WO2023119625A1

WO2023119625A1 - Scroll compressor

Info

Publication number: WO2023119625A1
Application number: PCT/JP2021/048198
Authority: WO
Inventors: 政哉岡本; 浩二増本; 修平小山
Original assignee: 三菱電機株式会社
Priority date: 2021-12-24
Filing date: 2021-12-24
Publication date: 2023-06-29

Abstract

This scroll compressor comprises a shell (1), a main frame (2), a fixed scroll (4), an orbiting scroll (5), and a crankshaft (7), wherein the main frame (2) has an intake port (26) for supplying a refrigerant, which whirls around the crankshaft (7) in a space under the main frame (2), to a compression chamber. The intake port (26) is formed so as to be inclined, with respect to the axial direction of the crankshaft (7), along a direction in which the refrigerant flows from the space under the main frame (2) towards a space over the same.

Description

scroll compressor

The present disclosure relates to scroll compressors.

Conventionally, scroll compressors are known as compressors used in, for example, air conditioners or refrigeration systems. For example, the scroll compressor disclosed in Patent Document 1 includes a shell, a main frame fixed to the inner wall surface of the shell, and a fixed bed plate fixed to the inner wall surface of the shell and provided with a first spiral body. and an orbiting scroll having an orbiting bed plate which is pivotally supported by a main frame and provided with a second spiral body that meshes with the first spiral body. In the scroll compressor, a compression chamber for compressing refrigerant is formed between the first spiral body and the second spiral body by meshing the first spiral body and the second spiral body. The main frame is formed with an intake port for drawing refrigerant from the low pressure space of the shell into the compression chamber. The intake port is a space formed along the axial direction of the crankshaft so that the lower space and upper space of the main frame communicate with each other. Refrigerant flows into the interior of the shell from a suction pipe provided on the side of the shell, and flows into the compression chamber through a suction port provided on the main frame while rotating around the crankshaft axis in the lower space of the main frame. be.

JP 2020-515425 A

In the scroll compressor disclosed in Patent Document 1, the intake port formed in the main frame is formed in a direction perpendicular to the direction in which the crankshaft revolves around the axis. In other words, the intake port is not formed along the flow of the refrigerant moving from the lower space to the upper space of the main frame. Therefore, in this scroll compressor, when the refrigerant swirling in the lower space of the main frame flows into the suction port, it is likely to be subject to resistance, which may cause pressure loss of the refrigerant. In addition, as the compressor rotates at a higher speed, the amount of refrigerant circulated increases, and when the flow velocity of the refrigerant increases, the pressure loss increases, and there is a risk that the performance will deteriorate.

The present disclosure has been made to solve the above problems, and even if the refrigerant circulation amount increases and the refrigerant flow velocity increases, the increase in refrigerant pressure loss can be reduced, and performance deterioration can be suppressed. An object of the present invention is to provide a scroll compressor capable of

A scroll compressor of the present disclosure includes a shell having a closed space, a main frame fixed to an inner wall surface of the shell, a fixed scroll having a first substrate provided with a first spiral body,
an orbiting scroll that is swingably supported by the main frame, has a second substrate provided with a second spiral body that meshes with the first spiral body, and forms a compression chamber that compresses a refrigerant together with the fixed scroll; and a crankshaft for transmitting rotational driving force to the orbiting scroll, and the main frame is provided with a coolant that revolves around the crankshaft in a lower space of the main frame to supply the compression chamber. The intake port is inclined with respect to the axial direction of the crankshaft along the direction in which the refrigerant flows from the lower space to the upper space of the main frame. be.

According to the present disclosure, the intake port is formed to be inclined along the direction in which the refrigerant flows with respect to the axial direction of the crankshaft. In addition, the resistance that the refrigerant receives can be reduced. Therefore, even if the circulation amount of the refrigerant increases and the flow velocity of the refrigerant increases, the increase in the pressure loss of the refrigerant can be reduced, and the deterioration of the performance can be suppressed.

1 is a longitudinal sectional view showing an internal structure of a scroll compressor according to an embodiment; FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is the perspective view which decomposed|disassembled and showed the principal part of the scroll compressor which concerns on embodiment. It is an enlarged view of the III section shown in FIG. FIG. 4 is an explanatory diagram showing the flow of refrigerant in the scroll compressor according to the embodiment; It is an explanatory view showing roughly the suction port of the main frame of the scroll compressor concerning an embodiment. It is a cross-sectional view of the compression mechanism part of the scroll compressor which concerns on embodiment. FIG. 2 is an enlarged vertical cross-sectional view of the internal structure of the scroll compressor according to the embodiment, showing a portion in which a suction port is formed; It is explanatory drawing which looked at the main frame of the scroll compressor which concerns on embodiment from the downward side. It is explanatory drawing which looked at the main frame of the scroll compressor which concerns on embodiment from the downward side. It is a modification of the scroll compressor which concerns on embodiment, Comprising: It is a cross-sectional view of a compression mechanism part.

Embodiments of the present disclosure will be described below with reference to the drawings. In each figure, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. Further, the shape, size, arrangement, etc. of the configuration described in each drawing can be changed as appropriate.

Embodiment.
FIG. 1 is a vertical cross-sectional view showing the internal structure of a scroll compressor 100 according to an embodiment. FIG. 2 is an exploded perspective view showing the essential parts of the scroll compressor 100 according to the embodiment. FIG. 3 is an enlarged view of section III shown in FIG. The scroll compressor 100 according to the present embodiment shown in FIG. 1 is a so-called vertical scroll compressor that is used with the central axis of the crankshaft 7 substantially perpendicular to the ground. The scroll compressor 100 is one of the components of a refrigeration cycle used in, for example, refrigerators, freezers, air conditioners, refrigeration systems, water heaters, and the like.

The scroll compressor 100 sucks and compresses the refrigerant circulating in the refrigeration cycle, and discharges it in a high-temperature, high-pressure state. The scroll compressor 100, as shown in FIGS. A drive mechanism portion 6 that drives the portion 3 and a crankshaft 7 that connects the compression mechanism portion 3 and the drive mechanism portion 6 are provided.

The shell 1, as shown in FIG. 1, is made of a conductive member such as metal. The shell 1 has a sealed space formed therein by closing both ends of a cylindrical body. A main frame 2 , a compression mechanism portion 3 , a drive mechanism portion 6 , and a crankshaft 7 are housed inside the shell 1 .

The shell 1 has a cylindrical main shell 1a, a substantially hemispherical upper shell 1b that closes the upper opening of the main shell 1a, and a substantially hemispherical lower shell 1c that closes the lower opening of the main shell 1a. . Each of the upper shell 1b and the lower shell 1c has a part of the side wall fixed to the main shell 1a by welding or the like. The shell 1 is supported by a fixed base 1d fixed to the lower shell 1c.

As shown in FIG. 2, the inner wall surface of the main shell 1a consists of a large-diameter first inner wall surface 10a formed at the upper end, and a large-diameter first inner wall surface 10a formed below the first inner wall surface 10a. a second inner wall surface 10b having a smaller diameter than the second inner wall surface 10b; and a third inner wall surface 10c formed below the second inner wall surface 10b and having a smaller diameter than the inner diameter of the second inner wall surface 10b. A first stepped portion 11a formed by the lower end of the first inner wall surface 10a and the upper end of the second inner wall surface 10b and projecting radially from the inner wall surface of the shell 1 functions as a positioning portion for the fixed scroll 4. As shown in FIG. A second stepped portion 11b formed by the lower end of the second inner wall surface 10b and the upper end of the third inner wall surface 10c and projecting radially from the inner wall surface of the shell 1 functions as a positioning portion for the main frame 2. As shown in FIG.

As shown in FIG. 1, the main shell 1a is provided with a suction pipe 13 for taking refrigerant into the interior of the shell 1 and a power supply section 19 for supplying power to the scroll compressor 100. As shown in FIG. The suction pipe 13 is connected to a hole formed in the side wall of the main shell 1a by welding or the like while being partially inserted. The intake pipe 13 communicates with the internal space of the shell 1 . The power supply unit 19 includes a cover 19a, power supply terminals 19b, and wiring 19c. The power supply terminal 19b is a metal member, one end of which is arranged so as to be surrounded by the cover 19a, and the other end of which is arranged inside the main shell 1a. The wiring 19 c has one end connected to the power supply terminal 19 b and the other end connected to the drive mechanism section 6 .

A discharge pipe 14 for discharging the compressed refrigerant to the outside of the shell 1 is connected to the upper shell 1b. The discharge pipe 14 communicates with the internal space of the shell 1 . The discharge pipe 14 is connected by welding or the like while being partially inserted into a hole formed in the upper portion of the upper shell 1b. Further, an oil reservoir 18 for storing lubricating oil is provided in the inner bottom portion of the shell 1 .

As shown in FIGS. 1 and 2, the main frame 2 is a cylindrical metal frame tapering downward in stages, and supports the swing scroll 5 so as to swing freely. The outer peripheral wall of the main frame 2 is fixed to the second inner wall surface 10b of the main shell 1a by shrink fitting or the like while the outer peripheral wall is supported by the second step portion 11b of the main shell 1a. An annular flat surface 20 is formed on the upper surface of the main frame 2 . A ring-shaped thrust plate 25 made of a steel plate material such as valve steel is provided on the flat surface 20 . The thrust plate 25 functions as a thrust sliding surface of the main frame 2 and supports the thrust load of the compression mechanism section 3 .

Further, as shown in FIG. 2, the inside of the cylinder of the main frame 2 is composed of a housing portion 21 and a main bearing portion 22 that supports the crankshaft 7. As shown in FIG. The housing portion 21 is provided on the upper side of the main frame 2 . The main bearing portion 22 is provided on the lower side of the main frame 2 .

As shown in FIG. 2, the accommodating portion 21 is formed such that the inner diameter gradually decreases downward. The accommodation portion 21 has an Oldham accommodation portion 21a at a step portion located on the flat surface 20 side, and a bush accommodation portion 21b at a step portion located on the main bearing portion 22 side. A pair of first Oldham grooves 21c are provided in the Oldham housing portion 21a and a part of the flat surface 20 so as to face each other with the shaft hole interposed therebetween. The first Oldham groove 21c is a key groove. The first Oldham groove 21c partially overlaps the thrust plate 25 when the main frame 2 is viewed from above.

In addition, the main frame 2 is formed with an intake port 26 for supplying the compression mechanism 3 with refrigerant that revolves around the crankshaft 7 in the lower space of the main frame 2 . The intake port 26 is formed vertically through the outer end side of the flat surface 20 of the main frame 2 so as to communicate the lower space and the upper space of the main frame 2 . Specifically, in the outer peripheral wall of the main frame 2 , a concave portion 27 is formed along the circumferential direction of the main frame 2 so as to allow communication between the lower space and the upper space of the main frame 2 . The intake port 26 is a space surrounded by the recess 27 and the inner wall surface of the shell 1, as shown in FIGS. Further, the thrust plate 25 is formed with a notch portion 25a formed by notching a portion of the outer periphery at a position corresponding to the suction port 26 of the main frame 2. As shown in FIG. The notch 25a has the same shape as the suction port 26 or is larger than it so as not to cover the suction port 26. As shown in FIG.

In addition, as shown in FIGS. 1 and 3, the main frame 2 is fixed by inserting an oil return pipe 24 into an oil return hole 23 formed through the inside and outside. The oil return hole 23 communicates with the bush accommodating portion 21b. The oil return pipe 24 is provided to return the lubricating oil accumulated in the housing portion 21 to the oil reservoir 18 provided in the lower shell 1c. In addition, the number of the oil return hole 23 and the oil return pipe 24 is not limited to one, and a plurality of them may be provided.

The main frame 2 is made of iron-based metal or aluminum-based metal. When the main frame 2 is formed using a ferrous material, the shape is formed by casting. Further, when the main frame 2 is formed using a carbon steel material for machine structural use, it is formed by machining. The main frame 2 is formed by casting or forging when using an aluminum-based material.

The compression mechanism section 3 has a fixed scroll 4 and an orbiting scroll 5 . As shown in FIGS. 2 and 3, the fixed scroll 4 has a disk-shaped first substrate 4a and a first spiral body 4b provided on the lower surface of the first substrate 4a. The orbiting scroll 5 has a disk-shaped second substrate 5a and a second spiral body 5b provided on the upper surface of the second substrate 5a and meshing with the first spiral body 4b. The orbiting scroll 5 is installed eccentrically with respect to the fixed scroll 4 . The first spiral body 4b of the fixed scroll 4 and the second spiral body 5b of the orbiting scroll 5 are combined to form a compression chamber 30 for compressing the refrigerant.

The fixed scroll 4 is made of metal such as cast iron. The fixed scroll 4 is fixed to the first inner wall surface 10a by shrink fitting or the like while the outer peripheral surface of the first substrate 4a is supported by the first step portion 11a of the main shell 1a. The fixed scroll 4 is not limited to being fixed to the first inner wall surface 10a, and may be fixed to the main frame 2 by screwing or the like.

A discharge port 40 is formed in the central portion of the first substrate 4a for discharging the compressed high-temperature and high-pressure refrigerant. A chamber 15 having a discharge hole 15 a communicating with a discharge port 40 is provided on the upper surface of the fixed scroll 4 . The chamber 15 is provided with a discharge valve 17 that opens and closes the discharge hole 15a according to the pressure of the refrigerant. The discharge valve 17 opens the discharge hole 15a when the refrigerant in the compression chamber 30 communicating with the discharge port 40 reaches a predetermined pressure. The compressed high-temperature and high-pressure refrigerant is discharged from the discharge port 40 into the high-pressure space 16 above the fixed scroll 4 and discharged to the outside of the shell 1 through the discharge pipe 14 . A groove is formed at the tip of the first spiral body 4b, and a tip seal 41 made of hard plastic, for example, is provided in the groove.

The orbiting scroll 5 is made of metal such as aluminum. As shown in FIGS. 1 to 3, the orbiting scroll 5 revolves around the fixed scroll 4 without rotating due to an Oldham ring 54 for preventing rotation. The surface of the second substrate 5a on which the second spiral body 5b is not formed (lower surface in the illustrated example) functions as an orbiting scroll thrust bearing surface. A hollow cylindrical boss portion 51 is provided at the center of the orbiting scroll thrust bearing surface. A rocking bearing that rotatably supports the slider 80 of the bush 8 is provided on the inner peripheral surface of the boss portion 51 . The rocking bearing is a so-called journal bearing. The swing bearing is provided so that its central axis is parallel to the central axis of the crankshaft 7 . The orbiting scroll 5 revolves on the thrust sliding surface of the main frame 2 by rotating the eccentric shaft portion 71 of the crankshaft 7 inserted into the boss portion 51 .

A groove is formed at the tip of the second spiral body 5b, and a tip seal 52 made of hard plastic, for example, is provided in this groove. A pair of second Oldham grooves 53 are provided on the orbiting scroll thrust bearing surface so as to face each other with the boss portion 51 interposed therebetween. The second Oldham groove 53 is an elongated key groove. The pair of second Oldham grooves 53 are arranged so that the line connecting them is perpendicular to the line connecting the pair of first Oldham grooves 21c.

The Oldham ring 54 includes a ring portion 54a, a first key portion 54b, and a second key portion 54c. The ring portion 54 a has an annular shape and is housed in the Oldham housing portion 21 a of the main frame 2 . The first key portion 54b is provided on the lower surface of the ring portion 54a. The first key portions 54b are formed in pairs and are accommodated in the pair of first Oldham grooves 21c of the main frame 2, respectively. The second key portion 54c is provided on the upper surface of the ring portion 54a. The second key portions 54c are formed in pairs and are accommodated in the pair of second Oldham grooves 53 of the orbiting scroll 5, respectively. By aligning the second Oldham groove 53 of the orbiting scroll 5 with the second key portion 54c of the Oldham ring 54, the rotational position of the second spiral body 5b of the orbiting scroll 5 is determined. That is, the Oldham ring 54 positions the orbiting scroll 5 with respect to the main frame 2 and determines the phase of the second spiral body 5 b with respect to the main frame 2 . In the Oldham ring 54, the first key portion 54b slides in the first Oldham groove 21c and the second key portion 54c slides in the second Oldham groove 53 when the orbiting scroll 5 revolves due to the rotation of the crankshaft 7. By doing so, the orbiting scroll 5 is prevented from rotating.

The compression chamber 30 is formed by meshing the first spiral body 4b of the fixed scroll 4 and the second spiral body 5b of the orbiting scroll 5, and a tip seal 41 and a second seal 41 provided at the tip of the first spiral body 4b. It is formed by sealing with the substrate 5a, the tip seal 52 provided at the tip of the second spiral body 5b, and the first substrate 4a. The compression chambers 30 are composed of a plurality of compression chambers whose volumes decrease from the outside toward the inside in the radial direction of the scroll.

The refrigerant consists of, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon not having a carbon double bond, a hydrocarbon, or a mixture containing them. Halogenated hydrocarbons having carbon double bonds are HFC refrigerants with zero ozone depletion potential, Freon-based low GWP refrigerants, and tetrafluoropropenes such as HFO1234yf, HFO1234ze, and HFO1243zf represented by the chemical formula C3H2F4. exemplified. Halogenated hydrocarbons having no carbon double bond are exemplified by refrigerants mixed with R32 (difluoromethane) represented by CH2F2, R41 and the like. Hydrocarbons are exemplified by natural refrigerants such as propane and propylene. The mixture is exemplified by a mixed refrigerant obtained by mixing HFO1234yf, HFO1234ze, HFO1243zf and the like with R32, R41 and the like.

The drive mechanism section 6 drives the compression mechanism section 3 connected via the crankshaft 7, as shown in FIG. The drive mechanism 6 is composed of an annular stator 6a fixedly supported by shrink fitting or the like on the inner wall surface of the shell 1, and a rotor 6b rotatably mounted facing the inner surface of the stator 6a. . The stator 6a has, for example, a core formed by laminating a plurality of electromagnetic steel sheets and a winding wound through an insulating layer, and is formed in a ring shape in a plan view. The rotor 6b has a structure in which a permanent magnet is built in an iron core formed by laminating a plurality of electromagnetic steel sheets, and has a through hole penetrating vertically in the center. The rotor 6b is arranged with its outer peripheral surface maintaining a predetermined gap from the inner peripheral surface of the stator 6a.

The crankshaft 7 is a rod-shaped member made of metal, as shown in FIG. The crankshaft 7 has a main shaft portion 70 and an eccentric shaft portion 71 . The main shaft portion 70 is a shaft forming a main portion of the crankshaft 7, and is arranged so that its central axis coincides with the central axis of the main shell 1a. The main shaft portion 70 is fixed to the central through hole of the rotor 6b by shrink fitting or the like, and is fixed to the main bearing portion 22 provided in the central portion of the main frame 2 and the lower portion of the shell 1 by welding or shrink fitting. It is rotatably supported by a sub-bearing portion 90 provided in the central portion of the sub-frame 9 .

The eccentric shaft portion 71 is provided at the upper end portion of the main shaft portion 70 so that its central axis is eccentric with respect to the central axis of the main shaft portion 70, as shown in FIGS. The eccentric shaft portion 71 is connected to the orbiting scroll 5 via a bush 8 that is a metal member such as iron, and is rotatably supported by a boss portion 51 of the orbiting scroll 5 . The crankshaft 7 rotates with the rotation of the rotor 6b, and rotates the orbiting scroll 5 with the eccentric shaft portion 71. As shown in FIG. An oil passage 72 is provided inside the main shaft portion 70 and the eccentric shaft portion 71 so as to penetrate vertically along the axial direction.

The bushing 8 includes a slider 80 and a balance weight 81, as shown in FIGS. The slider 80 is a tubular member having a flange, and is rotatably inserted into the boss portion 51 . An eccentric shaft portion 71 is inserted into the slide surface of the slider 80 . In other words, the slider 80 is interposed between the orbiting scroll 5 and the eccentric shaft portion 71 to vary the radius of oscillation of the orbiting scroll 5 and to support the orbiting scroll 5 to revolve. be.

The balance weight 81 is provided to offset the centrifugal force of the orbiting scroll 5 generated by the orbiting motion. The balance weight 81 is provided eccentrically with respect to the center of rotation. The balance weight 81 has an annular lower portion, and a substantially C-shaped weight portion 81 a is provided on the upper portion on the side opposite to the direction of the centrifugal force acting on the orbiting scroll 5 . The scroll compressor 100 can reduce the pressing of the second spiral body 5 b against the first spiral body 4 b by the balance weight 81 . The balance weight 81 is fitted to the collar of the slider 80 by shrink fitting, for example.

The subframe 9 is a metal frame. The sub-frame 9 includes a sub-bearing portion 90 and an oil pump 91, as shown in FIG. The sub-bearing portion 90 is a ball bearing provided in the center of the sub-frame 9 . The oil pump 91 is a pump for sucking up lubricating oil stored in the oil sump 18 of the shell 1 and is provided below the sub-bearing portion 90 . The oil pump 91 is arranged so that at least a portion of it is immersed in lubricating oil.

The lubricating oil is stored in the oil reservoir 18. The lubricating oil is sucked up by the oil pump 91, passes through the oil passage 72 of the crankshaft 7, and is used to reduce wear between mechanically contacting parts such as the compression mechanism 3, adjust the temperature of the sliding parts, and improve the sealing performance. Improve. As the lubricating oil, an oil that is excellent in lubricating properties, electrical insulation, stability, refrigerant solubility, low-temperature fluidity, etc. and has an appropriate viscosity is suitable. Lubricating oils that can be used include, for example, naphthenic, polyol ester (POE), polyvinyl ether (PVE), and polyalkylene glycol (PAG) oils.

Next, while referring to FIGS. 1 to 3, the features of the intake port 26 of the main frame 2 will be described with reference to FIGS. 4 to 9. FIG. FIG. 4 is an explanatory diagram showing the flow of refrigerant in the scroll compressor 100 according to the embodiment. FIG. 5 is an explanatory diagram schematically showing the intake port 26 of the main frame 2 of the scroll compressor 100 according to the embodiment. FIG. 6 is a cross-sectional view of the compression mechanism section 3 of the scroll compressor 100 according to the embodiment. FIG. 7 is a vertical cross-sectional view of the internal structure of the scroll compressor 100 according to the embodiment, and is an enlarged view of a main part showing a portion where the suction port 26 is formed. FIG. 8 is an explanatory diagram of the main frame 2 of the scroll compressor 100 according to the embodiment viewed from below. FIG. 9 is an explanatory diagram of the main frame 2 of the scroll compressor 100 according to the embodiment viewed from below. In FIG. 4 , the black arrow indicates the direction in which the refrigerant flows, and the white arrow indicates the direction of rotation of the crankshaft 7 . Moreover, in FIG. 5, only the features of the present embodiment are described, and other constituent elements are omitted.

Refrigerant flows into the shell 1 through a suction pipe 13 provided on the side surface of the shell 1 as indicated by the black arrows in FIG. Meanwhile, it flows into the compression chamber 30 through the intake port 26 provided in the main frame 2 . Refrigerant flowing into the shell 1 from the suction pipe 13 may be divided into clockwise and counterclockwise directions around the boss portion 51. Only the same turning direction as the outline arrow) remains, and it turns in one direction, which is the rotation direction of the crankshaft 7 (the outline arrow in FIG. 4). That is, the whirling direction of the refrigerant is determined according to the rotating direction of the crankshaft 7 no matter how many times the scroll compressor 100 is started.

By the way, in the scroll compressor 100 , if the intake port 26 formed in the main frame 2 is formed in a direction perpendicular to the direction in which the crankshaft 7 revolves around the axis, then revolving in the lower space of the main frame 2 will occur. When the refrigerant flows into the suction port 26, it is susceptible to resistance, causing pressure loss in the refrigerant. In addition, as the scroll compressor 100 rotates at a higher speed, the circulation amount of the refrigerant increases, and when the flow velocity of the refrigerant increases, the pressure loss increases, and there is a possibility that the performance of the scroll compressor 100 deteriorates.

Therefore, as shown in FIG. 5, the intake port 26 of the scroll compressor 100 according to the present embodiment is formed to be inclined with respect to the axial direction of the crankshaft 7 along the direction in which the refrigerant flows. That is, the intake port 26 is formed to be inclined in accordance with the rotational direction of the crankshaft 7 . Therefore, the inlet 26 a and the outlet 26 b of the suction port 26 are out of alignment along the circumferential direction of the main frame 2 . The larger the inclination angle of the suction port 26 is, the more suitable it can follow the direction in which the refrigerant flows. constrains the angle of inclination. Therefore, the inclination angle of the intake port 26 is set in consideration of these restrictions.

In addition, as shown in FIG. 6, two intake ports 26 are provided so as to face each other in the radial direction of the main frame 2 . The outlet 26b of one of the intake ports 26 is located between the outer edge of the main frame 2 and a straight line _X1 extending from the outer end 4c (winding end portion) of the first spiral body 4b toward the outer edge of the main frame 2. With the intersection point _O1 as a base point, it is formed at a position away from the outer end portion 4c of the first spiral body 4b. The outlet 26b of the other suction port 26 is located between the outer edge of the main frame 2 and a straight line _X2 extending from the outer end 5c (winding end portion) of the second spiral body 5b toward the outer edge of the main frame 2. With the intersection point _O2 as a base point, it is formed at a position away from the outer end 5c of the second spiral body 5b.

A recessed portion 27 that constitutes the intake port 26 is formed as a twisted groove in the outer wall surface of the main frame 2 . Therefore, the refrigerant taken into the suction port 26 is caused to flow along the inner wall surface of the shell 1 by centrifugal force. At this time, if the outlet 26b of the suction port 26 is arranged in the immediate vicinity of the outer end 4c of the first spiral body 4b or the outer end 5c of the second spiral body 5b, the refrigerant flowing out of the suction port 26 will flow into the shell. 1, the refrigerant flows to the outside of the first spiral body 4b or the second spiral body 5b, and is not properly taken into the vortices of the first spiral body 4b or the second spiral body 5b.

Therefore, as described above, the outlet 26b of the suction port 26 is arranged at the position shown in FIG. Keeping distance is desirable. As a result, the refrigerant flowing out of the suction port 26 can be prevented from flowing to the outside of the first spiral body 4b or the second spiral body 5b, and can efficiently flow into the vortex of the first spiral body 4b or the second spiral body 5b. It is captured. However, the outlet 26b of the suction port 26 through which the refrigerant is taken in from the outer end 4c of the first spiral body 4b is positioned closer to the outer end 4c of the first spiral body 4b than to the outer end 5c of the second spiral body 5b. shall be provided in Similarly, the outlet 26b of the suction port 26, through which the refrigerant is taken in from the outer end 5c of the second spiral body 5b, is closer to the outer end 5c of the second spiral body 5b than to the outer end 4c of the first spiral body 4b. position.

The outlet 26b of the intake port 26 should be positioned so that when the crankshaft 7 makes one revolution and the orbiting scroll 5 rocks, the intake port 26 and the second spiral body 5b do not overlap with each other due to the rocking motion. is desirable. This is because when the outlet 26b of the suction port 26 and the second spiral body 5b overlap, pressure loss occurs due to the narrow opening area of the outlet 26b at that moment.

Further, as shown in FIG. 7, the shell 1 has a second stepped portion 11b that protrudes radially from the inner wall surface and supports the outer peripheral wall of the main frame 2. As shown in FIG. Therefore, if the space surrounded by the recessed portion 27 formed in the outer peripheral wall of the main frame 2 and the inner wall surface of the shell 1 is defined as the suction port 26, the opening of the inlet 26a through which the refrigerant passes is equal to the dimension of the second stepped portion 11b. The area is smaller than the opening area of the outlet 26b. When the opening area of the inlet 26a through which the refrigerant passes becomes smaller than the opening area of the outlet 26b, the speed of the refrigerant near the outlet 26b decreases slightly, and the pressure loss of the inlet 26a increases with respect to the outlet 26b. Therefore, the inlet 26a of the suction port 26 is formed radially larger than the outlet 26b of the suction port 26 by the dimension of the second stepped portion 11b protruding in the radial direction. At this time, the inner surface of the recess 27 is inclined radially outward from the inlet 26a toward the outlet 26b. Therefore, since the opening area of the inlet 26a of the suction port 26 and the opening area of the outlet 26b of the suction port 26 can be made substantially the same, the pressure loss of the inlet 26a can be suppressed. The opening area of the inlet 26a of the suction port 26 and the opening area of the outlet 26b of the suction port 26 may be different if there is no problem such as pressure loss.

Also, as shown in FIG. 8, the two suction ports 26 may be a main port 260 and a sub-port 261 having an opening area smaller than that of the main port 260. The reason for changing the opening area of the suction port 26 is that the size of the opening area is restricted by the arrangement relationship of the reinforcing rib 28 provided on the main frame 2, the suction pipe 13 connected to the shell 1, and other members. because there is In this case, the sub-port 261 is desirably formed at a position closer to the suction pipe 13 than the main port 260 is. Further, desirably, as shown in FIG. 9, the main port 260 is formed at a position opposed to the intake pipe 13 with the main bearing portion 22 interposed therebetween. Optimally, the sub-port 261 is formed in the circumferential direction of the main frame 2 between the main port 260 and the main bearing portion 22 . By bringing the sub-port 261 closer to the suction pipe 13 in this way, the refrigerant can easily enter from the sub-port 261, and the amount of refrigerant taken in by the first spiral body 4b and the second spiral body 5b can be made approximately the same.

That is, the hole shape and size of the inlet 26a and the outlet 26b of the suction port 26 may be the same or different. In addition, considering the lower structure of the main frame 2, the intake port 26 is arranged such that the inlet 26a is positioned on the inner diameter side or the outer diameter side of the main frame 2, and the outlet 26b is positioned on the outer diameter side or the inner diameter side. , the inlet 26a and the outlet 26b may be shifted in the radial direction of the main frame 2.

In addition, by tilting the suction port 26 and reducing the resistance when the refrigerant flows into the suction port 26, the flow velocity of the refrigerant swirling in the lower space of the main frame 2 increases, and the refrigerating machine oil is taken into the compression chamber 30 together with the refrigerant. may increase the amount of Therefore, as shown in FIG. 5, it is desirable that the inner wall surface 26c of the suction port 26 is formed in a fine uneven surface so that the surface roughness of the inner wall surface 26c of the suction port 26 is moderately rough. As for the surface roughness of the inner wall of the suction port 26, for example, if it is cast, it is the casting surface, and if it is machined, it is a medium-grade machined surface or higher. By doing so, the refrigerating machine oil taken into the compression chamber 30 together with the refrigerant adheres to the fine uneven surface of the inner wall of the suction port 26, and the amount of refrigerating machine oil taken in can be suppressed.

Incidentally, when injecting the injection refrigerant into the compression chamber 30, the first substrate 4a of the fixed scroll 4 is provided with an inflow hole for injection at a position corresponding to the portion A shown in FIG. The injection coolant can be efficiently taken into the vortex together with the coolant that has flowed in from 26 .

Note that FIG. 10 is a cross-sectional view of the compression mechanism section 3, which is a modification of the scroll compressor 100 according to the embodiment. The suction port 26 is not limited to the configuration shown in FIGS. 1-9. As shown in FIG. 10, the intake port 26 is formed as a through hole extending vertically through the outer end side of the flat surface 20 of the main frame 2 so as to communicate between the lower space and the upper space of the main frame 2. It may be configured as

In this case, each suction port 26 is provided so that the position of the outlet 26 b faces the refrigerant intake position B that is taken into the compression chamber 30 . The position B where the refrigerant that has flowed into the upper space of the main frame 2 from the outlet 26b is taken into the compression chamber 30 is the outer end portion 5c (winding end portion) of the second spiral body 5b of the orbiting scroll 5 and the end portion of the fixed scroll 4. There are two points at the outer end portion 4c (winding end portion) of the first spiral body 4b. By providing the outlet 26b of the intake port 26 so as to face the intake position A of the refrigerant taken into the compression chamber 30, the refrigerant coming out of the intake port 26 is taken into the compression chamber 30 in the shortest distance, so that the refrigerant is received. Can suppress resistance. In addition, the intake port 26 of the present embodiment has, as an example, an oval shape in a plan view. The long axis direction of the ellipse is the same as the tangential direction of the outer periphery of the main frame 2 , and it is preferable that the extension of the long axis passes through the position A where the refrigerant is taken into the compression chamber 30 . Furthermore, the outlet 26b of the intake port 26 should preferably be positioned so that when the crankshaft 7 makes one revolution and the orbiting scroll 5 rocks, the intake port 26 and the second spiral body 5b do not overlap with each other due to the rocking motion. . This is because when the outlet 26b of the suction port 26 and the second spiral body 5b overlap, pressure loss occurs due to the narrow opening area at that moment.

Also, the hole shape and size of the inlet 26a and the outlet 26b of the suction port 26 shown in FIG. 10 may be the same or different. In addition, considering the lower structure of the main frame 2, the intake port 26 is arranged such that the inlet 26a is positioned on the inner diameter side or the outer diameter side of the main frame 2, and the outlet 26b is positioned on the outer diameter side or the inner diameter side. , the inlet 26a and the outlet 26b may be shifted in the radial direction of the main frame 2. Further, as shown in FIG. 5, the suction port 26 may have an inner wall surface 26c formed in a fine uneven surface so that the surface roughness of the inner wall surface 26c of the suction port 26 is moderately rough.

As described above, the scroll compressor 100 according to the present embodiment includes a shell 1 having a sealed space, a main frame 2 fixed to the inner wall surface of the shell 1, and a first spiral body 4b provided with a first spiral body 4b. It has a fixed scroll 4 having a substrate 4a, and a second substrate 5a which is swingably supported by the main frame 2 and provided with a second spiral body 5b which meshes with the first spiral body 4b. and a crankshaft 7 for transmitting rotational driving force to the orbiting scroll 5 . The main frame 2 has a suction port 26 for supplying the refrigerant swirling around the crankshaft 7 in the lower space of the main frame 2 into the compression chamber 30 . The intake port 26 is formed to be inclined with respect to the axial direction of the crankshaft 7 along the direction in which the coolant flows from the lower space to the upper space of the main frame 2 .

In the scroll compressor 100 according to the present embodiment, the intake port 26 is inclined with respect to the axial direction of the crankshaft 7 along the direction in which the refrigerant flows, that is, along the direction in which the refrigerant revolves around the axis of the crankshaft 7. As a result, when the refrigerant swirling in the lower space of the main frame 2 flows into the suction port 26, the resistance received by the refrigerant can be reduced. Therefore, even if the circulation amount of the refrigerant increases and the flow velocity of the refrigerant increases, the increase in the pressure loss of the refrigerant can be reduced, and the deterioration of the performance can be suppressed.

The outlet 26b of the suction port 26 has a base point at the intersection O1 between the straight line _X1 extending from the outer end 4c of the first spiral body 4b toward the outer peripheral edge of the main frame 2 and the outer peripheral edge of the main frame ₂ . , a straight line _X2 extending from a position away from the outer end portion 4c of the first spiral body 4b and the outer end portion 5c of the second spiral body 5b toward the outer peripheral edge of the main frame 2, and It is formed at one or both of the positions separated from the outer end portion 5c of the second spiral body 5b with the point of intersection _O2 with the peripheral edge as a base point. Thereby, the outlet 26b of the intake port 26 can be provided at a constant distance from the outer end 4c of the first spiral body 4b or the outer end 5c of the second spiral body 5b. Therefore, the scroll compressor 100 can prevent the refrigerant flowing out of the suction port 26 from flowing to the outside of the first spiral body 4b or the second spiral body 5b. It is entrapped in the vortex of 5b.

The intake port 26 has a main port 260 and a sub-port 261 having an opening area smaller than that of the main port 260 . Accordingly, it is possible to cope with the case where the size of the opening area of the suction port 26 is restricted by the arrangement relationship of the reinforcing rib 28 provided on the main frame 2, the suction pipe 13 connected to the shell 1, and other members. can be done.

The scroll compressor 100 according to the present embodiment further includes a suction pipe 13 that is connected to the shell 1 and sucks refrigerant from the outside of the shell 1 into the inside. The sub-port 261 is formed at a position closer to the intake pipe 13 than the main port 260 is. That is, by bringing the sub-port 261 closer to the suction pipe 13, the refrigerant can easily enter from the sub-port 261, and the amount of refrigerant taken in by the first spiral body 4b and the second spiral body 5b can be made approximately the same.

In addition, the main frame 2 has a main bearing portion 22 that supports the crankshaft 7 in its central portion. The main port 260 is formed at a position facing the intake pipe 13 with the main bearing portion 22 interposed therebetween. The sub-port 261 is formed between the main port 260 and the main bearing portion 22 in the circumferential direction of the main frame 2 . That is, by bringing the sub-port 261 closer to the suction pipe 13, the refrigerant can easily enter from the sub-port 261, and the amount of refrigerant taken in by the first spiral body 4b and the second spiral body 5b can be made approximately the same.

The shell 1 has a second step portion 11b that protrudes radially from the inner wall surface and supports the main frame 2. The inlet 26a of the suction port 26 is formed radially larger than the outlet 26b of the suction port 26 by the dimension of the second stepped portion 11b protruding in the radial direction. In the scroll compressor 100 according to the present embodiment, the opening area of the inlet 26a of the suction port 26 and the opening area of the outlet 26b of the suction port 26 are substantially the same even when the second step portion 11b is provided. Since the area can be reduced, the pressure loss of the inlet 26a can be suppressed.

The suction port 26 has an inner wall surface 26c formed in a fine uneven surface. As a result, the refrigerating machine oil taken into the compression chamber 30 together with the refrigerant adheres to the fine uneven surface of the inner wall of the suction port 26, and the amount of refrigerating machine oil taken in can be suppressed.

Although the scroll compressor 100 has been described above based on the embodiment, the scroll compressor 100 is not limited to the configuration of the embodiment described above. For example, the illustrated internal configuration of the scroll compressor 100 is not limited to the contents described above, and may include other components. Further, the number of suction ports 26 is not limited to two as shown in the figure, and may be one or three or more. In short, the scroll compressor 100 includes a range of design changes and application variations that are normally made by those skilled in the art within a range that does not deviate from the technical idea.

1 shell, 1a main shell, 1b upper shell, 1c lower shell, 1d fixed base, 2 main frame, 3 compression mechanism, 4 fixed scroll, 4a first substrate, 4b first spiral, 4c outer end, 5 rocking Scroll 5a Second substrate 5b Second spiral body 5c Outer end 6 Drive mechanism 6a Stator 6b Rotor 7 Crankshaft 8 Bushing 9 Subframe 10a First inner wall surface 10b Second inner wall Wall surface, 10c Third inner wall surface, 11a First stepped portion, 11b Second stepped portion, 13 Suction pipe, 14 Discharge pipe, 15 Chamber, 15a Discharge hole, 16 High pressure space, 17 Discharge valve, 18 Oil reservoir, 19 Power supply section , 19a cover, 19b power supply terminal, 19c wiring, 20 flat surface, 21 accommodating portion, 21a Oldham accommodating portion, 21b bush accommodating portion, 21c first Oldham groove, 22 main bearing portion, 23 oil return hole, 24 oil return pipe, 25 Thrust plate, 25a notch, 26 suction port, 26a inlet, 26b outlet, 26c inner wall surface, 27 recess, 28 reinforcing rib, 30 compression chamber, 40 discharge port, 41 tip seal, 51 boss, 52 tip seal, 53 Second Oldham groove, 54 Oldham ring, 54a ring portion, 54b first key portion, 54c second key portion, 70 main shaft portion, 71 eccentric shaft portion, 72 oil passage, 80 slider, 81 balance weight, 81a weight portion, 90 auxiliary bearing, 91 oil pump, 100 scroll compressor, 260 main port, 261 sub port.

Claims

a shell having an enclosed space;
a main frame fixed to the inner wall surface of the shell;
a fixed scroll having a first substrate provided with a first spiral body;
an orbiting scroll that is swingably supported by the main frame, has a second substrate provided with a second spiral body that meshes with the first spiral body, and forms a compression chamber that compresses a refrigerant together with the fixed scroll; ,
a crankshaft that transmits rotational driving force to the orbiting scroll,
The main frame has an intake port for supplying the refrigerant swirling around the crankshaft in the lower space of the main frame into the compression chamber,
The scroll compressor, wherein the intake port is inclined with respect to the axial direction of the crankshaft along the direction in which the refrigerant flows from the lower space to the upper space of the main frame.
The outer peripheral wall of the main frame is formed with a recess that communicates the lower space and the upper space of the main frame along the circumferential direction of the main frame,
2. The scroll compressor according to claim 1, wherein said intake port is surrounded by said recess and an inner wall surface of said shell.
The scroll compressor according to claim 1 or 2, wherein the inlet and the outlet of said intake port are formed with their positions shifted in the circumferential direction of said main frame.
The scroll compressor according to any one of claims 1 to 3, wherein the suction port is formed to be inclined in accordance with the rotational direction of the crankshaft.
The outlet of the intake port has a base point at the intersection of a straight line extending from the outer end of the first spiral body toward the outer peripheral edge of the main frame and the outer peripheral edge of the main frame. A position away from the outer end and a straight line extending from the outer end of the second spiral body toward the outer peripheral edge of the main frame intersects with the outer peripheral edge of the main frame as a base point, and the second spiral The scroll compressor according to any one of claims 1 to 4, wherein the scroll compressor is formed at one or both of the positions remote from the outer end of the body.
The scroll compressor according to any one of claims 1 to 5, wherein the suction port has a main port and a sub-port having an opening area smaller than that of the main port.
further comprising a suction pipe that is connected to the shell and sucks refrigerant from the outside of the shell to the inside;
7. The scroll compressor according to claim 6, wherein said sub-port is formed at a position closer to said intake pipe than said main port.
The main frame has a bearing portion that supports the crankshaft in a central portion,
The main port is formed at a position facing the suction pipe with the bearing interposed therebetween,
8. The scroll compressor according to claim 7, wherein said sub-port is intermediate between said main port and said bearing portion and is formed in the circumferential direction of said main frame.
The shell has a stepped portion that protrudes radially from an inner wall surface and supports the main frame,
The scroll compression according to any one of claims 1 to 8, wherein the inlet of the suction port is formed radially larger than the outlet of the suction port by the dimension of the radially projecting stepped portion. machine.
The scroll compressor according to any one of claims 1 to 9, wherein the suction port has an inner wall surface formed in a fine uneven surface.
11. The scroll compressor according to claim 10, wherein the suction port has a surface roughness of the inner wall surface equal to or higher than a casting surface or a medium grade machine finish surface.