Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a casing, a main frame, a fixed scroll, an orbiting scroll, and a back pressure plate. A plate accommodation recess is formed in one side surface of the orbiting scroll facing the main frame, and the back pressure plate is slidably inserted into the plate accommodation recess in the axial direction of a rotary shaft to form a back pressure chamber between the back pressure plate and the orbiting scroll. As such, a back pressure chamber assembly is simplified to reduce manufacturing costs, a sealing force of the back pressure chamber is increased to reduce suction loss due to overheating of suction refrigerant, and as large an actual area of the back pressure chamber as possible is secured, thereby enlarging a back pressure area supporting the orbiting scroll and stably supporting the orbiting scroll.

Description

Scroll compressor

[0001] The present invention relates to a scroll compressor.

[0002] Compressors used in refrigeration cycles, such as those in refrigerators or air conditioners, perform the function of compressing refrigerant gas and transferring it to the condenser. Rotary compressors or scroll compressors are primarily used in air conditioners; scroll compressors are being applied not only to air conditioners but, more recently, also to compressors for water heaters that require higher compression ratios than air conditioners.

[0003] Scroll compressors are classified as hermetic compressors if the drive unit (or electric unit) and the compressor unit are contained in a single casing, and as open compressors if they are provided independently; they are classified as upper compression type if the compressor unit is located above the drive unit, and lower compression type if it is located below; and they can be classified as low pressure type if the space housing the drive unit is for suction pressure, and high pressure type if it is for discharge pressure.

[0004] Additionally, the scroll compressor may include a fixed scroll equipped with a fixed wrap and a rotary scroll equipped with a rotary wrap that engages with the fixed wrap. Scroll compressors can be classified into fixed back pressure and rotary back pressure types depending on the back pressure method. The fixed back pressure method is a method in which a back pressure chamber is formed on the back surface of the fixed scroll, and the rotary back pressure method is a method in which a back pressure chamber is formed on the back surface of the rotary scroll. Typically, in the fixed back pressure method, the fixed scroll is constrained in the circumferential direction but is configured to be movable in the axial direction, so it is sometimes described as a non-rotating scroll. Hereinafter, it will be described uniformly as a fixed scroll.

[0005] Patent Document 1 (US2015 / 0345493 A1) discloses a low-pressure and fixed-back pressure type scroll compressor. A fixed-back pressure type scroll compressor like Patent Document 1 requires the addition of multiple parts to form a back pressure chamber on the back surface of the fixed scroll, which can increase manufacturing costs.

[0006] Patent Document 2 (US2007 / 0092390 A1) discloses a low-pressure, swirling back-pressure type scroll compressor. In a swirling back-pressure type scroll compressor like Patent Document 2, a back-pressure chamber is formed in the main frame facing the swirling scroll. Consequently, the sealing member forming the back-pressure chamber is separated from the swirling scroll, which can cause leakage of the refrigerant in the back-pressure chamber. As a result, the relatively high-temperature refrigerant may heat the refrigerant being sucked into the compression chamber, causing suction loss. Furthermore, in Patent Document 2, since the back-pressure chamber is formed in the main frame, the swirling scroll moves relative to the main frame, which limits the area of ​​the back-pressure chamber and may be disadvantageous for stably supporting the swirling scroll. Additionally, in Patent Document 2, since the back-pressure chamber is formed in the main frame, there is a limit to reducing the weight of the swirling scroll, which may lead to a decrease in the performance of the compressor. Such performance degradation of the compressor may occur more significantly in the case of a large-capacity scroll compressor.

[0007] The objective of the present invention is to provide a scroll compressor capable of reducing manufacturing costs by simplifying the back pressure chamber assembly that brings the rotating scroll and the stationary scroll into close contact.

[0008] Another objective of the present invention is to provide a scroll compressor capable of increasing the sealing force of the back pressure chamber to prevent leakage of refrigerant in the back pressure chamber or the inflow of a high-pressure medium into the back pressure chamber.

[0009] Another objective of the present invention is to provide a scroll compressor capable of increasing energy efficiency by reducing the weight of the rotating scroll.

[0010] Another objective of the present invention is to provide a scroll compressor capable of stably supporting a swivel scroll by forming the back pressure chamber area as wide as possible.

[0011] Another objective of the present invention is to provide a scroll compressor capable of tightly sealing the space between the rotating scroll and the stationary scroll by increasing the back pressure of the back pressure chamber.

[0012] Another objective of the present invention is to provide a scroll compressor capable of reducing friction loss between a rotating scroll and a stationary scroll by appropriately adjusting the back pressure of the back pressure chamber.

[0013] Another objective of the present invention is to provide a scroll compressor capable of increasing the suction volume while simultaneously increasing the wrap strength.

[0014] To achieve the objective of the present invention, a scroll compressor comprising a casing, a main frame, a fixed scroll, a slewing scroll, and a back pressure plate may be provided. The main frame may be fixed inside the casing. The fixed scroll may be coupled to one side of the main frame. The slewing scroll may be provided between the main frame and the fixed scroll and may have a slewing plate portion eccentrically coupled to a rotation axis, and a slewing wrap extending from one side of the slewing plate portion and engaging with the fixed wrap of the fixed scroll to form a compression chamber. The back pressure plate may be provided between the slewing scroll and the main frame facing it, and may form a back pressure chamber between it and the slewing scroll. A plate receiving groove may be formed on one side of the slewing scroll facing the main frame to receive the back pressure plate. Through this, the back pressure chamber assembly is simplified to reduce manufacturing costs, the sealing force of the back pressure chamber is increased to reduce suction loss caused by overheating of the suction refrigerant, and the actual back pressure chamber area is secured as wide as possible to expand the back pressure area supporting the spinning scroll, thereby enabling stable support of the spinning scroll.

[0015] For example, an Oldham ring is provided between the main frame and the rotary scroll, and a keyway may be formed in the rotary scroll to receive the key of the Oldham ring in a sliding manner. In the back pressure plate, a key receiving groove portion in which the key of the Oldham ring is received in a sliding manner may be formed to correspond to the keyway of the rotary scroll.

[0016] For example, a key receiving projection may be formed on one side of the pivot scroll facing the main frame, extending toward the main frame along the circumference of the keyway. The key receiving projection may be inserted into the key receiving groove of the back pressure plate so that the back pressure plate can be coupled to the pivot scroll.

[0017] As another example, the back pressure plate may be provided with a discharge passage for discharging the refrigerant of the back pressure chamber to the outside of the back pressure chamber.

[0018] For example, the discharge passage may include a discharge hole, a discharge groove, and a discharge guide groove. The discharge hole may be formed to penetrate between the two sides of the back pressure plate. The discharge groove may be formed by being recessed to a predetermined depth on the other side of the back pressure plate facing the main frame, communicating with the discharge hole. The discharge guide groove may be formed on the other side of the back pressure plate to communicate with the discharge groove, and may be formed with a cross-sectional area smaller than that of the discharge groove to extend to the outer surface of the back pressure plate.

[0019] Specifically, the discharge groove is formed in an annular shape, and the discharge guide groove can extend along the circumference of the discharge groove.

[0020] As another example, the back pressure chamber may include a first back pressure chamber and a second back pressure chamber. The second back pressure chamber is separated from the first back pressure chamber and may form a lower pressure than that of the first back pressure chamber.

[0021] For example, an Oldham ring may be provided between the main frame and the pivot scroll, and a keyway may be formed in the pivot scroll to receive the key of the Oldham ring in a sliding manner. A key receiving groove may be formed in the back pressure plate to receive the key of the Oldham ring in a sliding manner. The first back pressure chamber may be formed in an annular shape on the inner side of the key receiving groove, and a plurality of second back pressure chambers may be formed in an arc shape on both sides in the circumferential direction with the key receiving groove in between.

[0022] Specifically, on at least one of the two sides of the plate receiving groove and the back pressure plate facing it, a sealing projection may be formed that protrudes toward the opposite side between the inner wall and the outer wall of the plate receiving groove. A sealing member for sealing the back pressure chamber may be provided on the radial side of the sealing projection.

[0023] More specifically, a sealing groove into which a part of the sealing member is inserted may be formed on at least one of the one side of the plate receiving groove and the one side of the back pressure plate facing it.

[0024] As another example, on at least one of the sides of the plate receiving groove and the side of the back pressure plate facing it, a sealing projection may be formed that protrudes toward the opposite side between the inner wall and the outer wall of the plate receiving groove. A sealing member may be provided on the cross-section of the sealing projection.

[0025] For example, a sealing groove into which a part of the sealing member is inserted may be formed on at least one of the one side of the plate receiving groove and the one side of the back pressure plate facing it. The sealing member may be inserted into the sealing groove together with the sealing projection.

[0026] Alternatively, a back pressure passage may be formed in the above-mentioned rotating scroll to communicate between the compression chamber and the back pressure chamber. The back pressure passage may include a first back pressure passage that penetrates the rotating end plate portion and communicates to the first back pressure chamber, and a second back pressure passage that penetrates the rotating end plate portion and communicates to the second back pressure chamber from a compression chamber having a pressure lower than the pressure of the compression chamber to which the first back pressure passage communicates.

[0027] Specifically, the second back pressure chambers are formed in a plurality of arc shapes on both sides in the circumferential direction with the key receiving groove in between, and the plurality of second back pressure chambers can be communicated with each other through the key receiving groove. The second back pressure passage can be communicated with any one of the plurality of second back pressure chambers.

[0028] As another example, the back pressure chamber may be formed annularly on one side of the back pressure plate facing the pivoting scroll.

[0029] For example, an Oldham ring may be provided between the main frame and the pivot scroll, and a keyway may be formed in the pivot scroll to receive the key of the Oldham ring in a sliding manner. A key receiving groove may be formed in the back pressure plate to receive the key of the Oldham ring in a sliding manner. A part of the back pressure chamber may be formed to be located on the inner side of the key receiving groove, and another part of the back pressure chamber may be formed to be located on both sides in the circumferential direction with the key receiving groove in between.

[0030] More specifically, on one side of the back pressure plate facing the rotary scroll, a plurality of sealing protrusions protruding toward the rotary scroll may be formed at a predetermined radial interval. A sealing member may be provided between the inner wall of the plate receiving groove and the sealing protrusion facing it radially, and between the outer wall of the plate receiving groove and the sealing protrusion facing it radially.

[0031] More specifically, a back pressure passage may be formed in the above-mentioned rotating scroll to communicate between the compression chamber and the back pressure chamber. The back pressure passage may communicate with the back pressure chamber by continuously penetrating the rotating end plate at the end of the rotating wrap.

[0032] As another example, the back pressure plate can be inserted into the plate receiving groove so as to slide in the axial direction of the rotation axis.

[0033] As another example, the aforementioned slewing scroll may further include a rotational shaft insertion part that overlaps the slewing wrap and the rotational shaft radially at the center of the slewing plate part and extends in the axial direction of the rotational shaft. A portion of the slewing wrap may extend from the leading edge of the rotational shaft insertion part facing the fixed scroll. Through this, the distance between the bearing reaction force and the gas reaction force acting on the slewing scroll is reduced, thereby decreasing the overturning moment of the slewing scroll. Consequently, the behavior of the slewing scroll is stabilized, thereby suppressing leakage between compression chambers and simultaneously lowering back pressure, which can reduce frictional loss between scrolls. At the same time, by forming a compression chamber up to the center of the slewing scroll, the compression ratio increases, and volumetric efficiency can be improved.

[0034] For example, the aforementioned swivel plate portion may be provided with a swivel step surface between the outer surface of the swivel wrap and the inner surface of the swivel wrap facing it, and the aforementioned fixed wrap may be provided with a fixed step surface corresponding to the swivel step surface. At least a portion of the back pressure chamber may be formed to overlap with a compression chamber located closer to the center than the swivel step surface when projected in the axial direction. Through this, the center of the swivel scroll, which is subjected to a relatively high compressive force, can be stably supported, thereby effectively blocking leakage between the compression chambers.

[0035] The scroll compressor according to the present invention can increase the sealing force for the back pressure chamber as the back pressure chamber assembly is inserted into the rotating scroll. This effectively prevents refrigerant leakage from the back pressure chamber or refrigerant inflow into the back pressure chamber, thereby suppressing suction loss and / or compression loss.

[0036] In addition, the scroll compressor according to the present invention can reduce the number of parts and / or assembly steps forming the back pressure chamber assembly and simultaneously reduce the weight of the slewing scroll as the back pressure plate forming the back pressure chamber assembly is coupled to the slewing scroll. Through this, the number of parts and / or assembly steps forming the back pressure chamber assembly are reduced, thereby lowering manufacturing costs, while the motor input is lowered, which can improve energy efficiency.

[0037] In addition, the scroll compressor according to the present invention can secure an actual back pressure chamber area as large as possible by providing a back pressure chamber assembly forming a back pressure chamber inside the rotating scroll. Through this, the back pressure area supporting the rotating scroll is expanded, thereby enabling stable support of the rotating scroll.

[0038] In addition, the scroll compressor according to the present invention can form a high back pressure on the discharge side and a low back pressure on the intermediate pressure side as the back pressure chamber is connected to the compression chamber forming the discharge pressure as well as the compression chamber forming the intermediate pressure. Through this, leakage between the compression chambers on the discharge side can be effectively suppressed, and excessive contact between the scrolls on the suction side can be suppressed, thereby further increasing the compression efficiency of the scroll compressor.

[0039] In addition, the scroll compressor according to the present invention can suppress leakage of the refrigerant in the back pressure chamber to the low-pressure portion of the casing even if the behavior of the swirling scroll is unstable, as the back pressure chamber assembly is provided on the swirling scroll and the sealing member forming the back pressure chamber assembly seals the back pressure chamber. Through this, the refrigerant in the back pressure chamber can suppress heating of the suction refrigerant in the low-pressure portion, thereby suppressing the decrease in compression efficiency due to suction loss.

[0040] In addition, the scroll compressor according to the present invention is formed such that the rotating shaft insertion part overlaps radially with the slewing wrap, and at the same time, a portion of the slewing wrap is extended on the leading edge of the rotating shaft insertion part, thereby allowing a compression chamber to be formed in the center of the slewing scroll. Through this, the compression ratio can be increased and volumetric efficiency improved as the compression cycle of the compression chamber is lengthened while the rotating shaft insertion part extends toward the slewing wrap. At the same time, the wrap height at the discharge ends of the fixed wrap and the slewing wrap is lowered and the wrap thickness is increased, thereby increasing the wrap strength of the fixed wrap and the slewing wrap and suppressing wrap breakage.

[0041] FIG. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0042] FIG. 2 is a perspective view showing a part of the compression section in FIG. 1 disassembled.

[0043] FIG. 3 is a perspective view showing a back pressure chamber assembly according to the present embodiment broken down.

[0044] FIG. 4 is a plan view showing the back pressure chamber assembly in FIG. 2.

[0045] FIG. 5 is a cross-sectional view along "V-V" of FIG. 3.

[0046] FIGS. 6 and FIGS. 7 are cross-sectional views showing the operation of a back pressure chamber assembly according to the present embodiment, where FIG. 6 shows the stop and / or start, and FIG. 7 shows the normal operation.

[0047] FIG. 8 is a cross-sectional view showing another embodiment of a back pressure chamber assembly.

[0048] FIG. 9 is a plan view showing the bottom surface of the back pressure plate in the back pressure chamber assembly of FIG. 8.

[0049] FIG. 10 is a cross-sectional view showing another embodiment of a back pressure chamber assembly.

[0050] FIG. 11 is a plan view showing another embodiment of a back pressure chamber assembly.

[0051] FIG. 12 is a cross-sectional view of the line "XII-XII" of FIG. 11.

[0052] Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0053] Scroll compressors can be classified into hermetic or open types depending on whether the drive motor and the compressor unit are installed together within the internal space of the casing. This embodiment describes a hermetic scroll compressor as a representative example. However, it can be applied equally to an open scroll compressor.

[0054] In addition, scroll compressors can be classified into stationary scroll compressors and mobile scroll compressors. Stationary types are typically used for building HVAC, while mobile types are used for vehicle HVAC. This embodiment describes a stationary scroll compressor as a representative example. However, the same applies to mobile scroll compressors.

[0055] In addition, scroll compressors can be classified into low-pressure or high-pressure types depending on the pressure of the refrigerant filled in the internal space of the casing. In the low-pressure type, the internal space of the casing is filled with refrigerant at the suction pressure, while in the high-pressure type, the internal space of the casing is filled with refrigerant at the discharge pressure. This embodiment is described using a low-pressure scroll compressor as a representative example. However, it can be applied equally to high-pressure scroll compressors.

[0056] In addition, scroll compressors can be classified into upper compression and lower compression types depending on the installation location of the compression section. In the upper compression type, the compression section is installed above the drive motor, while in the lower compression type, the compression section is installed below the drive motor. This embodiment is described using an upper compression type scroll compressor as a representative example. However, it can be applied equally to a lower compression type scroll compressor.

[0057] In addition, scroll compressors can be classified into single-rotation scroll compressors and mutual-rotation scroll compressors depending on whether the scroll rotates. A single-rotation scroll compressor is configured such that one scroll is fixed or its rotational movement is restricted while the other scroll performs a pivotal movement, whereas a mutual-rotation scroll compressor is configured such that both scrolls rotate. This embodiment is described using a single-rotation scroll compressor as a representative example. However, it can be applied in the same way to a mutual-rotation scroll compressor.

[0058] In addition, scroll compressors can be classified into vertical scroll compressors, in which the rotation axis is positioned perpendicular to the ground, and horizontal scroll compressors, in which the rotation axis is positioned 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 as the side facing the ground. The following description uses a vertical scroll compressor as an example. However, it can be applied in the same or similar way to a horizontal scroll compressor. Therefore, in the following description, the axial direction is understood as the axial direction of the rotation axis and the radial direction as the radial direction of the rotation axis; the axial direction can be understood as the up-down direction, the radial direction as the left-right side, the inner circumference as the upper surface, and the axial and radial directions as the side.

[0059] FIG. 1 is a cross-sectional view showing a scroll compressor according to the present invention, and FIG. 2 is a perspective view showing a part of the compression section in FIG. 1 disassembled.

[0060] Referring to FIGS. 1 and 2, the scroll compressor according to the present embodiment may have a drive motor (120) forming a drive unit in the lower half of the casing (110), and a main frame (130), a fixed scroll (140), a pivoting scroll (150), and a back pressure chamber assembly (160) forming a compression unit on the upper side of the drive motor (120). The drive unit may be coupled to one end of a rotating shaft (125), and the compression unit may be coupled to the other end of the rotating shaft (125). Accordingly, the compression unit is connected to the drive unit by the rotating shaft (125) and operates by the rotational force of the drive unit.

[0061] Referring to FIG. 1, the casing (110) may include a cylindrical shell (111), an upper cap (112), and a lower cap (113).

[0062] The cylindrical shell (111) has a cylindrical shape with open upper and lower ends, and the aforementioned drive motor (120) and main frame (130) can be inserted and fixed into the inner surface. A refrigerant suction pipe (117), to be described later, can be penetrated and connected to the upper half of the cylindrical shell (111), for example, the upper side of the drive motor (120).

[0063] The upper cap (112) can be joined to cover the open upper end of the cylindrical shell (111), and the lower cap (113) can be joined to cover the open lower end of the cylindrical shell (111). Accordingly, the internal space of the casing (110) can be sealed.

[0064] An annular high-low pressure separator plate (114) can be inserted and connected between the cylindrical shell (111) and the upper cap (112). In other words, the outer side of the high-low pressure separator plate (114) is connected between the cylindrical shell (111) and the upper cap (112), and the inner side of the high-low pressure separator plate (114) can be connected in close contact with the back surface of the fixed scroll (140). Accordingly, the internal space of the casing (110) can be separated into a low-pressure section (110a) forming a suction space and a high-pressure section (110b) forming a discharge space, centered around the high-low pressure separator plate (114).

[0065] A refrigerant suction pipe (115) can be formed through the middle of the cylindrical shell (111) and a refrigerant discharge pipe (116) can be formed through the upper cap (112). Accordingly, the refrigerant suction pipe (115) can be connected to the low-pressure portion (110a) of the casing (110) forming the suction space, and the refrigerant discharge pipe (116) can be connected to the high-pressure portion (110b) of the casing (110) forming the discharge space.

[0066] Referring to FIG. 1, the drive motor (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) is fixed to the inner wall surface of a cylindrical shell (111) by hot press fitting, and the rotor (122) may be rotatably provided inside the stator (121).

[0067] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0068] The stator core (1211) is formed in a cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot press fitting. The stator coil (1212) is wound on the stator core (1211) and can be electrically connected to an external power source through a terminal (not shown) that is coupled through the casing (110).

[0069] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0070] The rotor core (1221) is formed in a cylindrical shape and can be rotatably inserted into the stator core (1211) at a predetermined gap. The permanent magnet (1222) can be embedded in the rotor core (1222) at a predetermined gap along the circumferential direction.

[0071] Additionally, a rotating shaft (125) can be press-fitted and coupled to the center of the rotor core (1221). An eccentric portion (1251) is provided at the top of the rotating shaft (125) so that a pivoting scroll (150), to be described later, can be coupled eccentrically. Accordingly, the rotational force of the drive motor (120) can be transmitted to the pivoting scroll (150) through the rotating shaft (125).

[0072] Additionally, an oil passage (1252) is formed by penetrating the interior of the rotating shaft (125) in the axial direction, and an oil pickup (126) for sucking up oil stored in the lower part of the casing (110) may be provided at the bottom of the rotating shaft (125) so as to be in communication with the oil passage (1252). Accordingly, the oil stored in the oil storage space (110c) of the casing (110) is pumped by the oil pickup and sucked up through the oil passage (1252), thereby lubricating the sliding surface.

[0073] Referring to FIGS. 1 and 2, the main frame (130) according to the present embodiment may include a main flange portion (131) and an axis support protrusion (132).

[0074] The main flange portion (131) can be fixed in close contact with the inner surface of the cylindrical shell (111). In this case, at least one oil recovery passage (not shown) spaced apart from the inner surface of the cylindrical shell (111) can be formed on the outer surface of the main flange portion (131). Accordingly, oil supplied between the main frame (130) and the rotating scroll (150) can be recovered into the oil storage space (110c) of the casing (110) through the oil recovery passage (not shown).

[0075] Additionally, a scroll fixing surface (1311) is formed on one side of the main flange portion (131), that is, on the edge of the upper surface facing the fixed scroll (140), and an Oldham ring supporting surface (1312) is formed on the inner side of the scroll fixing surface (1311), and a thrust supporting surface (1313) can be formed on the inner side of the Oldham ring supporting surface (1312).

[0076] The scroll fixing surface (1311) is a part where the fixed scroll (140) is seated and fixed, and can be formed in a stepped shape that is higher than the Oldham ring support surface (1312) and / or the thrust support surface (1313) by a predetermined height. Accordingly, a stepped surface is formed between the inner surface of the scroll fixing surface (1311) and the outer surface of the Oldham ring support surface (1312), and oil flowing into the Oldham ring support surface (1312) and / or the thrust support surface (1313) can be stored in a certain amount inside the scroll fixing surface (1311).

[0077] Although not illustrated in the drawing, the scroll fixing surface (1311) may be formed at the same height as the Oldham ring support surface (1312) and / or the thrust support surface (1313). In this case, the entire or most of the upper surface of the main flange portion (131) forms a flat plane, thereby allowing the main frame (130) to be easily formed.

[0078] The Oldham ring support surface (1312) is a part on which the Oldham ring (170), to be described later, is seated and slides, and can be formed flat. Accordingly, the Oldham ring (170) is seated on the Oldham ring support surface (1312) and slides smoothly, thereby suppressing the rotation of the rotary scroll (150).

[0079] A first key groove (1312a) into which the first key (172) of the Oldham ring (170) is slidably inserted may be formed on the Oldham ring support surface (1312). The first key groove (1312a) may be formed radially elongated to correspond to the first key. For example, the first key groove (1312a) may be formed by being recessed to a predetermined depth in the Oldham ring support surface (1312).

[0080] The thrust support surface (1313) is a portion on which the back pressure plate (162) of the back pressure chamber assembly (160), to be described later, is seated and slides, and can be formed flat like the Oldham ring support surface (1312). Accordingly, the back pressure plate (162) of the back pressure chamber assembly (160), to be described later, is supported axially on the thrust support surface (1313) and can perform a smooth pivoting motion.

[0081] The shaft support protrusion (132) extends from the center of the main flange portion (131) toward the drive motor (120), and a shaft support hole (1321) may be formed on the inner side of the shaft support protrusion (132) by penetrating both axial sides of the main flange portion (131). Accordingly, the main frame (130) can radially support a rotating shaft (125) inserted into the shaft support hole (1321).

[0082] Referring to FIG. 1, the fixed scroll (140) according to the present embodiment can be fixed to the main frame (130) with the pivoting scroll (150), which will be described later, in between. For example, the fixed scroll (140) may include a fixed plate portion (141), a fixed wrap (142), and a fixed side wall portion (143).

[0083] The fixed end plate (141) is formed in the shape of a disc and can be fixed laterally in the low-pressure section (110a) of the casing (110). A discharge port (1411) and a bypass hole (1412) can be formed through the center of the fixed end plate (141) in the axial direction. Accordingly, the refrigerant compressed in the compression chamber (V) can be discharged to the high-pressure section (110b), which is the discharge space, through the discharge port (1411), or discharged to the high-pressure section (110b) through the bypass hole (1412) before reaching the discharge port (1411).

[0084] The fixed wrap (142) can extend from the lower surface of the fixed plate section (141) toward the rotating scroll (150). The fixed wrap (142) can be formed in various shapes, such as an involute. For example, the fixed wrap (142) may be formed as a logarithmic spiral or as a plurality of arc curves.

[0085] However, if the fixed wrap (142) is formed as a logarithmic spiral, the pivot wrap (152) described later must also be formed as a logarithmic spiral, so the shape of the rotation shaft insertion part (153) described later is limited, and the stroke volume can be reduced at the same wrap height and end plate width.

[0086] The fixed wrap (142) according to the present embodiment may be formed such that the wrap curve is formed by connecting a plurality of arcs with different diameters and origins. Accordingly, the wrap thickness of the fixed wrap (142) may be formed differently along the wrap formation direction.

[0087] For example, in the fixed wrap (142) according to the present embodiment, the wrap thickness of the discharge end, which is towards the center, can be formed to be thicker than the wrap thickness of the suction end, which is towards the outermost end. Accordingly, the wrap strength at the discharge end of the fixed wrap (142), which receives a relatively high gas force, can be increased to suppress damage to the fixed wrap (142). In addition, the wrap curve of the fixed wrap (142) is formed wide so that the stroke volume can be expanded at the same wrap height and end plate width. The same applies to the swivel wrap (152) to be described later.

[0088] Additionally, the fixed wrap (142) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example is illustrated in which the wrap height of the fixed wrap (142) differs along the wrap formation direction of the fixed wrap (142). For example, in this embodiment, a fixed step surface (1421) is formed in the middle of the fixed wrap (142), so that the wrap height of the discharge end, which is towards the center with respect to the fixed step surface (1421), is formed lower than the wrap height of the suction end, which is towards the outermost edge. Accordingly, the wrap strength at the discharge end of the fixed wrap (142), which receives a relatively high gas force, is increased, thereby suppressing damage to the fixed wrap (142).

[0089] The fixed step surface (1421) can be formed at a position where the compression chamber communicates with the discharge port (1411) at the discharge start time (discharge start point) of the compression chamber (V) that starts discharge relatively earlier among the two compression chambers (V). The same applies to the pivoting step surface (1511) to be described later, which will be explained again later.

[0090] The fixed side wall portion (143) may be formed in an annular shape by extending axially from the edge of the compression surface of the fixed end plate portion (141) to surround the fixed wrap (142). One side of the fixed side wall portion (143) facing the main frame (130) may be placed on and fastened to the scroll support surface (1311) of the main frame (130). Accordingly, the fixed scroll (140) may be supported axially on the main frame (130) and fixed axially.

[0091] Referring to FIG. 1, the pivot scroll (150) according to the present embodiment may be coupled to the eccentric portion (1251) of the rotation axis (125) and provided between the main frame (130) and the fixed scroll (140). Specifically, the pivot scroll (150) may include a pivot plate portion (151), a pivot wrap (152), and a rotation axis insertion portion (153).

[0092] The pivot plate section (151) is formed in a roughly circular shape and can be received inside the scroll support surface (1311) of the main frame (130). A second key groove (151a) can be formed on one side of the pivot plate section (151), that is, on the edge of the lower surface (back side) facing the main frame (130), so that the second key (173) of the Oldham ring (170) can be inserted. Accordingly, the pivot plate section (151) can rotate inside the scroll support surface (1311) by means of the Oldham ring (170).

[0093] In this case, a first key receiving portion (hereinafter referred to as the key receiving protrusion) (1611) may be formed on the back surface of the pivot plate portion (151) and extend along the circumference of the second key groove (151a) and protrude toward the main frame (130). The key receiving protrusion (1611) may be inserted into the second key receiving portion (hereinafter referred to as the key receiving groove) (1621) of the back pressure plate (162) to be described later, so that the back pressure plate (162) is coupled to the pivot plate portion (151). The key receiving groove (1611) will be explained again later together with the plate receiving groove (161).

[0094] The upper surface (compression surface) of the pivot plate section (151) may be formed at a uniform height or partially at a different height. For example, if the pivot shaft insertion section (153) of the pivot plate section (151) extends only toward the main frame (130) from the rear surface of the pivot plate section (151) facing the main frame (130), the entire pivot plate section (151) may be formed at a uniform height. However, if the pivot shaft insertion section (153) is formed to penetrate the pivot plate section (151) and overlap radially with the pivot wrap (152) to be described later, the height of the pivot plate section (151) may be partially, that is, higher in the part where the pivot shaft insertion section (153) is formed. In this embodiment, an example is illustrated in which the height of the pivot plate section (151) at the center is formed higher than the height at the edge. Accordingly, the upper surface (compression surface) of the rotating plate section (151) can be formed such that the discharge side height is higher than the suction side height, centered on the rotating step surface (1511). Through this, the rotation shaft insertion section (153), which will be described later, protrudes in a direction toward the fixed plate section (141), thereby shortening the distance between the first point of application where rotational force acts on the rotating scroll (150) and the second point of application where compressive force acts, and thus reducing the overturning moment of the rotating scroll (150).

[0095] The pivoting step surface (1511) connects the outer surface at the discharge end of the pivoting wrap (152) and the inner surface of the pivoting wrap (152) facing it in a radial direction, and, as with the fixed step surface (1421) mentioned earlier, can be formed at a position where the corresponding compression chamber (V) communicates with the discharge port (1411) at the discharge start time (discharge start point) of the compression chamber (V) adjacent to the discharge port (1411) among the two compression chambers.

[0096] In other words, as the discharge port (1411) is formed as an elongated irregular ellipse, at the point where the rotating step surface (1511) and the fixed step surface (1421) are separated, one end of the rotating step surface (1511) (specifically, the outer side of the rotating wrap) can be formed to be connected to a part of the discharge port (1411) or overlap in the axial direction. Accordingly, at the moment when the rotating step surface (1511) is separated from the fixed step surface (1421) during the rotational movement of the rotating scroll (150), both compression chambers (V) are connected to each other, and at the same time, one compression chamber (V) is connected to the discharge port (1411). Then, even if both compression chambers (V) are connected, the refrigerant in both compression chambers (V) moves to the discharge port (1411) and is discharged together, thereby suppressing compression loss in both compression chambers (V).

[0097] Additionally, on one side of the rotating plate section (151), that is, on the back side of the rotating plate section (151) facing the main frame (130), a plate receiving groove (161) is formed to form a back pressure chamber (160a) by inserting a back pressure plate (162), which will be described later, so as to slide in the axial direction of the rotation axis (125). A back pressure passage (164) can be formed inside the rotating plate section (151) to communicate between the compression chamber (V) and the plate receiving groove (161). Accordingly, the back pressure chamber assembly (160), which will be described later, is integrally provided with the rotating scroll, and the weight of the rotating scroll (150) is reduced to increase compression efficiency. At the same time, the back pressure chamber assembly (160) can rotate together with the rotating scroll (150) to stably form back pressure on the rotating scroll (150). The plate receiving groove (161), the back pressure plate (162), and the back pressure passage (164) each form part of the back pressure chamber assembly (160), and this will be explained again later.

[0098] The pivoting wrap (152) can be extended toward the fixed scroll (140) from the upper surface (compression surface) of the pivoting plate section (151). Accordingly, the pivoting wrap (152) can be engaged with the fixed wrap (142) to form two pairs of compression chambers (V).

[0099] The pivoting wrap (152) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (142). For example, the pivoting wrap (152) may be formed as a logarithmic spiral or as a plurality of arc curves.

[0100] However, as previously explained in the fixed wrap (142), when the pivot wrap (152) is formed as a logarithmic spiral, not only is the shape of the rotation shaft insertion part (153) limited, but the stroke volume can also be reduced at the same wrap height and end plate width. Accordingly, the pivot wrap (152) according to the present embodiment can be formed such that the wrap curve is formed by connecting multiple arcs with different diameters and origins, similar to the fixed wrap (142). Accordingly, the pivot wrap (152) can be formed such that the wrap thickness varies along the wrap formation direction, similar to the fixed wrap (142).

[0101] For example, in the present embodiment, the wrapping thickness of the discharge end, which is towards the center, of the swirling wrap (152) may be formed to be thicker than the wrapping thickness of the suction end, which is towards the outermost end. Accordingly, the wrapping strength at the discharge end of the swirling wrap (152), which receives a relatively high gas force, can be increased to suppress damage to the swirling wrap (152). In addition, the wrapping curve of the fixed wrap (142) is formed wide so that the stroke volume can be expanded at the same wrapping height and end plate width.

[0102] The swivel wrap (152) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example is shown where the wrap height of the swivel wrap (152) is different along the wrap formation direction. For example, according to this embodiment, the wrap height of the swivel wrap (152) may be formed such that the wrap height of the discharge end, which is towards the center with respect to the swivel step surface (1511), is lower than the wrap height of the suction end, which is towards the outermost edge. Accordingly, the wrap strength at the discharge end of the swivel wrap (152), which receives a relatively high gas force, is increased, thereby suppressing damage to the fixed wrap (142).

[0103] The rotation shaft insertion part (153) is a part to which the eccentric part (1251) of the rotation shaft (125) is coupled. It is formed in a cylindrical shape and may be equipped with an eccentric bearing made of a bushing bearing on its inner surface. For convenience, the bushing bearing is defined as the inner surface of the rotation shaft insertion part (153) in the following description. Accordingly, the inner surface of the rotation shaft insertion part (153) can be understood as substantially referring to the inner surface of the bushing bearing.

[0104] The rotational shaft insertion part (153) may be formed to be located inside the pivoting wrap (152). For example, the inner surface of the rotational shaft insertion part (153) may be formed at a position that overlaps with the discharge end of the pivoting wrap (152) when projected in the axial direction. In other words, the outer surface of the rotational shaft insertion part (153) may be formed to be located on the same circle as the virtual circle connecting the outer surface at the discharge end of the pivoting wrap (152). Accordingly, the inner surface around the discharge end of the pivoting wrap (152) is located inside the outer surface of the rotational shaft insertion part (153) as previously described, that is, at the front end surface (not indicated) of the rotational shaft insertion part (153). Then, the rotational shaft insertion part (153) is formed to overlap radially with the pivot wrap (152), and the bearing area of ​​the rotational shaft insertion part (153) is secured wide to stably support the pivot scroll (150), while simultaneously forming a compression chamber (V) on the front end surface of the rotational shaft insertion part (153).

[0105] FIG. 3 is a perspective view showing a back pressure chamber assembly according to the present embodiment in a broken state, FIG. 4 is a plan view showing the back pressure chamber assembly in FIG. 2, FIG. 5 is a cross-sectional view along "V-V" of FIG. 3, FIG. 6 and FIG. 7 are cross-sectional views showing the operation of the back pressure chamber assembly according to the present embodiment, FIG. 6 showing the stop and / or start, FIG. 7 showing the normal operation, respectively.

[0106] Referring again to FIGS. 1 and 2, the back pressure chamber assembly (160) according to the present embodiment may be provided on one side of the rotating scroll (150), that is, on the back side (or compression back side) of the rotating plate portion (151) facing the main frame (130). Accordingly, the back pressure of the back pressure chamber (160a) (more precisely, the force of the back pressure acting on the back pressure chamber) acts on the rotating scroll (150). In other words, the rotating scroll (150) is pushed in the direction toward the fixed scroll (140) by the back pressure and seals the space between the two compression chambers (V).

[0107] Referring to FIGS. 3 to 5, the back pressure chamber assembly (160) may include a plate receiving groove (161), a back pressure plate (162), a sealing member (163), and a back pressure passage (164). The plate receiving groove (161) is a space in which the back pressure chamber (160a) is formed, the back pressure plate (162) is a member that varies the volume of the back pressure chamber (160a), the sealing member (163) is a member that seals the back pressure chamber (160a), and the back pressure passage (164) is a passage that supplies the refrigerant (and oil) of the compression chamber (V) to the back pressure chamber (160a). Accordingly, the back pressure plate (162) forming the back pressure chamber assembly (160) is inserted into the rotating scroll (150) and rotates together with the rotating scroll (150) while moving along the axial direction, thereby pressing the rotating scroll (150) toward the fixed scroll (140).

[0108] Referring to FIGS. 3 to 5, the plate receiving groove (161) according to the present embodiment may be formed to be recessed to a predetermined depth on the back surface of the pivoting plate portion (151) facing the main frame (130), as previously described. In other words, the plate receiving groove (161) may be formed such that the inner wall portion (161a) and the outer wall portion (161b) are spaced apart by a predetermined radial distance. For example, the inner wall portion (161a) of the plate receiving groove (161) may be formed such that its surface is spaced apart from the inner surface of the rotation shaft insertion portion (153) by a sealing distance, and is formed to be as close as possible to the inner surface of the rotation shaft insertion portion (153). The outer wall portion (161b) of the plate receiving groove (161) can be formed such that its surface is spaced apart from the outer surface of the rotating plate portion (151) by a sealing distance, and is as close as possible to the outer surface of the rotating plate portion (151). Accordingly, the radial width of the plate receiving groove (161) can be formed as wide as possible while reducing the weight of the rotating scroll (150) as much as possible. Through this, the motor input is lowered to improve energy efficiency, and at the same time, the area of ​​the back pressure chamber (160a) is increased, thereby stably supporting the rotating scroll (150) and improving compression efficiency.

[0109] The plate receiving groove (161) is formed in an annular shape, with the inner wall portion (161a) and the outer wall portion (161b) each forming a circular shape. In the outer wall portion (161b), a scroll-side key receiving portion (hereinafter referred to as a key receiving protrusion) (1611) for receiving the second key (173) of the Oldham ring (170) may be formed. For example, the key receiving protrusion (1611) may protrude axially toward the back pressure plate (162) from the back pressure surface (161c) of the plate receiving groove (161), and may be formed to be radially recessed toward the inner wall portion (161a) from the outer wall portion (161b) of the plate receiving groove (161). Accordingly, the key receiving protrusion (1611) can be inserted into the key receiving protrusion (1611) of the back pressure plate (162) to be described later, and coupled to restrain the back pressure plate (162) in the radial and circumferential directions.

[0110] Additionally, a scroll-side sealing projection (1612) may be formed in an annular shape between the inner wall portion (161a) and the outer wall portion (161b) of the plate receiving groove (161). A third sealing member (1633) may be provided between the scroll-side sealing projection (1612) and the intermediate sealing projection (1623c) of the back pressure plate (162) to be described later. Accordingly, the third sealing member (1633) tightly seals the first back pressure chamber (160a1) and the second back pressure chamber (160a2) to be described later, thereby separating them into multiple back pressure chambers (160a1) and (160a2) having different pressures.

[0111] In this case, the scroll-side sealing projection (1612) can be inserted into the plate-side sealing groove (1622) of the back pressure plate (162) to be described later. For example, the axial length of the scroll-side sealing projection (1612) can be formed such that at least a portion of the scroll-side sealing projection (1612) remains inside the plate-side sealing groove (1622) to be described later, even if the back pressure plate (162) is pushed and moved toward the main frame (130). Accordingly, even if the back pressure plate (162) moves axially during the operation of the compressor, the scroll-side sealing projection (1612) can be prevented from being dislodged from the plate-side sealing groove (1622) to be described later, and the third sealing member (1633) can be prevented from getting stuck between the scroll-side sealing projection (1612) and the plate-side sealing groove (1622) to be described later. Through this, the back pressure plate (162) can be smoothly raised and lowered inside the plate receiving groove (161) to form a thrust surface with the main frame (130) while stably forming the back pressure chamber (160a).

[0112] Although not illustrated in the drawing, the sealing protrusion and the sealing groove may be formed on opposite sides. For example, a sealing protrusion may be formed on the back pressure plate (162) and a sealing groove may be formed on the plate receiving groove (161). This is formed on one side in the radial direction of the intermediate sealing protrusion (1623c) and the intermediate sealing groove (1613c) to be described later, and in this case, the dimensions of the sealing protrusion and the sealing groove may be formed in the same way as in the example described above.

[0113] Additionally, a plurality of sealing grooves (1613a), (1613b), and (1613c) may be formed on the back pressure surface (161c) of the plate receiving groove (161) so that the sealing protrusions (1623a), (1623b), and (1623c) of the back pressure plate (162), which will be described later, are respectively inserted therein. For example, an inner sealing groove (1613a) may be formed on the inner side of the plate receiving groove (161), an outer sealing groove (1613b) on the outer side, and an intermediate sealing groove (1613c) may be formed between the inner sealing groove (1613a) and the outer sealing groove (1613b). Each of these sealing grooves (1613a)(1613b)(1613c) can be formed to correspond to each sealing projection (1623a)(1623b)(1623c) to be described later. Accordingly, the sealing member (1631)(1632)(1633) to be described later can be prevented from getting stuck between the plate receiving groove (161) and the back pressure plate (162).

[0114] Referring to FIGS. 3 to 5, the back pressure plate (162) according to the present embodiment may be made of a material lighter than the slewing scroll, such as engineering plastic. Accordingly, the weight of the slewing scroll (150) including the back pressure plate (162) is reduced, thereby reducing the motor input and improving energy efficiency.

[0115] Specifically, the back pressure plate (162) may be formed in an annular shape so as to be inserted into the plate receiving groove (161) provided on the back surface of the rotating scroll (150) in the axial direction of the rotation axis (125). For example, the inner surface of the back pressure plate (162) may be formed in a circular shape so as to make sliding contact with the inner wall portion (161a) of the plate receiving groove (161), and the outer surface of the back pressure plate (162) may be formed in a circular shape so as to make sliding contact with the outer wall portion (161b) of the plate receiving groove (161). However, while the outer surface of the back pressure plate (162) is formed in a circular shape overall, the plate-side key receiving portion (hereinafter, key receiving groove portion) (1621) may be formed to be recessed in the radial direction so as to insert the key receiving protrusion (1611) of the plate receiving groove (161). Accordingly, the outer surface of the back pressure plate (162) can be formed in a shape that is radially indented from both sides toward the inner surface when projected in the axial direction.

[0116] In this case, a plurality of sealing protrusions (1623a), (1623b), and (1623c) may be formed spaced apart from each other along the radial direction between the inner surface and the outer surface of the back pressure plate (162). For example, on one side (hereinafter referred to as the back pressure surface) (162a) of the back pressure plate (162) facing the pivoting plate portion (151) in the axial direction, an inner sealing protrusion (1623a) may be formed on the inner surface side of the back pressure plate (162), an outer sealing protrusion (1623b) may be formed on the outer surface side of the back pressure plate (162), and an intermediate sealing protrusion (1623c) may be formed between the inner sealing protrusion (1623a) and the outer sealing protrusion (1623b) at a predetermined radial interval from each other. Accordingly, a high-pressure side back pressure chamber (hereinafter, first back pressure chamber) (160a1) can be formed between the inner sealing projection (1623a) and the middle sealing projection (1623c), and a low-pressure side back pressure chamber (hereinafter, second back pressure chamber) (160a2) can be formed between the outer sealing projection (1623b) and the middle sealing projection (1623c).

[0117] In addition, in this case, these sealing protrusions (1623a), (1623b), and (1623c) are each formed as annular shapes having the same height, but the inner sealing protrusion (1623a) and the middle sealing protrusion (1623c) are formed as circular shapes, whereas the outer sealing protrusion (1623b) can be formed as a circular shape bent along the outer surface of the back pressure plate (162) including the key receiving groove (1621). In other words, the inner sealing protrusion (1623a) and the middle sealing protrusion (1623c) are formed to be completely separated from each other in the radial direction, whereas the outer sealing protrusion (1623b) and the middle sealing protrusion (1623c) are formed to be separated in the radial direction overall, but connected to each other in some parts.

[0118] For example, a connecting projection (1623d) is formed extending radially toward the intermediate sealing projection (1623c) from the portion forming the key receiving groove (1621) among the outer sealing projections (1623b), so that the outer sealing projection (1623b) and the intermediate sealing projection (1623c) can be partially connected to each other. Accordingly, a first back pressure chamber (160a1) is formed in a circular shape between the inner sealing projection (1623a) and the intermediate sealing projection (1623c), while a second back pressure chamber (160a2) can be formed in an arc shape on both sides between the inner sealing projection (1623a) and the intermediate sealing projection (1623c), with the key receiving groove (1621) in between.

[0119] In this case, both second back pressure chambers (160a2) may be connected to the compression chamber by their respective back pressure passages (not shown), or they may be connected to the compression chamber (V) together by a single back pressure passage (164). This embodiment illustrates the latter case, that is, an example in which both second back pressure chambers (160a2) are connected to the same compression chamber (V) by sharing a single back pressure passage (164). In other words, the two second back pressure chambers (160a2) can be connected to each other as the connecting projection (1623d) connecting the outer sealing projection (1623b) and the middle sealing projection (1623c) is spaced apart from the back pressure surface (161c) of the plate receiving groove (161). Accordingly, the second back pressure chambers (160a2) on both sides can be connected together to the low-pressure side compression chamber (V2) by a single back pressure passage (164).

[0120] Additionally, a portion of each sealing projection (1623a)(1623b)(1623c) can be inserted into each sealing groove (1613a)(1613b)(1613c) provided in the plate receiving groove (161) described above. In other words, the end of the inner sealing projection (1623a) can be inserted into the outer sealing groove (1613a), the end of the outer sealing projection (1623b) into the outer sealing groove (1613b), and the end of the middle sealing projection (1623c) into the middle sealing groove (1613c).

[0121] In this case, the axial length of each sealing projection (1623a)(1623b)(1623c) can be formed such that even if the back pressure plate (162) is pushed toward the main frame (130), at least a portion of each sealing projection (1623a)(1623b)(1623c) can remain inside each sealing groove (1613a)(1613b)(1613c). Accordingly, when the back pressure plate (162) moves axially relative to the pivot scroll (150) during operation of the compressor, it is possible to prevent each sealing projection (1623a)(1623b)(1623c) from being disengaged from each sealing groove (1613a)(1613b)(1613c), and it is possible to prevent each sealing member (1631)(1632)(1633), which will be described later, from getting stuck between each sealing projection (1623a)(1623b)(1623c) and each sealing groove (1613a)(1613b)(1613c). Through this, as previously explained, the back pressure plate (162) can be smoothly raised and lowered inside the plate receiving groove (161) to stably form a thrust surface with the main frame (130), while simultaneously tightly sealing the back pressure chamber (160a) to form it stably.

[0122] Referring to FIGS. 3 to 5, the sealing member (163) according to the present embodiment is provided between the plate receiving groove (161) and the back pressure plate (162) to seal the back pressure chamber (160a), and may include an inner sealing member (1631), an outer sealing member (1632), and an intermediate sealing member (1633). The inner sealing member (1631) is provided on the inner side of the back pressure chamber (160a), the outer sealing member (1632) is provided on the outer side of the back pressure chamber (160a), and the intermediate sealing member (1633) may be provided in the middle of the back pressure chamber (160a). Accordingly, as previously explained, a first back pressure chamber (160a1) can be formed between the inner sealing member (1631) and the intermediate sealing member (1633), and a second back pressure chamber (160a2) can be formed between the outer sealing member (1632) and the intermediate sealing member (1633).

[0123] For example, the inner sealing member (1631) may be provided such that at least a portion of it is located closer to the center than the pivoting step surface (1511) when projected axially, and the intermediate sealing member (1633) may be provided such that at least a portion of it is located closer to the center than the pivoting step surface (1511) when projected axially. Accordingly, at least a portion of the first back pressure chamber (160a1) may be located closer to the center than the pivoting step surface (1511) when projected axially, thereby overlapping axially with the compression chamber (e.g., the final compression chamber connected to the discharge port) (V1) which forms a relatively high pressure. Through this, the center side of the pivoting scroll (150) receiving a relatively high compression force among the pivoting scrolls (150) can be stably supported, thereby effectively blocking leakage between the compression chambers (V).

[0124] Additionally, the outer sealing member (1632) may be provided to be positioned outside the pivoting step surface (1511) when projected axially. Accordingly, at least a portion of the second back pressure chamber (160a2) may be positioned outside the pivoting step surface (1511) when projected axially, so that it may overlap with a compression chamber (e.g., a compression chamber forming an intermediate pressure) (V2) that forms a relatively low pressure. Through this, the edge of the pivoting scroll (150) that receives a relatively low compression force among the pivoting scrolls (150) can be supported with an appropriate back pressure, thereby effectively suppressing the fixed scroll (140) and the pivoting scroll (150) from being in close contact with each other.

[0125] Specifically, the inner sealing member (1631) is provided between the inner wall portion (161a) of the plate receiving groove (161) and the inner sealing projection (1623a) facing it in a radial direction, the outer sealing member (1632) is provided between the outer wall portion (161b) of the plate receiving groove (161) and the outer sealing projection (1623b) facing it in a radial direction, and the intermediate sealing member (1633) can be provided between the scroll-side sealing projection (1612) and the intermediate sealing projection (1623c) facing it in a radial direction. Accordingly, the inner sealing member (1631) separates the inner side of the first back pressure chamber (160a1), and the outer sealing member (1632) separates the outer side of the second back pressure chamber (160a2) from the internal space (more precisely, the low-pressure portion forming the suction space) (110a) of the casing (110), and the intermediate sealing member (1633) can separate the first back pressure chamber (160a1) and the second back pressure chamber (160a2).

[0126] Here, the inner sealing member (1631), the outer sealing member (1632), and the intermediate sealing member (1633) are each formed as elastic O-rings, and the axial diameter of each sealing member (1631)(1632)(1633) may be formed smaller than the axial height of each sealing projection (1623a)(1623b)(1623c). Accordingly, when operating the compressor, each back pressure chamber (160a1)(160a2) can be effectively sealed, and at the same time, the detachment of each sealing projection (1623a)(1623b)(1623c) from each sealing groove (1613a)(1613b)(1613c) can be prevented.

[0127] Referring to FIGS. 3 to 5, the back pressure passage (164) according to the present embodiment is connected between the compression chamber (V) and the back pressure chamber (160a) and may include a first back pressure passage (1641) and a second back pressure passage (1642). The first back pressure passage (1641) may be provided between the high-pressure side compression chamber (V1) and the first back pressure chamber (160a1), and the second back pressure passage (1642) may be provided between the low-pressure side compression chamber (V2) and the second back pressure chamber (160a2).

[0128] Specifically, the first back pressure passage (1641) may be connected to the first back pressure chamber (160a1) by passing through the pivot plate section (more precisely, around the rotation shaft insertion section) (151) in the compression chamber (V1) that forms the discharge pressure. In this case, the first back pressure passage (1641) may be formed axially, or it may be formed by being inclined or bent. In the former case, the processing of the first back pressure passage (1641) is easy, so manufacturing costs can be reduced, and the path length of the first back pressure passage (1641) can be minimized to quickly form back pressure in the back pressure chamber (160a). In the latter case, the inlet position and / or outlet position of the first back pressure passage (1641) can be appropriately adjusted, thereby increasing the design freedom for the first back pressure passage (1641) and / or the first back pressure chamber (160a1). This embodiment illustrates the former case, that is, an example in which the first back pressure passage (1641) is formed in the axial direction.

[0129] In this case, the inlet of the first back pressure passage (1641) may be connected to the compression chamber (V1) that forms the discharge pressure, and the outlet of the first back pressure passage (1641) may be connected to the first back pressure chamber (160a1). For example, the inlet of the first back pressure passage (1641) may be formed close to the inner wall surface of the swirling wrap (152) that forms the discharge pressure, and the outlet of the first back pressure passage (1641) may be connected close to the first back pressure chamber (160a1) from the inner sealing groove (1613a). Accordingly, the outlet of the first back pressure passage (1641) is positioned as close as possible to the first back pressure chamber (160a1), thereby allowing the first back pressure passage (1641) to be formed in an axial direction while preventing blockage of the first back pressure passage (1641).

[0130] In addition, in this case, the radial width of the inner sealing groove (1613a) may be formed to be larger than the radial width of the inner sealing projection (1623a), or a separate communication groove (not shown) may be formed on the inner wall surface of the inner sealing groove (1613a). Accordingly, the first back pressure passage (1641) can be formed axially, while the high-pressure side compression chamber (V1) and the first back pressure chamber (160a1) can be smoothly connected.

[0131] The second back pressure passage (1642) may be connected to the second back pressure chamber (160a2) by passing through the pivot plate section (151) in the compression chamber (V2), which forms an intermediate pressure between the suction pressure and the discharge pressure. In this case, the second back pressure passage (1642) may be formed to be independently connected to both second back pressure chambers (160a2), or a single second back pressure passage (1642) may be formed to be connected to both second back pressure chambers (160a2) in common. In the former case, the back pressure path between each second back pressure chamber (160a2) and the compression chamber (V2) is minimized so that the back pressure of the back pressure chamber (160a) can be formed quickly, and in the latter case, the processing of the second back pressure passage (1642) can be simplified so that manufacturing costs can be lowered. This embodiment illustrates the latter case, that is, an example in which one second back pressure passage (1642) is shared and connected to both second back pressure chambers (160a2).

[0132] Specifically, the inlet of the second back pressure passage (1642) is connected to the compression chamber (V2) that forms the intermediate pressure as described above, and the outlet of the second back pressure passage (1642) can be formed to be connected to either of the two second back pressure chambers (160a2).

[0133] In this case, as described above, since both second back pressure chambers (160a2) are connected to each other through the upper surface of the connecting projection (1623d) connecting the outer sealing projection (1623b) and the intermediate sealing projection (1623c), even if the second back pressure passage (1642) is connected to one of the second back pressure chambers (160a2), both second back pressure chambers (160a2) are connected to each other and can form the same intermediate back pressure. Accordingly, one second back pressure passage (1642) can be shared by multiple second back pressure chambers (160a2), thereby reducing the manufacturing cost for the second back pressure passage (1642).

[0134] In the drawing, the unexplained symbol 118 is a subframe, and 171 is the ring body of the Oldham ring.

[0135] The effects of the scroll compressor according to the above embodiment are as follows.

[0136] That is, when power is applied to the drive motor (120) and rotational force is generated, the pivoting scroll (150), which is eccentrically coupled to the rotation shaft (125), pivots relative to the fixed scroll (140) by the Oldham ring (170). At this time, two pairs of compression chambers (V) that move continuously are formed between the fixed scroll (140) and the pivoting scroll (150).

[0137] Then, as the rotating scroll (150) moves from the intake port (or intake chamber) (1411) toward the discharge port (or discharge chamber) (1412), the volume of both compression chambers (V) gradually decreases.

[0138] Then, 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 immediately sucked into and compressed in each suction pressure chamber (not labeled) forming both compression chambers (V), while the remaining refrigerant moves toward the drive motor (120) to cool the drive motor (120) and is then sucked into the suction pressure chamber (not labeled) together with other refrigerants.

[0139] Then, this refrigerant is compressed while moving along the path of both compression chambers (V). This refrigerant is discharged from the final compression chamber to the high-pressure section (110b) of the casing (110) through the discharge port (1411) of the fixed scroll (140), and this refrigerant is discharged to the outside of the compressor through the refrigerant discharge pipe (116).

[0140] At this time, as shown in FIGS. 6 and 7, a portion of the refrigerant compressed in the compression chamber (V) moves to the back pressure chamber (160a) of the back pressure chamber assembly (160) through the back pressure passage (164). In other words, before reaching the discharge port (1411), a portion of the refrigerant compressed in the compression chamber (V) moves to the second back pressure chamber (160a2) through the second back pressure passage (1642) in the low-pressure side compression chamber (V2) that forms an intermediate pressure, and to the first back pressure chamber (160a1) through the first back pressure passage (1641) in the high-pressure side compression chamber (V1) that forms a discharge pressure. Accordingly, the first back pressure chamber (160a1) forms a discharge pressure and the second back pressure chamber (160a2) forms an intermediate pressure, respectively, and pushes the back pressure plate (162) toward the main frame (130).

[0141] Then, the first back pressure chamber (160a1) forms a back pressure of the discharge pressure, thereby supporting the center side of the rotating scroll (150) with a high back pressure. Accordingly, as the center side of the rotating scroll (150) is closely attached to the fixed scroll (140), it becomes possible to effectively block the leakage of the refrigerant from the high-pressure side compression chamber (V1) to the low-pressure side compression chamber (V2).

[0142] In addition, the second back pressure passage (1642) connected to the second back pressure chamber (160a2) can be connected to a compression chamber (V2) having a relatively low intermediate pressure among the compression chambers forming an intermediate pressure. Accordingly, the back pressure applied to the outer side of the rotating scroll (150) is appropriately reduced so that the outer side of the rotating scroll (150) is supported by a back pressure of a relatively low intermediate pressure, thereby preventing the fixed scroll (140) and the rotating scroll (150) from being excessively in close contact.

[0143] In this way, as the back pressure chamber assembly (160) is provided between the main frame (130) and the rotating scroll (150), the number of parts and / or assembly work of the back pressure chamber assembly (160) can be reduced. Through this, the number of parts of the back pressure chamber assembly (160) can be reduced, thereby increasing the compression efficiency of the scroll compressor while lowering manufacturing costs.

[0144] In addition, as the back pressure chamber assembly (160) is inserted into and coupled with the rotating scroll (150), even if the movement of the rotating scroll (150) is unstable, the refrigerant in the back pressure chamber (160a) can be prevented from leaking into the low-pressure section (110a) of the casing (110). Through this, the refrigerant in the back pressure chamber (160a) can be prevented from heating the suction refrigerant in the low-pressure section (110a), thereby preventing a decrease in compression efficiency due to suction loss.

[0145] In addition, the back pressure plate (162) forming the back pressure chamber assembly (160) is made of a material lighter than the rotating scroll (150) and is inserted into the plate receiving groove (161) of the rotating scroll (150) to be combined, thereby reducing the weight of the rotating scroll (150). Through this, the number of parts and / or assembly costs forming the back pressure chamber assembly (160) are reduced, thereby reducing manufacturing costs, while the motor input is lowered, which can improve energy efficiency.

[0146] In addition, as the back pressure chamber assembly (160) forming the back pressure chamber (160a) is provided on the rotating scroll (150), the actual back pressure chamber (160a) area can be secured as wide as possible. Through this, the back pressure area supporting the rotating scroll (150) is expanded, allowing the rotating scroll (150) to be supported stably.

[0147] In addition, as the back pressure chamber (160a) is connected to the compression chamber (V1) that forms the discharge pressure as well as the compression chamber (V2) that forms the intermediate pressure, the back pressure on the discharge side can be formed high while the back pressure on the intermediate pressure side can be lowered. Through this, leakage between the compression chambers on the discharge side can be effectively suppressed, and excessive contact between the scrolls on the suction side can be suppressed, thereby further increasing the compression efficiency of the scroll compressor.

[0148] In addition, even if the back pressure chamber assembly (160) is provided on the rotating scroll (150) and the sealing member (163) forming the back pressure chamber assembly (160) seals the back pressure chamber (160a), the leakage of the refrigerant in the back pressure chamber (160a) to the low-pressure section (110a) of the casing (110) can be suppressed even if the movement of the rotating scroll (150) is unstable. Through this, the refrigerant in the back pressure chamber (160a) is suppressed from heating the suction refrigerant in the low-pressure section (110a), thereby suppressing the decrease in compression efficiency due to suction loss.

[0149] Additionally, as the rotational shaft insertion part (153) is formed to overlap radially with the rotational wrap (152), and a part of the rotational wrap (152) is extended on the front end surface of the rotational shaft insertion part (153), a compression chamber (V) can also be formed in the center of the rotational scroll (or fixed scroll) (150). Through this, the rotational shaft insertion part (153) is extended toward the rotational wrap (152), and the compression cycle of the compression chamber (V) is lengthened, thereby increasing the compression ratio and improving volumetric efficiency. At the same time, the wrap height at the discharge end of the rotational wrap (152) is lowered and the wrap thickness is increased, thereby increasing the wrap strength of the rotational wrap (152) and suppressing wrap breakage. The same applies to the fixed wrap (142).

[0150] Meanwhile, other embodiments of the back pressure chamber assembly are as follows.

[0151] That is, in the above-described embodiment, the back pressure chamber is sealed to the internal space of the casing, but in some cases, the back pressure chamber may be in communication with the internal space of the casing.

[0152] FIG. 8 is a cross-sectional view showing another embodiment of a back pressure chamber assembly, and FIG. 9 is a plan view showing the bottom surface of a back pressure plate in the back pressure chamber assembly of FIG. 8.

[0153] Referring again to FIGS. 1 and 2, the back pressure assembly (160) according to the present embodiment is provided on one side of the pivot scroll (150) facing the main frame (130), and the basic configuration of the back pressure assembly (160) and the resulting effects are almost identical to the previously described embodiment. For example, a plate receiving groove (161) forming part of the back pressure chamber assembly (160) is formed as a recess on the back surface of the pivoting plate section (151) facing the main frame (130), and a back pressure plate (162) that forms a back pressure chamber (160a) together with the plate receiving groove (161) is slidably inserted into the plate receiving groove (161). A plurality of sealing members (163) are provided between the plate receiving groove (161) and the back pressure plate (162) to seal the back pressure chamber (160a), and a back pressure passage (164) that connects the compression chamber (V) and the back pressure chamber (160a) can be formed in the pivoting scroll (150). Accordingly, the back pressure chamber assembly (160) has a large back pressure area as in the above-described embodiment and can suppress refrigerant leakage in the back pressure chamber (160a). This is replaced by the description of the aforementioned embodiments.

[0154] Additionally, an Oldham ring (170) is provided between the main frame (130) and the pivot scroll (150), and a key receiving protrusion (1611) is formed on the back pressure surface (161c) of the plate receiving groove (161) facing the main frame (130) to receive the second key (173) of the Oldham ring (170), and a key receiving groove (1621) into which the key receiving protrusion (1611) is inserted may be formed on the back pressure plate (162). Accordingly, the key receiving protrusion (1611) and the key receiving groove (1621) are constrained to each other in the radial and circumferential directions, so that the back pressure plate (162) can be coupled to the pivot scroll (150). This is also replaced by the description of the previously mentioned embodiment.

[0155] However, as shown in FIGS. 8 and 9, in this embodiment, a discharge passage (165) may be further formed in the back pressure plate (162) which forms part of the back pressure chamber assembly (160). In other words, a discharge hole (1651) is formed in the back pressure plate (162) that penetrates from the back pressure surface (162a) where the back pressure chamber (160a) is provided to the thrust surface (162b) on the opposite side, and a discharge groove (1652) and a discharge guide groove (1653) may be formed in the thrust surface (162b) of the back pressure plate (162) that are in communication with the discharge hole (1651) and are recessed to a predetermined depth.

[0156] In this case, the discharge hole (1651) can be formed to communicate with the first back pressure chamber (160a1), which is relatively high pressure. Accordingly, it is possible to prevent the back pressure of the first back pressure chamber (160a1) from rising excessively and the rotating scroll (150) from being excessively pressed against the fixed scroll (140).

[0157] The discharge groove (1652) may be formed in an annular shape to accommodate the outlet end of the discharge hole (1651). The discharge groove (1652) may be formed wider than the cross-sectional area of ​​the discharge hole (1651). Accordingly, the refrigerant flowing into the discharge groove (1652) through the discharge hole (1651) acts as a kind of gas bearing, lubricating the thrust surface with the main frame (130) and reducing friction loss.

[0158] The discharge guide groove (1653) may be connected to the outer surface of the discharge groove (1652) and extend to the outer surface of the back pressure plate (162). For example, the discharge guide groove (1632) may be extended along the circumference of the discharge groove (1652) to surround the discharge groove (1652). The cross-sectional area of ​​the discharge guide groove (1653) may be smaller than the cross-sectional area of ​​the discharge groove (1652), for example, approximately equal to or smaller than the cross-sectional area of ​​the discharge hole (1651). Accordingly, the high-pressure refrigerant discharged from the first back pressure chamber (160a1) may be depressurized as it passes through the discharge guide groove (1653) and discharged to the low-pressure portion (110a) of the casing (110). Through this, the specific volume of the suction refrigerant may be suppressed from rising due to the high-pressure refrigerant discharged from the back pressure chamber (160a).

[0159] In the case where a discharge passage (165) is formed in the back pressure plate (162) as described above, the pressure in the back pressure chamber (160a) formed between the back pressure plate (162) and the rotating scroll (more precisely, the plate receiving groove) (150) is suppressed from rising excessively, thereby reducing friction loss between the rotating scroll (150) and the fixed scroll (140) and / or between the rotating scroll (more precisely, the back pressure plate) (150) and the main frame (130).

[0160] Although not illustrated in the drawing, a back pressure control valve (not shown) may be provided in the middle of the discharge passage (165). For example, a back pressure control valve (not shown) may be further provided in the middle or at the outlet side of the discharge passage (165). Accordingly, when the back pressure of the back pressure chamber (160a) is higher than a set arbitrary pressure, the discharge passage (165) opens, allowing the refrigerant in the back pressure chamber (160a) to be discharged to the outside of the back pressure chamber (160a). Through this, the back pressure of the back pressure chamber (160a) can be maintained at an appropriate level, thereby effectively suppressing leakage between compression chambers while effectively reducing friction loss between scrolls and / or friction loss on the thrust surface.

[0161] Meanwhile, another embodiment of the back pressure chamber assembly is as follows.

[0162] That is, in the aforementioned embodiments, a sealing member for sealing the back pressure chamber is provided on the side of the sealing projection, but in some cases, the sealing member may be provided on the cross-section of the sealing projection.

[0163] FIG. 10 is a cross-sectional view showing another embodiment of a back pressure chamber assembly.

[0164] Referring again to FIGS. 1 and 2, the back pressure assembly (160) according to the present embodiment is provided on one side of the pivot scroll (150) facing the main frame (130), and the basic configuration of the back pressure assembly (160) and the resulting effects are almost identical to the previously described embodiment. For example, a plate receiving groove (161) forming part of the back pressure chamber assembly (160) is formed as a recess on the back surface of the pivoting plate section (151) facing the main frame (130), and a back pressure plate (162) that forms a back pressure chamber (160a) together with the plate receiving groove (161) is slidably inserted into the plate receiving groove (161). A plurality of sealing members (163) are provided between the plate receiving groove (161) and the back pressure plate (162) to seal the back pressure chamber (160a), and a back pressure passage (164) that connects the compression chamber (V) and the back pressure chamber (160a) can be formed in the pivoting scroll (150). Accordingly, the back pressure chamber assembly (160) has a large back pressure area as in the above-described embodiment and can suppress refrigerant leakage in the back pressure chamber (160a). This is replaced by the description of the aforementioned embodiments.

[0165] Additionally, an Oldham ring (170) is provided between the main frame (130) and the pivot scroll (150), and a key receiving protrusion (1611) is formed on the back pressure surface (161c) of the plate receiving groove (161) facing the main frame (130) to receive the second key (173) of the Oldham ring (170), and a key receiving groove (1621) into which the key receiving protrusion (1611) is inserted may be formed on the back pressure plate (162). Accordingly, the key receiving protrusion (1611) and the key receiving groove (1621) are constrained to each other in the radial and circumferential directions, so that the back pressure plate (162) can be coupled to the pivot scroll (150). This is also replaced by the description of the previously mentioned embodiment.

[0166] Additionally, a discharge passage (165) may be formed in the back pressure plate (162) that penetrates between the back pressure surface (162a) and the thrust surface (162b) of the back pressure plate (162). Accordingly, the back pressure of the back pressure chamber (160a) can be suppressed from rising excessively, thereby suppressing leakage between the compression chambers and preventing friction loss between members, while simultaneously effectively lubricating the thrust surface between the main frame (130) and the back pressure plate (162). This is also replaced by the description of the previously mentioned embodiment.

[0167] However, as shown in FIG. 10, in this embodiment, an inner sealing member (1631) that seals the inner side of the back pressure plate (162), an outer sealing member (1632) that seals the outer side of the back pressure plate (162), and an intermediate sealing member (1633) that seals between the first back pressure chamber (160a1) and the second back pressure chamber (160a2) may be provided on the cross-section of each sealing projection (1623a) (1623b) (1623c).

[0168] For example, an inner sealing member (1631) may be provided on the cross-section of an inner sealing projection (1623a), an outer sealing member (1632) on the cross-section of an outer sealing projection (1623b), and an intermediate sealing member (1633) on the cross-section of an intermediate sealing projection (1623c). In this case, each sealing groove (1613a) (1613b) (1613c) may be formed on the back pressure surface (161c) of the plate receiving groove (161) facing each sealing projection (1623a) (1623b) (1623c) so that each sealing projection (1623a) (1623b) (1623c) is inserted together with each sealing member (1631) (1632) (1633). Accordingly, even if each sealing member (1631)(1632)(1633) is not fixed to each sealing projection (1623a)(1623b)(1623c), each sealing member (1631)(1632)(1633) can maintain its position during operation of the compressor.

[0169] In addition, in this case, each sealing member (1631)(1632)(1633) may have a metal rubber gasket having an elastic protrusion (not indicated) on the surface facing the rotating scroll (150). Accordingly, even if the back pressure plate (162) moves up and down along the axial direction in the plate receiving groove (161) of the rotating scroll (150), the elastic protrusion of the sealing member (1631)(1632)(1633) is elastically deformed, maintaining contact with the sealing groove (1613a)(1613b)(1613c), thereby effectively sealing each back pressure chamber (160a1)(160a2).

[0170] As described above, when each sealing member (1631)(1632)(1633) is provided on the cross-section of each sealing projection (1623a)(1623b)(1623c), a separate space for inserting the sealing member (1631)(1632)(1633) into the side of each sealing projection (1623a)(1623b)(1623c) can be eliminated. Accordingly, the gap between the two sealing projections (1623a)(1623b) provided on the inner and outer sides of the back pressure plate (162) can be widened, thereby further expanding the area of ​​the back pressure chamber (160a).

[0171] In addition, in this embodiment, the scroll-side sealing projection and plate-side sealing groove for supporting the intermediate sealing member (1633) may be excluded. Accordingly, compared to inserting the respective sealing members (1631)(1632)(1633) into the sides of the sealing projections (1623a)(1623b)(1623c), the number of sealing projections is reduced, thereby increasing the actual area of ​​the back pressure chamber (160a), while simultaneously simplifying the processing and / or assembly of the sealing projections and sealing grooves, which can reduce manufacturing costs.

[0172] Although not illustrated in the drawing, each sealing member may be fixed to the cross-section of each sealing projection. In this case, the back pressure seal assembly (160) can be further simplified by excluding the sealing groove into which each sealing member and sealing projection are inserted.

[0173] Meanwhile, another embodiment of the back pressure chamber assembly is as follows.

[0174] That is, in the aforementioned embodiments, a plurality of back pressure chambers and one back pressure passage are provided, but in some cases, it may consist of one back pressure chamber and one back pressure passage.

[0175] FIG. 11 is a plan view showing another embodiment of a back pressure chamber assembly, and FIG. 12 is a cross-sectional view taken along line "XII-XII" of FIG. 11.

[0176] Referring again to FIGS. 1 and 2, the back pressure assembly (160) according to the present embodiment is provided between the main frame (130) and the pivot scroll (150), and the basic configuration of the back pressure assembly (160) and the resulting effects are similar to the embodiments described above. For example, a plate receiving groove (161) forming part of the back pressure chamber assembly (160) is formed as a recess on the back surface of the pivoting plate section (151) facing the main frame (130), and a back pressure plate (162) that forms a back pressure chamber (160a) together with the plate receiving groove (161) is slidably inserted into the plate receiving groove (161). A plurality of sealing members (163) are provided between the plate receiving groove (161) and the back pressure plate (162) to seal the back pressure chamber (160a), and a back pressure passage (164) that connects the compression chamber (V) and the back pressure chamber (160a) can be formed in the pivoting scroll (150). Accordingly, the back pressure chamber assembly (160) has a large back pressure area as in the above-described embodiment and can suppress refrigerant leakage in the back pressure chamber (160a). This is replaced by the description of the aforementioned embodiments.

[0177] Additionally, an Oldham ring (170) is provided between the main frame (130) and the pivot scroll (150), and a key receiving protrusion (1611) is formed on the back pressure surface (161c) of the plate receiving groove (161) facing the main frame (130) to receive the second key (173) of the Oldham ring (170), and a key receiving groove (1621) into which the key receiving protrusion (1611) is inserted may be formed on the back pressure plate (162). Accordingly, the key receiving protrusion (1611) and the key receiving groove (1621) are constrained to each other in the radial and circumferential directions, so that the back pressure plate (162) can be coupled to the pivot scroll (150). This is also replaced by the description of the previously mentioned embodiment.

[0178] Additionally, a discharge passage (165) may be formed in the back pressure plate (162) that penetrates between the back pressure surface (162a) and the thrust surface (162b) of the back pressure plate (162). Accordingly, the back pressure of the back pressure chamber (160a) can be suppressed from rising excessively, thereby suppressing leakage between the compression chambers and preventing friction loss between members, while simultaneously effectively lubricating the thrust surface between the main frame (130) and the back pressure plate (162). This is also replaced by the description of the previously mentioned embodiment.

[0179] However, as shown in FIGS. 11 and 12, in this embodiment, a back pressure passage (164) communicating with the compression chamber (V) and the back pressure chamber (160a) may be formed by penetrating the swirling wrap (152). In other words, the inlet (164a) of the back pressure passage (164) is formed by penetrating the cross-section of the swirling wrap (152) that forms the discharge pressure, and the outlet (164b) of the back pressure passage (164) may be formed to communicate with the plate receiving groove (161), as in the previously described embodiments. Accordingly, a refrigerant with a discharge pressure or a pressure close to the discharge pressure is supplied to the back pressure chamber (160a) through the back pressure passage (164) to form the back pressure of the back pressure chamber (160a).

[0180] In this case, only one back pressure chamber (160a) may be formed. That is, an inner sealing projection (1623a) is formed on the inner side of the back pressure plate (162) that overlaps radially with the inner wall portion (161a) of the plate receiving groove (161), and an outer sealing projection (1623b) is formed on the outer side of the back pressure plate (162) that overlaps radially with the outer wall portion (161b) of the plate receiving groove (161), and the inner sealing projection (1623a) and the outer sealing projection (1623b) may be spaced apart radially. Accordingly, one back pressure chamber (160a) forming an annular shape may be formed in the back pressure plate (162) between the inner sealing projection (1623a) and the outer sealing projection (1623b).

[0181] In addition, in this case, an inner sealing member (1631) may be provided between the inner wall portion (161a) of the plate receiving groove (161) and the inner sealing projection (1623a) of the back pressure plate (162) facing it, and an outer sealing member (1632) may be provided between the outer wall portion (161b) of the plate receiving groove (161) and the outer sealing projection (1623b) of the back pressure plate (162) facing it.

[0182] In addition, in this case, each sealing groove (1613a) (1613b) into which each sealing member (1623a) (1623b) is inserted may be further formed on the back pressure surface (161c) of the plate receiving groove (161) facing the cross-section of each sealing member (1623a) (1623b). For example, an inner sealing groove (1613a) into which a part of the inner sealing member (1631) is inserted may be formed on the inner side of the plate receiving groove (161), and an outer sealing groove (1613b) into which a part of the outer sealing member (1632) is inserted may be formed on the outer side of the plate receiving groove (161). These inner sealing grooves (1613a) and outer sealing grooves (1613b) can be formed such that, as in the embodiments described above, the inner sealing projection (1623a) and the outer sealing projection (1623b) can remain inside their respective sealing grooves (1613a) and (1613b) during operation of the compressor.

[0183] As described above, when the back pressure passage (164) is formed by penetrating the cross-section of the swivel wrap (152), the back pressure of the back pressure chamber (160a), to which the outlet (164b) of the back pressure passage (164) is connected, can be appropriately adjusted according to the lifting and lowering of the swivel scroll (150). For example, if the back pressure of the back pressure chamber (160a) rises excessively, the swivel scroll (150) rises strongly toward the fixed scroll (140), and the cross-section of the swivel wrap (152) comes into close contact with the fixed end plate (141), thereby blocking the inflow of refrigerant into the back pressure chamber (160a). Then, the inflow of refrigerant from the compression chamber (V) to the back pressure chamber (160a) is restricted, thereby suppressing the back pressure of the back pressure chamber (160a) from rising excessively. Conversely, when the back pressure of the back pressure chamber (160a) decreases, the cross-section of the swivel wrap (152) is separated from the fixed end plate (141), and the refrigerant flow into the back pressure chamber (160a) resumes, thereby increasing the back pressure of the back pressure chamber (160a). Accordingly, even though only one back pressure chamber (160a) and one back pressure passage (164) are formed, the back pressure of the back pressure chamber (160a) is appropriately maintained, thereby suppressing leakage between compression chambers and suppressing friction loss between components. Through this, the back pressure chamber assembly can be simplified, thereby lowering manufacturing costs.

[0184] In addition, in this case, since only one back pressure chamber (160a) is formed, the sealing protrusion, sealing groove, and part of the sealing member can be excluded compared to the case where multiple back pressure chambers (160a) are provided separately from each other. Accordingly, the back pressure chamber assembly (160) can be further simplified, thereby further reducing manufacturing costs.

[0185] Meanwhile, although the back pressure chamber assembly according to the aforementioned embodiments has been examined primarily in the context of its application to a low-pressure scroll compressor, as previously explained, the back pressure chamber assembly according to the aforementioned embodiments can be applied in the same way to a high-pressure scroll compressor. However, while the back pressure chamber prevents the refrigerant in the back pressure chamber from leaking into the low-pressure chamber forming the suction space in a low-pressure compressor, the back pressure chamber can suppress the refrigerant in the high-pressure section forming the discharge space from flowing into the back pressure chamber and causing the pressure in the back pressure chamber to rise excessively.

Claims

1. Casing; A main frame fixed inside the above casing; A fixed scroll coupled to one side of the main frame; A pivoting plate portion provided between the main frame and the fixed scroll and eccentrically coupled to a rotation axis, and a pivoting scroll having a pivoting wrap extending from one side of the pivoting plate portion and engaging with a fixed wrap of the fixed scroll to form a compression chamber; and It includes a back pressure plate provided between the aforementioned rotating scroll and the aforementioned main frame facing it, and forming a back pressure chamber between it and the aforementioned rotating scroll. A scroll compressor having a plate receiving groove formed on one side of the rotary scroll facing the main frame to accommodate the back pressure plate.

2. In Paragraph 1, An Oldham ring is provided between the main frame and the rotary scroll, and a keyway is formed in the rotary scroll so that a key of the Oldham ring is slidably received. The above back pressure plate, A scroll compressor in which a key receiving groove portion, into which the key of the above Oldham ring is slidably received, is formed to correspond to the key groove of the above-mentioned pivot scroll.

3. In Paragraph 2, On one side of the rotary scroll facing the main frame, a key receiving projection is formed that extends toward the main frame along the circumference of the keyway, and The above key receiving protrusion is, A scroll compressor in which the back pressure plate is inserted into the key receiving groove of the back pressure plate and the back pressure plate is coupled to the pivot scroll.

4. In Paragraph 1, The above back pressure plate, A scroll compressor equipped with a discharge passage for discharging the refrigerant in the back pressure chamber to the outside of the back pressure chamber.

5. In Paragraph 4, The above discharge passage is, A discharge hole penetrating between both sides of the above-mentioned back pressure plate; A discharge groove formed by being recessed to a predetermined depth on the other side of the back pressure plate facing the main frame, communicating with the discharge hole; and A scroll compressor comprising a discharge guide groove formed on the other side of the back pressure plate to communicate with the discharge groove, formed with a cross-sectional area smaller than that of the discharge groove and extending to the outer surface of the back pressure plate.

6. In Paragraph 5, A scroll compressor in which the discharge groove is formed in an annular shape and the discharge guide groove extends along the circumference of the discharge groove.

7. In Paragraph 1, The above back pressure chamber is, First back pressure chamber; and A scroll compressor comprising a second back pressure chamber separated from the first back pressure chamber and forming a lower pressure than the first back pressure chamber.

8. In Paragraph 7, An Oldham ring is provided between the main frame and the rotary scroll, and a keyway is formed in the rotary scroll so that a key of the Oldham ring is slidably received. The above back pressure plate has a key receiving groove formed therein in which the key of the Oldham ring is slidably received, and A scroll compressor in which the first back pressure chamber is formed in an annular shape on the inner side of the key receiving groove, and the second back pressure chamber is formed in a plurality of arc shapes on both sides in the circumferential direction with the key receiving groove in between.

9. In Paragraph 8, On at least one side of the plate receiving groove and the back pressure plate facing it, a sealing projection is formed that protrudes toward the opposite side between the inner wall and the outer wall of the plate receiving groove. A scroll compressor having a sealing member for sealing the back pressure chamber on the radial side of the sealing projection.

10. In Paragraph 9, A scroll compressor having a sealing groove formed on at least one side of the plate receiving groove and the back pressure plate facing it, into which a part of the sealing member is inserted.

11. In Paragraph 8, On at least one side of the plate receiving groove and the back pressure plate facing it, a sealing projection is formed that protrudes toward the opposite side between the inner wall and the outer wall of the plate receiving groove. A scroll compressor having a sealing member provided on the cross-section of the sealing projection.

12. In Paragraph 11, On at least one of the two sides of the plate receiving groove and the back pressure plate facing it, a sealing groove is formed into which a part of the sealing member is inserted. The above sealing member is, A scroll compressor inserted into the sealing groove together with the sealing projection.

13. In Paragraph 8, A back pressure passage is formed in the above-mentioned rotating scroll to connect the compression chamber and the back pressure chamber, and The above back pressure passage is, A first back pressure passage penetrating the above-mentioned pivot plate portion and communicating with the first back pressure chamber; and A scroll compressor comprising a second back pressure passage communicating with the second back pressure chamber in a compression chamber having a pressure lower than the pressure of the compression chamber to which the first back pressure passage communicates, penetrating the above-mentioned rotating plate portion.

14. In Paragraph 13, The above second back pressure chambers are formed in a plurality of arc shapes on both sides in the circumferential direction with the key receiving groove in between, and the plurality of second back pressure chambers are connected to each other through the key receiving groove. The above second back pressure passage is, A scroll compressor connected to one of the plurality of second back pressure chambers.

15. In Paragraph 1, The above back pressure chamber is, A scroll compressor formed annularly on one side of the back pressure plate facing the aforementioned rotating scroll.

16. In Paragraph 15, An Oldham ring is provided between the main frame and the rotary scroll, and a keyway is formed in the rotary scroll so that a key of the Oldham ring is slidably received. The above back pressure plate has a key receiving groove formed therein in which the key of the Oldham ring is slidably received, and A scroll compressor in which a portion of the back pressure chamber is formed to be located on the key receiving groove side, and another portion of the back pressure chamber is formed to be located on both sides in the circumferential direction with the key receiving groove in between.

17. In Paragraph 16, On one side of the back pressure plate facing the aforementioned rotating scroll, a plurality of sealing protrusions protruding toward the rotating scroll are formed at a predetermined interval in the radial direction, and A scroll compressor having a sealing member provided between the inner wall of the plate receiving groove and the sealing projection facing it in the radial direction, and between the outer wall of the plate receiving groove and the sealing projection facing it in the radial direction.

18. In Paragraph 17, A back pressure passage is formed in the above-mentioned rotating scroll to connect the compression chamber and the back pressure chamber, and The above back pressure passage is, A scroll compressor that communicates with the back pressure chamber by continuously penetrating the pivot plate section at the end of the pivot lap.

19. In Paragraph 1, The above back pressure plate is, A scroll compressor that is inserted into the plate receiving groove in the above-mentioned direction of the rotation axis so as to slide.

20. In any one of paragraphs 1 through 19, The above-mentioned pivot scroll further includes a pivot shaft insertion part that overlaps the pivot wrap and the pivot axis in the radial direction at the center of the pivot plate part and extends in the axial direction of the pivot axis. A scroll compressor in which a portion of the pivoting wrap extends from the front end surface of the rotating shaft insertion part facing the fixed scroll.

21. In Paragraph 20, The above-mentioned pivot plate portion is provided with a pivoting step surface between the outer surface of the pivoting wrap and the inner surface of the pivoting wrap facing it, and the above-mentioned fixed wrap is provided with a fixed step surface corresponding to the pivoting step surface. At least a portion of the above-mentioned back pressure chamber is, A scroll compressor formed to communicate with a compression chamber located closer to the center than the aforementioned pivoting step surface when projected in the axial direction.

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