CN218376868U - Fixed scroll assembly and scroll compressor - Google Patents
Fixed scroll assembly and scroll compressor Download PDFInfo
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- CN218376868U CN218376868U CN202221903714.XU CN202221903714U CN218376868U CN 218376868 U CN218376868 U CN 218376868U CN 202221903714 U CN202221903714 U CN 202221903714U CN 218376868 U CN218376868 U CN 218376868U
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Abstract
The utility model relates to a decide vortex subassembly and including this vortex compressor who decides vortex subassembly. The fixed scroll component comprises a movable scroll part, at least two bypass holes, a piston chamber, a bypass discharge channel, a piston, a connecting groove, a sealing component and a bypass control device. The piston chambers are respectively disposed at opposite sides of the respective bypass holes from the compression chambers and extend to outer end surfaces. Each piston is received in a respective piston chamber and is configured to be movable between a sealing position in which the piston covers the respective bypass orifice to prevent the bypass orifice from communicating with the respective bypass discharge passage and a release position; in the release position, the piston is away from the bypass orifice to allow the bypass orifice to communicate with the bypass discharge passage. The connecting groove is provided on the outer end surface and configured to communicate the piston chambers with each other. The seal assembly is configured to seal the connection groove. The bypass control device is configured to selectively communicate or interrupt the high-pressure fluid source with the connecting recess.
Description
Technical Field
The present disclosure relates to the field of scroll compressors, and more particularly, to a fixed scroll assembly and a scroll compressor capable of adjusting capacity.
Background
The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
Scroll compressors are known as compression machines of the capacity type. The capacity modulation technique is a technique of changing the displacement without changing the rotational speed of the compressor or unloading the compression mechanism. The capacity adjusting technology can enable the output capacity of the unit to better adapt to the requirement of terminal load, reduce the start and stop of the unit, and improve the energy efficiency and the comfort of the system. Typically, the capacity modulation mechanism achieves part load operation by bypassing a certain compression chamber to a low pressure region.
Some existing capacity adjusting mechanisms have more parts, complex structures and higher cost. Other existing capacity adjustment mechanisms have more sealing surfaces, which increases the machining requirements and reduces reliability. Other existing capacity adjusting mechanisms have difficulty in processing due to structural limitations of the compression mechanism.
SUMMERY OF THE UTILITY MODEL
It is an object of the present disclosure to provide a non-orbiting scroll assembly and a scroll compressor incorporating a capacity adjustment mechanism. The capacity adjustment mechanism has a small number of parts, a simple and compact structure, low cost and/or reliable operation.
According to one aspect of the present disclosure, there is provided a non-orbiting scroll assembly including an orbiting scroll member, at least two bypass holes, a piston chamber, a bypass discharge passage, a piston, a connection groove, a sealing assembly, and a bypass control device. The non-orbiting scroll member has an end plate having an inner end surface, an outer end surface and an outer peripheral surface, and a vane extending from the inner end surface, an exhaust port for discharging compressed fluid being provided in the end plate. Each bypass hole extends to the inner end surface and communicates with a compression chamber. The piston chambers are respectively disposed at opposite sides of the corresponding bypass holes from the compression chamber and extend to the outer end surfaces. The bypass discharge passage is configured to communicate the respective piston chamber to a low pressure region. Each piston is received in a respective piston chamber and is configured to be movable between a sealing position in which the piston covers a respective bypass orifice to prevent the bypass orifice from communicating with a respective bypass exhaust passage and a release position; in the release position, the piston is away from the bypass orifice to allow the bypass orifice to communicate with the bypass discharge passage. The connection groove is provided on the outer end face and configured to communicate the piston chambers with each other. The seal assembly is configured to seal the connection groove. The bypass control device is configured to selectively communicate or interrupt a high-pressure fluid source with the connecting groove.
According to the fixed vortex assembly disclosed by the invention, the movement resistance of the piston is small, and the response time is short. By adopting the connecting groove and the single sealing component, the number of parts can be obviously reduced, the structure is compact, and the processing and assembling processes are simplified. The coupling groove is provided on the outer end face of the end plate, thereby facilitating design, processing and assembly.
In some embodiments, the bypass control device includes a first fluid passage, a second fluid passage, and a valve. The first fluid passage extends from the high pressure fluid source to the valve. The second fluid passage extends from the valve to the connecting groove. The valve is configured to be movable between a first position that allows the first fluid passage to communicate with the second fluid passage and a second position that does not allow the first fluid passage to communicate with the second fluid passage.
In some embodiments, the valve is a solenoid valve and is configured to move to the first position when de-energized and to move to the second position when energized.
In some embodiments, the solenoid valve is attached to an outer peripheral surface of the end plate.
In some embodiments, the high pressure fluid source comprises a compression chamber, a back pressure chamber, or a vent.
In some embodiments, the non-orbiting scroll member further has an inner cylindrical portion and an outer cylindrical portion extending from an outer end face of the end plate, the inner cylindrical portion surrounding the exhaust port, the outer cylindrical portion surrounding the inner cylindrical portion. The back pressure chamber is defined by the inner cylindrical portion, the outer cylindrical portion, and the outer end face. The connecting groove is located between the inner and outer cylindrical portions and is sealed from the back pressure chamber by the seal assembly.
In some embodiments, the non-orbiting scroll assembly further includes a back pressure channel for introducing fluid in a compression chamber to the back pressure chamber.
In some embodiments, the seal assembly includes a seal gasket overlying the connection groove, a pressure plate disposed on the seal gasket, and a fastener mounting the pressure plate and the seal gasket to the end plate.
In some embodiments, the sealing gasket and the pressure plate are in the shape of a circular arc plate.
In some embodiments, the connecting groove comprises a plurality of sections and a rounded transition between the plurality of sections.
In some embodiments, the non-orbiting scroll assembly further includes a sealing structure provided on an outer circumferential surface of the corresponding piston to divide the corresponding piston chamber into a first chamber communicating with the corresponding bypass hole and a second chamber communicating with the connection groove.
In some embodiments, the sealing structure comprises: a seal and an annular groove for receiving the seal; or a labyrinth seal.
In some embodiments, the piston comprises a tapered surface or a flat bottom surface for abutting and sealing the bypass orifice.
In some embodiments, the piston includes a recess extending downwardly from the top surface, the recess being in fluid communication with the connecting groove.
In some embodiments, the piston chamber has an inner circumferential wall that mates with the piston. The piston has a cylindrical outer circumferential surface having a constant diameter, or a tapered outer circumferential surface tapered toward the bypass hole.
In some embodiments, a plurality of the bypass discharge passages may be provided for each bypass hole.
According to another aspect of the present disclosure, there is also provided a scroll compressor including the above-described non-orbiting scroll assembly.
Further areas of applicability will become apparent from the description provided herein. It should be understood that the specific examples and embodiments described in this section are for illustrative purposes only and are not intended to limit the scope of the present disclosure.
Drawings
Features and advantages of one or more embodiments of the present disclosure will become more readily understood from the following description taken in conjunction with the accompanying drawings, in which:
FIG. 1 is a schematic perspective view of a non-orbiting scroll assembly according to an embodiment of the present disclosure;
FIG. 2 is an exploded schematic view of the non-orbiting scroll assembly of FIG. 1;
FIG. 3 is a top schematic view of the non-orbiting scroll assembly of FIG. 1;
FIG. 4 is a schematic view of the non-orbiting scroll assembly of FIG. 3 with the seal assembly removed;
FIG. 5 is a schematic longitudinal cross-sectional view of the non-orbiting scroll assembly of FIG. 1 taken along the piston with the piston in a sealing position;
FIG. 6 is a schematic longitudinal cross-sectional view of the non-orbiting scroll assembly of FIG. 1 taken along the piston with the piston in a released position;
FIG. 7 is a cross-sectional schematic view of the non-orbiting scroll assembly of FIG. 1 taken along a fluid passageway communicating with a valve;
FIG. 8 is a schematic longitudinal cross-sectional view taken along the first fluid of FIG. 7, showing an example of collecting high pressure fluid from the compression chamber;
FIG. 9 is a schematic plan view of the example of FIG. 8 from one side of the blade;
FIG. 10 is a schematic cross-sectional view of an example of collecting high pressure fluid from a back pressure chamber;
FIG. 11 is a schematic cross-sectional view of an example of collecting high pressure fluid from an exhaust port;
FIG. 12 is a schematic plan view of the example of FIGS. 10 and 11 from one side of the blade;
FIG. 13 is a schematic perspective view of the piston shown in FIG. 2, according to an embodiment of the present disclosure;
FIG. 14 is a longitudinal cross-sectional view of a piston according to another embodiment of the present disclosure;
FIG. 15 is a longitudinal cross-sectional view of a piston according to yet another embodiment of the present disclosure;
FIG. 16 is a longitudinal cross-sectional schematic view of a non-orbiting scroll assembly according to another embodiment of the present disclosure; and
FIG. 17 is a perspective view of a non-orbiting scroll assembly according to yet another embodiment of the present disclosure.
Corresponding reference characters indicate like or corresponding parts and features throughout the drawings.
Detailed Description
Exemplary embodiments will now be described more fully with reference to the accompanying drawings.
The exemplary embodiments are provided so that this disclosure will be thorough and will more fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
To achieve partial load operation, two bypass structures are typically provided in the non-orbiting scroll member to bypass the working fluid in the compression chambers to a low pressure region. According to the fixed scroll assembly disclosed by the invention, a bypass control mechanism which is simple in structure and reliable in operation is integrated. The bypass control mechanism according to the present disclosure is also particularly applicable to a non-orbiting scroll member having a back pressure chamber formed on the outer end surface side of the end plate.
The bypass control mechanism according to the present disclosure includes a piston for controlling communication and interrupting communication of each bypass structure, a connecting groove for communicating respective chambers for controlling movement of the piston with each other, a single seal assembly for sealing the connecting groove, and a valve for controlling communication and interrupting communication between the high pressure source and the connecting groove. The moving resistance of the piston is small, and the response time is short. By adopting the connecting groove and the single sealing component, the number of parts can be obviously reduced, the structure is compact, and the processing and assembling processes are simplified. The coupling groove is provided on the outer end face of the end plate, thereby facilitating design, processing and assembly. The non-orbiting scroll assembly according to the present disclosure may further provide a sealing structure on an outer circumferential surface of the piston such that chambers at both sides thereof are sealed from each other, thereby improving sealing and leakage preventing performance and improving reliability.
"high pressure" as referred to herein refers to a pressure greater than the pressure of fluid within the compression chamber in communication with the bypass orifice. "Low pressure" as referred to herein refers to a pressure less than the pressure of fluid within the compression chamber in communication with the bypass orifice.
As used herein, a "compression chamber" refers to a closed compression chamber located between an open suction chamber and a discharge chamber. The suction chamber communicates with a low-pressure area or low-pressure conduit for supplying a low-pressure fluid to be compressed. The exhaust cavity is communicated with an exhaust port of the compression mechanism.
A non-orbiting scroll assembly 100 according to an embodiment of the present disclosure will be described with reference to fig. 1 to 9. As shown in fig. 1-9, the non-orbiting scroll assembly 100 includes a non-orbiting scroll member 110. The non-orbiting scroll member 110 is engaged with an orbiting scroll member (not shown) to form a compression mechanism that compresses a working fluid. The construction of the orbiting scroll member is known in the art and therefore will not be described in detail herein.
Referring to fig. 5 and 6, non-orbiting scroll member 110 includes end plate 102, vanes 104, and exhaust port 106. End plate 102 has an inner end surface (lower end surface in the figure) 102a, an outer end surface (upper end surface in the figure) 102b opposite to inner end surface 102a, and an outer peripheral surface 102c. The blades 104 extend downward from the inner end surface 102a of the end plate 102. A discharge port 106 is provided at substantially the center of the end plate 102, and the compressed working fluid is discharged out of the compression mechanism via the discharge port 106.
The non-orbiting scroll member 110 includes a bypass passage for communicating the compression pockets to a low pressure region for part load operation. As shown in fig. 5 and 6, the bypass passage is composed of the bypass hole 111, the piston chamber 121, and the bypass discharge passage 141. The bypass hole 111 directly communicates with the compression chamber, i.e., adjacent to the compression chamber. The bypass hole 111 has an inlet adjacent to the compression chamber and an outlet adjacent to the piston chamber. The piston chamber 121 is disposed at the opposite side of the bypass hole 111 from the compression chamber. The piston chamber 121 extends from the outlet of the bypass hole 111 to the outer end face 102b of the end plate 102. The bypass discharge passage 141 serves to communicate the piston chamber 121 to a low pressure region outside the non-orbiting scroll member. The bypass discharge passage 141 extends laterally from the side of the piston chamber 121 to the outer peripheral surface 102c.
The piston chamber 121 is configured to receive the piston 130. The piston 130 is movable (vertically movable in the figure) in the piston chamber 121. When the piston 130 moves toward the bypass hole 111 (downward in the drawing) and reaches a closed position covering the bypass hole 111, the piston 130 blocks the communication of the bypass passage, as shown in fig. 5. At this time, the scroll compressor is operating at full load. When the piston 130 moves away from the bypass hole 111 (upward in the drawing) and reaches a release position where the bypass hole 111 communicates with the bypass discharge passage 141, the bypass passage communicates, as shown in fig. 6. At this time, the scroll compressor is partially loaded.
Movement of the piston 130 may be achieved by controlling the fluid pressure above the piston chamber. Referring to fig. 2 and 4, the non-orbiting scroll assembly 100 further includes a coupling recess 125, a seal assembly 160 sealing the coupling recess 125, and a bypass control device 150 selectively communicating or interrupting a high pressure fluid source with the coupling recess 125.
Referring to fig. 4, a connection groove 125 is provided on the outer end face 102b of the end plate 102 and serves to communicate the piston chambers 121 with each other. Since the coupling groove 125 is formed on the outer end surface 102b, the structure is simple and the processing is easy. In the example shown in the figures, the connecting groove 125 comprises a plurality of sections with rounded transitions between the sections, which may effectively reduce flow losses. It should be understood that the coupling groove 125 may be changed as needed and the design is flexible.
Referring to fig. 2, the seal assembly 160 includes a seal gasket 161, a pressure plate 162, and a fastener 163. The sealing gasket 161 covers the coupling groove 125 to seal the coupling groove 125. As such, the fluid in the piston chamber 121 may be prevented from leaking into the back pressure chamber BC or the fluid in the back pressure chamber BC may be prevented from leaking into the piston chamber 121. The pressing plate 162 is provided on the gasket 161 to protect the gasket 161 and to facilitate mounting of the gasket 161. The pressure plate 162 and the sealing gasket 161 may have similar structures. In the example shown in the drawings, the platen 162 and the seal gasket 161 are circular-arc plate-shaped. Fasteners 163 are used to mount the platen 162 and the sealing gasket 161 to the endplate 102. For example, the fastener 163 may be a screw or a rivet. Accordingly, the sealing gasket 161 and the pressure plate 161 may have holes for receiving the fasteners 163.
In the example shown in the drawings, the connecting groove 125 and the seal assembly 160 are both located between the inner cylindrical portion 107 and the outer cylindrical portion 108. In this way, the structure of the compression mechanism or compressor may be more compact, and it may be advantageous to reduce the axial height of the compression mechanism or compressor.
It should be understood that the structure, arrangement, etc. of the non-orbiting scroll member, the coupling groove, and the seal assembly should not be limited to the specific examples illustrated in the drawings, but may be changed as needed. For example, the non-orbiting scroll member may omit the back pressure chamber BC and, accordingly, the coupling groove 125 and seal assembly 160 may be located at any suitable location on the outer end face.
Referring to fig. 7, the bypass control device 150 includes a first fluid passage 151, a second fluid passage 152, and a valve 153. The first fluid passage 151 extends from a high pressure fluid source to the valve 153. The second fluid passage 152 extends from the valve 153 to the connection groove 125. The valve 153 is configured to be movable between a first position that allows the first fluid passage 151 to communicate with the second fluid passage 152 and a second position that does not allow the first fluid passage 151 to communicate with the second fluid passage 152.
As shown in fig. 2, the valve 153 is attached to the outer peripheral surface 102c of the end plate 102. Accordingly, the first fluid passage 151 and the second fluid passage 152 each extend to the outer peripheral surface 102c of the end plate 102 to be connected to the respective ports 156, 157 of the valve 153, respectively (see fig. 7). The internal structure of valve 153 that allows ports 156 and 157 to be connected or disconnected may be any suitable structure known and will not be described in detail herein.
When the scroll compressor is operating at full load, the valve 153 is switched to the first position as shown in FIG. 5 so that the first fluid passage 151 is in communication with the second fluid passage 152, thereby introducing high pressure fluid from a high pressure source into the connecting groove 125 and, in turn, into each piston chamber 121. At this time, the pressure applied to the top surface of the piston 130 by the high pressure fluid will be greater than the pressure applied to the bottom surface of the piston 130 by the fluid in the compression chamber, and thus the piston 130 abuts against the outlet of the bypass hole 111, preventing the fluid in the compression chamber from bypassing to the low pressure region.
When the scroll compressor is operating at part load, the valve 153 is switched to the second position as shown in FIG. 6 such that the first fluid passage 151 is not in communication with the second fluid passage 152, thereby preventing high pressure fluid from flowing into each piston chamber 121. At this time, the pressure of the fluid in the compression chamber against the bottom surface of the piston 130 pushes the piston 130 upward, moving the piston 130 away from the outlet of the bypass hole 111, and thus allowing the fluid in the compression chamber to bypass to a low pressure region.
The valve 153 may be a solenoid valve. In the event that the scroll compressor is operated at full load for a long period of time, the valve 153 may be configured to be switched to the first position as shown in FIG. 5 when de-energized and to be switched to the second position as shown in FIG. 6 when energized. In the event that the scroll compressor is operated at part load conditions for an extended period of time, the valve 153 may be configured to be switched to the second position as shown in FIG. 6 when de-energized and to be switched to the first position as shown in FIG. 5 when energized. In this way, the valve 153 can be in the deenergized state for a long period of time, whereby the life of the valve 153 can be significantly extended, that is, the probability of failure of the valve 153 is significantly reduced.
The first fluid passage 151 is used to introduce high-pressure fluid from a high-pressure source. The first fluid passage 151 may have a smaller bore diameter, and thus the pressure fluctuation may be reduced by increasing the damping. The high pressure fluid source may be any suitable high pressure region including, for example, a compression chamber, a back pressure chamber BC, or a vent 106.
Fig. 7 to 9 show examples of compression chambers as high pressure fluid sources. Referring to fig. 7 to 9, the first fluid passage 151 extends from the compression chamber, i.e., has an inlet 113 at the inner end face 102a of the end plate 102. The fluid pressure in the compression chamber at the inlet 113 is greater than the fluid pressure in the compression chamber at the bypass hole 111. That is, the inlet 113 is located radially inward of the bypass hole 111 along the spiral path of the vane 104 (see fig. 9). In the example shown in fig. 7-9, the first fluid channel 151 includes a laterally extending section and an axially downwardly extending section.
Fig. 10 shows an example of the back pressure chamber BC as a high pressure fluid source. Referring to fig. 10, the first fluid passage 151 extends from the back pressure chamber BC, i.e., has an inlet 115 at an outer end face 102b defining the back pressure chamber BC. In this case, the fluid pressure in the back pressure chamber BC is greater than the fluid pressure in the compression chamber at the bypass hole 111. In the example shown in fig. 10, the first fluid channel 151 includes a laterally extending section and an axially upwardly extending section.
Fig. 11 shows an example of the exhaust port 106 as a high-pressure fluid source. Referring to fig. 11, the first fluid channel 151 extends from the wall of the exhaust port 106, i.e., has an inlet 117 at the wall of the exhaust port 106. In the example shown in fig. 11, the first fluid channel 151 includes only laterally extending segments.
For the example shown in fig. 11, it is advantageous to provide an exhaust valve 101 above the exhaust port 106. The discharge valve 101 is a check valve that allows the compressed working fluid to be discharged from the discharge port 106 but prevents the working fluid outside the compression mechanism from flowing backward to the discharge port 106 and the compression chamber. Therefore, the exhaust valve 101 can prevent damage to the valve 153 due to excessive return air pressure.
Fig. 12 is a schematic plan view of the example of fig. 10 and 11, viewed from one side of the blade. In contrast to the example shown in fig. 9, the examples shown in fig. 10 and 11 omit the passage (i.e., the passage inlet 113) that collects high pressure fluid into the compression chamber. Therefore, the area of the high-pressure fluid collected is different, and the arrangement of the first fluid passage 151 is slightly different.
Referring again to fig. 4 and 7, second fluid passage 152 is used to communicate port 157 of valve 153 to connection groove 125 on outer face 102b. Advantageously, port 157 may communicate with a low pressure region when valve 153 is switched to the second position shown in fig. 6, thereby ensuring that fluid in the compression chamber can lift the piston. The second fluid channel 152 has an outlet 123 that opens into the connecting groove 125. In the illustrated example, the second fluid passage 152 has a laterally extending passage and an axially upwardly extending passage.
It should be understood that the structure of the bypass control and its various components should not be limited to the specific examples shown in the figures, but may be varied as desired. For example, the configuration, size, location, etc. of the various fluid channels may be varied as desired.
The piston 130 according to an embodiment of the present disclosure will be described below with reference to fig. 13. The piston 130 is generally cylindrical in shape, having a top surface 1311, a bottom surface 1312 opposite the top surface 1311, and an outer peripheral surface 1314 extending between the top surface 1311 and the bottom surface 1312. The piston 130 may have a recess 1315 extending downward from the top surface 1311 for receiving high pressure fluid. The piston 130 may have features 1317 that facilitate operation of a tool (not shown). The features 1317 may vary depending on the configuration of the tool and are not necessarily limited to the specific examples shown in the figures.
Referring to fig. 5 and 6, the bottom surface 1312 may include a central flat surface 1312a and a tapered surface 1312b for abutting and sealing the bypass hole 111. Further, a seal 136 may be disposed between the outer circumferential surface 1314 of the piston 130 and the wall of the piston chamber 121. To this end, an annular recess 1316 may be provided on the outer peripheral surface 1314 of the piston 130 to accommodate the seal 136. For example, the seal 136 may be an O-ring. The piston chamber 121 is partitioned by a seal 136 into a first chamber (lower chamber in the drawing) 121a communicating with the bypass hole 111 and a second chamber (upper chamber in the drawing) 121b communicating with the connection groove 125. The low-pressure first chamber and the high-pressure second chamber are sealed from each other by the seal 136, improving sealing performance and thus reliability. The seal 136 and the annular recess 1316 for receiving the seal 136 form a seal between the piston 130 and the wall of the piston chamber 121.
Fig. 14 shows a longitudinal sectional view of a piston 230 according to another embodiment of the present disclosure. The piston 230 is different from the piston 130 in a sealing structure between walls of the piston chamber. Referring to fig. 14, the piston 230 has a labyrinth seal structure 2316 provided on an outer circumferential surface 2314 thereof. The labyrinth seal structure 2316 includes a plurality of annular grooves (three annular grooves are shown in the drawing) provided in series in the axial direction. These annular grooves in turn create throttling and resistance to the fluid, thereby achieving a sealing effect. A conical seal is used between the piston 230 and the bypass hole 111. Similar to the piston 130, the bottom surface 2312 of the piston 230 includes a central flat surface 2312a and a tapered surface 2312b located radially outward of the flat surface 2312 a. The tapered surface 2312b serves to abut and seal the tapered surface at the outlet of the bypass hole 111.
Fig. 15 shows a longitudinal sectional view of a piston 330 according to still another embodiment of the present disclosure. The piston 330 is different from the piston 230 in a structure for sealing the bypass hole 111. Specifically, the piston 330 has a flat bottom surface 3312. The flat bottom surface 3312 is seated on a plane on which the outlet of the bypass hole 111 is located to perform a plane sealing of the bypass hole 111. Similar to the piston 230, a labyrinth seal 3316 is employed between the piston 330 and the wall of the piston chamber.
Fig. 16 shows a longitudinal sectional view of the non-orbiting scroll assembly 200 having a different shape of the piston chamber 221. In the non-orbiting scroll assembly 200, the piston chamber 221 has a tapered inner circumferential wall 222 tapered toward the bypass hole 111. The piston may have an outer circumferential surface of the same shape as the piston chamber, i.e., may have a tapered outer circumferential surface (not shown) that tapers toward the bypass hole 111. In each of the examples shown in fig. 1 to 15, the piston has a cylindrical outer peripheral surface with a substantially constant diameter, and accordingly, the piston chamber may have a cylindrical inner peripheral wall with a substantially constant diameter. The structure of the piston and piston chamber should not be limited to the specific examples shown in the figures, but may be varied as desired as long as the functions described herein are achieved.
FIG. 17 illustrates a perspective view of non-orbiting scroll assembly 300 having a different configuration of bypass discharge passages. The non-orbiting scroll assembly 300 may have two bypass discharge passages 141a and 141b communicating to a low pressure region for each bypass passage. Multiple bypass exhaust passages may improve exhaust efficiency. It should be understood that the bypass discharge passages should not be limited to the specific examples shown in the figures, but may be varied in number, shape, size, etc. as desired.
The non-orbiting scroll assembly according to the present disclosure may be applied to various types of scroll compressors and can bring about the above-described advantages similar to the non-orbiting scroll assembly.
Various embodiments and modifications of the present disclosure have been specifically described above, but it should be understood by those skilled in the art that the present disclosure is not limited to the specific embodiments and modifications described above but may include other various possible combinations and combinations. Other modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the disclosure. All such variations and modifications are intended to fall within the scope of the present disclosure. Moreover, all the components described herein can be replaced by other technically equivalent components.
Claims (17)
1. A non-orbiting scroll assembly comprising:
a non-orbiting scroll member having an end plate with an inner end surface, an outer end surface and an outer circumferential surface, and a vane extending from the inner end surface, an exhaust port for discharging compressed fluid being provided in the end plate;
at least two bypass holes, each extending to the inner end surface and communicating with a compression cavity;
piston chambers respectively disposed at opposite sides of the respective bypass holes from the compression chambers and extending to the outer end surfaces;
a bypass discharge passage configured to communicate the respective piston chamber to a low pressure region;
a piston, each piston housed in a respective piston chamber and configured to be movable between a sealing position in which it covers a respective bypass aperture to prevent it from communicating with a respective bypass discharge channel and a release position; in the release position, the piston is away from the bypass orifice to allow the bypass orifice to communicate with the bypass discharge passage;
a connection groove provided on the outer end face and configured to communicate the piston chambers with each other;
a seal assembly configured to seal the connection groove; and
a bypass control device configured to selectively communicate or interrupt a high pressure fluid source with the connecting groove.
2. The non-orbiting scroll assembly of claim 1, wherein the bypass control device comprises a first fluid passage, a second fluid passage, and a valve,
the first fluid passage extends from the high pressure fluid source to the valve;
the second fluid passage extends from the valve to the connecting groove; and
the valve is configured to be movable between a first position that allows the first fluid passage to communicate with the second fluid passage and a second position that does not allow the first fluid passage to communicate with the second fluid passage.
3. The non-orbiting scroll assembly according to claim 2, wherein the valve is a solenoid valve and is configured to move to the first position when de-energized and to move to the second position when energized.
4. The non-orbiting scroll assembly according to claim 3, wherein the solenoid valve is attached to an outer peripheral surface of the end plate.
5. The non-orbiting scroll assembly as claimed in claim 2, wherein the high pressure fluid source comprises a compression chamber, a back pressure chamber or a discharge port.
6. The non-orbiting scroll assembly of claim 5 further having an inner cylindrical portion and an outer cylindrical portion extending from an outer end face of the end plate, the inner cylindrical portion surrounding the exhaust port and the outer cylindrical portion surrounding the inner cylindrical portion,
the back pressure chamber is defined by the inner cylindrical portion, the outer cylindrical portion and the outer end face,
the connecting groove is located between the inner cylindrical portion and the outer cylindrical portion and is sealed from the back pressure chamber by the seal assembly.
7. The non-orbiting scroll assembly according to claim 6 further comprising a back pressure passage for introducing fluid in a compression chamber to the back pressure chamber.
8. The non-orbiting scroll assembly of any one of claims 1 to 7 wherein the seal assembly includes a seal gasket overlying the connection groove, a pressure plate disposed on the seal gasket, and a fastener mounting the pressure plate and the seal gasket to the end plate.
9. The non-orbiting scroll assembly as claimed in claim 8, wherein the sealing gasket and the pressure plate are circular arc plate shaped.
10. The non-orbiting scroll assembly of any one of claims 1 to 7, wherein the connection groove comprises a plurality of sections and a radiused transition between the plurality of sections.
11. The non-orbiting scroll assembly according to any one of claims 1 to 7, further comprising a sealing structure provided on an outer circumferential surface of the corresponding piston to divide the corresponding piston chamber into a first chamber communicating with the corresponding bypass hole and a second chamber communicating with the connection groove.
12. The non-orbiting scroll assembly according to claim 11, wherein the sealing structure comprises:
a seal and an annular groove for receiving the seal; or
A labyrinth seal structure.
13. The non-orbiting scroll assembly according to any one of claims 1 to 7 wherein the piston includes a tapered surface or a flat bottom surface for abutting and sealing the bypass hole.
14. The non-orbiting scroll assembly according to any one of claims 1 to 7 wherein the piston includes a recess extending downwardly from a top surface, the recess being in fluid communication with the connecting groove.
15. The non-orbiting scroll assembly according to any one of claims 1 to 7, wherein the piston chamber has an inner circumferential wall that mates with the piston,
the piston has a cylindrical outer circumferential surface having a constant diameter, or a tapered outer circumferential surface tapered toward the bypass hole.
16. A non-orbiting scroll assembly as claimed in any one of claims 1 to 7 wherein a plurality of bypass discharge passages may be provided for each bypass aperture.
17. A scroll compressor, characterized in that it comprises a non-orbiting scroll assembly according to any one of claims 1 to 16.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221903714.XU CN218376868U (en) | 2022-07-22 | 2022-07-22 | Fixed scroll assembly and scroll compressor |
| PCT/CN2023/104781 WO2024002348A1 (en) | 2022-06-30 | 2023-06-30 | Fixed scroll assembly and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221903714.XU CN218376868U (en) | 2022-07-22 | 2022-07-22 | Fixed scroll assembly and scroll compressor |
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| CN218376868U true CN218376868U (en) | 2023-01-24 |
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| CN202221903714.XU Active CN218376868U (en) | 2022-06-30 | 2022-07-22 | Fixed scroll assembly and scroll compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024002348A1 (en) * | 2022-06-30 | 2024-01-04 | 谷轮环境科技（苏州）有限公司 | Fixed scroll assembly and scroll compressor |
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2022
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024002348A1 (en) * | 2022-06-30 | 2024-01-04 | 谷轮环境科技（苏州）有限公司 | Fixed scroll assembly and scroll compressor |
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