JP7262010B2 - scroll compressor - Google Patents

Description

The present invention relates to scroll compressors.

Patent Literature 1 discloses a closed-vessel low-pressure type scroll compressor. This scroll compressor, as shown in FIG. is pressed against the fixed scroll 304 to prevent the orbiting scroll 301 from separating from the fixed scroll 304, thereby suppressing deterioration in performance.

Japanese Patent No. 5601404

The present disclosure provides a scroll compressor in which performance and reliability are improved while suppressing cost increases by pressing the orbiting scroll against the fixed scroll just enough.

In the scroll compressor of the present disclosure, the end plate of the orbiting scroll is provided with a back pressure introduction path that communicates the wrap bottom surface and the back surface of the orbiting scroll, and the back pressure port inlet is provided on the back pressure introduction path on the side of the wrap bottom surface of the orbiting scroll. , a back pressure port outlet is provided on the back side of the orbiting scroll, and the back pressure port inlet is a compression chamber (A compression chamber) where the pressure becomes the discharge pressure and a compression chamber (B compression chamber) where the pressure is during compression. When the back pressure port inlet opens to the A compression chamber, the back pressure port outlet opens to the high pressure application region, and the back pressure port inlet opens to the B compression chamber. The back pressure port outlet is configured to open to the intermediate pressure applying region when the pressure is on, and the pressure of the compression chambers having different pressures is introduced into the two back pressure chambers through one pressure introducing path.

The scroll compressor of the present disclosure, even in a closed container low-pressure compressor, presses the orbiting scroll appropriately against the fixed scroll while suppressing costs, suppresses deterioration in performance due to an increase in sliding loss, and has high performance and high reliability. You can provide a sex scroll compressor.

Longitudinal sectional view of the scroll compressor in Embodiment 1 Principal part sectional drawing of the scroll compressor in Embodiment 1 FIG. 2 is a bottom view showing the fixed scroll of the scroll compressor according to Embodiment 1; FIG. 2 is a top perspective view showing the orbiting scroll of the scroll compressor according to Embodiment 1. FIG. Sectional view showing the orbiting scroll of the scroll compressor in Embodiment 1 Sectional view showing the main bearing of the scroll compressor in Embodiment 1 FIG. 2 is a correlation diagram of the fixed scroll and the orbiting scroll when the back pressure port inlet opens to the compression chamber A and the back pressure port outlet opens to the high pressure application region in the scroll compressor according to the first embodiment. Longitudinal cross section of FIG. 6A FIG. 2 is a correlation diagram of the fixed scroll and the orbiting scroll when the back pressure port inlet opens to the B compression chamber and the back pressure port outlet opens to the intermediate pressure applying region in the scroll compressor according to the first embodiment. Longitudinal sectional view of FIG. 7A Longitudinal cross-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 (Fig. 8), the closed container low pressure type scroll compressor reduced the pressure in the compression chamber 302 in one section during compression. The pressure is introduced into the back pressure chamber 303, and the orbiting scroll 301 is pressed against the fixed scroll 304 by that pressure. As a result, depending on the operating conditions, the force that presses the orbiting scroll 301 against the fixed scroll 304 becomes excessive, resulting in an increase in sliding loss, which causes performance deterioration and reliability deterioration. In order to make the force for pressing the orbiting scroll 301 against the fixed scroll 304 appropriate regardless of operating conditions, a plurality of back pressure chambers are provided, and the pressure of a separate compression chamber is introduced into each of the back pressure chambers. However, in this case, there is a problem that two routes for introducing pressure are required, which increases the cost.

As described above, conventional scroll compressors have problems in terms of performance, reliability, and cost. rice field.

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 7B.

[1-1. composition]
FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention.

FIG. 2 is a cross-sectional view of the main parts of the scroll compressor.

1 and 2, the compressor 10 has a cylindrical sealed container 20 having a vertical longitudinal direction as an outer shell. In this specification, the vertical direction is the Z-axis direction in each drawing.

The compressor 10 is a closed scroll compressor that includes 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 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 after being compressed by the compression mechanism 30, and the low-pressure space 70 is a space filled with low-pressure refrigerant before being compressed by the compression mechanism 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 . Compressor 10 introduces a low-pressure refrigerant into low-pressure space 70 from a refrigeration cycle circuit (not shown) provided outside sealed container 20 via refrigerant suction pipe 80 . Also, the high-pressure refrigerant compressed by the compression mechanism section 30 is first introduced into the high-pressure space 60 . Thereafter, 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 .

Fixed scroll 110 , orbiting scroll 120 , and Oldham's 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 arranged below and adjacent to the partition plate 50 and fastened to the main bearing 130 with bolts or the like.

The orbiting scroll 120 is provided below the fixed scroll 110 so as to engage with the fixed scroll 110 and move axially between the fixed scroll 110 and the main bearing 130 .

The Oldham's ring 140 is provided between the fixed scroll 110 and the orbiting scroll 120 to prevent the orbiting scroll 120 from rotating and making an orbiting motion.

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 . A first discharge port 113 is formed at substantially the center of the fixed scroll end plate 111 , and a suction portion 115 for taking refrigerant into the compression chamber 150 is formed in the peripheral wall 114 .

An upper boss portion 116 is provided in the center of the upper surface (the surface on the partition plate 50 side) of the fixed scroll 110 . The upper boss portion 116 is a cylindrical protrusion that protrudes from the upper surface of the fixed scroll 110 . The first discharge port 113 opens on the upper surface of the upper boss portion 116 . A discharge space 110</b>H is formed between the upper surface side of the upper boss portion 116 and the partition plate 50 . The first discharge port 113 communicates with the discharge space 110H.

A second discharge port 51 is provided in the center of the partition plate 50 . A discharge check valve 160 for freely opening and closing the second discharge port 51 and a discharge check valve stop 170 for preventing excessive deformation of the discharge check valve 160 are provided on the upper surface of the partition plate 50 .

The discharge space 110</b>H communicates with the compression chamber 150 through the first discharge port 113 and communicates with the high pressure space 60 through the second discharge port 51 .

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 . The upper boss portion 116 of the fixed scroll 110 is inserted into the concave portion 52 and is sealed with the low pressure space 70 by the seal member 180 to form the discharge space 110H.

The orbiting scroll 120, as shown in FIG. I have. The lower boss portion 123 is a cylindrical protrusion formed substantially in the center of the lower surface 121 b 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 (described later) side and the outer wall (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 accommodation portion 131 is a recess for accommodating the lower boss portion 123 . The bearing portion 132 is a through hole whose upper end opens at the boss housing portion 131 and whose lower end opens into the low-pressure space 70 .

The main bearing 130 supports the orbiting scroll 120 on its upper surface and supports the rotating shaft 190 with the bearing portion 132 .

The rotating shaft 190 is a shaft having a longitudinal direction in the vertical direction. One end side of the rotating shaft 190 is supported by the bearing portion 132 , and the other end side is supported by the auxiliary bearing 200 . The secondary bearing 200 is a bearing provided below the low pressure space 70 , preferably within the oil sump 100 . An eccentric shaft 191 eccentric to the axis of the rotating shaft 190 is provided at the upper end of the rotating shaft 190 . The eccentric shaft 191 is slidably inserted into the lower boss portion 123 via the swing bush 210 and the turning bearing 124 . The lower boss portion 123 is pivotally driven by an eccentric shaft 191 .

An oil passage 192 through which lubricating oil passes is formed inside the rotary shaft 190 . The oil passage 192 is a through hole formed in the axial direction of the rotating shaft 190 . One end of the oil passage 192 opens into the oil reservoir 100 as a suction port 193 provided at the lower end of the rotary shaft 190 . A paddle 220 for pumping lubricating oil from the suction port 193 to the oil passage 192 is provided above the suction port 193 .

A first branched oil passage 194 and a second branched oil passage 195 are formed inside the rotating shaft 190 . One end of the first branch oil passage 194 opens as a first oil supply port 196 at the bearing surface of the bearing portion 132 , and the other end communicates with the oil passage 192 . One end of the second branch oil passage 195 opens as a second oil supply port 197 at the bearing surface of the sub bearing 200 , and the other end communicates with the oil passage 192 .

Furthermore, the upper end of the oil passage 192 opens inside the boss accommodation portion 131 as a third oil filler port 198 . 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 .

The rotating shaft 190 is connected to the electric motor 40 . Electric motor 40 is arranged between main bearing 130 and sub-bearing 200 . 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 190 is fixed to the rotor 42 . The rotating shaft 190 has a balance weight 230a provided above the rotor 42 and a balance weight 230b provided below the rotor 42 . The balance weight 230a and the balance weight 230b are arranged at positions shifted by 180° in the circumferential direction of the rotating shaft 190. As shown in FIG.

The rotating shaft 190 rotates with a balance between the centrifugal force generated by the balance weights 230 a and 230 b and the centrifugal force generated by the orbital motion of the orbiting scroll 120 . Note that the balance weights 230 a and 230 b may be provided on the rotor 42 .

A detailed configuration of the compressor 10 will be further described.

FIG. 3 is a bottom view of the fixed scroll of the scroll compressor according to this embodiment.

As shown in FIG. 3, the fixed spiral wrap 112 has an involute curve that starts from 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. It is a wall with a shaped cross section. The stationary spiral wrap 112 has a predetermined height (vertical length) and a predetermined wall thickness (radial length of the stationary spiral wrap 112).

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

FIG. 4A is a top perspective view of the orbiting scroll of the scroll compressor according to this embodiment, and FIG. 4B is a sectional view of the orbiting scroll.

As shown in FIGS. 4A and 4B, the orbiting spiral wrap 122 starts winding at a starting end 122a located on the center side of the orbiting scroll end plate 121 and gradually expands in radius toward a terminal end 122b located on the outer peripheral side. , walls with involute curvilinear cross-sections. The orbiting spiral wrap 122 has a predetermined height (length in the vertical direction) and a predetermined wall thickness (length in the radial direction of the orbiting spiral wrap 122) equal to those of the fixed spiral wrap 112 .

In the orbiting scroll end plate 121, a back pressure introduction path 125 is formed radially straight from the end plate outer peripheral surface 121a toward the center of the orbiting scroll end plate 121, and the end plate outer peripheral surface 121a side is blocked by a plug 126. It's leaking. A back pressure port entrance 127 is formed in the wrap bottom surface of the orbiting scroll 120 and communicates with the back pressure introducing path 125 . A back pressure port outlet 128 is formed in the lower surface 121 b of the orbiting scroll end plate 121 and communicates with the back pressure introducing path 125 .

The back pressure port inlet 127 alternately opens into a compression chamber (A compression chamber) communicating with the first discharge port 113 on the outer wall side and a compression chamber (B compression chamber) on the inner wall side during compression along with the turning movement. do.

FIG. 5 is a cross-sectional view of the main bearing of the scroll compressor according to this embodiment.

Three annular grooves 133a (outer), 133b (middle), and 133c (inner) are formed on the surface supporting the orbiting scroll 120 on the outside of the boss accommodating portion 131 of the main bearing 130. , 133c, seal members 240a (outer), 240b (middle), and 240c (inner) are inserted as shown in FIG. The sealing members 240a (outer), 240b (middle), and 240c (inner) form a space by contacting the lower surface 121b of the orbiting scroll 120, and a pressure higher than that of the low-pressure space 70 is introduced into this space to apply pressure. A region 250 is formed.

The pressure application area 250 is partitioned into a high pressure application area 251 and an intermediate pressure application area 252 by a seal member 240b. (See Figure 2)
FIG. 6A is a correlation diagram of the fixed scroll and orbiting scroll when the back pressure port inlet 127 opens to the A compression chamber and the back pressure port outlet 128 opens to the high pressure application region 251, and FIG. 6B is a vertical sectional view at that time. is.

7A is a correlation diagram of the fixed scroll and orbiting scroll when the back pressure port inlet 127 opens to the B compression chamber and the back pressure port outlet 128 opens to the intermediate pressure applying region 252, and FIG. It is a longitudinal cross-sectional view.

[1-2. motion]
The operation and effect of the compressor 10 configured as described above will be described below.

When the electric motor 40 is driven, the rotary shaft 190 rotates together with the rotor 42 . As the rotary shaft 190 rotates, the eccentric shaft 191 and the Oldham ring 140 prevent the orbiting scroll 120 from rotating on its own axis and rotate the central axis of the rotary shaft 190 . The refrigerant that revolves around the center and is introduced into the low-pressure space 70 through the refrigerant suction pipe 80 cools the electric motor 40 and is sucked into the compression chamber 150 from the suction portion 115 of the fixed scroll 110, whereby the volume of the compression chamber 150 is reduced. , and the refrigerant in the compression chamber 150 is compressed.

The intermediate pressure refrigerant during compression passes through the back pressure introduction path 125 in the section where the back pressure port inlet 127 opens to the B compression chamber, and is introduced into the intermediate pressure imparting region 252 provided on the lower surface 121b of the orbiting scroll 120. be done. At this time, the pressure in the B compression chamber changes as compression progresses in the open section. Along with this, the pressure in the intermediate pressure applying region 252 also fluctuates. After opening the B compression chamber, the back pressure port inlet 127 is temporarily blocked by the upper surface 112 d of the wrap of the fixed scroll 110 , then opens to the A compression chamber, and the refrigerant at the discharge pressure is introduced into the high pressure applying region 251 .

The orbiting scroll 120 is pressed against the fixed scroll 110 by the pressure applied to the intermediate pressure applying region 252 and the high pressure applying region 251 of the lower surface 121b of the orbiting scroll 120 in this manner. At this time, the pressure applied to the intermediate pressure applying region 252 can be adjusted by adjusting the compression chamber to which the back pressure port inlet 127 opens. Further, by adjusting the areas of the high pressure applying region 251 and the intermediate pressure applying region 252, the force for pressing the orbiting scroll 120 against the fixed scroll 110 can be adjusted. can be set to press against the fixed scroll 110, and it is possible to suppress sliding loss and deterioration of reliability due to excessive pressing force.

Here, by making the time that the back pressure port inlet 127 opens to the A compression chamber longer than the time that it opens to the B compression chamber, the section that opens to the B compression chamber is shortened, and the B compression chamber changes in that section. is suppressed, and the pressure fluctuation in the intermediate pressure application region 252 to which the pressure is introduced can be reduced, so that the orbiting scroll 120 can be pressed against the fixed scroll 110 with a stable force.

In addition, since the back pressure introduction path 125 is formed on a radial straight line, the back pressure port inlet 127 and the back pressure port outlet 128 communicating therewith are also positioned on substantially the same radial straight line. Therefore, when the center of the involute curve forming the orbiting spiral wrap 122 of the orbiting scroll 120 is substantially the same as the center of the orbiting scroll end plate 121, the timing at which the back pressure port inlet 127 opens to the A compression chamber and the back pressure port outlet 128 are opened to the high pressure application region 251 at substantially the same timing. Similarly, the timing at which the back pressure port inlet 127 opens to the B compression chamber and the timing at which the back pressure port outlet 128 opens to the intermediate pressure application region 252 are substantially the same. Therefore, communication between the A compression chamber and the intermediate pressure applying region 252 and communication between the B compression chamber and the high pressure applying region 251 can be prevented.

Further, by making the diameter of the back pressure port inlet 127 smaller than the wrap thickness of the fixed scroll 110, the back pressure port inlet 127 does not open to the A compression chamber and the B compression chamber at the same time. Leakage into the room can be prevented. Similarly, by making the diameter of the back pressure port outlet 128 smaller than the seal width of the seal member 240b, the back pressure port outlet 128 does not open to the high pressure applying region 251 and the medium pressure applying region 252 at the same time. Therefore, leakage from the high pressure applying region 251 to the medium pressure applying region 252 can be prevented.

Further, by setting the diameter of the back pressure introduction path 125 to half or less of the thickness of the orbiting scroll end plate 121, the rigidity of the orbiting scroll end plate 121 can be secured, and deformation of the orbiting scroll 120 can be suppressed.

In addition, by forming the back pressure introduction path 125 with a straight hole that communicates the back pressure port inlet 127 and the back pressure port outlet 128, the number of processing steps can be reduced, and the stopcock 126 is not required, thereby reducing costs. can.

[1-3. effects, etc.]
As described above, in the present embodiment, the scroll compressor is provided with the back pressure introduction path 125 that communicates the wrap bottom surface and the back surface of the orbiting scroll 120 in the end plate of the orbiting scroll 120, and the back pressure introduction path 125 A back pressure port inlet 127 is provided on the wrap bottom side of the orbiting scroll 120, and a back pressure port outlet 128 is provided on the rear side of the orbiting scroll 120. The back pressure port inlet 127 is a compression chamber (A compression chamber) where the pressure becomes the discharge pressure. chamber) and a compression chamber (B compression chamber) where the pressure is in the middle of compression, and when the back pressure port inlet 127 is open to the A compression chamber, the back pressure port outlet 128 applies high pressure. When the back pressure port inlet 127 opens to the B compression chamber, the back pressure port outlet 128 opens to the intermediate pressure application region 252, thereby introducing one back pressure. Pressure can be applied to high pressure application area 251 and intermediate pressure application area 252 in path 125 . Therefore, it is possible to properly press the orbiting scroll 120 against the fixed scroll 110 without increasing the cost and regardless of the operating conditions, thereby preventing deterioration in performance and reliability due to an increase in sliding loss. can.

Further, by setting the time for the back pressure port inlet 127 to open to the A compression chamber longer than the time for the back pressure port inlet 127 to open to the B compression chamber, the back pressure port inlet 127 opens to the B compression chamber. Since the amount of pressure change in the B compression chamber that changes while it is open to the chamber is suppressed, the pressure fluctuation in the intermediate pressure applying region 252 is suppressed, and the orbiting scroll 120 is moved to the fixed scroll 110 with a stable pressure. can be pushed.

In addition, since the back pressure port inlet 127 and the back pressure port outlet 128 are positioned on substantially the same radial straight line of the end plate of the orbiting scroll 120, the back pressure port inlet 127 and the back pressure port outlet 128 can be made substantially the same.

In addition, by setting the wrap thickness of the fixed scroll 110 substantially equal to the seal width of the seal member 180 that separates the high pressure applying region 251 and the intermediate pressure applying region 252, the back pressure port inlet 127 can be The timing at which the back pressure port outlet 128 is closed by the seal member 180 can be substantially synchronized with the timing at which the back pressure port outlet 128 is closed by the wrap.

Further, the diameter of the back pressure port inlet 127 is smaller than the wrap thickness of the fixed scroll 110, and the diameter of the back pressure port outlet 128 is smaller than the seal width of the seal member 180, so that the back pressure port inlet 127 can be Since the A compression chamber and the B compression chamber are not opened at the same time, and the back pressure port outlet 128 is not opened at the high pressure application region 251 and the intermediate pressure application region 252 at the same time, the back pressure is reduced. can be properly controlled.

Further, by setting the diameter of the back pressure introduction path 125 to approximately half or less of the thickness of the end plate of the orbiting scroll 120, the rigidity of the end plate can be maintained. can be secured.

In addition, since the back pressure introduction path 125 is formed by a straight hole that communicates the back pressure port inlet 127 and the back pressure port outlet 128, the number of processing steps can be reduced and the cost can be reduced.

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, in the scroll compressor according to the present disclosure, even in a closed vessel low-pressure compressor, by pressing the orbiting scroll against the fixed scroll with an appropriate force, performance deterioration and reliability due to an increase in sliding loss can be improved. Since deterioration can be prevented, it is useful for scroll compressors of refrigeration 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 Terminal end 112d Upper surface 113 First discharge port 114 Peripheral wall 115 Suction portion 116 Upper boss portion 120 Orbiting scroll 121 Orbiting scroll end plate 121a End plate outer peripheral surface 121b Lower surface 122 Orbiting spiral wrap 122a starting end 122b terminal end 123 lower boss portion 124 swivel bearing 125 back pressure introducing path 126 stopcock 127 back pressure port inlet 128 back pressure port outlet 130 main bearing 131 boss accommodating portion 132 bearing portion 133a, 133b, 133c annular groove 134 return path 140 Oldham ring 150 compression chamber 160 discharge check valve 170 discharge check valve stop 180 seal member 190 rotating shaft 191 eccentric shaft 192 oil passage 193 suction port 194 first branch oil passage 195 second branch oil passage 196 first oil filler port 197 2nd oil supply port 198 3rd oil supply port 200 auxiliary bearing 210 swing bush 220 paddle 230a, 230b balance weight 240a, 240b, 240c sealing member 250 pressure application area 251 high pressure application area 252 intermediate pressure application area

Claims (7)

A high-pressure space and a low-pressure space are partitioned in the sealed container by a partition plate, a compression mechanism and an electric motor for driving the compression mechanism are arranged in the low-pressure space, and the compression mechanism is adjacent to the partition plate. A fixed scroll, an orbiting scroll that meshes with the fixed scroll to form a compression chamber, an Oldham ring that prevents rotation of the orbiting scroll, and a main bearing that supports the orbiting scroll, the back surface of the orbiting scroll In a scroll compressor having a configuration in which a pressure applying region that applies a pressure higher than the low pressure in the low pressure space in the closed container is provided in the closed container, and the pressure is used to press the orbiting scroll against the fixed scroll, the pressure applying region is provided with a seal member to provide a discharge pressure and an intermediate pressure applying region for applying pressure in the middle of compression. A back pressure port inlet and a back pressure port outlet are provided on the back side of the orbiting scroll, and the back pressure port inlet is a compression chamber (compression chamber A) in which the pressure becomes the discharge pressure. and alternately open to the compression chamber (B compression chamber) whose pressure is in the middle of compression, and when the back pressure port inlet opens to the A compression chamber, the back pressure port outlet opens to the high pressure application region. and a scroll compressor in which the back pressure port outlet opens to the intermediate pressure applying region when the back pressure port inlet opens to the B compression chamber. 2. A scroll compressor according to claim 1, wherein the time during which said back pressure port inlet opens to said A compression chamber is longer than the time during which said back pressure port inlet opens to said B compression chamber. 3. The scroll compressor according to claim 1, wherein the back pressure port inlet and the back pressure port outlet are arranged substantially on a straight line with the same radius of the end plate of the orbiting scroll. 4. A scroll compressor according to claim 3, wherein the wrap thickness of said fixed scroll and the seal width of said seal member are substantially the same. The scroll compressor according to any one of claims 1 to 4, wherein the diameter of the back pressure port inlet is smaller than the wrap thickness of the fixed scroll, and the diameter of the back pressure port outlet is smaller than the seal width of the seal member. The scroll compressor according to any one of claims 1 to 5, wherein the diameter of the back pressure introduction path is set to be substantially half or less of the thickness of the end plate of the orbiting scroll. The scroll compressor according to any one of claims 1 to 6, wherein the back pressure introducing path is formed by a straight hole communicating between the back pressure port inlet and the back pressure port outlet.

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