JP7223929B2 - scroll compressor - Google Patents

Description

The present disclosure relates to scroll compressors.

Patent Literature 1 discloses a scroll compressor. This scroll compressor is of the high pressure type in a closed vessel. As shown in FIG. 9, the back surface of the orbiting scroll 6 is provided with an oil chamber, which is a pressure region equivalent to the high pressure in the closed container, and a back pressure chamber 14, which applies intermediate pressure during compression. . As a result, the orbiting scroll 6 is properly pressed against the fixed scroll 3 even if the operating conditions change, so that the orbiting scroll does not separate from the fixed scroll, thereby avoiding deterioration in performance due to leakage.

JP-A-60-69280

The present disclosure provides a scroll compressor that can prevent the orbiting scroll from separating from the fixed scroll even in a closed container low-pressure type scroll compressor, thereby suppressing deterioration in performance due to pressure leakage from the compression chamber.

A scroll compressor according to the present disclosure includes a closed container, a partition plate that divides the inside of the closed container into a high-pressure space and a low-pressure space, a compression mechanism disposed in the low-pressure space, and an electric motor that drives the compression mechanism. have. The compression mechanism has a fixed scroll, an orbiting scroll that meshes with the fixed scroll to form a compression chamber, and an Oldham ring that prevents rotation of the orbiting scroll. The Oldham ring is arranged between the fixed scroll and the orbiting scroll.

1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1. FIG. 2 is a cross-sectional view of a main part of the scroll compressor according to Embodiment 1. FIG. 3 is a top perspective view of the orbiting scroll of the scroll compressor according to Embodiment 1. FIG. 4 is a cross-sectional view of the orbiting scroll of the scroll compressor according to Embodiment 1. FIG. 5 is a bottom view of the fixed scroll of the scroll compressor according to Embodiment 1. FIG. 6 is a cross-sectional view of a fixed scroll of the scroll compressor according to Embodiment 1. FIG. 7 is a top view of an Oldham ring of the scroll compressor according to Embodiment 1. FIG. 8 is a cross-sectional view of the main part of the scroll compressor according to Embodiment 1. FIG. FIG. 9 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, scroll compressors, in addition to the high-pressure scroll compressor in a closed container shown in Patent Document 1, had a high-pressure region and a low-pressure region in the closed container. There was a closed container low pressure type scroll compressor in which a compression mechanism and an electric motor were provided in a partitioned low pressure area. In this hermetically sealed container low-pressure type scroll compressor, a low-pressure region in which an eccentric bearing is arranged is formed at the center of the back surface of the orbiting scroll. Therefore, if the Oldham's ring is arranged on the back side of the orbiting scroll, it is not possible to secure the necessary area for the pressure application area on the back side of the orbiting scroll. As a result, the orbiting scroll is separated from the fixed scroll due to insufficient force for pressing the orbiting scroll against the fixed scroll, which causes pressure leakage from the compression chamber, resulting in a problem of performance deterioration. The inventors have come to constitute the subject matter of the present disclosure in order to solve such problems.

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 8. FIG.

[1-1. composition]
FIG. 1 is a vertical cross-sectional view of a scroll compressor according to an embodiment of the present disclosure, and FIG. 2 is a cross-sectional view of essential parts of the scroll compressor.

1 and 2, the compressor 10 has a cylindrical sealed container 20 whose longitudinal direction is the vertical direction as an outer shell. 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 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 (see FIGS. 5 and 6 described later). .

The orbiting scroll 120 includes a disc-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 (see the figure below). 3 and FIG. 4). 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 (described later) side and the outer wall surface (described later) 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 .

A first branch oil passage 164 and a second branch oil passage 165 are formed inside the rotating 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 .

A plurality of annular grooves 133 (see FIG. 2) 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 space 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 pressure higher than that of the low-pressure space 70 is introduced into this space to form a pressure-applying region 220 .

In this embodiment, the pressure application area 220 is further partitioned into a high pressure application area 221 and an intermediate pressure application area 222 by a seal member 210 . A pressure equivalent to the discharge gas is introduced into the high pressure applying region 221 . The pressure of the gas during compression is introduced into the intermediate pressure applying region 222 . As a result, the optimum pressing force can be set under various operating conditions with different compression pressures.

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.

FIG. 3 is a top perspective view of the orbiting scroll of the scroll compressor according to the present embodiment. FIG. 4 is a longitudinal sectional view of the orbiting scroll.

The orbiting spiral wrap 122 is a wall having an involute curvilinear cross-section, starting from a starting end 122a located on the center side of the orbiting scroll end plate 121 and gradually expanding in radius toward a terminal end 122b located on the outer peripheral side. be. 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 discharge port at substantially the center of the orbiting scroll 120 . As shown in FIG. 4 , 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 applying region 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 applying region 222 (see FIG. 2).

As shown in FIG. 3, on the Oldham ring 140 side of the orbiting scroll end plate 121, a pair of parallel second key grooves 129 are provided.

FIG. 5 is a bottom view of the fixed scroll of the scroll compressor according to this embodiment. FIG. 6 is a cross-sectional view of the fixed scroll.

As shown in FIGS. 5 and 6, the fixed spiral wrap 112 starts winding at a starting end 112a located on the center side of the fixed scroll end plate 111 and gradually expands in radius toward a terminal end 112c located on the outer peripheral side. , walls with involute curvilinear cross-sections. 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).

The stationary spiral wrap 112 has an inner wall surface (center wall surface) and an outer wall surface (peripheral wall surface) from the starting end 112a to the intermediate portion 112b. Only the inner wall surface is provided from the intermediate portion 112b to the terminal end 112c.

A first discharge port 113 is formed at substantially the center of the fixed scroll end plate 111 . 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 ports 114 include a set of bypass ports 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 of port sets are provided.

An outer peripheral stepped portion 115 having a step with respect to the tip of the fixed spiral wrap 112 is formed on the outer peripheral portion of the fixed scroll 110 . 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 .

As shown in FIG. 5, the outer peripheral portion of the fixed scroll 110 is provided with a pair of parallel first key grooves 116 that are not on a straight line.

A peripheral wall 117 of the fixed scroll 110 is formed with a suction portion 118 for taking refrigerant into the compression chamber 150 .

As shown in FIG. 6, 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 110H is formed between the upper boss portion 119 and the partition plate 50 on the upper surface side of the upper boss portion 119 (see FIG. 1). The first discharge port 113 and the bypass port 114 communicate with the discharge space 110H.

A bypass check valve 230 for freely 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 (Fig. 1). By using a reed valve for the bypass check valve 230, the size in the height direction can be made compact.

FIG. 7 is a top view of the Oldham ring of the scroll compressor according to this embodiment.

Oldham ring 140 is arranged between fixed scroll 110 and orbiting scroll 120 . In the present embodiment, Oldham's ring 140 is arranged on outer peripheral stepped portion 115 (see FIG. 6) of fixed scroll 110 .

The Oldham ring 140 includes a substantially annular ring portion 141, a pair of first keys 142 protruding from the upper surface of the ring portion 141, and a pair of second keys 143 protruding from the lower surface of the ring portion 141. . The first keys 142 are arranged on parallel straight lines that are not aligned. The second keys 143 are also arranged on parallel straight lines that are not aligned. The straight line on which the first key 142 is arranged and the straight line on which the second key 143 is arranged are provided so as to be orthogonal.

The first key 142 engages the first keyway 116 of the fixed scroll 110 and the second key 143 engages the second keyway 129 of the orbiting scroll 120 . This allows the orbiting scroll 120 to orbit without rotating with respect to the fixed scroll 110 .

FIG. 8 is a cross-sectional view of the essential parts 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 seal member 270 seals between the discharge space 110H and the low-pressure space 70 .

[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 suction portion 118 of fixed scroll 110 . The refrigerant sucked into compression chamber 150 is compressed as the volume of compression chamber 150 decreases.

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

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

Here, an Oldham ring 140 is disposed between the fixed scroll 110 and the orbiting scroll 120 in the present disclosure. Therefore, the intermediate pressure application area 222 and the high pressure application area 221 provided on the back surface of the orbiting scroll 120 can be configured widely. Therefore, the area of the pressure applying region 220 necessary for properly pressing the orbiting scroll 120 against the fixed scroll 110 is ensured. As a result, even in the closed container low-pressure compressor, it is possible to prevent the pressure from leaking due to the separation of the orbiting scroll 120 from the fixed scroll 110, thereby preventing a decrease in efficiency.

In addition, the stationary scroll 110 of the compressor 10 of the present embodiment is formed with an outer peripheral stepped portion 115 , and the Oldham ring 140 is arranged on the outer peripheral stepped portion 115 . Therefore, the thrust area between the tip of the stationary spiral wrap 112 and the orbiting scroll end plate 121 can be reduced to reduce the sliding loss. Moreover, since the thickness of the orbiting scroll end plate 121 can be ensured, the rigidity of the orbiting scroll 120 can be ensured.

Furthermore, since the outer peripheral stepped portion 115 communicates with the suction portion 118 , the suctioned refrigerant exists in the outer peripheral stepped portion 115 . Therefore, the Oldham ring 140 is lubricated with the oil contained in the sucked refrigerant.

Also, as shown in FIG. 7, the first key 142 and the second key 143 are not arranged on the same straight line. Therefore, the first key groove 116 of the fixed scroll 110 and the second key groove 129 of the orbiting scroll 120 can be formed without increasing the outer diameters of the fixed scroll 110 and orbiting scroll 120 . Therefore, it is possible to avoid an increase in the outer diameter of the closed container 20 .

[1-3. effects, etc.]
As described above, in the scroll compressor according to the present embodiment, the Oldham ring for preventing rotation of the orbiting scroll, which is meshed with the fixed scroll to form the compression chamber, is arranged between the fixed scroll and the orbiting scroll. . Therefore, no space is required for arranging the Oldham's ring on the back of the orbiting scroll. Therefore, a large area can be secured on the back surface of the orbiting scroll as a pressure application area necessary for properly pressing the orbiting scroll against the fixed scroll. Therefore, even in a closed-vessel low-pressure compressor in which the inside of the closed vessel is divided into a high-pressure space and a low-pressure space by a partition plate, pressure leakage can be suppressed by preventing the orbiting scroll from separating from the fixed scroll. , can prevent the efficiency of the compressor from decreasing.

The Oldham's ring is arranged in a low pressure area communicating with the low pressure space. Therefore, since the Oldham ring is lubricated with the oil contained in the sucked refrigerant, the reliability of the sliding portion can be improved.

The pressure application area may be formed by a high pressure area or an intermediate pressure area or both. The pressure of the discharged gas is introduced into the high-pressure region, and the pressure of the gas being compressed is introduced into the intermediate-pressure region. Therefore, it is possible to set the pressing force of the orbiting scroll to an optimum pressing force under various operating conditions with different compression pressures. Therefore, it is possible to more efficiently reduce pressure leakage loss due to separation of the orbiting scroll from the fixed scroll and sliding loss due to excessive pressing of the orbiting scroll against the fixed scroll.

The fixed scroll is configured such that the outer peripheral portion of the fixed scroll is stepped down from the wrap tip end of the fixed scroll by at least the thickness of the Oldham ring. As a result, the thrust area between the fixed scroll and the orbiting scroll can be reduced to reduce the thrust sliding loss. In addition, the rigidity of the orbiting scroll can be ensured by ensuring the thickness of the end plate (end plate) of the orbiting scroll.

A pair of parallel first grooves that are not aligned are formed on the Oldham ring side of the fixed scroll. A pair of parallel second grooves that are not aligned are formed on the Oldham ring side of the orbiting scroll. A first key portion slidably fitted in the first groove is provided on the fixed scroll side of the Oldham ring, and a first key portion slidably fitted in the second groove is provided on the orbiting scroll side of the Oldham ring. A mating second key portion is provided. The sliding direction of the first key portion and the sliding direction of the second key portion are configured to be perpendicular to each other. As a result, the grooves can be formed without increasing the outer diameters of the fixed scroll and the orbiting scroll, thereby avoiding the need to increase the outer diameter of the sealed container.

Note that the above-described embodiment is for illustrating the technology in the present disclosure, and various changes, replacements, additions, omissions, etc. can be made within the scope of the claims or equivalents thereof.

As described above, the scroll compressor according to the present disclosure can be applied to a closed-vessel low-pressure scroll compressor in which the inside of the closed vessel is divided into a high-pressure space and a low-pressure space by a partition plate. 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 Closed 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 80 Refrigerant suction pipe 90 Refrigerant discharge pipe 100 Oil pool 110 Fixed scroll 110H Discharge space 111 Fixed scroll end plate 112 Fixed spiral wrap 112a Starting end 112b Intermediate portion 112c Terminating end 113 First discharge port 114 Bypass port 115 Outer peripheral stepped portion 116 First keyway 117 Peripheral wall 118 Suction portion 119 Upper boss portion 120 Orbiting scroll 121 Orbiting scroll end plate 122 Orbiting spiral wrap 122a Start end 122b Termination point 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 Second key groove 130 Main bearing 131 Boss accommodating portion 132 Bearing portion 133 Annular groove 134 Return path 140 Oldham ring 141 Ring portion 142 First key 143 Second key 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 supply Port 167 Second oil inlet 168 Third oil inlet 170 Auxiliary bearing 180 Swing bush 190 Paddle 200a, 200b Balance weight 210 Seal member 220 Pressure application area 221 High pressure application area 222 Intermediate pressure application area 230 Bypass check valve 240 Bypass check valve Stop 250 Discharge check valve 260 Discharge check valve stop 270 Seal member

Claims (5)

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 compression mechanism disposed in the low-pressure space and an electric motor driving the compression mechanism;
A scroll compressor comprising:
The compression mechanism section is
a fixed scroll arranged adjacent to the partition plate;
an orbiting scroll meshing with the fixed scroll to form a compression chamber;
an Oldham ring that prevents rotation of the orbiting scroll;
a main bearing that supports the orbiting scroll,
A pressure applying region having a pressure higher than the pressure of the low pressure space is arranged on the back surface of the orbiting scroll,
The orbiting scroll is pressed against the fixed scroll by the pressure in the pressure applying region,
The Oldham ring is arranged between the fixed scroll and the orbiting scroll ,
A portion of the pressure applying region exists below the Oldham ring.
scroll compressor. The Oldham ring is arranged in a low pressure area communicating with the low pressure space,
A scroll compressor according to claim 1. The pressure applying region is formed by at least one of a high pressure applying region and a medium pressure applying region having a lower pressure than the high pressure applying region,
The pressure of the discharge gas is introduced into the high pressure applying region, and the pressure of the gas in the process of being compressed is introduced into the intermediate pressure applying region.
The scroll compressor according to claim 1 or 2. The outer peripheral portion of the fixed scroll is stepped down from the wrap tip end of the fixed scroll by a thickness of the Oldham ring or more.
The scroll compressor according to any one of claims 1-3. A pair of parallel first grooves that are not on a straight line are arranged on the Oldham ring side of the fixed scroll,
A pair of parallel second grooves that are not aligned are arranged on the Oldham ring side of the orbiting scroll,
A pair of first key portions slidably fitted into the pair of first grooves are arranged on the fixed scroll side of the Oldham ring,
A pair of second key portions slidably fitted into the pair of second grooves are arranged on the orbiting scroll side of the Oldham ring,
The scroll compressor according to any one of claims 1 to 4, wherein the sliding direction of the pair of first key portions and the sliding direction of the pair of second key portions are orthogonal.

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