Scroll compressor

Abstract

Disclosed is a scroll compressor. The scroll compressor can include a housing, a main frame, an orbiting scroll, a fixed scroll, a back pressure space, a back pressure passage, and a back pressure valve which can be provided in the back pressure passage to selectively open and close the back pressure passage, the back pressure passage can communicate with a plurality of compression chambers having different pressures from each other in the compression chamber. Thus, the back pressure passage can selectively open and close the corresponding compression chamber and the back pressure space through the back pressure valve, and the back pressure of the back pressure space can be appropriately changed according to the operating condition of the compressor, thereby being able to suppress the inter-compression chamber leakage and / or the inter-scroll friction loss. In addition, thus, the operating region of the compressor can be expanded.

Description

Technical Field

[0001] This invention relates to a scroll compressor. Background Technology

[0002] Compressors used in the refrigeration cycle of refrigerators or air conditioners compress refrigerant gas and transport it to the condenser. Air conditioners primarily use rotary or scroll compressors. Scroll compressors are not only used in air conditioners but have also been increasingly applied in recent years to compressors for water heaters, which require higher pressure ratios than air conditioners.

[0003] In a scroll compressor, if the drive unit (or electric unit) and the compression unit are contained in one housing, it is a hermetically sealed compressor; if they are set up separately, it is an open compressor. If the compression unit is located above the drive unit, it is an upper compression type; if it is located below the drive unit, it is a lower compression type. If the space accommodating the drive unit is at suction pressure, it is a low-pressure type; if it is at discharge pressure, it is a high-pressure type.

[0004] Furthermore, the scroll compressor includes a fixed scroll disk with a fixed scroll portion and a rotating scroll disk with a rotating scroll portion that meshes with the fixed scroll portion. Scroll compressors can be classified into rotating back pressure type and fixed back pressure type based on the back pressure method. The rotating back pressure type forms a back pressure space on the back side of the rotating scroll disk, while the fixed back pressure type forms a back pressure chamber on the back side of the fixed scroll disk. This embodiment can be applied to scroll compressors using the rotating back pressure type.

[0005] In the scroll compressor described above, a thrust bearing surface is formed between the rotating scroll and the fixed scroll, allowing the rotating scroll to rotate while in sliding contact with the fixed scroll. In this case, in the back-pressure type, a back-pressure space is formed between the rotating scroll and the supporting main frame. The back pressure in this back-pressure space applies pressure to the rotating scroll towards the fixed scroll, causing the two scrolls to adhere tightly together, thereby suppressing leakage between the compression chambers. In other words, a back-pressure passage can be formed between the compression chamber (which forms the intermediate pressure) and the back-pressure space, allowing a portion of the compressed refrigerant to move from the compression chamber to the back-pressure space, thus creating back pressure at that space.

[0006] However, in a scroll compressor with a single back pressure path as described above, the back pressure in the back pressure space remains constant regardless of the compressor's operating conditions. Therefore, depending on the compressor's operating conditions, leakage between the compression chambers may occur, or frictional losses due to excessive contact may occur. In other words, under low pressure ratio operating conditions, the back pressure in the back pressure space is lower than the demand pressure, preventing the rotating scroll from maintaining a tight seal with the fixed scroll, leading to leakage between the compression chambers. Under high pressure ratio operating conditions, the pressure in the back pressure space is higher than the demand pressure, causing the rotating scroll to be too tightly fitted with the fixed scroll, resulting in increased frictional losses. Consequently, the compressor's operating range may become narrower. Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] The purpose of this invention is to provide a scroll compressor capable of suppressing leakage between compression chambers and / or frictional losses at the bearing surfaces between scroll plates.

[0009] Another object of the present invention is to provide a scroll compressor capable of appropriately adjusting the back pressure of the back pressure space according to operating conditions.

[0010] Another object of the present invention is to provide a scroll compressor that simplifies the control of the opening and closing of the back pressure passage, including the back pressure passage connecting the compression chamber and the back pressure space.

[0011] Technical solutions to the problem

[0012] To achieve the objectives of this invention, a scroll compressor comprising a housing, a main frame, a rotary scroll plate, a fixed scroll plate, a back pressure space, a back pressure passage, and a back pressure valve can be provided. The housing may have a discharge space. The main frame may be disposed inside the housing. The rotary scroll plate may axially support the main frame. The fixed scroll plate may be connected to the main frame across the rotary scroll plate and together with the rotary scroll plate form a compression chamber. The back pressure space may be disposed between the main frame and the rotary scroll plate. The back pressure passage may be disposed on the fixed scroll plate and communicate with the compression chamber. The back pressure valve may selectively open and close the back pressure passage. The back pressure passage may communicate with a plurality of compression chambers having different pressures. Thus, the back pressure passage can selectively open and close corresponding compression chambers and back pressure spaces through the back pressure valve, and appropriately change the back pressure of the back pressure space according to the compressor's operating conditions, thereby suppressing leakage between compression chambers and / or frictional losses between scroll plates. In addition, this allows for an expansion of the compressor's operating range.

[0013] As an example, the fixed scroll plate may also be provided with a valve pressurization passage connecting the back pressure passage and the discharge space of the housing. The back pressure valve may be arranged with one side facing the valve pressurization passage and slidingly inserted into the back pressure passage under the pressure of the discharge space. Thus, the back pressure valve can move under the pressure of the refrigerant transmitted from the discharge space through the valve pressurization passage and selectively connect the compression chamber and the valve pressurization passage, thereby simplifying the back pressure valve.

[0014] For example, the valve pressure passage facing the center of the back pressure valve is formed so that it is on the same line as the center of the back pressure valve. Therefore, by forming the inner diameter of the back pressure passage as small as possible, the inner diameter of the back pressure valve and / or the weight of the back pressure valve can be minimized, thereby improving valve responsiveness.

[0015] Additionally, the back pressure valve may include a valve body and a connecting passage. The valve body may have a plurality of opening and closing portions that selectively open and close the back pressure passage, and a connecting portion connecting the plurality of opening and closing portions. The connecting passage may selectively communicate with the back pressure passage depending on the position of the valve body. The connecting passage may be formed through the interior of the valve body. Thus, the connecting passage may move a corresponding compression chamber toward the back pressure space according to the position of the valve body.

[0016] Specifically, the connection passage may include a first passage portion and a second passage portion. The first passage portion may be disposed at the connection portion. The second passage portion may be disposed at one of the plurality of opening and closing portions adjacent to the back pressure space and communicate with the first passage portion. At least a portion of the second passage portion may be formed on the same line as the first passage portion along the back pressure passage. Thus, the refrigerant in the compression chamber can move rapidly into the back pressure space.

[0017] More specifically, the opening and closing part facing the valve pressure passage among the plurality of opening and closing parts can be formed in a blocked shape and slidably inserted into the back pressure passage. Thus, the back pressure valve can uniformly receive the pressure of the refrigerant transmitted from the discharge space through the valve pressure passage, while simultaneously tightly sealing the space between the two compression chambers forming the intermediate pressure and the valve pressure passage.

[0018] Furthermore, a valve support surface can be provided between the back pressure passage and the valve pressure passage to restrict the movement of the back pressure valve. Thus, the movement position of the back pressure valve can be limited by the valve support surface, thereby enabling stable operation.

[0019] Additionally, an elastic member can be provided on the opposite side of the valve pressure passage, across the back pressure valve, to elastically support the back pressure valve toward the valve pressure passage side. Thus, during low pressure ratio operation, the back pressure valve can move toward the valve pressure passage side, thereby enabling rapid opening and closing of the compression chamber and the back pressure space.

[0020] Specifically, a fixing member can be provided in the back pressure passage to support the other end of the elastic member. The fixing member can be separated from the sealing member that seals one end of the back pressure passage. This reduces the manufacturing cost of the sealing member while ensuring the widest possible passage cross-sectional area at the valve housing.

[0021] More specifically, a fixing member support surface can be formed on the inner circumferential surface of the back pressure passage to limit the insertion depth of the fixing member. Thus, the insertion depth of the fixing member can be limited by the fixing member support surface, thereby simplifying the assembly process while appropriately maintaining the elasticity of the elastic member.

[0022] Additionally, a fixing member supporting the second end of the elastic member can be provided in the back pressure passage. This fixing member can extend from a sealing member that seals the back pressure passage relative to the interior space of the housing. This increases the fastening force of the fixing member, thereby ensuring stable fixation of the elastic member even if the fixed scroll plate overheats.

[0023] In another embodiment, the back pressure passage can be formed as a single unit. The back pressure passage may include a valve housing, a plurality of back pressure inlets, and a back pressure outlet. The valve housing may be disposed on the fixed scroll plate and house the back pressure valve. The plurality of back pressure inlets may be connected to a plurality of compression chambers having different pressures at one end of the valve housing and selectively opened and closed by the back pressure valve. The back pressure outlet may be connected to the back pressure space at the other end of the valve housing. Thus, the back pressure passage, the back pressure valve, and the valve pressurization passage can be integrated, thereby reducing manufacturing costs.

[0024] Here, the plurality of back pressure inlets can be formed on the same line as the back pressure outlet, with reference to the length direction of the valve housing. Therefore, the inner diameter and / or weight of the back pressure valve can be minimized by forming the inner diameter of the back pressure passage as small as possible, thereby improving valve responsiveness.

[0025] In another embodiment, the back pressure passages can be arranged in a plurality of separate circumferentially. Each of the plurality of back pressure passages may include a valve housing, a back pressure inlet, and a back pressure outlet. The valve housing may be disposed on the fixed scroll plate and house the back pressure valve. The back pressure inlet may be connected at one end of the valve housing to one of the plurality of compression chambers having different pressures and may be selectively opened and closed by the back pressure valve. The back pressure outlet may be connected at the other end of the valve housing to the back pressure space. Thus, since the back pressure passages are formed to communicate independently with the plurality of compression chambers, not only is the operational reliability of the back pressure valve improved, but the position of the back pressure passages communicating with the intermediate pressure can also be appropriately adjusted according to operating conditions, thereby optimizing the back pressure of the back pressure space.

[0026] Invention Effects

[0027] The scroll compressor of the present invention may include a housing, a main frame, a rotating scroll plate, a fixed scroll plate, a back pressure space, a back pressure passage, and a back pressure valve. The back pressure valve may be disposed in the back pressure passage to selectively open and close the back pressure passage. The back pressure passage may be connected to a plurality of compression chambers having different pressures. Thus, the back pressure passage can selectively open and close corresponding compression chambers and back pressure spaces through the back pressure valve, and the back pressure of the back pressure space can be appropriately changed according to the operating conditions of the compressor, thereby suppressing leakage between compression chambers and / or frictional losses between scroll plates.

[0028] The scroll compressor of the present invention may also be provided with a valve pressurization passage connecting the back pressure passage and the discharge space of the housing. The back pressure valve may be arranged such that one side faces the valve pressurization passage and slides into the interior of the back pressure passage under the pressure of the discharge space. Thus, the back pressure valve can move under the pressure of the refrigerant transmitted from the discharge space through the valve pressurization passage and selectively connect the compression chamber and the valve pressurization passage, thereby simplifying the back pressure valve.

[0029] In the scroll compressor of the present invention, the back pressure passage can be formed as a single unit, and may include a valve housing, a plurality of back pressure inlets, and a back pressure outlet. The valve housing can accommodate a back pressure valve, and the plurality of back pressure inlets can be connected to a plurality of compression chambers having different pressures at one end of the valve housing and selectively opened and closed by the back pressure valves. A back pressure outlet can be connected to a back pressure space at the other end of the valve housing. Thus, the back pressure passage, the back pressure valve, and the valve pressurization passage can be integrated, thereby reducing manufacturing costs.

[0030] In the scroll compressor of the present invention, the back pressure passages can be arranged in a plurality of separate circumferentially. Each of the plurality of back pressure passages can include a valve housing, a back pressure inlet, and a back pressure outlet. A valve housing can accommodate a back pressure valve. A back pressure inlet can be connected at one end of the valve housing to one of the plurality of compression chambers having different pressures and can be selectively opened and closed by the back pressure valve. A back pressure outlet can be connected at the other end of the valve housing to the back pressure space. Thus, the back pressure passages can be configured to communicate independently with the plurality of compression chambers, thereby not only improving the operational reliability of the back pressure valve, but also allowing for appropriate adjustment of the position of the back pressure passage connected to the intermediate pressure according to operating conditions, thereby optimizing the back pressure of the back pressure space. Attached Figure Description

[0031] Figure 1 This is a cross-sectional view showing the scroll compressor of this embodiment.

[0032] Figure 2 This is a perspective view showing the back pressure valve assembly of this embodiment disassembled from the fixed scroll plate.

[0033] Figure 3 This is a perspective view showing the back pressure valve assembly of this embodiment assembled on a fixed scroll plate.

[0034] Figure 4 yes Figure 3 Top view.

[0035] Figure 5 It is Figure 4 A cross-sectional view showing section “A”.

[0036] Figure 6 yes Figure 5 Sectional view along line "VI-VI".

[0037] Figure 7 It is shown Figure 5 A cross-sectional view of another embodiment of the sealing component.

[0038] Figure 8a and Figure 8b It shows the basis Figure 2 A cross-sectional view of the operation of the back pressure valve assembly under the operating conditions of the compressor. Figure 8a This demonstrates the operation under low pressure ratio operating conditions. Figure 8b This demonstrates the operation under high pressure ratio conditions.

[0039] Figure 9 This is a top view of the fixed scroll plate shown to illustrate another embodiment of the back pressure valve assembly.

[0040] Figure 10 yes Figure 9 A sectional view along line "X-X".

[0041] Figure 11a and Figure 11b It is based on Figure 9 The operating conditions of the compressor are shown in the cross-sectional view to illustrate the operation of the back pressure valve assembly. Figure 11a This demonstrates the operation under low pressure ratio operating conditions. Figure 11b This demonstrates the operation under high pressure ratio conditions. Detailed Implementation

[0042] The scroll compressor of the present invention will now be described in detail with reference to an embodiment shown in the accompanying drawings.

[0043] Generally, scroll compressors can be classified as hermetically sealed or open-type depending on whether the drive motor and compression section are housed together within the casing. This embodiment uses a hermetically sealed scroll compressor as a representative example. However, the same principle applies to open-type scroll compressors.

[0044] Furthermore, scroll compressors can be categorized into stationary scroll compressors and mobile scroll compressors. Stationary compressors are typically used in building air conditioning systems, while mobile compressors are used in vehicle air conditioning systems. This embodiment uses a stationary scroll compressor as a representative example for explanation. However, the same principle applies to mobile scroll compressors.

[0045] Furthermore, scroll compressors can be classified as low-pressure or high-pressure types based on the pressure of the refrigerant filling the internal space of the casing. In low-pressure types, the internal space of the casing is filled with suction-type refrigerant, while in high-pressure types, the internal space of the casing is filled with discharge-type refrigerant. In this embodiment, a high-pressure scroll compressor is used as a representative example for explanation. However, the same principle applies to low-pressure scroll compressors.

[0046] Furthermore, scroll compressors can be categorized into top-compression and bottom-compression types based on the location of the compression section. In a top-compression type, the compression section is positioned above the drive motor, while in a bottom-compression type, the compression section is positioned below the drive motor. In this embodiment, a top-compression scroll compressor is used as a representative example for explanation. However, the same principle applies to bottom-compression scroll compressors.

[0047] Furthermore, scroll compressors can be classified into single-rotation scroll compressors and alternating-rotation scroll compressors based on whether the scroll plate rotates or not. In a single-rotation scroll compressor mechanism, one scroll plate is fixed or its rotational movement is restricted, while the other scroll plate rotates. In an alternating-rotation scroll compressor mechanism, both scroll plates rotate. This embodiment uses a single-rotation scroll compressor as a representative example for explanation. However, the same principle applies to alternating-rotation scroll compressors.

[0048] Figure 1 This is a cross-sectional view showing the scroll compressor of this embodiment.

[0049] Reference Figure 1 In the scroll compressor of this embodiment, a drive motor 120 is provided in the lower half of the housing 110, and a main frame 130 is provided above the drive motor 120. A compression section is provided on the upper side of the main frame 130. The compression section may include a fixed scroll plate 140 and a rotating scroll plate 150, but depending on the situation, the compression section may also include the main frame 130, which will be described below.

[0050] The housing 110 of this embodiment includes a cylindrical outer shell 111, an upper cap 112, and a lower cap 113. Therefore, the internal space 110a of the housing 110 can be divided based on the refrigerant flow sequence into an upper space located inside the upper cap 112, an intermediate space located inside the cylindrical outer shell 111, and a lower space located inside the lower cap 113. Hereinafter, the upper space will be defined as a discharge space 110b, the intermediate space as an oil separation space 110c, and the lower space as an oil storage space 110d.

[0051] The cylindrical outer shell 111 is a cylindrical shape with openings at both the top and bottom. On the inner circumference of the cylindrical outer shell 111, the drive motor 120 is pressed into and fixed to the lower half, and the main frame 130 is pressed into and fixed to the upper half.

[0052] Within the cylindrical outer shell 111, a refrigerant discharge pipe 116 is connected between the drive motor 120 and the main frame 130, and a refrigerant suction pipe 115 is connected through the upper cap 112. The refrigerant suction pipe 115 is directly connected to the suction pressure chamber (not labeled) of the compression section (described later) via the discharge space 110b of the shell 110, and the refrigerant discharge pipe 116 communicates with the internal space 110a of the shell 110. Thus, refrigerant can be directly supplied to the suction chamber (or suction pressure chamber) through the refrigerant suction pipe 115, and the high-pressure refrigerant discharged into the internal space 110a of the shell 110 can pass through the oil separation space 110c, and this refrigerant can be discharged through the refrigerant discharge pipe 116.

[0053] Reference Figure 1 In this embodiment, the drive motor 120 is disposed in the lower half of the oil separation space 110c of the high-pressure section in the internal space 110a of the housing 110, and includes a stator 121 and a rotor 122. The stator 121 is fixed to the inner wall surface of the cylindrical housing 111 by a heat-fitting method, and the rotor 122 is rotatably disposed inside the stator 121.

[0054] The rotating shaft 125 is press-fitted into the rotor 122. The upper end of the rotating shaft 125 is rotatably inserted into the main frame 130 (described later) and is supported radially, while the lower end of the rotating shaft 125 is rotatably inserted into the sub-frame 118 and is supported radially and axially.

[0055] An eccentric portion 1251 is provided at the upper end of the rotating shaft 125 so that the rotating shaft insertion portion 153 of the vortex disk 150 (described later) can be rotatably inserted into and engaged with it. The eccentric portion 1251 can also be inserted into and engaged with the rotating shaft insertion portion 153, and vice versa. This embodiment shows an example of the rotating shaft insertion portion 153 being inserted into and engaged with the eccentric portion 1251 of the rotating shaft 125.

[0056] An oil supply hole 1255 is formed inside the rotating shaft 125, extending through the two ends of the rotating shaft 125. The oil supply hole 1255 extends from the lower end of the rotating shaft 125 to the bottom surface of the eccentric portion 1251. Thus, oil stored in the oil storage space 110d, which forms the oil storage space 110d, can be supplied to the interior of the eccentric portion 1251 through the oil supply hole 1255.

[0057] At the lower end of the rotating shaft 125, specifically at the lower end of the oil supply port 1255, an oil suction device 126, including an oil pump, is provided. The inlet of the oil suction device 126 can be configured to be immersed in the oil stored in the oil storage space 110d. Thus, the oil stored in the oil storage space 110d can be pumped by the oil suction device 126 and drawn upwards through the oil supply port 1255.

[0058] Reference Figure 1 In this embodiment, the main frame 130 is disposed on the upper side of the drive motor 120 and is fixed to the inner wall surface of the cylindrical outer shell 111 by means of heat fitting or welding. The main frame 130 includes a main flange portion 131, a shaft support protrusion 132, and a back pressure space portion 133.

[0059] The upper surface of the main flange portion 131 can form a scroll disk support surface 134 that constitutes the thrust bearing surface (hereinafter, the first thrust bearing surface). As a result, the bottom surface (or back surface) of the swivel end plate portion 151, which will be described later, can be slidably placed on the scroll disk support surface 134 and supported in the axial direction.

[0060] The shaft support protrusion 132 extends from the center of the main flange portion 131 toward the drive motor 120, and a shaft support hole 1321 is formed on the inner side of the shaft support protrusion 132. Thus, the main flange portion 131 can be formed as an annular shape.

[0061] The back pressure space 133, together with the fixed thrust surface 142a (described later), forms the back pressure space S2. It is recessed to a predetermined depth at the edge of the scroll plate support surface 134 and formed as a ring. The back pressure space 133 communicates with the intermediate pressure chamber of the compression chamber V via the back pressure passage 170 (described later) and forms a back pressure that constitutes the intermediate pressure between the intake pressure and the exhaust pressure. As a result, the rotating scroll plate 150 is pushed towards the fixed scroll plate 140 and rises under the pressure (back pressure) of the back pressure space S. The rotating thrust surface 151a (described later) and the fixed thrust surface 142a are in close contact, forming a thrust bearing surface (hereinafter, the second thrust bearing surface) B2. The second thrust bearing surface B2 will be explained again later in the context of the fixed scroll plate 140 and / or the rotating scroll plate 150.

[0062] Reference Figure 1 The fixed scroll plate 140 in this embodiment includes a fixed end plate portion 141, a fixed side wall portion 142, and a fixed scroll portion 143.

[0063] The fixed end plate portion 141 is formed in a disk shape. The outer peripheral surface of the fixed end plate portion 141 can be in close contact with or separate from the inner peripheral surface of the upper cap 112 forming the discharge space 110b. The fixed end plate portion 141 can be formed with the same thickness. Thus, the root end of the fixed scroll portion 143, described later, is formed at the same height throughout the fixed scroll portion 143.

[0064] An intake port 1411 is formed at the edge of the fixed end plate portion 141, extending axially and communicating with the intake pressure chamber (not marked). A refrigerant intake pipe 115, which penetrates the upper cap 112 of the housing 110, is inserted into and connected to the intake port 1411. Thus, the refrigerant intake pipe 115 can be directly connected to the intake port 1411 of the fixed scroll plate 140 through the discharge space 110b of the housing 110.

[0065] A discharge port 1412 and a bypass hole (not shown) can be formed in the center of the fixed end plate portion 141. A discharge valve 145 for opening and closing the discharge port 1412 and a bypass valve (not shown) for opening and closing the bypass hole can be provided on the back side of the fixed end plate portion 141. Thus, the refrigerant compressed in the first compression chamber V1 and the second compression chamber V2 can be discharged from the upper side of the fixed scroll plate 140 to the discharge space 110b formed in the upper cap 112. Hereinafter, the compression chamber formed between the outer side of the swirling scroll portion 152 and the inner side of the fixed scroll portion 143 facing thereto will be defined as the first compression chamber V1, and the compression chamber formed between the inner side of the swirling scroll portion 152 and the outer side of the fixed scroll portion 143 facing thereto will be defined as the second compression chamber V2.

[0066] A portion of a back pressure passage 170 is formed in the fixed end plate portion 141. As described above, since the back pressure passage 170 is a passage for supplying intermediate-pressure refrigerant to the back pressure space portion 133 that forms the back pressure space S2, one end of the back pressure passage 170 is connected to the compression chamber V that forms the intermediate pressure, and the other end of the back pressure passage 170 is connected to the back pressure space portion 133. Thus, the back pressure passage 170 can be formed continuously through the fixed end plate portion 141 and the fixed side wall portion 142.

[0067] In this case, one end of the back pressure passage 170 can be configured to communicate with a plurality of compression chambers V having different pressures. A back pressure valve assembly 180 can be provided inside the back pressure passage 170 to allow selective communication between the plurality of compression chambers V and the back pressure passage 170. For example, the back pressure valve assembly 180 can be configured to selectively open and close the back pressure passage 170 under the pressure of the refrigerant discharged from the discharge space 110b. This allows for appropriate contact between the fixed scroll plate 140 and the rotary scroll plate 150 according to the compressor's operating conditions, thereby suppressing leakage between the compression chambers V and / or frictional losses at the second thrust bearing surface B2. This expands the compressor's operating range. The back pressure passage 170 will be described later along with the back pressure valve assembly 180.

[0068] The fixed side-wall portion 142 extends circumferentially from the edge of the fixed end plate portion 141 toward the main frame 130. Thus, the bottom surface of the fixed side-wall portion 142 can be tightly attached to and bolted to the upper surface of the main frame 130, that is, to the upper surface of the main flange portion 131.

[0069] The bottom surface of the fixed sidewall portion 142, that is, the surface facing the gyratory thrust surface 151a described later, slides in contact with the gyratory thrust surface 151a and forms the fixed thrust surface 142a constituting the second thrust bearing surface B2. Thus, the gyratory scroll 150 can be supported axially on both sides by the scroll support surface 134 of the main frame 130 and the bottom surface of the fixed sidewall portion 142.

[0070] On the thrust bearing surface of the fixed sidewall portion 142, i.e., the fixed thrust surface 142a, the other end of the back pressure passage 170 (described later) is penetrated. A back pressure connecting groove 142b can be formed radially elongated at the other end of the back pressure passage 170 to guide the refrigerant moving through the back pressure passage 170 to the back pressure space S. The back pressure connecting groove 142b can extend beyond the gyration radius of the gyratory end plate portion 151. Thus, during the gyratory motion of the gyratory scroll 150, the back pressure connecting groove 142b can always be in communication with the back pressure space S, thereby allowing the refrigerant in the compression chambers Vm1 and Vm2 to continuously move into the back pressure space S.

[0071] The fixed scroll portion 143 extends from the bottom surface of the fixed end plate portion 141 toward the rotating scroll disk 150. The fixed scroll portion 143 can be formed into various shapes such as an involute. For example, the fixed scroll portion 143 can be formed into a logarithmic spiral or into a plurality of circular arc curves.

[0072] The fixed scroll portions 143 can be formed with the same scroll height along the scroll forming direction, or they can be formed with different heights. In this embodiment, an example is shown where the scroll heights of the fixed scroll portions 143 are formed to be the same.

[0073] Reference Figure 1 The vortex disk 150 in this embodiment may include a vortex end plate portion 151, a vortex portion 152, and a rotating shaft insertion portion 153.

[0074] The gyratory end plate portion 151 is formed in a disk shape and is axially supported by the main frame 130 to perform gyratory motion between the main frame 130 and the fixed scroll disk 140. In other words, the bottom surface of the gyratory end plate portion 151, together with the scroll disk support surface 134 of the main frame 130, forms a first thrust bearing surface B1, and the upper surface of the gyratory end plate portion 151, together with the fixed thrust surface 142a of the fixed sidewall portion 142, forms a gyratory thrust surface 151a constituting a second thrust bearing surface B2. Hereinafter, the upper surface of the gyratory end plate portion 151 facing the fixed thrust surface 142a will be defined as the gyratory thrust surface 151a and will be described.

[0075] An oil supply passage 155 is formed inside the swivel end plate portion 151. One end of the oil supply passage 155 extends through the bottom surface of the swivel end plate portion 151 and communicates with the oil flow path 1255 of the rotating shaft 125. The other end of the oil supply passage 155 extends through to the upper surface of the swivel end plate portion 151, that is, through to the swivel thrust surface 151a. Thus, a portion of the oil drawn upward by the rotating shaft 125 is supplied to the second thrust bearing surface B2 and lubricates the second thrust bearing surface B2.

[0076] The swirling scroll portion 152 extends from the upper surface (compression surface) of the swirling end plate portion 151 toward the fixed scroll disk 140. Thus, the swirling scroll portion 152 can mesh with the fixed scroll portion 143 to form two pairs of compression chambers V1, V2.

[0077] The spiral scroll 152 can be formed into various shapes, such as an involute, to correspond to the fixed scroll 143. For example, the spiral scroll 152 can be formed into a logarithmic spiral or into a plurality of circular arcs.

[0078] The swirling scroll portions 152 can be formed with the same scroll height along the scroll forming direction, or they can be formed with different heights. In this embodiment, an example is shown where the scroll heights of the swirling scroll portions 152 are formed with the same height along the scroll forming direction.

[0079] The rotating shaft insertion portion 153 can extend from the geometric center of the cyclone 150 toward the eccentric portion 1251 of the rotating shaft 125. The rotating shaft insertion portion 153 can be rotatably inserted into the eccentric portion 1251 of the rotating shaft 125. Thus, the cyclone 150 rotates through the eccentric portion 1251 of the rotating shaft 125 and the rotating shaft insertion portion 153.

[0080] The figure notation 160 in the attached drawing is a cross ring.

[0081] The scroll compressor of this embodiment, as described above, operates as follows.

[0082] That is, if power is applied to the drive motor 120 and a rotational force is generated, the rotary scroll 150, which is eccentrically coupled to the rotating shaft 125, can rotate relative to the fixed scroll 140 via the cross ring 160. 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 rotary scroll 150.

[0083] In this way, during the swirling motion of the vortex disk 150, the first compression chamber V1 and the second compression chamber V2 move from the inlet (or, inlet pressure chamber) 1411 to the outlet (or, outlet pressure chamber) 1412, while their volume gradually decreases.

[0084] In this way, the refrigerant flows into the first compression chamber V1 and the second compression chamber V2 via the refrigerant suction pipe 115 and the suction port 1411 of the fixed scroll plate 140. The refrigerant moves towards the final compression chamber side and is compressed via the rotating scroll plate 150. The refrigerant is discharged from the final compression chamber into the discharge space 110b of the housing 110 through the discharge port 1412 of the fixed scroll plate 140. The refrigerant moves towards the oil separation space 110c and / or the oil storage space 110d of the housing 110 through the discharge passage (not shown) provided in the fixed scroll plate 140 and the main frame 130.

[0085] In this way, the following series of processes are repeated: the refrigerant circulates in the oil separation space 110c of the housing 110 and oil is separated from the refrigerant. The refrigerant with separated oil is discharged to the outside of the housing 110 through the refrigerant discharge pipe 116. Conversely, the oil separated from the refrigerant moves to the oil storage space 110d of the housing 110 and is stored. It is then supplied to the compression section through the oil suction device 126 and the oil supply hole 1255 of the rotating shaft 125.

[0086] At this time, during the refrigerant compression process in compression chamber V, if the pressure in compression chamber V rises, the rotary scroll 150 is pushed towards the main frame 130. Consequently, the rotary scroll 150 can separate from the fixed scroll 140, resulting in leakage between compression chambers V. This situation is more pronounced under high pressure ratio operating conditions.

[0087] Considering this, a back pressure passage 170 communicating with the back pressure space S can be provided in the compression chambers Vm1 and Vm2 that form the intermediate pressure. In this case, a portion of the refrigerant forming the intermediate pressure moves to the back pressure space S through the back pressure passage 170 and puts pressure on the fixed scroll plate 140 side of the swirling scroll plate 150, thus suppressing the situation where the swirling scroll plate 150 is pushed under the pressure of the compression chamber V.

[0088] However, if the back pressure passage 170 is connected to a compression chamber (intermediate pressure chamber) V, a back pressure suitable for the compressor's operating conditions cannot be formed. Therefore, in this embodiment, the back pressure of the back pressure space S can be configured to correspond to and change with the compressor's operating conditions. Thus, during low-pressure-ratio operation, the back pressure of the rotary scroll 150 is relatively high, effectively suppressing leakage between compression chambers V1 and V2. On the other hand, during high-pressure-ratio operation, the back pressure of the rotary scroll 150 is relatively low, effectively reducing frictional losses formed at the second thrust bearing surface B2 between the two scrolls 140 and 150. This expands the compressor's operating range.

[0089] Figure 2 This is a perspective view showing the back pressure valve assembly of this embodiment disassembled from the fixed scroll plate. Figure 3 This is a perspective view showing the back pressure valve assembly of this embodiment assembled on a fixed scroll plate. Figure 4 yes Figure 3 Top view, Figure 5 It is Figure 4 The "A" section is broken and shown in a cross-sectional view. Figure 6 yes Figure 5 Sectional view along line "VI-VI", Figure 7 It is shown Figure 5 A cross-sectional view of another embodiment of the fixing member.

[0090] Reference Figures 2 to 6In this embodiment, the fixed scroll plate 140 may be provided with the back pressure passage 170, the back pressure valve assembly 180, and the valve pressure passage 190 described above. The back pressure passage 170 is a passage that connects a plurality of compression chambers (more precisely, intermediate pressure chambers with an intermediate pressure between the suction pressure and the discharge pressure) Vm1 and Vm2, each having a different intermediate pressure, to the back pressure space S. The back pressure valve assembly 180 selectively opens and closes the valve of the back pressure passage 170, allowing one of the compression chambers Vm1 and Vm2 to connect to the back pressure space S. The valve pressure passage 190 selectively opens and closes the passage of the back pressure valve assembly 180 according to the pressure in the discharge space 110b. Thus, the back pressure passage 170 can selectively open and close the corresponding compression chambers Vm1 and Vm2 and the back pressure space S through the back pressure valve assembly 180, and appropriately change the back pressure of the back pressure space S according to the operating conditions of the compressor.

[0091] Reference Figures 2 to 5 In this embodiment, the back pressure passage 170 may include a valve receiving portion 171, a plurality of back pressure inlets 172, and a back pressure outlet 173. The valve receiving portion 171 is a space for accommodating the back pressure valve assembly 180. The back pressure inlets 172 are one end of the back pressure passage 170 that communicates with the compression chambers Vm1 and Vm2 forming the intermediate pressure chamber. The back pressure outlet 173 is the other end of the back pressure passage 170 that communicates with the back pressure space S. Thus, the back pressure passage 170 can be configured such that the back pressure inlets 172 and the back pressure outlet 173 are respectively connected to both ends of the valve receiving portion 171 via the valve receiving portion 171.

[0092] The valve receiving portion 171 can be formed as a smooth tube shape with a single inner diameter, or it can be formed as a multi-segment shape with multiple inner diameters. In this embodiment, since it is necessary to properly control the position of the back pressure valve assembly 180 inside the valve receiving portion 171, an example is shown where the inner circumferential surface of the valve receiving portion 171 is formed as a multi-segment shape with multiple inner diameters.

[0093] For example, the valve receiving portion 171 can be recessed from the outer peripheral surface of the fixed end plate portion 141 toward the discharge port 1412 by a predetermined length. In this case, one end of the valve receiving portion 171 forming the discharge port 1412 side end can be connected to the discharge space 110b through the valve pressure passage 190 described later, and the other end of the valve receiving portion 171 forming the outer peripheral surface side end of the fixed end plate portion 141 can be sealed using an additional sealing member 175.

[0094] A valve support surface 171a and / or a fixing member support surface 171b may also be formed on the inner peripheral surface of the valve receiving portion 171. The valve support surface 171a is a surface that restricts the movement of the back pressure valve 181 towards the outlet 1412 side, and the fixing member support surface 171b is a surface that restricts the fixed position of the fixing member 183 at the other end of the fixing elastic member 182. In this case, the valve support surface 171a and the fixing member support surface 171b can be formed sequentially from the outlet 1412 side end of the valve receiving portion 171 towards the outer peripheral surface side end. Thus, the movement position of the back pressure valve 181 can be restricted by the valve support surface 171a, thereby enabling stable operation, and the insertion depth of the fixing member 183 can be restricted by the fixing member support surface 171b, thereby simplifying the assembly process while appropriately maintaining the elasticity of the elastic member 182.

[0095] Furthermore, in this case, the valve support surface 171a and the fixing member support surface 171b can be formed to have different inner diameters, and can be formed such that the inner diameters increase sequentially from the valve support surface 171a to the fixing member support surface 171b. Thus, the valve support surface 171a and the fixing member support surface 171b can be machined from the outer peripheral surface of the fixing end plate portion 141 towards the outlet 1412, thereby easily forming their respective support surfaces 171a and 171b.

[0096] In this case, the support surface 171b of the fixing member can be formed as a circle, such as the valve support surface 171a, or it can be formed as an arc shape. In this embodiment, an example is shown where the respective support surfaces 171a and 171b are formed as circles. Thus, the respective support surfaces 171a and 171b can stably support the back pressure valve 181, the elastic member 182, and the fixing member 183.

[0097] Although not shown, only a valve support surface 171a may be formed on the inner peripheral surface of the valve receiving portion 171. For example, a stepped valve support surface 171a that restricts the movement of the back pressure valve 181 may be formed between the back pressure passage 170 and the valve pressure passage 190. This simplifies the inner peripheral surface of the valve receiving portion and makes it easier to process.

[0098] The back pressure inlet 172 can communicate with one end of the valve receiving portion 171 to a plurality of compression chambers Vm1, Vm2 that form an intermediate pressure. In other words, the back pressure inlet 172 extends from the valve receiving portion 171 to one side of the fixed end plate portion 141 that forms the compression chambers Vm1, Vm2, and the back pressure inlet 172 can be configured to communicate with a plurality of compression chambers Vm1, Vm2 that form different intermediate pressures. Thus, the plurality of back pressure inlets 172 can selectively communicate with one end of the valve receiving portion 171 depending on the position of the back pressure valve 181 described later.

[0099] For example, the back pressure inlet 172 may include a first inlet 172a and a second inlet 172b. The first inlet 172a may be connected to a compression chamber (or, a first intermediate pressure chamber) Vm1 that forms a relatively high intermediate pressure, and the second inlet 172b may be connected to a compression chamber (or, a second intermediate pressure chamber) Vm2 that forms a relatively low intermediate pressure. Thus, the inlet of the back pressure passage 170 may be connected to compression chambers Vm1 and Vm2, which have two different intermediate pressures, respectively.

[0100] The first inlet portion 172a and the second inlet portion 172b can be formed on the same line along the length direction of the valve receiving portion 171. For example, the first inlet portion 172a and the second inlet portion 172b can be formed on the same line as the back pressure outlet portion 173 in the radial direction. As a result, the inner diameter of the back pressure valve assembly 180 and / or the weight of the back pressure valve assembly 180 can be minimized by forming the inner diameter of the valve receiving portion 171 as small as possible, thereby improving valve responsiveness.

[0101] The first inlet portion 172a and the second inlet portion 172b can be formed with a cross-sectional area smaller than that of the valve receiving portion 171, and can be formed to have the same cross-sectional area as each other. For example, the first inlet portion 172a and the second inlet portion 172b can be formed as circles with a spiral thickness less than or equal to that of the spiral portion 152, so that the two inlet portions 172a and 172b have the same shape and / or inner diameter. Thus, the first inlet portion 172a and the second inlet portion 172b can be formed with the same shape, which makes them easy to process, and they can communicate with compression chambers Vm1 and Vm2 with different pressures, thereby forming different back pressures in the back pressure space S.

[0102] The back pressure outlet 173 can penetrate from the other end of the valve receiving portion 171 to one side of the fixed end plate portion 141 facing the back pressure space portion 133 of the main frame 130. In other words, the back pressure outlet 173 can be formed by penetrating one side of the fixed end plate portion 141 between the fixed member support surface 171b and the sealing member 175. Thus, the back pressure outlet 173 can selectively connect the back pressure passage 170 and the back pressure space S according to the position of the back pressure valve 181 described later.

[0103] As described above, the back pressure outlet portion 173 can be formed on the same line as the first inlet portion 172a and the second inlet portion 172b forming the back pressure inlet portion 172, with the length direction of the valve receiving portion 171 as a reference. As a result, the inner diameter of the valve receiving portion 171 can be minimized, thereby reducing the weight of the back pressure valve assembly 180.

[0104] Furthermore, the cross-sectional area of ​​the back pressure outlet 173 can be formed to be the same as the cross-sectional area of ​​the back pressure inlet 172. In other words, the inner diameter of the back pressure outlet 173 can be formed to be the same as the inner diameter of the first inlet 172a and / or the inner diameter of the second inlet 172b. As a result, the refrigerant discharged into the valve housing 171 through the back pressure inlet 172 can move rapidly into the back pressure space S through the back pressure outlet 173 without pressure drop.

[0105] Reference Figures 2 to 6 In this embodiment, the back pressure valve assembly 180 can be inserted into the valve receiving portion 171 of the back pressure passage 170. In other words, the back pressure valve assembly 180 can be formed by a piston valve that moves to a position selectively opening and closing the first inlet portion 172a and the second inlet portion 172b under the action of the pressure difference between the two ends. Thus, the back pressure valve 181 can suppress interference with surrounding components by being inserted into the interior of the fixed scroll plate 140.

[0106] For example, the back pressure valve assembly 180 may include a back pressure valve 181, an elastic member 182, and a fixing member 183. The back pressure valve 181 is the component that actually opens and closes the back pressure passage 170, the elastic member 182 is the component that supports the back pressure valve 181 toward the discharge space 110b, and the fixing member 183 is the component that fixes the end of the elastic member 182. Thus, the back pressure valve assembly 180 can be inserted into the valve receiving portion 171 of the back pressure passage 170 and move under the action of the pressure difference between the discharge space 110b and the back pressure space S, selectively opening and closing the back pressure passage 170.

[0107] Specifically, the back pressure valve 181 may include a valve body 1811 and a connection passage 1812. The valve body 1811 is the part that slides into the back pressure passage 170 and opens and closes the back pressure inlet 172, and the connection passage 1812 is the part that selectively communicates with the back pressure passage 170 according to the position of the valve body 1811.

[0108] The valve body 1811 may include a plurality of opening and closing portions 1811a and 1811b and a connecting portion 1811c. In other words, in the valve body 1811, the plurality of opening and closing portions 1811a and 1811b may extend radially from both ends of the connecting portion 1811c. As a result, not only can the valve body 1811 be easily manufactured, but the reliability of the valve can also be improved.

[0109] As described above, a plurality of opening and closing portions 1811a and 1811b can extend from both ends of the connecting portion 1811c in a flange shape and be integrally formed. In other words, each of the plurality of opening and closing portions 1811a and 1811b can be formed such that its outer diameter is almost the same as the inner diameter of the valve receiving portion 171. Thus, the plurality of opening and closing portions 1811a and 1811b can slide in contact with the valve receiving portion 171 and tightly open and close the first inlet portion 172a and / or the second inlet portion 172b.

[0110] For example, the plurality of opening and closing portions 1811a, 1811b may include a first opening and closing portion 1811a and a second opening and closing portion 1811b, and the interval between the first opening and closing portion 1811a and the second opening and closing portion may be formed to be less than or equal to the interval between the first inlet portion 172a and the second inlet portion 172b of the back pressure inlet portion 172. Thus, the first inlet portion 172a can be selectively opened and closed by the first opening and closing portion 1811a, and the second inlet portion 172b can be selectively opened and closed by the second opening and closing portion.

[0111] The first opening / closing part 1811a can be formed at a position facing the valve pressure passage 190, and the second opening / closing part can be formed at a position adjacent to the back pressure space S. Thus, the first opening / closing part 1811a can be formed as a pressure-applying part under the pressure of the discharge space 110b, and the second opening / closing part 1811b can be formed as part of the connecting passage 1812.

[0112] In other words, the first opening / closing part 1811a can be formed into a sealing disc shape and slide in contact with the valve receiving part 171. Thus, the first opening / closing part 1811a receives the pressure of the refrigerant transmitted from the discharge space 110b evenly through the valve pressure passage 190, while tightly sealing the space between the two compression chambers Vm1 and Vm2 forming the intermediate pressure and the valve pressure passage (discharge space) 190.

[0113] The second opening / closing portion 1811b may form a second passage portion 1812b with an opening to connect its two side surfaces. For example, the second opening / closing portion 1811b may be formed in a disc shape, and at least one second passage portion 1812b may be formed circumferentially. In this embodiment, the second passage portion 1812b may be formed in the shape of a hole, but depending on the situation, it may also be formed in the shape of a groove or a crescent shape recessed on the outer peripheral surface of the second opening / closing portion 1812b.

[0114] The connecting portion 1811c can be formed in the shape of a rod so that the centers of the two opening and closing portions 1811a and 1811b are connected to each other. In other words, the outer diameter of the connecting portion 1811c can be formed to be smaller than the outer diameter of the two opening and closing portions 1811a and 1811b. As a result, a first passage portion 1812a can be formed on the outer periphery of the connecting portion 1811c, forming a part of the connecting passage 1812 along the periphery.

[0115] In this case, the outer diameter of the connecting portion 1811c can be formed to be smaller than the imaginary circle that connects the centers of the second passage portions 1812b to each other. Thus, at least a portion of the first passage portion 1812a can communicate with the second passage portion 1812b along a straight line.

[0116] Although not shown, the connecting portion 1811c can also be formed as a rectangle when projected along its length. In other words, the connecting portion 1811c can also be cut into a crescent shape on the outer peripheral surface of the valve body 1811 or formed by recesses along the circumference at predetermined intervals. In this case, the crescent-shaped portion or the recessed portion can form the first passage portion 1812a.

[0117] The connecting passage 1812 may include a first passage portion 1812a and a second passage portion 1812b. The first passage portion 1812a may be formed in the connecting portion 1811c of the valve body 1811, and the second passage portion 1812b may be formed in the second opening / closing portion 1811b of the valve body 1811. In other words, the first passage portion 1812a may be formed along the outer peripheral surface of the connecting portion 1811c, which is formed to be smaller than the outer diameter of the second opening / closing portion 1811b, and the second passage portion 1812b may be formed to penetrate the second opening / closing portion 1811b and communicate with the first passage portion 1812a. Thus, the connecting passage 1812 can be formed to penetrate the interior of the valve body 1811, thereby enabling the corresponding compression chambers Vm1 and Vm2 to move rapidly toward the back pressure space S according to the position of the valve body 1811.

[0118] The elastic member 182 can be formed by a compression coil spring and elastically support the back pressure space S-side end of the back pressure valve 181. For example, one end of the elastic member 182 facing the discharge space 110b can contact the second opening / closing portion 1811b of the back pressure valve 181, and the other end of the elastic member 182 facing the back pressure space S can be supported by a fixing member 183 inserted into the valve receiving portion 171. Thus, the back pressure valve 181 can be elastically supported towards the discharge space 110b side inside the valve receiving portion 171 by the elastic member 182, so that the plurality of back pressure inlets 172a, 172b can be selectively opened and closed under the pressure of the discharge space 110b.

[0119] In this case, the elastic member 182 can be configured to be unaffected by the second passage portion 1812b of the second opening / closing portion 1811b described above, or it can be configured to be affected by as little interference as possible. For example, the inner diameter of the elastic member 182 can be configured to be larger than the inner diameter of the imaginary circle connecting the center of the second passage portion 1812b, or the outer diameter of the elastic member 182 can be configured to be smaller than the inner diameter of the imaginary circle. This minimizes the possibility that the connection passage 1812 connected to the back pressure passage 170 will be blocked by the elastic member 182. In this embodiment, an example is shown where the inner diameter of the elastic member 182 is larger than the inner diameter of the imaginary circle.

[0120] Reference Figure 6 The fixing member 183 can be separated from the sealing member 175 and individually fixed to the valve receiving portion 171. In other words, the fixing member 183 can be manufactured as a component independent of the sealing member 175 that seals the outer peripheral surface of the fixing end plate portion 141 of the valve receiving portion 171 and is assembled to the valve receiving portion 171. As a result, the manufacturing cost of the sealing member 175 can be reduced while ensuring the widest possible passage cross-sectional area at the valve receiving portion 171.

[0121] In this case, the fixing member 183 can be formed in a ring shape and inserted into the valve receiving portion 171. For example, the fixing member 183 can be formed as a ring and pressed in by thermocompression fitting, or it can be formed as a C-ring and elastically fixed. In this embodiment, an example of fixing the fixing member 183 formed as a ring by thermocompression fitting is shown.

[0122] Alternatively, in this case, the inner circumferential surface of the valve receiving portion 171 can be formed into a smooth tubular shape, or it can be recessed into the fixing member insertion groove (not shown). In the former case, the processing of the valve receiving portion 171 can be simplified; conversely, in the latter case, the insertion depth and / or fixing strength of the fixing member 183 can be increased.

[0123] like Figure 7 As shown, the fixing member 183 can also extend from the sealing member 175. In other words, the fixing member 183 can also extend long from the sealing member 175 toward the elastic member 182. This can increase the fastening force of the fixing member 183, so that even if the fixed scroll plate 140 overheats, the elastic member 182 can be stably fixed.

[0124] Refer again Figure 5 and Figure 6The valve pressure passage 190 can be configured such that the opposite side of the back pressure passage (more precisely, the valve housing) 170, centered on the back pressure valve 181, communicates with the discharge space 110b. In other words, the valve pressure passage 190 can be configured to face one side of the back pressure valve 181, which is slidably inserted into the valve housing 171d. Thus, based on the pressure difference between the back pressure passage (more precisely, the back pressure space) 170 and the valve pressure passage (more precisely, the discharge space) 190, the back pressure valve 181 opens the first inlet 172a and moves to a position that blocks the second inlet 172b (hereinafter, the first position), or conversely, the back pressure valve 181 blocks the first inlet 172a and moves to a position that opens the second inlet 172b (hereinafter, the second position).

[0125] For example, one end of the valve pressure passage 190 may open toward the back side of the fixed end plate portion 141 that forms the discharge space 110b, and the other end of the valve pressure passage 190 may open toward the valve receiving portion 171 described above. Thus, a portion of the refrigerant discharged into the discharge space 110b through the discharge port 1412 moves through the valve pressure passage 190 toward the valve receiving portion 171 that forms the back pressure passage 170 and applies pressure to the first opening / closing portion 1811a of the back pressure valve 181.

[0126] In this case, the center of the valve pressure passage 190 can be aligned with the center of the valve housing 171. In other words, the center of the valve pressure passage 190 facing the valve housing 171 can be aligned with the center of the first opening / closing portion 1811a facing the valve pressure passage 190. As a result, the pressure of the refrigerant transmitted through the valve pressure passage 190 can be uniformly applied to the back pressure valve 181, thereby enabling the back pressure valve 181 to operate quickly and stably.

[0127] Although not shown in the figure, one end of the valve pressure passage 190 may also be formed through the inner circumferential surface of the discharge port 1412. In this case, the valve pressure passage 190 can be formed in a straight line, thereby reducing the machining time of the valve pressure passage 190 and thus reducing manufacturing costs.

[0128] As described above, in this embodiment, the back pressure passage 170, which connects the compression chamber and the back pressure space S, can connect to a plurality of compression chambers Vm1 and Vm2 with different pressures. A back pressure valve 181 can be installed inside the back pressure passage 170. The back pressure valve 181 moves under the pressure of the discharge space 110b, selectively connecting the plurality of compression chambers Vm1 and Vm2 with different pressures to the back pressure space S. Therefore, the position of the back pressure valve 181 can be changed in conjunction with the compressor's operating conditions, thereby appropriately adjusting the back pressure of the back pressure space S. This allows for an expansion of the compressor's operating range by suppressing leakage between compression chambers during low-pressure-ratio operation and / or frictional losses between scroll plates during high-pressure-ratio operation.

[0129] Figure 8a and Figure 8b It shows the basis Figure 2 A cross-sectional view of the operation of the back pressure valve assembly under the operating conditions of the compressor. Figure 8a This demonstrates the operation under low pressure ratio operating conditions. Figure 8b This demonstrates the operation under high pressure ratio conditions.

[0130] For example, such as Figure 8a As shown, under low pressure ratio operating conditions, the pressure in the discharge space 110b decreases. Consequently, the refrigerant with relatively low pressure is transferred to the back pressure valve 181 through the valve pressurization passage 190. The back pressure valve 181, under the elastic force of the elastic member 182, remains in its initial position, i.e., the first position. The first opening / closing part 1811a opens the first inlet 172a, while the second opening / closing part 1811b blocks the second inlet 172b. The refrigerant in the compression chamber Vm1, with a relatively high intermediate pressure, is then transferred to the back pressure space S through the first inlet 172a, the connecting passage 1812, the valve receiving part 171, and the back pressure outlet 173. The back pressure space S then forms a relatively high first back pressure, strongly pressurizing the rotating scroll 150 towards the fixed scroll 140. Thus, the rotating scroll 150 can be relatively tightly pressed against the fixed scroll 140, effectively suppressing leakage between the compression chambers.

[0131] On the contrary, such as Figure 8bAs shown, under high-pressure ratio operating conditions, the pressure in the discharge space 110b increases. Consequently, the refrigerant with relatively higher pressure is transferred to the back pressure valve 181 through the valve pressurization passage 190. The back pressure valve 181 then moves to the second position against the elastic force of the elastic member 182. The first opening / closing part 1811a blocks the first inlet 172a, while the second opening / closing part 1811b opens the second inlet 172b. The refrigerant in the compression chamber Vm2, with a relatively low intermediate pressure, is then transferred to the back pressure space S through the second inlet 172b, the connecting passage 1812, the valve receiving part 171, and the back pressure outlet 173. The back pressure space S then forms a relatively low second back pressure and applies weak pressure to the rotating scroll 150 towards the fixed scroll 140. Thus, the rotating scroll 150 can maintain relatively weak contact with the fixed scroll 140, effectively suppressing frictional losses between the scrolls.

[0132] On the other hand, another embodiment of the back pressure passage is as follows.

[0133] That is, in the aforementioned embodiments, multiple compression chambers with different pressures can be connected to a single back pressure passage simultaneously, but depending on the circumstances, multiple compression chambers with different pressures can be connected to multiple back pressure passages independently.

[0134] Figure 9 This is a top view of the fixed scroll plate shown to illustrate another embodiment of the back pressure valve assembly. Figure 10 yes Figure 9 A sectional view along line "X-X".

[0135] Reference Figure 9 and Figure 10 In the scroll compressor of this embodiment, a back pressure passage 170 can be provided on the fixed scroll plate 140, which connects a plurality of compression chambers Vm1, Vm2 with different pressures to the back pressure space S. A back pressure valve assembly 180 can be provided on the back pressure passage 170 to selectively open and close the back pressure passage 170. A valve pressure application passage 190 communicating with the discharge space 110b of the housing 110 can be provided at one end of the back pressure passage 170. Thus, the pressure of the discharge space 110b can be changed according to the operating conditions of the compressor, and the position of the back pressure valve assembly 180 facing the valve pressure application passage 190 communicating with the discharge space 110b can be moved to a first position and a second position, thereby appropriately changing the back pressure of the back pressure space S.

[0136] Since the basic structure and function of the back pressure passage 170, the back pressure valve assembly 180, and the valve pressure passage 190 are almost similar to those of the aforementioned embodiments, the description of the aforementioned embodiments will be used instead.

[0137] However, in this embodiment, the back pressure passage 170 can be separated into a plurality of back pressure passages 170a and 170b, and each back pressure passage 170a and 170b can be provided with its own back pressure valve assembly 180a and 180b. Each valve pressure passage 190a and 190b can be connected to the opposite side of each back pressure passage 170a and 170b through the respective back pressure valve assembly 180a and 180b. In other words, multiple compression chambers Vm1 and Vm2 with different pressures can be independently connected to the back pressure space S through their respective back pressure passages 170a and 170b. Each back pressure passage 170a and 170b can be equipped with a back pressure valve assembly 180a and 180b that can selectively open and close the back pressure passage 170a and 170b. At one end of each back pressure passage 170a and 170b facing the back pressure valve assembly 180a and 180b, a valve pressure passage 190a and 190b for opening and closing the back pressure valve assembly 180a and 180b can be independently connected.

[0138] Specifically, the back pressure passage 170 may include a first back pressure passage 170a and a second back pressure passage 170b. The first back pressure passage 170a and the second back pressure passage 170b may be formed symmetrically on the same line, but depending on the situation, they may also be formed symmetrically on different lines. In this embodiment, an example is shown where the first back pressure passage 170a and the second back pressure passage 170b are formed symmetrically at their intersection points. Thus, the first back pressure passage 170a and the second back pressure passage 170b can avoid the empty space formed in the fixed scroll plate 140, such as bypass holes (not shown), thereby enabling unified processing of the first back pressure passage 170a and the second back pressure passage 170b, and thus reducing manufacturing costs. Since the first back pressure passage 170a and the second back pressure passage 170b are similar to the aforementioned... Figure 6 The back pressure passage 170 in the embodiments is formed almost identically, and therefore the description of the foregoing embodiments will be used instead.

[0139] The back pressure valve assembly 180 may include a first back pressure valve assembly 180a and a second back pressure valve assembly 180b. The first back pressure valve assembly 180a and the second back pressure valve assembly 180b may be formed with the same shape as each other, but depending on the circumstances, they may also be formed with different shapes. In this embodiment, an example is shown where the first back pressure valve assembly 180a and the second back pressure valve assembly 180b are formed with the same shape as each other. Therefore, manufacturing costs can be reduced by unifying the manufacturing and / or assembly of the back pressure valve assemblies 180a and 180b. Since the first back pressure valve assembly 180a and the second back pressure valve assembly 180b are similar to the aforementioned... Figure 6 The back pressure valve assembly 180 in the embodiments is formed in the same way, and therefore the description of the foregoing embodiments will be used instead.

[0140] The valve pressure passage 190 may include a first valve pressure passage 190a and a second valve pressure passage 190b. The first valve pressure passage 190a and the second valve pressure passage 190b may be configured to communicate independently with their respective back pressure passages 170a and 170b. Depending on the situation, a valve pressure passage (not shown) may also be configured to connect in parallel with a plurality of back pressure passages 170a and 170b. In this embodiment, an example is shown where the first valve pressure passage 190a and the second valve pressure passage 190b are formed independently. Therefore, the first valve pressure passage 190a and the second valve pressure passage 190b can be appropriately formed in the empty space of the fixed scroll plate 140, avoiding bypass holes, etc., thereby enabling unified processing of the first valve pressure passage 190a and the second valve pressure passage 190b and reducing manufacturing costs. Since the first valve pressure passage 190a and the second valve pressure passage 190b are related to the aforementioned... Figure 6 The valve pressure passage 190 in the embodiments is formed almost identically, and therefore the description of the foregoing embodiments will be used instead.

[0141] As described above, even if multiple back pressure passages 170a and 170b, back pressure valve assemblies 180a and 180b, and pressure valves 190a and 190b are provided, the back pressure of the back pressure space S can be appropriately adjusted according to the operating conditions of the compressor.

[0142] Furthermore, since the back pressure passages 170a and 170b are formed to be independently connected to the plurality of compression chambers Vm1 and Vm2, not only can the operational reliability of the back pressure valves 181a and 181b be improved, but the position of the back pressure passages 170a and 170b connected to the intermediate pressure can also be appropriately adjusted according to the operating conditions, thereby optimizing the back pressure of the back pressure space S.

[0143] Figure 11a and Figure 11b It is based on Figure 9 The operating conditions of the compressor are shown in the cross-sectional view to illustrate the operation of the back pressure valve assembly. Figure 11a This demonstrates the operation under low pressure ratio operating conditions. Figure 11b This demonstrates the operation under high pressure ratio conditions.

[0144] For example, such as Figure 11aAs shown, under low pressure ratio operating conditions, the pressure in the discharge space 110b decreases. Consequently, the refrigerant with relatively low pressure is transferred to the first back pressure valve 181a and the second back pressure valve 181b through the first valve pressurization passage 190a and the second valve pressurization passage 190b. The first back pressure valve 181a and the second back pressure valve 181b then maintain their first positions under the elastic force of the first elastic member 182a and the second elastic member 182b, respectively. The first opening / closing portion 1811a1 of the first back pressure valve 181a opens the first back pressure inlet 1721 of the first back pressure passage 170a, while conversely, the second opening / closing portion 1811b2 of the second back pressure valve 181b blocks the second back pressure inlet 1722 of the second back pressure passage 170b. Thus, the refrigerant in the compression chamber V1, which has a relatively high intermediate pressure, is transferred to the back pressure space S through the first back pressure inlet 1721, the first connecting passage 1813a, the first valve receiving portion 1711, and the first back pressure outlet 1731. Therefore, the back pressure space S forms a relatively high first back pressure and exerts strong pressure on the rotating scroll plate 150 towards the fixed scroll plate 140. As a result, the rotating scroll plate 150 can be in relatively strong contact with the fixed scroll plate 140, thereby effectively suppressing leakage between the compression chambers.

[0145] On the contrary, such as Figure 11b As shown, under high-pressure ratio operating conditions, the pressure in the discharge space 110b increases. Consequently, the relatively high-pressure refrigerant is transferred to the first back pressure valve 181a and the second back pressure valve 181b through the first valve pressurization passage 190a and the second valve pressurization passage 190b. Then, the first back pressure valve 181a and the second back pressure valve 181b overcome the elastic force of the first elastic member 182a and the second elastic member 182b, respectively, and move to their second positions. Thus, the first opening / closing portion 1811a1 of the first back pressure valve 181a blocks the first back pressure inlet 1721 of the first back pressure passage 170a, while conversely, the second opening / closing portion 1811b2 of the second back pressure valve 181b opens the second back pressure inlet 1722 of the second back pressure passage 170b. Therefore, the refrigerant in the compression chamber Vm2, which has a relatively low intermediate pressure, is transferred to the back pressure space S through the second back pressure inlet 1722, the second connecting passage 1813b, the second valve receiving portion 1712, and the second back pressure outlet 1732. Therefore, the back pressure space S forms a relatively low second back pressure and applies weak pressure to the rotating scroll 150 towards the fixed scroll 140. As a result, the rotating scroll 150 can maintain a relatively weak contact with the fixed scroll 140, thereby effectively suppressing frictional losses between the scrolls. This expands the operating range of the compressor.

[0146] On the other hand, in the foregoing embodiments, for convenience, the description focuses on an example where the back pressure passage connects to two compression chambers with different pressures. However, depending on the situation, the back pressure passage can also be configured to connect to three or more compression chambers. In this case, three or more back pressure inlets can be formed in one back pressure passage, and the three or more back pressure passages can also be formed independently. In this case, the back pressure of the back pressure space can be further varied according to the compressor's operating conditions, thereby further effectively suppressing leakage between compression chambers and / or frictional losses between scroll plates. As a result, the operating range of the compressor can be expanded.

[0147] On the other hand, in the aforementioned embodiments, the description focuses on a high-pressure scroll compressor in which the drive motor is located in the discharge space, but the same applies to a low-pressure scroll compressor in which the drive motor is located in the suction space and the discharge space is located on the discharge side of the compression section.

Claims

1. A scroll compressor, wherein, include: The shell has an ejection space; The main frame is located inside the shell. The vortex disk is supported along the axial direction by the main frame; A fixed scroll plate is attached to the main frame via the rotating scroll plate, and together with the rotating scroll plate, they form a compression chamber; The back pressure space is located between the main frame and the vortex disk; A back pressure passage is provided on the fixed scroll plate, so that the back pressure space is connected to the compression chamber; as well as A back pressure valve selectively opens and closes the back pressure passage; The back pressure passage is connected to a plurality of compression chambers in the compression chamber, each having a different pressure from the other.

2. The scroll compressor according to claim 1, wherein, The fixed scroll plate is also provided with a valve pressure passage connecting the back pressure passage and the discharge space of the housing; The back pressure valve is arranged such that one side faces the valve pressure passage and is slidably inserted into the back pressure passage according to the pressure of the discharge space.

3. The scroll compressor according to claim 2, wherein, The valve pressure passage facing the center of the back pressure valve is formed so that it is on the same line as the center of the back pressure valve.

4. The scroll compressor according to claim 2, wherein, The back pressure valve includes: The valve body has a plurality of opening and closing parts that selectively open and close the back pressure passage, and a connecting part connecting the plurality of opening and closing parts; and The connection passage is selectively connected to the back pressure passage according to the position of the valve body; The connection passage is formed by penetrating the interior of the valve body.

5. The scroll compressor according to claim 4, wherein, The connection path includes: A first passage portion is disposed in the connecting portion; and The second passage section is disposed in one of the plurality of opening and closing sections adjacent to the back pressure space and is connected to the first passage section; At least a portion of the second passage portion is formed on the same line as the first passage portion along the back pressure passage.

6. The scroll compressor according to claim 5, wherein, The opening and closing part facing the valve pressure passage among the plurality of opening and closing parts is formed in a blocked shape and is slidably inserted into the back pressure passage.

7. The scroll compressor according to claim 2, wherein, A valve support surface is provided between the back pressure passage and the valve pressure passage to restrict the movement of the back pressure valve.

8. The scroll compressor according to claim 2, wherein, An elastic member is provided on the opposite side of the valve pressure passage, across the back pressure valve, to elastically support the back pressure valve toward the valve pressure passage side.

9. The scroll compressor according to claim 8, wherein, A fixing member is provided in the back pressure passage to support the other end of the elastic member; The fixing member separates from the sealing member that seals one end of the back pressure passage.

10. The scroll compressor according to claim 9, wherein, A fixing member support surface is formed on the inner circumferential surface of the back pressure passage to limit the insertion depth of the fixing member.

11. The scroll compressor according to claim 8, wherein, A fixing member is provided in the back pressure passage to support the second end of the elastic member; The fixing member extends from the sealing member that seals the back pressure passage relative to the interior space of the housing.

12. The scroll compressor according to any one of claims 1 to 11, wherein, The back pressure passage forms a, The back pressure pathway includes: A valve receiving portion is disposed on the fixed scroll plate for accommodating the back pressure valve; A plurality of back pressure inlets are connected at one end of the valve housing to a plurality of compression chambers having different pressures, and are selectively opened and closed by the back pressure valve; and A back pressure outlet is connected to the back pressure space at the other end of the valve housing.

13. The scroll compressor according to claim 12, wherein, The plurality of back pressure inlets are formed on the same line as the back pressure outlet, with the length direction of the valve receiving portion as a reference.

14. The scroll compressor according to any one of claims 1 to 11, wherein, The back pressure pathways are separated from each other circumferentially, forming a plurality of pathways. Each of the plurality of back pressure paths includes: A valve receiving portion is disposed on the fixed scroll plate for accommodating the back pressure valve; A back pressure inlet, at one end of the valve housing, communicates with any one of a plurality of compression chambers having different pressures, and is selectively opened and closed by the back pressure valve; and A back pressure outlet is connected to the back pressure space at the other end of the valve housing.

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