CN114635855A

CN114635855A - Scroll compressor having a plurality of scroll members

Info

Publication number: CN114635855A
Application number: CN202011477466.2A
Authority: CN
Inventors: 郭伟平
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2020-12-15
Filing date: 2020-12-15
Publication date: 2022-06-17

Abstract

The present invention relates to a scroll compressor (100) comprising: a housing (110) defining a low pressure region (LR) within the housing at a suction pressure; a Compression Mechanism (CM) disposed within the housing (110) and including a non-orbiting scroll (150) and an orbiting scroll, the non-orbiting scroll (150) including a non-orbiting scroll end plate (154), an exhaust port (159) formed in the non-orbiting scroll end plate, a spiral non-orbiting scroll blade (156) formed at one side of the non-orbiting scroll end plate, and a high pressure space (DC) at an exhaust pressure formed at the other side of the non-orbiting scroll end plate in communication with the exhaust port; and a seal assembly (S100) comprising a first seal portion (S140) configured to abut against the non-orbiting scroll to isolate the high pressure space from the low pressure region. The invention provides a scroll compressor which does not provide a back pressure cavity, enables the space of a gas exhaust structure to be maximized and realizes unilateral sealing.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to scroll compressors and, more particularly, to scroll compressors having improvements in sealing and discharge configurations.

Background

Scroll compressors typically include a compression mechanism consisting of a fixed scroll and a movable scroll, which may be of a floating fixed scroll design, for example, by virtue of locating holes and bolt fit clearance configurations with a housing or main bearing housing for supporting the fixed scroll to provide axial and radial flexibility to the fixed scroll, thereby providing unloading possibilities for flooded starts and accommodating machining tolerances.

Further, in order to isolate the high and low pressure sides of the scroll compressor and to accommodate axial floating of the non-orbiting scroll, a floating seal is provided which is disposed within and cooperates with an annular recess of the non-orbiting scroll to form a back pressure chamber, the annular recess (i.e., the back pressure chamber) being communicable with an intermediate compression chamber (commonly referred to as an intermediate pressure chamber) of the scroll compression structure, and thus, the floating seal floats under the pressure in the fluid of the back pressure chamber. The diaphragm separates the interior space of the scroll compressor into a high pressure side and a low pressure side, and the upper surface of the floating seal contacts and creates a contact pressure with the lower surface of the diaphragm or a diaphragm seal attachment (e.g., a collar), creating a face seal effect to isolate the high pressure side from the low pressure side. Further, lip seals are provided on the inner and outer sides of the floating seal, respectively, to seal in contact with the radially inner and outer annular walls of the annular recess (back pressure chamber), respectively, thereby isolating the back pressure chamber from the low pressure side and the back pressure chamber from the high pressure side.

In the above configuration, on the one hand, the area of the annular recess of the non-orbiting scroll (between the radially inner and outer side walls of the annular recess) needs to be large enough to thereby float the seal assembly disposed within the annular recess to a pressure large enough to contact the diaphragm or the seal attachment of the diaphragm to satisfy the axial seal pressure, and on the other hand, the area of the high pressure chamber inside the radially inner side wall of the annular recess (the discharge chamber in fluid communication with the discharge port of the compression mechanism) is set small to reduce the axial load. However, this configuration results in the exhaust component disposed in the radially inner side wall being limited to a small area, reducing the degree of freedom in designing the exhaust component (the exhaust port and the exhaust valve) and failing to meet the demand for a wider range of compression ratios (particularly low compression ratios).

Disclosure of Invention

An object of the present invention is to provide a scroll compressor capable of achieving one-side sealing by eliminating a back pressure chamber by abutting a sealing portion of a seal assembly against a non-orbiting scroll to isolate a high pressure space from a low pressure region so that a discharge construction space is maximized.

It is another object of the present invention to reduce contact wear by securing or integrally forming a seal assembly with a bulkhead or a seal attachment of a bulkhead instead of abutting contact seals so that the drawback of failing to start due to the inability of the seal assembly to float upward in time is eliminated.

The present invention provides a scroll compressor, comprising: a housing defining a low pressure region within the housing at a suction pressure; the compression mechanism is arranged in the shell and comprises a fixed scroll and a movable scroll, wherein the fixed scroll comprises a fixed scroll end plate, an exhaust port formed in the fixed scroll end plate, a spiral fixed scroll blade formed on one side of the fixed scroll end plate and a high-pressure space which is formed on the other side of the fixed scroll end plate and communicated with the exhaust port and is positioned at the exhaust pressure; and a seal assembly including a first seal portion configured to abut against the non-orbiting scroll to isolate the high pressure space from the low pressure region.

Advantageously, the scroll compressor includes a partition dividing an interior space within the housing into a first region and a second region, the first region including the low pressure region and housing the compression mechanism, the second region receiving compressed high pressure working fluid from the high pressure space, the partition being provided with an aperture, and the seal assembly including a second seal for isolating the high pressure space from the low pressure region, the second seal being configured to abut against the partition or an attachment attached to the aperture of the partition.

Advantageously, the sealing assembly comprises a top plate and a bottom plate, the first sealing portion comprises a connection portion interposed between the top plate and the bottom plate and a lip portion abutting against the non-orbiting scroll, and the second sealing portion is formed at the top plate.

Advantageously, the scroll compressor further comprises an activation spring adapted to urge the seal assembly towards the partition plate.

Advantageously, the scroll compressor includes a partition dividing an interior space within the housing into a first region and a second region, the first region including the low pressure region and housing the compression mechanism, the second region receiving compressed high pressure working fluid from the high pressure space, the partition being provided with an aperture at which an attachment is attached, and the seal assembly including a top plate secured to or integral with the attachment.

Advantageously, the sealing assembly comprises a bottom plate attached to the top plate, and the first sealing portion comprises a connection portion interposed between the top plate and the bottom plate and a lip portion abutting against the non-orbiting scroll.

Advantageously, the non-orbiting scroll includes a hub portion partially defining the high pressure space, and the first seal portion abuts a radially inner side wall of the hub portion, or the first seal portion abuts a radially outer side wall of the hub portion.

Advantageously, the non-orbiting scroll includes a non-orbiting scroll body including the non-orbiting scroll end plate and a non-orbiting scroll cover plate attached to the non-orbiting scroll end plate, the hub being formed at the non-orbiting scroll cover plate.

Advantageously, the first seal portion abuts a radially outer side wall of the hub portion, the seal assembly comprises an extension extending radially inwardly beyond a radially inner side wall of the hub portion, and preferably the second seal portion is formed at the extension.

Advantageously, a variable volume ratio valve is provided in the high pressure space.

The present invention provides an improved sealing and venting design compared to prior scroll compressors: 1) the sealing part of the sealing assembly is abutted to the fixed scroll to isolate a high-pressure space from a low-pressure area, and under the condition that the fixed scroll is allowed to axially float, a back pressure cavity is eliminated, so that the space for an exhaust structure is maximized, the design freedom of exhaust hole arrangement and an exhaust valve assembly is improved, the high energy efficiency of the scroll compressor and a system applying the scroll compressor is kept in a wider operation range, the sealing structure is simplified, and the structure of the fixed scroll is further simplified; single-side (radial) sealing can be realized by eliminating a back pressure cavity, so that the number of sealing elements is reduced; a start-up resilient member is added to ensure seal assembly tip (axial) sealing at compressor start-up transient to prevent high pressure side fluid leakage to low pressure side at start-up transient. 2) The seal assembly is disposed on the hub portion of the cover plate such that the size of the seal assembly is reduced. 3) The seal assembly is fixed or integrated with the diaphragm or a seal attachment of the diaphragm to replace the (axial) abutting contact seal, eliminating the need for a starting elastic member, so that there are no prior art drawbacks such as inability to float up in time due to the seal assembly (e.g., PTFE seal is not prone to sticking at low temperatures, or low suction pressure and low intermediate or back pressure cavity pressure at low ambient temperatures) leading to conduction of the high and low pressure sides and failure to function, while there is no wear due to the end face contact seal of the seal assembly (e.g., minor misalignment under fluid pulsations), reducing part count and cost.

Drawings

The features and advantages of the present invention will be more readily understood from the following detailed description of the specific embodiments that is provided with reference to the accompanying drawings. In the drawings, wherein like features or components are designated with like reference numerals throughout the several views and are not necessarily drawn to scale, and wherein:

FIG. 1 is a schematic cross-sectional view of a scroll compressor including a seal assembly and a non-orbiting scroll according to one aspect of an embodiment of the present invention.

FIG. 2 is an enlarged schematic cross-sectional view of the seal assembly and non-orbiting scroll of the scroll compressor of FIG. 1.

FIG. 3 is an exploded perspective view of the seal assembly and non-orbiting scroll of the scroll compressor of FIG. 1.

FIG. 4 is a schematic cross-sectional view of a scroll compressor including a seal assembly disposed on a hub of a cover plate of a non-orbiting scroll in accordance with another aspect of an embodiment of the present invention.

FIG. 5 is an exploded perspective view of the seal assembly and non-orbiting scroll of the scroll compressor of FIG. 4.

FIG. 6 is a schematic cross-sectional view of a scroll compressor including a seal assembly according to yet another aspect of an embodiment of the present invention.

FIG. 7 is a variation of the scroll compressor of FIG. 4 including a seal assembly with the attachment of the top plate and the partition integrally formed.

FIG. 8 is a variation of the scroll compressor of FIG. 1 including a seal assembly with the attachment of the top plate and the partition integrally formed.

FIG. 9 is a schematic cross-sectional view of a related art scroll compressor including a seal assembly and a non-orbiting scroll disposed within an annular recess.

FIG. 10 is an enlarged schematic cross-sectional view of the seal assembly configuration and non-orbiting scroll of the scroll compressor of FIG. 9.

Detailed Description

The following description of various embodiments of the invention is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly.

First, the general configuration and operation principle of the scroll compressor will be described with reference to fig. 9 and 10. A scroll compressor (hereinafter sometimes also referred to as a compressor) generally includes a housing 110. The casing 110 may include a substantially cylindrical body 111, a top cover 112 disposed at one end of the body 111, a bottom cover 114 disposed at the other end of the body 111, and a partition plate 116 disposed between the top cover 112 and the body 111 to partition an inner space of the compressor into a high pressure side and a low pressure side. The space between the partition 116 and the top cover 112 constitutes a high pressure side, and the space between the partition 116, the body 111 and the bottom cover 114 constitutes a low pressure side. An intake joint (not shown) for sucking fluid is provided at a low pressure side, and an exhaust joint 119 for discharging compressed fluid is provided at a high pressure side. A motor 120 including a stator 122 and a rotor 124 is provided in the housing 110. A drive shaft 130 is provided in the rotor 124 to drive a compression mechanism constituted by a fixed scroll 150 and an orbiting scroll 160. Orbiting scroll 160 includes an end plate 164, a hub 162 formed at one side of the end plate, and a spiral vane 166 formed at the other side of the end plate. Non-orbiting scroll 150 includes an end plate 154, a helical vane 156 formed on one side of the end plate, and an annular recess 158 formed on the other side of the end plate, the annular recess including a radially outer side wall and a radially inner side wall. An exhaust port 159 is formed at a substantially central position of the end plate. The space around the exhaust port 159 also constitutes the high pressure side. A series of compression chambers C1, C2, and C3, the volumes of which gradually decrease from the radially outer side to the radially inner side, are formed between the spiral vane 156 of the non-orbiting scroll 150 and the spiral vane 166 of the orbiting scroll 160. The radially outermost compression pocket C1 is at suction pressure and the radially innermost compression pocket C3 is at discharge pressure. The intermediate compression chamber C2 is between the suction pressure and the discharge pressure and is also referred to as an intermediate pressure chamber.

One side of orbiting scroll 160 is supported by an upper portion (i.e., a supporting portion) of main bearing housing 140, and one end of drive shaft 130 is supported by a main bearing provided in main bearing housing 140. One end of drive shaft 130 is provided with eccentric crank pin 132 and a relief bushing is provided between eccentric crank pin 132 and hub 162 of orbiting scroll 160. Orbiting scroll 160 will be rotated in translation relative to non-orbiting scroll 150 (i.e., the central axis of orbiting scroll 160 rotates about the central axis of non-orbiting scroll 150, but orbiting scroll 160 does not itself rotate about its central axis) by the actuation of motor 120 to effect compression of the fluid. The translational rotation is realized by an oldham ring arranged between the fixed scroll 150 and the movable scroll 160. The fluid compressed by the fixed scroll 150 and the orbiting scroll 160 is discharged to a high pressure side through the discharge port 159.

To prevent the high pressure side fluid from flowing back to the low pressure side through the discharge port 159 under certain conditions, a check or discharge valve 190, which may be a variable volume ratio valve, may be provided at the discharge port 159, for example, to allow early discharge of some low compression ratio conditions where the discharge pressure to suction pressure ratio is low, so as to avoid power loss due to over-compression of the refrigerant, so that the scroll compressor remains energy efficient over a wider operating range.

The non-orbiting scroll 150 is provided with a positioning hole 151, and the main bearing housing 140 is provided with a bolt 141 for passing through the positioning hole 151, the positioning hole 151 and the bolt 141 being configured to form an axial gap and a radial gap therebetween, so that axial flexibility and radial flexibility are provided to the non-orbiting scroll (with respect to the main bearing housing).

Typically, a seal assembly S is disposed in the annular recess 158 of the non-orbiting scroll 150. That is, the seal assembly S is disposed between the partition 116 and the non-orbiting scroll 150. Annular recess 158 is in fluid communication with one of the series of compression pockets C1, C2, C3 via a through-hole 155 (also referred to as an intermediate pressure passage) formed in non-orbiting scroll end plate 154. Preferably, the annular recess 158 is in fluid communication with the intermediate compression chamber C2 via the through hole 155. Seal assembly S thus cooperates with annular recess 158 to form a back pressure chamber BC that provides back pressure to orbiting scroll 150. The axial displacement of the seal assembly S is limited by the spacer 116. When the pressure in each compression chamber exceeds the set value, the resultant force of the pressures in these compression chambers will exceed the lower pressure provided in back pressure chamber BC to cause fixed scroll 150 to move upward. At this time, the fluid in the compression chamber will leak to the low pressure side through the gap between the tip of the spiral vane 156 of the non-orbiting scroll 150 and the end plate 164 of the orbiting scroll 160 and the gap between the tip of the spiral vane 166 of the orbiting scroll 160 and the end plate 154 of the non-orbiting scroll 150 to achieve unloading, thereby providing axial flexibility to the scroll compressor. Thus, the seal assembly axially floats under the action of the compression chamber fluid from the intermediate pressure passage to accommodate the axial float of the non-orbiting scroll.

The construction and function of the seal assembly S will be described in more detail below. As shown in fig. 10, the sealing assembly S may include an upper plate S1, a lower plate S2, and first and third seals S3 and S5 disposed between the upper and lower plates S1 and S2. The shape of seal assembly S substantially corresponds to the shape of annular recess 158 (back pressure chamber BC), such that first seal S3 may seal against a radially inner sidewall of annular recess 158, and third seal S5 may seal against a radially outer sidewall of annular recess 158. In addition, the upper end of the upper plate S1 may seal against the partition 116 or a collar 117 provided on the partition 116.

The seal assembly S achieves sealing in the compressor in the following manner: 1) the upper end of the upper plate S1 abuts against the collar 117 on the partition 116 to effect separation of the high and low pressure sides; 2) the first seal S3 abuts the radially inner side wall of the annular recess 158 to effect separation of the high pressure side from the back pressure chamber BC; 3) the third seal S5 abuts the radially outer sidewall of the annular recess 158 to effect separation of the back pressure chamber BC from the low pressure side.

The above-described back pressure chamber for the floating seal requires an annular recess to be provided on the top plate of the non-orbiting scroll, and a back pressure chamber is formed between the radially inner side wall and the radially outer side wall of the annular recess. According to this back pressure chamber configuration, on the one hand, the area of the annular recess (back pressure chamber) needs to be large enough to ensure sufficient axial sealing pressure between the upper end of the seal assembly (upper plate) and the diaphragm or the collar of the diaphragm; on the other hand, the area of the high pressure chamber (exhaust chamber) inside the radially inner side wall is generally set small to reduce the axial load. However, for example, the discharge holes are usually arranged in a plurality of discharge holes arranged in the radial direction to be suitable for a plurality of compression ratios, while considering the arrangement of the discharge valve assembly cooperating with the discharge holes, which requires a large space, and therefore, the arrangement of the prior art may result in that the discharge valve assembly and the discharge holes arranged in the radially inner side wall are limited to a small area, reducing the design freedom of the discharge assembly, failing to meet the requirements of a wider range of compression ratios (particularly low compression ratios), and particularly resulting in a compressor being energy inefficient under low compression ratio conditions.

In view of the above, the present invention provides a compressor having an improved seal assembly and discharge configuration, and is described with reference to fig. 1 to 8.

Referring to fig. 1-3, and in conjunction with fig. 9-10, a scroll compressor 100 includes: a housing 110 defining a low pressure region LR at suction pressure therein; a compression mechanism CM disposed inside the casing 110 and including a fixed scroll 150 and an orbiting scroll, the fixed scroll 150 including a fixed scroll end plate 154, an exhaust port 159 formed in the fixed scroll end plate, a spiral fixed scroll blade 156 formed at one side of the fixed scroll end plate, and a high pressure space DC at an exhaust pressure formed at the other side of the fixed scroll end plate in communication with the exhaust port; and a seal assembly S100, which may include a first seal portion S140 configured to abut against the non-orbiting scroll to isolate the high pressure space from the low pressure region. A check valve or an exhaust valve, which may be a variable volume ratio valve 190, is provided in the high-pressure space DC.

By virtue of the above, in the case where the fixed scroll is allowed to axially float and the sealing between the high pressure side and the low pressure side is satisfied, the back pressure chamber is eliminated, so that the high pressure space for the exhaust structure is maximized, thereby improving the freedom of design of the exhaust hole arrangement and the exhaust valve assembly. In particular, the plenum may expand radially outward, allowing the variable volume ratio discharge valve, and thus the variable volume ratio orifice, to be disposed radially outward, which enables the scroll compressor, and systems employing the scroll compressor, to remain energy efficient over a wider operating range. In addition, single-side (radial) sealing can be realized by eliminating a back pressure cavity, the number of sealing pieces is reduced, and the fixed scroll is not required to be provided with an inner hub and an outer hub, so that the structure of the sealing assembly is simplified, and the structure of the fixed scroll is further simplified.

Specifically, the scroll compressor may include a partition 116 that divides the interior space within the housing into a first region, which may include the low pressure region LR and house the compression mechanism, and a second region that receives compressed high pressure working fluid from the high pressure space DC. The sealing assembly S100 may comprise a second sealing portion S142 adapted to abut against an attachment piece S120 attached to the partition 116 in an operational state, although the second sealing portion may also be configured to abut against the partition. The sealing assembly S100 may include a top plate S110 and a bottom plate S130, as illustrated, the first sealing portion S140 may advantageously include a connection portion (not shown) interposed between the top plate and the bottom plate and a lip portion abutting against the non-orbiting scroll and the second sealing portion S142 is formed at the top plate S110. The lip portion may be implemented as a flexible sealing lip which allows a certain flexibility of the non-orbiting scroll in the axial and radial directions for adjusting space for compensating manufacturing errors and for unloading of liquid-carrying conditions and the like, and the double plate structure allows the first sealing portion to be reliably and conveniently fixed. Of course, the person skilled in the art may conceive of other ways to realize the sealing between the first sealing portion and the non-orbiting scroll, for example, an annular sealing ring is disposed between the first sealing portion and the non-orbiting scroll.

In order to ensure the sealing assembly tip (axial) sealing at the compressor starting moment, a starting elastic component can be arranged to prevent the high-pressure side fluid from leaking to the low-pressure side at the starting moment, so that the compressor can be started normally. In the drawings, the scroll compressor also includes an activation spring S150 adapted to urge the seal assembly S100 toward the separator plate 116. In one aspect of an embodiment, the activation spring S150 may urge the top plate S110 and the bottom plate S130 of the seal assembly S100 toward the partition 116.

The partition 116 is provided with an orifice at which an attachment S120 is attached, which is an interference fit with the orifice and may serve as a sound-deadening seal that silences exhaust gas. Advantageously, as shown in fig. 7 and 8, the top plate S110 of the sealing assembly S100 is fixed to or integral with the attachment. Of course, the top plate may also be fixed to the attachment. The seal assembly is fixed or integrated with the diaphragm or an attachment of the diaphragm to replace (axial) abutting contact sealing (particularly metal-to-metal abutting contact sealing), and an elastic starting component is eliminated, so that the defects of the prior art that the high-pressure side and the low-pressure side are communicated and cannot work due to the fact that the seal assembly cannot float upwards in time under low-temperature working conditions (for example, a PTFE seal cannot be deformed and clamped at low temperature, or low suction pressure and low medium pressure cavity pressure under low ambient temperature) do not exist, meanwhile, the abrasion caused by the end face contact sealing (for example, micro-dislocation under the action of fluid pulsation) of the seal assembly does not exist, the number of parts is reduced, and the cost is reduced.

As shown, the non-orbiting scroll may include a hub portion 181 partially defining the high pressure space DC, and the first sealing portion S140 may abut against a radially inner side wall of the hub portion 181 (as shown in fig. 2 and 8), or the first sealing portion S140 may abut against a radially outer side wall of the hub portion 181 (as shown in fig. 6). The first sealing part S140 may be provided as a single sealing part to simplify the structure of the sealing assembly.

In another aspect of an embodiment, non-orbiting scroll 150 may include a non-orbiting scroll body, which may include a non-orbiting scroll end plate 154, and a non-orbiting scroll cover plate 170 attached to the non-orbiting scroll end plate 154, with a hub 171 formed at the non-orbiting scroll cover plate 170. In a split non-orbiting scroll, by means of a non-orbiting scroll cover plate, a seal assembly is allowed to be attached to the non-orbiting scroll cover plate without being attached to a non-orbiting scroll body, thereby allowing a high pressure space having a larger volume to be formed between the non-orbiting scroll body and the non-orbiting scroll cover plate, which is more suitable for mounting various valves. And, the seal assembly is disposed on the hub portion of the cap plate, so that the size of the seal assembly can be reduced, reducing costs.

Advantageously, with reference to fig. 6, where the seal assembly S100 may include a single first seal portion abutting a radially outer sidewall of the hub 181, the single first seal portion in fig. 6 being disposed on the hub 181 of the non-orbiting scroll (in the absence of a cover plate), the seal assembly S100 may include an extension S141 extending radially inward beyond the radially outer sidewall of the hub 181, in other words, an inner diameter dimension D1 of the extension is less than an outer diameter dimension D2 of the hub 181. More preferably, the extension portion S141 may extend beyond the radially inner sidewall of the hub portion 181. Similarly, in FIG. 4, where a single first seal is disposed on the hub portion 171 of the cover plate 170, the seal assembly S100 may also include an extension S141 that extends radially inward beyond the radially outer sidewall of the hub portion 171, i.e., an inner diameter dimension D3 of the extension is less than an outer diameter dimension D4 of the hub portion 171. More preferably, the extension portion S141 may extend beyond a radially inner sidewall of the hub portion 171. The extension allows a high pressure compression portion to be formed thereunder to push the seal assembly upward with high pressure in a high pressure region during operation of the compressor. Further, a second sealing part S142 may be formed at the extension part S141.

Although preferred embodiments of the present invention have been described in detail herein, it is to be understood that this invention is not limited to the precise construction herein shown and described and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such modifications and variations are within the scope of the invention as hereinafter claimed.

Claims

1. A scroll compressor (100) comprising:

a housing (110) defining a low pressure region (LR) within the housing at a suction pressure;

a Compression Mechanism (CM) disposed within the housing (110) and including a non-orbiting scroll (150) and an orbiting scroll, the non-orbiting scroll (150) including a non-orbiting scroll end plate (154), an exhaust port (159) formed in the non-orbiting scroll end plate, a spiral non-orbiting scroll blade (156) formed at one side of the non-orbiting scroll end plate, and a high pressure space (DC) at an exhaust pressure formed at the other side of the non-orbiting scroll end plate in communication with the exhaust port; and

a sealing assembly (S100) is provided,

characterized in that the sealing assembly comprises a first sealing portion (S140) configured to abut against the non-orbiting scroll to isolate the high pressure space from the low pressure region.

2. The scroll compressor (100) of claim 1, wherein:

the scroll compressor includes a partition plate (116) that partitions an inner space within the shell into a first region that includes the low pressure region (LR) and accommodates the compression mechanism and a second region that receives a compressed high pressure working fluid from the high pressure space (DC),

the partition (116) is provided with an orifice, an

The sealing assembly (S100) comprises a second sealing portion (S142) for isolating the high pressure space from the low pressure region, the second sealing portion being configured to abut against the partition or an attachment (S120) attached to the orifice of the partition.

3. The scroll compressor (100) of claim 2, wherein:

the sealing assembly (S100) includes a top plate (S110) and a bottom plate (S130),

the first sealing part (S140) includes a connection part interposed between the top plate and the bottom plate and a lip part abutting on the non-orbiting scroll, an

The second sealing portion (S142) is formed at the top plate (S110).

4. The scroll compressor (100) of claim 1, wherein the scroll compressor includes a start spring (S150) adapted to urge the seal assembly (S100) toward the separator plate (116).

5. The scroll compressor (100) of claim 1, wherein:

the partition (116) is provided with a bore at which an attachment (S120) is attached, and

the sealing assembly (S100) comprises a top plate (S110) fixed to or integral with the attachment.

6. The scroll compressor (100) of claim 5, wherein:

the sealing assembly (S100) comprises a bottom plate (S130) attached to the top plate, an

The first sealing portion (S140) includes a connection portion interposed between the top plate (S110) and the bottom plate (S130) and a lip portion abutting against the non-orbiting scroll.

7. The scroll compressor (100) of any of claims 1-6, wherein:

the non-orbiting scroll (150) includes a hub (181, 171) partially defining the high pressure space (DC), and

the first seal portion abuts against a radially inner side wall of the hub portion, or the first seal portion abuts against a radially outer side wall of the hub portion.

8. The scroll compressor (100) of claim 7, wherein the non-orbiting scroll (150) includes a non-orbiting scroll body including the non-orbiting scroll end plate (154) and a non-orbiting scroll cover plate (170), the non-orbiting scroll cover plate (170) being attached to the non-orbiting scroll end plate (154), the hub portion (171) being formed at the non-orbiting scroll cover plate (170).

9. The scroll compressor (100) of claim 2, wherein the non-orbiting scroll (150) includes a hub portion (181, 171) partially defining the high pressure space (DC), the first seal portion abutting a radially outer side wall of the hub portion, the seal assembly (S100) including an extension portion (S141) extending radially inward beyond a radially inner side wall of the hub portion, the second seal portion (S142) being formed at the extension portion (S141).

10. A scroll compressor (100) according to any of claims 1 to 6, wherein a variable volume ratio valve (190) is provided in the high pressure space (DC).