell rotation suppressing protrusion 211. is regulated. This eliminates the need for a positioning jig for the upper shell 2b. This will be explained in more detail. When assembling the compressor 1, the phases of the piping are determined in advance. In the first embodiment, the movement of the upper shell 2b in the circumferential direction is restricted by reducing the clearance of the upper shell rotation suppressing convex portion 211, so that the assembly phase of the upper shell 2b can be easily determined without a jig. I can do it. That is, by simply inserting the upper shell rotation suppressing convex portion 211 into the fixed scroll rotation suppressing recess 311, the assembly phase of the upper shell 2b can be automatically determined without a jig. As a result, the positional relationship between the discharge pipe 23 of the upper shell 2b and the upper shell rotation suppressing convex portion 211 is also automatically determined. Therefore, in the first embodiment, a positioning jig for the upper shell 2b is not required in the manufacturing process of the compressor 1.

Although the muffler 25 is not shown in FIG. 1, in the first embodiment, the muffler 25 may be provided as shown in FIG. As described above, depending on the model of the compressor 1, the muffler 25 is attached to the second surface 313 of the fixed scroll 3 in order to suppress noise. Conventionally, this muffler 25 has been fastened to the fixed scroll 3 with bolts. In the first embodiment as well, the muffler 25 may be fastened to the fixed scroll 3 with bolts, but the invention is not limited to that case. FIG. 13 is a partially enlarged sectional view showing the configuration of the area surrounded by the dashed line G in FIG. As shown in FIG. 3, the muffler 25 has a convex shape that protrudes toward one end side U. The lower end of the muffler 25 is open, and a flange portion 25a disposed outwardly is provided on the outer periphery of the opening. The flange portion 25a is formed around the entire circumference of the opening of the muffler 25, and constitutes a “lower end portion” of the muffler 25. The muffler 25 is fastened to the fixed scroll 3 by a flange portion 25a. In FIG. 13, the muffler 25 has an outer diameter equivalent to the inner diameter of the main shell 2a. Therefore, the tip 25b of the flange portion 25a is in contact with the first inner wall surface 111 of the main shell 2a, or is located between the upper shell positioning surface 213 and the second surface 313 of the fixed scroll 3. . That is, in FIG. 13, the flange portion 25a that constitutes the support surface of the muffler 25 is extended to the inner wall surface of the main shell 2a. Thereby, the flange portion 25a, which is the lower end portion of the muffler 25, can be sandwiched and fixed between the upper shell positioning surface 213 of the upper shell 2b and the second surface 313 of the fixed scroll 3. That is, the flange portion 25a is fixed by being sandwiched between the claw portion 214 of the upper shell 2b and the first substrate 3a over its entire circumference. In this manner, in the first embodiment, when the muffler 25 is provided, the flange portion 25a of the muffler 25 is sandwiched between the upper shell 2b and the first substrate 3a of the fixed scroll 3 in the Z direction. Thereby, the muffler 25 can be attached to the second surface 313 of the fixed scroll 3 without fastening bolts. Further, at this time, the muffler 25 may be provided with a notch 25c so as to be in the same phase as the fixed scroll rotation suppressing recess 311. FIG. 14 is a partially enlarged sectional view showing a configuration in which a notch 25c is provided in the area surrounded by the dashed line F in FIG. In the case of FIG. 14, the upper shell rotation suppressing convex portion 211 penetrates the inside of the notch 25c of the muffler 25 and is inserted into the fixed scroll rotation suppressing recess 311. As a result, the compressor 1 can be assembled by determining the phase of the muffler 25 as well as the phase of the fixed scroll 3 without using fastening bolts. This makes it possible to reduce costs and assembly time due to the boltless structure, and improve productivity. Furthermore, a convex portion protruding in the Z direction is formed on the muffler 25 similarly to the upper shell rotation suppressing convex portion 211 of the upper shell 2b, and the convex portion is inserted into a concave portion formed on the fixed scroll 3. The rotation may be stopped. In this case, the convex portion of the muffler 25 may be accommodated together with the upper shell rotation suppressing convex portion 211 in the same fixed scroll rotation suppressing recess 311 as the upper shell rotation suppressing convex portion 211 of the upper shell 2b.

As described above, in Embodiment 1, by having the above configurations (A) and (B), the floating of the fixed scroll 3 and , rotation of the fixed scroll 3 can be prevented. As a result, even if abnormal pressure rise occurs within the compression chamber 43, the positional accuracy of the fixed scroll 3 can be maintained. Further, as shown in FIG. 3, when the injection pipe 24 is provided and the fixed scroll 3 is largely displaced in the rotational direction, there is a risk that the injection pipe 24 will be damaged. However, in Embodiment 1, by having the above configuration (A), it is possible to suppress the occurrence of positional deviation due to rotation, or to suppress the positional deviation due to rotation to a slight deviation, so that the injection tube 24 can be prevented from being damaged.

Furthermore, in the first embodiment, when assembling the compressor 1, simply inserting the upper shell rotation suppressing convex portion 211 into the fixed scroll rotation suppressing recess 311 automatically adjusts the assembly phase of the upper shell 2b without using a jig. You can decide. Therefore, in the first embodiment, in the manufacturing process of the compressor 1, the fixed scroll 3 can be placed in the shell 2 with high positional accuracy without using a positioning jig for the upper shell 2b.

In addition, in Embodiment 1, an example was described in which a "convex part" is provided in the claw part 214 of the upper shell 2b, and a "first recessed part" is provided in the first substrate 3a of the fixed scroll 3. However, the invention is not limited to this case, and the claw portion 214 of the upper shell 2b may be provided with a "first recess", and the first substrate 3a of the fixed scroll 3 may be provided with a "protrusion".

Embodiment 2.
Next, the compressor 1 according to the second embodiment will be described with reference to FIGS. 17 and 18. FIG. 17 is a sectional view showing the configuration of an upper shell 2b provided in the compressor 1 according to the second embodiment. FIG. 17 is a diagram corresponding to FIG. 5 of the first embodiment. Further, FIG. 18 is a partial perspective view showing a rotation suppressing mechanism section 50A of the upper shell 2b and fixed scroll 3 in the compressor 1 according to the second embodiment. FIG. 18 is a diagram corresponding to FIG. 11 of the first embodiment.

In the second embodiment, the rotation suppression mechanism 50A includes a fixed scroll rotation suppression recess 311, an upper shell rotation suppression recess 212 formed in the claw portion 214 of the upper shell 2b, and a key 411. This point differs from the first embodiment. Since the other configurations are the same as those in Embodiment 1, their description will be omitted here.

As shown in FIG. 17, in the second embodiment as well, a fixed scroll rotation suppressing recess 311 is formed in the first substrate 3a of the fixed scroll 3, as in the first embodiment. The fixed scroll rotation suppression recess 311 is the same as that shown in Embodiment 1, so its description will be omitted here. However, the “distance W ₃ ” of the fixed scroll rotation suppression recess 311 may be the same as or different from the “distance W ₃ ” shown in the first embodiment.

Furthermore, in the second embodiment, as shown in FIGS. 14 and 17, an upper shell rotation suppressing recess 212 is formed in the claw portion 214 of the upper shell 2b. The upper shell rotation suppressing recess 212 is recessed from the upper shell positioning surface 213 of the claw portion 214 toward the one end side U. The upper shell rotation suppressing recess 212 is formed at a position that is in the same phase as the upper shell rotation suppressing protrusion 211 of the first embodiment. That is, the upper shell rotation suppressing recess 212 is formed at a position facing the fixed scroll rotation suppressing recess 311. The size and shape of the upper shell rotation suppression recess 212 are almost the same as the fixed scroll rotation suppression recess 311.

As shown in FIG. 18, the key 411 is fitted into both the fixed scroll rotation suppression recess 311 and the upper shell rotation suppression recess 212. That is, the upper part of the key 411 is fitted into the upper shell rotation suppression recess 212, and the lower part of the key 411 is fitted into the fixed scroll rotation suppression recess 311. Therefore, the shape of the upper part of the key 411 is complementary to the upper shell rotation suppressing recess 212, and the shape of the lower part of the key 411 is complementary to the shape of the fixed scroll rotation suppressing recess 311. By fitting the key 411 into both the fixed scroll rotation suppression recess 311 and the upper shell rotation suppression recess 212, the claw portion 214 and the first substrate 3a of the fixed scroll 3 are engaged with each other. The key 411 has, for example, a prismatic shape.

Note that when the key 411 is fitted into both the fixed scroll rotation suppression recess 311 and the upper shell rotation suppression recess 212, the upper shell positioning surface 213 of the claw portion 214 and the first substrate 3a of the fixed scroll 3 are connected to each other. The second surface 313 is in contact with the second surface 313 .

As described above, the second embodiment is a method in which rotation suppressing recesses are provided in both the upper shell 2b and the first substrate 3a of the fixed scroll 3, and the rotation suppressing recesses are fixed with the key 411.

Therefore, in the second embodiment, the fixed scroll rotation suppressing recess 311 formed in the first substrate 3a, the upper shell rotation suppressing recess 212 formed in the claw part 214, and the key 411 suppress the rotation. It constitutes a mechanism section 50A. The fixed scroll rotation suppressing recess 311 is sometimes called a "first locking part" or a "first recess". Further, the upper shell rotation suppressing convex portion 211 may be referred to as a “second locking portion” or a “second recess”. By the "first locking part" and the "second locking part" being engaged with each other via the key 411, that is, the key 411 is engaged with both the "first recess" and the "second recess". By being fitted, the claw portion 214 of the upper shell 2b and the first substrate 3a of the fixed scroll 3 are engaged with each other. The rotation suppression mechanism 50A suppresses movement of the fixed scroll 3 in the circumferential direction, so rotation of the fixed scroll 3 can be prevented.

Also, in the second embodiment, as in the first embodiment, as shown in FIG. and are sandwiched in the axial direction. Furthermore, the fixed scroll 3 is shrink-fitted to the main shell 2a. Thereby, it is possible to prevent the fixed scroll 3 from rising in the axial direction.

As described above, in the second embodiment, as in the first embodiment, a peripheral wall for fixing the fixed scroll 3 is not formed on the frame 5, and the lifting of the fixed scroll 3 and the fixed scroll 3 are prevented. Rotation can be prevented.

Since the upper shell 2b in the second embodiment is provided with the upper shell rotation suppressing recess 212 instead of a convex portion, the proportion of material resulting in cutting loss in the manufacturing stage in the unprocessed upper shell 2b is small. Moreover, since the base material of the upper shell 2b can be the same size as a conventional one without a convex portion, manufacturing costs can be kept low. Incidentally, in order to form the upper shell 2b of Embodiment 1 shown in FIG. Prepare something larger. Then, by cutting between the adjacent upper shell rotation suppressing protrusions 211, the upper shell rotation suppressing protrusions 211 are formed. Therefore, the material ratio resulting in cutting loss is larger than in the second embodiment.

When the upper shell rotation suppressing convex part 211 is provided in a part of the upper shell 2b as in the first embodiment, the strength of the upper shell rotation suppressing convex part 211 depends on the strength of the upper shell 2b. In the compressor 1 that uses high-pressure refrigerant, a large force is generated to rotate the fixed scroll 3 when the pressure in the compression chamber 43 is abnormally increased. Therefore, in order to improve the reliability of the upper shell rotation suppressing convex part 211, the distance L ₂ (see FIG. 11), which is the circumferential length of the upper shell rotation suppressing convex part 211, or the height H ₂ (see FIG. 11) needs to be increased. On the other hand, in the second embodiment, since rotation is suppressed using the key 411, the material and shape of the key 411 can be set arbitrarily. The key 411 is made of high-strength steel such as SUJ2 (high carbon chromium bearing steel). As a result, the size of the key 411 can be reduced, and the processing time for the upper shell 2b, fixed scroll 3, and key 411 can be expected to be shortened. Note that SUJ2 is a steel material that is often used for bearings and the like among special purpose steel materials. SUJ2 has excellent wear resistance.

In the second embodiment, the key 411 is shown in FIG. 17 as having a prismatic shape, but the key 411 is not limited to this case, and the key 411 may have any shape as long as it is easy to construct, such as a flat plate, a curved plate, or a cylinder. That's fine.

In the rotation suppressing mechanism 50A, as shown in FIG. 18, the length of the key 411 in the circumferential direction is defined as "distance _L4 ." Further, the size of the upper shell rotation suppressing recess 212 in the circumferential direction is defined as "distance W ₄ ". At this time, the difference between "distance W ₄ " and "distance L ₄ " is called a circumferential clearance. The circumferential clearance between the upper shell rotation suppressing recess 212 and the key 411 may be set to within 1.5 degrees with respect to the central axis of the main shaft 13 of the compressor 1. desirable. By setting the circumferential clearance within this range, the influence on the product due to the rotation of the fixed scroll 3 can be suppressed within an allowable range with respect to the performance determined by the compressor 1.

Similarly, in the rotation suppression mechanism portion 50A, as shown in _FIG _. ”. At this time, the difference between "distance W ₃ " and "distance L ₄ " is called a circumferential clearance. The circumferential clearance between the fixed scroll rotation suppressing recess 311 and the key 411 may be set to within 1.5 degrees in terms of the central angle with respect to the central axis of the main shaft 13 of the compressor 1. desirable. In this case as well, the influence on the product due to the rotation of the fixed scroll 3 can be suppressed within the permissible range with respect to the performance determined by the compressor 1.

Further, the circumferential length L ₄ of the key 411 in the rotation suppressing mechanism section 50A is 0.015 times or more and 0.035 times or less of the entire circumferential length L of the inner circle of the upper shell 2b. It is desirable that the length be . By making the length L ₄ 0.015 times or more, the strength of the key 411 can be ensured, and by making the length L 4 0.035 times or less, the plate thickness H ₃ of the fixed scroll 3 can be ensured. The strength of the thin wall portion 315 can be ensured.

Further, the depth _D3 of the fixed scroll rotation suppressing recess 311 in the rotation suppressing mechanism section 50A is desirably 3/4 or less of the thickness _T3 of the first substrate 3a of the fixed scroll 3. Thereby, the strength of the thin portion 315 of the fixed scroll 3 having a plate thickness of H ₃ can be ensured. Note that the depth _D3 of the fixed scroll rotation suppressing recess 311 and the depth _D4 of the upper shell rotation suppressing recess 212 may be the same or different.

Further, it is desirable that the tensile strength of the material forming the key 411 is at least twice the tensile strength of the material forming the upper shell 2b. Thereby, the strength of the key 411 can be ensured. Note that when the strength of the key 411 is higher than the strength of the upper shell rotation suppressing protrusion 211 shown in Embodiment 1, the length L ₄ of the key 411 is greater than the strength of the upper shell rotation suppressing protrusion 211 shown in Embodiment 1. 211 may be smaller than the length _L2 . Further, the sign of the length of the fixed scroll rotation suppressing recess 311, that is, _W3 , is the same as in the first embodiment, but when the length _L4 of the key 411 is small, the distance _W3 is naturally also In accordance with the length _L4 , it is smaller than in the first embodiment.

Embodiment 3.
FIG. 19 is a configuration diagram showing an example of the configuration of a refrigeration cycle device 601 according to the third embodiment. As shown in FIG. 19, the refrigeration cycle device 601 includes a compressor 1, a first heat exchanger 602, a first blower 603, an expansion valve 604, a second heat exchanger 605, and a second blower 606. , and a four-way valve 607.

The compressor 1 is the compressor 1 shown in Embodiment 1 or Embodiment 2. Compressor 1 sucks refrigerant flowing through refrigerant pipe 608 . The compressor 1 compresses the sucked refrigerant and discharges it to the refrigerant pipe 608. The refrigerant discharged from the compressor 1 flows into the first heat exchanger 602 or 605.

The first heat exchanger 602 and the second heat exchanger 605 exchange heat between the refrigerant flowing therein and air. The first heat exchanger 602 and the second heat exchanger 605 are, for example, fin-and-tube heat exchangers.

The first heat exchanger 602 functions as a condenser during cooling operation, and condenses and liquefies the refrigerant. The first heat exchanger 602 functions as an evaporator during heating operation, and evaporates and vaporizes the refrigerant.

The second heat exchanger 605 functions as an evaporator during cooling operation, and evaporates and vaporizes the refrigerant. The second heat exchanger 605 functions as a condenser during heating operation, and condenses and liquefies the refrigerant.

Further, the first blower 603 is attached to the first heat exchanger 602 and blows air toward the first heat exchanger 602. The second blower 606 is attached to the second heat exchanger 605 and blows air toward the second heat exchanger 605.

The four-way valve 607 is configured to switch its state between cooling operation and heating operation. The four-way valve 607 is a flow path switching device that switches the flow of refrigerant depending on the cooling operation and the heating operation. In the case of cooling operation, the four-way valve 607 is in the state shown by the solid line, and the refrigerant discharged from the compressor 1 flows into the first heat exchanger 602. On the other hand, in the case of heating operation, the four-way valve 607 is in the state shown by the broken line, and the refrigerant discharged from the compressor 1 flows into the second heat exchanger 605.

The expansion valve 604 is a pressure reducing device that reduces the pressure of the refrigerant and expands it, and is composed of, for example, an electronic expansion valve. When the expansion valve is an electronic expansion valve, the opening degree is adjusted based on instructions from a control device (not shown) or the like. Expansion valve 604 is provided between first heat exchanger 602 and second heat exchanger 605.

The compressor 1, the four-way valve 607, the first heat exchanger 602, the expansion valve 604, and the second heat exchanger 605 are connected by a refrigerant pipe 608 to form a refrigerant circuit that constitutes the refrigeration cycle device 601. There is.

The refrigerant is composed of, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a hydrocarbon, or a mixture thereof. Halogenated hydrocarbons having carbon double bonds are HFC refrigerants and fluorocarbon-based low GWP refrigerants that have zero ozone depletion potential. Examples of low GWP refrigerants include HFO refrigerants, including tetrafluoropropenes such as HFO1234yf, HFO1234ze, and HFO1243zf, which have the chemical formula C ₃ H ₂ F ₄ . Examples of halogenated hydrocarbons that do not have carbon double bonds include refrigerants in which R32 (difluoromethane), R41, and the like represented by CH ₂ F ₂ are mixed. Examples of hydrocarbons include natural refrigerants such as propane and propylene. An example of the mixture is a mixed refrigerant in which R32, R41, etc. are mixed with HFO1234yf, HFO1234ze, HFO1243zf, etc.

In Embodiment 3, the refrigerant thus includes, for example, HFO refrigerant or R32.

According to the third embodiment, the fixed scroll 3 can be arranged within the shell 2 with good positional accuracy without forming a peripheral wall for fixing the fixed scroll 3 to the frame 5 of the compressor 1. As a result, even if abnormal pressure rise occurs within the compression chamber 43, the positional accuracy of the fixed scroll 3 can be maintained.

1 Compressor, 1a Compression mechanism section, 1b Drive mechanism section, 1c Injection mechanism, 2 Shell, 2a Main shell, 2b Upper shell, 2c Lower shell, 2d Fixed base, 3 Fixed scroll, 3a First board, 3b First spiral body , 3c Discharge hole, 4 Oscillating scroll, 4a Second substrate, 4b Second spiral body, 4c Oscillating scroll boss portion, 4d Second Oldham groove, 4e Oscillating bearing, 4f Oscillating scroll thrust surface, 5 Frame, 5a Main body, 5b Frame boss, 5c Main bearing, 5d Suction port, 5e Swing bearing operating space, 5f Frame thrust surface, 5g Oldham housing section, 5h 1st Oldham groove, 5i Oil drain hole, 6 Oil return pipe, 7 Oldham Ring, 7a Ring part, 7b First key part, 7c Second key part, 8 Thrust plate, 8a Notch part, 9 Discharge valve, 10 Discharge valve holder, 11 Slider with balancer, 11a Slider part, 11b Balancer part, 12 Sleeve, 13 main shaft, 13a eccentric shaft part, 13b main shaft part, 13c oil supply passage, 13d main bearing part, 13e sub-bearing part, 14 first balancer, 15 rotor, 16 second balancer, 17 stator, 18 sub-frame, 19 sub- Bearing, 20 oil pump, 21 refrigeration oil, 22 suction pipe, 23 discharge pipe, 24 injection pipe, 25 muffler, 25a flange part, 25b tip part, 25c notch part, 26 glass terminal, 27 injection side hole, 40 oil sump part , 41 suction space, 42 discharge space, 43 compression chamber, 44 refrigerant intake space, 50 rotation suppression mechanism section, 50A rotation suppression mechanism section, 111 first inner wall surface, 112 first protrusion section, 113 first positioning surface, 114 2nd inner wall surface, 115 second protrusion, 116 second positioning surface, 211 upper shell rotation suppressing convex portion, 211a tip surface, 211b side surface, 211c side surface, 212 upper shell rotation suppressing recess, 213 upper shell positioning surface, 214 Claw portion, 311 Fixed scroll rotation suppression recess, 312 First surface, 313 Second surface, 314 Side surface, 315 Thin wall portion, 411 Key, 412 First surface, 413 Second surface, 414 Side surface, 511 Lower end surface portion, 601 Refrigeration Cycle device, 602 first heat exchanger, 603 first blower, 604 expansion valve, 605 second heat exchanger, 606 second blower, 607 four-way valve, 608 refrigerant piping, S1 rear clearance, S2 front clearance.

Claims

A bottomed cylindrical shell forming the outer shell;
a frame housed inside the shell;
an oscillating scroll slidably held in the frame;
a fixed scroll that forms a compression chamber for compressing refrigerant together with the oscillating scroll;
Equipped with
The shell is
a cylindrical main shell that accommodates the frame, the swinging scroll, and the fixed scroll;
an upper shell that seals an opening on one end side of the main shell;
has
The fixed scroll has a first substrate fixed to a first inner wall surface of the main shell,
The lower end portion of the upper shell has a claw portion that is inserted inside the opening on the one end side of the main shell,
the first substrate is held between the claw portion and the first inner wall surface in the axial direction of the shell;
The first substrate has a first locking part,
The claw portion has a second locking portion,
The first locking portion and the second locking portion are engaged with each other to constitute a rotation suppression mechanism portion that suppresses circumferential rotation of the fixed scroll.
compressor.
The claw portion has an upper shell positioning surface configured from a lower end surface of the claw portion,
The first inner wall surface of the main shell has a first protrusion that protrudes toward the inside of the main shell from the first inner wall surface and positions the fixed scroll,
the first substrate is held between the upper shell positioning surface and the first protrusion in the axial direction;
A compressor according to claim 1.
The rotation suppression mechanism section is
a first recess formed in the first substrate of the fixed scroll and forming the first locking part;
a convex portion formed on the claw portion of the upper shell, extending downward from a lower end surface of the claw portion, and constituting the second locking portion;
has
The first locking portion of the first substrate and the second locking portion of the claw portion are engaged with each other by fitting the convex portion into the first recess.
The compressor according to claim 1 or 2.
A circumferential clearance between the first concave portion and the convex portion in the rotation suppressing mechanism portion is set to be within 1.5 degrees at a central angle with respect to the central axis of the compressor.
The compressor according to claim 3.
A length L2 in the circumferential direction of the convex portion in the rotation suppressing mechanism portion is 0.015 times or more and 0.035 times or less with respect to the length L of the entire circumference of the inner circle of the upper shell.
The compressor according to claim 3 or 4.
The first recess in the rotation suppressing mechanism is recessed in the thickness direction of the first substrate,
The depth D3 of the first recess is 3/4 or less of the thickness T3 of the first substrate.
The compressor according to any one of claims 3 to 5.
The circumferential rotational deviation direction of the fixed scroll is a direction opposite to the rotational direction in which the oscillating scroll rotates,
When the clearance in the circumferential direction between the first concave portion and the convex portion in the rotation suppressing mechanism is divided into a front clearance on the front side in the direction of deviation and a rear clearance on the rear side, the circumference of the rear clearance The length L S1 in the direction is smaller than the length L S2 of the front clearance in the circumferential direction.
The compressor according to any one of claims 3 to 6.
The convex portion of the rotation suppressing mechanism has a rectangular shape when viewed from the radial direction,
The side surface portion of the rear clearance side and the side surface portion of the front clearance side of the convex portion extend downward from the lower end surface of the claw portion in parallel with each other.
The compressor according to claim 7.
The shape of the convex part in the rotation suppressing mechanism part when viewed from the radial direction is a trapezoidal shape that tapers downward from the lower end surface of the claw part,
The side surface portion of the protrusion on the front clearance side extends in the downward direction from the lower end surface of the claw portion,
A side surface portion of the convex portion on the rear clearance side is inclined outwardly with respect to the downward direction from the lower end surface of the claw portion toward the downward direction.
The compressor according to claim 7.
The shape of the convex part in the rotation suppressing mechanism part when viewed from the radial direction is a trapezoidal shape tapering downward from the lower end surface of the claw part,
The side surface portion of the protrusion on the front clearance side extends in the downward direction from the lower end surface of the claw portion,
The side surface portion of the convex portion on the rear clearance side is inclined inwardly with respect to the downward direction from the lower end surface of the claw portion toward the downward direction.
The compressor according to claim 7.
The rotation suppression mechanism section is
a first recess formed in the first substrate of the fixed scroll and forming the first locking part;
a second recess formed in the claw portion of the upper shell and forming the second locking portion;
a key fitted into both the first recess and the second recess;
has
By fitting the key into both the first recess and the second recess, the first locking portion of the first board and the second locking portion of the claw portion are engaged with each other. Ru,
The compressor according to claim 1 or 2.
The tensile strength of the material constituting the key is at least twice the tensile strength of the material constituting the upper shell.
The compressor according to claim 11.
The number of the rotation suppressing mechanisms is 1 or more and 4 or less,
The rotation suppressing mechanism parts are arranged at intervals from each other along the circumferential direction of the claw part.
The compressor according to any one of claims 1 to 12.
Equipped with a muffler to suppress noise,
The muffler has an outer diameter equivalent to an inner diameter of the main shell,
The lower end portion of the muffler is sandwiched between the claw portion of the upper shell and the first substrate over the entire circumference of the lower end portion of the muffler,
The lower end portion of the muffler has a notch, and at least a portion of the rotation suppressing mechanism is disposed to penetrate inside the notch.
The compressor according to any one of claims 1 to 13.
An upper shell with an open bottom end,
The lower end portion of the upper shell has a claw portion formed in a circumferential direction,
The claw portion has an upper shell rotation suppressing convex portion provided at at least one location in the circumferential direction of the claw portion and protruding downward from the claw portion,
The upper shell rotation suppressing convex portion is disposed below the upper shell and inserted into a portion of the suppressed object whose rotation in the circumferential direction is suppressed.
upper shell.