Scroll compressor

Abstract

The present invention provides a scroll compressor which comprises: a casing in which an inner space is sealed; a motor unit provided with a stator fixed in the inner space and a rotor which rotates inside the stator; a rotary shaft rotatably coupled to the rotor; a main frame disposed at one side of the motor unit to be fixed in the inner space of the casing; an orbiting scroll coupled to the rotary shaft so as to move in an orbital motion and supported on the main frame in the axial direction; a non-orbiting scroll coupled to be engaged with the orbiting scroll to form a compression chamber and having a discharge port through which a refrigerant compressed in the compression chamber is discharged; a back pressure chamber assembly disposed on one side surface of the non-orbiting scroll in the axial direction and supporting the non-orbiting scroll in a direction going toward the orbiting scroll; and a discharge valve which slides to be inserted in the back chamber assembly to open and close the discharge port, wherein the side of the discharge valve adjacent to the discharge port has a greater diameter than the opposite side thereof.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having a structure that improves the performance of the scroll compressor by reducing discharge resistance by additionally securing a discharge area.

[0002] A scroll compressor is a combination of a rotating scroll and a non-rotating scroll that are interlocked and combined, and the rotating scroll rotates relative to the non-rotating scroll to form a pair of compression chambers.

[0003] The compression chamber is composed of a suction chamber formed on the periphery, an intermediate chamber formed continuously from the suction chamber with a gradually decreasing volume toward the center, and a discharge chamber extending toward the center of the intermediate chamber. Typically, the suction chamber is formed by penetrating the side of the non-orbiting scroll, the intermediate chamber is sealed, and the discharge chamber is formed by penetrating the plate portion of the non-orbiting scroll.

[0004] Scroll compressors can be categorized as low-pressure and high-pressure types, depending on the refrigerant suction path. In a low-pressure type, the refrigerant suction pipe is connected to the internal space of the casing, so that the low-temperature suction refrigerant passes through the internal space of the casing and is guided to the suction pressure chamber. In a high-pressure type, the refrigerant suction pipe is directly connected to the suction pressure chamber, so that the refrigerant is guided directly to the suction pressure chamber without passing through the internal space of the casing.

[0005] In a conventional low-pressure scroll compressor, the refrigerant is sucked in through a suction pipe, compressed in the compression chambers of the orbiting scroll and the fixed scroll, and then discharged through a discharge pipe via the discharge path of the fixed scroll and the discharge path of the back chamber plate. At this time, the check valve blocks the discharge path of the fixed scroll before the compressor starts to build up pressure in the compression chamber, and when the compressor starts and the pressure in the compression chamber increases, the check valve rises and discharges the refrigerant. Therefore, the diameter of the check valve is designed to be larger than the discharge path of the fixed scroll, and a guide is installed on the back chamber plate to enable the valve to move up and down.

[0006] Patent Document 1 (Patent Registration No. 10-2155604) discloses a scroll compressor that can smoothly discharge refrigerant while reducing the dead volume by reducing the length of the discharge port.

[0007] To ensure initial pressure buildup in the compression section, the check valve must be designed with a diameter larger than the discharge path of the fixed scroll. Accordingly, existing discharge valves are cylindrical in design, and the valve guide installed on the back chamber plate takes up a large portion of the discharge path, creating resistance during refrigerant discharge and hindering compressor performance.

[0008] In order to reduce discharge resistance, there is a need for a structure to improve the performance of the compressor by securing a discharge area or discharge path.

[0009] The present invention has been devised to solve the above problems, and one object of the present invention is to provide a scroll compressor capable of reducing flow resistance and improving performance by expanding a discharge flow path.

[0010] Another object of the present invention is to provide a scroll compressor having a structure in which the contact area between the check valve and the back chamber plate can be reduced.

[0011]

[0012] In order to solve the above problem, the scroll compressor of the present invention includes a casing having a sealed internal space; a driving unit having a stator fixed to the internal space and a rotor rotated within the stator; a rotating shaft rotatably coupled to the rotor; a main frame provided on one side of the driving unit and fixed to the internal space of the casing; an orbiting scroll coupled to the rotating shaft so as to be rotatable and axially supported by the main frame; a non-orbiting scroll coupled to the orbiting scroll so as to be engaged with the non-orbiting scroll to form a compression chamber and having a discharge port for discharging refrigerant compressed in the compression chamber; a back pressure chamber assembly provided on one axial side of the non-orbiting scroll and supporting the non-orbiting scroll in a direction toward the orbiting scroll; and a discharge valve slidably inserted into the back pressure chamber assembly to open and close the discharge port, wherein the discharge valve is formed such that a diameter of one side adjacent to the discharge port is larger than a diameter of the other side.

[0013] This allows the discharge path around the other side of the discharge valve to expand, reducing the flow resistance.

[0014] The discharge valve may include a large-diameter portion provided on one side to open and close the discharge port; and a small-diameter portion provided on the other side to be slidably inserted into the back pressure chamber assembly.

[0015] The discharge valve is formed by forming a structure including a large diameter portion and a small diameter portion, so that the contact area between the discharge valve and the back pressure chamber assembly is reduced, thereby improving the responsiveness of the discharge valve due to friction and oil viscosity.

[0016] The above pressure chamber assembly is provided with a valve guide groove that guides movement of the discharge valve, and the valve guide groove may have a jaw portion that restricts upward movement of the large diameter portion.

[0017] By providing a step portion in the valve guide groove, the movement of the discharge valve can be restricted while the valve guide groove guides the movement of the discharge valve, thereby reducing the contact area between the discharge valve and the back pressure chamber assembly, thereby improving the responsiveness of the discharge valve due to friction and oil viscosity.

[0018] For example, the pressure chamber assembly may be provided with an intermediate discharge port communicating with the discharge port, and the diameter of the intermediate discharge port may be provided to be larger than half the diameter of the small diameter portion and smaller than twice the diameter of the small diameter portion.

[0019] The above valve guide groove may be provided with a small diameter guide groove that guides the small diameter part to be inserted so as to slide.

[0020] Due to this, the large diameter and small diameter parts of the discharge valve can be stably guided without interference within the back pressure chamber assembly.

[0021] Preferably, the jaw portion may be provided at one end of the small diameter guide groove.

[0022] The above-mentioned large diameter portion may be provided with a refrigerant receiving groove formed concavely in the direction toward the small diameter portion at the bottom to receive a portion of the discharged refrigerant.

[0023] By means of the refrigerant receiving groove, when the discharge valve blocks the discharge port, some of the refrigerant near the discharge port can be received in the refrigerant receiving groove, thereby minimizing the possibility of leakage between the discharge valve and the discharge port.

[0024] The above-mentioned large diameter portion may be provided at the lower portion, around the refrigerant receiving groove, and may be provided with a contact portion formed to be in contact with the end of the discharge port so as to enable the discharge port to be closed.

[0025] The above-mentioned back pressure chamber assembly may be provided with a plurality of intermediate discharge ports communicating with the discharge port, and a partition wall of a predetermined width may be provided between the plurality of intermediate discharge ports.

[0026] For example, the pressure chamber assembly may include a fixed plate portion formed in an annular shape, a first annular wall portion forming an inner surface of the fixed plate portion, and a second annular wall portion forming an outer surface of the fixed plate portion, wherein the first annular wall portion may have the intermediate discharge port provided on the inner side thereof, and a valve guide groove may be provided to guide movement of the discharge valve toward the inner side of the intermediate discharge port.

[0027] The partition wall may include a portion having the same width along the radial direction. This allows the discharge path to be expanded relatively wide around the other side of the discharge valve.

[0028] An axial side of the non-rotating scroll facing the pressure chamber assembly may be provided with a discharge guide groove that is formed to be sunken to a preset depth and accommodate the discharge port, and the discharge guide groove may be provided with a valve seat groove that is formed to be sunken in a direction from the outlet end of the discharge port toward the discharge port so that one side of the discharge valve is inserted therein.

[0029] Due to this, a structure is formed in which the discharge valve is inserted into the valve seat groove, so that when the discharge valve blocks the discharge port, leakage of refrigerant between the discharge valve and the discharge port can be minimized.

[0030] The above valve seat groove may have a height equal to the axial width of one side of the discharge valve or a height smaller than the axial width of one side of the discharge valve.

[0031] This enables the discharge valve to be more stably inserted into the valve seat groove, and minimizes refrigerant leakage between the discharge valve and the discharge port when the discharge valve blocks the discharge port.

[0032] On one axial side of the non-rotating scroll facing the back pressure chamber assembly, a discharge guide groove is formed to be sunken to a preset depth and accommodate the discharge port, and on one axial side of the non-rotating scroll facing the back pressure chamber assembly, a valve seat protrusion may be provided that protrudes from the discharge guide groove in a direction toward the discharge valve from the outlet end of the discharge port to enable one side of the discharge valve to be seated.

[0033] As the discharge valve is seated on the valve seat protrusion, a structure can be formed in which the discharge valve can more stably block the discharge port.

[0034] Preferably, the valve seat protrusion may have a height equal to the axial width of one side of the discharge valve or a height smaller than the axial width of one side of the discharge valve.

[0035] The scroll compressor of the present invention is formed so that the diameter of one side of the discharge valve is larger than the diameter of the other side, so that the discharge path around the other side of the discharge valve can be expanded, and the flow path resistance is reduced.

[0036] The scroll compressor of the present invention forms a structure including a large diameter portion and a small diameter portion, so that the contact area between the discharge valve and the back pressure chamber assembly is reduced, thereby improving the responsiveness of the discharge valve due to friction and oil viscosity.

[0037] The scroll compressor of the present invention has a valve guide groove and a jaw portion provided in a back pressure chamber assembly so that the valve guide groove guides the movement of the discharge valve while restricting the movement of the discharge valve, thereby reducing the contact area between the discharge valve and the back pressure chamber assembly and improving the reduction in responsiveness of the discharge valve due to friction and oil viscosity.

[0038] The scroll compressor of the present invention forms a structure in which a discharge valve is inserted into a valve seat groove, so that when the discharge valve blocks the discharge port, leakage of refrigerant between the discharge valve and the discharge port can be minimized.

[0039] Fig. 1 is a cross-sectional view showing a scroll compressor of the present invention.

[0040] Figure 2 is an exploded perspective view showing the back pressure chamber assembly, discharge valve and non-rotating scroll.

[0041] Figure 3 is a cross-sectional view showing a pressure chamber assembly, a discharge valve, and a non-rotating scroll.

[0042] Figure 4 is a cross-sectional view showing the pressure chamber assembly and discharge valve.

[0043] Figure 5 is an exploded perspective view showing an example in which a discharge valve is coupled to a pressure chamber assembly.

[0044] Figure 6 is a plan view of the pressure chamber assembly viewed from above.

[0045] Figure 7 is a cross-sectional view showing an example in which a discharge valve opens a discharge port when discharging refrigerant.

[0046] Figure 8 is a cross-sectional view showing an example in which a discharge valve closes a discharge port before refrigerant discharge.

[0047] Fig. 9 is an exploded perspective view showing an example in which a valve seat protrusion is provided in a non-rotating scroll.

[0048] Fig. 10 is a cross-sectional view showing an example in which a valve seat protrusion is provided in a non-rotating scroll.

[0049]

[0050] Hereinafter, a scroll compressor (10) related to the present invention will be described in more detail with reference to the drawings.

[0051] In this specification, identical or similar reference numbers are assigned to identical or similar components in different embodiments, and redundant descriptions thereof are omitted.

[0052] Additionally, even if the embodiments are different, a structure applied to one embodiment can be applied to another embodiment as long as there is no structural or functional contradiction.

[0053] Singular expressions include plural expressions unless the context clearly indicates otherwise.

[0054] In describing the embodiments disclosed in this specification, if it is determined that a detailed description of a related known technology may obscure the gist of the embodiments disclosed in this specification, the detailed description is omitted.

[0055] The attached drawings are only intended to facilitate understanding of the embodiments disclosed in this specification, and the technical ideas disclosed in this specification are not limited by the attached drawings, and should be understood to include all modifications, equivalents, or substitutes included in the spirit and technical scope of the present invention.

[0056] Figure 1 is a cross-sectional view illustrating a scroll compressor of the present invention.

[0057] Hereinafter, with reference to FIG. 1, the scroll compressor (10) of the present invention will be described.

[0058] The scroll compressor of the present invention comprises: a casing (110) having a sealed internal space; a motor (120) having a stator (121) fixed to the internal space and a rotor (122) rotated within the stator (121); a rotational shaft (125) rotatably coupled to the rotor (122); a main frame (130) provided on one side of the driving motor (120) and fixed to the internal space of the casing (110); an orbiting scroll (150) coupled to the rotational shaft (125) so as to be capable of rotational movement and axially supported by the main frame (130); a non-orbiting scroll (140) coupled to the orbiting scroll (150) to form a compression chamber and having a discharge port (1411) for discharging refrigerant compressed in the compression chamber; A back pressure chamber assembly (160) is provided on one axial side of the non-orbiting scroll (140) and supports the non-orbiting scroll (140) in a direction toward the orbiting scroll (150); and a discharge valve (145) is slidably inserted into the back pressure chamber assembly (160) and opens and closes the discharge port (1411).

[0059] In the present invention, the internal space of the casing (110) may include a low pressure portion (110a), a high pressure portion (110b), an oil storage space (110c), and a suction space (S) where refrigerant is sucked.

[0060] The discharge valve (145) is formed so that the diameter of one side adjacent to the discharge port (1411) is larger than the diameter of the other side.

[0061] Due to this, the discharge path of the back pressure chamber assembly (160) near the other side of the discharge valve (145) can be expanded, thereby reducing the flow resistance and improving performance.

[0062] In a conventional scroll compressor, the check valve must be designed with a diameter larger than the discharge path of the non-rotating scroll (140) in order to form the initial pressure in the compression section. Accordingly, the conventional discharge valve is designed in a cylindrical shape, and the valve guide installed in the back pressure chamber assembly (160) takes up a large space in the discharge path, causing resistance when discharging the refrigerant, which has the problem of hindering the performance of the compressor.

[0063] The present invention improves the performance of the compressor by securing a discharge area or discharge path by forming a diameter of one side adjacent to the discharge port (1411) of the discharge valve (145) to be larger than the diameter of the other side in order to reduce discharge resistance. In the present invention, the discharge valve (145) may be a check valve.

[0064] Hereinafter, the scroll compressor of the present invention will be described.

[0065] Scroll compressors can be classified into high-pressure scroll compressors and low-pressure scroll compressors depending on the path through which the refrigerant is sucked. Hereinafter, a low-pressure scroll compressor in which the internal space of the casing (110) is separated into a low-pressure section and a high-pressure section by a high-low-pressure separator plate and in which the refrigerant suction pipe is connected to the low-pressure section will be described as an example.

[0066] In addition, scroll compressors can be classified into a non-orbiting back pressure type in which a non-orbiting scroll (140) is pressurized toward an orbiting scroll (150) and a orbiting back pressure type in which an orbiting scroll (150) is pressurized toward a non-orbiting scroll (140) depending on the back pressure method. The following description focuses on a scroll compressor according to a non-orbiting back pressure method. However, the same can be applied to a orbiting back pressure method.

[0067] In addition, scroll compressors can be divided into vertical scroll compressors in which the rotation shaft (125) is arranged perpendicular to the ground and horizontal scroll compressors in which the rotation shaft (125) is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side can be defined as the side facing the ground. The following description will be given using a vertical scroll compressor as an example. However, the same can be applied to a horizontal scroll compressor.

[0068] In addition, scroll compressors can be classified into upper compression type and lower compression type depending on the relative position of the compression part with respect to the electric part (120). Hereinafter, an upper compression type scroll compressor having a vertical shape and a compression part located above the electric part (120) will be described.

[0069] In addition, scroll compressors can be classified into fixed-radius and variable-radius types depending on the rotation method of the orbiting scroll (150). The following description focuses on a variable-radius scroll compressor.

[0070] Fig. 1 is a longitudinal cross-sectional view showing the inside of a scroll compressor according to the present embodiment.

[0071] Referring to FIG. 1, a scroll compressor according to the present embodiment includes a driving motor (120) forming an electric motor (120) in the lower half of a casing (110), and a main frame (130), a non-orbiting scroll (140), an orbiting scroll (150), and a back pressure chamber assembly (160) forming a compression unit in the upper part of the driving motor (120). The electric motor (120) is coupled to one end of a rotating shaft (125), and the compression unit is coupled to the other end of the rotating shaft (125). Accordingly, the compression unit is connected to the electric motor (120) by the rotating shaft (125) and operates by the rotational force of the electric motor (120).

[0072] The casing (110) includes a cylindrical shell (111), an upper cap (112), and a lower cap (113).

[0073] The cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and the aforementioned driving motor (120) and main frame (130) are inserted and fixed on the inner surface. A terminal bracket (not shown) is coupled to the upper half of the cylindrical shell (111). A terminal (not shown) for transmitting external power to the driving motor (120) is coupled through the terminal bracket. A refrigerant suction pipe (117), which will be described later, is coupled through the upper half of the cylindrical shell (111), for example, the upper side of the driving motor (120).

[0074] The upper cap (112) is coupled to cover the opened upper part of the cylindrical shell (111). The lower cap (113) is coupled to cover the opened lower part of the cylindrical shell (111). The rim of a high-low pressure separation plate (115), which will be described later, is inserted between the cylindrical shell (111) and the upper cap (112) and is welded together to the cylindrical shell (111) and the upper cap (112). The rim of a support bracket (116), which will be described later, is inserted between the cylindrical shell (111) and the lower cap (113) and is welded together to the cylindrical shell (111) and the lower cap (113). Accordingly, the internal space of the casing (110) can be sealed.

[0075] The rim of the high-low pressure separator (115) is welded to the casing (110) as described above. The central portion of the high-low pressure separator (115) is bent so as to protrude toward the upper surface of the upper cap (112) and is placed on the upper side of the back pressure chamber assembly (160) to be described later. A refrigerant suction pipe (117) is connected to the lower side of the high-low pressure separator (115), and a refrigerant discharge pipe (118) is connected to the upper side. Accordingly, a low pressure portion (110a) forming a suction space can be formed on the lower side of the high-low pressure separator (115), and a high pressure portion (110b) forming a discharge space can be formed on the upper side.

[0076] In addition, a through hole (115a) is formed in the center of the high-low pressure separator (115). A sealing plate (1151) from which a floating plate (165) to be described later is detachably attached is inserted and coupled into the through hole (115a). The low-pressure section (110a) and the high-pressure section (110b) can be blocked by attaching and detaching the floating plate (165) and the sealing plate (1151), or can be communicated through the high-low pressure communication hole (1151a) of the sealing plate (1151).

[0077] In addition, the lower cap (113) forms an oil storage space (110c) together with the lower half of the cylindrical shell (111) forming the low-pressure portion (110a). In other words, the oil storage space (110c) is formed in the lower half of the low-pressure portion (110a), and the oil storage space (110c) forms a part of the low-pressure portion (110a). An oil pickup (126), which will be described later, is submerged in the oil storage space (110c), and when the compressor is in operation, the oil stored in the oil storage space (110c) is pumped by the oil pickup (126) and supplied to the sliding portion through the oil passage (1253) of the rotating shaft (125), which will be described later.

[0078] Referring to Fig. 1, the driving motor (120) according to the present embodiment is installed in the lower half of the low-pressure section (110a) and includes a stator (121) and a rotor (122). The stator (121) is fixed to the inner wall surface of the cylindrical shell (111) by hot pressing, and the rotor (122) is rotatably provided inside the stator (121).

[0079] The stator (121) includes a stator core (1211) and a stator coil (1212).

[0080] The stator core (1211) is formed in a cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot pressing. The stator coil (1212) is wound around the stator core (1211) and can be electrically connected to an external power source through a terminal (not shown) that is connected through the casing (110).

[0081] The rotor (122) includes a rotor core (1221) and a permanent magnet (1222).

[0082] The rotor core (1221) is formed in a cylindrical shape and is rotatably inserted into the interior of the stator core (1211) at a predetermined gap interval. Permanent magnets (1222) are embedded in the interior of the rotor core (1222) at a predetermined gap interval along the circumference.

[0083] In addition, a rotation shaft (125) is press-fitted and coupled to the center of the rotor core (1221). An eccentric pin portion (1252) is provided at the upper end of the rotation shaft (125), and an orbiting scroll (150), which will be described later, is eccentrically coupled thereto. Accordingly, the rotational force of the driving motor (120) can be transmitted to the orbiting scroll (150) through the rotation shaft (125).

[0084] Meanwhile, the lower end of the rotary shaft (125) is coupled to the rotor (122) and the upper end is coupled to the orbiting scroll (150) to be described later. Accordingly, the rotational power of the driving motor (120) is transmitted to the orbiting scroll (150) through the rotary shaft (125).

[0085] An oil passage (1253), which will be described later, is formed by penetrating the interior of the rotating shaft (125). For example, the oil passage (1253) penetrates between the lower and upper ends of the rotating shaft (125), and is formed to be inclined at a preset angle so as to move away from the center of the shaft from the lower end to the upper end. Accordingly, centrifugal force is generated in the oil passage (1253), so that oil can be smoothly supplied to the upper end of the rotating shaft (125).

[0086] In addition, an oil pickup (126) is provided at the bottom of the rotating shaft (125) to suck up oil stored in the oil storage space (110c) of the casing (110). The oil pickup (126) can be applied to various types of pumps, such as centrifugal pumps, viscous pumps, and gear pumps.

[0087] Referring to FIG. 1, the main frame (130) according to the present embodiment is installed on the upper side of the driving motor (120) and is fixed by hot pressing or welding to the inner wall surface of the cylindrical shell (111).

[0088] The main frame (130) according to the present embodiment includes a main flange portion (131), a main bearing portion (132), a rotation space portion (133), a scroll support portion (134), an old ring support portion (135), and a frame fixing portion (136).

[0089] The main flange portion (131) is formed in an annular shape and is accommodated in the low-pressure portion (110a) of the casing (110). The outer diameter of the main flange portion (131) is formed smaller than the inner diameter of the cylindrical shell (111), so that the outer surface of the main flange portion (131) is spaced apart from the inner surface of the cylindrical shell (111). However, a frame fixing portion (136), which will be described later, protrudes radially from the outer surface of the main flange portion (131). The outer surface of the frame fixing portion (136) is fixedly attached to the inner surface of the casing (110). Accordingly, the main frame (130) is fixedly coupled to the casing (110).

[0090] The main bearing portion (132) protrudes downward from the central lower surface of the main flange portion (131) toward the driving motor (120). The main bearing portion (132) has a cylindrical shaft hole (132a) extending axially therethrough. A rotation shaft (125) is inserted into the inner circumferential surface of the shaft hole (132a) and supported radially.

[0091] The pivot space (133) is sunken from the center of the main flange (131) toward the main bearing (132) to a preset depth and outer diameter. The pivot space (133) is formed to be larger than the outer diameter of the rotation shaft coupling (153) provided in the pivot scroll (150) described later. Accordingly, the rotation shaft coupling (153) can be accommodated so as to be pivotable within the pivot space (133).

[0092] The scroll support member (134) is formed in a ring shape along the periphery of the pivot space member (133) on the upper surface of the main flange member (131). Accordingly, the scroll support member (134) supports the lower surface of the pivot plate member (151) described later in the axial direction.

[0093] The Oldham ring support member (135) is formed in a ring shape along the outer circumference of the scroll support member (134) on the upper surface of the main flange member (131). Accordingly, the Oldham ring (170) is inserted into the Oldham ring support member (135) and is rotatably accommodated.

[0094] The frame fixing member (136) extends radially from the outer edge of the old ring support member (135). The frame fixing member (136) extends in an annular shape or extends as a plurality of protrusions spaced apart at predetermined intervals along the circumferential direction. In the present embodiment, an example in which the frame fixing member (136) is formed as a plurality of protrusions along the circumferential direction is illustrated.

[0095] Referring to FIG. 1, the non-orbiting scroll (140) according to the present embodiment is placed on the upper portion of the main frame (130) with the orbiting scroll (150) interposed therebetween. The non-orbiting scroll (140) may be fixedly coupled to the main frame (130) or may be coupled so as to be movable in the vertical direction. The present embodiment illustrates an example in which the non-orbiting scroll (140) is coupled so as to be movable in the axial direction with respect to the main frame (130).

[0096] A non-orbiting scroll (140) according to the present embodiment includes a non-orbiting plate portion (141), a non-orbiting wrap (142), a non-orbiting side wall portion (143), and a guide projection portion (144).

[0097] The non-rotating plate portion (141) is formed in a circular shape and is arranged transversely from the low pressure portion (110a) of the casing (110). A discharge port (1411), a bypass hole (1412), and a scroll side pressure hole (1413) are each axially penetrated through the central portion of the non-rotating plate portion (141).

[0098] The discharge port (1411) is formed at a position where the discharge pressure chambers (not shown) of the two compression chambers (V) formed on the inner and outer sides of the non-rotating wrap (142) are connected to each other. The bypass hole (1412) is formed to be connected to each of the two compression chambers (V). The scroll side back pressure hole (hereinafter, the first back pressure hole) (1413) is spaced apart from the discharge port (1411) and the bypass hole (1412).

[0099] The non-orbiting wrap (142) extends axially from the lower surface of the non-orbiting plate portion (141) facing the orbiting scroll (150) to a predetermined height, and extends so as to be wound spirally several times around the discharge port (1411) toward the non-orbiting side wall portion (143). The non-orbiting wrap (142) is formed to correspond to the orbiting wrap (152) described below, so as to form two pairs of compression chambers (V) between it and the orbiting wrap (152).

[0100] The non-rotating side wall portion (143) is formed in a ring shape by extending axially from the lower edge of the non-rotating plate portion (141) to surround the non-rotating wrap (142). A suction port (1431) penetrating radially is formed on one side of the outer circumference of the non-rotating side wall portion (143).

[0101] The guide protrusion (144) may extend radially from the lower outer circumference of the non-rotating side wall (143). The guide protrusion (144) may be formed in a single ring shape, or a plurality of guide protrusions (144) may be formed at predetermined intervals along the circumference. This embodiment will be described with reference to an example in which a plurality of guide protrusions (144) are formed at predetermined intervals along the circumference.

[0102] The non-rotating scroll (140) may have a fastening groove (1411a) formed on the upper surface for fastening a back pressure plate (161). A plurality of fastening grooves (1411a) may be formed at approximately equal intervals along the circumferential direction.

[0103] Referring to Fig. 1, the orbiting scroll (150) according to the present embodiment is coupled to a rotation shaft (125) and placed on the upper surface of the main frame (130). For example, the orbiting scroll (150) is provided between the main frame (130) and the non-orbiting scroll (140). An anti-rotation mechanism, an Oldham ring (170), is provided between the main frame (130). Accordingly, the orbiting scroll (150) is restricted from rotating and performs an orbiting motion with respect to the non-orbiting scroll (140).

[0104] Specifically, the rotary scroll (150) includes a rotary plate portion (151), a rotary wrap (152), and a rotary shaft coupling portion (153).

[0105] The pivot plate (151) is formed in a roughly circular shape. The pivot plate (151) is axially supported by the scroll support (134) of the main frame (130). Accordingly, the pivot plate (151) and the scroll support (134) facing it form an axial bearing surface (not shown).

[0106] The orbiting wrap (152) forms a compression chamber (V) together with the non-orbiting wrap (142). The orbiting wrap (152) is formed in a spiral shape by protruding at a preset height from the upper surface of the orbiting plate (151) facing the non-orbiting scroll (140). The orbiting wrap (152) is formed corresponding to the non-orbiting wrap (142) of the non-orbiting scroll (140) to perform an orbital motion by interlocking with the non-orbiting wrap (142) of the non-orbiting scroll (140) described later.

[0107] The rotary shaft coupling portion (153) protrudes from the lower surface of the rotary plate portion (151) toward the main frame (130). The rotary shaft coupling portion (153) has an inner circumferential surface formed in a cylindrical shape, into which a rotary bearing (not shown) made of a bushing bearing can be press-fitted. A sliding bush (155) is rotatably inserted into the interior of the rotary bearing, thereby forming the variable radius scroll compressor described above.

[0108] FIG. 2 is an exploded perspective view showing a back pressure chamber assembly (160), a discharge valve (145), and a non-orbiting scroll (140), FIG. 3 is a cross-sectional view showing a back pressure chamber assembly (160), a discharge valve (145), and a non-orbiting scroll (140), and FIG. 4 is a cross-sectional view showing a back pressure chamber assembly (160) and a discharge valve (145).

[0109] In addition, FIG. 5 is an exploded perspective view showing an example in which a discharge valve (145) is coupled to a back pressure chamber assembly (160), and FIG. 6 is a plan view of the back pressure chamber assembly (160) viewed from above.

[0110] Fig. 7 is a cross-sectional view showing an example in which the discharge valve (145) opens the discharge port (1411) when discharging the refrigerant, and Fig. 8 is a cross-sectional view showing an example in which the discharge valve (145) closes the discharge port (1411) before discharging the refrigerant.

[0111] Hereinafter, with reference to FIGS. 2 to 8, the configuration of the back pressure chamber assembly (160) and the configuration of the discharge valve (145) will be described.

[0112] Referring to Fig. 1, the back pressure chamber assembly (160) according to the present embodiment is provided on the upper side of the non-orbiting scroll (140). Accordingly, the back pressure of the back pressure chamber (160a) (more precisely, the force exerted by the back pressure on the back pressure chamber) acts on the non-orbiting scroll (140). In other words, the non-orbiting scroll (140) is pressed in the direction toward the orbiting scroll (150) by the back pressure to seal the compression chamber (V).

[0113] Specifically, the back pressure chamber assembly (160) includes a back pressure plate (161) and a floating plate (165). The back pressure plate (161) is coupled to the upper surface of the non-rotating plate portion (141). The floating plate (165) can be slidably coupled to the back pressure plate (161) to form a back pressure chamber (160a) together with the back pressure plate (161).

[0114] The back pressure plate (161) includes a fixed plate portion (1611), a first annular wall portion (1612), and a second annular wall portion (1613).

[0115] The fixed plate (1611) is formed in the shape of an annular plate with a hollow center. A plate-side back pressure hole (hereinafter, second back pressure hole) (1611a) penetrates axially. The second back pressure hole (1611a) is connected to the compression chamber (V) through the first back pressure hole (1413). Accordingly, the second back pressure hole (1611a), together with the first back pressure hole (1413), connects the compression chamber (V) and the back pressure chamber (160a).

[0116] The first annular wall portion (1612) and the second annular wall portion (1613) surround the inner and outer surfaces of the fixed plate portion (1611) from the upper surface of the fixed plate portion (1611). Accordingly, the outer surface of the first annular wall portion (1612), the inner surface of the second annular wall portion (1613), the upper surface of the fixed plate portion (1611), and the lower surface of the floating plate (165) form an annular pressure relief chamber (160a).

[0117] An intermediate discharge port (1612a) is formed in the first annular wall portion (1612) to communicate with the discharge port (1411) of the non-orbiting scroll (140). A valve guide groove (1612b) is formed on the inside of the intermediate discharge port (1612a) into which a discharge valve (145) is slidably inserted. A backflow prevention hole (1612c) is formed in the center of the valve guide groove (1612b). Accordingly, the discharge valve (145) selectively opens and closes between the discharge port (1411) and the intermediate discharge port (1612a) to prevent the discharged refrigerant from flowing back into the compression chamber (V).

[0118] In the present invention, the discharge valve (145) is formed so that the diameter of one side adjacent to the discharge port (1411) is larger than the diameter of the other side. The discharge port (1411) may be provided with a discharge path for discharging refrigerant.

[0119] One side of the discharge valve (145) may be the side that blocks the discharge port (1411) and restricts the flow of discharged refrigerant. It may be the lower side in FIGS. 2 to 4, etc.

[0120] The other side of the discharge valve (145) may be adjacent to the backflow prevention hole.

[0121] Additionally, the other side of the discharge valve (145) may be understood as a portion extending from one side to the opposite side of the discharge port (1411).

[0122] The discharge valve (145) must be formed with a larger diameter than the discharge port (1411) of the non-rotating scroll (140) to form the initial pressure in the compression section.

[0123] In the present invention, since the discharge valve (145) is formed to have different diameters at the top and bottom, rather than being a conventional cylindrical check valve, the diameter of the valve guide in the back pressure chamber assembly (160) that guides the discharge valve (145) can be reduced, and the flow path of the intermediate discharge port (1411) provided around the valve guide can be expanded.

[0124] The discharge valve (145) must be installed so that it can move up and down within the back pressure chamber assembly (160). For this purpose, the back pressure chamber assembly (160) may be provided with a valve guide groove (1612b).

[0125] The discharge valve (145) can be slidably inserted into the back pressure chamber assembly (160). For example, the discharge valve (145) can be inserted into a valve guide groove (1612b) provided on the inside of the back pressure chamber assembly (160).

[0126] The valve guide groove (1612b) may be provided on the inside of the pressure chamber assembly (160).

[0127] The discharge valve (145) may include a large diameter portion (145a) and a small diameter portion (145b).

[0128] The large diameter portion (145a) may be provided on one side of the discharge valve (145).

[0129] The large diameter (145a) can be configured to open and close the discharge port (1411).

[0130] The large diameter portion (145a) may be positioned to block the discharge port (1411) or may be spaced apart from the discharge port (1411).

[0131] The large diameter portion (145a) can be arranged to block the discharge port (1411) of the non-rotating scroll (140) to form pressure in the compression chamber before starting the compressor.

[0132] On the other hand, when the compressor starts and the pressure in the compression chamber increases, the large diameter part (145a) rises and opens the discharge port (1411) to discharge the refrigerant.

[0133] The diameter of the large diameter portion (145a) must be formed larger than the diameter of the discharge port (1411) of the non-rotating scroll (140).

[0134] The large diameter portion (145a) may be provided with a refrigerant receiving groove (145c) formed concavely in the direction toward the small diameter portion (145b) at the bottom to receive a portion of the discharged refrigerant. Accordingly, when the large diameter portion (145a) blocks the discharge port (1411) of the non-rotating scroll (140), the refrigerant near the discharge port (1411) is received in the refrigerant receiving groove (145c) of the large diameter portion (145a), thereby minimizing the refrigerant that may leak between the discharge valve (145) and the discharge port (1411).

[0135] The small diameter part (145b) is provided on the other side of the discharge valve (145) and is a part that is inserted so as to slide into the inside of the pressure relief assembly (160).

[0136] The small diameter portion (145b) can be inserted so as to slide into the valve guide groove (1612b) of the pressure chamber assembly (160).

[0137] As described above, the valve guide groove (1612b) can guide the movement of the discharge valve (145), for example, the small diameter portion (145b).

[0138] For example, the valve guide groove (1612b) may be provided with a small diameter guide groove (1612b1) that guides the small diameter portion (145b) to be inserted so as to slide.

[0139] Meanwhile, in order to limit the upward movement of the discharge valve (145), the valve guide groove (1612b) may further include a jaw portion (1612b3). The jaw portion (1612b3) may be provided at one end of the small-diameter guide groove (1612b1).

[0140] In the present invention, the discharge valve (145) is formed so that the diameter of one side adjacent to the discharge port (1411) is larger than the diameter of the other side. Therefore, compared to the discharge valve (145) of a conventional structure, the back pressure chamber assembly (160) around the other side is provided with a wider thickness. Accordingly, the diameter of the middle discharge port (1411) of the back pressure chamber assembly (160) around the other side can be made wider than in the conventional structure.

[0141] For example, the diameter of the intermediate discharge port (1411) may be provided to be larger than half the diameter of the small diameter portion (145b) and smaller than twice the diameter of the small diameter portion (145b).

[0142] This allows the discharge path to be expanded, reducing flow resistance and improving performance.

[0143] In addition, since the contact area between the discharge valve (145) and the back pressure chamber assembly (160) is reduced, the load applied to the back pressure chamber assembly (160) is reduced, and thus durability can be improved.

[0144] A plurality of intermediate discharge ports (1411) may be provided. A partition wall (1612d) of a predetermined width may be provided between the plurality of intermediate discharge ports (1411).

[0145] The partition wall (1612d) may include a portion having the same width along the radial direction.

[0146] Meanwhile, in the non-rotating scroll (140), a discharge guide groove (1415) is formed at the outlet end of the discharge port (1411). According to the embodiment, the discharge guide groove (1415) is formed around the discharge port (1411) on the upper surface (150a) of the non-rotating plate portion (151).

[0147] Referring to FIGS. 2 and 3, the discharge guide groove (1415) is formed by recessing a predetermined depth in the axial direction from the upper surface (150a) of the non-rotating plate portion (151) toward the lower surface (not shown). The discharge guide groove (1415) is formed in the shape of a long groove when projected on a plane.

[0148] For example, the discharge guide groove (1415) can be formed in a long groove shape having a long-axis side (1515a) and a short-axis side (1515b).

[0149] According to this embodiment, the outlet end of the discharge port (1411) is provided with a valve seat portion on which a discharge valve (145) is mounted.

[0150] For example, in this embodiment, the valve seat portion may be formed as a valve seat groove (1415a) into which one side (large diameter portion (145a)) of the discharge valve (145) can be inserted.

[0151] The valve seat groove (1415a) can be formed concavely so as to sink in the direction toward the discharge port (1411) from the outlet end of the discharge guide groove (1415).

[0152] The valve seat groove (1415a) may have a height equal to the axial width of one side of the discharge valve (145) or a height smaller than the axial width of one side of the discharge valve (145). For example, the recessed depth of the valve seat groove (1415a) may be formed to be equal to or smaller than half of the height of one side of the discharge valve (145), i.e., the large-diameter portion (145a).

[0153] The valve seat groove (1415a) can be formed in a shape that matches one side of the discharge valve (145) so that one side of the discharge valve (145) can be inserted.

[0154] For example, the valve seat groove (1415a) may have a circular cross-section.

[0155] As shown in FIGS. 7 and 8, by the structure in which one side of the discharge valve (145) is inserted into the valve seat groove (1415a), when the discharge valve (145) is closed to block the discharge port (1411), the discharge port (1411) of the refrigerant gas can be blocked more stably by being inserted into the valve seat groove (1415a), thereby improving the sealing performance.

[0156] Fig. 9 is an exploded perspective view showing an example in which a valve seat protrusion (1415b) is provided on a non-orbiting scroll (140), and Fig. 10 is a cross-sectional view showing an example in which a valve seat protrusion (1415b) is provided on a non-orbiting scroll (140).

[0157] The valve seat portion is not necessarily formed as a valve seat groove (1415a). As another example of the valve seat portion, the valve seat portion may be formed as a valve seat protrusion (1415b) on which one side (large diameter portion (145a)) of the discharge valve (145) can be seated.

[0158] The valve seat protrusion (1415b) can be formed convexly so as to protrude in the direction toward the discharge valve (145) from the outlet end of the discharge port (1411) in the discharge guide groove (1415).

[0159] The valve seat protrusion (1415b) may have a height smaller than the axial width of one side of the discharge valve (145). For example, the protrusion height of the valve seat groove (1415a) may be formed to be equal to or smaller than half of the height of one side of the discharge valve (145), i.e., the large-diameter portion (145a).

[0160] The valve seat protrusion (1415b) can be formed in a shape that matches one side of the discharge valve (145) so that one side of the discharge valve (145) can be seated.

[0161] For example, the valve seat protrusion (1415b) may have a circular cross-section.

[0162] By having a structure in which one side of the discharge valve (145) is seated on the valve seat protrusion (1415b), when the discharge valve (145) is closed to block the discharge port (1411), the discharge port (1411) of the refrigerant gas can be more stably blocked by being seated on the valve seat protrusion (1415b), thereby improving the sealing performance.

[0163] Meanwhile, the floating plate (165) is formed in an annular shape. It can be formed of a material lighter than the back pressure plate (161). Accordingly, the floating plate (165) moves axially with respect to the back pressure plate (161) according to the pressure of the back pressure chamber (160a) and is attached to and detached from the lower surface of the high-low pressure separator (115). For example, when the floating plate (165) comes into contact with the high-low pressure separator (115), it serves to seal the discharged refrigerant so that it does not leak to the low pressure section (110a) but is discharged to the high pressure section (110b).

[0164] The scroll compressor according to the above embodiment operates as follows.

[0165] That is, when power is applied to the stator coil (121a) of the stator (121), the rotor (122) rotates together with the rotation shaft (125). Then, the orbiting scroll (150) coupled to the rotation shaft (125) performs a rotational movement with respect to the non-orbiting scroll (140), and a pair of compression chambers (V) are formed between the orbiting wrap (152) and the non-orbiting wrap (142).

[0166] This compression chamber (V) gradually reduces in volume as it moves from the outside to the inside according to the rotational movement of the orbiting scroll (150). At this time, the refrigerant is sucked into the low pressure section (110a) of the casing (110) through the refrigerant suction pipe (117), and a portion of this refrigerant is directly sucked into each suction pressure chamber (not symbol) forming both compression chambers (V), while the remainder moves toward the driving motor (120), cools the driving motor (120), and is then sucked into the suction pressure chamber (not symbol).

[0167] Next, the refrigerant sucked into the suction pressure chamber (not symbol) is compressed as it moves toward the intermediate pressure chamber and the discharge pressure chamber (not symbol) along the movement path of the compression chamber (V). The refrigerant moving to the discharge pressure chamber (not symbol) pushes the discharge valve (145) and is discharged to the high pressure section (110b) through the discharge port (1411) and the intermediate discharge port (1612a), and this refrigerant fills the high pressure section (110b) and then is discharged through the refrigerant discharge pipe (118) through the condenser of the refrigeration cycle, repeating a series of processes.

[0168] As described above, in order to build up pressure in the compression chamber before the compressor starts, the large diameter portion (145a) of the discharge valve (145) is arranged to block the discharge port (1411). The lower end (contact portion) of the discharge valve (145) is seated in the valve seat groove (1415a) or the valve seat protrusion (1415b), thereby blocking the discharge port (1411) and blocking the intermediate discharge port (1411). At this time, some of the refrigerant in the compression chamber may be accommodated in the refrigerant accommodation groove (145c) at the lower end of the discharge valve (145).

[0169] As the compressor starts and the pressure in the compression chamber increases, the discharge valve (145) rises to open the discharge port (1411) to discharge the refrigerant. The large diameter portion (145a) of the discharge valve (145) is arranged to open the discharge port (1411). The lower end (contact portion) of the discharge valve (145) is spaced apart from the valve seat groove (1415a) or the valve seat protrusion (1415b) to open the discharge port (1411) to enable communication with the intermediate discharge port (1411). At this time, a portion of the refrigerant that has escaped from the compression chamber through the discharge port (1411) can be accommodated in the refrigerant receiving groove (145c) at the lower end of the discharge valve (145).

[0170] The discharge valve (145) can be guided in movement by the valve guide groove (1612b) of the pressure chamber assembly (160). When the discharge port (1411) of the discharge valve (145) is opened, the movement of the large diameter portion (145a) in the upward direction is restricted by the jaw portion (1612b3).

[0171] In this way, the discharge valve (145) selectively opens and closes between the discharge port (1411) and the intermediate discharge port (1612a) to prevent the discharged refrigerant from flowing back into the compression chamber (V).

[0172] In addition, another portion of the refrigerant compressed while passing through the intermediate pressure chamber (not shown) flows into the intermediate pressure chamber (160a) through the first pressure relief hole (1413) before reaching the discharge port (1411), thereby forming an intermediate pressure in the intermediate pressure chamber (160a). Then, the non-orbiting scroll (140) descends toward the orbiting scroll (150) to seal the space between the non-orbiting scroll (140) and the orbiting scroll (150), thereby preventing leakage between the compression chambers.

[0173]

[0174] The present invention can be used in a scroll compressor having a structure that improves the performance of the scroll compressor by reducing discharge resistance by additionally securing a discharge area.

Claims

1. A casing with a sealed internal space; A motor having a stator fixed to the internal space and a rotor rotating inside the stator; A rotating shaft rotatably coupled to the above rotor; A main frame provided on one side of the above electric part and fixed to the internal space of the casing; A rotary scroll coupled to a rotary shaft so as to be capable of rotary motion and axially supported on the main frame; A non-orbiting scroll which is coupled to be engaged with the above-mentioned orbiting scroll to form a compression chamber and has a discharge port for discharging the refrigerant compressed in the compression chamber; A back pressure chamber assembly provided on one axial side of the non-orbiting scroll and supporting the non-orbiting scroll in a direction toward the orbiting scroll; and It includes a discharge valve that is slidably inserted into the above pressure chamber assembly and opens and closes the discharge port, A scroll compressor in which the discharge valve is formed so that the diameter of one side adjacent to the discharge port is larger than the diameter of the other side.

2. In paragraph 1, The above discharge valve, A large diameter part provided on the above side to open and close the discharge port; and A scroll compressor comprising a small diameter part provided on the other side and slidably inserted into the back pressure chamber assembly.

3. In paragraph 2, The above pressure chamber assembly is provided with a valve guide groove that guides the movement of the discharge valve. A scroll compressor in which the above valve guide groove has a jaw portion that limits the upward movement of the large diameter portion.

4. In paragraph 3, A scroll compressor, wherein the above-mentioned back pressure chamber assembly is provided with an intermediate discharge port communicating with the discharge port, and the diameter of the intermediate discharge port is provided to be larger than half the diameter of the small-diameter portion and smaller than twice the diameter of the small-diameter portion.

5. In paragraph 3, The above valve guide groove is a scroll compressor having a small-diameter guide groove that guides the small-diameter part to be inserted so as to slide.

6. In paragraph 5, The above jaw portion is a scroll compressor provided at one end of the above small diameter guide groove.

7. In paragraph 2, A scroll compressor having a refrigerant receiving groove formed concavely in the lower portion toward the small diameter portion to receive a portion of the discharged refrigerant.

8. In paragraph 7, A scroll compressor having a contact portion formed in a lower portion around the refrigerant receiving groove and capable of contacting an end of the discharge port to enable closing the discharge port.

9. In paragraph 1, The above-mentioned back pressure chamber assembly is provided with a plurality of intermediate discharge ports communicating with the discharge port. A scroll compressor having a partition wall of a predetermined width provided between the plurality of intermediate discharge ports.

10. In paragraph 9, The above-mentioned pressure chamber assembly comprises a fixed plate portion formed in an annular shape, a first annular wall portion forming an inner surface of the fixed plate portion, and a second annular wall portion forming an outer surface of the fixed plate portion. The above first annular wall portion has the intermediate discharge port on the inside, A scroll compressor having a valve guide groove that guides movement of the discharge valve toward the inside of the intermediate discharge port.

11. In paragraph 9, A scroll compressor wherein the above-mentioned partition wall includes a portion having the same width along the radial direction.

12. In paragraph 1, On one axial side of the non-rotating scroll facing the above-mentioned back pressure chamber assembly, a discharge guide groove is formed to be sunken to a preset depth and to accommodate the discharge port. A scroll compressor having a valve seat groove in which the discharge guide groove is formed concavely so as to sink in the direction from the outlet end of the discharge port toward the discharge port and into which one side of the discharge valve is inserted.

13. In paragraph 12, A scroll compressor wherein the above valve seat groove has a height equal to or smaller than the axial width of one side of the discharge valve.

14. In paragraph 1, On one axial side of the non-rotating scroll facing the above-mentioned back pressure chamber assembly, a discharge guide groove is formed to be sunken to a preset depth and to accommodate the discharge port. A scroll compressor, wherein an axial side of the non-rotating scroll facing the above-mentioned back pressure chamber assembly is provided with a valve seat projection that protrudes from the discharge guide groove in the direction toward the discharge valve at the outlet end of the discharge port to enable one side of the discharge valve to be seated.

15. In paragraph 14, A scroll compressor in which the above valve seat projection has a height equal to or smaller than the axial width of one side of the discharge valve.

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