JP7262013B2 - scroll compressor - Google Patents

Description

The present disclosure relates to scroll compressors.

Patent Literature 1 discloses a closed-vessel low-pressure type scroll compressor. As shown in FIG. 12, this scroll compressor has a compression element 5 composed of a fixed scroll 3 and an orbiting scroll 4 in a chamber 2 on the low pressure side partitioned by a partition plate 1, and the orbiting scroll 4 is driven to orbit. and an electric element 6 are arranged. The refrigerant compressed by the compression element 5 is discharged through the discharge port 7 of the fixed scroll 3 into the high-pressure side chamber 8 partitioned by the partition plate 1 . In such a closed-vessel low-pressure scroll compressor, the pressure of the compression chamber 9 having an intermediate pressure between the low pressure and the high pressure is introduced to the back surface of the orbiting scroll 4, that is, to the low-pressure chamber 2 side. Thereby, the orbiting scroll 4 is pressed against the fixed scroll 3 so that the orbiting scroll 4 does not separate from the fixed scroll 3 .

US2010/0028182 publication

The present disclosure provides a scroll compressor with improved performance and reliability by properly pressing the orbiting scroll against the fixed scroll.

In the scroll compressor of the present disclosure, a low-pressure space, a low-pressure and high-pressure intermediate pressure chamber, and a high-pressure chamber are arranged behind the orbiting scroll, and pressure from these chambers presses the orbiting scroll against the fixed scroll. configured to be

FIG. 1 is a longitudinal sectional view showing the configuration of a scroll compressor according to Embodiment 1 of the present disclosure. FIG. 2 is a cross-sectional view of a main portion of a compression element of the scroll compressor. FIG. 3 is a cross-sectional view of a partition plate portion of the scroll compressor. FIG. 4 is a longitudinal sectional view showing the structure of a scroll compressor according to Embodiment 2. FIG. FIG. 5 is a longitudinal sectional view showing the configuration of a scroll compressor according to Embodiment 3. FIG. FIG. 6 is a cross-sectional view of a main portion of a compression element of the scroll compressor. FIG. 7 is a bottom view of the fixed scroll of the scroll compressor. FIG. 8 is an enlarged longitudinal sectional view of the vicinity of the annular seal member after assembly of the scroll compressor according to the fourth embodiment. FIG. 9 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembly of the scroll compressor. FIG. 10 is an enlarged longitudinal sectional view of the vicinity of the annular seal member before assembly of the scroll compressor according to the fifth embodiment. FIG. 11 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembly of the scroll compressor according to the sixth embodiment. FIG. 12 is a longitudinal sectional view of a conventional scroll compressor.

(Knowledge, etc. on which this disclosure is based)
At the time when the inventors came up with the present disclosure, as shown in Patent Document 1, a closed-vessel low-pressure type scroll compressor had a pressure in a compression chamber 9 between a low pressure and a high pressure on the back of the orbiting scroll 4. was introduced so that the orbiting scroll 4 would not separate from the fixed scroll 3 . In the configuration shown in Patent Document 1, an eccentric rotating shaft for orbiting the orbiting scroll 4 is installed at the center of the back surface of the orbiting scroll 4 . Here, since the inside of the sealed container of the scroll compressor has a low pressure, the central area on the back surface of the orbiting scroll 4 is a low pressure area. On the other hand, in the configuration shown in Patent Document 1, it is difficult to form a region for introducing the pressure of the compression chamber 9 on the back surface of the orbiting scroll 4 . Therefore, when the pressure in the compression chamber 9 is low, the pressure introduced to the back surface of the orbiting scroll 4 is also low, and the orbiting scroll 4 separates from the fixed scroll 3 . As a result, a gap is formed between the orbiting scroll 4 and the fixed scroll 3, and pressure leakage may reduce compression efficiency. Moreover, when the pressure in the compression chamber 9 is high, the pressure introduced to the back surface of the orbiting scroll 4 also increases. As a result, the orbiting scroll 4 does not move away from the fixed scroll 3, but the pressing force of the orbiting scroll 4 against the fixed scroll 3 becomes excessive, which may cause deterioration of performance or reliability.

In this way, the inventors have recognized that the conventional scroll compressor has room for improvement in terms of performance and reliability, and have come to constitute the subject matter of the present disclosure in order to solve this.

The present disclosure provides a scroll compressor that suppresses a decrease in efficiency and improves performance and reliability.

Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed description than necessary may be omitted. For example, detailed descriptions of well-known matters or redundant descriptions of substantially the same configurations may be omitted. This is to avoid the following description from becoming more redundant than necessary and to facilitate understanding by those skilled in the art.

It should be noted that the accompanying drawings and the following description are provided to allow those skilled in the art to fully understand the present disclosure and are not intended to limit the claimed subject matter thereby.

(Embodiment 1)
Embodiment 1 will be described below with reference to FIGS. 1 to 3. FIG.

[1-1. composition]
1 to 3, the compressor 10 has, as an outer shell, a cylindrical sealed container 20 whose longitudinal direction is the vertical direction. In this embodiment, the vertical direction is the Z-axis direction in each drawing.

The compressor 10 is a closed scroll compressor provided with a compression mechanism 30 for compressing refrigerant and an electric motor 40 for driving the compression mechanism 30 inside a closed container 20 .

A partition plate 50 that divides the inside of the closed container 20 into upper and lower parts is provided above the inside of the closed container 20 . The partition plate 50 partitions the inside of the sealed container 20 into a high-pressure space 60 and a low-pressure space 70 . The high-pressure space 60 is a space filled with high-pressure refrigerant that has been compressed by the compression mechanism section 30 . The low-pressure space 70 is a space filled with low-pressure refrigerant before being compressed by the compression mechanism section 30 .

The sealed container 20 includes a refrigerant suction pipe 80 that communicates the outside of the sealed container 20 with the low-pressure space 70 , and a refrigerant discharge pipe 90 that connects the outside of the closed container 20 with the high-pressure space 60 . A low-pressure refrigerant is introduced into the low-pressure space 70 of the compressor 10 from a refrigeration cycle circuit (not shown) provided outside the sealed container 20 via a refrigerant suction pipe 80 . The high-pressure refrigerant compressed by the compression mechanism section 30 is first introduced into the high-pressure space 60 . After that, the refrigerant is discharged from the high-pressure space 60 through the refrigerant discharge pipe 90 to the refrigeration cycle circuit.

An oil reservoir 100 in which lubricating oil is stored is formed at the bottom of the low-pressure space 70 .

The compressor 10 includes a compression mechanism section 30 and an electric motor 40 in a low pressure space 70 .

The compression mechanism section 30 is composed of at least a fixed scroll 110 , an orbiting scroll 120 , a main bearing 130 and a rotation suppressing member (hereinafter referred to as an Oldham ring) 140 . The fixed scroll 110 is arranged below the partition plate 50 and adjacent to the partition plate 50 . The orbiting scroll 120 is arranged below the fixed scroll 110 so as to mesh with the fixed scroll 110 .

The fixed scroll 110 includes a disk-shaped fixed scroll end plate 111 and a spiral fixed spiral wrap 112 erected on the lower surface of the fixed scroll end plate 111 .

The orbiting scroll 120 includes a disk-shaped orbiting scroll end plate 121 , a spiral orbiting spiral wrap 122 erected on the upper surface of the orbiting scroll end plate 121 , and a lower boss portion 123 . The lower boss portion 123 is a cylindrical protrusion formed substantially in the center of the lower surface of the orbiting scroll end plate 121 .

A compression chamber 150 is formed between the orbiting scroll 120 and the fixed scroll 110 by meshing the orbiting spiral wrap 122 of the orbiting scroll 120 and the fixed spiral wrap 112 of the fixed scroll 110 . The compression chambers 150 are formed on the inner wall surface side and the outer wall surface side of the orbiting spiral wrap 122 .

A main bearing 130 that supports the orbiting scroll 120 is provided below the fixed scroll 110 and the orbiting scroll 120 . The main bearing 130 includes a boss accommodating portion 131 provided substantially in the center of the upper surface, and a bearing portion 132 provided below the boss accommodating portion 131 . The boss accommodating portion 131 is a concave portion for accommodating the lower boss portion 123 of the orbiting scroll 120 . The bearing portion 132 is a through hole whose upper end opens to the boss accommodating portion 131 and whose lower end opens to the low-pressure space 70 .

The main bearing 130 supports the orbiting scroll 120 on its upper surface and supports the rotating shaft 160 with the bearing portion 132 .

The rotating shaft 160 is a shaft whose longitudinal direction is the vertical direction in FIG. One end side of the rotary shaft 160 is supported by the bearing portion 132 , and the other end side is supported by the auxiliary bearing 170 . Secondary bearing 170 is a bearing provided below low pressure space 70 , preferably within oil sump 100 . An eccentric shaft 161 eccentric to the axis of the rotating shaft 160 is provided at the upper end of the rotating shaft 160 . The eccentric shaft 161 is slidably inserted into the lower boss portion 123 via the swing bush 180 and the swivel bearing 124 . The lower boss portion 123 is pivotally driven by the eccentric shaft 161 .

An oil passage 162 through which lubricating oil passes is formed inside the rotary shaft 160 . The oil passage 162 is a through hole formed in the axial direction of the rotating shaft 160 . One end of the oil passage 162 opens into the oil reservoir 100 as a suction port 163 provided at the lower end of the rotating shaft 160 . A paddle 190 for pumping lubricating oil from the suction port 163 to the oil passage 162 is provided above the suction port 163 .

Inside the rotary shaft 160 , a first branched oil passage 164 is formed above the rotary shaft 160 and a second branched oil passage 165 is formed below the rotary shaft 160 . One end of the first branched oil passage 164 opens at the bearing surface of the bearing portion 132 as a first oil supply port 166 , and the other end of the first branched oil passage 164 communicates with the oil passage 162 . One end of the second branched oil passage 165 opens as a second oil supply port 167 on the bearing surface of the sub bearing 170 , and the other end of the second branched oil passage 165 communicates with the oil passage 162 .

The upper end of the oil passage 162 opens inside the boss accommodating portion 131 as a third oil supply port 168 .

The rotating shaft 160 is connected to the electric motor 40 . Electric motor 40 is arranged between main bearing 130 and sub-bearing 170 . The electric motor 40 includes a stator 41 fixed to the closed container 20 and a rotor 42 arranged inside the stator 41 .

The rotating shaft 160 is fixed to the rotor 42 . The rotating shaft 160 has a balance weight 200a provided above the rotor 42 and a balance weight 200b provided below the rotor 42 . The balance weight 200a and the balance weight 200b are arranged at positions shifted by 180° in the circumferential direction of the rotating shaft 160. As shown in FIG.

Rotating shaft 160 rotates while balancing the centrifugal force generated by balance weights 200 a and 200 b and the centrifugal force generated by the orbital motion of orbiting scroll 120 . Note that the balance weight 200 a and the balance weight 200 b may be provided on the rotor 42 .

Fixed scroll 110 , orbiting scroll 120 and Oldham ring 140 are arranged between partition plate 50 and main bearing 130 .

The partition plate 50 and the main bearing 130 are fixed to the closed container 20 . The fixed scroll 110 is fastened to the main bearing 130 with bolts or the like. The orbiting scroll 120 is axially movable between the fixed scroll 110 and the main bearing 130 .

In the present disclosure, low-pressure spaces (low-pressure regions) 71 and 72 having low pressure are arranged at the center and outermost periphery of the back surface of the orbiting scroll 120 . A high-pressure chamber 221 having a high pressure and an intermediate-pressure chamber 222 having an intermediate pressure are arranged between the low-pressure space 71 at the center and the low-pressure space 72 at the outermost periphery. The high-pressure chamber 221 is arranged on the back surface of the orbiting scroll 120 inside the intermediate-pressure chamber 222 , that is, on the center side.

Further, as shown in FIG. 2 , a plurality of annular grooves 133 are formed on the surface of the main bearing 130 that supports the orbiting scroll 120 outside the boss accommodating portion 131 . A seal member 210 is inserted into the annular groove 133 . A pressure chamber 220 is formed between the seal members 210 by the seal members 210 coming into contact with the back surface of the orbiting scroll 120 . A higher pressure than the low-pressure spaces (low-pressure areas) 71 and 72 is introduced into this space (pressure chamber 220). The sealing member 210 is made of a resin material such as PTFE, which is generally considered to have good sealing properties. Note that the sealing member 210 may be configured in an annular shape.

In this embodiment, the pressure chamber 220 is further partitioned into a high pressure chamber 221 and an intermediate pressure chamber 222 by a seal member 210 . A pressure equivalent to that of the discharge gas is introduced into the high-pressure chamber 221 . The intermediate pressure chamber 222 is supplied with the pressure of the gas during compression between the low pressure and the high pressure of the compression chamber 150 .

With this configuration, the area of the high-pressure chamber 221 and the intermediate-pressure chamber 222 with respect to the orbiting scroll 120 and the pressure of the compression chamber 150 introduced into the intermediate-pressure chamber 222 can be appropriately set. Therefore, even in a closed container low-pressure compressor, the orbiting scroll 120 does not move away from the fixed scroll 110 and the orbiting scroll 120 does not separate from the fixed scroll 110 under various operating conditions in which the compression pressure is low and high. It is possible to set an optimum pressing force that does not press too much.

A return path 134 is formed in the main bearing 130 , one end of which is open to the boss accommodating portion 131 and the other end of which is open to the lower surface of the main bearing 130 .

Oldham ring 140 is provided between fixed scroll 110 and orbiting scroll 120 . The Oldham's ring 140 prevents the rotation of the orbiting scroll 120 and makes an orbiting motion.

A detailed configuration of the compressor 10 will be further described with reference to FIG.

The orbiting spiral wrap 122 is a wall having an involute curved cross section whose radius gradually increases from the center side of the orbiting scroll end plate 121 toward the outer peripheral side. The orbiting spiral wrap 122 has a predetermined height (vertical length) and a predetermined wall thickness (the radial length of the orbiting spiral wrap 122).

A discharge counterbore 125 is formed in a compression chamber 150 communicating with a first discharge port 113 (to be described later) at substantially the center of the orbiting scroll 120 . As shown in FIG. 2 , the orbiting scroll end plate 121 is formed with a high-pressure introduction path 126 that communicates the discharge counterbore 125 and the high-pressure chamber 221 .

Further, the orbiting scroll end plate 121 is formed with an intermediate pressure port 127 in a region where an intermediate pressure refrigerant in the middle of compression exists. The intermediate pressure introduction path 128 communicates the intermediate pressure port 127 and the intermediate pressure chamber 222 (see FIG. 2).

A pair of key grooves are provided on the Oldham ring 140 side of the orbiting scroll end plate 121 .

The fixed spiral wrap 112 is a wall having an involute curved cross section whose radius gradually increases from the center side of the fixed scroll end plate 111 toward the outer peripheral side. The stationary spiral wrap 112 has a predetermined height (vertical length) equal to that of the orbiting spiral wrap 122 and a predetermined wall thickness (the radial length of the stationary spiral wrap 112).

A first discharge port 113 is formed at substantially the center of the fixed scroll end plate 111, as shown in FIG. A bypass port 114 is formed in the fixed scroll end plate 111 . The bypass port 114 is arranged in the vicinity of the first discharge port 113 and in a region where high-pressure refrigerant exists just before the completion of compression. The bypass port 114 includes a bypass port communicating with the compression chamber 150 formed on the outer wall surface side of the orbiting spiral wrap 122 and a bypass port communicating with the compression chamber 150 formed on the inner wall surface side of the orbiting spiral wrap 122. Two sets are provided.

As shown in FIGS. 1 and 2 , the outer peripheral portion of the fixed scroll 110 is formed with an outer peripheral stepped portion 115 having a step with respect to the tip of the fixed spiral wrap 112 . The outer peripheral stepped portion 115 is arranged at a position lower than the tip of the fixed spiral wrap 112 by the thickness of the Oldham ring 140 or more. An Oldham ring 140 is arranged on the outer peripheral step portion 115 .

A pair of key grooves are provided on the outer peripheral portion of the fixed scroll 110 .

A suction portion (not shown) for taking refrigerant into the compression chamber 150 is formed on the peripheral wall of the fixed scroll 110 .

As shown in FIG. 3, an upper boss portion 119 is provided in the center of the upper surface of the fixed scroll 110 (the surface on the partition plate 50 side). The upper boss portion 119 is a cylindrical protrusion that protrudes from the upper surface of the fixed scroll 110 . The first discharge port 113 and the bypass port 114 open on the upper surface of the upper boss portion 119 . A discharge space 110</b>H is formed between the upper boss portion 119 and the partition plate 50 on the upper surface side of the upper boss portion 119 . The first discharge port 113 and the bypass port 114 communicate with the discharge space 110H.

A bypass check valve 230 for opening and closing the bypass port 114 and a bypass check valve stop 240 for preventing excessive deformation of the bypass check valve 230 are provided on the upper surface of the upper boss portion 119 . By using a reed valve for the bypass check valve 230, the size in the height direction can be made compact.

Oldham ring 140 is arranged between fixed scroll 110 and orbiting scroll 120 . As described above, the Oldham ring 140 is arranged on the outer peripheral stepped portion 115 of the fixed scroll 110 .

The Oldham ring 140 includes a substantially annular ring portion, a pair of first keys protruding from the upper surface of the ring portion, and a pair of second keys protruding from the lower surface of the ring portion. The first keys are arranged on parallel straight lines that are not aligned. The second keys are arranged on parallel straight lines that are not aligned. The straight line on which the first keys are arranged and the straight line on which the second keys are arranged are provided so as to be orthogonal.

A first key engages a first keyway of fixed scroll 110 and a second key engages a second keyway of orbiting scroll 120 (not shown). This allows the orbiting scroll 120 to orbit without rotating with respect to the fixed scroll 110 .

FIG. 3 is a cross-sectional view of the main part of the partition plate portion of the scroll compressor according to the present embodiment.

A second discharge port 51 is provided in the center of the partition plate 50 . A discharge check valve 250 for freely opening and closing the second discharge port 51 and a discharge check valve stop 260 for preventing excessive deformation of the discharge check valve 250 are provided on the upper surface of the partition plate 50 .

A discharge space 110H is formed between the partition plate 50 and the fixed scroll 110 . The discharge space 110</b>H communicates with the compression chamber 150 through the first discharge port 113 and the bypass port 114 . The discharge space 110</b>H communicates with the high pressure space 60 through the second discharge port 51 .

The plate thickness of the discharge check valve 250 is thicker than the plate thickness of the bypass check valve 230 . This prevents the discharge check valve 250 from opening earlier than the bypass check valve 230 .

The cross-sectional area of the second discharge port 51 is larger than the cross-sectional area of the first discharge port 113 . Thereby, the pressure loss of the refrigerant discharged from the compression chamber 150 can be reduced.

Also, the inflow side of the second discharge port 51 may be tapered. Thereby, the pressure loss can be further reduced.

A concave portion 52 is provided around the second discharge port 51 on the lower surface of the partition plate 50 . An upper boss portion 119 of the fixed scroll 110 is inserted into the recess 52 to form a discharge space 110H. A boss seal member 270 seals between the discharge space 110H and the low-pressure space 70 . Boss seal member 270 may be configured in an annular shape.

[1-2. motion]
The operation and function of the compressor 10 configured as described above will be described below. By driving the electric motor 40 , the rotating shaft 160 rotates together with the rotor 42 . Due to the rotation of the eccentric shaft 161 accompanying the rotation of the rotating shaft 160 and the Oldham ring 140 , the orbiting scroll 120 orbits around the central axis of the rotating shaft 160 without rotating. Thereby, the refrigerant is introduced from the refrigerant suction pipe 80 into the low-pressure space 70 . The refrigerant introduced into low-pressure space 70 cools electric motor 40 and is sucked into compression chamber 150 from the suction portion of fixed scroll 110 . Refrigerant sucked into compression chamber 150 is compressed as its volume decreases.

The intermediate-pressure refrigerant during compression is introduced from the intermediate-pressure port 127 shown in FIG.

The compressed high-pressure refrigerant is introduced from the discharge counterbore 125 shown in FIG.

Therefore, the orbiting scroll 120 is pressed against the fixed scroll 110 from the rear surface of the orbiting scroll 120 by appropriately set pressures in the intermediate pressure chamber 222 and the high pressure chamber 221 . Therefore, the orbiting scroll 120 does not move away from the fixed scroll 110 and the orbiting scroll 120 does not separate from the fixed scroll 110 under various operating conditions in which the compression pressure is different from that in the case where only the intermediate pressure chamber 222 is provided. It is possible to set an optimum pressing force that does not press too much. Therefore, it is possible to prevent a decrease in efficiency and a decrease in reliability in the closed container low-pressure compressor.

The opening of the intermediate pressure introduction path 128 on the intermediate pressure chamber 222 side intermittently communicates with the intermediate pressure chamber 222 across the seal member 210 as the orbiting scroll 120 orbits.

As a result, the intermediate pressure chamber 222 can be intermittently communicated with the compression chamber 150 whose pressure fluctuates due to compression of the refrigerant. Therefore, the pressure pulsation in the intermediate pressure chamber 222 can be reduced, and the separation of the orbiting scroll 120 from the fixed scroll 110 can be more reliably suppressed, thereby improving the efficiency of the compressor.

Also, in the scroll compressor of the present disclosure, Oldham's ring 140 is arranged between fixed scroll 110 and orbiting scroll 120 . Thereby, the intermediate pressure chamber 222 and the high pressure chamber 221 provided on the back surface of the orbiting scroll 120 can be widened compared to the conventional compressor in which the Oldham ring 140 is arranged on the back surface side of the orbiting scroll 120 . Therefore, the areas of the intermediate pressure chambers 222 and the high pressure chambers 221 necessary for properly pressing the orbiting scroll 120 against the fixed scroll 110 can be secured. Therefore, even in a closed container low-pressure compressor, separation of the orbiting scroll 120 from the fixed scroll 110 is suppressed and the orbiting scroll 120 is prevented from moving away from the fixed scroll 110 under various operating conditions of different low and high compression pressures. It is possible to set an optimum pressing force that does not press too much against. Therefore, it is possible to prevent a decrease in efficiency and a decrease in reliability of the compressor.

The Oldham ring 140 is installed on the outer peripheral stepped portion 115 communicating with the low-pressure space 70 . Therefore, the sliding portion of the Oldham's ring 140 is lubricated with the oil contained in the sucked refrigerant, thereby preventing deterioration in reliability.

In addition, in the scroll compressor of the present disclosure, low-pressure spaces (low-pressure regions) 71 and 72 are arranged in the central portion and outermost peripheral portion of the back surface of the orbiting scroll 120 . A high pressure chamber 221 and an intermediate pressure chamber 222 are arranged between the low pressure spaces (low pressure regions) 71 and 72 on the back surface of the orbiting scroll 120 . The high pressure chamber 221 is arranged inside (center side) of the intermediate pressure chamber 222 . With such a configuration, the orbiting scroll 120 is pressed against the fixed scroll 110 with an appropriate pressing force.

In the compression chamber 150 formed by the orbiting scroll 120 and the fixed scroll 110, the refrigerant is compressed from low pressure to high pressure as it goes from the outer periphery to the center. Therefore, the central portion of the orbiting scroll 120 receives force in a direction away from the fixed scroll 110 due to a pressure close to high pressure. However, according to the configuration of the present embodiment, on the back surface of orbiting scroll 120, high pressure chamber 221 is arranged closer to the central portion than intermediate pressure chamber 222, so that the central portion of orbiting scroll 120 is stronger than the outer peripheral portion. It can be pressed against the fixed scroll 110 . Therefore, separation of the orbiting scroll 120 from the fixed scroll 110 can be more effectively suppressed, and pressure leakage can be reduced. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.

[1-3. effects, etc.]
As described above, the scroll compressor according to the present embodiment includes the partition plate 50 that divides the inside of the sealed container 20 into the high-pressure space 60 and the low-pressure space 70, the fixed scroll 110 adjacent to the partition plate 50, and the fixed scroll 110. It has an orbiting scroll 120 that meshes to form a compression chamber 150 , a rotation suppressing member 140 that prevents rotation of the orbiting scroll 120 , and a main bearing 130 that supports the orbiting scroll 120 . Fixed scroll 110 , orbiting scroll 120 , rotation suppressing member 140 , and main bearing 130 are arranged in low-pressure space 70 . Fixed scroll 110 and orbiting scroll 120 are arranged between partition plate 50 and main bearing 130 . Low-pressure spaces (low-pressure regions) 71 and 72 , an intermediate-pressure chamber 222 for low pressure and high pressure, and a high-pressure chamber 221 are arranged on the back surface of the orbiting scroll 120 .

Thus, even if the pressure inside the closed container is low, the intermediate pressure chamber 222 and the high pressure chamber 221 can introduce a proper pressure to a proper region on the back surface of the orbiting scroll 120 . Therefore, separation of the orbiting scroll 120 from the fixed scroll 110 can be suppressed, and pressure leakage can be reduced. In addition, since it is not necessary to attach a special component to the back surface of the orbiting scroll for enlarging the area to which pressure is applied, it is possible to prevent a decrease in efficiency and reliability with a simple configuration.

The scroll compressor according to the present embodiment has a configuration in which the central portion and the outermost peripheral portion on the back surface of the orbiting scroll are low pressure spaces (low pressure regions) 71 and 72, and the high pressure chamber 221 is arranged inside the intermediate pressure chamber 222. be. As a result, a large pressure can be applied to the central portion of the orbiting scroll 120 to which strong pressure is applied in the direction away from the fixed scroll 110 . Therefore, separation of the orbiting scroll 120 from the fixed scroll 110 can be effectively suppressed, pressure leakage can be reduced, and an appropriate pressing force can be applied to the orbiting scroll 120, resulting in reduced efficiency and reduced reliability. can be prevented.

In the scroll compressor of the present embodiment, an annular seal member 210 is arranged on the back surface of the orbiting scroll 120 to separate the low pressure spaces (low pressure regions) 71, 72, the intermediate pressure chamber 222, and the high pressure chamber 221 from each other. ing. As a result, pressure leakage between the low-pressure spaces (low-pressure areas) 71 and 72, the intermediate-pressure chamber 222, and the high-pressure chamber 221 can be reduced. Therefore, since an appropriate pressure can be stably introduced into the intermediate pressure chamber 222 and the high pressure chamber 221, separation of the orbiting scroll 120 from the fixed scroll 110 can be suppressed, and pressure leakage can be reduced. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability. Since it is possible to suppress the pressure from leaking from the intermediate pressure chamber 222 and the high pressure chamber 221 to the low pressure spaces (low pressure regions) 71, 72, it is possible to suppress a decrease in efficiency.

In addition, in the scroll compressor of the present embodiment, since the compression chamber 150 and the intermediate pressure chamber 222 are communicated with each other, the pressure communicating with the compression chamber 150 can be arbitrarily determined. Therefore, it is possible to press the orbiting scroll 120 against the fixed scroll 110 with an optimum pressure. Therefore, separation of the orbiting scroll 120 from the fixed scroll 110 can be suppressed, and pressure leakage can be reduced. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.

In addition, in the scroll compressor of the present embodiment, rotation suppressing member 140 is arranged between orbiting scroll 120 and fixed scroll 110 . As a result, the high pressure chambers 221 and the intermediate pressure chambers 222 can be provided in the area behind the orbiting scroll 120 to the maximum. Therefore, it is possible to properly press the orbiting scroll 120 against the fixed scroll 110, suppress the separation of the orbiting scroll 120 from the fixed scroll 110, and reduce pressure leakage. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.

(Embodiment 2)
FIG. 4 is a longitudinal sectional view of a scroll compressor according to Embodiment 2. FIG.

[2-1. composition]
As shown in FIG. 4, the compressor 10 has, as an outer shell, a cylindrical sealed container 20 whose longitudinal direction is the vertical direction. In this embodiment, the vertical direction is the Z-axis direction in each drawing.

Since the basic configuration of this embodiment is the same as that of the first embodiment, the description is omitted. Further, the same reference numerals are assigned to the same configurations as those described in the first embodiment, and the description thereof is partially omitted.

In this embodiment, a high pressure introduction path 129 is arranged inside fixed scroll 110 . A high pressure introduction path 126 is arranged inside the orbiting scroll 120 .

As a result, the orbiting scroll 120 orbits to intermittently communicate the high-pressure introduction path 126 and the high-pressure introduction path 129, thereby communicating the discharge space 110H where the high-pressure refrigerant is discharged from the fixed scroll 110 and the high-pressure chamber 221. be.

[2-2. motion]
According to the above configuration, a more stable pressure with less pulsation can be introduced into the high-pressure chamber 221 . Therefore, it is possible to stably press the orbiting scroll 120 against the fixed scroll 110, suppress the separation of the orbiting scroll 120 from the fixed scroll 110, and reduce pressure leakage. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.

Moreover, since the oil accumulated in the discharge space 110H can be supplied to the sliding portion between the orbiting scroll 120 and the fixed scroll 110, the reliability of the sliding portion can be improved.

[2-3. effects, etc.]
In the scroll compressor according to the present embodiment, discharge space 110H and high pressure chamber 221 are communicated with each other. As a result, a stable pressure can be applied to the high-pressure chamber 221 with relatively little fluctuation, so that the orbiting scroll 120 can be stably pressed against the fixed scroll 110 . Therefore, separation of the orbiting scroll 120 from the fixed scroll 110 can be suppressed more reliably, and pressure leakage can be reduced. Moreover, since an appropriate pressing force can be applied to the orbiting scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.

(Embodiment 3)
FIG. 5 is a longitudinal sectional view of a scroll compressor according to Embodiment 3. FIG. 6 is a cross-sectional view of main parts of the compression element of the scroll compressor, and FIG. 7 is a bottom view of the fixed scroll.

[3-1. composition]
As shown in FIGS. 5 and 6, the compressor 10 has, as an outer shell, a cylindrical sealed container 20 whose longitudinal direction is the vertical direction. In this embodiment, the vertical direction is the Z-axis direction in each drawing.

Since the basic configuration of this embodiment is the same as that of the first embodiment, the description is omitted. Further, the same reference numerals are assigned to the same configurations as those described in the first embodiment, and the description thereof is partially omitted.

In the present embodiment, the intermediate pressure chamber 222 and the high pressure chamber 221 are arranged inside the outermost peripheral portion 116 of the thrust sliding surface between the fixed scroll 110 and the orbiting scroll 120 (one-dot chain lines in FIGS. 6 and 7). there is Here, the outermost peripheral portion 116 of the thrust sliding surface refers to the peripheral edge of the maximum range of the thrust sliding surface between the fixed scroll 110 and the orbiting scroll 120 .

By arranging the pressure chambers as described above, pressing force is applied to the orbiting scroll 120 by the intermediate pressure chambers 222 and the high pressure chambers 221 inside the outermost peripheral portion 116 of the thrust sliding surface.

[3-2. motion]
In the scroll compressor of the present embodiment, orbiting scroll 120 is pressurized by intermediate pressure chamber 222 and high pressure chamber 221 provided inside outermost peripheral portion 116 of thrust sliding surface between fixed scroll 110 and orbiting scroll 120 . , is pressed against the fixed scroll 110 . Therefore, deformation of the outer peripheral portion of the orbiting scroll end plate 121 due to the pressure in the intermediate pressure chamber 222 and the high pressure chamber 221 can be suppressed.

[3-3. effects, etc.]
The scroll compressor according to the present embodiment has the structure of the first embodiment or the second embodiment, and furthermore, the intermediate pressure chamber 222 and the high pressure chamber 221 are separated from the thrust sliding surface outermost peripheral portion 116 of the orbiting scroll and the fixed scroll. are also placed inside.

As a result, deformation of the outer peripheral portion of the orbiting scroll end plate 121 due to the pressure in the intermediate pressure chamber 222 and the high pressure chamber 221 can be suppressed. For this reason, it is possible to suppress local sliding in the vicinity of the outermost peripheral portion 116 of the thrust sliding surface of the fixed scroll 110 in particular, and it is possible to prevent a decrease in efficiency and a decrease in reliability.

(Embodiment 4)
The scroll compressor of the present embodiment will be described with a focus on additional configurations or configurations different from those of the first to third embodiments. In this embodiment, seals between the low-pressure spaces (low-pressure areas) 71, 72 and the high-pressure chamber 221 and the intermediate-pressure chamber 222 are configured as described below. This makes it possible to more reliably and effectively prevent deterioration in performance and reliability.

FIG. 8 is an enlarged longitudinal sectional view of the vicinity of the annular seal member after assembly of the scroll compressor according to the present embodiment. Since the basic configuration of this embodiment is the same as that of the first to third embodiments, description thereof will be omitted. Further, the same reference numerals are assigned to the same configurations as those already described, and the description thereof is partially omitted.

As shown in FIG. 8, between the low-pressure spaces (low-pressure areas) 71 and 72 and the high-pressure chamber 221 and the intermediate-pressure chamber 222, a plurality of annular seal members 210 are provided in a plurality of storage grooves 133 provided in the main bearing 130. It is sealed by being inserted. Specifically, a plurality of annular seal members 210a, 210b, 210c are inserted into the storage grooves 133a, 133b, 133c, respectively. A plurality of spring members 211a, 211b and 211c are inserted between the plurality of annular seal members 210a, 210b and 210c and the bottom surfaces of the storage grooves 133a, 133b and 133c, respectively. In this embodiment, the plurality of spring members 211a, 211b, and 211c are configured such that the spring loads F during assembly are substantially the same.

Specifically, the spring load F of each of the plurality of spring members 211 is desirably within ±10% of the average spring load of the plurality of spring members 211 . Thereby, the plurality of annular seal members 210 are uniformly pressed against the orbiting scroll 120 by the plurality of spring members 211 . Therefore, it is possible to more reliably and effectively prevent a decrease in efficiency and a decrease in reliability.

In particular, the operation of the annular seal member 210 may become unstable immediately after the compressor is started or depending on the operating conditions. If the operation of the annular seal member 210 becomes unstable, the annular seal member 210 will not be pressed against the back surface of the orbiting scroll 120, and as a result, the intermediate pressure chamber 222 having a lower pressure than the high pressure chamber 221 will be filled with the high pressure of the high pressure chamber 221. Refrigerant and oil can flow excessively. In such a case, the orbiting scroll 120 is excessively pressed against the fixed scroll 110, which may reduce the efficiency of the compressor and cause a decrease in reliability.

However, according to the configuration of the present embodiment, the plurality of annular seal members 210a, 210b, 210c are pressed against the back surface of the orbiting scroll 120 by the spring loads of the plurality of spring members 211a, 211b, 211c. . Further, the plurality of spring members 211a, 211b, and 211c are configured such that the spring loads F at the time of assembly are substantially the same. Therefore, the back surface of the orbiting scroll 120 is imprinted by the annular seal members 210a, 210b, and 210c in good balance. That is, it is possible to stably stamp the back surface of the orbiting scroll 120 without being affected by pressure fluctuations or the like. For this reason, it is possible to improve the efficiency from the start of the compressor, and to suppress deterioration in performance and reliability due to unstable behavior of the orbiting scroll 120 .

In general, the spring load F is expressed as: spring load F=spring constant k×spring contraction amount x. In this embodiment, the spring constant ka of the spring member (first spring member) 211a, the spring constant kb of the spring member (second spring member) 211b, and the spring constant kc of the spring member (third spring member) 211c making the constants approximately equal to each other.

Specifically, the spring constant of each spring member 211 is preferably within ±10% of the average spring constant of the spring members 211 . Thereby, the spring load F of each spring member 211 can be within ±10% of the average of the spring load F.

FIG. 9 is an enlarged longitudinal sectional view of the vicinity of the annular seal member before assembly of the scroll compressor according to the present embodiment.

The spring constant ka of the spring member (first spring member) 211a, the spring constant kb of the spring member (second spring member) 211b, and the spring constant kc of the spring member (third spring member) 211c are substantially the same. Furthermore, in order to keep the contraction amount x of the spring constant, a storage groove (first storage groove) 133a, a storage groove (second storage groove) 133b, and a storage groove (third storage groove) 133c arranged in the main bearing 130 are provided. are made constant, and the natural lengths 211h (natural lengths 211ah, 211bh, 211ch) of the plurality of spring members 211a, 211b, 211c are made constant.

With this configuration, in a configuration in which the plurality of spring members 211a, 211b, and 211c have different outer diameters, for example, when leaf springs are used as the plurality of spring members 211, the spring thickness, spring width, number of folds, and the like of the leaf spring can be adjusted. , it is possible to easily keep the spring constants ka, kb and kc constant. By making the contraction amount x of the spring substantially the same, the spring load can be easily made substantially the same among the plurality of spring members.

In the above description, the depths 133h (depths 133ah, 133bh, 133ch) of the storage grooves 133a, 133b, 133c of the main bearing 130 are constant, and the plurality of spring members 211a, 211b, 211c are natural. The length 211h (natural lengths 211ah, 211bh, 211ch) is constant. However, by changing at least one of the depth 133h of each of the storage grooves 133a, 133b, and 133c and the natural length 211h of the plurality of spring members 211a, 211b, and 211c, each spring of the spring members 211a, 211b, and 211c is changed. It goes without saying that the amount of shrinkage x may be constant.

As described above, the scroll compressor according to the present embodiment includes a partition plate that divides the inside of the closed container into a high-pressure space and a low-pressure space, a fixed scroll adjacent to the partition plate, and a compression chamber that is meshed with the fixed scroll. an orbiting scroll, a rotation suppressing member that prevents the orbiting scroll from rotating, and a main bearing that supports the orbiting scroll. The fixed scroll, orbiting scroll, rotation suppressing member, and main bearing are arranged in a low-pressure space, and the fixed scroll and orbiting scroll are arranged between the partition plate and the main bearing. A low-pressure space, a low-pressure and high-pressure intermediate pressure chamber, and a high-pressure chamber are arranged behind the orbiting scroll. Furthermore, a plurality of annular seal members are arranged to partition the low pressure space, the intermediate pressure chamber and the high pressure chamber, and a plurality of spring members are arranged on the rear surface of the annular seal member.

Accordingly, even if the pressure inside the sealed container is low, it is possible to introduce a proper pressure to a proper region on the back surface of the orbiting scroll, thereby suppressing separation of the orbiting scroll from the fixed scroll. Therefore, pressure leakage can be reduced, and a proper pressing force can be applied to the orbiting scroll, thereby preventing reduction in efficiency and reliability.

In addition, since a plurality of spring members are arranged on the back surface of the plurality of annular seal members, by making the respective spring loads substantially the same among the plurality of spring members, it is possible to turn the compressor particularly immediately after starting the compressor. A plurality of annular seal members can be pressed against the fixed scroll in a well-balanced manner on the back surface of the scroll, thereby improving sealing performance. Therefore, the orbiting scroll can be stably pressed against the fixed scroll, and performance and reliability can be effectively improved.

It should be noted that the spring constants of the plurality of spring members may be mutually constant.

As a result, in a configuration in which the outer diameters of the plurality of spring members are different from each other, for example, when leaf springs are used as the plurality of spring members, the spring constant can be easily made constant by adjusting the spring thickness, spring width, number of folds, etc. of the leaf spring. It is possible to adjust. By making the amounts of spring compression of the plurality of spring members substantially the same, the spring loads of the plurality of spring members can be easily made substantially the same.

(Embodiment 5)
FIG. 10 is an enlarged longitudinal sectional view of the vicinity of the annular seal member before assembly of the scroll compressor according to the present embodiment.

Since the basic configuration of this embodiment is the same as that of Embodiments 1 to 4, description thereof is omitted. Further, the same reference numerals are assigned to the same configurations as those already described, and the description thereof is partially omitted.

In this embodiment, the spring constants ka, kb and kc of the plurality of spring members 211a, 211b and 211c are different from each other. Also, the natural lengths 211h of the plurality of spring members 211a, 211b, 211c are substantially the same.

According to this configuration, even if the spring constants ka, kb, kc of the plurality of spring members 211a, 211b, 211c are different from each other, the natural lengths 211h of the plurality of spring members 211a, 211b, 211c are substantially the same, and By adjusting the respective depths 133ah, 133bh, 133ch of the plurality of storage grooves 133a, 133b, 133c in the main bearing 130, the contraction amount x of the plurality of spring members 211a, 211b, 211c can be adjusted. Therefore, by adjusting the housing groove 133 of the main bearing 130 by machining, the spring loads F of the plurality of spring members 211a, 211b, and 211c can be easily made substantially the same.

Specifically, the natural length 211h of the plurality of spring members 211a, 211b, and 211c is desirably within ±30%. Since the depths 133ah, 133bh, and 133ch of the storage grooves can be processed with high accuracy, the spring loads of the plurality of spring members 211a, 211b, and 211c can be adjusted by adjusting the depths 133ah, 133bh, and 133ch of the storage grooves. F can be approximately the same as each other.

As described above, the scroll compressor of the present embodiment is configured such that the spring constants of the plurality of spring members are different from each other and the natural lengths of the plurality of spring members are substantially the same.

As a result, even if the spring constants of the plurality of spring members are different, by making the natural lengths of the plurality of spring members the same and adjusting the depths of the plurality of storage grooves in the main bearing, the contraction of the plurality of spring members can be minimized. Amount can be adjusted. Therefore, it is possible to easily make the spring loads of the plurality of spring members approximately equal to each other by processing the storage grooves.

(Embodiment 6)
FIG. 11 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembly of the scroll compressor according to the present embodiment.

Since the basic configuration of this embodiment is the same as that of Embodiments 1 to 4, description thereof is omitted. Further, the same reference numerals are assigned to the same configurations as those already described, and the description thereof is partially omitted.

In this embodiment, the spring constants ka, kb and kc of the plurality of spring members 211a, 211b and 211c are different from each other. The storage grooves 133a, 133b, 133c provided in the main bearing 130 have substantially the same depth 133h.

According to this configuration, even if the spring constants ka, kb, and kc of the plurality of spring members are different, the depths 133h of the plurality of storage grooves 133a, 133b, and 133c provided in the main bearing 130 are substantially the same. Also, by adjusting the respective natural lengths 211ah, 211bh, 211ch of the plurality of spring members 211a, 211b, 211c, the contraction amount x of the plurality of spring members 211a, 211b, 211c can be adjusted. Therefore, the spring loads F of the plurality of spring members 211a, 211b, and 211c can be made substantially equal to each other easily and at low processing costs.

Specifically, the depth 133h (depth 133ah, 133bh, 133ch) of the storage grooves 133a, 133b, 133c provided in the main bearing 130 is preferably within ±5%. As a result, since the processing tolerance of the natural lengths 211h (natural lengths 211ah, 211bh, 211ch) of the spring members 211a, 211b, 211c can be increased, the processing of the springs can be facilitated, and the processing cost can be reduced.

As described above, the scroll compressor of the present embodiment is configured such that the spring constants of the plurality of spring members are different from each other and the depths of the storage grooves provided in the main bearing are substantially the same. there is

As a result, even if the spring constants of the plurality of spring members are different from each other, the depths of the plurality of storage grooves provided in the main bearing are set to be the same, and the natural lengths of the plurality of spring members are adjusted. The contraction amount of the spring member can be adjusted. Therefore, the spring loads of the plurality of spring members can be made substantially equal to each other easily and at a lower processing cost.

It should be noted that each of the above-described embodiments and modifications are intended to illustrate the technology of the present disclosure, and various modifications, replacements, additions, and omissions may be made within the scope of the claims or equivalents thereof. can.

The scroll compressor according to the present disclosure can prevent reduction in efficiency and reliability by pressing the orbiting scroll against the fixed scroll with an appropriate force even in a closed-vessel low-pressure compressor. Therefore, it is useful for scroll compressors of refrigerating cycle devices used in electric appliances such as water heaters, hot water heaters and air conditioners.

REFERENCE SIGNS LIST 10 compressor 20 airtight container 30 compression mechanism 40 electric motor 41 stator 42 rotor 50 partition plate 51 second discharge port 52 recess 60 high pressure space 70 low pressure space 71, 72 low pressure space (low pressure region)
80 Refrigerant suction pipe 90 Refrigerant discharge pipe 100 Oil reservoir 110 Fixed scroll 110H Discharge space 111 Fixed scroll end plate 112 Fixed spiral wrap 113 First discharge port 114 Bypass port 115 Outer peripheral stepped portion 116 Thrust sliding surface outermost peripheral portion 119 Upper boss portion 120 Orbiting scroll 121 Orbiting scroll end plate 122 Orbiting spiral wrap 123 Lower boss portion 124 Orbiting bearing 125 Discharge counterbore 126 High pressure introduction path 127 Intermediate pressure port 128 Intermediate pressure introduction path 129 High pressure introduction path 130 Main bearing 131 Boss housing portion 132 Bearing portion 133 Annular groove (storage groove)
133a Annular groove (first storage groove)
133b annular groove (second storage groove)
133c Annular groove (third storage groove)
133h depth 133ah depth (first storage groove)
133bh depth (second storage groove)
133ch depth (third storage groove)
134 return route 140 Oldham ring (rotation suppression member)
150 compression chamber 160 rotating shaft 161 eccentric shaft 162 oil passage 163 suction port 164 first branch oil passage 165 second branch oil passage 166 first oil filler port 167 second oil filler port 168 third oil filler port 170 auxiliary bearing 180 swing bush 190 paddle 200a, 200b balance weight 210 sealing member (annular sealing member)
210a sealing member (first sealing member)
210b sealing member (second sealing member)
210c sealing member (third sealing member)
211 spring member 211a spring member (first spring member)
211b spring member (second spring member)
211c spring member (third spring member)
211h Natural length 211ah Natural length (first spring member)
211bh natural length (second spring member)
211ch natural length (third spring member)
220 pressure chamber 221 high pressure chamber 222 intermediate pressure chamber 230 bypass check valve 240 bypass check valve stop 250 discharge check valve 260 discharge check valve stop 270 boss seal member

Claims (8)

a closed container;
a partition plate that divides the inside of the sealed container into a high-pressure space and a low-pressure space;
a fixed scroll arranged adjacent to the partition plate;
an orbiting scroll meshing with the fixed scroll to form a plurality of compression chambers;
a rotation suppression member that prevents rotation of the orbiting scroll;
a main bearing that supports the orbiting scroll;
a rotating shaft that rotates by being driven by an electric motor and causes the orbiting scroll to orbit by the rotation suppressing member;
has
The main bearing includes a boss accommodating portion provided substantially in the center of an upper surface, and a bearing portion provided below the boss accommodating portion,
The boss accommodating portion accommodates a lower boss portion of the orbiting scroll,
The main bearing is a scroll compressor that supports the orbiting scroll on the upper surface and supports the rotating shaft on the bearing portion ,
The fixed scroll, the orbiting scroll, the rotation suppressing member, and the main bearing are arranged in the low pressure space,
The fixed scroll and the orbiting scroll are arranged between the partition plate and the main bearing,
The rotation suppressing member is arranged between the orbiting scroll and the fixed scroll,
An oil passage is formed inside the rotary shaft, the lower end of which opens into the oil reservoir and the upper end of which opens into the boss accommodating portion,
A return path is formed in the main bearing, one end of which is open to the boss accommodating portion and the other end of which is open to the lower surface of the main bearing,
The outermost peripheral portion on the back surface of the orbiting scroll and the boss accommodation portion are defined as a low pressure region,
forming a plurality of annular grooves on the upper surface outside the boss accommodation portion of the main bearing;
A pressure chamber is formed between the seal members by inserting a seal member into the annular groove,
further dividing the pressure chamber into a high pressure chamber and an intermediate pressure chamber by the seal member;
disposing the high-pressure chamber closer to the center than the intermediate-pressure chamber;
the compression chamber at the center of the orbiting scroll and the high pressure chamber are communicated with each other through a high pressure introduction path formed in an end plate of the orbiting scroll;
The compression chamber in the intermediate portion of the orbiting scroll and the intermediate pressure chamber are communicated with each other by an intermediate pressure introduction path formed in the end plate of the orbiting scroll.
scroll compressor. A discharge space in which the working medium is discharged from the fixed scroll and the high pressure chamber are intermittently communicated,
The scroll compressor according to claim 1 . The intermediate pressure chamber and the high pressure chamber are arranged on the rear surface of the orbiting scroll inside the outermost peripheral portion of the thrust sliding surface between the orbiting scroll and the fixed scroll,
The scroll compressor according to claim 1 or 2 . A first storage groove, a second storage groove, and a third storage groove are formed as the annular groove ,
As the seal members, a first seal member stored in the first storage groove, a second seal member stored in the second storage groove, and a third seal stored in the third storage groove a member ;
A first spring member is arranged on the back surface of the first seal member,
A second spring member is arranged on the back surface of the second seal member,
A third spring member is arranged on the back surface of the third sealing member,
The scroll compressor according to any one of claims 1 to 3 . The spring load of the first spring member, the spring load of the second spring member, and the spring load of the third spring member are the same during assembly.
The scroll compressor according to claim 4 . The spring constant of the first spring member, the spring constant of the second spring member, and the spring constant of the third spring member are the same.
The scroll compressor according to claim 4 or 5 . The spring constant of the first spring member, the spring constant of the second spring member, and the spring constant of the third spring member are different from each other, and the natural length of the first spring member and the natural length of the second spring member and the natural length of the third spring member are the same,
The scroll compressor according to claim 4 or 5 . The spring constant of the first spring member, the spring constant of the second spring member, and the spring constant of the third spring member are different from each other, and the depth of the first storage groove and the depth of the second storage groove are different from each other. is the same as the depth of the third storage groove,
The scroll compressor according to claim 4 or 5 .

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