Scroll compressor

Abstract

Disclosed is a scroll compressor. In the scroll compressor, an oil supply groove can be formed between a plurality of first key grooves of a main frame, and the oil supply groove can be formed between an outer circumferential surface of a scroll disk support portion and an imaginary circle passing through the radial center of the first key groove. By this, oil flowing along the periphery of the cross slip ring is trapped in the oil supply groove, rapidly moves to the first key groove, and thus friction loss and / or wear between the first key groove and the first key inserted in the first key groove can be effectively suppressed. This can also be effective at initial startup and / or intermittent operation of a low-pressure upper compression type scroll compressor using a pressure difference oil supply method.

Description

Technical Field

[0001] This invention relates to scroll compressors, and more particularly to a scroll compressor using a cross-shaped slip ring. Background Technology

[0002] In a scroll compressor, the moving scroll and the stationary scroll mesh together, and the moving scroll rotates relative to the stationary scroll, forming two pairs of compression chambers between the moving scroll and the stationary scroll.

[0003] The scroll compressor may be provided with an anti-rotation component that prevents the scroll plate (e.g., the moving scroll plate) receiving the rotational force of the drive motor from rotating relative to another scroll plate (e.g., the stationary scroll plate) or the fixed frame.

[0004] Anti-rotation components mainly include Oldham rings or pin-ring mechanisms. Oldham rings offer advantages in terms of ease of assembly compared to pin-ring mechanisms. Typically, an Oldham ring has a ring body between the main frame and the moving scroll plate. Keys are formed on both sides of the ring body, slidably connecting it to the main frame and the moving scroll plate. Alternatively, a key can be formed on one side of the ring body, slidably connecting it to the stationary and moving scroll plates. The former can be defined as a two-way Oldham ring, and the latter as a one-way Oldham ring. The following description focuses on a two-way Oldham ring with keys formed on both sides of the ring body, slidably inserted into the main frame and the moving scroll plate, but the same principle applies to the latter.

[0005] As the cross-shaped slip ring slides relative to the main frame (or stationary scroll plate) and the moving scroll plate, oil can be smoothly supplied between the key of the cross-shaped slip ring and the keyway of the main frame (or stationary scroll plate) and / or between the key of the cross-shaped slip ring and the keyway of the moving scroll plate, which can be advantageous in terms of lubrication. In particular, the keyway of the main frame is located closer to the outer contour than the thrust surface of the main frame, and the increased distance from the center of the main frame to the keyway may cause a delay in oil supply to the keyway of the main frame. This may occur more frequently, especially during low pressure ratio operation where the differential pressure oil supply is reduced.

[0006] In response, as disclosed in Patent Document 1 (US Patent Publication US2005-0063837A1), a solution is provided that has an oil supply groove connected to a keyway of the main frame via the thrust surface of the main frame. However, in Patent Document 1, the bearing area of ​​the thrust surface of the main frame is reduced, which may lead to a corresponding increase in surface pressure and thus increased frictional losses. In the case of low-pressure top-compression scroll compressors like those in Patent Document 1, where oil is supplied using pressure differential, the aforementioned problems may occur more severely because the oil supply to the thrust surface is delayed.

[0007] As described in Patent Document 2 (US Publication US2013 / 0164164A1), a scheme is disclosed in which oil reservoirs are formed on both sides of the keyway in the circumferential direction of the main frame to store a predetermined amount of oil around the keyway. However, in Patent Document 2, the oil reservoirs are blocked by cross-shaped slip rings, which not only delays the flow of oil into the reservoirs relative to their area, but also, because the reservoirs are far apart in the circumferential direction, some of the oil passing through the thrust surface leaks between the two reservoirs, further delaying the flow of oil into the reservoirs and / or the keyway. When this scheme is applied to the low-pressure top-compression scroll compressor utilizing pressure differential in Patent Document 1, the same oil supply delay may occur. Summary of the Invention

[0008] The purpose of this invention is to provide a scroll compressor capable of suppressing frictional loss and wear between the key of a cross-shaped slip ring and the keyway into which the key of the cross-shaped slip ring is slidably inserted.

[0009] Another object of the present invention is to provide a scroll compressor capable of smoothly and rapidly supplying oil between the key of a cross-shaped slip ring and a keyway into which the key of the cross-shaped slip ring is slidably inserted.

[0010] Another object of the present invention is to provide a scroll compressor capable of smoothly and rapidly supplying oil to the sliding surface between the key and the keyway by directly supplying oil to the keyway into which the key is inserted with a cross slip ring.

[0011] Another object of the present invention is to provide a scroll compressor capable of rapidly supplying oil to a keyway into which a key for inserting a cross-shaped slip ring is inserted in a low-pressure type top-compression scroll compressor utilizing pressure differential.

[0012] To achieve the objectives of this invention, a scroll compressor comprising a housing, a moving scroll, a stationary scroll, a main frame, and a cross-slip ring can be provided. The moving scroll can be coupled to a rotating shaft inside the housing and perform gyratory motion. The stationary scroll can form a compression chamber together with the moving scroll. The main frame can be fixed within the internal space of the housing. An annular scroll support portion can be formed at the center of the main frame, and a cross-slip ring support portion can be formed on the outer periphery of the scroll support portion. The cross-slip ring can be supported by the cross-slip ring support portion and disposed between the main frame and the moving scroll. A plurality of first keyways can be formed at predetermined intervals along the circumferential direction on the main frame. The first keys of the cross-slip ring are respectively inserted into the plurality of first keyways, and an oil supply groove can be formed between the plurality of first keyways. The oil supply groove can be formed between the outer peripheral surface of the scroll support portion and an imaginary circle passing through the radial center of the first keyway. In this way, the oil flowing in along the periphery of the cross-shaped slip ring is captured in the oil supply groove and then moves rapidly towards the first keyway, thereby effectively suppressing frictional losses and / or wear between the first keyway and the first key inserted into it. This also works during the initial start-up and / or intermittent operation of low-pressure top-compression scroll compressors using differential pressure oil supply.

[0013] As an example, the oil supply groove can be formed in an arc shape along the outer periphery of the scroll plate support portion on the cross-shaped slip ring support portion. At least one end of the oil supply groove can be connected to a plurality of the first keyways. In this way, oil flowing into the oil supply groove can be rapidly supplied to each of the first keyways.

[0014] As another example, one end of the oil supply groove can be connected to one side of the first keyway among the plurality of first keyways, and the other end can be separated from the other side of the first keyway among the plurality of first keyways. In this way, the oil flowing into the oil supply groove can be concentrated and supplied to the side of each first keyway with higher pressure.

[0015] For example, the first key can be slidably inserted radially into the first keyway. One end of the oil supply groove can be connected to the circumferential side of the rotating shaft on both sides of the first keyway. This allows a large amount of oil to be supplied to the side with relatively high pressure. When the first key reciprocates, this oil flows between the side of the first key with high pressure and the opposite side of the first keyway, thereby effectively suppressing frictional loss and / or wear between the first keyway and the first key.

[0016] In addition, the arc length of the oil supply groove can be greater than or equal to the minimum interval between the other end of the oil supply groove and the other side of the first keyway opposite to the first keyway on one side along the circumferential direction.

[0017] As another example, the oil supply groove can be configured such that, with the center of the main frame aligned with the center of the cross slip ring, at least a portion of the oil supply groove is located closer to the inner side than the inner circumferential surface of the cross slip ring. This minimizes the portion of the oil supply groove obstructed by the cross slip ring, allowing oil to flow smoothly and quickly into the oil supply groove.

[0018] For example, the oil supply groove can be formed such that, with the center of the main frame coinciding with the center of the cross slip ring, the outer side of the oil supply groove is located at the same position as the inner circumferential surface of the cross slip ring or at a position closer to the inner side than the inner circumferential surface of the cross slip ring.

[0019] As another example, the oil supply groove can be formed such that at least a portion of the oil supply groove overlaps the edge where the scroll plate support and the cross slip ring support meet. In this way, the oil supply groove is located as close as possible to the scroll plate support, allowing the oil passing through the scroll plate support to move rapidly into the oil supply groove.

[0020] For example, the oil supply groove can be formed by extending along the edge where the scroll plate support and the cross slip ring support meet.

[0021] As another example, the first key can be slidably inserted radially into the first keyway, and the oil supply groove can be connected to the inner end of the first keyway, which is radially opposite to the scroll plate support. In this way, the oil supply groove is located as close as possible to the scroll plate support while minimizing the portion obstructed by the cross-shaped slip ring, thereby allowing oil to flow smoothly and quickly into the oil supply groove.

[0022] For example, the inner end of the first keyway can be formed into an arc shape, and at least a portion of the inner end of the first keyway can be formed to overlap axially with the outer peripheral surface of the scroll plate support. In this way, the oil supply groove can be formed closest to the scroll plate support.

[0023] Specifically, an oil supply guide groove can be formed on the outer peripheral surface of the scroll plate support, and the oil supply guide groove overlaps axially with the inner end of the first keyway. This allows the oil flowing into the thrust surface of the scroll plate support to move more rapidly towards the first keyway through the oil supply guide groove.

[0024] As another example, the oil supply groove can be formed with the same cross-sectional area along the circumference. This allows for easy machining of the oil supply groove while maintaining a constant flow of oil into the first keyway through the oil supply groove.

[0025] As another example, the oil supply groove can be configured such that the cross-sectional area of ​​the oil supply groove connected to the circumferential side of the rotating shaft on both sides of the first keyway is larger than the cross-sectional area of ​​the oil supply groove connected to the circumferential side of the rotating shaft on the opposite rotation direction. In this way, the oil flowing into the oil supply groove can be concentrated and supplied to the side of each first keyway with higher pressure.

[0026] As another example, the main frame can be formed with a thrust surface that contacts the moving scroll disk axially. The thrust surface of the moving scroll disk, opposite to the thrust surface of the main frame, can be formed flat. This allows for easy machining of the moving scroll disk while minimizing surface pressure on the thrust surface of the moving scroll disk.

[0027] As another example, the main frame may have a thrust surface that contacts the moving scroll disk axially. One or more oil transfer grooves may be formed on the thrust surface of the moving scroll disk opposite the thrust surface of the main frame. This forces the oil in the swirling space towards the cross-ring support side, thereby enabling the oil in the swirling space to move more rapidly towards the oil transfer groove and / or the first keyway.

[0028] For example, a second keyway can be formed on the thrust surface of the moving scroll disk, and the second key of the cross slip ring is inserted into the second keyway. The oil supply transmission groove can be formed such that at least a portion of the oil supply transmission groove overlaps with the second keyway in the circumferential direction at a position spaced apart from the second keyway.

[0029] Furthermore, the radial width of the oil transfer groove can be greater than or equal to the radial width of the thrust surface of the main frame. Attached Figure Description

[0030] Figure 1 This is a cross-sectional view showing the interior of the scroll compressor in this embodiment.

[0031] Figure 2 This is an exploded perspective view showing the compression section of the scroll compressor in this embodiment, including the main frame.

[0032] Figure 3 This is a top view showing the assembly of the main frame and the cross slip ring in the scroll compressor of this embodiment.

[0033] Figure 4 It is shown in magnification Figure 3 A top view of section "A".

[0034] Figure 5 yes Figure 4 A cross-sectional view with "VV" lines.

[0035] Figure 6This is a schematic diagram used to illustrate the structure and effect of the oil supply tank in this embodiment.

[0036] Figure 7 This is a schematic diagram showing another embodiment of the oil tank.

[0037] Figure 8 This is a schematic diagram showing another embodiment of the oil tank.

[0038] Figure 9 This is a perspective view showing the compression section of another embodiment of a scroll compressor, exploded.

[0039] Figure 10 yes Figure 9 Top view of the assembly.

[0040] Figure 11 yes Figure 10 A sectional view along the "XI-XI" line. Detailed Implementation

[0041] Hereinafter, the scroll compressor of the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.

[0042] Generally, scroll compressors can be classified into low-pressure and high-pressure types based on the refrigerant intake path. In a low-pressure type, the refrigerant intake pipe is connected to the internal space of the casing, allowing the low-temperature refrigerant to pass through the internal space of the casing before being led to the compression chamber. In a high-pressure type, the refrigerant intake pipe is directly connected to the compression chamber, allowing the refrigerant to be led directly to the compression chamber without passing through the internal space of the casing. This embodiment uses a low-pressure scroll compressor as an example. However, the same or similar methods can be applied to high-pressure scroll compressors.

[0043] Furthermore, scroll compressors can be classified into upper compression type and lower compression type based on the relative position of the compression section to the electric drive section. In the upper compression type, the compression section is located above the drive section, while in the lower compression type, the compression section is located below the drive section. This embodiment will be described using an upper compression type scroll compressor as an example. However, the same or similar methods can be applied to lower compression type scroll compressors.

[0044] Furthermore, scroll compressors can be classified into open-type and closed-type based on whether the drive unit (electric motor) and the compressor unit are housed together within the casing. In an open-type compressor, the electric motor unit constituting the drive unit is separate from the compressor unit; in a closed-type compressor, the electric motor unit and the compressor unit are housed within the same casing. This embodiment uses a closed-type scroll compressor as an example. However, the same or similar methods can be applied to open-type scroll compressors.

[0045] Furthermore, scroll compressors can be classified into longitudinal and transverse types based on their relationship to the ground and the rotating shaft. A longitudinal type is one where the rotating shaft is vertically positioned relative to the ground, while a transverse type is one where the rotating shaft is parallel or inclined relative to the ground. For example, in a longitudinal scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side can be defined as the side facing the ground. This embodiment uses a longitudinal scroll compressor as an example. However, the same or similar interpretations can be applied to transverse scroll compressors. Therefore, in the following, axial direction can be understood as the axis of rotation, radial direction as the radial direction of rotation, axial direction as the vertical direction, radial direction as the left and right sides, inner circumferential surface as the top surface, and axial and radial directions as the sides.

[0046] Furthermore, scroll compressors can be categorized into fixed back pressure and rotary back pressure types based on the direction of pressure application from the scroll plate. Fixed back pressure involves applying pressure from the stationary scroll plate to the moving scroll plate, while rotary back pressure involves applying pressure from the moving scroll plate to the stationary scroll plate. This embodiment focuses on a scroll compressor with fixed back pressure. However, the same or similar methods can be applied to rotary back pressure compressors.

[0047] In addition, scroll compressors can be differentiated in various ways according to a reference, and this embodiment can be applied in the same or similar way to scroll compressors using cross slip rings.

[0048] Figure 1 This is a longitudinal sectional view showing the interior of the scroll compressor in this embodiment. Figure 2 This is an exploded perspective view showing the compression section of the scroll compressor in this embodiment, including the main frame.

[0049] Reference Figure 1 and Figure 2 In the scroll compressor of this embodiment, a drive motor 120 is provided in the lower half of the housing 110. A main frame 130, a moving scroll plate 150, a stationary scroll plate 140, and a back pressure chamber assembly 160 are sequentially arranged on the upper side of the drive motor 120. The drive motor 120 constitutes the electric motor unit, and the main frame 130, stationary scroll plate 140, moving scroll plate 150, and back pressure chamber assembly 160 constitute the compression unit. The electric motor unit can be connected to one end of the rotating shaft 125, and the compression unit can be connected to the other end of the rotating shaft 125. Thus, the compression unit is connected to the electric motor unit via the rotating shaft 125 and operates using the rotational force of the electric motor unit.

[0050] Reference Figure 1 The housing 110 may include a cylindrical outer shell 111, an upper cap 112, and a lower cap 113.

[0051] The cylindrical outer shell 111 can be a cylindrical shape with openings at both the top and bottom ends, and the aforementioned drive motor 120 and main frame 130 can be inserted and fixed to the inner circumferential surface. The upper half of the cylindrical outer shell 111 is combined with a terminal bracket (not shown), and a terminal (not shown) for transmitting external power to the drive motor 120 can pass through and be combined with the terminal bracket.

[0052] The upper cap 112 can be combined to cover the upper end of the opening of the cylindrical outer shell 111, and the lower cap 113 can be combined to cover the lower end of the opening of the cylindrical outer shell 111. The edge of the high and low pressure separation plate 115, described later, can be inserted between the cylindrical outer shell 111 and the upper cap 112, and fused together with the cylindrical outer shell 111 and the upper cap 112. The edge of the support bracket 116 can be inserted between the cylindrical outer shell 111 and the lower cap 113, and fused together with the cylindrical outer shell 111 and the lower cap 113. Thus, the internal space of the housing 110 can be sealed.

[0053] In this case, with the high-low pressure separation plate 115 as a reference, the refrigerant suction pipe 117 can be connected through and joined to the cylindrical outer shell 111, and the refrigerant discharge pipe 118 can be connected through and joined to the upper cap 112. Thus, a low-pressure section 110a constituting the suction space can be formed on the lower side of the high-low pressure separation plate 115, and a high-pressure section 110b constituting the discharge space can be formed on the upper side.

[0054] The lower cap 113 can form an oil storage space 110c together with the lower half of the cylindrical outer shell 111 that constitutes the low-pressure section 110a. In other words, the oil storage space 110c can be formed in the lower half of the low-pressure section 110a, and the oil storage space 110c can constitute a part of the low-pressure section 110a.

[0055] Reference Figure 1 In this embodiment, the drive motor 120 can be disposed in the lower half of the low-pressure section 110a, and can include a stator 121 and a rotor 122. The stator 121 can be hot-pressed and fixed to the inner wall surface of the cylindrical outer shell 111, and the rotor 122 can be rotatably disposed inside the stator 121.

[0056] The stator 121 may include a stator core 1211 and a stator coil 1212.

[0057] The stator core 1211 is formed in a cylindrical shape and can be hot-pressed to the inner circumferential surface of the cylindrical outer shell 111. The stator coil 1212 can be wound around the stator core 1211 and can be electrically connected to an external power source through terminals (not shown) that pass through and are connected to the housing 110.

[0058] The rotor 122 may include a rotor core 1221 and a permanent magnet 1222.

[0059] The rotor core 1221 can be formed into a cylindrical shape and can be rotatably inserted into the stator core 1211 with a predetermined gap. The permanent magnet 1222 is spaced apart from the rotor core 1221 along the circumferential direction and embedded in the rotor core 1221.

[0060] The rotating shaft 125 can be pressed into the center of the rotor core 1221, and an eccentric part 125a can be provided at the upper end of the rotating shaft 125 for eccentric engagement with the moving scroll 150 described later. Thus, the rotational force of the drive motor 120 can be transmitted to the moving scroll 150 through the rotating shaft 125.

[0061] An oil flow path 125b can be formed axially through the interior of the rotating shaft 125. An oil suction member 126 for drawing oil stored in the lower part of the housing 110 can be provided at the lower end of the rotating shaft 125. Thus, the oil stored in the lower part of the housing 110 can be drawn along the oil flow path 125b of the rotating shaft 125 and moved towards the swirling space 133. The oil can be dispersed due to pressure difference and / or collision with the rotating shaft insertion part 153 swirling in the swirling space 133 and supplied to the bearing surface between adjacent components.

[0062] In this case, the oil suction component 126 can be a positive displacement pump, such as one with a cycloidal gear, or a centrifugal pump, such as one with a propeller. This embodiment illustrates the latter, i.e., an example of using a centrifugal pump capable of guiding oil supply through pressure differential.

[0063] Reference Figure 1 and Figure 2 In this embodiment, the main frame 130 can be hot-pressed or welded to the inner wall of the cylindrical outer shell 111 above the drive motor 120 constituting the low-pressure part 110a.

[0064] Specifically, the main frame 130 of this embodiment may include a main flange portion 131, a main bearing portion 132, a swirling space portion 133, a scroll plate support portion 134, a cross slip ring support portion 135, and a frame fixing portion 136.

[0065] The outer peripheral surface of the main flange portion 131 can be separated from the inner peripheral surface of the cylindrical outer shell 111, and the frame fixing portion 136, described later, can protrude radially from the outer peripheral surface of the main flange portion 131 and be fixed to the inner peripheral surface of the cylindrical outer shell 111. Thus, the main frame 130 can be fixedly attached to the shell 110.

[0066] The main bearing portion 132 can protrude downward toward the drive motor 120 from the bottom surface of the center side of the main flange portion 131, and a cylindrical bearing hole 132a can be axially passed through its center portion. Thus, the rotating shaft 125 can be inserted into the inner circumferential surface of the bearing hole 132a and radially supported.

[0067] The swirling space 133 can be formed by recessing from the top surface of the center side of the main flange 131 toward the main bearing 132 to a predetermined depth. The inner diameter of the swirling space 133 can be larger than the outer diameter of the rotating shaft insertion portion 153 of the moving scroll 150, which will be described later. As a result, the rotating shaft insertion portion 153 can swirl inside the swirling space 133 and cause the oil flowing into the swirling space 133 to scatter.

[0068] The scroll plate support portion 134 can be formed in an annular shape on the top surface of the main flange portion 131 along the periphery of the swirling space portion 133. In other words, an annular frame-side thrust surface 134a can be formed on the top surface of the scroll plate support portion 134, and the scroll plate-side thrust surface 151a of the moving scroll plate 150 (described later) is slidably supported axially on the frame-side thrust surface 134a. The frame-side thrust surface 134a can be formed flat. Thus, the scroll plate support portion 134 can suppress the increase of surface pressure at the frame-side thrust surface 134a while stably supporting the moving scroll plate 150 (described later) axially.

[0069] The cross-shaped slip ring support 135 can be formed in an annular shape on the top surface of the main flange 131 along the outer peripheral surface 134b of the scroll plate support 134. Thus, the cross-shaped slip ring 170 can be inserted into and rotatably accommodated in the cross-shaped slip ring support 135.

[0070] A first keyway 1351 may be formed on the top surface of the cross-shaped slip ring support 135, and the first key 172 of the cross-shaped slip ring 170, described later, is slidably inserted into the first keyway 1351 in the radial direction. For example, the first keyway 1351 may be formed with a circumferential phase difference of 180°. Thus, the two first keyways 1351 may be arranged on the same line in the radial direction.

[0071] The first keyway 1351 extends radially, with its outer end opening toward the low-pressure portion 110a of the housing 110. Conversely, its inner end can be formed into a blocked semi-circular shape relative to the outer peripheral surface 134b of the scroll plate support portion 134. Thus, oil flowing into the first keyway 1351 moves from the inner end to the outer end and lubricates the first keyway 1351 and the first key 172.

[0072] Oil supply grooves (1352, 1352) can be connected to the two circumferential side surfaces (1351a, 1351a) of the first keyway 1351, respectively. In other words, an oil supply groove 1352 with a predetermined width and depth can be formed on the circumferential side surface 1351a around the inner end of the first keyway 1351, which is recessed on the top surface of the cross-slip ring support 135. The two ends of the oil supply groove 1352 can terminate at the circumferential side surface (or the arc surface forming the inner end) 1351a of the first keyway 1351 and be connected to the first keyway 1351, respectively. The oil supply groove 1352 can extend long along the outer circumferential surface 134b of the scroll plate support 134. Thus, the oil moving from the swirling space 133 to the cross-slip ring support 135 side via the scroll plate support 134 can be captured in the oil supply groove 1352 and quickly flow into the first keyway 1351. The oil supply groove 1352 will be described later, together with the first keyway 1351.

[0073] The frame fixing portion 136 can be formed by extending radially outward from the outer contour of the cross-shaped slip ring support portion 135. The frame fixing portion 136 can extend in a ring or in a circumferential direction as a plurality of protrusions spaced apart at a predetermined interval. This embodiment shows an example in which the frame fixing portion 136 is formed as a plurality of protrusions in a circumferential direction.

[0074] Guide bushings 137 can be fixedly connected to the frame fixing part 136, and the guide bushings 137 are slidably inserted into the stationary vortex disk 140 described later in the axial direction. Thus, the stationary vortex disk 140 described later can be slidably supported on the main frame 130 in the axial direction but is restricted in the radial direction.

[0075] Reference Figure 1 In this embodiment, the stationary scroll plate 140 can be attached to the upper side of the main frame 130 over the moving scroll plate 150. The stationary scroll plate 140 can also be fixedly attached to the main frame 130, or it can be movably attached to the main frame 130 in the vertical direction. This embodiment shows an example in which the stationary scroll plate 140 is movably attached to the main frame 130 in the axial direction.

[0076] The stationary vortex disk 140 of this embodiment may include a stationary vortex end plate portion 141, a stationary vortex tooth 142, a fixed side wall portion 143, and a guide protrusion 144.

[0077] The stationary vortex end plate portion 141 is formed in the shape of a disk and is arranged laterally in the low-pressure portion 110a of the housing 110. The discharge port 141a, the bypass hole 141b, and the vortex disk side back pressure hole 141c can be formed axially through the center of the stationary vortex end plate portion 141.

[0078] The stationary vortex tooth 142 can extend axially at a predetermined height from the bottom surface of the stationary vortex end plate portion 141 facing the moving vortex disk 150, and can extend spirally around the fixed side wall portion 143 from the periphery of the discharge port 141a. Thus, the stationary vortex tooth 142 can be formed to correspond to the moving vortex tooth 152 described later, and form two pairs of compression chambers V1, V2 between the stationary vortex tooth 142 and the moving vortex tooth 152.

[0079] The fixed sidewall portion 143 can be formed into an annular shape by extending axially from the bottom edge of the stationary scroll end plate portion 141 to surround the stationary scroll tooth 142. A radially penetrating suction port 143a can be formed on one side of the outer peripheral surface of the fixed sidewall portion 143. As a result, the refrigerant drawn in through the refrigerant suction pipe 117 can be rapidly drawn into the compression chamber through the suction port 143a.

[0080] The guide protrusion 144 can extend radially from the lower outer peripheral surface of the fixed sidewall portion 143. The guide protrusion 144 can be formed as a ring, or a plurality of them can be formed at predetermined intervals along the circumferential direction. This embodiment will be described with an example of a plurality of guide protrusions 144 being formed at predetermined intervals along the circumferential direction.

[0081] A plurality of guide protrusions 144 can be slidably inserted into the aforementioned guide bushings 137 along the axial direction. Thus, the stationary vortex disk can be slidably supported on the main frame along the axial direction, but is restricted in the radial direction.

[0082] Reference Figure 1 and Figure 2 In this embodiment, the moving scroll plate 150 can be integrated with the rotating shaft 125 and disposed on the top surface of the main frame 130. For example, the moving scroll plate 150 is disposed between the main frame 130 and the stationary scroll plate 140, and a cross-shaped slip ring 170 as an anti-rotation mechanism can be disposed between the moving scroll plate 150 and the main frame 130. Thus, the moving scroll plate 150 is restricted from rotational movement and rotates relative to the stationary scroll plate 140.

[0083] Specifically, the moving scroll plate 150 may include a rotating end plate portion 151, a moving scroll tooth 152, and a rotating shaft insertion portion 153.

[0084] The gyratory endplate portion 151 can be generally formed in a disk shape. The gyratory endplate portion 151 can be axially supported on the scroll disk support portion 134 of the main frame 130. In other words, the bottom surface of the frame-side thrust surface 134a of the gyratory endplate portion 151 facing the scroll disk support portion 134 can be formed with a scroll disk-side thrust surface 151a that is axially supported on the frame-side thrust surface 134a. Thus, the gyratory endplate portion 151 can be axially supported on the scroll disk support portion 134 and smoothly perform gyratory motion.

[0085] On the bottom surface of the gyratory end plate 151, in other words, the thrust surface 151a of the scroll disk side, a second keyway 1511 can be formed, into which the second key 173 of the cross slip ring 170 (described later) is slidably inserted. The second keyway 1511 can be configured in the circumferential direction with a phase difference of 180°, similar to the first keyway 1351 described above, but with a phase difference of approximately 90° from the first keyway 1351 in the circumferential direction. Thus, the moving scroll disk 150 can perform gyratory motion while being restricted from rotation by the main frame 130 via the cross slip ring 170.

[0086] The scroll plate side thrust surface 151a can be formed as flat as the frame side thrust surface 134a described above. Thus, the swivel end plate portion 151 can stably support the scroll plate support portion 134 of the main frame 130 while suppressing the increase in surface pressure at the scroll plate side thrust surface 151a. However, depending on the situation, the scroll plate side thrust surface 151a can be formed with an oil transfer groove 1512 to allow the oil drawn into the swivel space portion 133 through the oil flow path 125b of the rotating shaft 125 to move more rapidly towards the cross slip ring support portion 135. The oil transfer groove 1512 can be formed at a position spaced at a predetermined interval from the second keyway 1511 in the circumferential direction. The oil transfer groove 1512 will be described later with reference to another embodiment.

[0087] The moving vortex tooth 152 can protrude from the top surface of the rotating end plate portion 151 facing the stationary vortex disk 140 at a predetermined height and be formed in a spiral shape. The moving vortex tooth 152 can be formed correspondingly to the stationary vortex tooth 142 of the stationary vortex disk 140, so as to mesh with the stationary vortex tooth 142 and perform a rotary motion. The moving vortex tooth 152 can form a compression chamber V together with the stationary vortex tooth 142.

[0088] The rotating shaft insertion portion 153 protrudes from the bottom of the rotary end plate portion 151 onto the main frame 130 by a predetermined length. The rotating shaft insertion portion 153 can be formed in a cylindrical shape, and the eccentric portion 125a of the rotating shaft 125 can be rotatably coupled to the inner circumferential surface of the rotating shaft insertion portion 153. Thus, the rotational force of the drive motor 120 is transmitted to the rotating shaft insertion portion 153 through the eccentric portion 125a of the rotating shaft 125, and the rotational force transmitted to the rotating shaft insertion portion 153 is restricted by the cross slip ring 170 to cause the rotating scroll plate 150 to rotate.

[0089] Reference Figure 1 In this embodiment, the back pressure chamber assembly 160 can be disposed on the upper side of the stationary scroll plate 140. Thus, the back pressure of the back pressure chamber 160a (more precisely, the force exerted by the back pressure on the back pressure chamber) acts on the stationary scroll plate 140. In other words, the stationary scroll plate 140 can be pressed against the moving scroll plate 150 by the back pressure to seal the compression chamber V.

[0090] The back pressure chamber assembly 160 may include a back pressure plate 161 and a floating plate 165. The back pressure plate 161 may be attached to the top surface of the stationary vortex end plate portion 141, and the floating plate 165 may be slidably attached to the back pressure plate 161 and together with the back pressure plate 161 form a back pressure chamber 160a.

[0091] Reference Figure 1 and Figure 2 In this embodiment, the cross slip ring 170 can be disposed between the main frame 130 and the moving scroll plate 150. As described above, the cross slip ring 170 can be slidably coupled to the main frame 130 and the moving scroll plate 150 respectively, or slidably coupled to the stationary scroll plate 140 and the moving scroll plate 150 respectively. This embodiment shows an example of a bidirectional cross slip ring 170 slidably coupled to the main frame 130 and the moving scroll plate 150.

[0092] Specifically, the cross-shaped slip ring 170 of this embodiment may include a ring body 171, a first key 172, and a second key 173. The ring body 171 may be integrally formed with the first key 172 and / or the second key 173, or the first key 172 and the second key 173 may be subsequently assembled to the ring body 171. This embodiment illustrates an example where the ring body 171 is integrally formed with the first key 172 and the second key 173. However, the same applies to the case where the first key 172 and / or the second key 173 are subsequently assembled to the ring body 171.

[0093] The ring body 171 can be formed into a ring shape from aluminum. This reduces the centrifugal force on the rotating body including the cross-shaped slip ring 170 by reducing its weight. Consequently, the motor load on the drive motor 120 can be reduced, thereby improving compressor performance.

[0094] The first key 172 can be formed by protruding from one axial side (e.g., the bottom surface) of the ring body 171 toward the main frame 130. The first key 172, as a component that can be slidably inserted into the first keyway 1351 of the main frame 130, can also be formed of a material different from that of the main frame 130, which is made of cast iron.

[0095] The first key 172 can be formed in a long rectangular parallelepiped shape in the radial direction, corresponding to the first keyway 1351. For example, the radial length of the first key 172 can be less than or equal to the radial length of the first keyway 1351, and the width length of the first key 172 can be less than the width length of the first keyway 1351. Thus, the first key 172 can slide radially in the first keyway 1351 and can restrict its rotational movement.

[0096] The second key 173 can be formed in the same direction as the first key 172, that is, protruding from one side (e.g., the top surface) of the ring body 171 toward the moving scroll plate 150. Thus, the cross slip ring 170 of this embodiment forms a bidirectional cross slip ring 170.

[0097] The second key 173, which is a component slidably inserted into the second keyway 1511 of the moving scroll disk 150, can be formed of a material different from the moving scroll disk 150, which is made of cast iron. However, if the moving scroll disk 150 is made of aluminum, the second key 173 can also be formed of a wear-resistant material such as cast iron. In this case, the second key 173 can be subsequently assembled to the ring body 171, or it can be coated with a wear-resistant material.

[0098] The second key 173 can be formed radially into an elongated cuboid shape corresponding to the second keyway 1511. For example, the radial length of the second key 173 is less than or equal to the radial length of the second keyway 1511, while the width length of the second key 173 can be less than the width length of the second keyway 1511. Thus, the second key 173 slides radially in the second keyway 1511 and restricts its rotational movement.

[0099] The scroll compressor in this embodiment operates as follows.

[0100] That is, if power is applied to the stator coil 1212 of the stator 121, the rotor 122 rotates together with the rotating shaft 125. As a result, the moving scroll 150 coupled to the rotating shaft 125 rotates relative to the stationary scroll 140, forming two pairs of compression chambers V between the moving scroll teeth 152 and the stationary scroll teeth 142.

[0101] Then, as the compression chamber V moves from the outside to the inside following the rotational motion of the scroll plate 150, its volume gradually decreases. At this time, the refrigerant is drawn into the low-pressure section 110a of the housing 110 through the refrigerant suction pipe 117. A portion of the refrigerant is directly drawn into the respective suction pressure chambers (not marked) that constitute the first compression chamber V1 and the second compression chamber V2, while another portion moves toward the drive motor 120 and is drawn into the suction pressure chamber after cooling the drive motor 120.

[0102] Then, the refrigerant drawn into the compression chamber V repeats the following series of processes: it is compressed while moving along the movement path of the compression chamber V toward the discharge port 141a, and the refrigerant is finally discharged to the high pressure section 110b through the discharge port 141a while pushing the discharge valve 145 in the compression chamber, and then discharged into the refrigeration cycle through the refrigerant discharge pipe 118.

[0103] At this time, a portion of the refrigerant compressed in the compression chamber V is pre-bypassed from each compression chamber V1, V2 to the high-pressure section 110b through the bypass hole 141b before reaching the discharge port 141a, thereby preventing the refrigerant from being over-compressed to above the set pressure in each compression chamber V1, V2.

[0104] Furthermore, another portion of the refrigerant compressed in compression chamber V moves to back pressure chamber 160a through back pressure port 141c before reaching discharge port 141a, thus creating an intermediate pressure in back pressure chamber 160a. As a result, back pressure plate 161 can receive pressure towards stationary scroll plate 140 under the pressure of back pressure chamber 160a and descend, pressurizing the stationary scroll plate 140 towards the moving scroll plate 150. This tightly seals the stationary scroll plate 140 and the moving scroll plate 150, suppressing leakage between compression chambers V, thereby enabling the refrigerant to be compressed as it moves along the movement path of compression chamber V as described above.

[0105] On the other hand, if the rotating shaft 125 rotates, the oil suction member 126 pumps the oil stored in the oil storage space 110c of the housing 110. The pumped oil is drawn in through the oil flow path 125b of the rotating shaft 125 and dispersed in the swirling space 133. A portion of the oil flows through the gap between the scroll plate support 134 and the moving scroll plate 150, in other words, the gap between the frame-side thrust surface 134a and the scroll plate-side thrust surface 151a flows to the cross slip ring support 135. The oil flows into the cross slip ring support 135 between the first keyway 1351 and the first key 172, and lubricates the first keyway 1351 and the first key 172.

[0106] However, as described above, since the two first keyways 1351 are separated from each other by a phase difference of 180° in the circumferential direction, most of the oil flowing into the cross-shaped slip ring support 135 cannot move to the first keyways 1351, but instead flows out to the low-pressure section 110a of the housing 110. Therefore, during initial startup and / or intermittent operation, due to the oil supply delay between the first keyways 1351 and the first key 172, insufficient oil can lead to frictional losses and / or wear, which may reduce reliability.

[0107] Furthermore, if wear occurs between the first keyway 1351 and the first key 172 as described above, the movement of the moving scroll 150, which receives force in the direction of rotation via the cross ring 170, may become unstable. This can lead to frictional losses between the stationary scroll 140 and the moving scroll 150, or leakage between the compression chambers, resulting in decreased compressor efficiency. In particular, if the cross ring 170 or its first key 172 is made of aluminum while the main frame 130 is made of cast iron, the cross ring 170 may experience even greater wear.

[0108] In this embodiment, an oil supply groove 1352 is formed in the main frame 130, and the oil supply groove 1352 can be formed to be as unobstructed as possible by the ring body 171 of the cross slip ring 170. In this way, the oil flowing along the scroll plate support 134 to the cross slip ring support 135 can be guided to flow rapidly into the first keyway 1351.

[0109] Figure 3 This is a top view showing the assembly of the main frame and the cross slip ring in the scroll compressor of this embodiment. Figure 4 It is shown in magnification Figure 3 A top view of section "A". Figure 5 yes Figure 4 The "VV" line sectional view, Figure 6 This is a schematic diagram illustrating the structure and effect of the oil supply tank in this embodiment.

[0110] Refer again Figure 2 A swirling space portion 133 is recessed at the center of the top surface of the main frame 130. A vortex disk support portion 134 is formed in a ring shape along the periphery of the swirling space portion 133. A cross-shaped slip ring support portion 135 can be formed on the outer contour of the vortex disk support portion 134 to surround the vortex disk support portion 134. The cross-shaped slip ring support portion 135 can form a step downward at a predetermined depth on the outer periphery of the vortex disk support portion 134. Thus, the vortex disk support portion 134 is formed in a ring-shaped protrusion, and the inner peripheral surface (not marked) of the cross-shaped slip ring support portion 135 can extend radially at the lower end of the outer peripheral surface 134b of the vortex disk support portion 134.

[0111] Reference Figures 2 to 4 In this embodiment, the cross-shaped slip ring support portion 135 of the main frame 130 can be formed with a first keyway 1351 into which the first key 172 of the cross-shaped slip ring 170 is slidably inserted radially, as described above. An arc-shaped oil supply groove 1352 extending in the circumferential direction is connected to the first keyway 1351. In other words, the oil supply groove 1352 is recessed in the cross-shaped slip ring support portion 135 to a predetermined depth, and at least one end (1352a, 1352b) of the oil supply groove 1352 can be connected to the inner end 1351b of the first keyway 1351 facing the outer peripheral surface 134b of the scroll plate support portion 134 at both radial ends of the first keyway 1351. Thus, the oil supply groove 1352, together with the first keyway 1351, can form a closed loop configured as a circle or an arc.

[0112] For example, the oil supply groove 1352 can be formed such that, with the geometric center Om of the main frame 130 (more precisely, the center of the spiral space portion, or hereinafter defined as the center of the main frame) and the geometric center Oo of the cross slip ring 170 (hereinafter the center of the cross slip ring) coincide, at least a portion of the oil supply groove 1352 is located closer to the inner side than the inner circumferential surface of the cross slip ring 170. In other words, the oil supply groove 1352 can be formed such that, with the center Om of the main frame and the center Oo of the cross slip ring 170 coincide, the outer surface of the oil supply groove 1352 is located at the same position as the inner circumferential surface of the cross slip ring 170 (more precisely, the inner circumferential surface of the ring body), or is located closer to the inner side than the inner circumferential surface of the cross slip ring 170. This embodiment shows an example where the outer surface of the oil supply groove 1352 is located closer to the inner side than the inner circumferential surface of the cross slip ring 170. Thus, the oil supply groove 1352 is located at the innermost side of the cross slip ring support 135, so that the oil supply groove 1352 is not obstructed by the cross slip ring 170, or even if it is obstructed, the obstructed portion can be minimized. In this way, during initial start-up and / or intermittent operation, most of the oil flowing from the vortex space 133 along the scroll plate support 134 to the cross slip ring support 135 moves through the oil supply groove 1352 to the first keyway 1351, and the oil is rapidly supplied between the first keyway 1351 and the first key 172 during the radial sliding of the first key 172 in the first keyway 1351.

[0113] Specifically, in this embodiment, the oil supply groove 1352 can be formed such that at least a portion overlaps with the edge E where the scroll plate support 134 and the cross slip ring support 135 meet (more precisely, it corresponds to the inner top surface of the cross slip ring support forming the edge, but is defined as the edge below). For example, the oil supply groove 1352 can be formed extending in the circumferential direction along the edge E where the scroll plate support 134 and the cross slip ring support 135 meet. Thus, the oil supply groove 1352 is formed as close as possible to the outer peripheral surface 134b of the scroll plate support 134, thereby minimizing the portion of the oil supply groove 1352 that is obscured by the cross slip ring 170.

[0114] In this case, such as Figure 3 and Figure 4 As shown, the radial width D1 of the oil supply groove 1352 can be greater than or equal to the radial distance D2 from the edge E where the scroll plate support 134 and the cross slip ring support 135 meet to the inner side surface 1352a of the oil supply groove 1352. Therefore, as described above, the oil supply groove 1352 is formed as close as possible to the outer peripheral surface 134b of the scroll plate support 134, thereby minimizing the portion of the oil supply groove 1352 obscured by the cross slip ring 170.

[0115] Furthermore, in this case, the oil supply groove 1352 can be connected to the inner end 1351b of the first keyway 1351, which is radially opposite to the outer peripheral surface 134b of the scroll plate support 134, as described above. For example, the inner end 1351b of the first keyway 1351 can be formed in an arc shape, and at least a portion of the inner end 1351b of the first keyway 1351 can be formed to overlap axially with the outer peripheral surface 134b of the scroll plate support 134. In other words, a semi-circular oil supply guide groove 1341 can be formed on the outer peripheral surface 134b of the scroll plate support 134 to overlap axially with the inner end 1351b of the first keyway 1351. As a result, the oil moving from the swirling space section 133 to the frame-side thrust surface 134a of the scroll plate support section 134 is supplied more rapidly to the respective first keyway 1351 through the oil supply guide groove 1341 provided on the outer peripheral surface 134b of the scroll plate support section 134.

[0116] On the other hand, refer to Figure 3 The oil supply groove 1352 can be configured such that at least one end of either of its two ends is connected to the first keyway 1351, and the oil supply groove 1352 is connected to the first keyway 1351 on the inner side of an imaginary circle C1 passing through the radial center of the first keyway 1351. In other words, the oil supply groove 1352 can be configured to connect to the first keyway 1351 between the outer peripheral surface 134b of the scroll plate support portion 134 and the imaginary circle C1. Thus, the oil supply groove 1352 can be configured to be as close as possible to the outer peripheral surface 134b of the scroll plate support portion 134 of the cross slip ring support portion 135. In this way, the oil supply groove 1352 is not obstructed or is obstructed to a minimum by the cross slip ring 170, thereby allowing the oil flowing along the scroll plate support portion 134 to the cross slip ring support portion 135 to be smoothly collected in the oil supply groove 1352.

[0117] In this case, such as Figure 6 As shown, the oil supply groove 1352 can be formed with the same cross-sectional area in the circumferential direction. Thus, the oil supply groove 1352 can be easily machined while keeping the amount of oil flowing into the first keyway 1351 through the oil supply groove 1352 constant.

[0118] Furthermore, in this case, the radial width D1 of the oil supply groove 1352 can be less than the radial length L1 of the first keyway 1351. In other words, the oil supply groove 1352 is formed with the same cross-sectional area in the circumferential direction, and the radial width D1 of the oil supply groove 1352 can be less than half of the radial length L1 of the first keyway 1351. Thus, the oil supply groove 1352 is formed to minimize overlap with the cross slip ring 170 while ensuring sufficient support area for the cross slip ring support portion 135 other than the oil supply groove 1352, thereby stably supporting the ring body of the cross slip ring 170.

[0119] ReferenceFigure 6 When an oil supply groove 1352 is formed on the inner circumference of the cross slip ring support 135, in other words, on the edge E where the scroll plate support 134 and the cross slip ring support 135 meet, or near the edge E, the oil supply groove 1352 can be prevented from being blocked by the cross slip ring 170 housed in the cross slip ring support 135, or even if it is blocked, the blocking portion can be minimized. Thus, the oil drawn in through the oil flow path 125b of the rotating shaft 125 and stored in the vortex space 133 is smoothly collected in the oil supply groove 1352 as it flows into the cross slip ring support 135 via the scroll plate support 134. This oil can then move laterally along the oil supply groove 1352 and flow into the first keyway 1351. In this way, the low-pressure top-compression scroll compressor using differential pressure oil supply can also quickly supply oil between the first keyway 1351 and the first key 172 during initial start-up and / or intermittent operation, thereby suppressing frictional loss and / or wear between the first keyway 1351 and the first key 172.

[0120] Furthermore, the movement of the moving scroll 150 can be prevented from becoming unstable by suppressing wear between the first keyway 1351 and the first key 172. This suppresses frictional losses between the stationary scroll 140 and the moving scroll 150 and / or leakage between the compression chambers, thereby improving compressor efficiency. The above effects can also be achieved when the main frame 130 and the cross ring 170 are made of different materials.

[0121] On the other hand, another embodiment of the oil tank is as follows.

[0122] That is, in the above embodiments, both ends of the oil supply groove are connected to their respective first keyways, but depending on the situation, one end of the oil supply groove can be connected to the first keyway, while the other end can be separated from the first keyway.

[0123] Figure 7 This is a schematic diagram showing another embodiment of the oil tank.

[0124] Refer again Figure 1 The basic structure and function of the scroll compressor in this embodiment can be the same as or almost the same as those in the embodiments described above. For example, the scroll compressor in this embodiment can be a low-pressure top-compression scroll compressor that uses the pressure difference described above for oil supply.

[0125] In this case, a moving scroll disk 150 is axially supported on the top surface of the main frame 130, and a cross slip ring 170 is provided between the main frame 130 and the moving scroll disk 150. The first key 172 of the cross slip ring 170 can be slidably connected to the main frame 130, and the second key 173 of the cross slip ring 170 can be slidably connected to the moving scroll disk 150.

[0126] On the top surface of the main frame 130, in other words, the cross-shaped slip ring support 135 can have a plurality of first keyways (1351, 1351), and oil supply grooves (1352, 1352) extending in the circumferential direction can be formed between the plurality of first keyways (1351, 1351). The oil supply grooves 1352 can be formed on the inner circumferential side of the cross-shaped slip ring support 135, in other words, near or at the edge E where the scroll plate support 134 and the cross-shaped slip ring support 135 meet. Thus, at least a portion of the oil supply grooves 1352 can be located closer to the inner side than the inner circumferential side of the cross-shaped slip ring 170, so that most of the oil supply grooves 1352 are not obstructed by the cross-shaped slip ring 170. In this way, during initial startup and / or intermittent operation, the oil in the swirling space 133 flows along the scroll plate support 134 to the cross slip ring support 135 and is captured in the oil supply groove 1352, and is quickly guided to the first keyway 1351, thereby suppressing insufficient oil between the first keyway 1351 and the first key 172.

[0127] However, as Figure 7 As shown, in this embodiment, one end 1352a of the oil supply groove 1352 can be connected to the first keyway 1351, and the other end 1352b can be separated from the first keyway 1351. For example, the first end 1352a of the oil supply groove 1352 can be connected to the inner end 1351b of one side of the first keyway 1351, and the second end 1352b of the oil supply groove 1352 can be separated from the inner end 1351b of the other side of the first keyway 1351. Therefore, the length of the oil supply groove 1352 is shortened, and correspondingly, not only can the oil supply groove 1352 be easily machined, but the support area of ​​the wider cross-shaped slip ring support 135 can also be ensured.

[0128] In this case, the first end 1352a of the oil groove 1352 can be formed to connect with the circumferential side 1351a of the two circumferential side surfaces (1351a, 1351a) of the first keyway 1351, which has a relatively larger pressure. In other words, it is connected to the inner end 1351b extending from the rotation direction side circumferential side 1351a of the rotating shaft 125. As a result, a large amount of oil is concentrated on the circumferential side 1351a of the circumferential side surface (or friction surface) 1351a between the first keyway 1351 and the first key 172, which is subject to a relatively large frictional load. This can more effectively reduce frictional loss and / or wear between the first keyway 1351 and the first key 172.

[0129] In addition, in this case, such as Figure 7As shown, the arc length L2 of the oil supply groove 1352 can be greater than or equal to the circumferential distance L3 between the second end 1352b of the oil supply groove 1352 and the circumferential side surface 1351a (more precisely, the inner end) of the first keyway 1351 opposite to it in the circumferential direction. Therefore, only one end of the oil supply groove 1352 is directly connected to the first keyway 1351, and the oil supply between the first keyway 1351 and the first key 172 is maximized, thereby reducing frictional loss and / or wear between the first keyway 1351 and the first key 172.

[0130] On the other hand, another embodiment of the oil tank is as follows.

[0131] That is, in the above embodiments, the cross-sectional areas between the two ends of the oil supply groove are formed in the same way, but depending on the situation, the cross-sectional areas between the two ends of the oil supply groove may be formed differently.

[0132] Figure 8 This is a schematic diagram showing another embodiment of the oil tank.

[0133] Refer again Figure 1 The basic structure and function of the scroll compressor in this embodiment can be the same as or almost the same as those in the embodiments described above. For example, the scroll compressor in this embodiment can be a low-pressure top-compression scroll compressor that uses the pressure difference described above for oil supply.

[0134] In this case, a moving scroll disk 150 is axially supported on the top surface of the main frame 130, and a cross slip ring 170 is provided between the main frame 130 and the moving scroll disk 150. The first key 172 of the cross slip ring 170 can be slidably connected to the main frame 130, and the second key 173 of the cross slip ring 170 can be slidably connected to the moving scroll disk 150.

[0135] On the top surface of the main frame 130, in other words, the cross-shaped slip ring support 135 has a plurality of first keyways (1351, 1351), and an oil supply groove 1352 extending in the circumferential direction can be formed between the plurality of first keyways (1351, 1351). The oil supply groove 1352 can be formed on the inner circumferential side of the cross-shaped slip ring support 135, in other words, near or at the edge E where the scroll plate support 134 and the cross-shaped slip ring support 135 meet. Thus, at least a portion of the oil supply groove 1352 can be located closer to the inner side than the inner circumferential surface of the cross-shaped slip ring 170, in other words, closer to the inner side than the inner circumferential surface of the ring body 171, so that most of the oil supply groove 1352 is not obstructed by the cross-shaped slip ring 170. In this way, during initial startup and / or intermittent operation, the oil in the swirling space 133 flows along the vortex disk support 134 to the cross slip ring support 135 and is captured in the oil supply groove 1352, and is quickly guided to the first keyway 1351, thereby suppressing insufficient oil between the first keyway 1351 and the first key 172.

[0136] However, as Figure 8 As shown, the cross-sectional area between the two ends of the oil supply groove 1352 in this embodiment can be formed differently. In other words, the oil supply groove 1352 can be formed to have a plurality of cross-sectional areas in the circumferential direction. As a result, the oil flow rate of the oil supply groove 1352 can be appropriately adjusted.

[0137] For example, the oil supply groove 1352 may include a first oil supply groove 1355 and a second oil supply groove 1356 connected to each other. In this case, the cross-sectional area A1 of the oil supply groove 1352 connected to the circumferential side surface 1351a (more precisely, the inner end) on the rotation direction side of the rotating shaft 125 can be larger than the cross-sectional area A2 of the oil supply groove 1352 extending to the opposite side. In other words, as Figure 8As shown, when both ends of the oil supply groove 1352 are connected to the first keyways (1351, 1351) on both sides, the cross-sectional area A1 (e.g., radial width or axial depth) of the first oil supply groove 1355, which is connected to the circumferential side surface 1351a (more precisely, the inner end) of the rotating shaft 125 in the rotation direction direction, can be formed to be larger than the cross-sectional area A2 (e.g., radial width or axial depth) of the second oil supply groove 1356, which is connected to the circumferential side surface 1351a (more precisely, the inner end) of the rotating shaft 125 in the opposite rotation direction direction. Therefore, not only oil flowing into the first oil supply groove 1355, but also oil flowing into the second oil supply groove 1356, allows a large amount of oil to move towards the first oil supply groove 1355 while simultaneously moving towards the circumferential side surface 1351a of the first keyway 1351 where the pressure is relatively greater. In this way, a large amount of oil is concentrated on the circumferential side surface (or friction surface) 1351a between the first keyway 1351 and the first key 172, on the side of the circumferential side surface 1351a subjected to a relatively large frictional load, while more effectively reducing the frictional loss and / or wear between the first keyway 1351 and the first key 172. The above can be equally applied to situations such as... Figure 7 In one embodiment, one end 1352a of the oil supply groove 1352 is connected to the first keyway 1351 on one side, while the other end 1352b of the oil supply groove 1352 is separated from the first keyway 1351 on the other side.

[0138] On the other hand, another embodiment of the oil tank is as follows.

[0139] That is, in the above embodiments, the oil supply groove is only formed on the main frame, but depending on the situation, the oil supply groove can also be formed on the moving scroll plate.

[0140] Figure 9 This is an exploded perspective view showing the compression section of another embodiment of the scroll compressor. Figure 10 yes Figure 9 Assembly top view, Figure 11 yes Figure 10 A sectional view along the "XI-XI" line.

[0141] Refer again Figure 1 The basic structure and function of the scroll compressor in this embodiment can be the same as or almost the same as those in the embodiments described above. For example, the scroll compressor in this embodiment can be a low-pressure top-compression scroll compressor that uses the pressure difference described above for oil supply.

[0142] In this case, a moving scroll disk 150 is axially supported on the top surface of the main frame 130, and a cross slip ring 170 is provided between the main frame 130 and the moving scroll disk 150. The first key 172 of the cross slip ring 170 can be slidably connected to the main frame 130, and the second key 173 of the cross slip ring 170 can be slidably connected to the moving scroll disk 150.

[0143] On the top surface of the main frame 130, in other words, the cross-shaped slip ring support 135 has a plurality of first keyways (1351, 1351), and oil supply grooves (1352, 1352) extending in the circumferential direction can be formed between the plurality of first keyways (1351, 1351). The oil supply grooves 1352 can be formed on the inner circumferential side of the cross-shaped slip ring support 135, in other words, near or at the edge E where the scroll plate support 134 and the cross-shaped slip ring support 135 meet. Thus, at least a portion of the oil supply grooves 1352 can be located closer to the inner side than the inner circumferential surface of the cross-shaped slip ring 170 (more precisely, the inner circumferential surface of the ring body), so that most of the oil supply grooves 1352 are not obstructed by the cross-shaped slip ring 170. In this way, during initial startup and / or intermittent operation, the oil in the swirling space 133 flows along the vortex disk support 134 to the cross slip ring support 135 and is captured in the oil supply groove 1352. The oil is then quickly directed to the first keyway 1351, thereby suppressing insufficient oil between the first keyway 1351 and the first key 172.

[0144] However, refer to Figures 9 to 11 In this embodiment, the oil supply groove (hereinafter referred to as the oil supply transfer groove) 1512 can also be formed on the thrust surface 151a of the moving scroll disk 150, which is opposite to the thrust surface 135a of the main frame 130. As a result, the oil in the swirling space 133 and / or the oil flowing between the two thrust surfaces 135a and 151a can accumulate in the oil supply transfer groove 1512 provided on the thrust surface 151a of the moving scroll disk 150, thereby moving more rapidly toward the oil supply groove 1352 side of the main frame 130. Through this, a large amount of oil flows rapidly into the oil supply groove 1352 of the main frame 130, and this oil can be supplied more quickly to the first keyway 1351 along the oil supply groove 1352.

[0145] An oil transfer groove 1512 can be formed on the thrust surface 151a of the scroll plate side, and this oil transfer groove 1512 can be formed between the second keyways 1511. In other words, the oil transfer groove 1512 can be formed circumferentially separated from the second keyways 1511. This suppresses the movement of oil accumulated in the oil transfer groove 1512 towards the second keyway 1511 side, thereby ensuring the amount of oil supplied to the first keyway 1351 side.

[0146] In this case, the oil transfer groove 1512 can be formed such that at least a portion overlaps with the second keyway 1511 in the circumferential direction. In other words, the radial width D3 of the oil transfer groove 1512 can be greater than or equal to the radial width D4 of the frame-side thrust surface 134a. For example, the radial width D3 of the oil transfer groove 1512 can be equal to the radial width D4 of the frame-side thrust surface 134a. Thus, when the rotating scroll plate 150 rotates, the oil transfer groove 1512 can cross the frame-side thrust surface 134a, so that the inner end and the outer end of the oil transfer groove 1512 are connected to the gyration space 133 and the cross-slip ring support 135, respectively. In this way, the oil in the gyration space 133 can be directed to the cross-slip ring support 135, in other words, the oil groove 1352 moves more rapidly.

[0147] When projected axially, the oil transfer groove 1512 can be circular, radially elongated (rectangular), or circumferentially elongated (arc). When the oil transfer groove 1512 is circular, its volume can be easily ensured while its shape is relatively compact. When it is rectangular, the bearing area of ​​the scroll plate-side thrust surface 151a can be maximized while allowing the oil in the swirling space 133 to move rapidly towards the cross-ring support 135. When the oil transfer groove 1512 is arc-shaped, its circumferential range can be enlarged, allowing the oil in the swirling space 133 to move even more rapidly towards the cross-ring support 135. This embodiment shows an example where the oil transfer groove 1512 is circular.

Claims

1. A scroll compressor, wherein, include: case; The moving scroll plate is connected to the rotating shaft inside the housing and performs a gyratory motion. The stationary scroll plate, together with the moving scroll plate, forms a compression chamber; The main frame is fixed inside the shell. An annular scroll plate support is formed at the center of the main frame, and a cross slip ring support is formed on the outer periphery of the scroll plate support. as well as A cross slip ring, supported by the cross slip ring support, is disposed between the main frame and the moving scroll plate; The main frame has a plurality of first keyways spaced at predetermined intervals along its circumference. The first keys of the cross-shaped slip rings are respectively inserted into the plurality of first keyways, and oil supply grooves are formed between the plurality of first keyways. The oil supply groove is formed between the outer peripheral surface of the scroll plate support and an imaginary circle passing through the radial center of the first keyway.

2. The scroll compressor according to claim 1, wherein, The oil supply groove is formed in an arc shape along the outer periphery of the scroll plate support portion on the cross slip ring support portion. At least one end of the oil supply groove is connected to a plurality of the first keyways.

3. The scroll compressor according to claim 1, wherein, One end of the oil supply groove is connected to one side of the first keyway among the plurality of first keyways, and the other end is separated from the other side of the first keyway among the plurality of first keyways.

4. The scroll compressor according to claim 3, wherein, The first key is slidably inserted into the first keyway in a radial direction. One end of the oil supply groove is connected to the circumferential side of the rotating shaft on both sides of the first keyway.

5. The scroll compressor according to claim 3, wherein, The arc length of the oil supply groove is greater than or equal to the minimum interval between the other end of the oil supply groove and the first keyway on the opposite side of the other end of the oil supply groove in the circumferential direction.

6. The scroll compressor according to claim 1, wherein, The oil supply groove is formed such that, with the center of the main frame coinciding with the center of the cross slip ring, at least a portion of the oil supply groove is located closer to the inner side than the inner circumferential surface of the cross slip ring.

7. The scroll compressor according to claim 6, wherein... The oil supply groove is formed such that, with the center of the main frame coinciding with the center of the cross slip ring, the outer side of the oil supply groove is located at the same position as the inner circumferential surface of the cross slip ring or at a position closer to the inner side than the inner circumferential surface of the cross slip ring.

8. The scroll compressor according to claim 1, wherein, The oil supply groove is formed such that at least a portion of the oil supply groove overlaps the edge where the scroll plate support and the cross slip ring support meet.

9. The scroll compressor according to claim 8, wherein, The oil supply groove extends along the edge where the scroll plate support and the cross slip ring support meet.

10. The scroll compressor according to claim 1, wherein, The first key is slidably inserted into the first keyway in a radial direction. The oil supply groove is connected to the inner end of the first keyway in the radial direction opposite to the scroll plate support.

Images