Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a non-orbiting scroll and an orbiting scroll which are coupled to be engaged with each other so as to form a compression chamber. The non-orbiting scroll has a plurality of back pressure holes. At least one of the plurality of back pressure holes allows communication between the back pressure chamber and the compression chamber not only during the orbital motion of the orbiting scroll, but also during initial startup or shutdown. Therefore, the plurality of back pressure holes transfer a refrigerant from the compression chamber to the back pressure chamber at all times, and move the non-orbiting scroll toward the orbiting scroll by means of back pressure such that leakage of the refrigerant between the compression chambers can be blocked.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor capable of reducing the number of parts and saving material costs.

[0002] Scroll compressors can be classified into low-pressure and high-pressure types depending on the path through which the refrigerant is sucked.

[0003] The low-pressure type is a method in which low-temperature suction refrigerant is introduced into the internal space of the casing through a refrigerant suction pipe connected to the internal space of the casing, and is guided to the suction pressure chamber after passing through the internal space of the casing.

[0004] The high-pressure type is a method in which the refrigerant suction pipe is directly connected to the suction pressure chamber, so that the suction refrigerant is guided directly to the suction pressure chamber without passing through the internal space of the casing.

[0005] A scroll compressor comprises a non-orbiting scroll and an orbiting scroll. The orbiting scroll is engaged with the non-orbiting scroll and orbits the non-orbiting scroll. The orbiting scroll and the non-orbiting scroll form a pair of compression chambers.

[0006] The compression chamber is composed of a suction pressure chamber formed on the periphery, an intermediate pressure chamber formed continuously with the volume gradually decreasing toward the center from the suction pressure chamber, and a discharge pressure chamber connected to the center of the intermediate pressure chamber.

[0007] The refrigerant sucked into the suction pressure chamber (not shown) is compressed as it moves toward the intermediate pressure chamber and discharge pressure chamber (not shown) along the movement path of the compression chamber (V).

[0008] A scroll compressor may be provided with a back pressure chamber. The back pressure chamber may be communicated with the compression chamber through a back pressure hole. The back pressure hole may be formed to penetrate axially through the plate portion of the non-orbiting scroll.

[0009] The pressure of the refrigerant flowing into the back pressure chamber, i.e., the back pressure, moves the non-orbiting scroll toward the orbiting scroll, thereby sealing the space between the non-orbiting scroll and the orbiting scroll, thereby preventing leakage of the refrigerant between the compression chambers.

[0010] The back pressure chamber can apply back pressure appropriately through a single back pressure hole.

[0011] However, conventional scroll compressors may have a problem in which the orbiting wrap rotates backward due to pressure differences between compression chambers during initial startup or shutdown.

[0012] The above-mentioned back pressure hole may be blocked by the retreat (reverse rotation) of the rotating lap. This may result in the back pressure not being formed in the back pressure chamber, which may result in refrigerant leakage between the compression chambers.

[0013] Or, if the back pressure hole is blocked while the pressure in the back pressure chamber is excessively high, the non-orbiting scroll may be pressed toward the orbiting scroll by the excessive back pressure, causing orbital resistance of the orbiting scroll.

[0014] Figure 1 is a schematic diagram showing a plate spring (3) mounted on the inside of the rotary shaft coupling part (1) of the rotary scroll to prevent backward movement of the rotary wrap.

[0015] In order to prevent the orbiting wrap from retreating, a plate spring (3) is provided between the rotating shaft coupling portion (1) of the orbiting scroll and the eccentric portion (2a) of the rotating shaft (2). Spring support grooves (1a, 1b) are formed on both sides inside the rotating shaft coupling portion (1).

[0016] The plate spring (3) is curved in an arc shape to surround one side of the eccentric portion (2a) of the rotating shaft (2), and both ends of the plate spring (3) are supported by spring support grooves (1a, 1b). The elastic force of the plate spring (3) acts in the opposite direction to the direction in which the turning wrap recedes so that it unfolds into its original flat shape. Through this, the plate spring (3) can prevent the turning wrap from receding by using the elastic force.

[0017] However, the above-mentioned plate spring (3) has a problem in that it complicates the joint structure between the rotary scroll and the rotating shaft (2) and increases the material cost due to the addition of parts of the plate spring (3).

[0018] In addition, there is a problem that the rigidity of the rotating scroll is reduced when a spring support groove (1a, 1b) is formed inside the rotary shaft coupling part (1) to support the plate spring (3).

[0019] In addition, the support area of ​​the spring support home (1a, 1b) is narrow, and the elasticity of the plate spring (3) may be reduced due to repeated rotational motion of the rotation scroll.

[0020] The purpose of the present invention is to provide a scroll compressor having a structure capable of solving the above-described problems.

[0021] The first purpose is to provide a scroll compressor having a structure in which the back pressure hole can always be connected without blockage of the back pressure hole due to reverse rotation of the turning wrap during initial start-up or stop.

[0022] The second purpose is to provide a scroll compressor having a simple structure that can prevent a decrease in rigidity of an orbiting scroll due to the formation of a spring support groove without using a plate spring.

[0023] The third objective is to provide a scroll compressor with a structure that can reduce the number of parts and material costs.

[0024] As a result of intensive research, the inventors of the present invention have found that the first to third objectives of the present invention can be achieved by the following embodiments of the present invention.

[0025] In order to achieve the above-described object, the present invention comprises: a casing; a driving motor provided inside the casing; a main frame disposed on one side of the driving motor; a non-orbiting scroll supported on the main frame; an orbiting scroll connected to the driving motor through a rotational shaft, pivotally coupled to the non-orbiting scroll, and forming a compression chamber together with the non-orbiting scroll; and a back-pressure chamber assembly having a back-pressure chamber and disposed on one side of the non-orbiting scroll in a direction opposite to the orbiting scroll with respect to the non-orbiting scroll. A plurality of back-pressure holes may be formed in the non-orbiting scroll so as to communicate with the back-pressure chamber and the compression chamber.

[0026] According to one embodiment, the non-orbiting scroll includes a non-orbiting plate portion; and a non-orbiting wrap that protrudes axially from the non-orbiting plate portion toward the orbiting scroll, the orbiting scroll includes an orbiting plate portion; and an orbiting wrap that is engaged with the non-orbiting wrap and forms the compression chamber together with the non-orbiting wrap, and the plurality of back pressure holes are formed to penetrate the non-orbiting plate portion in the axial direction and can be arranged to be spaced apart from each other in the circumferential direction of the non-orbiting plate portion.

[0027] According to one embodiment, the compression chamber has a suction pressure chamber, an intermediate pressure chamber, and a discharge pressure chamber formed continuously from the outside of the non-orbiting scroll toward the center, and the back pressure hole can connect the intermediate pressure chamber and the back pressure chamber.

[0028] In one embodiment, the plurality of back pressure holes may have a spacing distance less than or equal to the thickness of the rotating wrap.

[0029] According to one embodiment, the maximum separation distance between the outermost portions of the two back pressure holes intersecting an imaginary center line radially passing through the centers of two adjacent back pressure holes among the plurality of back pressure holes may be greater than or equal to the thickness of the rotating wrap.

[0030] According to one embodiment, the plurality of back pressure holes may be spaced apart from each other in a range of 1° to 30° along the circumferential direction.

[0031] In another embodiment, the plurality of back pressure holes may have a spacing greater than the thickness of the rotating wrap.

[0032] According to another embodiment, the plurality of back pressure holes may be spaced apart from each other by an angle of 150° to 180° along the circumferential direction.

[0033] According to one embodiment, a discharge port may be formed at the radial center of the non-orbiting scroll. The plurality of back pressure holes may have different radial distances from the center of the discharge port.

[0034] According to one embodiment, the compression chamber may include a first compression chamber formed between the outer circumference of the orbiting wrap and the inner circumference of the non-orbiting wrap based on the orbiting wrap; and a second compression chamber formed between the inner circumference of the orbiting wrap and the outer circumference of the non-orbiting wrap. One of the plurality of back pressure holes may be communicated with the first compression chamber, and another of the plurality of back pressure holes may be communicated with the second compression chamber.

[0035] According to one embodiment, the casing may further include a refrigerant suction pipe formed in the casing so as to be in communication with the internal space of the casing. A suction port may be formed on one side of the non-orbiting scroll so as to be in communication with the internal space of the casing. A portion of the refrigerant sucked through the refrigerant suction pipe may pass through the internal space of the casing and be sucked into the compression chamber through the suction port.

[0036] According to an embodiment of the present invention, the following effects can be achieved.

[0037] First, the plurality of back pressure holes are spaced circumferentially at predetermined intervals from each other on the non-orbiting scroll, so that at least one of the plurality of back pressure holes is not blocked by the orbiting wrap and can be opened to communicate with the back pressure chamber not only during the orbiting motion of the orbiting scroll but also during initial startup or stop. Here, the opening of the back pressure hole means that a part or the entire area of ​​the back pressure hole is opened.

[0038] Accordingly, the back pressure chamber can constantly receive refrigerant flowing from the intermediate pressure chamber through the back pressure hole to form a back pressure equal to the intermediate pressure. In addition, the non-orbiting scroll can receive back pressure from the back pressure chamber and move toward the orbiting scroll.

[0039] Through this, the non-orbiting scroll and the orbiting scroll can be brought into close contact with each other, thereby sealing the space between the non-orbiting scroll and the orbiting scroll. In addition, leakage of refrigerant between the first compression chamber and the second compression chamber can be prevented.

[0040] Second, since at least one of the plurality of back pressure holes always connects the compression chamber and the back pressure chamber, the back pressure hole does not become completely blocked even if the rotary wrap rotates in reverse due to the pressure difference in the compression chamber, so there is no need to install a plate spring between the rotary shaft coupling portion and the eccentric portion of the rotary shaft.

[0041] Due to this, there is no need to add parts such as the above-mentioned leaf spring, so the number of parts can be reduced and the material cost of the leaf spring, etc. can be reduced.

[0042] Third, the problem of the joint structure of the rotary scroll and the rotating shaft becoming complicated due to the addition of the above-mentioned plate spring can be resolved.

[0043] Fourth, since there is no need to form a spring support groove to support the above-mentioned plate spring in the rotary shaft joint, the problem of reduced rigidity of the rotating scroll can be resolved.

[0044] Figure 1 is a schematic diagram showing a plate spring mounted on the inside of a rotating joint of a rotating scroll to prevent backward movement of the rotating lap.

[0045] FIG. 2 is a conceptual diagram showing a cross-section of a scroll compressor according to one embodiment of the present invention.

[0046] Figure 3 is a conceptual diagram showing a non-rotating scroll having multiple pressure relief holes, enlarged from III in Figure 2.

[0047] Figure 4 is a conceptual diagram showing the spaced structure of a plurality of pressure relief holes formed in the non-rotating scroll in Figure 3, as viewed from the bottom.

[0048] Figure 5 is a conceptual diagram showing a portion of a plurality of pressure holes in Figure 4 covered by a rotating wrap.

[0049] Figure 6 is a conceptual diagram showing a partially enlarged cross-section of a scroll compressor according to another embodiment of the present invention.

[0050] Figure 7 is a conceptual diagram showing the spacing structure of multiple pressure relief holes formed in the non-rotating scroll in Figure 6, as viewed from the bottom.

[0051] Figure 8 is a graph showing the state of communication / blockage of the back pressure hole according to the crank angle during the rotational movement of the rotating scroll according to the present invention.

[0052] Hereinafter, a scroll compressor according to an embodiment of the present invention will be described in detail with reference to the attached drawings.

[0053] In the following description, descriptions of some components may be omitted to clarify the features of the present invention.

[0054] 1. Definition of Terms

[0055] Terms that include ordinal numbers, such as first, second, etc., may be used to describe various components, but the components are not limited by these terms. These terms are used solely to distinguish one component from another.

[0056] When a component is referred to as being "connected" or "connected" to another component, it should be understood that it may be directly connected or connected to that other component, but that there may be other components intervening. Conversely, when a component is referred to as being "directly connected" or "connected" to another component, it should be understood that there are no other components intervening.

[0057] As used herein, singular expressions include plural expressions unless the context clearly indicates otherwise.

[0058] As used herein, “radial” or “radial” means a shape that extends out in all directions from a central point like spokes of a wheel.

[0059] “Axial” as used in the following description means the longitudinal direction of the axis of rotation.

[0060] As used in the following description, “radial direction” means the longitudinal direction of a line segment from the center of a circle or cylinder to a point on the circumference (circumference).

[0061] As used in the following description, “circumferential” means the direction of the circumference of a circle.

[0062] 2. Description of the configuration of a scroll compressor according to one embodiment of the present invention

[0063] FIG. 2 is a conceptual diagram showing a cross-section of a scroll compressor according to one embodiment of the present invention.

[0064] Hereinafter, each configuration of a scroll compressor according to an embodiment of the present invention will be described with reference to the attached drawings.

[0065] (1) Components of a scroll compressor

[0066] A scroll compressor according to the present invention includes a casing (100). The casing (100) forms the exterior or outer periphery of the compressor. An accommodation space is provided within the casing (100) to accommodate components constituting the compressor.

[0067] A drive motor (110) is installed inside the casing (100). The drive motor (110) constitutes an electric part. A compression part is installed on the upper side of the drive motor (110).

[0068] The electric motor is coupled to one end of the rotary shaft (117). The compression motor is coupled to the other end of the rotary shaft (117). Through this, the compression motor is connected to the electric motor via the rotary shaft (117) and can operate by receiving rotational power from the electric motor.

[0069] The casing (100) includes a cylindrical shell (101), a cover (103), and a base (107).

[0070] The cylindrical shell (101) may be formed in a cylindrical shape. Both ends of the cylindrical shell (101) may be opened in the vertical direction. A driving motor (110) and a main frame (120) may be inserted and fixed to the inner surface of the cylindrical shell (101).

[0071] A terminal bracket can be attached to the upper portion of the cylindrical shell (101). A terminal can be connected through the terminal bracket. The terminal is configured to apply external power to the driving motor (110).

[0072] A refrigerant suction pipe (102) may be connected to the upper side of the cylindrical shell (101) so as to penetrate therethrough. The inner end of the refrigerant suction pipe (102) may be connected to the receiving space of the casing (100) so as to be in communication with it. The outer end of the refrigerant suction pipe (102) may be connected to the evaporator. The refrigerant suction pipe (102) may be positioned higher than the driving motor (110).

[0073] The cover (103) is coupled to cover the upper part of the cylindrical shell (101). A high-low pressure separator plate (104) may be provided between the cylindrical shell (101) and the cover (103). The high-low pressure separator plate (104) is configured to divide the receiving space of the casing (100) into a high-pressure section (105) and a low-pressure section (106). The high-pressure section (105) is arranged on the upper part of the fixed-pressure separator plate, and the low-pressure section (106) is arranged on the lower part of the high-low pressure separator plate (104).

[0074] A refrigerant discharge pipe (1031) is formed on one side of the cover (103) to communicate with the high pressure section (105).

[0075] The rim of the high-pressure separator (104) can be inserted between the cylindrical shell (101) and the cover (103) and joined to the inner surface of the cylindrical shell (101) and the cover (103) by welding. Through this, the upper space of the casing (100) is sealed to form an oil separation space.

[0076] The base (107) can be press-fitted to the lower end of the cylindrical shell (101). Through this, the lower space of the casing (100) is sealed to form an oil storage space.

[0077] The drive motor (110) is installed at the bottom of the low pressure section (106). The drive motor (110) includes a stator (111) and a rotor (114).

[0078] 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 press-fitted and joined to the inner surface of the cylindrical shell (101).

[0079] The stator coil (113) is wound around the stator core (112). 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).

[0080] 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 installed rotatably with a preset air gap inside the high-frequency magnetic core.

[0081] The permanent magnet (116) can be mounted embedded in the interior of the rotor core (115). The permanent magnets (116) are spaced apart at predetermined intervals along the circumference of the rotor core (115).

[0082] A rotating shaft (117) can be press-fitted and coupled to the center of the rotor core (115). An orbiting scroll (130), which will be described later, can be eccentrically coupled to the upper end of the rotating shaft (117). Through this, the rotational force of the driving motor (110) can be transmitted to the orbiting scroll (130) through the rotating shaft (117).

[0083] An eccentric portion (1171) is formed eccentrically at the top of the rotation shaft (117). The eccentric portion (1171) can be eccentrically connected to the rotation shaft connection portion (134) of the orbiting scroll (130).

[0084] Through this, the rotary scroll (130) can perform a rotary motion around the rotation axis (117).

[0085] The axial ends of the rotation shaft (117) may be supported by the main frame (120) and the subframe (108), which will be described later, respectively, with respect to the driving motor (110). The subframe (108) may be arranged on the lower side of the driving motor (110). The subframe (108) may be fixedly installed on the lower side of the inner surface of the cylindrical shell (101).

[0086] An oil pickup (118) may be installed at the bottom of the rotating shaft (117). The oil pickup (118) is positioned to be immersed in oil stored at the bottom of the casing (100). The oil pickup (118) is configured to suck up oil and move it to the top of the rotating shaft (117). An oil passage is formed to penetrate the interior of the rotating shaft (117) in the axial direction.

[0087] The compression section may include at least one of a main frame (120), a rotating scroll (130), a non-rotating scroll (140), and a back pressure chamber assembly (150).

[0088] The main frame (120) is fixedly installed on the inner surface of the cylindrical shell (101). The main frame (120) is placed on the upper side of the driving motor (110).

[0089] The main frame (120) may be configured to include at least one of a flange portion (121), a bearing portion (122), a rotation space portion (123), a scroll support portion (124), an old ring support portion (125), and a frame fixing portion (126).

[0090] The flange portion (121) may be formed in an annular shape. The flange portion (121) is accommodated in the low pressure portion (106) of the casing (100). The flange portion (121) extends radially. The outer diameter of the flange portion (121) may be smaller than the inner diameter of the cylindrical shell (101).

[0091] The frame fixing member (126) may be formed to protrude radially from the outer surface of the flange portion (121). The outer surface of the frame fixing member (126) may be fixed to the inner surface of the casing (100) in close contact with the inner surface. Through this, the main frame (120) may be fixed to the inner surface of the casing (100).

[0092] The bearing part (122) protrudes downward from the center bottom surface of the flange part (121) toward the driving motor (110). A cylindrical shaft through hole is formed axially through the inner surface of the bearing part (122). The rotating shaft (117) is press-fitted and coupled to the inner surface of the bearing part (122) through the shaft through hole. The rotating shaft (117) is rotatably supported by the bearing part (122).

[0093] The pivot space (123) is formed to be sunken from the center of the flange portion (121) toward the bearing portion (122). The pivot space (123) has a preset depth and diameter. The diameter of the pivot space (123) is formed to be larger than the outer diameter of the rotation shaft coupling portion (134) of the pivot scroll (130) described later.

[0094] Through this, the rotary shaft coupling part (134) can be rotatably accommodated inside the rotary space part (123).

[0095] The scroll support member (124) extends radially from the upper surface of the flange member (121). The scroll support member (124) is formed to protrude in an annular shape along the circumference of the pivot space member (123). Through this, the scroll support member (124) can axially support the lower surface of the pivot plate member (131) described later.

[0096] The Oldham ring support member (125) is formed in a ring shape along the outer circumference of the scroll support member (124) on the upper surface of the flange member (121). The Oldham ring (135) can be inserted into the Oldham ring support member (125) and rotatably accommodated.

[0097] The frame fixing member (126) is formed to protrude radially from the outer surface of the Oldham ring support member (125). The frame fixing member (126) may extend along the circumference or be formed to protrude radially. In the present embodiment, a plurality of frame fixing members (126) protrude radially, and the plurality of frame fixing members (126) are arranged to be spaced apart along the circumference of the Oldham ring support member (125).

[0098] The orbiting scroll (130) is coupled to the rotation shaft (117). The orbiting scroll (130) is arranged between the main frame (120) and the non-orbiting scroll (140). An anti-rotation mechanism, an Oldham ring (135), is provided between the main frame (120) and the orbiting scroll (130). Through this, the orbiting scroll (130) is restricted from rotating and can rotate relative to the non-orbiting scroll (140).

[0099] The orbiting scroll (130) can be configured to include a orbiting plate (131), a orbiting wrap (132), and a rotating shaft coupling (134).

[0100] The pivot plate (131) can be formed in a circular shape. The outer diameter of the pivot plate (131) is supported in the axial direction by being placed on the scroll support (124) of the frame. Through this, the mutual contact surface of the pivot plate (131) and the scroll support (124) can form an axial bearing surface.

[0101] The orbiting wrap (132) protrudes from the upper surface of the orbiting plate (131) toward the non-orbiting scroll (140) and may be formed in a spiral shape. The orbiting wrap (132) is configured to perform an orbiting motion by interlocking with the non-orbiting wrap (144) of the non-orbiting scroll (140) described later. The orbiting wrap (132) is formed to correspond to the non-orbiting wrap (144).

[0102] Through this, the rotating lap (132) can form a compression chamber (133) together with the non-rotating lap (144).

[0103] The compression chamber (133) may be composed of a first compression chamber (1331) and a second compression chamber (1332) based on the orbiting wrap (132). The first compression chamber (1331) and the second compression chamber (1332) may each be composed of a suction pressure chamber (133a), an intermediate pressure chamber (133b), and a discharge pressure chamber (133c). The suction pressure chamber (133a), the intermediate pressure chamber (133b), and the discharge pressure chamber (133c) are formed continuously from the outer periphery of the non-orbiting scroll (140) toward the center of the non-orbiting scroll (140).

[0104] The first compression chamber (1331) refers to a compression chamber (133) formed between the outer surface of the orbital wrap (132) and the inner surface of the non-orbital wrap (144) facing it.

[0105] The second compression chamber (1332) refers to a compression chamber (133) formed between the inner surface of the orbital wrap (132) and the outer surface of the non-orbital wrap (144) facing it.

[0106] The rotary shaft coupling portion (134) is formed to protrude from the lower surface of the pivot plate portion (131) toward the main frame (120). The rotary shaft coupling portion (134) may be formed in a cylindrical shape. A slewing bearing made of a bushing bearing may be press-fitted into the interior of the rotary shaft coupling portion (134).

[0107] The non-orbiting scroll (140) is placed on the upper part of the main frame (120) with the orbiting scroll (130) in between. The non-orbiting scroll (140) may be fixedly connected to the main frame (120) or may be connected so as to be movable in the vertical direction. In this embodiment, the non-orbiting scroll (140) is shown as being connected so as to be movable in the axial direction with respect to the main frame (120).

[0108] A non-orbiting scroll (140) is configured to include at least one of a non-orbiting plate portion (141), a non-orbiting wrap (144), a non-orbiting side wall portion (145), and a guide portion (146).

[0109] The non-rotating plate portion (141) can be formed in a circular shape. The non-rotating plate portion (141) is arranged transversely to the low pressure portion (106) of the casing (100). An outlet (142) is formed to penetrate axially through the central portion of the non-rotating plate portion (141).

[0110] The discharge port (142) is formed at a location where the discharge pressure chambers (133c) of the first and second compression chambers (1331, 1332) are connected to each other. The first and second compression chambers (1331, 1332) are formed on the inner and outer sides of the non-rotating wrap (144).

[0111] A plurality of back pressure holes (143) (hereinafter, first back pressure holes (143a, 143b)) are arranged radially apart from the discharge port (142). The first back pressure holes (143a, 143b) are formed to penetrate the non-rotating plate portion (141) in the axial direction.

[0112] The non-orbiting wrap (144) protrudes axially from the lower surface of the non-orbiting plate portion (141) toward the orbiting scroll (130) by a predetermined height. The non-orbiting wrap (144) extends around the discharge port (142) toward the non-orbiting side wall portion (145) in a spiral manner several times.

[0113] The non-rotating wrap (144) can be formed to correspond to the rotating wrap (132). The lengths of the non-rotating wrap (144) and the rotating wrap (132) can be the same. Through this, two pairs of compression chambers (133) can be formed between the non-rotating wrap (144) and the rotating wrap (132).

[0114] The back pressure hole (143) of the present invention can be applied to a symmetrical scroll compressor. Here, symmetrical means that the length and shape of the non-orbiting wrap (144) and the orbiting wrap (132) are the same.

[0115] The non-rotating side wall portion (145) protrudes axially from the lower edge of the non-rotating plate portion (141) to surround the non-rotating wrap (144). The non-rotating side wall portion (145) may be formed in an annular shape. An intake port (1451) is formed on one side of the outer circumferential surface of the non-rotating side wall portion (145).

[0116] The suction port (1451) is formed to penetrate axially toward the compression chamber (133) from one side of the non-rotating side wall (145) so as to connect the low pressure portion (106), which is the internal space of the casing (100), and the compression chamber (133).

[0117] The guide portion (146) may extend radially from the lower outer circumference of the non-rotating side wall portion (145). The guide portion (146) may be formed in a single ring shape or may be formed to protrude radially. In the present embodiment, the guide portion (146) is formed to protrude radially, and a plurality of guide portions (146) are arranged to be spaced apart from each other in the circumferential direction.

[0118] The back pressure chamber assembly (150) is arranged to face in the opposite direction to the orbiting scroll (130) with respect to the non-orbiting scroll (140). The back pressure chamber assembly (150) may be arranged above the non-orbiting scroll (140). Through this, the back pressure of the back pressure chamber (159) (more precisely, the force exerted by the back pressure on the back pressure chamber (159)) is applied to the non-orbiting scroll (140) in the form of back pressure.

[0119] In other words, the non-orbiting scroll (140) is pressurized toward the orbiting scroll (130) by the back pressure to seal the first compression chamber (1331) and the second compression chamber (1332).

[0120] Specifically, the back pressure chamber assembly (150) includes a back pressure plate (151) and a floating plate (158). The back pressure plate (151) is coupled to the upper surface of the non-rotating plate portion (141). The floating plate (158) is slidably coupled to the back pressure plate (151).

[0121] The floating plate (158) can form a back pressure chamber (159) together with the back pressure plate (151).

[0122] The back pressure plate (151) may be configured to include a fixed plate portion (152), a first annular wall portion (153), and a second annular wall portion (157). A second back pressure hole (1521a, 1521b) is formed to penetrate axially through the fixed plate portion (1522). The second back pressure hole (1521a, 1521b) is connected to a back pressure chamber (159).

[0123] The first back pressure hole (143a, 143b) and the second back pressure hole (1521a, 1521b) can be formed to overlap in the axial direction. Through this, the first back pressure hole (143a, 143b) and the second back pressure hole (1521a, 1521b) can communicate the compression chamber (133) and the back pressure chamber (159).

[0124] The first annular wall portion (153) protrudes axially from the upper surface of the fixed plate portion (152). The first annular wall portion (153) extends circumferentially along the inner perimeter of the fixed plate portion (152). The second annular wall portion (157) is arranged radially outer of the first annular wall portion (153).

[0125] The second annular wall portion (157) protrudes axially from the upper surface of the fixed plate portion (152). The second annular wall portion (157) extends circumferentially along the outer perimeter of the fixed plate portion (152).

[0126] The outer surface of the first annular wall portion (153), the inner surface of the second annular wall portion (157), the upper surface of the fixed plate portion (152), and the lower surface of the floating plate (158) can form a back pressure chamber (159). The back pressure chamber (159) can be formed in a ring shape.

[0127] An intermediate discharge port (154) is formed in the first annular wall portion (153). The intermediate discharge port (154) is connected to the discharge port (142) of the non-orbiting scroll (140). A valve guide groove may be formed inside the intermediate discharge port (154). A discharge valve (156) may be coupled to the valve guide groove so as to be able to slide up and down.

[0128] A backflow prevention hole (155) is formed in the center of the valve guide groove.

[0129] The discharge valve (156) can selectively open and close between the discharge port (142) and the intermediate discharge port (154). Through this, the refrigerant discharged from the discharge port (142) and the intermediate discharge port (154) can be prevented from flowing back into the compression chamber (133).

[0130] The floating plate (158) may be formed in an annular shape. The floating plate (158) may be formed of a material having a lower specific gravity than the back pressure plate (151). Through this, the floating plate (158) can move axially with respect to the back pressure plate (151) depending on the pressure in the back pressure chamber (159). The floating plate (158) may be in close contact with or spaced apart from the lower surface of the high-low pressure separation plate (104).

[0131] For example, when the floating plate (158) is in close contact with the high-low pressure separator (104), the discharged refrigerant can be discharged to the high-pressure section (105) without leaking to the low-pressure section (106). The floating plate (158) can serve to seal the back pressure chamber (159).

[0132] The operation of the scroll compressor is described as follows.

[0133] When power is applied to the stator coil (113) of the stator (111), the rotor (114) rotates together with the rotation axis (117) due to the electromagnetic interaction between the stator (111) and the rotor (114), for example, the interaction between the electric field generated in the stator coil (113) and the magnetic field of the permanent magnet (116).

[0134] An orbiting scroll (130) coupled to a rotating shaft (117) performs an orbiting motion with respect to a non-orbiting scroll (140). Two pairs of compression chambers (133) are formed between the orbiting wrap (132) and the non-orbiting wrap (144).

[0135] This compression chamber (133) gradually reduces in volume as it moves from the outside to the inside according to the rotational movement of the rotating scroll (130). At this time, the refrigerant is sucked into the low-pressure portion (106), which is the internal space of the casing (100), through the refrigerant suction pipe (102).

[0136] A portion of the above refrigerant passes through the low pressure portion (106) of the casing (100) and the suction port (1451) of the non-rotating scroll (140) and is directly sucked into each suction pressure chamber (133a) forming the first compression chamber (1331) and the second compression chamber (1332). Another portion of the above refrigerant moves toward the drive motor (110) and cools the drive motor (110) before being sucked into the suction pressure chamber (133a).

[0137] Next, the refrigerant sucked into the suction pressure chamber (133a) is compressed as it moves toward the intermediate pressure chamber (133b) and the discharge pressure chamber (133c) along the movement path of the compression chamber (133). The refrigerant moving to the discharge pressure chamber (133c) is discharged to the high pressure section (105) through the discharge port (142) and the intermediate discharge port (154) while pushing the discharge valve (156).

[0138] The above refrigerant fills the high pressure section (105) and then repeats a series of processes in which it is discharged through the condenser of the refrigeration cycle via the refrigerant discharge pipe (1031).

[0139] Additionally, another portion of the refrigerant compressed while passing through the intermediate pressure chamber (133b) may flow into the back pressure chamber (159) through the first back pressure holes (143a, 143b) and the second back pressure holes (1521a, 1521b) before reaching the discharge port (142). The back pressure chamber (159) into which the refrigerant flows from the intermediate pressure chamber (133b) may form an intermediate pressure.

[0140] Here, the intermediate pressure means an intermediate pressure that is greater than the pressure of the suction pressure chamber (133a) and less than the pressure of the discharge pressure chamber (133c).

[0141] Through this, the back pressure chamber (159) pressurizes the non-orbiting scroll (140) by the back pressure of the intermediate pressure and lowers it toward the orbiting scroll (130). The non-orbiting wrap (144) of the non-orbiting scroll (140) is in close contact with the orbiting plate (131) of the orbiting scroll (130), thereby sealing the space between the non-orbiting scroll (140) and the orbiting scroll (130), thereby preventing leakage of refrigerant between the first compression chamber (1331) and the second compression chamber (1332).

[0142] However, during initial startup or stop, the orbiting scroll (130) may rotate in reverse due to the pressure difference between the compression chambers (133). The orbiting wrap (132) of the orbiting scroll (130) is arranged to overlap the first back pressure hole (143a, 143b) in the axial direction, thereby blocking the first back pressure hole (143a, 143b).

[0143] 3. Description of the spacing structure of a plurality of pressure relief holes (143a, 143b) according to one embodiment of the present invention.

[0144] Figure 3 is a conceptual diagram showing a non-rotating scroll (140) equipped with multiple pressure relief holes (143a, 143b) by enlarging III in Figure 2.

[0145] Figure 4 is a conceptual diagram showing the spacing structure of a plurality of pressure relief holes (143a, 143b) formed in the non-rotating scroll (140) in Figure 3, as viewed from the bottom.

[0146] Figure 5 is a conceptual diagram showing a portion of a plurality of pressure holes (143a, 143b) in Figure 4 covered by a rotating wrap (132).

[0147] In order to solve the above-described problem in the present invention, a plurality of back pressure holes (143a, 143b) may be provided in the non-orbiting scroll (140). In the following description, unless otherwise specified, the back pressure holes (143a, 143b) will be understood as having the same concept as the first back pressure hole (143a, 143b) of the non-orbiting scroll (140) described above.

[0148] The back pressure holes (143a, 143b) are formed to penetrate axially through the non-orbiting plate portion (141) of the non-orbiting scroll (140). The back pressure holes (143a, 143b) are arranged radially outwardly from the discharge port (142) of the non-orbiting scroll (140). A plurality of back pressure holes (143a, 143b) are arranged to be spaced apart from each other.

[0149] A plurality of pressure relief holes (143a, 143b) can be connected to the first compression chamber (1331) and the second compression chamber (1332), respectively.

[0150] A plurality of back pressure holes (143a, 143b) may be arranged at predetermined intervals along the circumferential direction. The plurality of back pressure holes (143a, 143b) may have different radial distances from the center of the non-orbiting scroll (140).

[0151] In this embodiment, the distance between the plurality of back pressure holes (143a, 143b) may be smaller than or equal to the thickness of the rotating wrap (132). Here, the distance between the plurality of back pressure holes (143a, 143b) means the distance between the centers of two back pressure holes (143a, 143b) adjacent in the circumferential direction.

[0152] Alternatively, the maximum separation distance between the plurality of back pressure holes (143a, 143b) may be greater than or equal to the thickness of the turning wrap (132). Here, the maximum separation distance between the plurality of back pressure holes (143a, 143b) means the distance between the two points that are spaced apart the most among the plurality of points where an imaginary center line passing through the center of each of the two back pressure holes (143a, 143b) in the radial direction intersects the outermost circles of the two back pressure holes (143a, 143b).

[0153] In this embodiment, the circumferential spacing of the plurality of back pressure holes (143a, 143b) may range from 0.1° to 30°. The spacing between the plurality of back pressure holes (143a, 143b) may include 0.1° or 30°. If the spacing between the plurality of back pressure holes (143a, 143b) is outside the above numerical limitation range, a pressure disturbance may occur between the first compression chamber (1331) and the second compression chamber (1332).

[0154] Accordingly, according to the present invention, the plurality of back pressure holes (143a, 143b) have a structure in which they are spaced apart from each other in the circumferential direction at a preset interval on the non-orbiting scroll (140), so that at least one of the plurality of back pressure holes (143a, 143b) can be opened without being blocked by the orbiting wrap (132) and communicate with the back pressure chamber (159) not only during the orbiting movement of the orbiting scroll (130) but also during the initial start or stop. Here, the opening of the back pressure holes (143a, 143b) means that a part or the entire area of ​​the back pressure holes (143a, 143b) is opened.

[0155] Accordingly, the back pressure chamber (159) can constantly receive refrigerant flowing in from the intermediate pressure chamber (133b) through the back pressure holes (143a, 143b) to form a back pressure of the intermediate pressure level. In addition, the non-orbiting scroll (140) can receive back pressure from the back pressure chamber (159) and move toward the orbiting scroll (130).

[0156] Through this, the non-orbiting scroll (140) and the orbiting scroll (130) can be brought into close contact with each other, thereby sealing the space between the non-orbiting scroll (140) and the orbiting scroll (130). In addition, it is possible to prevent refrigerant from leaking between the first compression chamber (1331) and the second compression chamber (1332).

[0157] In addition, since at least one of the plurality of back pressure holes (143a, 143b) always connects the compression chamber (133) and the back pressure chamber (159), even if the rotary wrap (132) rotates in reverse due to the pressure difference in the compression chamber (133), the back pressure holes (143a, 143b) do not become completely blocked, and therefore, there is no need to install a plate spring between the rotary shaft coupling portion (134) and the eccentric portion (1171) of the rotary shaft (117).

[0158] Due to this, there is no need to add parts such as the above-mentioned leaf spring, so the number of parts can be reduced and the material cost of the leaf spring, etc. can be reduced.

[0159] In addition, the problem of the joint structure of the rotating scroll (130) and the rotating shaft (117) becoming complicated due to the addition of the above-mentioned plate spring can be resolved.

[0160] In addition, since there is no need to form a spring support groove to support the above-mentioned plate spring in the rotary shaft coupling portion (134), the problem of the rigidity of the rotating scroll (130) being reduced can be resolved.

[0161] 4. Description of the spacing structure of multiple pressure relief holes (243a, 243b) according to another embodiment of the present invention.

[0162] Figure 6 is a conceptual diagram showing a partially enlarged cross-section of a scroll compressor according to another embodiment of the present invention.

[0163] Figure 7 is a conceptual diagram showing the spacing structure of a plurality of pressure relief holes (243a, 243b) formed in the non-rotating scroll (240) in Figure 6, as viewed from the bottom.

[0164] The present embodiment differs from the embodiments of FIGS. 3 to 5 described above in the separation structure of the plurality of pressure holes (243a, 243b).

[0165] The back pressure holes (243a, 243b) are formed to penetrate axially through the non-orbiting plate portion of the non-orbiting scroll (240). The back pressure holes (243a, 243b) are arranged radially outwardly from the discharge port of the non-orbiting scroll (240). A plurality of back pressure holes (243a, 243b) are arranged to be spaced apart from each other.

[0166] A plurality of pressure relief holes (243a, 243b) can be connected to the first compression chamber (1331) and the second compression chamber (1332), respectively.

[0167] A plurality of back pressure holes (243a, 243b) may be arranged at predetermined intervals along the circumferential direction. The plurality of back pressure holes (243a, 243b) may have different radial distances from the center of the non-orbiting scroll (240).

[0168] In this embodiment, the distance between the plurality of pressure holes (243a, 243b) may be greater than the thickness of the turning wrap (132).

[0169] In the present embodiment, the circumferential spacing of the plurality of back pressure holes (243a, 243b) may be in the range of 150° to 180°. The spacing between the plurality of back pressure holes (243a, 243b) may include 150° or 180°. If the spacing between the plurality of back pressure holes (243a, 243b) is outside the above numerical limitation range, a pressure disturbance may occur between the first compression chamber (1331) and the second compression chamber (1332).

[0170] Figure 8 is a graph showing the state of communication / blockage of the pressure relief holes (143a, 143b, 243a, 243b) according to the crank angle during the rotational movement of the rotation scroll (130) according to the present invention.

[0171] In Fig. 8, path A represents the movement path of the first compression chamber (1331). Path B represents the movement path of the second compression chamber (1332).

[0172] The thick solid line shows the communication / blockage status of the back pressure hole (143a, 243a) of the A path according to the crank angle of the turning lap (132). The thin solid line shows the communication / blockage status of the back pressure hole (143b, 243b) of the B path according to the crank angle of the turning lap (132).

[0173] Among the plurality of back pressure holes (143a, 143b, 243a, 243b) according to the present invention, one back pressure hole (143a, 243a) may be connected to the first compression chamber (1331), and another back pressure hole (143b, 243b) among the plurality of back pressure holes (143a, 143b, 243a, 243b) may be connected to the second compression chamber (1332).

[0174] As illustrated in FIG. 8, at least one of the plurality of back pressure holes (143a, 143b, 243a, 243b) can communicate the compression chamber (1331, 1332) and the back pressure chamber (159) according to the crank angle (rotational movement) of the turning wrap (132).

[0175] In the section where the crank angle of the turning lap (132) is 0° to 145°, the back pressure holes (143a, 243a) of the A path connect the first compression chamber (1331) and the back pressure chamber (159), but the back pressure holes (143b, 243b) of the B path can block the second compression chamber (1332) and the back pressure chamber (159).

[0176] In the section where the crank angle of the turning lap (132) is 145° to 160°, the back pressure holes (143a, 243a) of the A path and the back pressure holes (143b, 243b) of the B path can connect the first and second compression chambers (1331, 1332) with the back pressure chamber (159), respectively.

[0177] In the section where the crank angle of the turning lap (132) is 160° to 360°, the back pressure holes (143a, 243a) of the A path block the first compression chamber (1331) and the back pressure chamber (159), but the back pressure holes (143b, 243b) of the B path can connect the second compression chamber (1332) and the back pressure chamber (159).

Claims

1. Casing; A driving motor provided inside the above casing; A main frame arranged on one side of the above driving motor; A non-rotating scroll supported on the above mainframe; A rotating scroll connected to the driving motor through a rotating shaft, pivotally coupled to the non-orbiting scroll, and forming a compression chamber together with the non-orbiting scroll; and It includes a back pressure chamber, and a back pressure chamber assembly disposed on one side of the non-orbiting scroll in the opposite direction to the orbiting scroll with respect to the non-orbiting scroll, A scroll compressor in which a plurality of back pressure holes are formed in the non-rotating scroll so as to be connected to the back pressure chamber and the compression chamber.

2. In paragraph 1, The above non-rotating scroll is, Non-rotating plate section; and Including a non-rotating wrap that protrudes axially toward the rotating scroll from the non-rotating plate portion, The above rotating scroll is, Swivel plate; and It includes a rotating wrap that is interlocked with the non-rotating wrap and forms the compression chamber together with the non-rotating wrap, A scroll compressor in which the plurality of back pressure holes are formed to penetrate the non-rotating plate section in the axial direction and are spaced apart from each other in the circumferential direction of the non-rotating plate section.

3. In paragraph 1, The above compression chamber has a suction pressure chamber, an intermediate pressure chamber, and a discharge pressure chamber formed continuously from the outside of the non-orbiting scroll toward the center, The above back pressure hole is a scroll compressor that connects the intermediate pressure chamber and the back pressure chamber.

4. In paragraph 2, A scroll compressor in which the plurality of back pressure holes have a spacing distance smaller than or equal to the thickness of the rotating wrap.

5. In paragraph 2, A scroll compressor in which the maximum separation distance between the outermost parts of the two backing holes and the imaginary center line passing radially through the centers of two adjacent backing holes among the plurality of backing holes is greater than or equal to the thickness of the orbital wrap.

6. In paragraph 1, A scroll compressor in which the plurality of pressure relief holes are spaced apart from each other in the circumferential direction by an angle of 1° to 30°.

7. In paragraph 2, A scroll compressor in which the plurality of back pressure holes have a spacing greater than the thickness of the rotating wrap.

8. In paragraph 1, A scroll compressor in which the plurality of pressure relief holes are spaced apart from each other by an angle of 150° to 180° along the circumferential direction.

9. In paragraph 1, A discharge port is formed at the radial center of the above non-rotating scroll, A scroll compressor in which the plurality of back pressure holes have different radial distances from the center of the discharge port.

10. In paragraph 2, The above compression chamber is, A first compression chamber formed between the outer surface of the above-mentioned turning wrap and the inner surface of the above-mentioned non-turning wrap based on the above-mentioned turning wrap; and It includes a second compression chamber formed between the inner surface of the above-mentioned rotating wrap and the outer surface of the above-mentioned non-rotating wrap, A scroll compressor, wherein one of the plurality of back pressure holes is communicated with the first compression chamber, and another of the plurality of back pressure holes is communicated with the second compression chamber.

11. In paragraph 1, Further comprising a refrigerant suction pipe formed in the casing so as to be connected to the internal space of the casing, A suction port is formed on one side of the above non-rotating scroll so as to be in communication with the internal space of the casing, A scroll compressor in which a portion of the refrigerant sucked through the refrigerant suction pipe passes through the internal space of the casing and is sucked into the compression chamber through the suction port.

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