Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises: a casing; a main frame; a fixed scroll; an orbiting scroll; an oil supply channel for guiding oil to the space between the fixed and orbiting scrolls; and an oil discharge channel for recovering oil back into the inner space of the casing, wherein the oil supply and oil discharge channels may be provided between the fixed and orbiting scrolls and connected to each other. As such, rapid discharge toward the inner space of the casing of the oil pulled up along the rotary shaft is prevented, thus assuring sufficient supply of oil to the thrust surface between the fixed and orbiting scrolls.

Description

scroll compressor

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

[0002] Compressors used in refrigeration cycles such as refrigerators and air conditioners compress refrigerant gas and transmit it to the condenser. Air conditioners primarily use rotary or scroll compressors. Scroll compressors are increasingly being used not only in air conditioners but also in water heater compressors, which require even higher compression ratios.

[0003] A scroll compressor is classified as a sealed compressor if the drive unit (or electric unit) and the compression unit are included in one casing, and as an open type if they are provided independently. If the compression unit is located above the drive unit, it is classified as an upper compression type, and if located below, it is classified as a lower compression type. If the space where the drive unit is accommodated is suction pressure, it is classified as a low pressure type, and if it is discharge pressure, it is classified as a high pressure type.

[0004] In addition, a scroll compressor includes a fixed scroll having a fixed wrap and an orbiting scroll having an orbiting wrap meshed with the fixed wrap. Scroll compressors can be classified into orbiting back-pressure types and fixed back-pressure types depending on the back-pressure method. In the orbiting back-pressure method, a back-pressure chamber is formed on the back surface of the orbiting scroll, and in the fixed back-pressure method, a back-pressure chamber is formed on the back surface of the fixed scroll. In the fixed back-pressure method, the fixed scroll is usually restrained in the circumferential direction but is provided to be movable in the axial direction, so it is sometimes defined and described as a non-orbiting scroll. Hereinafter, it will be described uniformly as a fixed scroll.

[0005] Patent document (Japanese Patent Laid-Open No. 2014-70509) discloses a high-pressure, rotating back-pressure scroll compressor. In scroll compressors like the one described in the patent document, oil drawn through oil passages on a rotating shaft flows into an eccentric space. Some of the oil is then returned to the casing's oil storage space through an oil drainage passage, while another portion is supplied to the thrust surface and / or compression chamber through an oil supply passage.

[0006] However, in the conventional scroll compressor described above, since the oil supply passages for the thrust surface and / or the compression chamber are formed separately above the oil drain passage, most of the oil is first drained through the oil drain passage, and the remaining portion moves to the oil supply passage. As a result, the amount of oil moving to the oil supply passage is relatively small, which not only fails to smoothly lubricate the thrust surface, but also, since most of the oil moving to the oil supply passage is consumed on the thrust surface, the amount of oil supplied to the compression chamber decreases, which may increase friction loss in the compression chamber.

[0007] In addition, in the conventional scroll compressor as described above, since the rotating shaft coupling part extends from one side of the rotating plate part to the opposite side of the rotating wrap, the discharge-side rotating wrap becomes longer, which weakens the strength of the rotating wrap, and the gap between the point of application of the rotating force and the point of application of the compressive force increases, which increases the overturning moment for the rotating scroll, which may cause the behavior of the orbiting scroll to become unstable. In consideration of this, if the rotating shaft coupling part is sunken in the direction where the rotating wrap is formed, the oil supply passage that guides the oil sucked through the rotating shaft to the sliding surface may be bent several times, which not only increases the manufacturing cost, but also increases the friction loss on the sliding surface due to the delay in oil supply.

[0008] The purpose of the present invention is to provide a scroll compressor capable of securing a sufficient amount of oil supply to a thrust surface and / or a compression chamber in a rotary back pressure method.

[0009] Another object of the present invention is to provide a scroll compressor capable of enhancing the lubrication effect on the thrust surface.

[0010] Another object of the present invention is to provide a scroll compressor capable of reducing suction loss by appropriately controlling the amount of fuel supplied to a compression chamber.

[0011] Another object of the present invention is to provide a scroll compressor capable of reducing manufacturing costs by simplifying the oil supply passage that guides oil to the thrust surface and / or compression chamber.

[0012] Another object of the present invention is to provide a scroll compressor capable of securing suction volume while reducing the overturning moment for the orbiting scroll and increasing wrap strength.

[0013] In order to achieve the object of the present invention, a scroll compressor including a casing, a main frame, a fixed scroll, an orbiting scroll, a fuel supply passage, and an fuel drain passage may be provided. The main frame may be fixed to the inside of the casing. The fixed scroll may be coupled to the main frame. The orbiting scroll may form a compression chamber together with the fixed scroll. For example, the orbiting scroll may include an orbiting plate portion provided between the main frame and the fixed scroll, an orbiting wrap provided on the orbiting plate portion to form a compression chamber together with a fixed wrap of the fixed scroll, a rotation shaft coupling portion recessed in the orbiting plate portion toward which the orbiting wrap is formed and into which a rotation shaft is inserted, and a first fuel supply hole penetrating from an inner circumferential surface of the rotation shaft coupling portion to one side of the orbiting plate portion facing the fixed scroll. The above-mentioned oil supply passage is provided in at least one of the fixed scroll and the orbiting scroll so as to be connected to the first oil supply hole, so as to guide oil sucked through the rotating shaft to the thrust surface between the fixed scroll and the orbiting scroll. The above-mentioned oil drainage passage is provided in at least one of the fixed scroll and the orbiting scroll, so as to drain oil sucked through the rotating shaft into the interior of the casing. The above-mentioned oil drainage passage may be connected to the middle of the above-mentioned oil supply passage so as to be connected to the first oil supply hole. Through this, it is possible to prevent oil sucked along the rotating shaft from being drained directly toward the interior space of the casing, thereby ensuring a sufficient amount of oil supplied to the thrust surface between the fixed scroll and the orbiting scroll.

[0014] For example, the oil supply passage may include a first oil supply groove provided on at least one thrust surface among the fixed thrust surface of the fixed scroll and the orbiting thrust surface of the orbiting scroll facing it. The first oil supply groove may be formed in an annular shape, and the oil drain passage may be connected at the middle of the first oil supply groove. Through this, oil flowing into the first oil supply groove can evenly lubricate the entire thrust surface along the first oil supply groove.

[0015] For example, the oil drainage passage may include an oil drainage groove that is sunken into the fixed thrust surface by a predetermined depth and connected to the first oil supply groove. At least a portion of the oil drainage groove may be exposed to the outer surface of the orbiting scroll when the orbiting scroll rotates. Through this, when the compressor is in operation, the oil drainage passage is always open to the internal space of the casing, and the oil sucked through the oil passage of the rotating shaft can be smoothly recovered.

[0016] Alternatively, the oil drainage passage may include an oil drainage groove that is sunk into the orbiting thrust surface by a preset depth and connected to the first oil supply groove. The oil drainage groove may be opened to the outer circumference of the orbiting scroll and communicated with the interior of the casing. Accordingly, oil flowing into the thrust surface between the fixed scroll and the orbiting scroll is evenly distributed over the entire thrust surface through the first oil supply groove, thereby smoothly lubricating the thrust surface, and at the same time, a portion of the oil may be smoothly recovered into the internal space of the casing through the oil drainage groove provided in the orbiting scroll.

[0017] As another example, the first oil supply hole may be opened to the orbiting thrust surface of the orbiting scroll facing the fixed thrust surface of the fixed scroll. A first oil supply groove may be formed in the fixed thrust surface and recessed to a preset depth. The first oil supply groove may extend along the fixed thrust surface and be connected to the first oil supply hole. Through this, oil may be stably supplied to the thrust surface between the fixed scroll and the orbiting scroll, thereby reducing frictional loss on the thrust surface, thereby improving compressor performance.

[0018] For example, the above-mentioned fuel supply passage may include at least one communication groove that is sunken into the fixed thrust surface by a preset depth and accommodates the first fuel supply hole in the middle of the first fuel supply groove. The cross-sectional area of ​​the communication groove may be formed to be larger than the cross-sectional area of ​​the first fuel supply groove. Through this, the first fuel supply hole can always be accommodated in the communication groove during the orbital movement of the orbiting scroll, so that the first fuel supply hole and the first fuel supply groove can be continuously communicated.

[0019] For example, the above-mentioned fuel supply passage may extend from the above-mentioned first fuel supply groove and form a second fuel supply groove that is connected to the compression chamber. The cross-sectional area of ​​the above-mentioned second fuel supply groove may be formed to be smaller than or equal to the cross-sectional area of ​​the above-mentioned fuel drain passage. This can suppress excessive inflow of high-pressure and / or high-temperature oil into the suction pressure chamber, thereby reducing suction loss.

[0020] For example, the above-mentioned fuel supply passage may further include a second fuel supply hole penetrating between the first fuel supply groove and the compression chamber. The second fuel supply hole may be provided with a fuel supply control valve that selectively opens and closes the second fuel supply hole. Through this, the amount of oil supplied to the compression chamber can be appropriately controlled, thereby preventing excessive high-pressure and / or high-temperature oil from flowing into the compression chamber.

[0021] Specifically, the second refueling hole may include a first hole portion communicating with the first refueling groove; and a second hole portion extending from the first hole portion and communicating with the compression chamber and formed to have a smaller cross-sectional area than the first hole portion. The refueling control valve may include a first valve portion slidably inserted into the first hole portion; a second valve portion extending from the first valve portion and slidably inserted into the second hole portion and formed to have a length smaller than or equal to the length of the second hole portion; and a refueling guide hole having one end penetrating the first valve portion and communicating with the first hole portion, and the other end penetrating the second valve portion and communicating with the compression chamber. The other end of the refueling guide hole may penetrate the outer circumferential surface of the second valve portion. Through this, the amount of refueling introduced toward the compression chamber through the refueling guide hole may vary depending on the overlapping length between the second valve portion and the second hole portion.

[0022] More specifically, an elastic member may be provided between the first hole portion and the first valve portion to elastically support the fuel supply control valve toward the first hole portion. Through this, the amount of fuel supplied to the compression chamber can be controlled by opening and closing the fuel supply control valve (1815) according to the pressure difference between the first fuel supply groove and the compression chamber.

[0023] As another example, the first oil supply hole may be opened to the orbiting thrust surface of the orbiting scroll facing the fixed thrust surface of the fixed scroll. A first oil supply groove may be formed in the orbiting thrust surface and recessed to a preset depth. The first oil supply groove may extend along the orbiting thrust surface and be connected to the first oil supply hole. Through this, when the orbiting scroll rotates, oil is subjected to centrifugal force to spread widely on the thrust surface, and at the same time, oil can be quickly drained through the drain groove.

[0024] For example, the above-mentioned fuel supply passage may be formed by recessing a predetermined depth in the above-mentioned turning thrust surface to form a second fuel supply groove that is connected to the compression chamber. The cross-sectional area of ​​the second fuel supply groove may be formed to be smaller than or equal to the cross-sectional area of ​​the above-mentioned fuel drain passage. This can suppress excessive inflow of high-pressure and / or high-temperature oil into the suction pressure chamber, thereby reducing suction loss.

[0025] As another example, a back pressure chamber assembly may be further included between the orbiting scroll and the main frame facing it, pressurizing the orbiting scroll toward the fixed scroll. The back pressure chamber assembly may be provided on one side of the main frame facing the orbiting scroll. This simplifies the back pressure chamber assembly, thereby reducing manufacturing costs.

[0026] For example, the back pressure chamber assembly may include a back pressure passage, a back pressure space, and a sealing member. The back pressure passage may pass through the orbiting scroll so as to be connected to the compression chamber. The back pressure space may be formed in an annular shape to accommodate the back pressure passage. The sealing member may be provided on an end surface of the back pressure space facing the orbiting scroll to form a back pressure chamber inside the back pressure space. The oil supply passage may be formed at a predetermined interval from one side of the back pressure passage. Through this, the back pressure chamber assembly may be simplified while allowing smooth and rapid oil supply to the sliding surface.

[0027] As another example, the invention may further include a back pressure chamber assembly provided between the orbiting scroll and the main frame facing the orbiting scroll to pressurize the orbiting scroll toward the fixed scroll. The back pressure chamber assembly may be provided on one side of the orbiting scroll facing the main frame. Through this, the back pressure chamber assembly increases the sealing force between the main frame and the orbiting scroll, effectively blocking refrigerant leakage from the back pressure chamber or refrigerant inflow into the back pressure chamber, thereby suppressing suction loss and / or compression loss. In addition, the back pressure chamber area is secured to be wider, so that the orbiting scroll can be more securely supported.

[0028] For example, the back pressure chamber assembly may include a back pressure passage, a back pressure space, and a floating member. The back pressure passage may penetrate the orbiting scroll so as to be in communication with the compression chamber. The back pressure space may be formed in an annular shape to accommodate the back pressure passage. The floating member may be slidably coupled to the back pressure space to form a back pressure chamber inside the back pressure space. The oil supply passage may be formed at a predetermined interval from one side of the back pressure passage. Through this, the open side of the back pressure space may be sealed to more effectively seal the back pressure chamber, while also smoothly and quickly supplying oil to the sliding surface.

[0029] A scroll compressor according to the present invention comprises a casing, a main frame, a fixed scroll, an orbiting scroll, an oil supply passage for guiding oil between the fixed scroll and the orbiting scroll, and an oil drain passage for recovering oil into the internal space of the casing, wherein the oil supply passage and the oil drain passage are provided between the fixed scroll and the orbiting scroll and can be connected to each other. Through this, oil sucked along the rotational axis can be prevented from being drained directly toward the internal space of the casing, thereby ensuring a sufficient amount of oil supplied to the thrust surface between the fixed scroll and the orbiting scroll.

[0030] A scroll compressor according to the present invention has at least one first oil supply hole formed on an orbiting scroll, the first oil supply hole being opened to an orbiting thrust surface facing a fixed thrust surface of a fixed scroll, and a first oil supply groove formed on the fixed thrust surface to be sunken to a preset depth, and the first oil supply groove can extend along the fixed thrust surface and be connected to the first oil supply hole. Through this, oil can be stably supplied to the thrust surface between the fixed scroll and the orbiting scroll, thereby reducing frictional loss on the thrust surface, thereby improving compressor performance.

[0031] A scroll compressor according to the present invention comprises a second oil supply groove formed extending from the inner circumference of a first oil supply groove and communicating with a compression chamber, wherein the cross-sectional area of ​​the second oil supply groove may be formed to be smaller than or equal to the cross-sectional area of ​​an oil drain passage. This can suppress excessive inflow of high-pressure and / or high-temperature oil into the suction chamber, thereby reducing suction loss.

[0032] The scroll compressor according to the present invention further includes a second oil supply hole penetrating between the first oil supply groove and the compression chamber, wherein the second oil supply hole may be provided with an oil supply control valve that selectively opens and closes the second oil supply hole. Through this, the amount of oil supplied to the compression chamber can be appropriately controlled, thereby preventing excessive high-pressure and / or high-temperature oil from flowing into the compression chamber.

[0033] A scroll compressor according to the present invention has at least one first oil supply hole formed on an orbiting scroll, the first oil supply groove being sunken to a predetermined depth on the orbiting thrust surface, and the first oil supply groove extending along the orbiting thrust surface can be connected to the first oil supply hole. Through this, when the orbiting scroll rotates, oil is subjected to centrifugal force to spread widely on the thrust surface, and at the same time, oil can be quickly drained through the drain groove.

[0034] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0035] Fig. 2 is a perspective view showing the compression unit in an exploded view of a scroll compressor according to the present embodiment.

[0036] Figure 3 is a plan view showing the assembled compression part in Figure 2.

[0037] Figure 4 is a cross-sectional view taken along the line “Ⅳ-Ⅳ” of Figure 3.

[0038] Figure 5 is an exploded perspective view of another embodiment of a fueling passage.

[0039] Figure 6 is an assembly plan view of Figure 5.

[0040] Figure 7 is a cross-sectional view taken along line “Ⅶ-Ⅶ” of Figure 6.

[0041] Figures 8a and 8b are cross-sectional views showing the operation of the fuel control valve of Figure 5.

[0042] Figure 9 is an exploded perspective view of another embodiment of the fuel supply and exhaust passages.

[0043] Figure 10 is an assembly plan view of Figure 9.

[0044] Fig. 11 is a cross-sectional view showing a portion of a scroll compressor to which another embodiment of a back pressure chamber assembly is applied.

[0045] Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0046] Scroll compressors can be classified as sealed or open, depending on whether the drive motor and compression unit are installed together within the internal space of the casing. This embodiment uses a sealed scroll compressor as a representative example. However, the same principles can be applied to open scroll compressors.

[0047] Scroll compressors can also be categorized into fixed scroll compressors and mobile scroll compressors. Fixed scroll compressors are typically used for building air conditioning, while mobile scroll compressors are used for vehicle air conditioning. This embodiment uses a fixed scroll compressor as a representative example. However, the same principles can be applied to mobile scroll compressors.

[0048] Scroll compressors can also be categorized as low-pressure or high-pressure depending on the pressure of the refrigerant filled within the internal space of the casing. In a low-pressure type, the internal space of the casing is filled with refrigerant at suction pressure, while in a high-pressure type, the internal space of the casing is filled with refrigerant at discharge pressure. This embodiment describes a low-pressure scroll compressor as a representative example. However, the same principles can be applied to high-pressure scroll compressors.

[0049] Additionally, scroll compressors can be categorized into upper compression types and lower compression types depending on the installation location of the compression unit. In the upper compression type, the compression unit is installed above the driving motor, and in the lower compression type, the compression unit is installed below the driving motor. This embodiment describes an upper compression type scroll compressor as a representative example. However, the same principles can be applied to a lower compression type scroll compressor.

[0050] In addition, scroll compressors can be classified into single-rotating scroll compressors and reciprocating scroll compressors depending on whether the scrolls rotate. Single-rotating scroll compressors are configured such that one scroll is fixed or has limited rotational movement while the other scroll rotates, while reciprocating scroll compressors are configured such that both scrolls rotate. This embodiment will be described using a single-rotating scroll compressor as a representative example. However, the same principles can be applied to reciprocating scroll compressors.

[0051] In addition, scroll compressors can be divided into vertical scroll compressors in which the rotation axis is arranged perpendicular to the ground and horizontal scroll compressors in which the rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side can be defined as the side facing the ground. The following description will be given using a vertical scroll compressor as an example. However, the same or similar application can be applied to a horizontal scroll compressor. Therefore, the axial direction is understood as the axial direction of the rotation axis, the radial direction is understood as the radial direction of the rotation axis, and the axial direction can be understood as the up-down direction, the radial direction can be understood as the left and right sides, the inner surface can be understood as the upper surface, and the axial radial direction can be understood as the side, respectively.

[0052] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0053] Referring to FIG. 1, the scroll compressor according to the present embodiment may be provided with a driving motor (120) forming an electric power unit in the lower half of a casing (110), and a main frame (130), a fixed scroll (140), an orbiting scroll (150), and a back pressure chamber assembly (160) forming a compression unit may be provided in the upper part of the driving motor (120). The electric power 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 electric power unit by the rotating shaft (125) and operates by the rotational force of the electric power unit.

[0054] The casing (110) may include a cylindrical shell (111), an upper cap (112), and a lower cap (113).

[0055] The cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and the aforementioned driving motor (120) and main frame (130) can be inserted and fixed into the inner surface. A refrigerant suction pipe (115), which will be described later, can be connected by penetrating the upper half of the cylindrical shell (111), for example, the upper side of the driving motor (120).

[0056] The upper cap (112) can be coupled to cover the opened upper portion of the cylindrical shell (111), and the lower cap (113) can be coupled to cover the opened lower portion of the cylindrical shell (111). Accordingly, the internal space of the casing (110) can be sealed.

[0057] An annular high-low pressure separator (114) can be inserted and connected between the cylindrical shell (111) and the upper cap (112). In other words, the outer circumference of the high-low pressure separator (114) is connected between the cylindrical shell (111) and the upper cap (112), and the inner circumference of the high-low pressure separator (114) can be tightly fastened to the back surface of the fixed scroll (140). Accordingly, the internal space of the casing (110) can be separated into a low-pressure portion (110a) forming a suction space centered on the high-low pressure separator (114) and a high-pressure portion (110b) forming a discharge space.

[0058] A refrigerant suction pipe (115) may be connected through the middle of the cylindrical shell (111), and a refrigerant discharge pipe (116) may be connected through the upper cap (112). Accordingly, the refrigerant suction pipe (115) may be connected to the low-pressure portion (110a) of the casing (110) forming the suction space, and the refrigerant discharge pipe (116) may be connected to the high-pressure portion (110b) of the casing (110) forming the discharge space.

[0059] Referring to FIG. 1, a driving motor (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) may be fixed to the inner wall surface of a cylindrical shell (111) by hot pressing, and the rotor (122) may be rotatably provided inside the stator (121).

[0060] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0061] The stator core (1211) is formed in a cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot pressing. The stator coil (1212) is wound around the stator core (1211) and can be electrically connected to an external power source through a terminal (not shown) that is connected through the casing (110).

[0062] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0063] The rotor core (1221) is formed in a cylindrical shape and can be rotatably inserted into the interior of the stator core (1211) at a predetermined gap interval. The permanent magnet (1222) can be embedded in the interior of the rotor core (1222) at a predetermined gap interval along the circumference.

[0064] In addition, a rotation shaft (125) can be press-fitted and coupled to the center of the rotor core (1221). An eccentric portion (1251) is provided at the upper end of the rotation shaft (125), so that an orbiting scroll (150), which will be described later, can be eccentrically coupled thereto. Accordingly, the rotational force of the driving motor (120) can be transmitted to the orbiting scroll (150) through the rotation shaft (125).

[0065] In addition, an oil passage (1252) may be formed axially through the inside of the rotating shaft (125), and an oil pickup (126) for sucking up oil stored in the lower part of the casing (110) may be provided at the lower end 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.

[0066] Referring to FIG. 1, the main frame (130) according to the present embodiment may include a main flange portion (131) and an axial support portion (132).

[0067] The main flange portion (131) may 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) may be formed on the outer surface of the main flange portion (131) and spaced apart from the inner surface of the cylindrical shell (111). Accordingly, oil supplied between the main frame (130) and the orbiting scroll (150) may be recovered to the oil storage space (110c) of the casing (110) through the oil recovery passage (not shown).

[0068] In addition, 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), an old ring support surface (1312) is formed on the inner side of the scroll fixing surface (1311), and a thrust support surface (1313) can be formed on the inner side of the old ring support surface (1312).

[0069] The scroll fixing surface (1311) is a portion where the fixed scroll (140) is fixed and secured, and may be formed to have a predetermined height difference from the old ring support surface (1312) and / or the thrust support surface (1313). Accordingly, a step surface is formed between the inner surface of the scroll fixing surface (1311) and the outer surface of the old ring support surface (1312), so that a certain amount of oil flowing into the old ring support surface (1312) and / or the thrust support surface (1313) can be stored on the inner side of the scroll fixing surface (1311).

[0070] In addition, the scroll fixing surfaces (1311) may be formed at predetermined intervals along the circumferential direction by extending in the radial direction. Accordingly, a type of oil recovery passage (not shown) may be formed between the scroll fixing surfaces (1311) through which oil supplied to the sliding surface through the oil supply passage (181) described later is recovered to the oil storage space (110c).

[0071] Although not shown in the drawing, the scroll fixing surface (1311) may be formed at the same height as the old 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 the same plane, so that the main frame (130) can be easily formed.

[0072] The Oldham ring support surface (1312) is a portion where the Oldham ring (170), which will 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 orbiting scroll (150).

[0073] A first key groove (not shown) may be formed on the Oldham ring support surface (1312) into which the first key (not shown) of the Oldham ring (170) is slidably inserted. The first key groove may be formed to be radially long to correspond with the first key. For example, the first key groove may be formed by being recessed into the Oldham ring support surface (1312) by a preset depth.

[0074] The thrust support surface (1313) is a portion where the sealing member (163) of the pressure relief assembly (160) described later is inserted to form the pressure relief space (162), and can be formed flat like the old ring support surface (1312). Accordingly, the turning plate can be secured and supported in the axial direction during operation stoppage and / or abnormal operation.

[0075] The shaft support protrusion (132) extends from the center of the main flange portion (131) toward the driving motor (120), and a shaft support hole (1321) may be formed on the inside of the shaft support protrusion (132) so as to penetrate both axial side surfaces of the main flange portion (131). Accordingly, the main frame (130) can radially support the rotation shaft (125) inserted into the shaft support hole (1321).

[0076] Referring to Fig. 1, a fixed scroll (140) according to the present embodiment can be fixed to a main frame (130) with a rotating scroll (150) to be described later therebetween. For example, the fixed scroll (140) can include a fixed plate portion (141), a fixed wrap (142), and a fixed side wall portion (143).

[0077] The fixed plate portion (141) is formed in a disc shape and can be fixed laterally in the low-pressure portion (110a) of the casing (110). A discharge port (1411) and a bypass hole (1412) can be formed to penetrate axially through the central portion of the fixed plate portion (141). Accordingly, the refrigerant compressed in the compression chamber (V) can be discharged to the high-pressure portion (110b), which is a discharge space, through the discharge port (1411), or can be discharged to the high-pressure portion (110b) through the bypass hole (1412) before reaching the discharge port (1411).

[0078] In addition, the fixed plate portion (141) may be formed with a first refueling groove (1812) and a second refueling groove (1813) that form part of a refueling passage (181) to be described later. For example, the first refueling groove (1812) is formed on a fixed thrust surface (1431) facing the orbiting thrust surface (1512) of the orbiting scroll (150) at the outer edge of the fixed wrap (142) and is connected to the first refueling hole (1811) to be described later, and the second refueling groove (1813) may be connected to the first refueling groove (1812) and is connected to a compression chamber (V), more precisely, a suction pressure chamber. Accordingly, the oil sucked through the oil passage (1252) of the rotating shaft (125) can be supplied to the thrust surface (1413)(1512) between the fixed scroll (140) and the orbiting scroll (150) through the first oil supply groove (1812) and to the compression chamber (V) through the second oil supply groove (1813) to lubricate the sliding surface.

[0079] In addition, a fuel supply groove (1821), which forms part of a fuel supply passage (182) to be described later, may be connected in the middle of the first fuel supply groove (1812). Accordingly, the fuel supply passage (181) and the fuel supply passage (182) are connected to each other, thereby securing the amount of fuel supplied to the fuel supply passage (181). The first fuel supply groove (1812) and the second fuel supply groove (1813) will be described again later along with the fuel supply passage (182).

[0080] The fixed wrap (142) can extend from the lower surface of the fixed plate portion (141) toward the orbiting scroll (150). The fixed wrap (142) can be formed in various shapes, such as an involute. For example, the fixed wrap (142) can be formed in a logarithmic spiral or in a plurality of circular arc curves.

[0081] However, when the fixed wrap (142) is formed in a logarithmic spiral, the rotating wrap (152) to be described later must also be formed in a logarithmic spiral, so not only is the shape of the rotating shaft coupling part (153) to be described later limited, but the stroke volume may also be reduced at the same wrap height and plate width.

[0082] Accordingly, the fixed wrap (142) according to the present embodiment may be formed in a form in which the wrap curve connects multiple circular arcs with different diameters and origins. Accordingly, the fixed wrap (142) may be formed with different wrap thicknesses along the wrap formation direction.

[0083] For example, the fixed wrap (142) according to the present embodiment may be formed so that the wrap thickness at the discharge end, which is the center, is thicker than the wrap thickness at the suction end, which is the outermost. Accordingly, the wrap strength at the discharge end of the fixed wrap (142), which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142). In addition, the wrap curve of the fixed wrap (142) can be formed wide, so that the stroke volume can be expanded at the same wrap height and plate width. The same applies to the rotating wrap (152) described later.

[0084] In addition, 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 the present embodiment, an example is shown in which the wrap heights of the fixed wrap (142) are different along the wrap formation direction of the fixed wrap (142). For example, in the present 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 the center based on the fixed step surface (1421), may be formed lower than the wrap height of the suction end, which is the outermost. Accordingly, the wrap strength of the discharge end of the fixed wrap (142), which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142).

[0085] The fixed step surface (1421) can be formed at a position where the compression chamber (e.g., the first compression chamber) (V1) that starts discharging relatively early among the two compression chambers (V1) (V2) is connected to the discharge port (1411) at the discharge start angle (discharge start time). This also applies to the pivot step surface (1511) described later, which will be described later.

[0086] The fixed side wall portion (143) may be formed in a ring shape by extending axially from the compression surface edge of the fixed plate portion (141) to wrap around the fixed wrap (142). One side of the fixed side wall portion (143) facing the main frame (130) may be fastened to and placed on the scroll support surface (1311) of the main frame (130). Accordingly, the fixed scroll (140) may be axially supported and axially fixed to the main frame (130).

[0087] Referring to FIG. 1, the orbiting scroll (150) according to the present embodiment may be coupled to an eccentric portion (1251) of a rotation shaft (125) and provided between the main frame (130) and the fixed scroll (140). Specifically, the orbiting scroll (150) may include a rotation plate portion (151), a rotation wrap (152), and a rotation shaft coupling portion (153).

[0088] The pivot plate (151) is formed in a roughly circular shape and can be accommodated on the inner side of the scroll support surface (1311) of the main frame (130). A second key groove (not shown) can be formed on one side of the pivot plate (151), that is, on the lower edge facing the main frame (130), so that a second key (not shown) of an Oldham ring (170) can be inserted. Accordingly, the pivot plate (151) can perform a pivotal movement on the inner side of the scroll support surface (1311) by the Oldham ring (170).

[0089] The pivot plate (151) may be formed with the same thickness, or may be formed with different thicknesses in parts. For example, if the rotation shaft coupling portion (153) extends only from the rear surface of the pivot plate (151) toward the main frame (130), the pivot plate (151) may be formed with the same thickness throughout. However, if the rotation shaft coupling portion (153) is recessed from the pivot plate (151) toward the pivot wrap (152) to be described later, the thickness of the pivot plate (151) may be formed to be thicker in parts, that is, in the part where the rotation shaft coupling portion (153) is formed.

[0090] In this embodiment, an example is shown in which the center side thickness of the pivot plate part (151) is formed thicker than the edge side thickness. Accordingly, the upper surface (compression surface) of the pivot plate part (151) is formed so that the height of the pivot plate part (151) on the discharge side is higher than the height of the pivot plate part (151) on the suction side, centered on the pivot step surface (1511). Through this, the rotary shaft coupling part (153) described later protrudes in the direction toward the fixed plate part (141), so that the gap between the first point of action where the rotational force is applied to the pivot scroll (150) and the second point of action where the compression force is applied is shortened, thereby reducing the overturning moment of the pivot scroll (150).

[0091] The turning step surface (1511) connects the outer surface of the discharge end of the turning wrap (152) and the inner surface of the turning wrap (152) facing it in the radial direction, but, like the fixed step surface (1421) above, it can be formed at a position where the compression chamber (e.g., the first compression chamber) (V1) adjacent to the discharge port (1411) among the compression chambers on both sides communicates with the discharge port (1411) at the discharge start angle (discharge start time).

[0092] In other words, since the discharge port (1411) is formed in an irregular elliptical shape, at the point where the turning step surface (1511) and the fixed step surface (1421) are separated, one end of the turning step surface (1511) (more precisely, the outer side of the turning wrap) can be formed to be connected to or axially overlap a part of the discharge port (1411). Accordingly, at the moment when the turning step surface (1511) is separated from the fixed step surface (1421) during the turning movement of the turning scroll (150), the two compression chambers (V1) (V2) are communicated with each other, and at the same time, one compression chamber (e.g., the first compression chamber) (V1) is communicated with the discharge port (1411). Then, even if the two compression chambers (V1)(V2) are connected, the refrigerant in the two compression chambers (V1)(V2) moves to the discharge port (1411) and is discharged together, thereby suppressing the compression loss in the two compression chambers (V1)(V2).

[0093] In addition, a plurality of first oil supply holes (1811) forming part of the oil supply passage (181) may be formed in the pivot plate (151). For example, the plurality of first oil supply holes (1811) may penetrate the interior of the pivot plate (151), and one end may be opened to the inner surface of the rotary shaft coupling part (153) from the lower end of the bushing bearing (155), and the other end may be opened to the rotary thrust surface (1512) facing the fixed thrust surface (1431). In this case, a plurality of oil supply connection grooves (1811a) may be formed to be sunken in at the corners of the inner surface of the rotary shaft coupling part (153) so as to be respectively connected to the plurality of first oil supply holes (1811). Accordingly, a plurality of first oil supply holes (1811) can penetrate the inner surface of the rotary shaft coupling part (153) into the turning thrust surface (1512). Through this, oil in the oil supply space (S) to be described later can be quickly and smoothly supplied to the thrust surface (1413)(1512) through the plurality of first oil supply holes (1811). The first oil supply holes (1811) will be described later together with the oil drainage passage (182).

[0094] The orbiting wrap (152) according to the present embodiment can extend from the upper surface (compression surface) of the orbiting plate portion (151) toward the fixed scroll (140). Accordingly, the orbiting wrap (152) can be interlocked with the fixed wrap (142) to form two pairs of compression chambers (V1) (V2).

[0095] The orbital wrap (152) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (142). For example, the orbital wrap (152) can be formed in a logarithmic spiral or in a plurality of circular arc curves.

[0096] However, as described above in the fixed wrap (142), when the orbital wrap (152) is formed in a logarithmic spiral, not only is the shape of the rotating shaft coupling portion (153) limited, but the stroke volume may also be reduced at the same wrap height and plate width. Accordingly, the orbital wrap (152) according to the present embodiment, like the fixed wrap (142), may be formed in a form in which the wrap curve connects a plurality of circular arcs having different diameters and origins. Accordingly, the orbital wrap (152), like the fixed wrap (142), may be formed such that the wrap thickness varies along the wrap formation direction.

[0097] For example, the swirl wrap (152) according to the present embodiment may be formed so that the wrap thickness of the discharge end, which is the center, is thicker than that of the suction end, which is the outermost end. Accordingly, the wrap strength of the swirl wrap (152) at the discharge end, which receives a relatively high gas force, can be increased, thereby suppressing damage to the swirl wrap (152). In addition, the wrap curve of the fixed wrap (142) can be formed wide, so that the stroke volume can be expanded at the same wrap height and plate width.

[0098] The orbital wrap (152) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In the present embodiment, an example is shown in which the wrap heights of the orbital wrap (152) are different along the wrap formation direction. For example, the wrap height of the orbital wrap (152) according to the present embodiment may be formed so that the wrap height of the discharge end, which is the center, is lower than the wrap height of the suction end, which is the outermost, based on the orbital step surface (1511). Accordingly, the wrap strength of the orbital wrap (152) at the discharge end, which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142).

[0099] The rotary shaft coupling portion (153) is a portion where the eccentric portion (1251) of the rotary shaft (125) is coupled, and may be formed in a cylindrical shape and may have a bushing bearing (155) provided on the inner surface thereof. Accordingly, the inner surface of the bushing bearing (155) may form the inner surface of the actual rotary shaft coupling portion (153).

[0100] The rotating shaft coupling portion (153) may be formed to be located on the inside of the orbital wrap (152). For example, the inner circumference of the rotating shaft coupling portion (153) may be formed at a position overlapping the discharge end of the orbital wrap (152) when projected in the axial direction. In other words, the outer circumference of the rotating shaft coupling portion (153) may be formed to be located on the same circle as an imaginary circle connecting the outer surface of the discharge end of the orbital wrap (152). Accordingly, the inner surface around the discharge end of the orbital wrap (152) is located inside the outer circumference of the rotating shaft coupling portion (153) as described above, that is, on the front end surface (153a) of the rotating shaft coupling portion (153). Then, the rotary shaft coupling portion (153) is formed to be sunken so as to overlap with the rotary wrap (152) in the radial direction, and the bearing area of ​​the rotary shaft coupling portion (153) is secured widely so as to stably support the rotary scroll (150) while forming a compression chamber (V1) (V2) in the front end face (153a) of the rotary shaft coupling portion (153).

[0101] Referring to FIG. 1, the back pressure chamber assembly (160) according to the present embodiment may be provided on the main frame (130) so as to make sliding contact with the orbiting scroll (150). In other words, the back pressure chamber assembly (160) may have a back pressure space portion (162) forming part of the back pressure chamber assembly (160) formed on the thrust support surface (1313) of the main frame (130) facing the orbiting scroll (150). Accordingly, the structure of the back pressure chamber assembly (160) may be simplified, making it easy to manufacture and assemble.

[0102] Specifically, the back pressure chamber assembly (160) may include a back pressure passage (161), a back pressure space (162), and a sealing member (163). The back pressure passage (161) penetrates the turning plate (151) to communicate between the compression chamber (V) and the back pressure space (162), the back pressure space (162) is formed in an annular shape to accommodate the back pressure passage (161), and the sealing member (163) is a member provided on an end surface of the back pressure space (162) facing the turning scroll (150) to form a back pressure chamber (160a) inside the back pressure space (162). Accordingly, the back pressure chamber assembly (160) forms a back pressure chamber (160a) that is connected to the compression chamber (V) between the main frame (130) and the orbiting scroll (150), thereby pressurizing the orbiting scroll (150) toward the fixed scroll (140).

[0103] The back pressure passage (161) may be formed to penetrate between the axial sides of the pivot plate (151). For example, only one back pressure passage (161) may be formed to communicate with one compression chamber (V1) (V2), or multiple back pressure passages (161) may be formed to communicate with each of the compression chambers (V1) (V2). This embodiment illustrates an example in which only one back pressure passage (161) is formed.

[0104] In this case, one end of the back pressure passage (161) may be formed to penetrate the side of the compression chamber (V1) (V2), and the other end of the back pressure passage (161) may be formed to penetrate the side of the back pressure chamber (160a). Accordingly, the compression chamber (V1) (V2) and the back pressure chamber (160a) are connected to each other through the back pressure passage (161), so that a portion of the refrigerant compressed in the compression chamber (V1) (V2) can quickly move to the back pressure chamber (160a).

[0105] Although not shown in the drawing, a back pressure valve (not shown) that opens and closes the back pressure passage (161) may be provided in the middle of the back pressure passage (161). For example, the back pressure valve may be formed to allow the movement of refrigerant from the compression chamber (V1)(V2) to the back pressure chamber (160a), while blocking the movement of refrigerant from the back pressure chamber (160a) to the compression chamber (V1)(V2). Accordingly, the pressure in the back pressure chamber (160a) can be varied, thereby suppressing pulsating pressure in the back pressure chamber (160a).

[0106] The back pressure space (162) may extend from one side of the main frame (130) facing the orbiting scroll (150), that is, from the thrust support surface (1313) of the main frame (130) toward the orbiting scroll (150). For example, the back pressure space (162) may be formed of a plurality of back pressure guides (1621)(1622) that extend annularly from the thrust support surface (1313) of the main frame (130) and are spaced apart from each other by a preset interval in the radial direction.

[0107] Specifically, the plurality of back pressure guides (1621)(1622) may be formed of an inner back pressure guide (1621) provided on the inner side and an outer back pressure guide (1622) provided on the outer side with the back pressure passage (161) therebetween. Each of the inner back pressure guides (1621) and the outer back pressure guides (1622) may be formed in an annular shape. Accordingly, a back pressure room (160a) may be formed between the inner back pressure guide (1621) and the outer back pressure guide (1622) together with a sealing member (1631)(1632) described later.

[0108] Among the plurality of back pressure guides (1621)(1622), the inner back pressure guide (1621) may be formed radially spaced apart from the inner surface of the rotation shaft coupling portion (153) provided at the center of the pivot plate portion (151) by a preset interval. Accordingly, when the inner back pressure guide (1621) is spaced apart from the outer surface of the rotation shaft (125) by a preset interval, a fuel supply space (S) may be formed between the inner surface of the inner back pressure guide (1621) and the outer surface of the rotation shaft (125). Through this, a portion of the oil sucked in through the oil passage (1252) of the rotating shaft (125) is stored in the oil supply space (S) between the inner surface of the inner pressure guide (1621) and the outer surface of the rotating shaft (125), so that the oil can be smoothly supplied to the oil supply passage (181) provided inside the rotating scroll (150) while lubricating the space between the orbiting scroll (150) and the sealing member (163).

[0109] In addition, an inner sealing groove (1651) may be formed on the leading surface of the inner pressure guide (1621), and an outer sealing groove (1652) may be formed on the leading surface of the outer pressure guide (1622). An inner sealing member (1631) may be slidably inserted into the inner sealing groove (1651), and an outer sealing member (1632) may be slidably inserted into the outer sealing groove (1652), respectively, in the axial direction. The side walls of the inner sealing member (1631) and the outer sealing member (1632) are pressed against the side walls of the inner sealing groove (1651) and the outer sealing groove (1652), respectively, by the pressure of the fuel supply space (S) and / or the pressure of the back pressure chamber (160a), and the axial side surface of the inner sealing member (1631) and the axial side surface of the outer sealing member (1632) facing the main frame (130) can be pressed against the main frame (130), respectively. Accordingly, the back pressure chamber (160a) provided inside the back pressure space (162) can be sealed.

[0110] Although not shown in the drawing, the back pressure space (162) may be formed in a circular shape that is sunken to a preset depth in the thrust support surface (1313) of the main frame (130). In this case, an inner sealing groove (1651) may be formed in a circular shape on the inner side of the back pressure space (162), and an outer sealing groove (1652) may be formed in a circular shape on the outer side. The inner sealing member (1631) and the outer sealing member (1632) described above may be inserted into these sealing grooves (1651)(1652) so as to be in close contact in the radial direction and movable in the axial direction, respectively.

[0111] The unexplained symbol 118 in the drawing is a subframe.

[0112] The operational effects of the scroll compressor according to the present embodiment as described above are as follows.

[0113] That is, when power is applied to the driving motor (120) and rotational force is generated, the orbiting scroll (150) eccentrically coupled to the rotation shaft (125) rotates relative to the fixed scroll (140) by the old ring (170). At this time, a first compression chamber (V1) and a second compression chamber (V2) that move continuously are formed between the fixed scroll (140) and the orbiting scroll (150).

[0114] Then, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually becomes narrower as the orbiting scroll (150) moves from the suction port (or suction chamber) (not shown) toward the discharge port (or discharge chamber) (1411) while performing the orbiting motion.

[0115] Then, the refrigerant is sucked into the low pressure section (110a) of the casing (110) through the refrigerant suction pipe (115), and a portion of this refrigerant is directly sucked into each of the suction pressure chambers (not shown) forming the first compression chamber (V1) and the second compression chamber (V2) and compressed, while the remaining refrigerant moves toward the drive motor (120), cools the drive motor (120), and is then sucked into the suction pressure chamber (not shown) together with other refrigerants.

[0116] Then, the refrigerant is compressed while moving along the movement path of the first compression chamber (V1) and the second compression chamber (V2). The refrigerant is discharged from the final compression chamber (V) to the upper space (110b) of the casing (110) through the discharge port (1411) of the fixed scroll (140), and the refrigerant is discharged to the outside of the compressor through the refrigerant discharge pipe (116).

[0117] At this time, a portion of the refrigerant compressed in the compression chamber (V1)(V2) moves to the back pressure chamber (160a) of the back pressure chamber assembly (160) provided between the rotating scroll (150) and the main frame (130) through the back pressure passage (161) before reaching the discharge port (1411). Accordingly, the back pressure chamber (160a) forms an intermediate pressure and pushes the sealing member (163) of the back pressure chamber assembly (160) toward the main frame (130).

[0118] Then, the orbiting scroll (150) is pressurized in the direction toward the fixed scroll (140) by the pressure of the back pressure chamber (160a) and rises. Accordingly, as the orbiting scroll (150) is pressed against the fixed scroll (140), it is possible to prevent the refrigerant in the compression chambers (V1) and (V2) on both sides from leaking from the high-pressure side compression chamber forming the intermediate pressure chamber to the low-pressure side compression chamber.

[0119] Meanwhile, the oil stored in the oil storage space (110c) of the casing (110) is sucked up through the oil passage (1252) of the rotary shaft (125), and some of this oil is sprayed from the upper end of the rotary shaft (125) into the internal space of the rotary shaft coupling portion (153). This oil flows down through the inner surface of the rotary shaft coupling portion (153), that is, between the inner surface of the bush bearing (155) and the outer surface of the rotary shaft (125), lubricates the space between the bush bearing (155) and the rotary shaft (125), and then accumulates in the oil supply space (S) between the main frame (130) and the orbiting scroll (150). Some of this oil flows between the sealing member (1631)(1632) forming the back pressure chamber assembly (160) and the orbiting scroll (150) to lubricate the space between the sealing member (1631)(1632) and the orbiting scroll (150), while the other oil lubricates the thrust surface (1413)(1512) between the orbiting scroll (150) and the fixed scroll (140) through the oil supply passage (181) penetrating the orbiting plate portion (151). A portion of the oil lubricating the thrust surface (1413)(1512) is discharged from the thrust surface (1413)(1512) through the drainage passage (182) and returned to the oil storage space (110c) of the casing, while a portion of the oil flows into the compression chamber (V) through the oil supply passage (181) and lubricates the sliding surface within the compression chamber (V).

[0120] Fig. 2 is a perspective view showing the compression unit in a scroll compressor according to the present embodiment in disassembly, Fig. 3 is a plan view showing the compression unit in Fig. 2 in an assembled state, and Fig. 4 is a cross-sectional view taken along line “Ⅳ-Ⅳ” of Fig. 3.

[0121] Referring to FIGS. 2 to 4, the fuel supply passage (181) according to the present embodiment may include a plurality of first fuel supply holes (1811), a first fuel supply groove (1812), and a second fuel supply groove (1813), and the fuel drain passage (182) may include a plurality of fuel drain grooves (1821). The fuel drain passage (182) may be connected to the middle of the fuel supply passage (181), that is, to the first fuel supply groove (1812). Accordingly, the oil sucked through the oil passage (1252) of the rotating shaft (125) is stored in the oil supply space (S) between the main frame (130) and the orbiting scroll (150), and after lubricating the thrust surface (1413)(1512) through the oil supply passage (181), some of it is recovered through the oil drain passage (182), while some of it can be supplied to the compression chamber (V). In this way, the oil stored in the oil supply space (S) is not drained immediately but lubricates the thrust surface (1413)(1512) first, so that the oil supply amount for the thrust surface (1413)(1512) can be secured.

[0122] Specifically, a plurality of first oil supply holes (1811) forming part of the oil supply passage (181) may be formed by penetrating the interior of the orbiting plate (151) as described above, with one end penetrating the inner surface of the rotating shaft coupling part (153) and the other end penetrating the orbiting thrust surface (1512). Accordingly, oil stored in the oil supply space (S) between the main frame (130) and the orbiting scroll (150) can be quickly and smoothly moved to the thrust surface (1413) (1512) between the fixed scroll (140) and the orbiting scroll (150) through the plurality of first oil supply holes (1811).

[0123] Although not shown in the drawing, only one first fueling hole (1811) may be formed. In this case, it may be advantageous in terms of fueling to have the first fueling hole (1811) have its outlet located around the suction pressure chamber and to form the inner diameter of the first fueling hole (1811) large.

[0124] The first oil refueling groove (1812) may be formed to be connected to the plurality of first oil refueling holes (1811) on the fixed thrust surface (1431) facing the other end of the plurality of first oil refueling holes (1811). In other words, the first oil refueling groove (1812) may be formed in an annular shape to surround the fixed wrap (142). Accordingly, oil moving to the first oil refueling groove (1812) through the plurality of first oil refueling holes (1811) can lubricate the entire thrust surface (1413) (1512) along the first oil refueling groove (1812).

[0125] The first lubrication groove (1812) can be formed with the same cross-sectional area along the circumference. Accordingly, the first lubrication groove (1812) can be easily processed, while the entire thrust surface (1413) (1512) can be quickly and uniformly lubricated.

[0126] In addition, a communication groove (1812a) may be formed in the middle of the first fueling groove (1812), that is, at a portion facing the other end of the first fueling hole (1811). The communication groove (1812a) may be formed so that its inner diameter is greater than or equal to the turning radius of the orbiting scroll (150). In other words, the cross-sectional area of ​​the communication groove (1812a) may be formed larger than the cross-sectional area of ​​the first fueling groove (1812). Accordingly, when the orbiting scroll (150) rotates, the other end of the first fueling hole (1811) is always accommodated in the communication groove (1812a), so that the first fueling hole (1811) and the first fueling groove (1812) may be continuously communicated.

[0127] The second oil supply groove (1813) may extend from the inner surface of the first oil supply groove (1812) toward the compression chamber (V). In other words, the second oil supply groove (1813) may be formed to extend radially around the suction end of the fixed wrap (142), but communicate with the suction pressure chamber forming the outermost compression chamber (V) by bypassing the fixed wrap (142). Accordingly, a portion of the oil moving along the first oil supply groove (1812) may be supplied to the compression chamber (V) through the second oil supply groove (1813).

[0128] In this case, the cross-sectional area of ​​the second oil supply groove (1813) may be formed to be almost the same as the cross-sectional area of ​​the first oil supply groove (1812), but may be formed to be smaller than or equal to the cross-sectional area of ​​the oil drain groove (1821) to be described later. For example, the cross-sectional area of ​​the second oil supply groove (1813) may be formed to be smaller than the cross-sectional area of ​​the oil drain groove (1821). Accordingly, even when the pressure of the compression chamber, that is, the suction pressure decreases due to the change in the volume of the suction pressure chamber during operation of the compressor, it is possible to suppress excessive inflow of high-pressure and / or high-temperature oil into the compression chamber (more precisely, the suction pressure chamber) (V), thereby reducing the suction loss.

[0129] Meanwhile, the drainage groove (1821) forming the drainage passage (182) may extend from the outer surface of the first supply groove (1812) toward the inner surface of the casing (110). In other words, the drainage groove (1821) may be formed on the fixed thrust surface (1431) facing the pivot thrust surface (1512), and while one end may be connected to the outer surface of the first supply groove (1812), the other end may be formed to extend radially toward the outer surface of the fixed side wall portion (143) forming the outer surface of the fixed thrust surface (1431). In this case, the other end of the drainage groove (1821) may be formed to penetrate the outer surface of the fixed side wall portion (143), but as in the present embodiment, the other end of the drainage groove (1821) may be formed in a closed shape by extending only to near the outer surface of the fixed side wall portion (143). In the former case, the oil moving along the first oil supply groove (1812) can be quickly drained and recovered through the oil drain groove (1821), and in the latter case, since the other end of the oil drain groove (1821) is blocked, the oil moving along the first oil supply groove (1812) is advantageously left in the first oil supply groove (1812), so that the thrust surface (1413)(1512) can be lubricated more effectively. The latter can be more effective when applied to a compressor in which the fixed scroll (140) is positioned lower than the orbiting scroll (150), such as a bottom compression scroll compressor.

[0130] The oil drainage groove (1821) may be extended to a length that is not covered by the orbiting scroll (150), for example, to a length that can be at least partially exposed to the outer surface of the orbiting plate (151) when the orbiting scroll (150) rotates. Accordingly, when the compressor is in operation, the oil drainage passage (182) is always open to the internal space of the casing (110), and the oil sucked through the oil passage (1252) of the rotating shaft (125) can be smoothly recovered.

[0131] As described above, since the oil drainage passage (182) is connected to the middle of the oil supply passage (181), the oil sucked through the oil passage (1252) of the rotary shaft (125) can be guided to be drained while passing through the oil supply passage (181). This prevents the oil sucked along the rotary shaft (125) from being drained directly toward the internal space of the casing (110), thereby ensuring a sufficient amount of oil to be supplied to the sliding surfaces, including the thrust surface (1413) (1512).

[0132] In addition, since the first oil supply groove (1812) forming part of the oil supply passage (181) is formed in an annular shape on the fixed thrust surface (1431), lubrication can be evenly provided between the fixed thrust surface (1431) and the orbiting thrust surface (1512). Through this, oil can be stably supplied to the thrust surface (1413)(1512) between the fixed scroll (140) and the orbiting scroll (150), thereby reducing frictional loss on the thrust surface (1413)(1512), thereby improving compressor performance.

[0133] In addition, since the second oil refueling groove (1813), which forms part of the oil refueling passage (181), extends from the first oil refueling groove (1812) to the suction pressure chamber, oil can smoothly flow from the relatively high-pressure first oil refueling groove (1812) to the relatively low-pressure suction pressure chamber. In this case, by appropriately adjusting the cross-sectional area of ​​the second oil refueling groove (1813), excessive oil flow into the compression chamber (V) can be suppressed.

[0134] In addition, as the oil drainage groove (1821) forming the oil drainage passage (182) extends radially from the first oil supply groove (1812), oil can be drained after passing through at least a portion of the oil supply passage (181), as described above. Through this, sufficient oil supply to the thrust surface (1413)(1512) between the fixed scroll (140) and the orbiting scroll (150) can be secured. In this case, as the oil drainage groove (1821) is formed to be exposed outside the orbiting radius of the orbiting scroll (150), the oil drainage groove (1821) is continuously connected with the internal space of the casing (110), so that the oil lubricating the thrust surface (1413)(1512) can be smoothly drained into the internal space of the casing (110).

[0135] In addition, as the rotating shaft coupling portion (153) is formed to be sunken toward the orbiting wrap (152) and a portion of the orbiting wrap (152) is extended to the front end face (153a) of the rotating shaft coupling portion (153), a compression chamber (V) can be formed at the center of the orbiting scroll (or fixed scroll) (150). Through this, as the rotating shaft coupling portion (153) is extended toward the orbiting wrap (152), the compression cycle of the compression chamber (V) is lengthened, thereby increasing the compression ratio and improving the volumetric efficiency. In addition, the wrap height at the discharge end of the orbiting wrap (152) is lowered and the wrap thickness is thickened, thereby increasing the wrap strength of the orbiting wrap (152) and suppressing wrap breakage. The same applies to the fixed wrap (142).

[0136] Meanwhile, there are other examples of refueling routes, as follows:

[0137] That is, in the embodiment described above, the fuel passage is continuously opened toward the compression chamber, but in some cases, the fuel passage and the compression chamber may be selectively opened and closed.

[0138] Fig. 5 is an exploded perspective view of another embodiment of a fuel supply passage, Fig. 6 is an assembly plan view of Fig. 5, Fig. 7 is a cross-sectional view taken along line “Ⅶ-Ⅶ” of Fig. 6, and Figs. 8a and 8b are cross-sectional views showing the operation of the fuel supply control valve of Fig. 5.

[0139] Referring to FIGS. 5 to 7, the scroll compressor according to the present embodiment has a back pressure chamber assembly (160) provided between the main frame (130) and the orbiting scroll (150), but the basic configuration and the resulting operational effects of the fixed scroll (140) and the orbiting scroll (150) are almost the same. For example, the orbiting scroll (150) may have an orbiting wrap (152) formed on the first side (151b) of the orbiting plate portion (151), and a rotating shaft coupling portion (153) formed to be recessed by a preset depth in the direction from the second side (151c) of the orbiting plate portion (151) toward the first side (151b). Accordingly, the rotary shaft coupling portion (153) is formed to be sunken toward the orbiting wrap (152), so that the gap between the point of application where the rotational force is applied to the orbiting scroll (150) and the point of application where the compressive force is applied is narrowed, thereby stabilizing the behavior of the orbiting scroll (150).

[0140] In addition, a first oil supply hole (1811) may be formed by penetrating from the inner surface of the rotating shaft coupling portion (153) to the orbiting thrust surface (1512) provided on the first side of the orbiting plate portion (151) inside the orbiting scroll (150), and a first oil supply groove (1812) may be formed in an annular shape on the fixed thrust surface (1431) of the fixed scroll (140). In addition, an oil drain groove (1821) may be formed on the fixed thrust surface (1431) that extends radially from the outer surface of the first oil supply groove (1812) toward the outer surface of the fixed scroll (140). Accordingly, oil sucked through the oil passage (1252) of the rotating shaft (125) flows into the first oil supply groove (1812) through the first oil supply hole (1811) to lubricate the thrust surface (1413) (1512) between the fixed scroll (140) and the orbiting scroll (150), and a portion of this oil can be recovered into the internal space of the casing (110) through the oil drain groove (1821).

[0141] However, in the present embodiment, a second oil supply hole (1814) extending from the middle of the inner surface of the first oil supply groove (1812) to the compression chamber (V) is formed, and a fuel supply control valve (1815) that selectively opens and closes the second oil supply hole (1814) may be provided in the second oil supply hole (1814). Accordingly, the amount of oil supplied to the compression chamber (V) can be appropriately controlled, thereby preventing excessive high-pressure and / or high-temperature oil from flowing into the compression chamber (V).

[0142] Specifically, the second refueling hole (1814) may include a first hole portion (1814a) and a second hole portion (1814b). The first hole portion (1814a) may be connected to the first refueling groove (1812) through a refueling connection hole (1814c), and the second hole portion (1814b) may extend from the first hole portion (1814a) and be connected to the compression chamber (V). In this case, the cross-sectional area of ​​the second hole portion (1814b) may be formed smaller than the cross-sectional area of ​​the first hole portion (1814a), so that a valve support surface (1814d) may be formed in a step between the first hole portion (1814a) and the second hole portion (1814b). Accordingly, the valve stop surface (1815c) of the fuel control valve (1815) to be described later is caught on the valve support surface (1814d) so that the first valve part (1815a) can reciprocate only within the first hole part (1814a).

[0143] The fuel control valve (1815) may include a first valve portion (1815a) and a second valve portion (1815b). The first valve portion (1815a) may be slidably inserted into the first hole portion (1814a), and the second valve portion (1815b) may extend from the first valve portion (1815a) and be slidably inserted into the second hole portion (1814b). In this case, the cross-sectional area of ​​the second valve portion (1815b) may be formed smaller than the cross-sectional area of ​​the first valve portion (1815a), so that a valve stop surface (1815c) may be formed with a step between the first valve portion (1815a) and the second valve portion (1815b). Accordingly, the valve stop surface (1815c) of the fuel control valve (1815) may be caught on the valve support surface (1814d) as described above, and its movement in the longitudinal direction may be restricted.

[0144] In addition, in this case, the length of the second valve portion (1815b) may be formed to be smaller than or equal to the length of the second hole portion (1814b). Accordingly, the second valve portion (1815b) can be prevented from being exposed to the inside of the compression chamber (V) while the valve stop surface (1815c) of the fuel supply control valve (1815) is in close contact with the valve support surface (1814d). Through this, the reliability between the fixed scroll (140) and the orbiting scroll (150) can be secured, while the flow resistance between the second hole portion (1814b) and the second valve portion (1815b) can be minimized.

[0145] In addition, a fuel guide hole (1815d) that communicates between the first fuel supply groove (1812) and the compression chamber (V) may be formed inside the fuel control valve (1815). For example, one end of the fuel guide hole (1815d) may pass through the first valve portion (1815a) and be connected to the first hole portion (1814a), and the other end of the fuel guide hole (1815d) may pass through the outer surface of the second valve portion (1815b) and be connected to the inside of the second hole portion (1814b). In this case, the cross-sectional area of ​​the fuel guide hole (1815d) may be formed to be smaller than or equal to the cross-sectional area of ​​the fuel drain groove (1821), preferably smaller. Accordingly, the amount of fuel flowing into the compression chamber (more precisely, the suction pressure chamber) (V) through the fuel guide hole (1815d) can be varied depending on the overlapping length between the second valve part (1815b) and the second hole part (1814b).

[0146] In addition, an elastic member (1816) may be provided between one end of the second fueling hole (1814) and the fueling control valve (1815) facing it to elastically support the fueling control valve (1815). For example, the elastic member (1816) may be formed of a compression coil spring, and one end may be supported between the first hole portion (1814a) and the second hole portion (1814b), while the other end may be supported between the first valve portion (1815a) and the second valve portion (1815b). In other words, one end of the elastic member (1816) may be supported on the valve support surface (1814d), and the other end of the elastic member (1816) may be supported on the valve stop surface (1815c). Accordingly, the amount of fuel supplied to the compression chamber (V) can be controlled by opening and closing the fuel control valve (1815) according to the pressure difference between the first fuel supply home (1812) and the compression chamber (more precisely, the pressure of the suction pressure chamber) (V).

[0147] For example, when the pressure of the compression chamber (V) is high as in Fig. 8a, in other words, when the suction pressure becomes higher than a certain pressure due to the change in the volume of the suction pressure chamber, the pressure of the oil flowing into the first hole (1814a) of the second fuel supply hole (1814) from the first fuel supply groove (1812) becomes smaller than the combined force of the pressure of the compression chamber (V) and the elastic force of the elastic member (1816). Then, the fuel supply control valve (1815) is pushed to move to the opposite side of the compression chamber (V) by the pressure of the compression chamber (V) and the elastic force of the elastic member (1816). Then, the second valve part (1815b) of the oil supply control valve (1815) slides on the second hole part (1814b) and moves to the opposite side of the compression chamber (V), thereby shortening the overlapping length (L1) between the second valve part (1815b) and the second hole part (1814b). Then, the flow resistance in the second hole part (1814b) is reduced, so that the oil flowing into the second hole part (1814b) through the oil supply guide hole (1815d) can quickly and smoothly flow into the compression chamber (V). Through this, the oil is sufficiently introduced into the compression chamber (V), thereby reducing the friction loss within the compression chamber (V), and at the same time, the pressure within the compression chamber (V) is high, so that the suction loss within the compression chamber (V) due to the oil inflow can be suppressed from increasing.

[0148] On the other hand, as in Fig. 8b, when the pressure in the compression chamber (V) is low, that is, when the suction pressure becomes lower than a certain pressure due to the change in the volume of the suction pressure chamber, the oil flowing into the first hole (1814a) of the second fuel supply hole (1814) from the first fuel supply groove (1812) overcomes the elastic force of the elastic member (1816) and pressurizes the fuel supply control valve (1815) toward the compression chamber (V). Then, the fuel supply control valve (1815) is pushed toward the compression chamber (V) by the pressure of the first fuel supply groove (1812). Then, as the second valve part (1815b) of the fuel supply control valve (1815) slides on the second hole part (1814b) and moves toward the compression chamber (V), the overlapping length (L1') between the second valve part (1815b) and the second hole part (1814b) increases. Then, the flow resistance in the second hole part (1814b) increases, so that the oil flowing into the second hole part (1814b) through the fuel supply guide hole (1815d) may be delayed in flowing into the compression chamber (V) due to the flow resistance. Through this, when the pressure inside the compression chamber (V) is low, the inflow of high-temperature and high-pressure oil into the compression chamber (V) can be minimized, thereby suppressing an increase in suction loss inside the compression chamber (V).

[0149] Meanwhile, other examples of fuel supply and discharge channels are as follows.

[0150] That is, in the above-described embodiment, the fuel supply passage and the fuel drain passage are formed in the fixed scroll, but in some cases, the fuel supply passage and the fuel drain passage may be formed in the orbiting scroll.

[0151] Fig. 9 is an exploded perspective view of another embodiment of a fuel supply channel and a fuel drain channel, and Fig. 10 is an assembled plan view of Fig. 9.

[0152] Referring to FIGS. 9 and 10, the scroll compressor according to the present embodiment has a back pressure chamber assembly (160) provided between the main frame (130) and the orbiting scroll (150), but the basic configuration and the resulting operational effects of the fixed scroll (140) and the orbiting scroll (150) are almost the same. For example, the orbiting scroll (150) may have an orbiting wrap (152) formed on the first side (151b) of the orbiting plate portion (151), and a rotating shaft coupling portion (153) formed to be recessed by a preset depth in the direction from the second side (151c) of the orbiting plate portion (151) toward the first side (151b). Accordingly, the rotary shaft coupling portion (153) is formed to be sunken toward the orbiting wrap (152), so that the gap between the point of application where the rotational force is applied to the orbiting scroll (150) and the point of application where the compressive force is applied is narrowed, thereby stabilizing the behavior of the orbiting scroll (150).

[0153] In addition, a first oil supply hole (1811) may be formed by penetrating from the inner circumference of the rotary shaft coupling portion (153) to the rotary thrust surface (1512) provided on the first side surface (151b) of the rotary plate portion (151) inside the orbiting scroll (150). Accordingly, oil sucked in through the oil passage (1252) of the rotary shaft (125) can be quickly supplied to the thrust surface (1413) (1512) between the fixed scroll (140) and the orbiting scroll (150) through the first oil supply hole (1811).

[0154] However, in the present embodiment, the first oil supply groove (1812) connected to the first oil supply hole (1811) is formed in an annular shape on the orbiting thrust surface (1512) of the orbiting scroll (150), and the oil drain groove (1821) may be formed to extend radially from the outer surface of the first oil supply groove (1812) toward the outer surface of the orbiting scroll (150). In this case, the oil drain groove (1821) may be formed to penetrate so as to be open to the outer surface of the orbiting scroll (150). Accordingly, the oil flowing into the thrust surface (1413)(1512) through the first oil supply hole (1811) is evenly distributed over the entire thrust surface (1413)(1512) through the first oil supply groove (1812), thereby smoothly lubricating the thrust surface (1413)(1512) between the fixed scroll (140) and the orbiting scroll (150), and at the same time, a portion of this oil can be recovered into the internal space of the casing (110) through the oil drain groove (1821) provided in the orbiting scroll (150).

[0155] As described above, when the oil supply passage (181) and the oil drain passage (182) are provided in the orbiting scroll (150), the oil is subjected to centrifugal force during the orbiting movement of the orbiting scroll (150) and is widely spread on the thrust surface (1413) (1512), and can also be quickly drained through the oil drain groove (1821).

[0156] In addition, in this case, the second oil supply groove (1813) may be formed to be connected to the first oil supply groove (1812) in the orbiting scroll (150), or may be formed to be connected to the first oil supply groove (1812) in the fixed scroll (140) as in the embodiment of FIG. 2 described above. In the former case, the fixed scroll (140) can be easily processed by forming the oil supply passage (181) in the orbiting scroll (150) as a single unit, and in the latter case, the excessive inflow of oil into the compression chamber (V) can be simply and effectively controlled. This embodiment illustrates the former case, that is, an example in which the second oil supply groove (1813) is formed in the orbiting scroll (150).

[0157] Although not shown in the drawing, instead of the second oil refueling groove (1813), a second oil refueling hole (1814) may be formed in the fixed scroll (or orbiting scroll) (140) as in the embodiment of Fig. 5, and an oil refueling control valve (1815) may be inserted into the second oil refueling hole (1814). In this case, as described above, by appropriately controlling the oil supply to the compression chamber (V), suction loss due to excessive oil inflow into the compression chamber (V) can be suppressed.

[0158] Meanwhile, there are other embodiments of the back pressure chamber assembly as follows.

[0159] That is, in the above-described embodiment, the back pressure chamber assembly is formed on the main frame facing the orbiting scroll, but in some cases, the back pressure chamber assembly may be formed on the orbiting scroll facing the main frame.

[0160] Fig. 11 is a cross-sectional view showing a portion of a scroll compressor to which another embodiment of a back pressure chamber assembly is applied.

[0161] Referring to FIG. 11, the back pressure chamber assembly (160) according to the present embodiment is provided between the main frame (130) and the orbiting scroll (150), and may be formed on the second side (151c) of the orbiting plate portion (151) facing the main frame (130). For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so that it can orbit together with the orbiting scroll (150), and the back pressure space portion (162) forming a part of the back pressure chamber assembly (160) may extend as a single body from the rear surface of the orbiting plate portion (151) facing the main frame (130) toward the main frame (130).

[0162] In addition, a floating member (165) is slidably inserted into the back pressure space (162), and the floating member (165) can form a sealed back pressure chamber (160a) inside the back pressure space (162) by connecting a plurality of first sliding members (1651) forming the side surfaces thereof to each other by a second sliding member (1652). Accordingly, even if the floating member (165) moves along the back pressure guides (1621)(1622) on both sides forming the back pressure space (162), the inside of the back pressure space (162) forming the back pressure chamber (160a) can be sealed by the floating member (165).

[0163] In this case, a fuel supply passage (181) formed of a first fuel supply hole (1811), a first fuel supply groove (1812), and a second fuel supply groove (or a second fuel supply hole) (1813) may be formed in the fixed scroll (140) and / or the orbiting scroll (150), and a fuel drain passage (182) formed of a fuel drain groove (1821) may be formed in the middle of the first fuel supply groove (1812). Since these fuel supply passages (181) and fuel drain passages (182) are the same as those in the embodiments of FIGS. 2, 5, and 9 described above, the description thereof will be replaced with the description of the embodiments described above.

[0164] As described above, the back pressure chamber assembly (160) is provided on the orbiting scroll (150), and the back pressure chamber assembly (160) can perform a rotational movement together with the orbiting scroll (150). Accordingly, the back pressure area of ​​the back pressure chamber assembly (160) can be expanded.

[0165] In addition, the opening side of the back pressure space portion (162) forming part of the back pressure chamber assembly (160) may be blocked by a floating member (165) that is slidably coupled to the back pressure space portion (162). Accordingly, it is possible to effectively prevent the refrigerant in the back pressure chamber (160a) from leaking into the low pressure portion (110a).

[0166] Although not illustrated in the drawing, the back pressure space (162) may be inserted into and joined to the orbiting scroll. In this case, the back pressure space (162) may be formed of a lightweight material and / or a low-hardness material. This reduces the weight of the orbiting scroll, including the back pressure space (162), while simultaneously suppressing wear between the back pressure space (162) and the floating member (165), thereby enhancing reliability.

Claims

1. Casing; A main frame fixed inside the above casing; A fixed scroll coupled to the above mainframe; An orbiting scroll having a turning plate portion provided between the main frame and the fixed scroll, a turning wrap provided in the turning plate portion to form a compression chamber together with the fixed wrap of the fixed scroll, a rotating shaft coupling portion recessed in the turning plate portion toward which the turning wrap is formed and into which a rotating shaft is inserted, and a first oil supply hole penetrating from an inner circumferential surface of the turning shaft coupling portion to one side of the turning plate portion facing the fixed scroll; An oil supply passage provided on at least one of the fixed scroll and the orbiting scroll so as to be connected to the first oil supply hole, and guiding oil sucked through the rotating shaft to a thrust surface between the fixed scroll and the orbiting scroll; and It includes an oil drainage passage provided on at least one of the fixed scroll and the rotating scroll, and drains oil sucked through the rotating shaft into the interior of the casing. The above drainage passage is, A scroll compressor connected to the first refueling hole and connected to the middle of the refueling passage.

2. In paragraph 1, The above refueling route is, It includes a first oil supply groove provided on at least one thrust surface among the fixed thrust surface of the fixed scroll and the rotating thrust surface of the rotating scroll facing it, A scroll compressor in which the first oil supply groove is formed in an annular shape and the oil drainage passage is connected in the middle of the first oil supply groove.

3. In paragraph 2, The above fuel drainage passage includes a fuel drainage groove that is sunken into the fixed thrust surface by a preset depth and connected to the first fuel drainage groove, The above-mentioned home is, A scroll compressor in which at least a portion of the orbiting scroll is exposed to the outside of the orbiting scroll during the orbiting motion of the orbiting scroll.

4. In paragraph 2, The above fuel passage includes a fuel groove that is sunken to a preset depth in the turning thrust surface and connected to the first fuel groove, The above-mentioned home is, A scroll compressor having an opening on the outer surface of the above-mentioned rotating scroll and communicating with the interior of the above-mentioned casing.

5. In paragraph 1, The above first oiling hole is opened to the orbiting thrust surface of the orbiting scroll facing the fixed thrust surface of the fixed scroll, A first refueling groove is formed on the above fixed thrust surface, which is sunken to a preset depth. The above first fuel home is, A scroll compressor extending along the above fixed thrust surface and connected to the first oil supply hole.

6. In paragraph 5, The above fueling passage includes at least one communication groove that is sunken into the fixed thrust surface by a preset depth and accommodates the first fueling hole in the middle of the first fueling groove, The cross-sectional area of ​​the above flue groove is A scroll compressor formed with a cross-sectional area larger than that of the first fuel refueling groove.

7. In paragraph 5, The above fuel supply passage extends from the first fuel supply groove and forms a second fuel supply groove that is connected to the compression chamber, The cross-sectional area of ​​the above second fuel groove is A scroll compressor formed to have a cross-sectional area smaller than or equal to the cross-sectional area of ​​the above-mentioned oil passage.

8. In paragraph 5, The above fuel passage further includes a second fuel hole penetrating between the first fuel groove and the compression chamber, A scroll compressor having a second fuel supply hole provided with a fuel supply control valve that selectively opens and closes the second fuel supply hole.

9. In paragraph 8, The above second fueling hole is, A first hole portion connected to the first refueling groove; and It includes a second hole portion extending from the first hole portion and communicating with the compression chamber, and formed with a cross-sectional area smaller than that of the first hole portion. The above fuel control valve, A first valve part that is slidably inserted into the first hole part; A second valve part extending from the first valve part and slidably inserted into the second hole part, and formed to be smaller than or equal to the length of the second hole part; and It includes a fuel supply guide hole that penetrates the first valve part and is connected to the first hole part at one end, and penetrates the second valve part and is connected to the compression chamber at the other end. The other end of the above refueling guide hole is A scroll compressor that penetrates the outer surface of the second valve section.

10. In paragraph 9, A scroll compressor, wherein an elastic member is provided between the first hole portion and the first valve portion to elastically support the fuel supply control valve toward the first hole portion.

11. In paragraph 1, The above first oiling hole is opened to the orbiting thrust surface of the orbiting scroll facing the fixed thrust surface of the fixed scroll, A first fuel refueling groove is formed on the above-mentioned turning thrust surface, which is sunken to a preset depth. The above first fuel home is, A scroll compressor extending along the above-mentioned turning thrust surface and connected to the above-mentioned first fueling hole.

12. In paragraph 11, The above fuel supply passage is sunk to a preset depth in the above turning thrust surface to form a second fuel supply groove that is connected to the compression chamber. The cross-sectional area of ​​the above second fuel groove is A scroll compressor formed to have a cross-sectional area smaller than or equal to the cross-sectional area of ​​the above-mentioned oil passage.

13. In any one of paragraphs 1 to 12, It further includes a back pressure chamber assembly provided between the above-mentioned orbiting scroll and the main frame facing it, and pressurizing the above-mentioned orbiting scroll toward the above-mentioned fixed scroll. The above pressure chamber assembly is, A scroll compressor provided on one side of the main frame facing the above-mentioned rotating scroll.

14. In paragraph 13, The above pressure chamber assembly is, A pressure relief passage penetrating the rotating scroll to communicate with the compression chamber; A pressure relief space formed in an annular shape to accommodate the pressure relief passage; and A scroll compressor including a sealing member provided on an end surface of the back pressure space portion facing the above-mentioned rotating scroll and forming a back pressure chamber inside the back pressure space portion.

15. In any one of paragraphs 1 to 12, It further includes a back pressure chamber assembly provided between the above-mentioned orbiting scroll and the main frame facing it, and pressurizing the above-mentioned orbiting scroll toward the above-mentioned fixed scroll. The above pressure chamber assembly is, A scroll compressor provided on one side of the above-mentioned rotating scroll facing the above-mentioned main frame.

16. In paragraph 15, The above pressure chamber assembly is, A pressure relief passage penetrating the rotating scroll to communicate with the compression chamber; A pressure relief space formed in an annular shape to accommodate the pressure relief passage; and A scroll compressor including a floating member that is slidably coupled to the above-mentioned back pressure space to form a back pressure chamber inside the back pressure space.

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