CN115217757A

CN115217757A - Scroll compressor having a plurality of scroll members

Info

Publication number: CN115217757A
Application number: CN202110423475.1A
Authority: CN
Inventors: 刘轩; 邹宏伟; 房元灿; 张冲
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2021-04-20
Filing date: 2021-04-20
Publication date: 2022-10-21

Abstract

The present disclosure relates to a scroll compressor, including: the scroll compressor comprises an orbiting scroll and a non-orbiting scroll, a central compression cavity and a plurality of intermediate compression cavities are formed between the orbiting scroll and the non-orbiting scroll, wherein a first concave part configured as a sealing cavity is formed at one side of a non-orbiting scroll end plate, a first passage and a second passage are further formed in the non-orbiting scroll end plate, the first passage selectively provides fluid communication between at least one first intermediate compression cavity and the sealing cavity, the second passage selectively provides fluid communication between the sealing cavity and a suction pressure region of the scroll compressor, a check valve is disposed in the sealing cavity, and a valve plate of the check valve can simultaneously cover a first opening of the first passage in the sealing cavity and a second opening of the second passage in the sealing cavity to synchronously open or close both the first passage and the second passage. According to the scroll compressor disclosed by the invention, the capacity adjustment can be realized, the structure is simple, the performance is good, and the operation is reliable.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having a capacity adjustment mechanism.

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 compression assembly of a scroll compressor includes a scroll member comprised of a non-orbiting scroll member and an orbiting scroll member. Generally, the fixed scroll part and the movable scroll part each include a single-line scroll blade, the two scroll blades are engaged with each other to form a series of compression chambers between the fixed scroll part and the movable scroll part to compress a working medium (such as a gaseous refrigerant), and a compressed high-pressure gas is discharged through a discharge port in the center of the fixed scroll.

The scroll compressor may vary the operating capacity of the compressor in a number of ways, such as varying the compressor speed and/or unloading the scroll member, as required by operating conditions. In addition, there is also known a mechanism for achieving capacity modulation without changing the rotational speed of the compressor and without unloading the scroll member, the mechanism including an annular ring, a seal, a spacer, a solenoid valve, and the like, the annular ring, the seal and the spacer forming a seal chamber, the seal chamber being controlled by the solenoid valve to communicate with a higher pressure region in the compressor or with a lower pressure region in the compressor, and a pressure difference between upper and lower sides of the annular ring being able to be controlled so as to move the annular ring up and down to open or close a relief hole provided in the fixed scroll member to communicate with at least one intermediate compression chamber. When the pressure relief hole is opened, the molded line of the front part of the scroll mechanism does not participate in compression, thereby realizing the purpose of capacity change.

Although such a capacity adjustment mechanism has a cost advantage over frequency conversion and a better energy efficiency over fixed frequency integration, it still has drawbacks. For example, the structure is complex, the parts are numerous, the sealing surface is numerous and easy to leak, the height of the fixed scroll hub is high, and the casting difficulty is high.

Accordingly, there is a need for further improvements in capacity modulating mechanisms for scroll compressors.

Disclosure of Invention

An object of the present disclosure is to provide a scroll compressor having a novel capacity modulation mechanism capable of performing capacity modulation without changing the rotational speed of the compressor and/or unloading the scroll mechanism, wherein the capacity modulation mechanism mainly includes a check valve capable of replacing known components such as an annular ring, a seal member, and a spacer, and thus, the structure is simpler, the number of parts is less, the number of sealing surfaces is less, the leakage risk is lower, and the installation and manufacturing are easier.

It is another object of the present disclosure to make the capacity modulating mechanism more compact to further optimize the spatial design within the scroll compressor, particularly at the non-orbiting scroll member.

Another object of the present disclosure is to improve the sealing performance of the check valve of the capacity adjustment mechanism and also to reduce the closing response time of the check valve, thereby ensuring smooth switching of the capacity adjustment mechanism between the partial capacity mode and the full capacity mode.

It is yet another object of the present disclosure to provide a scroll compressor with a novel capacity modulation mechanism, wherein the capacity modulation mechanism can be combined with frequency conversion technology, thereby making the ratio of maximum displacement to minimum displacement of the compressor larger, extending the range of frequency conversion of the compressor, and at the same time making the compressor perform better when operating at partial capacity and obtaining better lubrication conditions.

According to one aspect of the present disclosure, there is provided a scroll compressor including: an orbiting scroll including a first end plate and a first scroll blade formed on the first end plate; a non-orbiting scroll having a second end plate and a second scroll blade formed at a first side of the second end plate, the first and second scroll blades being engaged with each other to form a central compression chamber and a plurality of intermediate compression chambers between the orbiting and non-orbiting scrolls, wherein the second end plate is formed at a second side opposite to the first side with a first recess configured as a sealed chamber, the second end plate is further formed therein with a first passage configured to selectively provide fluid communication between the sealed chamber and at least one of the plurality of intermediate compression chambers and the sealed chamber, and a second passage configured to selectively provide fluid communication between the sealed chamber and a suction pressure region of the scroll compressor, the first passage includes a first opening located within the sealed chamber, the second passage includes a second opening located within the sealed chamber, a check valve is disposed within the sealed chamber, and a valve plate of the check valve can simultaneously cover the first and second openings to synchronously open or close both the first and second passages.

Optionally, a third channel is provided in the second end plate, the third channel is in fluid communication with the seal cavity and is connected to a solenoid valve that can be switched between a first state in which the third channel fluidly communicates the seal cavity with a suction pressure region of the scroll compressor via the solenoid valve to open a valve plate of the check valve, and a second state in which the third channel is closed by the solenoid valve or fluidly communicates the seal cavity with a high pressure or medium pressure region of the scroll compressor via the solenoid valve to close the valve plate of the check valve.

Optionally, a hub is formed in the center of the second side of the second end plate, a non-orbiting scroll central exhaust passage in fluid communication with the non-orbiting scroll exhaust port is formed in the hub, and a port hole is further formed in the hub, the port hole fluidly communicating the seal chamber with the non-orbiting scroll central exhaust passage, and a cross-sectional area of the port hole is smaller than a cross-sectional area of the third passage.

Optionally, a fourth passage is provided in the second end plate, the fourth passage being in fluid communication with the central compression chamber or with a second intermediate compression chamber of the plurality of intermediate compression chambers, wherein the pressure of the second intermediate compression chamber is higher than the pressure of the first intermediate compression chamber, and the fourth passage is connected to the solenoid valve, in the first state the fourth passage is closed by the solenoid valve, in the second state the fourth passage is in fluid communication with the third passage through the solenoid valve.

Optionally, the scroll compressor includes a cover plate disposed on the second side of the second end plate, the cover plate covering the first recess thereby forming a sealed cavity.

Optionally, the second side of the second end plate is formed with a second recess configured as a back pressure chamber of the non-orbiting scroll, the first recess is formed below the second recess in the axial direction, and the scroll compressor includes a seal spacer plate covering the first recess to form a seal chamber.

Optionally, the sealed cavity is configured as first and second chambers spaced apart from each other disposed on both sides of the axis of the non-orbiting scroll, the first and second chambers being in fluid communication through a channel formed on the second end plate.

Optionally, the valve plate of the check valve includes a first end portion and a second end portion, the first end portion and the second end portion are connected by a connecting portion, the first end portion is fixed to the second end plate, and the second end portion selectively opens or closes the first opening and the second opening.

Optionally, the check valve includes a baffle located above the valve plate, and through holes are provided at positions of the baffle corresponding to the first opening and the second opening below the valve plate.

Alternatively, in the seal chamber, the second end plate is formed with a boss portion surrounding the first opening and the second opening, and the valve sheet can be brought into contact with the boss portion to seal the first opening and the second opening.

Optionally, within the sealed cavity, the second end plate is formed with a sink surrounding and spaced from the first opening, the sink being in fluid communication with the second opening and not in fluid communication with the first opening.

Optionally, the first passage includes an eccentrically disposed first bore segment connected to the sealed cavity and a second bore segment connected to the at least one first intermediate compression cavity, the second bore segment configured as a plurality of bores distributed generally along the scroll profile.

According to the scroll compressor disclosed by the invention, the novel capacity adjusting mechanism comprising the check valve can realize capacity adjustment under the condition that the rotating speed of the compressor and/or the unloading of the scroll mechanism are/is not changed, and the scroll compressor has the advantages of simple structure, high reliability, quick response, easiness in installation and manufacture, suitability for a vertical compressor and a transverse compressor, good performance and wide application prospect.

Drawings

Features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

fig. 1 is an exploded perspective view of a capacity adjustment mechanism of a scroll compressor according to a first embodiment of the present disclosure;

FIG. 2 is a longitudinal cross-sectional view of a capacity modulating mechanism of a scroll compressor according to a first embodiment of the present disclosure;

fig. 3 is a partially cut-away perspective view of a non-orbiting scroll of a scroll compressor according to a first embodiment of the present disclosure;

FIG. 4 is a plan view of a valve plate of a check valve of a capacity modulating mechanism of a scroll compressor according to a first embodiment of the present disclosure;

FIG. 5 is an exploded perspective view of a capacity adjustment mechanism of a scroll compressor according to a second embodiment of the present disclosure;

FIG. 6 is a top view of a capacity modulating mechanism of a scroll compressor according to a second embodiment of the present disclosure, with a cover plate removed;

FIG. 7 is a bottom view of a non-orbiting scroll of a scroll compressor according to a second embodiment of the present disclosure;

FIGS. 8a and 8b are longitudinal cross-sectional views, in different directions, of a non-orbiting scroll of a scroll compressor according to a second embodiment of the present disclosure, showing a third passage in the non-orbiting scroll end plate connecting a seal chamber with a solenoid valve and a fourth passage connecting the solenoid valve with a second intermediate compression chamber of the scroll compressor, respectively;

FIG. 9 is an exploded perspective view of a capacity adjustment mechanism of a scroll compressor according to a third embodiment of the present disclosure;

FIG. 10 is a longitudinal cross-sectional view of a capacity modulating mechanism of a scroll compressor according to a third embodiment of the present disclosure;

FIG. 11 is a top plan view of a capacity modulating mechanism of a scroll compressor according to a third embodiment of the present disclosure with the floating seal of the back pressure chamber removed and with various passages and openings in the non-orbiting scroll end plate delineated in phantom lines in a perspective manner;

FIGS. 12a and 12b are partial longitudinal sectional views in different directions of a non-orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure, in which a check valve, a first passage, a second passage, and openings thereof are mainly illustrated;

fig. 13 is a partial perspective view of a non-orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure, in which a structure at a check valve mounting position is mainly shown;

FIG. 14 is a perspective view of a check valve of a capacity adjustment mechanism of a scroll compressor according to a third embodiment of the present disclosure;

fig. 15a and 15b are a perspective view and a longitudinal sectional view, respectively, of a check valve of a capacity adjustment mechanism of a scroll compressor according to a first modification of the present disclosure;

fig. 15c is a longitudinal sectional view of a check valve of a capacity adjustment mechanism of a scroll compressor according to a second modification of the present disclosure;

FIG. 16 is an exploded perspective view of a capacity adjustment mechanism of a scroll compressor according to a comparative example of the present disclosure;

FIG. 17 is a longitudinal cross-sectional view of a capacity modulating mechanism of a scroll compressor according to a comparative example of the present disclosure; and

FIG. 18 is an enlarged detail view of a seal chamber portion of the capacity adjustment mechanism of FIG. 17.

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.

The general structure of a scroll compressor, and particularly a capacity adjustment mechanism 100 of the scroll compressor, according to a first embodiment of the present disclosure is described below with reference to fig. 1. Generally, a scroll compressor includes a scroll mechanism, a motor, a rotary shaft, a main bearing housing, and a housing defining an inner space accommodating the above components. The interior space of the housing defines a suction pressure region and a discharge pressure region.

The scroll mechanism includes a non-orbiting scroll 120 and an orbiting scroll 110. The orbiting scroll 110 includes an orbiting scroll end plate and an orbiting scroll blade formed at one side of the orbiting scroll end plate. As shown in fig. 2, the non-orbiting scroll 110 includes a non-orbiting scroll end plate 122 and a non-orbiting scroll blade 124 extending from one side (first side) of the non-orbiting scroll end plate 122. The non-orbiting scroll blade 124 and the orbiting scroll blade are engageable with each other such that a series of compression chambers (including a central compression chamber and an intermediate compression chamber) are formed between the non-orbiting scroll blade 124 and the orbiting scroll blade when the scroll compressor is operating. The motor is configured to rotate a rotary shaft that drives the orbiting scroll 110 in an orbiting motion relative to the non-orbiting scroll 120 (i.e., the central axis of the orbiting scroll orbits the central axis of the non-orbiting scroll, but the orbiting scroll does not rotate about its central axis), and the working fluid enters the scroll mechanism from a suction pressure region, is compressed by a series of compression chambers, is discharged from a discharge port 129 in the center of the non-orbiting scroll end plate 122, and is discharged to a discharge pressure region.

To achieve capacity modulation of the compressor, the scroll compressor further includes a capacity modulation mechanism 100 located generally on the opposite side (second side) of the non-orbiting scroll end plate 122 from the non-orbiting scroll vanes 124. The capacity adjusting mechanism 100 mainly includes a solenoid valve 170, a check valve 150, a packing 160, a cover plate 130, and a fixing member 180. The packing 160 and the cover plate 130 are sequentially mounted and fixed to the second side of the non-orbiting scroll end plate 122 by sequentially passing the fixing member 180 through the mounting hole 180 on the cover plate 130 and the mounting hole 180 on the packing 160 and inserting into the mounting hole 181 on the non-orbiting scroll end plate 122, thereby forming a sealed chamber C1 between the non-orbiting scroll 120 and the cover plate 130. The check valve 150 is disposed in the sealed chamber C1, and the operation fluid is allowed to flow from at least one first intermediate compression chamber of the scroll mechanism to the suction pressure region through the sealed chamber C1 in a single direction by opening and closing the check valve 150, so that a partial parting line of the scroll does not participate in compression, thereby achieving the purpose of capacity modulation.

Specifically, referring to fig. 2, the substantially circular cover plate 130 includes a cover plate end plate 133, and a cover plate hub portion 132 and a cover plate peripheral portion 134 formed on one side (first side) of the cover plate end plate 133. A cover plate hub 132 is centrally located on the cover plate 130, and a cover plate peripheral edge 134 is coaxially disposed about the cover plate hub 132 to form an annular cavity 131 between the cover plate hub 132 and the cover plate peripheral edge 134. The floating seal 140 is disposed on a first side of the cover plate 130 to cooperate with the annular recess 131 to form the back pressure chamber C2. The non-orbiting scroll end plate 122 is formed with a non-orbiting scroll hub 128 surrounding a discharge port 129 at a second side of the non-orbiting scroll end plate 122, the non-orbiting scroll hub 128 defining a non-orbiting scroll central discharge passage C0 communicating with the discharge port 129 for guiding the compressed working fluid to a discharge pressure region. The non-orbiting scroll end plate 122 is also formed with a generally annular recess 126 around a hub 128 on a second side thereof. By fixing the cover plate end plate 133 to the second side of the non-orbiting scroll end plate 122 and inserting the packing 160 corresponding to the shape of the surface of the second side of the non-orbiting scroll end plate 122 between the cover plate end plate 133 and the non-orbiting scroll end plate 122, a substantially annular seal cavity C1, which is defined by the recess 126 and the cover plate end plate 133 in common and sealed by the packing 160, can be formed between the cover plate end plate 133 and the non-orbiting scroll end plate 122.

It will be appreciated by those skilled in the art that although the sealed chamber C1 is shown in the drawings as being formed by the cover plate 130 covering the recessed portion 126 of the non-orbiting scroll end plate 122, the sealed chamber C1 may be formed by a recessed portion of the other side (second side) of the cover plate end plate 133 opposite to the cover plate hub portion 132, or by a recessed portion of the cover plate end plate 133 and a recessed portion of the non-orbiting scroll end plate 122 together.

Referring to fig. 2 and 3, a first passage 121 and a second passage 123 are formed in the non-orbiting scroll end plate 122. An opening of one end of the first passage 121 is disposed in at least one first intermediate compression chamber of the scroll mechanism, and a first opening 1211 of the other end is disposed in the sealed chamber C1, thereby enabling fluid communication between the at least one first intermediate compression chamber and the sealed chamber C1. The second opening 1231 of one end of the second passage 123 is provided in the sealed chamber C1 and the opening of the other end is provided at the outer surface of the non-orbiting scroll end plate 122, thereby enabling fluid communication of the sealed chamber C1 with the suction pressure region outside the non-orbiting scroll 120. As shown in fig. 2, the first channel 121 may be configured as a straight channel extending in the axial direction, and the second channel 123 may be configured as a bent channel having a section extending in the axial direction and a section extending in the radial direction. Additionally, the first passage may also be configured to be formed jointly by two eccentric orifice segments (see fig. 12b, the first passage 321 being formed by the joint of the eccentric first and second orifice segments 3215, 3213) so that the intermediate compression pockets, which are closer to the radially inner side of the scroll, can communicate with the seal pocket, thereby enlarging the range of capacity modulation.

The first opening 1211 of the first passage 121 is formed on the bottom surface of the sealed chamber C1 adjacent to the second opening 1231 of the second passage 123, and the valve sheet 151 of the check valve 150 can cover both the first opening 1211 and the second opening 1231, thereby forming a more compact structure. In addition, as shown in fig. 2 and 3, a boss 1221 extending in an axial direction from the bottom surface of the sealed cavity C1 may be further formed around the first opening 1211 and the second opening 1231, and the first opening 1211 and the second opening 1231 are formed on the top surface of the boss 1211. When the check valve 150 is closed, the valve plate 151 of the check valve abuts against the top surface of the boss 1221, thereby closing the first and

second openings

1211 and 1231. The design of the boss enables more installation space to be obtained than when the first opening 1211 and the second opening 1231 are directly formed on the bottom surface of the sealed chamber C1, so that the check valve is more easily fitted to the opening of the passage, and the working fluid is more easily discharged out of the scroll mechanism through the first passage and the second passage.

In addition, a third passage 125 is also formed in the non-orbiting scroll end plate 122. The third passage 125 may be configured to extend substantially in a radial direction, and an opening of one end thereof is disposed in the seal chamber C1 and the other end thereof communicates with the solenoid valve 170 disposed on the outer circumferential side of the non-orbiting scroll 120. The solenoid valve 170 has a control passage therein capable of communicating with a suction pressure region of the compressor. The third passage 125 can selectively communicate the sealed chamber C1 and the suction pressure region via the solenoid valve 170 (control passage) by switching of the solenoid valve 170. Further, a port 127 communicating the fixed scroll center discharge passage C0 and the seal chamber C1 is formed in the boss portion 128 of the fixed scroll 120.

A capacity adjusting process of the scroll compressor will be described with reference to fig. 2. When the scroll compressor is in a full-capacity working condition, the electromagnetic valve 170 is closed, the third channel 125 cannot communicate the sealed cavity C1 with a suction pressure area of the compressor through the control channel in the electromagnetic valve 170 and is in a closed state, the sealed cavity C1 is communicated with the fixed scroll central exhaust channel C0 through the duct 127, part of the high-pressure working fluid enters the sealed cavity C1 from the fixed scroll central exhaust channel C0 through the duct 127, therefore, the pressure in the sealed cavity C1 is approximately equal to the pressure in the fixed scroll central exhaust channel C0, and the sealed cavity C1 is in a high-pressure state. At this time, since the pressure in the non-orbiting scroll central discharge passage C0 is greater than the pressure of the middle compression chamber of the scroll member and is greater than the pressure of the suction pressure region, the pressure above the valve plate 151 of the check valve (which may correspond to the pressure of the working fluid in the sealing chamber C1 acting on the valve plate) is greater than the pressure below the valve plate 151 (which may correspond to the pressure of the working fluid in the first and

second passages

121 and 123 acting on the valve plate), and the valve plate 151 is pressed against the first and

second openings

1211 and 1231 by the pressure difference to simultaneously seal both the first and

second openings

1211 and 1231. The check valve 150 closes the first and

second passages

121 and 123, and the working fluid in the first intermediate compression chamber cannot be discharged to the outside of the scroll mechanism through the first and

second passages

121 and 123, and thus the scroll compressor operates at full capacity.

When the scroll compressor is in a partial-capacity working condition, the solenoid valve 170 is opened, the third channel 125 communicates the sealed chamber C1 with the suction pressure area of the compressor through the control channel in the solenoid valve 170 to be in an open state, and the high-pressure working fluid in the sealed chamber C1 is discharged to the suction pressure area of the compressor through the third channel 125 and the control channel in the solenoid valve, so that the pressure in the sealed chamber C1 is rapidly reduced and can be approximately equal to the pressure in the suction pressure area. At this time, the pressure above the valve sheet 151 of the check valve is lower than the pressure below the valve sheet 151, and thus the valve sheet 151 is lifted up by the pressure difference while leaving the first and

second openings

1211 and 1231. The check valve 150 opens the first and

second passages

121 and 123, and the working fluid in the first intermediate compression chamber communicating with the first passage 121 is discharged from the discharge port 129 without being gradually compressed to the center of the scroll mechanism, but is discharged to the suction pressure region outside the scroll mechanism via the first passage 121, the seal chamber C1, and the second passage 123. That is, the scroll line portion corresponding to the first intermediate compression chamber and the leading portion of the scroll line portion thereof no longer participate in compression and the scroll compressor thus operates at partial capacity.

It should be noted that the cross-sectional area of the third passage 125 should be larger than the cross-sectional area of the orifice 127 for the purpose of rapidly reducing the pressure in the capsule C1 under partial-volume conditions. In addition, in order to reduce the leakage of the high-pressure working fluid in the non-orbiting scroll central exhaust passage C0 through the orifice 127 under the partial capacity condition, the diameter of the orifice 127 may be set as small as possible, preferably less than 1mm. Additionally, a resistance device is preferably provided at the orifice 127 to further reduce the leakage rate of the high pressure working fluid.

It will be appreciated by those skilled in the art that two sets of first and second passages may be formed in the non-orbiting scroll end plate symmetrically disposed on either side of the non-orbiting scroll axis, and two check valves 150 may be provided within the sealed chamber C1 to cover the openings of the two sets of passages, respectively, to balance the scroll mechanism in both partial capacity and full capacity conditions.

Further, preferably, referring to fig. 1 and 4, in the present disclosure, the check valve 150 includes a valve plate 151 configured in the form of an elongated cantilever beam and a flapper (fig. 14). The first end portion of the valve sheet 151 is formed as a mounting portion provided with a sheet mounting hole 1512, and a fixing member such as a bolt passes through the baffle and through the sheet mounting hole 1512 to fix the check valve 150 to the bottom surface of the sealing chamber C1. The second end portion of the valve sheet 151 is formed as a cover portion 1511, and the mounting portion of the valve sheet 151 and the cover portion 1511 (i.e., the first end portion and the second end portion) are connected by a connection portion 1513. The cover portion 1511 is configured in a size sufficient to cover the first opening 1211 and the second opening 1231 at the same time. Due to the valve plate design in the form of the long cantilever beam, the check valve 150 has small opening resistance and can be opened sensitively in response to pressure change, so that smooth switching from a full-capacity working condition to a partial-capacity working condition is ensured.

The advantage of the first embodiment according to the present disclosure is explained below by comparing with the capacity adjustment mechanism of the scroll compressor of the comparative example shown in fig. 16, 17, and 18. In the comparative example, the main components, the installation manner, and the operation principle of the scroll compressor are similar to those of the first embodiment of the present disclosure, and thus, the description thereof is omitted.

Referring to fig. 16 and 17, the scroll compressor according to the comparative example includes a scroll member composed of a non-orbiting scroll 20 and an orbiting scroll 10, the orbiting scroll 10 including an orbiting scroll end plate and an orbiting scroll blade formed at one side of the orbiting scroll end plate, the non-orbiting scroll 20 including a non-orbiting scroll end plate 22, a non-orbiting scroll blade 24 extending from one side (first side) of the non-orbiting scroll end plate 22, and a non-orbiting scroll hub 28 extending from the other side (second side) of the non-orbiting scroll end plate 22. The non-orbiting and orbiting

scroll blades

24 and 24 are engageable with each other such that a series of compression chambers (including a central compression chamber and an intermediate compression chamber) are formed between the non-orbiting and orbiting

scroll blades

24 and 24 when the scroll compressor is operating. The working fluid is progressively compressed from the radially outer side of the scroll member to the centre via a series of compression chambers and is discharged from a discharge port 29 at the centre of the non-orbiting scroll end plate 22 and finally discharged to the discharge pressure region of the scroll compressor through a non-orbiting scroll central discharge passage C0' surrounded by a non-orbiting scroll hub 28 in communication with the discharge port 29.

The scroll compressor according to the comparative example further includes a capacity condition mechanism 100' disposed on the side (second side) of the non-orbiting scroll end plate 22 opposite to the non-orbiting scroll blade 24. The capacity adjustment mechanism 100' basically includes a solenoid valve 70, a spacer plate 30, a U-shaped seal 60, an annular ring 50 and an inner seal 80. The spacer plate 30, U-seal 60, annular ring 50 and inner seal 80 are in turn mounted to the second side of the non-orbiting scroll end plate 22 and form a coaxial arrangement therewith about the non-orbiting scroll hub 28. Referring to fig. 18, the annular ring 50 includes an inner diameter portion 51 located radially inward and an outer diameter portion 52 located radially outward, wherein the inner diameter portion 51 extends substantially radially and is capable of contacting a surface of the second side of the non-orbiting scroll end plate 22 (shown as an upper surface of the non-orbiting scroll end plate 22 in fig. 17), and the outer diameter portion 52 is formed as a recess that is recessed in comparison with the inner diameter portion 51 in a direction axially away from the non-orbiting scroll end plate 22. The spacer plate 30 is disposed at the opening of the recess formed by the outer diameter 52 and the U-shaped seal 60 is disposed between the spacer plate 30 and the outer diameter 52, thereby forming the seal cavity 26 in the recess of the outer diameter 52. In addition, referring to fig. 17, the outer diameter portion 52 is further formed with a flange portion 53 extending toward a direction axially facing away from the non-orbiting scroll end plate 22, and an annular space for accommodating the floating seal 40 is formed between the flange portion 53 and the non-orbiting scroll hub 28, so that a back pressure chamber 31 collectively enclosed by the floating seal 40, the outer diameter portion 52 of the annular ring 50, the inner diameter portion 51 of the annular ring 50, and the non-orbiting scroll hub 28 is formed between the annular ring 50 and the non-orbiting scroll hub 28. Wherein the inner seal 80 is disposed between the inner diameter portion 51 within the back pressure chamber 31 and the non-orbiting scroll hub 28 to seal the back pressure chamber 31. The back pressure chamber 31 communicates through a through hole formed in the non-orbiting scroll 20 (non-orbiting scroll end plate 22 and/or non-orbiting scroll hub 28) to at least one intermediate compression chamber in the series of compression chambers.

The non-orbiting scroll end plate 22 includes a first passage 21 communicating with at least one intermediate compression chamber C in the series of compression chambers. The intermediate compression chamber C is located radially outward of the fixed scroll than the intermediate compression chamber communicating with the back pressure chamber 31. The solenoid valve 70, which is additionally disposed on the outer peripheral side of the non-orbiting scroll 20, can also selectively fluidly communicate the seal chamber 26 with the back pressure chamber 31 or fluidly communicate the seal chamber 26 with the suction pressure region (a passage for communication is not shown in the drawing). When the solenoid valve 70 controls the seal cavity 26 to communicate with the suction pressure region, the pressure in the seal cavity 26 is lower than the outside pressure of the annular ring 50 (which may correspond to the pressure of the working fluid in the back pressure cavity 31 and the working fluid in the suction pressure region acting together on the annular ring 50), and under the action of the inside-outside pressure difference, the annular ring 50 moves axially toward the non-orbiting scroll end plate 22, so that the bottom surface 511 of the inner diameter portion 51 of the annular ring 50 is pressed against the opening 211 of the first passage 21 on the second side of the non-orbiting scroll end plate 22 to form a seal, thereby closing the first passage 21. At this time, the working fluid in the intermediate compression chamber C cannot flow out, and the scroll compressor operates in a full capacity state. When the solenoid valve 70 controls the seal chamber 26 to communicate with the back pressure chamber 31, the pressure of the seal chamber 26 is greater than the pressure outside the annular ring 50, and the annular ring 50 moves in the axial direction toward the direction away from the non-orbiting scroll end plate 22 by the difference in the inside and outside pressures, so that the bottom surface 511 of the inner diameter portion 51 of the annular ring 50 is away from the opening 211 of the first passage 21, thereby opening the first passage 21. At this time, the working fluid in the intermediate compression chamber C is discharged to the suction pressure region through the first passage 21 and the opening 211 thereof. At this time, the scroll line portion corresponding to the intermediate compression chamber C and the front portion thereof are no longer involved in compression, and the scroll compressor is thus operated in a partial capacity state.

The capacity adjustment mechanism 100' in the comparative example includes more components such as the annular ring 50, which is complicated in structure and high in cost, compared to the first embodiment of the present disclosure; the capacity adjusting mechanism 100' comprises a plurality of sealing elements such as a U-shaped sealing element 60 and an inner sealing element 80, sealing needs to be formed on a plurality of surfaces, and the annular ring 50 moves along the axial direction under the action of pressure difference, so that a plurality of sealing elements including the U-shaped sealing element 60 and the inner sealing element 80 are moving friction pairs, are easy to leak and have low reliability; in addition, the components of the capacity adjustment mechanism 100' are mounted around the non-orbiting scroll hub 28 and require a certain axial mounting space, whereby the non-orbiting scroll hub 28 needs to be manufactured to have a large axial length, which also causes a difficulty in casting the non-orbiting scroll.

The volume adjusting mechanism 100 according to the first embodiment of the present disclosure controls whether the first intermediate compression chamber is communicated with the suction pressure region or not mainly through the check valve 150, so that the structure is simpler and the manufacturing cost is low; since no moving parts such as the annular ring 150 are required, the use of several seals, in particular moving friction pairs, is omitted, wherein only the static sealing surface of the check valve 150 is present, reducing the risk of leakage and increasing reliability; in addition, the casting difficulty of the fixed vortex is reduced, and the installation is easier. According to the capacity adjusting mechanism disclosed by the invention, the capacity adjusting mechanism not only can be used for a vertical scroll compressor as shown in the figure, but also can be applied to a horizontal scroll compressor, and has the advantages of wide application range and good adaptability; it is particularly important that, in this disclosure, the valve plate of the check valve 150 covers both the first opening and the second opening, and compared with the technical solution that the valve plate only covers the first opening and the second opening is disposed outside the valve plate, since the suction pressure is always maintained below the valve plate, it is more beneficial to the sealing of the valve plate. Compared with the technical scheme that the second opening is arranged outside the valve plate and is always exposed, in the technical scheme of the disclosure, when the full-capacity working condition is adopted, high pressure is kept in the sealing cavity C1, high-pressure fluid in the sealing cavity C1 cannot leak through the second opening, and the performance of the compressor is improved; or compare in the second opening setting outside the valve block and be provided with the technical scheme of extra seal part, in the technical scheme of this disclosure, saved extra the second passageway and carry out the overall arrangement sealed to its second opening, adopt same valve block to seal first opening and second opening both, further simplified the structure, reduced production and installation cost.

Fig. 5 shows an overall structure of a scroll compressor, and particularly, a capacity adjusting mechanism 200 of the scroll compressor according to a second embodiment of the present disclosure. In the second embodiment, the main components, the installation manner and the operation principle of the scroll compressor are similar to those of the first embodiment of the present disclosure, and thus, the detailed description thereof is omitted.

As shown in fig. 5, in the second embodiment, the scroll compressor includes a scroll mechanism composed of an orbiting scroll 210 and a non-orbiting scroll 220, and a capacity adjustment mechanism 200 located on the opposite side of the non-orbiting scroll 220 from the orbiting scroll 210. The capacity adjustment mechanism 200 mainly includes a solenoid valve 270, a check valve 250, a packing 260, a cover plate 230, and a fixing member 280 (floating seal not shown). Liner 260 and cover plate 230 are sequentially mounted to non-orbiting scroll 220 by inserting a fixing member 280 through a mounting hole on cover plate 230, a mounting hole 282 on liner 260, and a mounting hole 281 on the non-orbiting scroll end plate in that order.

Referring to fig. 5 and 6, the end plate of the non-orbiting scroll 220 is formed at a side (second side) thereof opposite to the non-orbiting scroll blades with a non-orbiting scroll hub 228 surrounding an exhaust port 229 at the center of the non-orbiting scroll 220, the non-orbiting scroll hub 228 defining a non-orbiting scroll center exhaust passage C0 communicating with the exhaust port 229 for guiding the compressed working fluid to an exhaust pressure region. Non-orbiting scroll end plate 122 is also formed with a generally annular recess 226 on a second side thereof surrounding a non-orbiting scroll hub 228. By securing cover plate 230 to the second side of the non-orbiting scroll end plate and inserting gasket 260 between cover plate 230 and non-orbiting scroll 220, a sealed cavity C1 (shown in fig. 8a and 8 b) defined collectively by recess 226 and cover plate 230 and sealed by gasket 260 can be formed between cover plate 230 and non-orbiting scroll end plate 230. Referring to fig. 6 and 7, a first passage 221 capable of communicating at least one first intermediate compression chamber of a series of compression chambers with the hermetic chamber C1 and a second passage (not shown in the drawings) communicating the hermetic chamber C1 with a suction pressure region of the compressor are formed on the non-orbiting scroll end plate, and a check valve 250 can simultaneously cover an opening of the first passage 221 in the hermetic chamber C1 and an opening of the second passage in the hermetic chamber C1, thereby synchronously opening or closing the first passage 221 and the second passage. The arrangement of the first passage, the second passage and the check valve is similar to that of the first embodiment, and thus, the description thereof is omitted. Although the floating seal and the back pressure chamber it is configured with are not shown in the figures, fig. 6 and 7 show a back pressure port 242 for communicating with some intermediate compression chamber to maintain the intermediate pressure of the back pressure chamber, the back pressure port 242 may extend axially through the non-orbiting scroll end plate and non-orbiting scroll hub 228 to the back pressure chamber above the cover plate 230.

Unlike the first embodiment, the scroll compressor according to the second embodiment of the present disclosure omits a port that communicates the fixed scroll central discharge passage C0 with the hermetic chamber C1, and introduces high or intermediate pressure from the central compression chamber or the second intermediate compression chamber to the hermetic chamber C1 to open and close the check valve 250.

Referring to fig. 8a and 8b, third and

fourth passages

2251 and 2252 are also formed in the end plate of the non-orbiting scroll 220. The third passage 2251 may be configured to extend in a radial direction, or may be formed by two ducts connected to each other extending in an axial direction and extending in a radial direction. An opening at one end of the first passage 2251 is provided in the seal chamber C1, and an opening at the other end communicates with the solenoid valve 270 on the outer peripheral side where the fixed scroll 220 is provided. The fourth passage 2252 may be configured to include an axially extending orifice 244 and a radially extending orifice connected to the orifice 244. An opening at one end of the fourth passage 2252 is provided in one of the second intermediate or central compression chambers (i.e., the port 244 communicates with one of the second intermediate or central compression chambers) and an opening at the other end communicates with the solenoid valve 270. In addition, in order to ensure moderate pressure in the sealed chamber C1 during operation of the capacity adjustment mechanism 200, facilitating closing of the solenoid valve 270, the second intermediate compression chamber communicating with the port 244 may be closer to the center of the non-orbiting scroll than the first intermediate compression chamber communicating with the first passage 221, i.e., the second intermediate compression chamber communicating with the port 244 may have a higher pressure than the first intermediate compression chamber communicating with the first passage 221. The solenoid valve 270 has a control passage therein which can communicate with a suction pressure region of the compressor or with the fourth passage 2252. By switching of the solenoid valve 270, the third passage 2251 can communicate the hermetic chamber C1 with the suction pressure zone via the solenoid valve 270 (control passage), or communicate the hermetic chamber C1 with the second intermediate compression chamber or the central compression chamber via the solenoid valve 270 (control passage) and the fourth passage 2252. The solenoid valve 270 is configured as a two-position three-way valve, that is, when the solenoid valve 270 is switched to a state in which the third passage 2251 communicates with the suction pressure zone, the fourth passage 2252 is in a closed state; when the solenoid valve 270 is switched to a state in which the third passage 2251 communicates with the fourth passage 2252, neither the third passage 2251 nor the fourth passage 2252 communicates with the suction pressure zone.

Specifically, when the scroll compressor is in the full capacity condition, the solenoid valve 270 is switched to communicate the third passage 2251 with the fourth passage 2252, and a portion of the working fluid in the central or second intermediate compression chamber enters the fourth passage 2252 from the opening of the bore 244 and flows into the capsule C1 through the control passage and the third passage 2251 in the solenoid valve 270, so that the pressure in the capsule C1 is substantially equal to the pressure in the central or second intermediate compression chamber, and the capsule C1 is in a high or medium pressure state. At this time, the pressure above the valve sheet of the check valve 250 (which may correspond to the pressure of the working fluid of the sealing chamber C1 acting on the valve sheet) is greater than the pressure below the valve sheet (which may correspond to the pressure of the working fluid in the first passage 221 and the second passage acting on the valve sheet), and the valve sheet is pressed against the openings of the first passage 221 and the second passage to simultaneously seal the two openings by the pressure difference. The check valve closes the first passage 221 and the second passage, and the working fluid in the first intermediate compression chamber cannot be discharged to the outside of the scroll mechanism through the first passage 221 and the second passage, and thus the scroll compressor operates at full capacity.

When the scroll compressor is in a partial capacity condition, the solenoid valve 270 is switched to communicate the third passage 2251 with the suction pressure zone, and the high-pressure or medium-pressure working fluid in the sealed chamber C1 is discharged to the suction pressure zone of the compressor via the third passage 2251 and the control passage in the solenoid valve 270, resulting in a rapid decrease in the pressure in the sealed chamber C1, which may be approximately equal to the pressure in the suction pressure zone. At this time, the pressure above the valve sheet of the check valve 250 is smaller than the pressure below the valve sheet, so the valve sheet is lifted up by the pressure difference while leaving the openings of the first and

second passages

221 and 221. The check valve 250 opens the first passage 221 and the second passage, and the working fluid in the first intermediate compression chamber communicating with the first passage 221 is discharged from the discharge port 229 without being gradually compressed to the center of the scroll mechanism, but is discharged to the outside of the scroll mechanism via the first passage 221, the seal chamber C1, and the second passage. That is, the scroll line portion corresponding to the first intermediate compression chamber and the front portion of the scroll line portion thereof are no longer involved in compression, and the scroll compressor thus operates at partial capacity.

The second embodiment according to the present disclosure not only has advantages similar to those of the first embodiment, such as simpler structure of the capacity adjustment mechanism, easier manufacturing and installation, low manufacturing cost, high reliability, etc., but also further improves the performance of the compressor because the fourth passage communicating with the second intermediate compression chamber or the central compression chamber is in a closed state when the hermetic chamber C1 communicates with the suction pressure region via the solenoid valve, and thus the working fluid in the second intermediate compression chamber or the central compression chamber does not unnecessarily leak via the solenoid valve.

Fig. 9 shows an overall structure of a scroll compressor, and particularly, a capacity adjusting mechanism 300 of the scroll compressor according to a third embodiment of the present disclosure. In the third embodiment, the main components, the installation manner, and the operation principle of the scroll compressor are similar to those of the first embodiment of the present disclosure, and thus, the description thereof is omitted.

As shown in fig. 9, in the third embodiment, a scroll compressor includes a scroll mechanism composed of an orbiting scroll 310 and a non-orbiting scroll 320, and a capacity adjustment mechanism 300 located on the opposite side of the non-orbiting scroll 320 from the orbiting scroll 310. The capacity adjustment mechanism 300 mainly includes a solenoid valve 370, a check valve 350, a packing 360, a seal-dividing plate 330, and a fixing member 380. The packing 360 and the seal partition plate 330 are sequentially mounted to the non-orbiting scroll 320 by sequentially inserting the fixing member 380 through the mounting hole 383 on the seal partition plate 330, the mounting hole 382 on the packing 360, and the mounting hole 381 on the non-orbiting scroll end plate.

Unlike the first embodiment, the sealing chamber C1 of the capacity adjustment device of the scroll compressor according to the third embodiment of the present disclosure is embedded below the back pressure chamber C2 in the axial direction. Referring to fig. 10, non-orbiting scroll end plate 322 is formed with a non-orbiting scroll hub 328 surrounding the center exhaust port on the side (second side) of non-orbiting scroll end plate 322 opposite non-orbiting scroll blades 324, and non-orbiting scroll end plate 322 is further formed with a generally annular recess 326 surrounding hub 328 on the second side thereof. The bottom of the recess 326 is further recessed to form a sunken recess 327 for constructing the seal chamber C1. The sinking recess 327 is configured in a shape corresponding to the shape of the check valve 350. A stepped portion 331 for supporting the packing 360 and the seal spacer 330 is formed at the junction of the subsidence recess 327 and the recess 326. After the gasket 360 and the seal spacer 330 are mounted in place at the stepped portion 331, the gasket 360 and the seal spacer 330 cover the depressed recess portion 327 to define a seal chamber C1 together with the depressed recess portion 327. The floating seal 340, when installed in the recess 326, cooperates with the recess 326 and the seal spacer 330 to define a back pressure chamber C2. Thus, in the third embodiment, the back pressure chamber C2 and the seal chamber C1 are integrally formed in the non-orbiting scroll end plate 322, the seal chamber C1 is closer to the non-orbiting scroll blade 324, and the back pressure chamber C2 is farther from the non-orbiting scroll blade 324. In addition, in the third embodiment, the seal partition plate 330 and the packing 360 are configured in a shape and size matching those of the depressed recess 327, so as to be fitted to the stepped portion 331 from inside the recess 326 to form the seal cavity C1.

In the third embodiment according to the present disclosure, due to the integrated design of the seal chamber C1 and the back pressure chamber C2, the seal chamber C1 is formed below the back pressure chamber C2 in the axial direction, which not only further simplifies the structure, makes manufacturing and installation easier, but also further improves reliability.

Referring to fig. 11, in the third embodiment, the number of the sealing chambers C1 is two corresponding to the number of the check valves 350. The two sealed chambers C1 are respectively provided on both sides of the axis of the non-orbiting scroll, and may communicate through a channel 3226 formed at the bottom of the recess 326 of the non-orbiting scroll end plate 322. The two sealed chambers C1 and the channel 3226 connecting the two sealed chambers C1 are isolated from the back pressure chamber C2 by the seal spacer 330 and the gasket 360. Thus, by one solenoid valve 370, the third passage 3251 communicating the solenoid valve 370 with the hermetic chamber C1, and the fourth passage 3252 communicating one second intermediate compression chamber or the central compression chamber with the solenoid valve 370, it is possible to simultaneously perform pressure control of the two hermetic chambers C1, thereby synchronously opening or closing the check valves 350 respectively located in the two hermetic chambers C1. When the check valve 350 is opened, a first intermediate compression chamber of the series of compression chambers can enter the seal chamber C1 through the first passage 321 provided in the non-orbiting scroll end plate 322 and be discharged to the outside of the scroll mechanism through the second passage 323. The third channel 3251 and the fourth channel 3252 and their related configurations are similar to the third channel 2251 and the fourth channel 2252 in the second embodiment, and the first channel 321 and the second channel 323 and their related configurations are similar to the first channel 121 and the second channel 123 in the first embodiment, and are not described again here.

When the scroll compressor is in the full capacity operating mode, the solenoid valve 370 is switched to communicate the third channel 3251 with the fourth channel 3252, and part of the working fluid in the central or second intermediate compression cavity flows into the sealed cavity C1 through the fourth channel 3252 and through the control channel in the solenoid valve 370 and the third channel 3251, so that the pressure in the sealed cavity C1 is substantially equal to that of the central or second intermediate compression cavity, and the sealed cavity C1 is in a high-pressure or medium-pressure state. At this time, the pressure above the valve plate (which may correspond to the pressure of the working fluid in the sealing chamber C1 acting on the valve plate) of the check valve 350 is greater than the pressure below the valve plate (which may correspond to the pressure of the working fluid in the first channel 321 and the second channel 323 acting on the valve plate), and under the action of the pressure difference, the valve plate is pressed against the first opening 3211 in the sealing chamber C1 of the first channel 321 and the second opening 3231 in the sealing chamber C1 of the second channel 323 to simultaneously seal the first opening 3211 and the second opening 3231. The check valve closes the first and

second passages

321 and 323, and the working fluid in the first intermediate compression chamber cannot be discharged to the outside of the scroll mechanism through the first and

second passages

321 and 323, and thus the scroll compressor operates at full capacity.

When the scroll compressor is in a partial-capacity condition, the solenoid valve 370 is switched to communicate the third channel 3251 with the suction pressure region, and the high-pressure or medium-pressure working fluid in the sealed cavity C1 is discharged to the suction pressure region of the compressor through the third channel 3251 and the control channel in the solenoid valve 370, resulting in a rapid decrease in the pressure in the sealed cavity C1, which may be substantially equal to the pressure in the suction pressure region. At this time, the pressure above the valve plate of the check valve 350 is smaller than the pressure below the valve plate, so the valve plate is lifted up by the pressure difference and simultaneously leaves the first opening 3211 and the second opening 3231. The check valve 350 opens the first and

second passages

321 and 323, and the working fluid in the first intermediate compression chamber communicating with the first passage 321 is discharged from the discharge port 329 without being gradually compressed to the center of the scroll mechanism, but is discharged to the outside of the scroll mechanism via the first passage 321, the seal chamber C1, and the second passage 323. That is, the scroll line portion corresponding to the first intermediate compression chamber communicating with the first passage 321 and the front portion thereof are not involved in compression any more, and thus the scroll compressor operates at a partial capacity.

Additionally, as shown in fig. 12b, the first passage 321 includes a first tunnel segment 3215 and a second tunnel segment 3213 that are eccentrically disposed from one another. The first tunnel segment 3215 has a first opening 3211 disposed in the capsule C1 at one end and a second tunnel segment 3213 at the other end. The second bore segment 3213 is connected at one end to the first bore segment 3215 and at the other end to the first intermediate compression chamber. As shown in fig. 12a, the second duct segment 3213 may be configured as a plurality of juxtaposed apertures, preferably distributed generally along the scroll line, and the first duct segment 3215 may be configured as an elongated aperture extending generally along the scroll line. The second opening 3231 may be disposed radially outward of the first opening 3211 such that the first and

second openings

3211, 3231 are more compactly disposed below the flap of the check valve 350. Through such a structural design, under a partial-capacity working condition, the working fluid of the first intermediate compression chamber can more and more rapidly flow to the suction pressure region through the first opening 3211 and the second opening 3231, and the fluid flow is smoother and easier.

Preferably, referring to fig. 13, a sinking groove 3212 communicating with the second opening 3231 but spaced apart from the first opening 3211 is further formed between the second opening 3231 and the first opening 3211. The undercut 3212 may be formed in a racetrack-like shape surrounding the first opening 3211, and the depth of the undercut 3212 is preferably 0.5mm to 1mm. A spaced sealing surface 3213 formed by the bottom of the sunken recess 327 (the seal cavity C1) surrounding the first opening 3211 is formed between the sunken groove 3212 and the first opening 3211. When the check valve 350 is closed, the valve plate 351 covers the first opening 3211 and the second opening 3231, and the bottom surface of the valve plate 351 contacts the spaced sealing surface 3213 and the sealing surfaces formed by the bottom of the sunken recess 327 (the sealing cavity C1) at the outer peripheries of the second opening 3231 and the sunken groove 3212, thereby forming a seal with the first opening 3211 and the second opening 3231. The sink groove 3212 reduces the area of the sealing surface, so that the specific sealing pressure of the valve plate is increased, the sealing effect of the valve plate is better, and the valve plate is less prone to leakage; on the other hand, because heavy groove 3212 and second opening 3231 communicate, that is to say can keep the pressure unanimous with the suction pressure district throughout in the heavy groove 3212, under full capacity operating mode, the design of heavy groove 3212 makes the pressure of valve block 351 below lower, more be close to suction pressure to the upper and lower pressure differential of valve block 351 has been increased, the sealing performance of valve block has been improved.

Preferably, referring to fig. 14, the check valve 350 includes a valve plate 351 and a baffle 352 above the valve plate 351. One end of the valve sheet 351 and one end of the check plate 352 are each formed as a mounting portion provided with a mounting hole through which a fixing member such as a bolt 353 is inserted and a check valve mounting hole 3531 on the bottom surface of the seal chamber C1 through the valve sheet mounting hole, thereby fixing the check valve 350 in place. The other end of the valve sheet 351 is formed as a cover portion 3511 capable of simultaneously covering the first and

second apertures

3211 and 3231. The shutter 352 is also provided with a shutter through hole 3521 at a position corresponding to the covering portion 3511. When the partial-capacity operating mode is switched to the full-capacity operating mode, high-pressure or medium-pressure fluid enters the sealing cavity C1 through the fourth channel 3251 and the 3252 of the third tee, and due to the fact that the baffle 352 is provided with the baffle through hole 3521, the high-pressure or medium-pressure fluid can reach the position above the valve plate 351 more quickly and more easily, and the pressure above the valve plate 351 is increased more quickly in response to the switching of the operating mode, so that the valve plate 351 is closed more quickly. Therefore, the open hole design of the baffle 352 can reduce the valve plate closing response time and ensure the smooth switching from the partial capacity working condition to the full capacity working condition.

The second embodiment according to the present disclosure not only has advantages similar to those of the first and second embodiments, such as simpler structure of the capacity adjustment mechanism, easier manufacturing and installation, low manufacturing cost, no unnecessary leakage, high reliability, etc., but also further simplifies the structure and improves the reliability due to the integrated design of the seal cavity and the back pressure cavity. In addition, due to the design of the first opening, the second opening, the sinking groove and the opening of the check valve baffle, the sealing performance of the check valve is further improved, and the response time of the check valve is shortened.

It will be appreciated by those skilled in the art that although the check valves are shown as elongated cantilever beam structures in the first through third embodiments of the present disclosure, the check valves may be configured in other suitable structures as long as one-way flow, switching between partial-capacity and full-capacity conditions is satisfied. For example, fig. 15a, 15b, 15c show different check valve configurations. In the first modified example shown in fig. 15a, 15b, the check valve 450 is configured in a circular shape, and includes a valve mounting plate 454, a valve flapper 453, and a valve sheet 451 positioned in a space enclosed by the mounting plate 454 and the valve flapper 453. The valve mounting plate 454 is secured over first and second openings in the capsule C1, the valve mounting plate 454 having a valve mounting plate opening 4541 centrally located therein, the first and second openings being capable of fluid communication with the capsule C1 only through the valve mounting plate opening 4541. The valve flapper 453 has a plurality of openings, for example, a circular arc-shaped valve flapper first opening 4531 and a circular valve flapper second opening 4532, formed therein, which communicate with the seal chamber C1. The valve plate 451 is substantially circular in shape in conformity with the shape of the valve mounting plate opening 4541. When the seal chamber C1 is at a high pressure or a medium pressure, the valve plate 451 is moved downward by the pressure difference to press against the valve mounting plate 454, sealing the valve mounting plate opening 4541 of the valve mounting plate 454, thereby closing the first and second openings in the seal chamber C1; when the seal chamber C1 is at a low pressure, the valve plate 451 moves upward away from the valve mounting plate opening 4541 of the valve mounting plate 454 by the pressure difference, thereby opening the first and second openings in the seal chamber C1.

The check valve in the first modified example is more convenient to manufacture and install, and can be used particularly in combination with the design of the boss 1221 formed around the first opening and the second opening as shown in fig. 2 and 3, further reducing the production cost.

Fig. 15c shows a second modified example of the check valve, and similar to the first modified example, the check valve 550 configuration includes a valve mounting plate 554, a valve flapper 553, and a valve plate 551 that is located in a space enclosed by the valve mounting plate 554 and the valve flapper 553. In contrast, a guide portion 5533 extending toward the valve mounting plate 554 in the axial direction is formed at the center of the valve baffle 553. The valve sheet 551 is configured to include a peripheral portion 5511 extending in the axial direction and a bottom plate portion 5512 extending in the radial direction. The peripheral portion 5511 of the valve sheet 551 is fitted around the outer periphery of the guide portion 5533 and can slide relative to the guide portion 5533 in the axial direction, so that the valve sheet 551 can move up and down in the axial direction under the guidance of the guide portion 5533. When the sealed chamber C1 is at a high pressure or a medium pressure, the valve plate 551 moves downward by the pressure difference, the bottom plate portion 5512 of the valve plate 551 presses against the valve mounting plate 554, and the valve mounting plate opening 5541 of the valve mounting plate 554 is sealed, thereby closing the first opening and the second opening in the sealed chamber C1; when the seal chamber C1 is at a low pressure, the valve plate 551 moves upward away from the valve mounting plate opening 5541 of the valve mounting plate 554 by the pressure difference, thereby opening the first and second openings in the seal chamber C1. Compared with the first modified example in which the valve sheet 451 is freely moved between the valve mounting plate and the valve flapper, the movement and position of the valve sheet can be better controlled and the sealing performance of the valve sheet can be improved by the movement of the valve sheet 551 guided by the guide portion 5533 of the valve flapper 553.

It will also be appreciated by those skilled in the art that capacity modulation mechanisms according to the present disclosure can be combined with variable frequency technology to provide a larger maximum and minimum displacement wall for the compressor, to extend the range of variable frequency for the compressor, and to provide better performance and better lubrication conditions for the compressor when operating at partial capacity.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the specific embodiments described and illustrated in detail herein, and that various changes may be made to the exemplary embodiments by those skilled in the art without departing from the scope defined by the appended claims. It should also be understood that features of the various embodiments may be combined with each other or may be omitted without departing from the scope of the claims.

Claims

1. A scroll compressor, comprising:

an orbiting scroll (110, 210, 310) having a first end plate and a first scroll blade formed thereon;

a non-orbiting scroll (120, 220, 320) having a second end plate (122, 322) and a second scroll blade (124, 324) formed on a first side of the second end plate, the first and second scroll blades engaging each other to form a central compression chamber and a plurality of intermediate compression chambers between the orbiting and non-orbiting scrolls,

wherein the second end plate is formed with a first recess (126, 226, 327) configured as a sealed cavity (C1) at a second side opposite the first side, the second end plate further having formed therein a first passage (121, 221, 321) configured to selectively provide fluid communication between at least one first intermediate compression cavity of the plurality of intermediate compression cavities and the sealed cavity, and a second passage (123, 323) configured to selectively provide fluid communication between the sealed cavity and a suction pressure region of the scroll compressor,

the first channel comprises a first opening (1211, 3211) located in the sealing cavity, the second channel comprises a second opening (1231, 3231) located in the sealing cavity, a check valve (150, 250, 350) is arranged in the sealing cavity, and a valve plate (151, 351, 451, 551) of the check valve can simultaneously cover the first opening (1211, 3211) and the second opening (1231, 3231) so as to synchronously open or close the first channel and the second channel.

2. The scroll compressor of claim 1, wherein a third passage (125, 2251, 3251) is provided in the second end plate, the third passage being in fluid communication with the seal cavity and being connected to a solenoid valve (170, 270, 370) switchable between a first state in which the third passage fluidly communicates the seal cavity with a suction pressure region of the scroll compressor via the solenoid valve to open a vane of the check valve, and a second state in which the third passage is closed by the solenoid valve or in which the third passage fluidly communicates the seal cavity with a high or medium pressure region of the scroll compressor via the solenoid valve to close the vane of the check valve.

3. The scroll compressor of claim 2, wherein the second side of the second end plate has a hub (128, 228, 328) centrally formed therein, a non-orbiting scroll central discharge passage (C0) being formed in the hub in fluid communication with the non-orbiting scroll discharge port (129, 229, 329), and a port (127) formed therein fluidly connecting the sealed cavity with the non-orbiting scroll central discharge passage, the port having a cross-sectional area smaller than that of the third passage.

4. A scroll compressor as claimed in claim 2, wherein a fourth passage (2252, 3252) is provided in the second end plate, the fourth passage being in fluid communication with the central compression chamber or with a second of the plurality of intermediate compression chambers, wherein the pressure of the second intermediate compression chamber is higher than the pressure of the first intermediate compression chamber, and the fourth passage is connected to the solenoid valve, in the first condition the fourth passage being closed by the solenoid valve, in the second condition the fourth passage being in fluid communication with the third passage through the solenoid valve.

5. The scroll compressor of claim 1, wherein the scroll compressor includes a cover plate (130, 230) disposed on the second side of the second end plate, the cover plate covering the first recess (126, 226) thereby forming the sealed cavity.

6. The scroll compressor of claim 1, wherein the second side of the second end plate is formed with a second recess (326) configured as a back pressure cavity (C2) of the non-orbiting scroll, the first recess (327) is formed below the second recess (326) in an axial direction, and the scroll compressor includes a seal spacer plate (330) covering the first recess to form the seal cavity.

7. The scroll compressor of claim 6, wherein the sealed cavity is configured as first and second chambers spaced apart from each other disposed on either side of an axis of the non-orbiting scroll, the first and second chambers being in fluid communication through a channel (3226) formed on the second end plate.

8. The scroll compressor of any one of claims 1 to 7, wherein the valve plate of the check valve includes a first end portion and a second end portion, the first end portion and the second end portion being connected by a connecting portion, the first end portion being fixed to the second end plate, the second end portion selectively opening or closing the first opening and the second opening.

9. The scroll compressor of any one of claims 1 to 7, wherein the check valve includes a flapper (352) above the vane, the flapper having through holes (3521) provided at positions corresponding to the first and second openings below the vane.

10. The scroll compressor according to any one of claims 1 to 7, wherein the second end plate is formed with a boss portion (1211) surrounding the first and second openings in the seal cavity, and the valve sheet is contactable with the boss portion so as to seal the first and second openings.

11. The scroll compressor of any one of claims 1 to 7, wherein within the sealed cavity, the second end plate is formed with a counterbore (3212) surrounding and spaced apart from the first opening, the counterbore being in fluid communication with the second opening and not in fluid communication with the first opening.

12. The scroll compressor of any one of claims 1 to 7, wherein the first passage includes an eccentrically disposed first tunnel segment (3213) connected to the sealed cavity and a second tunnel segment (3215) connected to the at least one first intermediate compression cavity, the second tunnel segment configured as a plurality of tunnels distributed generally along a scroll profile.