CN217813919U - Scroll compressor having a plurality of scroll members - Google Patents

Abstract

The utility model relates to a scroll compressor, include: the compression mechanism comprises a fixed scroll and an orbiting scroll, the fixed scroll and the orbiting scroll are matched to form a series of compression cavities for compressing working fluid, and the fixed scroll comprises a fluid channel; and a floating seal disposed at one side of the non-orbiting scroll to define a back pressure chamber therebetween, the back pressure chamber communicating with an intermediate pressure compression chamber among the compression chambers via a fluid passage such that the floating seal is axially floatable by compression chamber fluid from the intermediate pressure compression chamber, a gas flow reversing structure disposed between the fluid passage and the floating seal, the gas flow reversing structure configured to adjust a direction of compression chamber fluid discharged from the fluid passage. The utility model provides a improve in the aspect of the floating seal in order to realize reliably sealed scroll compressor.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to scroll compressors and, more particularly, to a scroll compressor having improvements in floating seal construction.

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 an annular recess of the non-orbiting scroll and cooperates therewith 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 compression chamber) of the scroll compression structure, and thus, the floating seal is floated by the pressure in the fluid in 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.

Normally, after the compressor is started, the back pressure chamber on the non-orbiting scroll introduces fluid, such as an intermediate pressure compression chamber, to urge the floating seal to rise uniformly upward until the upper surface of the floating seal and the lower surface of the diaphragm or diaphragm seal attachment contact and form a face seal to isolate the high pressure side from the low pressure side.

However, in the case of a rapid start of the compressor, for example, the flow rate of the fluid entering the back pressure chamber on the fixed scroll is too fast and instantaneously collides against the lower surface of the floating seal to push the floating seal to ascend, and the floating seal is inclined to be stuck at both sides of the back pressure chamber due to the difference in ascending rate of the portions caused by the uneven force applied to the lower surface thereof, thereby causing the fluid leakage between the high pressure side, the low pressure side and the back pressure chamber to cause the seal failure.

SUMMERY OF THE UTILITY MODEL

It is an object of the present invention to provide a scroll compressor improved in terms of floating seal by providing an air flow reversing structure between a fluid passage allowing a compression chamber fluid to pass and the floating seal to achieve reliable sealing.

The utility model provides a scroll compressor, include: a compression mechanism comprising a non-orbiting scroll and an orbiting scroll cooperating to form a series of compression chambers for compressing a working fluid, the non-orbiting scroll comprising a fluid passage; and a floating seal disposed on one side of the non-orbiting scroll to define a back pressure chamber therebetween, the back pressure chamber communicating with an intermediate pressure compression chamber of the compression chambers via the fluid passage such that the floating seal is axially floatable by compression chamber fluid from the intermediate pressure compression chamber, a gas flow reversing structure disposed between the fluid passage and the floating seal, the gas flow reversing structure configured to adjust a direction of the compression chamber fluid discharged from the fluid passage.

Advantageously, the gas flow reversing arrangement is configured such that the fluid passage remains normally open.

Advantageously, the fluid passage includes an exhaust port in fluid communication with the back pressure chamber, and the gas flow reversing structure includes a baffle disposed spaced from the exhaust port.

Advantageously, the gas flow diverting structure is in the form of a cage and comprises an annular supporting body and a central baffle axially offset with respect to the annular supporting body, the annular supporting body and the central baffle being connected by at least one connecting arm to form a plurality of radial channels between the annular supporting body and the central baffle.

Advantageously, the cage is an integral component formed directly from sheet metal processes.

Advantageously, the retainer further comprises a clamping portion extending from the annular support body, the clamping portion being clamped with a corresponding portion of the non-orbiting scroll to secure the retainer to the non-orbiting scroll.

Advantageously, the non-orbiting scroll further includes an annular recess accommodating the floating seal and defining the back pressure chamber, the discharge port of the fluid passage is disposed at a bottom of the annular recess, a counter bore is disposed around the discharge port at the bottom of the annular recess, the counter bore is configured to be stepped to include a top inner wall surface, a top surface, a bottom surface, and a bottom inner wall surface connecting the top surface and the bottom surface, the holder further includes a first clamping portion and/or a second clamping portion, the first clamping portion radially extends from the annular support body and a radially outer end of the first clamping portion is clamped to the bottom inner wall surface, the second clamping portion radially extends from the annular support body and then axially extends and then radially extends to include an inner radial section, an axial section, and an outer radial section, the axial section is clamped to the bottom inner wall surface, and a radially outer end of the outer radial section is clamped to the top inner wall surface.

Advantageously, the cage is constructed and arranged such that the central baffle is below the outer radial section or below both the outer radial section and the top surface.

Advantageously, the gas flow reversing arrangement is in the form of a bolt and comprises a bolt portion provided with an axial passage and a nut portion provided with a radial passage, such that the compression chamber fluid discharged from the fluid passage is reversed by first entering the axial passage and then entering the radial passage.

Advantageously, the radial passage comprises two mutually intersecting through holes through the nut portion.

Advantageously, the non-orbiting scroll further includes an annular recess accommodating the floating seal and defining the back pressure chamber, the discharge port of the fluid passage is provided at a bottom of the annular recess, a counter bore is provided at the bottom of the annular recess around the discharge port, the counter bore is configured to be stepped so as to include a top inner wall surface, a top surface, a bottom surface, and a bottom inner wall surface connecting the top surface and the bottom surface, and the bolt portion is screwed with the bottom inner wall surface so as to fix the bolt to the non-orbiting scroll.

Advantageously, the non-orbiting scroll further comprises an annular recess housing the floating seal and defining the back pressure chamber, the discharge port of the fluid passage being provided at the bottom of the annular recess, a counterbore being provided at the bottom of the annular recess around the discharge port, the gas flow reversing structure being arranged in the counterbore such that the gas flow reversing structure does not protrude from the counterbore.

Compared with the prior scroll compressor, the utility model provides a modified floating seal design: 1) By providing the gas flow reversing structure between the fluid passage in fluid communication with the intermediate pressure compression chamber and the floating seal, the floating seal is allowed to stably axially float under the influence of the compression chamber fluid regulated by the gas flow reversing structure to achieve reliable sealing even in the case of a rapid start of the compressor. Specifically, the fluid in the compression chamber in the fluid channel in fluid communication with the medium-pressure compression chamber first flows through the air flow reversing structure, and the flow direction of the fluid changes when the fluid flows through the air flow reversing structure, for example, the fluid can change from flowing in an approximate axial direction to flowing in an approximate radial direction, and then the fluid fills the whole back pressure chamber, so that the floating seal ring is uniformly pushed to lift up, and the functions of isolating each chamber and providing downward pressure for the movable and fixed scroll fitting are realized. Therefore, the fluid in the compression cavity after the direction change can not directly impact the floating sealing element any more, so that the phenomenon of sealing failure caused by the inclined clamping of the floating sealing element due to uneven stress is avoided; 2) By means of the airflow reversing structure in the form of the retainer, the airflow reversing structure can also be directly formed into an integral component by utilizing a sheet metal process, so that the process is simple and the cost of accessories is reduced; 3) By means of the airflow reversing structure in the bolt form, the mounting mode is simple, the assembly efficiency is improved, and the cost is reduced. And can also directly utilize current hexagon head bolt to punch and reform transform, further improve parts machining efficiency height and reduce 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 related art scroll compressor including a non-orbiting scroll and a seal assembly disposed in an annular recess of the non-orbiting scroll.

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

Fig. 3 is a schematic perspective view of a non-orbiting scroll of a scroll compressor according to an embodiment of the present invention including an air flow reversing structure in the form of a retainer.

FIG. 4 is a schematic cross-sectional view of the non-orbiting scroll and the cage of the scroll compressor of FIG. 3.

Fig. 5 is a perspective view of a retainer of the scroll compressor of fig. 3.

Fig. 6 is a schematic perspective view of a non-orbiting scroll of a scroll compressor according to another embodiment of the present invention including an air flow reversing structure in the form of a bolt.

FIG. 7 is a schematic cross-sectional view of the non-orbiting scroll and bolt of the scroll compressor of FIG. 6.

Fig. 8 is a perspective view of the bolts of the scroll compressor of fig. 6.

Fig. 9 is a schematic cross-sectional view of the bolt of fig. 6 showing its reversing passage.

Fig. 10 is another schematic cross-sectional view of the bolt of fig. 6 including its reversing channel.

Detailed Description

The following description of the various embodiments of the present 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 in the respective drawings to denote the same components, and thus the configurations of the same components will not be described repeatedly.

The general construction and operating principle of the scroll compressor will be described first with reference to fig. 1 and 2. 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. A vent 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, which have volumes gradually decreasing from a radially outer side to a radially inner side, are formed between spiral vane 156 of non-orbiting scroll 150 and spiral vane 166 of 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 therefore also referred to as the intermediate pressure compression chamber.

One side of orbiting scroll 160 is supported by an upper portion (i.e., a support portion) of main bearing housing 140, and one end of driving shaft 130 is supported by a main bearing provided in main bearing housing 140. One end of the drive shaft 130 is provided with an eccentric crank pin 132 and a relief bushing is provided between the eccentric crank pin 132 and a hub 162 of the 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 provided as a floating seal 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. The 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 a medium pressure fluid passage) formed in the non-orbiting scroll end plate 154. Preferably, the annular recess 158 is in fluid communication with the intermediate pressure 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 the seal assembly S substantially corresponds to the shape of the annular recess 158 (back pressure chamber BC), such that the first seal S3 may seal against a radially inner sidewall of the annular recess 158, and the third seal S5 may seal against a radially outer sidewall of the annular recess 158. Further, the upper end of the upper plate S1 may seal against the spacer 116 or a collar 117 provided on the spacer 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 a collar 117 on the partition 116 to achieve separation of the high pressure side and the low pressure side; 2) The first seal S3 abuts against 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 against the radially outer side wall of the annular recess 158 to effect the separation of the back pressure chamber BC from the low pressure side.

However, in the case of a rapid start of the compressor, for example, the flow rate of the fluid entering the back pressure chamber on the non-orbiting scroll is too fast and instantaneously collides against the lower surface of the floating seal/seal assembly to push the floating seal to ascend, and the floating seal is inclined due to the uneven force applied to the lower surface thereof and the ascending rate of each portion is different, so that the entire sealing structure is stuck to both sides of the back pressure chamber, thereby causing fluid leakage between the high pressure side, the low pressure side and the back pressure chamber and sealing failure.

In view of the above, the present invention provides a compressor having an improved floating seal configuration, and the floating seal configuration will be described with reference to fig. 1 to 10.

One embodiment of the present application is described with reference to fig. 3 to 5, and fig. 3 is a schematic perspective view of a non-orbiting scroll of a scroll compressor including an air flow reversing structure in the form of a retainer according to one embodiment of the present invention. FIG. 4 is a schematic cross-sectional view of the non-orbiting scroll and the cage of the scroll compressor of FIG. 3. Fig. 5 is a perspective view of a retainer of the scroll compressor of fig. 3.

The present invention is directed to providing an airflow reversing structure between a fluid passage of the non-orbiting scroll in communication with the intermediate pressure compression pocket (e.g., through hole 155 provided in non-orbiting scroll end plate 154) and the floating seal or seal assembly, the airflow reversing structure configured to adjust the direction of the compression pocket fluid discharged from the fluid passage, e.g., to adjust the compression pocket fluid to a direction different from the direction toward the floating seal. By means of the airflow reversing structure, even if the compressor is started quickly, the floating sealing piece stably axially floats under the action of the compression cavity fluid regulated by the airflow reversing structure to realize reliable sealing, specifically, the compression cavity fluid in a fluid channel communicated with the medium-pressure compression cavity fluid firstly flows through the airflow reversing structure, the flow direction of the compression cavity fluid changes when flowing through the airflow reversing structure, for example, the flow direction can be changed from the approximately axial direction to the approximately radial direction or to the direction forming an angle with the axial direction, and then the whole back pressure cavity is filled, so that the floating sealing ring is uniformly pushed to lift up, and the functions of isolating each cavity and providing downward pressure for the movable and fixed vortex attachment are realized. Therefore, the fluid in the compression chamber after the direction change does not directly impact the floating sealing element, and the phenomenon that the floating sealing element is inclined and clamped due to uneven stress to cause sealing failure is avoided.

Referring to fig. 5, the gas flow reversing structure may be in the form of a cage 200 and comprises an annular support body 220 and a central baffle 240 axially offset with respect to the annular support body, the annular support body and the central baffle being connected by at least one connecting arm 230 to form a plurality of radial channels 250 between the annular support body and the central baffle.

By means of this cage structure, the generally axially flowing compression chamber fluid from the fluid passage is blocked by the central baffle and thus flows out generally radially (the compression chamber fluid changes from a previous generally axial direction to a generally radial direction) via a plurality of radial passages, e.g. directed to the side wall of the annular recess of the non-orbiting scroll. While the central baffle 240 is shown as being perpendicular to the axial direction such that axially flowing compression chamber fluid exits generally radially from the radial passages 250, in other aspects of the embodiments, the central baffle may be angled with respect to the axial direction so long as the angled central baffle does not directly impinge the floating seal with compression chamber fluid exiting the radial passages.

The airflow reversing structure in the form of the retainer can be directly formed into an integral component by utilizing a sheet metal process, so that the process is simple and the cost of accessories is reduced.

The holder 200 further includes a catching portion extending from the annular support body, the catching portion catching with a corresponding portion of the non-orbiting scroll to fix the holder to the non-orbiting scroll. In an advantageous aspect according to the first embodiment, a counterbore 180 is provided around the discharge port at the bottom of the annular recess 158 (see fig. 4), the counterbore being configured in a stepped shape so as to include a top inner wall surface 181, a top surface 182, a bottom surface 183, and a bottom inner wall surface 184 connecting the top surface and the bottom surface.

Referring to fig. 5, the holder 200 may further include a first clamping portion 222 and a second clamping portion 221, the first clamping portion 222 extends radially from the annular support body 220, and a radially outer end of the first clamping portion is clamped to the bottom inner wall surface 184, the second clamping portion 221 extends radially from the annular support body 220, then extends axially, and then extends radially, so as to include an inner radial section, an axial section, and an outer radial section, the axial section is clamped to the bottom inner wall surface 184, and a radially outer end of the outer radial section is clamped to the top inner wall surface 181. In the drawings, 6 first catching portions 222 and two second catching portions 221 symmetrically arranged are shown which are uniformly provided along the circumferential direction of the annular supporting body 220, however, those skilled in the art may provide the number of catching portions as needed. Also, the cage 200 is constructed and arranged so that the central baffle 240 is below the outer radial section or below both the outer radial section and the top surface.

The structure that the retainer is clamped in the counter bore enables the whole structure of the airflow reversing structure to be flush with the surface of the end plate or below the surface of the end plate, namely, the airflow reversing structure is arranged in the counter bore so that the airflow reversing structure does not protrude from the counter bore, and therefore interference with a floating sealing piece is avoided. Simultaneously, the cooperation of joint portion and counter bore is connected and is made to be connected to the retainer firmly to decide the vortex to the detachable of joint portion and counter bore is connected the cooperation and is also favorable to equipment and maintenance.

Next, another embodiment of the present application will be described with reference to fig. 6 to 10, and fig. 6 is a schematic perspective view of a non-orbiting scroll of a scroll compressor including an air flow reversing structure in the form of a bolt according to another embodiment of the present invention. FIG. 7 is a schematic cross-sectional view of the non-orbiting scroll and bolt of the scroll compressor of FIG. 6. Fig. 8 is a perspective view of the bolts of the scroll compressor of fig. 6. Fig. 9 is a schematic cross-sectional view of the bolt of fig. 6 showing its reversing passage. FIG. 10 is another schematic cross-sectional view of the bolt of FIG. 6 including its reversing channel.

Specifically, referring to fig. 6-10, the gas flow reversing structure may be in the form of a bolt 300 and include a bolt portion 320 provided with an axial passage 321 and a nut portion 340 provided with a radial passage 341 such that compression chamber fluid discharged from the fluid passage 155 is reversed by first entering the axial passage 321 and then entering the radial passage 341. In the ventilation bolt structure shown in the figure, the axial channel is a vertical hole, the radial channel is a transverse through hole, the transverse through hole can be two transverse through holes which penetrate through the nut part and are communicated with each other in a cross mode, the installation mode of the bolt is simple, and the assembly efficiency and the cost can be improved. In an advantageous aspect of the embodiment, the existing hexagon head bolt can be directly utilized for hole drilling modification, wherein the transverse through hole penetrates through two opposite surfaces of the nut part of the bolt, so that the part machining efficiency is high and the cost is low.

In this embodiment, the same counterbore configuration as in the previous embodiment also exists. Specifically, referring to fig. 7, a counter bore is provided around the discharge port at the bottom of the annular recess 158, the counter bore is configured to be stepped so as to include a top inner wall surface 181, a top surface 182, a bottom surface 183, and a bottom inner wall surface 184 connecting the top surface and the bottom surface, and a bolt portion 320 of a bolt 300 is screwed with the bottom inner wall surface 184 so as to fix the bolt to the non-orbiting scroll.

In embodiments of the present application, the gas flow reversing structure, for example in the form of a cage or in the form of a bolt, may be configured such that the fluid passage remains normally open. Wherein the nut portion of the central baffle or bolt of the retainer as the gas flow reversing structure may be provided to serve as a baffle spaced apart from the discharge port of the fluid passage.

Although preferred embodiments of the present invention have been described in detail herein, it is to be understood that the invention is not limited to the precise construction herein described and illustrated, 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 intended to fall within the scope of the claims appended hereto.

Claims (12)

1. A scroll compressor, comprising:

a compression mechanism comprising a non-orbiting scroll and an orbiting scroll cooperating to form a series of compression chambers for compressing a working fluid, the non-orbiting scroll comprising a fluid passage; and

a floating seal disposed on one side of the non-orbiting scroll to define a back pressure chamber between the floating seal and the non-orbiting scroll, the back pressure chamber communicating with an intermediate pressure compression chamber of the compression chambers via the fluid passage such that the floating seal is axially floatable by compression chamber fluid from the intermediate pressure compression chamber,

wherein a flow reversing structure is disposed between the fluid passage and the floating seal, the flow reversing structure configured to adjust a direction of the compression chamber fluid discharged from the fluid passage.

2. The scroll compressor of claim 1, wherein the gas flow reversing structure is configured such that the fluid passage remains normally open.

3. The scroll compressor of claim 1, wherein the fluid passage includes a discharge port in fluid communication with the back pressure chamber, the gas flow reversing structure including a baffle disposed spaced from the discharge port.

4. The scroll compressor of any one of claims 1 to 3, wherein the gas flow reversing structure is in the form of a cage and includes an annular support body and a central baffle plate axially offset relative to the annular support body, the annular support body and the central baffle plate being connected by at least one connecting arm to form a plurality of radial passages between the annular support body and the central baffle plate.

5. The scroll compressor of claim 4, wherein the retainer is a one-piece member directly formed by a sheet metal process.

6. The scroll compressor of claim 4, wherein the retainer further comprises a snap-in portion extending from the annular support body that snaps into a corresponding portion of the non-orbiting scroll to secure the retainer to the non-orbiting scroll.

7. The scroll compressor of claim 6, wherein:

the non-orbiting scroll further includes an annular recess accommodating the floating seal and defining the back pressure chamber, a discharge port of the fluid passage is provided at a bottom of the annular recess,

a counter bore is provided at a bottom of the annular recess around the discharge port, the counter bore being configured in a step shape so as to include a top inner wall surface, a top surface, a bottom surface, and a bottom inner wall surface connecting the top surface and the bottom surface,

the retainer further comprises a first clamping portion and/or a second clamping portion, the first clamping portion extends radially from the annular support body, the radial outer end of the first clamping portion is clamped on the bottom inner wall surface, the second clamping portion extends radially from the annular support body, then extends axially and extends radially, and then comprises an inner radial section, an axial section and an outer radial section, the axial section is clamped on the bottom inner wall surface, and the radial outer end of the outer radial section is clamped on the top inner wall surface.

8. The scroll compressor of claim 7, wherein the retainer is constructed and arranged such that the central baffle is below the outer radial segment or below both the outer radial segment and the top surface.

9. The scroll compressor of any one of claims 1 to 3, wherein the gas flow reversing structure is in the form of a bolt and includes a bolt portion provided with an axial passage and a nut portion provided with a radial passage such that the compression chamber fluid discharged from the fluid passage reverses direction by first entering the axial passage and then entering the radial passage.

10. The scroll compressor of claim 9, wherein the radial passage includes two intersecting through holes through the nut portion.

11. The scroll compressor of claim 9, wherein:

the non-orbiting scroll further includes an annular recess accommodating the floating seal and defining the back pressure chamber, a discharge port of the fluid passage is provided at a bottom of the annular recess,

a counter bore is provided at a bottom of the annular recess around the discharge port, the counter bore being configured in a step shape so as to include a top inner wall surface, a top surface, a bottom surface, and a bottom inner wall surface connecting the top surface and the bottom surface,

the bolt portion is screwed with the bottom inner wall surface to fix the bolt to the fixed scroll.

12. The scroll compressor of any one of claims 1 to 3, wherein:

the non-orbiting scroll further includes an annular recess accommodating the floating seal and defining the back pressure chamber, a discharge port of the fluid passage is provided at a bottom of the annular recess,

a counterbore is provided at the bottom of the annular recess around the discharge port, the gas flow reversing structure being disposed in the counterbore such that the gas flow reversing structure does not protrude from the counterbore.

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