Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a casing. The casing has a drive motor and a compression unit accommodated therein. The casing has beads provided on the outer circumferential surface thereof. The outer circumferential surfaces of the beads protrude radially outward from the outer circumferential surface of the casing. The inner circumferential surfaces of the beads are recessed radially outward from the inner circumferential surface of the casing. Accordingly, the beads can reduce radiated noise of the compressor by increasing rigidity of the casing. In addition, the beads expand an oil flow path, thereby securing a greater amount of oil recovery.

Description

Scroll compressor

[0001] The present invention relates to a scroll compressor capable of expanding the area of ​​the oil passage while increasing shell rigidity.

[0002] Scroll compressors can be classified into a closed-type scroll compressor in which the drive unit (or electric unit) and the compression unit are provided together inside the casing, and an open-type scroll compressor in which the drive unit (or electric unit) is provided outside the casing and only the compression unit is provided inside the casing.

[0003] Scroll compressors can be classified into upper compression or lower compression types depending on the location of the drive motor and the compressor, which constitute the drive or electric drive unit. The upper compression type is a method in which the compressor is located above the drive motor. The lower compression type is a method in which the compressor is located below the drive motor. This classification is based on examples where the casing is installed in a vertical or vertical shape; however, if the casing is installed horizontally, the left side may be classified as the upper side and the right side as the lower side for convenience.

[0004] Scroll compressors can be classified into low-pressure scroll compressors, in which the internal space of a casing equipped with a compression section forms the suction pressure, and high-pressure scroll compressors, in which the internal space of the casing forms the discharge pressure. While upper compression scroll compressors can be configured as low-pressure or high-pressure types, lower compression scroll compressors are generally configured as high-pressure scroll compressors considering the position of the suction pipe.

[0005] A high-pressure scroll compressor supplies oil from the casing to the compression chamber by utilizing the difference between the internal pressure of the casing and the internal pressure of the compression chamber (hereinafter referred to as differential pressure) as the internal space of the casing forms a discharge pressure. Accordingly, the oil supply pump can be simplified in a high-pressure scroll compressor. Unless otherwise specified, the scroll compressor described below may be defined as a bottom-compressing type and a high-pressure scroll compressor.

[0006] A scroll compressor is disclosed in the prior art patent document KR 10-2019-0131787 A (hereinafter referred to as 'Patent Document 1') related to the present invention.

[0007] According to Patent Document 1, a plurality of D-cut surfaces are formed along the circumferential direction on the outer surface of the stator. An oil passage may be formed between the D-cut and the inner surface of the cylindrical shell to allow oil to pass through.

[0008] The oil separated from the refrigerant in the upper space of the casing can move to the lower space of the casing through the oil passage.

[0009] However, Patent Document 1 states that when the area of ​​the D-cut forming the oil passage is expanded to increase the amount of oil recovered, the rigidity of the stator is reduced, causing the problem of the stator being deformed when the stator is press-fitted into the inner surface of the cylindrical shell.

[0010] As a result, the air gap between the rotor and the stator is reduced, leading to problems such as increased noise and vibration in the compressor.

[0011] In the case of casings, there is a problem in that it is difficult to increase rigidity by selectively increasing the shell thickness only in the necessary parts. Therefore, to increase the rigidity of the casing, the overall thickness of the shell must be increased.

[0012] The objective of the present invention is to provide a scroll compressor with a structure capable of solving the aforementioned problems.

[0013] The first objective is to provide a scroll compressor with a structure capable of increasing the rigidity of the casing without increasing the shell thickness.

[0014] The second objective is to provide a scroll compressor with a structure that can expand the area of ​​the oil passage without increasing the stator decut.

[0015] The third objective is to provide a scroll compressor with a structure capable of minimizing noise and vibration caused by stator deformation during stator press-fitting.

[0016] The fourth objective is to provide a scroll compressor with a structure that can increase the amount of oil recovered and improve the reliability and efficiency of the compression section.

[0017] The fifth objective is to provide a scroll compressor with a structure capable of selectively increasing rigidity where necessary in the casing.

[0018] As a result of intensive research, the inventors have found that the problem of the present invention or the first to third objectives described above can be achieved by the following embodiments of the present invention.

[0019] To achieve the above-mentioned objective, the scroll compressor according to the present invention is provided with a bead on the outer surface of the casing. The bead protrudes radially outward from the outer surface of the casing. Thereby, the bead can increase the rigidity of the casing and also increase the area of ​​the oil passage without increasing the thickness of the casing.

[0020] According to one example, the scroll compressor comprises: a casing forming the exterior of the compressor; a drive motor provided inside the casing; a compression unit disposed on one side of the drive motor and discharging compressed refrigerant into the internal space of the casing; a rotating shaft transmitting rotational force from the drive motor to the compression unit; and a bead formed to protrude radially outward from the outer surface of the casing toward the rotating shaft.

[0021] Through this, the bead can increase the rigidity of the casing and increase the area of ​​the oil passage.

[0022] According to one example, the casing may be formed in a cylindrical shape. The bead may extend along the circumferential or longitudinal direction of the casing.

[0023] Through this, the bead can selectively increase rigidity only where necessary in the casing. In particular, the bead forms an oil passage to connect oil grooves formed on the outer surface of the drive motor and the outer surface of the compression part, respectively.

[0024] According to one example, the beads may be provided in multiple numbers. The multiple beads may be spaced apart in the circumferential or longitudinal direction of the casing.

[0025] Through this, multiple of the above beads can be optimized to increase stiffness where necessary.

[0026] According to one example, the bead may include a first curved surface protruding radially outward from the outer circumference of the casing; and a second curved surface that is recessed radially outward from the inner circumference of the casing and faces in a direction opposite to the first curved surface in the radial direction. A thickness of the bead may be formed between the first curved surface and the second curved surface.

[0027] Through this, the bead can have a circumferential surface with the same curvature as the casing.

[0028] According to one example, the thickness of the casing may be formed between the outer surface and the inner surface of the casing. The thickness of the bead may correspond to the thickness of the casing.

[0029] Through this, the thickness of the bead is formed to be the same as or similar to the thickness of the casing, so that it can significantly contribute to increasing the rigidity of the casing without increasing the thickness of the casing.

[0030] According to one example, the maximum radial depth of the bead that is recessed outwardly in the radial direction from the inner circumference of the casing may be greater than or equal to the thickness of the casing.

[0031] Through this, the bead can increase the rigidity of the casing and expand the area of ​​the oil passage where necessary.

[0032] According to one example, the casing may include a cylindrical shell formed in a cylindrical shape; an upper shell covering the upper part of the cylindrical shell; and a lower shell covering the lower part of the cylindrical shell.

[0033] The above bead may be formed to protrude radially outward from the outer surface of the cylindrical shell.

[0034] Through this, the bead can increase the rigidity of the cylindrical shell and increase the area of ​​the oil passage.

[0035] According to one example, the rotation axis may be extended in the vertical direction. The cylindrical shell may be extended parallel to the axial direction of the rotation axis. The bead may be extended in the axial direction.

[0036] Through this, the bead can expand the area of ​​the oil passage at the top and bottom of the cylindrical shell.

[0037] According to one example, the rotation axis may be extended in the vertical direction. The cylindrical shell may be extended parallel to the axial direction of the rotation axis. The bead may be extended in the circumferential direction of the cylindrical shell.

[0038] Through this, the bead can increase the rigidity of the cylindrical shell and expand the area of ​​the oil passage of the cylindrical shell.

[0039] According to one example, the rotation axis may be extended in the vertical direction. The cylindrical shell may be extended parallel to the axial direction of the rotation axis. The bead may be extended in the axial and circumferential directions of the cylindrical shell.

[0040] Through this, the bead can increase the rigidity of the cylindrical shell as well as expand the area of ​​the oil passage of the cylindrical shell, thereby increasing the amount of oil recovered.

[0041] According to one example, the cylindrical shell may include a first cylindrical portion having a first diameter; and a second cylindrical portion having a second diameter larger than the first diameter and extending along the axial direction from one side of the first cylindrical portion.

[0042] The above bead may be provided in at least one of the first cylinder and the second cylinder.

[0043] Through this, the cylindrical shell is composed of a cylindrical section with a two-stage structure having different diameters, thereby increasing the rigidity of the casing.

[0044] According to one example, the first cylinder can accommodate the drive motor. The second cylinder can accommodate the compression part.

[0045] Through this, the diameter of the compression part can be configured to be larger than the diameter of the drive motor.

[0046] According to one example, the second cylinder may be positioned below the first cylinder. In this way, the scroll compressor may be configured as a bottom-compressing compressor.

[0047] According to one example, it may further include an inclined portion formed at an angle to connect the first cylinder portion and the second cylinder portion.

[0048] Through this, the inclined portion connects the connection point of the first cylinder portion and the second cylinder portion in an inclined shape rather than an angular shape, thereby minimizing resistance when oil, etc. moves.

[0049] According to one example, the drive motor may include a stator coupled to the inner circumference of the casing; a rotor rotatably disposed with an air gap inside the stator; and a first oil groove formed to penetrate axially in the outer circumference of the stator.

[0050] The above bead may be arranged to face the first oil groove in the radial direction.

[0051] Through this, the bead can further expand the area of ​​the oil passage together with the first oil groove to increase the amount of oil recovered.

[0052] According to one example, the compression member may include a pivot scroll coupled to the rotation axis; and a fixed scroll coupled to engage with the pivot scroll and forming a compression chamber together with the pivot scroll. It may include a second oil groove formed to penetrate axially on the outer surface of the fixed scroll.

[0053] The above bead may be positioned to face the above second oil groove in the radial direction.

[0054] Through this, the bead can further expand the area of ​​the oil passage together with the second oil groove to increase the amount of oil recovered.

[0055] According to one example, the compression unit may be positioned below the drive motor.

[0056] Through this, the scroll compressor can be a bottom compression type.

[0057] A scroll compressor according to another example of the present invention comprises a casing, a drive motor, a compression unit, and a rotating shaft. The drive motor may have a stator coupled to the inner circumference of the casing and a rotor rotatably disposed with an air gap inside the stator. The compression unit may have a main frame disposed on one side of the drive motor; a pivot scroll; and a fixed scroll coupled to engage with the pivot scroll and forming a compression chamber together with the pivot scroll. The rotating shaft may transmit rotational force from the drive motor to the compression unit. The scroll compressor may further include a bead formed to protrude radially outward from the outer circumference of the casing toward the rotating shaft.

[0058] Through this, the bead can increase rigidity without increasing the thickness of the casing. The bead forms an oil passage on the inner surface of the casing, significantly contributing to the expansion of the oil passage and thereby increasing the amount of oil recovered.

[0059] According to another example, the scroll compressor may further include a first oil groove formed between the inner surface of the casing and the outer surface of the drive motor; and a second oil groove formed between the inner surface of the casing and the outer surface of the compression part.

[0060] The above bead may be extended along the axial direction to connect the first oil groove and the second oil groove.

[0061] According to another example, the casing may include: a first cylindrical portion having a first diameter that accommodates the drive motor; a second cylindrical portion having a second diameter larger than the first diameter that accommodates the compression portion; and an inclined portion formed at an angle with respect to the axial direction to connect the first cylindrical portion and the second cylindrical portion.

[0062] Through this, the casing may include cylindrical parts with different diameters.

[0063] According to another example, the bead may be extended axially.

[0064] The above bead may include: a first bead portion provided on one side of the first cylindrical portion and positioned to face the outer surface of the stator; a second bead portion extending axially from one side of the first bead portion toward one end of the first cylindrical portion; and a third bead portion extending in the opposite direction to the second bead portion along the axial direction of the second cylindrical portion with the first bead portion in between.

[0065] Through this, the first bead portion and the second bead portion can be formed in the first cylinder portion, and the third bead portion can be formed in a necessary place in the cylinder portion.

[0066] According to another example, the circumferential width of the second bead portion or the third bead portion is,

[0067] The circumferential width of the first bead portion may be greater than or equal to the above.

[0068] By doing so, the second bead portion is located in the upper space of the casing, and the circumferential width of the second bead portion is greater than the circumferential width of the first bead portion, thereby increasing the amount of oil collected from the refrigerant in the upper space.

[0069] According to another example, the bead may extend along the circumferential direction of the second cylinder portion.

[0070] Through this, the bead extends circumferentially along the outer surface of the compression part coupled to the inner surface of the second cylinder part, and can connect the oil grooves of the compression part that are spaced apart in multiple places.

[0071] According to another example, the above bead can be formed in a multi-stage form.

[0072] The above bead may further include an inner bead portion protruding radially outward from the outer surface of the casing; and an outer bead portion protruding further radially outward from the outer surface of the inner bead portion.

[0073] Through this, the bead can be formed in a multi-stage or multi-layered form, thereby further expanding the cross-sectional area of ​​the oil channel.

[0074] According to another example, the bead may further include an axial bead extending along the axial direction of the casing; and a circumferential bead extending along the circumferential direction of the casing.

[0075] Through this, the axial bead and the circumferential bead form oil passages in various directions, allowing more oil to be recovered from the upper space of the casing to the lower space.

[0076] According to one example, the cross-sectional shape of the bead may be formed in a shape that is a combination of one or more of a triangle, a square, a trapezoid, or an arc.

[0077] According to another example, the casing is formed in a cylindrical shape. When the casing is cut radially, the bead may include: a first tapered portion formed at an angle extending away from the outer surface of the casing in a radially outward direction; a second tapered portion spaced apart along the circumferential direction from the first tapered portion and formed at an angle extending away from the outer surface of the casing in a radially outward direction; and a connecting portion connecting the first tapered portion and the second tapered portion adjacent in the circumferential direction.

[0078] According to another example, the first tapered portion and the second tapered portion may be symmetrical with respect to a radial centerline passing radially through the center of the casing and the center of the bead.

[0079] According to an embodiment of the present invention, the following effects can be achieved.

[0080] First, a bead is provided on the outer surface of the casing. The bead is formed to protrude radially outward from the outer surface of the casing. The bead may have a curvature corresponding to the outer surface of the casing. The thickness of the bead may be formed to be the same as the thickness of the casing.

[0081] Multiple beads may be provided. Beads may be formed where increased stiffness is required.

[0082] Through this, the bead can improve the rigidity of the casing. The bead can reduce radiated noise generated between the parts and the casing during compressor operation.

[0083] Second, the inner surface of the bead can be formed to be recessed radially outward from the inner circumference of the casing. Through this, the inner surface of the bead can form an oil passage on the inner circumference of the casing.

[0084] For example, the bead may include a first bead, a second bead, and a third bead. The first bead may be positioned toward the upper space of the casing. The first bead may collect oil separated from the upper space of the casing.

[0085] The second bead may be positioned to surround the outer surface of the drive motor. The second bead may be connected to communicate with the first bead. A first oil groove (e.g., a D-cut) may be formed on the outer surface of the drive motor so as to be recessed radially inward.

[0086] The second bead may be positioned to face the first oil groove. The second bead may be formed to be recessed radially outward from the inner surface of the casing surrounding the outer surface of the drive motor.

[0087] Through this, the second bead forms a first oil channel together with the first oil groove, thereby expanding the area of ​​the oil channel.

[0088] The third bead may be positioned to surround the outer surface of the compression section. The third bead may be connected to the second bead in communication. A second oil groove may be formed on the outer surface of the compression section so as to be recessed radially inward.

[0089] The third bead may be positioned to face the second oil groove. The third bead may be formed to be recessed radially outward from the inner surface of the casing surrounding the outer surface of the compression part.

[0090] Through this, the third bead forms the first oil channel together with the second oil groove, thereby expanding the area of ​​the oil channel.

[0091] The third bead can be connected to communicate with the lower space of the casing. Through this, the third bead can store the oil recovered through the first bead and the second bead in the lower space of the casing.

[0092] Therefore, the bead can secure a higher recovery rate. The bead can improve reliability and efficiency through noise reduction and the expansion of the oil recovery path.

[0093] FIG. 1 is a cross-sectional view illustrating the components of a scroll compressor according to one embodiment of the present invention.

[0094] FIG. 2 is a perspective view showing a bead extending along the axial direction on the entire outer surface of the casing in FIG. 1.

[0095] FIG. 3 is a cross-sectional view taken along III-III in FIG. 2, and is a conceptual diagram showing the bead and the first oil groove arranged facing each other.

[0096] FIG. 4 is a perspective view showing a bead extending along the axial direction on the lower part of the outer surface of a casing according to another embodiment of the present invention.

[0097] FIG. 5 is a cross-sectional view taken along VV in FIG. 4, and is a conceptual diagram showing the bead and the second oil groove arranged facing each other.

[0098] FIG. 6 is a perspective view showing a bead extending along the circumferential direction on the lower part of the outer surface of a casing according to another embodiment of the present invention.

[0099] Figure 7 is a conceptual diagram showing the casing of Figure 6 enclosing the parts of the compressor.

[0100] FIG. 8 is a perspective view showing a plurality of beads extending along the circumferential direction on the lower part of the outer surface of a casing according to another embodiment of the present invention.

[0101] FIG. 9 is a conceptual diagram showing a plurality of beads formed in the casing in FIG. 8 surrounding the compression part of the compressor and the oil storage space of the casing, respectively.

[0102] FIG. 10 is a perspective view showing a bead extending along the circumferential direction and formed in a multi-stage shape on the lower part of the outer surface of a casing according to another embodiment of the present invention.

[0103] Figure 11 is a conceptual diagram showing the bead formed in the casing in Figure 10 surrounding the oil storage space.

[0104] FIG. 12 is a perspective view showing a bead extending along the axial and circumferential directions on the outer surface of a casing according to another embodiment of the present invention.

[0105] Figure 13 is a conceptual diagram showing the casing of Figure 12 enclosing the parts of the compressor.

[0106] FIG. 14 is a perspective view showing a bead extending along the axial and circumferential directions on the lower part of the outer surface of a casing according to another embodiment of the present invention.

[0107] FIG. 15 is a perspective view showing a bead extending along the axial direction on the upper part of the outer surface of a casing according to another embodiment of the present invention.

[0108] FIG. 16 is a cross-sectional view taken along XVI-XVI in FIG. 15, and is a conceptual diagram showing the cross-sectional shape of the bead.

[0109] FIG. 17 is a conceptual diagram for comparing and explaining the area of ​​the oil passage according to the depression depth (3 mm, 5 mm) of the bead of the comparative example and the present invention.

[0110] Figure 18 is a graph showing the magnitude of radiated noise between the parts and the casing according to frequency during compressor operation.

[0111] Hereinafter, a scroll compressor according to an embodiment of the present invention will be described in detail with reference to the attached drawings.

[0112] In the following description, descriptions of some components may be omitted to clarify the features of the present invention.

[0113] 1. Definition of Terms

[0114] Terms including ordinal numbers, such as first, second, etc., may be used to describe various components, but said components are not limited by said terms. These terms are used solely for the purpose of distinguishing one component from another.

[0115] When it is stated that one component is "connected" or "connected" to another component, it should be understood that while it may be directly connected or connected to that other component, there may also be other components in between. On the other hand, when it is stated that one component is "directly connected" or "directly connected" to another component, it should be understood that there are no other components in between.

[0116] As used in this specification, singular expressions include plural expressions unless the context clearly indicates otherwise.

[0117] In the following description, “radial” or “radial” refers to a shape extending outward from a central point like spokes of a wheel.

[0118] In the following description, “axial direction” refers to the longitudinal direction of the axis of rotation.

[0119] In the following description, the term “radial direction” refers to the longitudinal direction of a line segment extending from the center of a circle or cylinder to a point on the circumference.

[0120] In the following description, “circumferential direction” refers to the direction of the circumference.

[0121] 2. Description of the configuration of a scroll compressor according to an embodiment of the present invention

[0122] FIG. 1 is a cross-sectional view illustrating the components of a scroll compressor according to one embodiment of the present invention.

[0123] Hereinafter, each configuration of a scroll compressor according to an embodiment of the present invention will be described with reference to the attached drawings.

[0124] A scroll compressor may include a casing (100), a drive motor (110), and a compression unit (120). However, the bead (150) structure of the casing (100) to be described later will be explained separately in a separate section.

[0125] (1) Components of a scroll compressor

[0126] The scroll compressor according to the present invention can be applied to an upper compression type scroll compressor or a lower compression type scroll compressor. The scroll compressor according to the present embodiment is shown applied to a lower compression type.

[0127] The scroll compressor described above includes a casing (100). The casing (100) forms the exterior or outer periphery of the compressor. A receiving space is provided inside the casing (100) to accommodate components constituting the compressor.

[0128] A drive motor (110) is installed inside the casing (100). The drive motor (110) constitutes an electric motor. A compression unit (120) is installed on the lower side of the drive motor (110).

[0129] The electric motor is coupled to one side of the rotating shaft (117). The compression unit (120) is coupled to the other side of the rotating shaft (117). Through this, the compression unit (120) is connected to the electric motor via the rotating shaft (117) and can operate by receiving rotational force from the electric motor.

[0130] The casing (100) includes a cylindrical shell (101), an upper shell (102), and a lower shell (103).

[0131] The cylindrical shell (101) can be formed in a cylindrical shape. Both ends of the cylindrical shell (101) can be opened in the vertical direction. A driving motor (110) and a main frame (121) can be inserted and fixed to the inner circumference of the cylindrical shell (101).

[0132] The upper shell (102) can be press-fitted to the upper part of the cylindrical shell (101). The upper shell (102) can form an upper space (1021) on the upper part of the casing (100) together with the cylindrical shell (101). The upper space (1021) is a sealed space and can temporarily store compressed refrigerant discharged from the compression unit (120) to be described later.

[0133] Oil and compressed refrigerant may be mixed in the upper space (1021) above. The oil and compressed refrigerant may be separated from each other due to differences in specific gravity. The oil, which has a relatively higher specific gravity, may pass through the drive motor (110) and the compression section (120) and move to the lower space (1031) of the casing (100).

[0134] A terminal bracket may be attached to the upper part of the upper shell (102). A terminal may be connected through the terminal bracket. The terminal is configured to apply external power to the drive motor (110).

[0135] A discharge pipe (104) may be connected to one side of the upper part of the upper shell (102) so as to pass through it. The inner end of the discharge pipe (104) may be connected to communicate with the upper space (1021) of the casing (100). The outer end of the discharge pipe (104) may be connected to a condenser. The discharge pipe (104) may be positioned higher than the drive motor (110).

[0136] Through this, the discharge pipe (104) can discharge the compressed refrigerant in the upper space (1021) of the casing (100) to the outside.

[0137] A suction pipe (134) is connected to one side of the cylindrical shell (101) so as to be in communication with the compression chamber of the compression unit (120) to be described later.

[0138] The lower shell (103) can be press-fitted to the bottom of the cylindrical shell (101). By doing so, the lower space (1031) of the casing (100) is sealed to form an oil storage space.

[0139] The drive motor (110) is installed on the upper part of the cylindrical shell (101). The drive motor (110) includes a stator (111) and a rotor (114).

[0140] The stator (111) includes a stator core (112) and a stator coil (113). The stator core (112) may be formed in a cylindrical shape. The stator core (112) may be pressed into and coupled to the inner surface of the cylindrical shell (101).

[0141] The stator core (112) includes a plurality of teeth (1121) and slots (1122). The teeth (1121) are formed to protrude radially toward the center from the inner surface of the stator core (112). The plurality of teeth (1121) are spaced apart at equal intervals in the circumferential direction of the stator core (112).

[0142] A slot (1122) may be formed between two adjacent teeth (1121) in the circumferential direction. Multiple teeth (1121) and multiple slots (1122) are arranged alternately along the circumferential direction. The slot (1122) is formed to penetrate the axial direction of the stator core (112).

[0143] The stator coil (113) is wound onto the stator core (112) through the slot (1122). The stator coil (113) is electrically connected to an external power source through a terminal so that the external power source can be applied to the stator coil (113).

[0144] An insulator may be installed to provide electrical insulation between the stator core (112) and the stator coil (113). The insulator may include a first insulator (1131) and a second insulator (1132).

[0145] The first insulator (1131) can be inserted and coupled to one axial side of the stator core (112) through the slot (1122). The second insulator (1132) can be inserted and coupled to the other axial side of the stator core (112) through the slot (1122).

[0146] The rotor (114) includes a rotor core (115) and a permanent magnet (116). The rotor core (115) may be formed in a cylindrical shape. The rotor core (115) is rotatably installed inside the stator core (112) with a predetermined air gap.

[0147] The permanent magnets (116) can be mounted so as to be embedded inside the rotor core (115). The permanent magnets (116) can be spaced apart at predetermined intervals along the circumferential direction of the rotor core (115).

[0148] A rotating shaft (117) can be press-fitted and coupled to the center of the rotor core (115). A rotating scroll (126), to be described later, can be eccentrically coupled to the lower part of the rotating shaft (117). Through this, the rotational force of the drive motor (110) can be transmitted to the rotating scroll (126) through the rotating shaft (117).

[0149] The rotation shaft (117) is formed to be long in the axial direction. One end of the rotation shaft (117) is connected to a drive motor (110), and the other end of the rotation shaft (117) can be connected to a compression part (120).

[0150] For example, the upper part of the rotation shaft (117) is coupled to be fixed to the rotor (114), and the lower part of the rotation shaft (117) can be inserted rotatably by passing through the main frame (121), the pivot scroll (126), and the fixed scroll (130) in sequence, which will be described later.

[0151] An eccentric portion (119) is eccentrically formed at the lower part of the rotation axis (117). The eccentric portion (119) can be eccentrically coupled to the rotation axis coupling portion (129) of the pivot scroll (126).

[0152] Through this, the rotating scroll (126) can rotate around the axis of rotation (117).

[0153] One side and the other side of the rotation axis (117) in the axial direction can be supported by a first bearing provided at the center of the main frame (121) and a second bearing provided at the center of the fixed scroll (130), respectively, with respect to the pivot scroll (126).

[0154] An oil pickup (118) may be installed at the bottom of the rotating shaft (117). The oil pickup (118) is positioned to be submerged in oil stored in the lower part of the casing (100). The oil pickup (118) is configured to suck in oil and move it to the upper part of the rotating shaft (117). An oil supply channel is formed to penetrate axially through the interior of the rotating shaft (117).

[0155] The compression unit (120) may include a main frame (121), a pivot scroll (126), a fixed scroll (130), and a discharge cover (138). For example, the fixed scroll (130) may be provided on the lower side of the main frame (121), and the pivot scroll (126) may be axially supported by the fixed scroll (130) and pivotably provided between the main frame (121) and the fixed scroll (130).

[0156] The main frame (121) may include a frame plate section (122), a frame side wall section (124), and a main bearing section (123).

[0157] The frame end plate (122) is formed in an annular shape and can be fixedly coupled to the inner circumference of the casing (100) at the lower side of the drive motor (110). For example, the frame end plate (122) can be fixed to the inner circumference of the cylindrical shell (101) by hot press fitting or by welding.

[0158] The frame side wall portion (124) may be formed in a cylindrical shape. The frame side wall portion (124) may be formed to protrude axially from the outer periphery of the frame plate portion (122) toward the fixed scroll (130) to be described later.

[0159] A plurality of first communication holes (1241) may be formed in the frame side wall portion (124). The plurality of first communication holes (1241) may be formed to penetrate in the axial direction. A recess portion (1242) may be formed in the frame end plate portion (122). The recess portion (1242) may be formed to be recessed on one axial surface of the frame end plate portion (122) to accommodate the plurality of first communication holes (1241).

[0160] The recess section (1242) is connected to the flow separation unit (160), which will be described later, through the first communication hole (1241), so that the refrigerant discharged through the first communication hole (1241) can be guided to move into the inside of the flow separation unit (160).

[0161] The Euro separation unit (160) may be positioned between the drive motor (110) and the main frame (121). The Euro separation unit (160) may include a first Euro guide (161), a second Euro guide (162), and a guide connection part (163). The first Euro guide (161) may be formed in the shape of a circular ring.

[0162] The first Euro guide (161) can extend toward the drive motor (110) from one axial surface of the frame plate portion (122). One axial end of the first Euro guide (161) can be joined by contacting one axial surface of the frame plate portion (122).

[0163] The axial end of the first Euro guide (161) can be connected to one axial surface of the stator core (112). One side of the first Euro guide (161) can be connected to a second insulator (1132) located on the lower side of the stator core (112).

[0164] The second Euro guide (162) may be provided on the inner side of the first Euro guide (161). The second Euro guide (162) may be formed in the shape of a circular ring with a smaller diameter than the first Euro guide (161). The second Euro guide (162) may extend toward the drive motor (110) from one axial side of the frame.

[0165] One axial end of the second Euro guide (162) can be connected by contacting one axial surface of the frame plate portion (122). One side of the second Euro guide (162) can be positioned spaced apart from the lower surface of the stator (111) nose.

[0166] The guide connecting portion (163) may extend radially between the first flow guide (161) and the second flow guide (162). The guide connecting portion (163) is configured to connect one axial end of the first flow guide (161) and one axial end of the second flow guide (162). The guide connecting portion (163) may be formed in the shape of a disc.

[0167] The guide connection part (163) is provided with a guide hole (164). The guide hole (164) is formed to be penetrating so as to be in communication with the first communication hole (1241) described above.

[0168] A refrigerant passage may be formed between the first Euro guide (161) and the second Euro guide (162). The refrigerant passage may be connected to communicate with the air gap between the stator (111) and the rotor (114).

[0169] Through this, the refrigerant passing through the first communication hole (1241) moves to the refrigerant flow path through the guide hole (164), and the refrigerant can pass through the drive motor (110) through the gap and move to the upper space (1021) of the casing (100).

[0170] An oil connection channel may be formed between the inner surface of the cylindrical shell (101) and the outer surface of the first oil guide (161). The upper side of the oil connection channel may be connected to communicate with the first oil groove (1123) formed between the inner surface of the cylindrical shell (101) and the outer surface of the drive motor (110), which will be described later. The lower side of the oil connection channel may be connected to communicate with the second oil groove (1321) formed between the inner surface of the cylindrical shell (101) and the outer surface of the compression part (120), which will be described later.

[0171] Through this, the oil separated in the upper space (1021) of the casing (100) can be moved to the lower space (1031) of the casing (100) and stored by passing through the first oil groove (1123), the oil passage of the oil separation unit (160), and the second oil groove (1321).

[0172] The main bearing portion (123) may protrude from the center of the frame plate portion (122) toward the drive motor (110) by a predetermined height. A main bearing hole, into which a rotation shaft (117) is rotatably inserted, may be formed through the center of the main bearing portion (123) in the axial direction.

[0173] Accordingly, the inner surface of the main bearing hole can support the rotating shaft (117) radially by forming a main bearing surface together with the main bearing surface of the rotating shaft (117) facing it. A bushing bearing (not shown) can be pressed into the inner surface of the main bearing hole so that the bushing bearing forms the actual main bearing surface.

[0174] The pivot scroll (126) is coupled to the rotation axis (117). The pivot scroll (126) is positioned between the main frame (121) and the fixed scroll (130). An Oldham ring (125), which is an anti-rotation mechanism, is provided between the main frame (121) and the pivot scroll (126). Through this, the pivot scroll (126) is restricted from rotating and can pivot relative to the fixed scroll (130).

[0175] The rotating scroll (126) may be configured to include a rotating plate section (127), a rotating wrap (128), and a rotating shaft coupling section (129).

[0176] The rotating plate portion (127) can be formed in the shape of a disc. The upper surface of the rotating plate portion (127) can be axially supported on the main frame (121).

[0177] An intermediate pressure chamber may be formed at the edge of the rotating plate section (127), that is, on the outer surface of the rotating plate section (127), together with the main frame (121) and the fixed scroll (130). The intermediate pressure chamber is connected to the compression chamber through an intermediate pressure passage to form an intermediate pressure (back pressure). Accordingly, the rotating plate section (127) receives the back pressure of the intermediate pressure chamber and is axially supported toward the fixed scroll (130), thereby suppressing leakage between the compression chambers.

[0178] The pivot wrap (128) can be formed in an involute shape. However, the pivot wrap (128) can be formed in various shapes other than an involute together with the fixed wrap (135). For example, the pivot wrap (128) may have a shape formed by connecting multiple arcs with different diameters and origins, and the outermost curve may be formed in a roughly elliptical shape having a major axis and a minor axis. The fixed wrap (135) may be formed in the same way.

[0179] The rotational shaft coupling portion (129) can be formed to penetrate axially at the inner end of the pivoting wrap (128), that is, at the central portion of the pivoting plate portion (127). Accordingly, the discharge hole (139), which will be described later, can be formed at the center of the pivoting scroll (126), that is, at an eccentric position from the rotational shaft coupling portion (129).

[0180] A rotating shaft (117) can be rotatably inserted and coupled to the rotating shaft coupling part (129). Accordingly, the outer periphery of the rotating shaft coupling part (129) is connected to the pivoting wrap (128) to form a first compression chamber (1281) together with the fixed wrap (135) during the compression process.

[0181] The pivoting wrap (128) is configured to pivot by engaging with the fixed wrap (135) of the fixed scroll (130) to be described later.

[0182] The rotating wrap (128) can be coupled with the fixed wrap (135) described later to form a first compression chamber (1281) and a second compression chamber (1282).

[0183] The compression chamber may be composed of a first compression chamber (1281) and a second compression chamber (1282) based on the swivel wrap (128). The first compression chamber (1281) and the second compression chamber (1282) may each consist of an intake pressure chamber, an intermediate pressure chamber, and a discharge pressure chamber. The intake pressure chamber, the intermediate pressure chamber, and the discharge pressure chamber are formed continuously from the outer edge of the fixed scroll (130) toward the center of the fixed scroll (130).

[0184] The first compression chamber (1281) refers to a compression chamber formed between the outer surface of the pivoting wrap (128) and the inner surface of the fixed wrap (135) facing it.

[0185] The second compression chamber (1282) refers to a compression chamber formed between the inner surface of the pivoting wrap (128) and the outer surface of the fixed wrap (135) facing it.

[0186] The fixed scroll (130) is positioned at the bottom of the main frame (121) with the rotating scroll (126) in between.

[0187] The fixed scroll (130) may include at least one of a fixed plate portion (131), a fixed bearing portion (136), a fixed side wall portion (132), and a fixed wrap (135).

[0188] The fixed plate portion (131) may be formed in the shape of a disc. The fixed plate portion (131) may be positioned at a predetermined interval on the lower side of the frame plate portion (122). A plurality of fastening holes (1311) may be formed to penetrate axially through the edge of the fixed plate portion (131).

[0189] A plurality of fastening grooves (141) may be formed to penetrate axially along the edge of the frame plate portion (122). Fastening members, such as screws, may be fastened to the fixed plate portion (131) and the frame plate portion (122) through the fastening hole (1311) and the fastening groove (141). Through this, the fixed scroll (130) may be coupled to the main frame (121) by the fastening members.

[0190] The above fastening hole (1311) can be formed to penetrate axially into the fixed side wall portion (132) to be described later.

[0191] A fixed bearing hole may be formed through the center of the fixed plate portion (131) in the vertical direction.

[0192] The fixed bearing portion (136) may protrude from the back surface of the fixed end plate portion (131) toward the discharge cover (138) to be described later by a predetermined height. A fixed bearing hole, into which a rotation shaft (117) is rotatably inserted, may be formed through the center of the fixed bearing portion (136) in the axial direction.

[0193] The fixed bearing portion (136) can form a part of the fixed end plate portion (131). The diameter of the fixed bearing portion (136) can be formed to be smaller than the diameter of the fixed end plate portion (131).

[0194] Accordingly, the inner surface of the fixed bearing hole can support the rotating shaft (117) in the radial direction by forming a fixed bearing surface together with the fixed bearing part (136) of the rotating shaft (117) facing it.

[0195] A bushing bearing can be press-fitted into the inner surface of the fixed bearing hole. The inner surface of the bushing bearing can form a substantial fixed bearing surface. The second bearing described above can be implemented as a bushing bearing.

[0196] A plurality of discharge holes (139) may be formed around the fixed bearing hole. The discharge holes (139) may be formed at an eccentric position from the center of the fixed plate portion (131). The plurality of discharge holes (139) may include a first discharge hole and a second discharge hole. The first discharge hole may be connected to communicate with the first compression chamber (1281). The second discharge hole may be connected to communicate with the second compression chamber (1282).

[0197] The discharge hole (139) may be formed to be in communication with the discharge pressure chambers of the first and second compression chambers (1282). The first and second compression chambers (1282) are formed on the inner and outer sides of the fixing wrap (135).

[0198] The discharge hole (139) can be opened and closed by a discharge valve (1391). The discharge valve (1391) can be implemented as an elastic rectangular plate spring. The discharge valve (1391) can open and close the discharge hole (139) by bending according to the discharge pressure of the refrigerant.

[0199] A plurality of bypass holes (140) may be provided in the fixed end plate portion (131) (see FIG. 5). The bypass holes (140) may be formed to penetrate axially through the fixed end plate portion (131) and the fixed bearing portion (136). Two or three bypass holes (140) may form a set and may be arranged adjacent to the inner and outer surfaces, respectively, in the radial direction of the fixed wrap (135). In this embodiment, two bypass holes (140) are shown forming a set.

[0200] A set of bypass holes (140) can be opened and closed simultaneously by a bypass valve (not shown).

[0201] A fastening groove (141) for fastening a bypass valve can be formed on the back surface of the fixed bearing part (136) in correspondence with the number of bypass valves.

[0202] The bypass hole (140) can be selectively opened by the bypass valve when excessive pressure occurs in the compression chamber during operation. For example, when the liquid refrigerant is not evaporated by the heat of compression, excessive pressure may occur in the compression chamber, and the bypass valve can open the bypass hole (140) due to the excessive pressure.

[0203] The fixed side wall portion (132) may be formed in a cylindrical shape. The fixed side wall portion (132) may protrude upward from the outer periphery of the fixed end plate portion (131). The fixed side wall portion (132) may extend circumferentially along the circumference of the fixed end plate portion (131).

[0204] The upper part of the fixed side wall (132) can be connected to the main frame (121).

[0205] A suction port (133) is provided on one side of the fixed side wall (132). The suction port (133) may be formed to penetrate radially on one side of the fixed side wall (132). A suction pipe (134) may be inserted into and connected to the suction port (133).

[0206] One end of the suction pipe (134) is connected to the compression chamber through the suction port (133). The other end of the suction pipe (134) passes through the cylindrical shell (101) and is connected to the evaporator (not shown) of the refrigeration cycle.

[0207] Accordingly, the refrigerant passing through the evaporator (not shown) of the refrigeration cycle can be directly sucked into the compression chamber. The internal space of the casing (100) can be filled with the refrigerant discharged from the compression chamber to form a high-pressure scroll compressor.

[0208] A plurality of second communication holes (142) may be formed to penetrate the outer periphery and the fixed side wall (132) of the fixed plate portion (131). The plurality of second communication holes (142) may be arranged in pairs of an even number and spaced apart in the circumferential direction.

[0209] The upper portion of the second communication hole (142) can be connected to the first communication hole (1241) formed at the edge of the main frame (121). The lower portion of the second communication hole (142) can be connected to the muffler space (1381) of the discharge cover (138) to be described later. Through this, the compressed refrigerant discharged through the discharge hole (139) can move toward the discharge pipe (104) of the upper shell (102) by passing sequentially through the second communication hole (142) of the fixed scroll (130) and the first communication hole (1241) of the main frame (121) from the muffler space (1381) of the discharge cover (138).

[0210] A plurality of second oil grooves (1321) may be formed on the outer surface of the fixed side wall portion (132). The second oil grooves (1321) may be formed to penetrate the fixed side wall portion (132) in the axial direction. The second oil grooves (1321) may be formed in the shape of semicircular grooves. The second oil grooves (1321) may be formed to be recessed radially toward the center of the fixed end plate portion (131).

[0211] A plurality of second oil grooves (1321) may be arranged circumferentially spaced apart along the outer surface of the fixed side wall (132).

[0212] Through this, the second oil groove (1321) can serve as a passage to move oil in the internal space of the casing (100) to the lower space (1031) of the casing (100).

[0213] The fixed wrap (135) may protrude axially toward the pivot scroll (126) from the upper surface of the fixed plate portion (131). The fixed wrap (135) may extend along a spiral direction toward the center of the fixed plate portion (131) from one side of the inner circumference of the fixed side wall portion (132).

[0214] The fixed wrap (135) can be coupled with the pivot wrap (128) to form a compression chamber. A first compression chamber (1281) may be formed between the inner surface of the fixed wrap (135) and the outer surface of the pivot wrap (128), and a second compression chamber (1282) may be formed between the outer surface of the fixed wrap (135) and the inner surface of the pivot wrap (128).

[0215] Since the fixed wrap (135) is formed to correspond to the shape of the aforementioned rotating wrap (128), a redundant description is omitted.

[0216] The discharge cover (138) can be attached to the back surface of the fixed scroll (130). Here, the back surface of the fixed scroll (130) refers to the lower surface of the fixed scroll (130) based on FIG. 1.

[0217] A muffler space (1381) is provided inside the discharge cover (138). The muffler space (1381) can be connected to a discharge hole (139) that penetrates the fixed scroll (130).

[0218] Accordingly, the refrigerant discharged from the compression chamber through the discharge hole (139) passes through the muffler space (1381) and moves to the upper space (1021) of the casing (100) through the second communication hole (142) and the first communication hole (1241) described above.

[0219] The discharge cover (138) can be coupled to the fixed end plate (131) to surround the outer surface of the fixed bearing part (136). Through this, the discharge cover (138) can separate the oil moving to the lower space (1031) of the casing (100) through the second oil groove (1321) from the discharge gas discharged through the discharge hole (139).

[0220] (2) Bead (150) structure of the casing (100) according to one embodiment

[0221] FIG. 2 is a perspective view showing a bead (150) extending along the axial direction on the entire outer surface of the casing (100) in FIG. 1.

[0222] FIG. 3 is a cross-sectional view taken along III-III in FIG. 2, which is a conceptual diagram showing the bead (150) and the first oil groove (1123) arranged facing each other.

[0223] The casing (100) may include a bead (150). The bead (150) may be formed to protrude radially outward from the outer surface of the casing (100). The bead (150) may form a curved portion on the circumferential surface of the casing (100). The bead (150) has a thickness (153) corresponding to the thickness of the casing (100).

[0224] Here, "corresponding" means that the thickness (153) of the bead (150) and the thickness of the casing (100) are the same or similar to each other.

[0225] The bead (150) can be formed by press processing. Press processing is a metalworking method that involves using a press machine to cut or shape a metal sheet into a desired shape. In this embodiment, the bead (150) is formed by using a press machine to create a protruding or indented shape in a specific part of the metal sheet.

[0226] The bead (150) can be formed in a curved shape having the same or similar curvature as the outer surface (circular surface) of the casing (100).

[0227] The bead (150) includes a first curved surface (151) and a second curved surface (152). The first curved surface (151) of the bead (150) may be positioned toward the outside of the casing (100). The first curved surface (151) is formed to protrude radially outward from the outer surface of the casing (100). The first curved surface (151) may be formed with a first curvature corresponding to the outer surface of the casing (100).

[0228] The second curved surface (152) of the bead (150) may be positioned toward the inside of the casing (100). The first curved surface (151) and the second curved surface (152) of the bead (150) are positioned toward opposite directions in the radial direction. The second curved surface (152) is formed to be recessed radially outward on the inner circumference of the casing (100).

[0229] The second curved surface (152) may be formed with a second curvature corresponding to the inner circumference of the casing (100). The depth of the depression of the second curved surface (152) may be equal to or greater than the thickness of the casing (100). The protrusion length of the first curved surface (151) and the depth of the depression of the second curved surface (152) may be equal to each other.

[0230] The thickness (153) of the bead (150) is formed between the first curved surface (151) and the second curved surface (152) of the bead (150).

[0231] The beads (150) can be arranged in various patterns and shapes. The beads (150) can be extended in at least one of the axial and circumferential directions of the casing (100). The beads (150) can be formed in a multi-stage or multi-layered form. In this embodiment, they are shown extended along the axial direction of the casing (100).

[0232] The beads (150) may be provided in multiple numbers. The multiple beads (150) may be spaced apart at predetermined intervals along the circumferential direction of the casing (100). The spacing between the multiple beads (150) may vary.

[0233] Through this, the bead (150) can increase the rigidity of the casing (100). The bead (150) can form an oil passage on the inner surface of the casing (100) to increase the area of ​​the oil passage.

[0234] The casing (100) includes a cylindrical shell (101). The cylindrical shell (101) may be configured in a multi-stage form. Here, a multi-stage form may be defined as a form in which cylindrical parts of different diameters are connected to each other.

[0235] The cylindrical shell (101) may include a first cylindrical part (1011) to a Nth cylindrical part having different diameters. Here, N is a natural number. In this embodiment, the cylindrical shell (101) is shown configured to include a first cylindrical part (1011) and a second cylindrical part (1012).

[0236] The first cylindrical part (1011) is formed in a cylindrical shape having a first diameter. The first cylindrical part (1011) can be placed on the upper part of the cylindrical shell (101). A driving motor (110) can be accommodated inside the first cylindrical part (1011). The stator (111) of the driving motor (110) can be press-fitted to the inner circumference of the first cylindrical part (1011).

[0237] A first oil groove (1123) may be formed on the outer surface of the stator core (112). A plurality of first oil grooves (1123) may be provided. A plurality of first oil grooves (1123) may be spaced apart at equal intervals in the circumferential direction along the outer surface of the stator core (112). A D-cut may be formed in a portion of the outer surface of the stator core (112) so as to be recessed radially inward. The D-cut is named as such because it resembles the shape of the letter “D”.

[0238] The D-cut can form a first oil groove (1123). The first oil groove (1123) can be formed on the outer surface of the stator (111) to form a part of the first oil passage (1591).

[0239] The inner surface of the first cylinder (1011) is positioned to face the outer surface of the stator (111) in the radial direction.

[0240] The second cylindrical part (1012) is formed in a cylindrical shape having a second diameter. The second cylindrical part (1012) can be placed at the bottom of the cylindrical shell (101). A compression part (120) can be accommodated inside the second cylindrical part (1012). The main frame (121) and the fixed scroll (130) of the compression part (120) can be coupled to the inner circumference of the second cylindrical part (1012).

[0241] A second oil groove (1321) may be formed on the outer surface of the main side wall of the main frame (121) and the fixed side wall (132) of the fixed scroll (130), for example, of the compression part (120). The second oil groove (1321) may be provided in multiple numbers. Multiple second oil grooves (1321) may be arranged spaced apart in the circumferential direction along the outer surface of the compression part (120). The second oil groove (1321) may be formed on the outer surface of the compression part (120) so as to be recessed inward in the radial direction.

[0242] The second oil groove (1321) can be formed on the outer surface of the compression part (120) to form a part of the second oil passage (1592).

[0243] The inner surface of the second cylinder (1012) is positioned to face the outer surface of the compression section (120) in the radial direction.

[0244] The inclined portion (1013) is positioned between the first cylindrical portion (1011) and the second cylindrical portion (1012). The inclined portion (1013) is extended at an angle predetermined with respect to the axial direction. The inclined portion (1013) extends in the circumferential direction of the cylindrical shell (101).

[0245] One end of the inclined portion (1013) is connected to the first cylindrical portion (1011). The other end of the inclined portion (1013) is connected to the second cylindrical portion (1012). Through this, the inclined portion (1013) can smoothly connect the diameter difference between the first cylindrical portion (1011) and the second cylindrical portion (1012).

[0246] The bead (150) may be provided in at least one of the first cylinder (1011) and the second cylinder (1012). In this embodiment, the bead (150) is shown provided in the first cylinder (1011) and the second cylinder (1012).

[0247] The bead (150) extends in the axial direction. The bead (150) may be configured to have a first bead portion (154), a second bead portion (155), and a third bead portion (156). The first bead portion (154) may be positioned to face radially with the outer surface of the stator (111). The first bead portion (154) may be positioned to face radially with the first oil groove (1123) of the stator (111).

[0248] The first bead portion (154) has a predetermined circumferential width. The first bead portion (154) can be extended along the axial direction of the first cylinder portion (1011).

[0249] Through this, the first bead portion (154) is formed to be recessed radially outward from the inner circumference of the first cylinder portion (1011), thereby expanding the area of ​​the oil passage together with the first oil groove (1123).

[0250] The second bead portion (155) may be positioned on one side of the first bead portion (154). In this embodiment, the second bead portion (155) is shown extending upward from the top of the first bead portion (154). The second bead portion (155) may be connected to communicate with the upper space (1021) of the first cylinder portion (1011).

[0251] The second bead portion (155) has a predetermined circumferential width. The circumferential width of the second bead portion (155) may be greater than or equal to the circumferential width of the first bead portion (154).

[0252] This embodiment shows that the circumferential width of the second bead portion (155) is formed to be wider than the circumferential width of the first bead portion (154).

[0253] Through this, the second bead portion (155) can collect oil separated from the upper space (1021) of the first cylinder portion (1011) on the inner surface of the second bead portion (155) through a wider area.

[0254] A first inclined bead (157) may be formed between the first bead portion (154) and the second bead portion (155). At least one side of the first inclined bead (157) is formed to be inclined with respect to the axial direction to smoothly connect the difference in circumferential width between the first bead portion (154) and the second bead portion (155). In this embodiment, one side of the first inclined bead (157) is shown as being inclined.

[0255] Through this, the first inclined bead (157) can minimize the flow resistance of the oil.

[0256] Oil can move from the second bead section (155) to the first bead section (154). The area of ​​the first oil passage (1591) formed by the first oil groove (1123) is expanded by the addition of the first bead section (154), thereby securing a larger amount of oil recovery along the first oil passage (1591).

[0257] The oil flowing into the first bead portion (154) and the first oil groove (1123) can cool the heat generated in the stator (111) as it passes through the outer surface of the stator (111).

[0258] The third bead portion (156) may be positioned on the other side of the first bead portion (154). In this embodiment, the third bead portion (156) is shown extending downward along the axial direction of the inclined portion (1013) and the second cylindrical portion (1012) from the bottom of the first bead portion (154). The bottom portion of the third bead portion (156) may be connected to communicate with the lower space (1031) of the second cylindrical portion (1012).

[0259] The third bead portion (156) has a predetermined circumferential width. The circumferential width of the third bead portion (156) may be greater than or equal to the circumferential width of the first bead portion (154).

[0260] This embodiment shows that the circumferential width of the third bead portion (156) is formed to be wider than the circumferential width of the first bead portion (154). The circumferential width of the third bead portion (156) can be formed to correspond to the circumferential width of the second bead portion (155).

[0261] Through this, the third bead section (156) can recover the oil separated from the upper space (1021) of the first cylinder section (1011) through a wider area to the lower space (1031) of the second cylinder section (1012) through the inner surface of the third bead section (156).

[0262] A second inclined bead (158) may be formed between the first bead portion (154) and the third bead portion (156). At least one side of the second inclined bead (158) is formed to be inclined with respect to the axial direction to smoothly connect the difference in circumferential width between the first bead portion (154) and the third bead portion (156). In this embodiment, one side of the second inclined bead (158) is shown as being inclined.

[0263] Through this, the second inclined bead (158) can minimize the flow resistance of the oil.

[0264] Oil can move from the first bead section (154) to the third bead section (156). The area of ​​the second oil passage (1592) formed by the second oil groove (1321) is expanded by the addition of the third bead section (156), thereby securing a larger amount of oil recovery along the second oil passage (1592).

[0265] The axial lengths of the first bead section (154), the second bead section (155), and the third bead section (156) may differ from each other. For example, the axial length of the first bead section (154) is longer than the axial length of the second bead section (155). The axial length of the third bead section (156) is longer than the axial length of the first bead section (154).

[0266] Accordingly, according to the present invention, the bead (150) can increase the rigidity of the casing (100) to reduce noise. The bead (150) expands the oil passage so that the oil separated from the upper space (1021) of the casing (100) moves along the expanded oil passage to the lower space (1031) of the casing (100), thereby securing a larger amount of oil recovery.

[0267] (3) Bead (250) structure of the casing (100) according to another embodiment

[0268] FIG. 4 is a perspective view showing a bead (250) extending along the axial direction on the lower part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0269] FIG. 5 is a cross-sectional view taken along VV in FIG. 4, which is a conceptual diagram showing the bead (250) and the second oil groove (1321) arranged facing each other.

[0270] In this embodiment, the position of the bead (250) is different from the embodiment of FIGS. 1 to 3 described above.

[0271] In this embodiment, the bead (250) is shown provided on the outer surface of the second cylindrical part (1012). The bead (250) may be formed to protrude radially outward from the outer surface of the second cylindrical part (1012). The bead (250) may be formed to extend along the axial direction of the second cylindrical part (1012).

[0272] The beads (250) are provided in multiple numbers. The multiple beads (250) may be spaced apart along the circumferential direction of the second cylindrical part (1012). However, the beads (250) may not be formed in the first cylindrical part (1011).

[0273] Through this, the plurality of beads (250) can reduce the radiated noise of the compressor by increasing the rigidity of the casing (100). The plurality of beads (250) can expand the area of ​​the oil passage, thereby not only smoothly recovering oil into the oil storage space but also improving the reliability and efficiency of the compression section (120).

[0274] Other components are identical or similar to the embodiments of FIGS. 1 to 3 described above, so a redundant description will be omitted.

[0275] (4) Bead (350, 450) structure of casing (100) according to another embodiment

[0276] FIG. 6 is a perspective view showing a bead (350) extending along the circumferential direction on the lower part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0277] FIG. 7 is a conceptual diagram showing the casing (100) of FIG. 6 enclosing the parts of the compressor.

[0278] FIG. 8 is a perspective view showing a plurality of beads (350) extending along the circumferential direction on the lower part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0279] FIG. 9 is a conceptual diagram showing a plurality of beads (350) formed in the casing (100) in FIG. 8 wrapping the compression part (120) of the compressor and the oil storage space of the casing (100), respectively.

[0280] FIG. 10 is a perspective view showing a bead (450) extending along the circumferential direction and formed in a multi-stage shape on the lower part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0281] FIG. 11 is a conceptual diagram showing the bead (450) formed in the casing (100) in FIG. 10 surrounding the oil storage space.

[0282] In this embodiment, the shape and position of the bead (350) are different from the embodiments of FIGS. 1 to 5 described above.

[0283] In this embodiment, the bead (350) may extend along the circumferential direction of the second cylindrical part (1012). The bead (350) may be formed in the shape of a circular closed loop. The bead (350) may be named a circumferential bead (350) in that it is formed to extend along the circumferential direction.

[0284] The cylindrical beads (350) may be provided in multiple numbers. The multiple cylindrical beads (350) may be spaced apart in the axial direction of the second cylindrical part (1012). The cylindrical beads (350) may be configured by having a first cylindrical bead (351) and a second cylindrical bead (352).

[0285] The first cylindrical bead (351) can be arranged to wrap around the outer surface of the compression part (120).

[0286] Through this, the first cylindrical bead (351) not only reduces the radiated noise of the compressor by increasing the rigidity of the casing (100), but also secures a larger amount of oil recovery by expanding the area of ​​the oil passage.

[0287] The second cylindrical bead (352) may not overlap radially with the compression portion (120). The axial widths of the first cylindrical bead (351) and the second cylindrical bead (352) may differ from each other. In this embodiment, the axial width of the second cylindrical bead (352) may be greater than the axial width of the first cylindrical bead (351).

[0288] Through this, the second cylindrical bead (352) can increase the rigidity of the casing (100) and reduce the radiated noise of the compressor.

[0289] The cylindrical bead (450) can be formed in a multi-stage or multi-layered form.

[0290] The cylindrical bead (450) can be configured by having an inner bead portion (451) and an outer bead portion (452).

[0291] The inner bead portion (451) may be formed to protrude radially outward from the outer surface of the cylindrical shell (101). The inner bead portion (451) may be formed to protrude radially outward from the outer surface of the second cylindrical portion (1012).

[0292] The inner bead portion (451) may extend in the circumferential direction of the cylindrical shell (101). The inner bead portion (451) may extend along the circumferential direction of the second cylindrical portion (1012). The inner bead portion (451) may have a first axial width. Here, the axial width refers to the distance between the top and bottom of the inner bead portion (451) when a virtual axial straight line passing through the inner bead portion (451) along the axial direction is drawn.

[0293] The outer bead portion (452) may be formed to protrude radially outward from the outer surface of the inner bead portion (451). The outer bead portion (452) may extend along the circumferential direction of the inner bead portion (451). The outer bead portion (452) may have a second axial width that is narrower than the first axial width.

[0294] Through this, the inner bead portion (451) and the outer bead portion (452) can increase the rigidity of the casing (100) and reduce the radiated noise of the compressor.

[0295] Other components are identical or similar to the embodiments of FIGS. 1 to 5 described above, so a redundant description will be omitted.

[0296] (5) Bead (550, 551, 560) structure of casing (100) according to another embodiment

[0297] FIG. 12 is a perspective view showing beads (550, 560) extending along the axial and circumferential directions on the outer surface of a casing (100) according to another embodiment of the present invention.

[0298] FIG. 13 is a conceptual diagram showing the casing (100) of FIG. 12 enclosing the parts of the compressor.

[0299] FIG. 14 is a perspective view showing beads (551, 560) extending along the axial and circumferential directions on the lower part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0300] This embodiment differs from the embodiments of FIGS. 1 to 11 described above in that the shape of the beads (550, 551, 560) is provided in a combined form of axial beads (550, 551) and circumferential beads (560).

[0301] In this embodiment, the beads (550, 551, 560) may be configured to include axial beads (550, 551) and circumferential beads (560). The axial beads (550, 551) may be formed to protrude radially outward from the outer surface of the cylindrical shell (101). The axial beads (550, 551) may extend along the axial direction of the cylindrical shell (101).

[0302] The axial bead (550, 551) may be provided in at least one of the first cylindrical portion (1011), the inclined portion (1013), and the second cylindrical portion (1012). According to the embodiment of FIGS. 12 and 13, the axial bead (550) is shown as being continuously extended along the axial direction in the first cylindrical portion (1011), the inclined portion (1013), and the second cylindrical portion (1012).

[0303] Through this, the axial bead (550) can secure a larger amount of oil recovery by increasing the area of ​​the first oil passage (1591) formed between the inner surface of the first cylinder (1011) and the outer surface of the drive motor (110).

[0304] According to the embodiment of FIG. 14, the axial bead (551) is shown extending along the axial direction in the second cylinder (1012).

[0305] Axial beads (550, 551) may be provided in multiple numbers. Multiple axial beads (550, 551) may be spaced apart along the circumferential direction of the cylindrical shell (101). Multiple axial beads (350) may be spaced apart along the circumferential direction of the second cylindrical part (1012).

[0306] The circumferential bead (560) may be formed to protrude radially outward from the outer surface of the cylindrical shell (101). The circumferential bead (560) may extend along the circumferential direction of the cylindrical shell (101). The circumferential bead (560) may be provided in any one of the first cylindrical part (1011), the inclined part (1013), and the second cylindrical part (1012).

[0307] In this embodiment, the circumferential bead (560) is shown being provided in the second cylinder part (1012).

[0308] The circumferential beads (560) may be provided in multiple numbers. The multiple circumferential beads (560) may be spaced apart along the axial direction of the cylindrical shell (101). The multiple circumferential beads (560) may be spaced apart along the axial direction of the second cylindrical part (1012).

[0309] The circumferential bead (560) may be placed between two axial beads (550, 551) adjacent in the circumferential direction of the cylindrical shell (101). The circumferential bead (560) may be placed between two axial beads (550, 551) adjacent in the circumferential direction of the second cylindrical part (1012).

[0310] Through this, the circumferential bead (560) can connect two axial beads (550, 551) that are spaced apart in the circumferential direction.

[0311] The circumferential bead (560) can further increase the rigidity of the casing (100) and further reduce the radiated noise of the compressor.

[0312] (6) Bead (650) structure of the casing (100) according to another embodiment

[0313] FIG. 15 is a perspective view showing a bead (650) extending along the axial direction on the upper part of the outer surface of a casing (100) according to another embodiment of the present invention.

[0314] FIG. 16 is a cross-sectional view taken along XVI-XVI in FIG. 15, and is a conceptual diagram showing the cross-sectional shape of the axial bead (650).

[0315] In this embodiment, the shape of the bead (650) is different from the embodiments of FIGS. 1 to 14 described above.

[0316] In this embodiment, the bead (650) may extend along the axial direction of the cylindrical shell (101). Here, the bead (650) may be named an axial bead (650) in that it extends along the axial direction.

[0317] The axial bead (650) may be formed to protrude radially outward from the outer surface of the cylindrical shell (101). The axial bead (650) may be formed to protrude radially outward from the outer surface of the first cylindrical part (1011).

[0318] The axial bead (650) has a constant circumferential width along the axial direction of the cylindrical shell (101).

[0319] The axial beads (650) may be provided in multiple numbers. The multiple axial beads (650) may be spaced apart at equal intervals in the circumferential direction of the cylindrical shell (101).

[0320] The cross-sectional shape of the axial bead (650) can be formed in various shapes, such as a triangle, a square, a trapezoid, a sector, or an arc. In this embodiment, the cross-sectional shape of the axial bead (650) is shown as being formed in a trapezoidal shape.

[0321] In this embodiment, when looking at the cross-sectional shape of the axial bead (650), the axial bead (650) may include a first tapered portion (651), a second tapered portion (652), and a connecting portion (653). Here, the cross-sectional shape is the view of the axial bead (650) from above when the cylindrical shell (101) is cut radially.

[0322] The first tapered portion (651) may be positioned to the left of the axial bead (650) with respect to a radial centerline passing radially through the center of the cylindrical shell (101) and the center of the axial bead (650). The first tapered portion (651) may be formed to be inclined upward toward the radial centerline along a clockwise direction.

[0323] The outer surface of the first tapered portion (651) may be formed to be inclined in a direction that moves away from the outer circumference of the cylindrical shell (101) toward the radial centerline. The inner surface of the first tapered portion (651) may be formed to be inclined in a direction that moves away from the inner circumference of the cylindrical shell (101) toward the radial centerline.

[0324] The second tapered portion (652) may be positioned to the right of the axial bead (650) with respect to the radial centerline. The second tapered portion (652) may be formed to slope downward from the radial centerline along the clockwise direction.

[0325] The outer surface of the second tapered portion (652) may be formed to be inclined in a direction that moves away from the outer circumference of the cylindrical shell (101) toward the radial centerline. The inner surface of the second tapered portion (652) may be formed to be inclined in a direction that moves away from the inner circumference of the cylindrical shell (101) toward the radial centerline.

[0326] The connecting portion (653) is configured to connect the first tapered portion (651) and the second tapered portion (652). The connecting portion (653) may be formed in a curved or flat shape. In this embodiment, the connecting portion (653) is shown formed in a flat shape.

[0327] The axial bead (650) can be formed symmetrically with respect to the radial centerline.

[0328] The axial bead (650) can form a first oil passage (1591) together with a first oil groove (1123) formed on the outer surface of the stator (111) of the drive motor (110).

[0329] The maximum depth of the axial bead (650) can be formed to be equal to or greater than the thickness of the cylindrical shell (101).

[0330] Through this, the axial bead (650) can expand the area of ​​the oil passage on the inner surface of the cylindrical shell (101).

[0331] Other components are identical or similar to the embodiments of FIGS. 1 to 14 described above, so a redundant description will be omitted.

[0332] FIG. 17 is a conceptual diagram for comparing and explaining the area of ​​the oil passage according to the depression depth (D1: 3mm, D2: 5mm) of the bead (650) of the comparative example and the present invention.

[0333] FIG. 18 is a graph showing the magnitude of radiated noise between the parts and the casing (100) according to frequency during the operation of the compressor.

[0334] In the compressor according to the comparative example shown in Fig. 17, a bead (650) is not formed on the outer surface of the cylindrical shell (101), so the area of ​​the oil passage is relatively small.

[0335] The compressor according to the present invention further comprises a bead (650) formed to protrude radially outward from the outer surface of the cylindrical shell (101).

[0336] Referring to FIG. 17, when the maximum depression depth (D1) of the bead (650) is 3 mm, the cross-sectional area of ​​the oil passage according to the present invention is increased to 140% compared to the cross-sectional area of ​​the oil passage according to the comparative example.

[0337] In addition, when the maximum depression depth (D2) of the bead (650) is 5 mm, the cross-sectional area of ​​the oil passage according to the present invention is increased to 210% compared to the cross-sectional area of ​​the oil passage according to the comparative example.

[0338] In this embodiment, the bead (650) is formed selectively only where necessary for noise reduction, that is, in the high resonance frequency region between the component and the cylindrical shell (101), based on the analysis of the resonance frequency region between the component and the cylindrical shell (101).

[0339] In this embodiment, the magnitude of the radiated noise according to the frequency of the compressor was measured and analyzed, and it was confirmed that the noise was reduced by 2 dB.

[0340] In this embodiment, the frequency range of the compressor with the largest noise level was selected as the main target frequency range. The main target frequency range is 3200~4200 Hz.

Claims

1. A casing forming the exterior of the compressor; A drive motor provided inside the above casing; A compression unit disposed on one side of the above-mentioned drive motor and discharging compressed refrigerant into the internal space of the casing; A rotating shaft that transmits rotational force from the above-mentioned drive motor to the above-mentioned compression unit; and A bead formed to protrude radially outward from the outer surface of the casing, comprising Scroll compressor.

2. In Paragraph 1, The above casing is formed in a cylindrical shape, and The above bead extends along the circumferential or longitudinal direction of the casing, and The above beads are provided in multiple numbers, and A plurality of the above beads are spaced apart in the circumferential or longitudinal direction of the casing, Scroll compressor.

3. In Paragraph 1 or 2, The above bead is, A first curved surface protruding radially outward from the outer circumference of the above casing; and It includes a second curved surface that is recessed outwardly in the radial direction from the inner circumference of the casing and faces in a direction opposite to the first curved surface in the radial direction, The thickness of the bead is formed between the first curved surface and the second curved surface, and The thickness of the casing is formed between the outer surface and the inner surface of the casing, and The thickness of the above bead corresponds to the thickness of the above casing, Scroll compressor.

4. In any one of paragraphs 1 through 3, The maximum radial depth of the bead that is recessed outwardly in the radial direction from the inner circumference of the casing is greater than or equal to the thickness of the casing. Scroll compressor.

5. In any one of paragraphs 1 through 4, The above casing is, Cylindrical shell formed in a cylindrical shape; An upper shell covering the upper part of the above-mentioned cylindrical shell; and It includes a lower shell covering the lower part of the above-mentioned cylindrical shell, and The above bead is formed to protrude radially outward from the outer surface of the cylindrical shell. Scroll compressor.

6. In Paragraph 5, The above rotation axis extends in the vertical direction, and The above cylindrical shell extends parallel to the axial direction of the rotation axis, and The above bead extends in the axial direction or in the circumferential direction of the cylindrical shell, or extends in both the axial direction and the circumferential direction. Scroll compressor.

7. In Paragraph 5 or 6, The above cylindrical shell is, A first cylindrical part having a first diameter that accommodates the above-mentioned drive motor; A second cylindrical part that accommodates the above compression part, has a second diameter larger than the first diameter, and extends along the axial direction from the lower side of the first cylindrical part; and It includes an inclined portion formed at an angle to connect the first cylindrical portion and the second cylindrical portion, and The above bead is provided in at least one of the first cylindrical part, the second cylindrical part and the inclined part, Scroll compressor.

8. In any one of paragraphs 1 through 7, The above drive motor is, A stator coupled to the inner circumference of the above casing; A rotor rotatably disposed with an air gap inside the stator; and It includes a first oil groove formed to penetrate axially on the outer surface of the above stator, and The above bead is positioned to face the above first oil groove in the radial direction, Scroll compressor.

9. In any one of paragraphs 1 through 8, The above compression unit is, A pivot scroll coupled to the above rotation axis; and It includes a fixed scroll that is coupled to engage with the above-mentioned rotary scroll and forms a compression chamber together with the above-mentioned rotary scroll, and It includes a second oil groove formed to penetrate axially on the outer surface of the above fixed scroll, and The above bead is positioned to face the above second oil groove in the radial direction, Scroll compressor.

10. In any one of paragraphs 1 through 9, The above compression unit is positioned below the drive motor, Scroll compressor.

11. In any one of paragraphs 1 through 10, A first oil groove formed between the inner surface of the casing and the outer surface of the drive motor; and It further includes a second oil groove formed between the inner surface of the casing and the outer surface of the compression part, and The above bead extends along the axial direction to connect the first oil groove and the second oil groove, Scroll compressor.

12. In any one of paragraphs 7 through 11, The above bead extends in the axial direction, and The above bead is, A first bead portion provided on one side of the first cylindrical portion and arranged to face the outer surface of the drive motor; A second bead portion extending axially from one side of the first bead portion toward one end of the first cylindrical portion; and It includes a third bead portion extending in the opposite direction to the second bead portion along the axial direction of the second cylindrical portion with the first bead portion in between, The circumferential width of the second bead portion or the third bead portion is, Larger than or equal to the circumferential width of the first bead portion, Scroll compressor. Scroll compressor.

13. In any one of paragraphs 7 through 11, The above beads are formed in a multi-stage shape, and The above bead is, An inner bead portion protruding radially outward from the outer surface of the above casing; and A further comprising an outer bead portion protruding further radially outward from the outer surface of the inner bead portion, Scroll compressor.

14. In any one of paragraphs 1 through 13, The cross-sectional shape of the above bead is formed in a shape that is a combination of one or more of a triangle, a square, a trapezoid, or an arc. Scroll compressor.

15. In any one of paragraphs 1 through 14, The above casing is formed in a cylindrical shape, and When the above casing is cut radially, the bead is, A first tapered portion formed at an angle extending away from the outer surface of the casing in a radially outward direction; A second tapered portion arranged spaced apart from the first tapered portion along the circumferential direction and formed to be inclined in a direction moving away from the outer surface of the casing in the radial direction; It includes a connecting portion connecting the first tapered portion and the second tapered portion adjacent in the circumferential direction, and The first tapered portion and the second tapered portion are symmetrical with respect to a radial centerline passing radially through the center of the casing and the center of the bead. Scroll compressor.

Images