CN210218102U

CN210218102U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN210218102U
Application number: CN201920765067.2U
Authority: CN
Inventors: Xuan Liu; 刘轩; Qiongyu Zhang; 张琼宇
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2019-05-24
Filing date: 2019-05-24
Publication date: 2020-03-31
Anticipated expiration: 2029-05-24

Abstract

The present disclosure provides a scroll compressor, comprising: an orbiting scroll including an orbiting scroll end plate and an orbiting wrap formed at one side of the orbiting scroll end plate; and a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap formed on one side of the non-orbiting scroll end plate, the non-orbiting scroll and the orbiting scroll cooperating to form a series of compression pockets therebetween, the series of compression pockets including a central compression pocket and an intermediate compression pocket located radially outward of the central compression pocket, the intermediate compression pocket including at least a set of first and second intermediate compression pockets; wherein a fluid passage selectively communicating with a discharge region is provided between the first intermediate compression chamber and the second intermediate compression chamber, the first intermediate compression chamber and the second intermediate compression chamber being in direct communication through the fluid passage. According to the present disclosure, it is possible to provide a compressor having a variable volume ratio function which is not limited by an installation space and has a simple structure.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present disclosure relates to the field of scroll compressors, and more particularly, to scroll compressors having variable volume ratio functionality.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

The compressor may be applied to application systems requiring different pressures, such as an air conditioning system, a refrigerator system, etc., and thus, a case where a discharge pressure of a compression chamber (a maximum pressure in the compression chamber) is greater than a pressure required for a specific application system, that is, an over-compression case may occur. In the case of over-compression, the fluid compressed to the discharge pressure will drop to the pressure required by the application system after exiting the compression chambers, and therefore the compressor does unnecessary work, which will reduce the efficiency of the compressor.

In order to reduce or prevent over-compression of the working fluid, compressors having a Variable Volume Ratio (VVR) function have been developed. Such a compressor can achieve a variable volume ratio, i.e., operate at a low volume ratio when the system required pressure is low and at a high volume ratio when the system required pressure is high, using a VVR valve provided in a VVR orifice, thereby effectively avoiding an over-compression phenomenon and improving the efficiency of the compressor. However, in the field of compressors, there still exist technical problems that the VVR function cannot be realized or the structure for realizing the VVR function is complicated and high in cost due to the limited installation space and the inability to provide the VVR valve.

SUMMERY OF THE UTILITY MODEL

It is an object of one or more embodiments of the present disclosure to provide a compressor in which a variable volume ratio mechanism that is not limited by an installation space and has a simple structure is provided.

It is another object of one or more embodiments of the present disclosure to provide a compressor in which there is a variable volume ratio mechanism suitable for a small displacement compressor provided with a non-orbiting scroll hub.

Another object of one or more embodiments of the present disclosure is to provide a compressor in which a variable volume ratio mechanism having high compatibility can be realized in a simple and fast manner.

It is another object of one or more embodiments of the present disclosure to provide a compressor in which a variable volume ratio mechanism having less new parts to be developed and thus having low development difficulty and high development speed is provided.

It is another object of one or more embodiments of the present disclosure to provide a compressor in which a variable volume ratio mechanism is provided that does not require a split design, has no cover plate, and has little leakage to operate reliably.

According to one aspect of the present disclosure, there is provided a scroll compressor including: an orbiting scroll including an orbiting scroll end plate and an orbiting wrap formed at one side of the orbiting scroll end plate; and a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap formed on one side of the non-orbiting scroll end plate, the non-orbiting scroll and the orbiting scroll cooperating to form a series of compression pockets therebetween, the series of compression pockets including a central compression pocket and an intermediate compression pocket located radially outward of the central compression pocket, the intermediate compression pocket including at least a set of first and second intermediate compression pockets; wherein a fluid passage selectively communicating with a discharge region is provided between the first intermediate compression chamber and the second intermediate compression chamber, the first intermediate compression chamber and the second intermediate compression chamber being in direct communication through the fluid passage.

According to one aspect of the present disclosure, the scroll compressor includes: a primary discharge port and a secondary discharge port disposed at the non-orbiting scroll end plate, the primary discharge port in fluid communication with the central compression chamber, and the secondary discharge port common to the first and second intermediate compression chambers selectively in fluid communication with a discharge region.

According to one aspect of the disclosure, the fluid passage includes a first section communicating to the first intermediate compression pocket, a second section communicating to the second intermediate compression pocket, and a connecting section connecting the first and second sections.

According to one aspect of the present disclosure, the fluid passage is disposed in the non-orbiting scroll end plate, the connection section includes a first connection section in communication with the first section and a second connection section in communication with the second section, the first connection section and the second connection section intersect, and the secondary discharge port is in direct fluid communication with one of the first intermediate compression chamber and the second intermediate compression chamber.

According to an aspect of the present disclosure, the fluid passage is provided in the orbiting scroll end plate, and the connection section is formed as a single section, and the secondary discharge port is in direct fluid communication with one of the first intermediate compression chamber and the second intermediate compression chamber.

According to one aspect of the present disclosure, the connection section has a first end penetrating the non-orbiting scroll end plate or the orbiting scroll end plate, the first end being provided with a stopper preventing fluid leakage.

According to an aspect of the present disclosure, the fluid passage is provided on at least one of the fixed scroll and the movable scroll.

According to an aspect of the present disclosure, the fluid passage includes a channel provided at a free-end surface of the fixed wrap and/or the movable wrap, and first and second notches extending from the channel communicating to the first and second intermediate compression pockets, respectively.

According to an aspect of the present disclosure, the non-orbiting scroll end plate is formed with an inner annular wall on a side opposite to the fixed wrap, the main discharge port and the auxiliary discharge port are disposed radially inside the inner annular wall, and the discharge area is defined by the inner annular wall; and a variable volume ratio valve is provided at the secondary discharge port, the variable volume ratio valve allowing fluid flow from the first and second intermediate compression chambers to the discharge region and preventing fluid flow from the discharge region to the first and second intermediate compression chambers.

According to one aspect of the disclosure, the variable volume ratio valve comprises a single valve plate covering the variable volume ratio orifice and a valve stop controlling the maximum range of motion of the valve plate, the valve plate comprising a fixed part and a single movable part movable relative to the fixed part between an open position and a closed position.

The compressor structure according to the present disclosure can not only be free from the limitation of the installation space but also realize the VVR function in a structurally simple manner.

Drawings

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

Fig. 1 is a sectional view schematically showing a compressor having a VVR function according to a first comparative example;

fig. 2 is a perspective view schematically showing a fixed scroll and a VVR valve of a compressor having a VVR function according to a first comparative example;

fig. 3A is a perspective view schematically showing a fixed scroll and a VVR valve of a compressor having a VVR function according to a second comparative example;

fig. 3B shows a VVR valve according to a second comparative example in detail;

fig. 4 schematically illustrates a compressor non-orbiting scroll and an orbiting scroll according to a first embodiment of the present disclosure;

FIG. 5 schematically illustrates a plug installed in a transverse connection section according to one embodiment of the present disclosure;

FIG. 6 illustrates a bulkhead in detail, according to an embodiment of the disclosure;

FIG. 7 schematically illustrates a plug installed in a transverse connection section according to another embodiment of the present disclosure;

FIG. 8 shows in detail a plug according to another embodiment of the present disclosure;

fig. 9 schematically illustrates a non-orbiting scroll of a compressor according to a second embodiment of the present disclosure;

fig. 10 schematically illustrates a scroll mechanism of a compressor according to a second embodiment of the present disclosure;

fig. 11 schematically illustrates a non-orbiting scroll of a compressor according to a third embodiment of the present disclosure;

fig. 12 schematically illustrates an orbiting scroll of a compressor according to a third embodiment of the present disclosure;

fig. 13 schematically illustrates a scroll mechanism of a compressor according to a third embodiment of the present disclosure; and

fig. 14A and 14B schematically illustrate a discharge port arrangement of a compressor according to one embodiment of the present disclosure.

Detailed Description

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

A compressor having a VVR function according to a comparative example will be described with reference to fig. 1 to 3B, in which fig. 1 is a sectional view schematically showing a compressor having a VVR function according to a first comparative example; fig. 2 is a perspective view schematically showing a fixed scroll and a VVR valve of a compressor having a VVR function according to a first comparative example; fig. 3A and 3B schematically show a fixed scroll and a VVR valve of a compressor having a VVR function according to a second comparative example.

As shown in fig. 1, the compressor 1 includes a substantially closed housing 20. The housing 20 may be composed of a generally cylindrical body portion 22, a top cover 24 provided at one end of the body portion 22, and a bottom cover 26 provided at the other end of the body portion 22. A partition plate 30 is provided between the top cover 24 and the body portion 22 to partition the inner space of the housing 20 into the fluid suction chamber 21 and the fluid discharge chamber 23. The space between the partition plate 30 and the top cover 24 constitutes the fluid discharge chamber 23, and the space between the partition plate 30, the body portion 22 and the bottom cover constitutes the fluid suction chamber 21. An intake joint for sucking fluid is provided at one side of the fluid suction chamber 21, and an exhaust joint for discharging compressed fluid is provided at one side of the fluid discharge chamber 23.

A compression mechanism and a drive mechanism for driving the compression mechanism are provided in the housing 20. The compression mechanism sucks fluid from the fluid suction chamber 21 of the housing 20 and discharges the fluid after compression into the fluid discharge chamber 23 of the housing 20. More specifically, referring to fig. 1, the compression mechanism may include, for example, a non-orbiting scroll 40 and an orbiting scroll 50. Orbiting scroll 50 includes an end plate 54 and a spiral wrap 56 formed on one side of the end plate. Non-orbiting scroll 40 includes an end plate 44 and a spiral wrap 46 formed on one side of the end plate, end plate 44 including a discharge port 42 formed at a substantially central position of the end plate and first and second variable

volume ratio orifices

64 and 66 located radially outward of discharge port 42. Wrap 46 of non-orbiting scroll 40 and wrap 56 of orbiting scroll 50 intermesh to define therebetween a series of compression pockets of progressively decreasing volume from the radially outer side to the radially inner side and progressively increasing pressure. Specifically, the pressure in the radially outermost one of the compression chambers is the smallest, the pressure in the radially innermost compression chamber, i.e., the central compression chamber C1 at the center of the scroll is the largest, and a plurality of intermediate compression chambers located between the radially outermost and innermost positions have intermediate pressures between the maximum and minimum pressures. The fluid communication described in this section of the exhaust port 42 with the central compression chamber corresponds to direct fluid communication), while the first and second variable

volume ratio orifices

64, 66 are in partial fluid communication with the two intermediate compression chambers C2, C3 located on either side of the central compression chamber.

To achieve axial sealing between the tip of wrap 46 of non-orbiting scroll 40 and end plate 54 of orbiting scroll 50, and between the tip of wrap 56 of orbiting scroll 50 and end plate 44 of non-orbiting scroll 40, typically, a back pressure chamber 70 is provided on the opposite side of end plate 44 of non-orbiting scroll 40 from wrap 46. More specifically, an inner annular wall 43 and an outer annular wall 45 are formed on the end plate 44. An inner annular wall 43 is formed around the exhaust port 42. The back pressure chamber 70 is formed by the space surrounded by the end plate 44, the inner annular wall 43 and the outer annular wall 45 and is closed by a seal assembly disposed therein. Back pressure chamber 70 is in fluid communication with one of the intermediate pressure chambers between orbiting scroll 50 and non-orbiting scroll 40 through an axially extending through hole (not shown) formed in end plate 44, thereby creating a force that compresses non-orbiting scroll 40 toward orbiting scroll 50, and non-orbiting scroll 40 and orbiting scroll 50 may be effectively pressed together by the pressure in back pressure chamber 70.

In the exhaust region defined by the inner annular wall 43, a variable volume ratio valve 100 (hereinafter, referred to as a VVR valve) is provided to prevent excessive compression of the working fluid. As specifically shown in fig. 2, the VVR valve 100 includes a valve plate 110, a valve plate 120, a valve holder 130, a pin 140, and a wave spring 150. The valve plate 110 is provided with first and second fluid through holes at positions corresponding to the first and second variable

volume ratio orifices

64 and 66, respectively. The valve plate 110 is provided with a valve sheet 120 to selectively open or close the fluid passing hole. The valve plate 120 has two movable portions 126 and one fixed portion 124 which are symmetrical. The two movable parts 126 are displaceable between an open position and a closed position relative to the fixed part 124. The valve plate 120 is provided with a valve holder 130. The pin 140 extends through pin holes formed in the valve plate, and the valve holder to circumferentially fix the valve plate 110, the valve plate 120, and the valve holder 130. The wave spring 150 axially holds the valve plate, and valve retainer together.

During operation of the compressor 1, working fluid is drawn into the compression mechanism and compressed as it flows from a radially outermost position to a radially innermost position, the compressed fluid is discharged through the discharge port 42 to a discharge area defined by the inner annular wall 43, and then discharged to the discharge chamber 23 via a one-way valve provided at a central position of the partition plate 30. In the event of excessive compression, however, the fluid may be discharged to the exhaust region through the VVR valve 100 in advance before reaching the radially innermost position. Specifically, when the pressure of the fluid in the compression chamber in the radially intermediate position is greater than the pressure of the fluid in the discharge chamber 23 (i.e., over-compression occurs), the pressure on the lower side of the valve plate 120 is greater than the pressure on the upper side, and the valve plate 120 moves toward the open position by the pressure difference, thereby allowing the fluid to be discharged through the variable

volume ratio orifices

64, 66 and the fluid passage hole in advance. When the pressure of the fluid contained in the compression chamber at the radially intermediate position is smaller than the pressure of the fluid in the discharge chamber 23, the valve sheet 120 returns to the closed position by the elastic restoring force and the pressure difference, thereby sealing the variable

volume ratio orifices

64, 66.

In the compressor 1, in order to enable the back pressure chamber 70 to provide a stable and sufficient pressure to effectively prevent fluid leakage between the respective compression chambers, it is necessary to ensure that the back pressure chamber 70 has a sufficient space, whereby the space inside the annular wall 43 is very limited. In particular, for a small displacement scroll compressor, the space inside the annular wall 43 may have only a diameter of 20mm to 30mm, in which case it is difficult to fit the VVR valve 100 to the inside of the annular wall 43 to achieve the VVR function of the compressor.

On the other hand, fig. 3A and 3B schematically show the fixed scroll and the VVR valve of the compressor having the VVR function according to the second comparative example, and other configurations of the compressor are substantially the same as those of the compressor according to the first comparative example. The compressor according to the second comparative example employs the cover plate 220 to divide the discharge area and the back pressure chamber into upper and lower parts, so that the mounting space of the VVR valve is not limited by the size of the back pressure chamber as in the first comparative example. Specifically, referring to fig. 3A, non-orbiting scroll end plate 144 and cover plate 220 are secured together by a plurality of screws 210, wherein non-orbiting scroll end plate 144 is provided with a recess 208 on the opposite side of the formed wrap, recess 208 being formed around discharge port 202 and variable

volume ratio orifices

164, 166, thereby forming a discharge area at recess 208 (i.e., the underside of cover plate 220).

A corresponding VVR valve 200 is provided in each of the variable

volume ratio ports

164, 166. The VVR valve 200 allows fluid to flow from the compression chamber to the exhaust region and prevents fluid from flowing from the exhaust region to the compression chamber. The VVR valve 200 may include a valve plate 220 covering the variable

volume ratio orifices

164, 166 and a valve stop 230 that prevents the valve plate 220 from deforming excessively. The valve plate 220 has a movable portion 226 and a fixed portion 224, the movable portion 226 being displaceable between an open position and a closed position relative to the fixed portion 224. The VVR valve 200 may be fixed to a valve fixing hole formed in the non-orbiting scroll end plate 144 by a fastener 240 such as a screw.

The upper side of the cover plate 220 forms a recess 222, the recess 222 being in fluid communication with an intermediate pressure chamber in the compression chambers through an intermediate pressure bore, and a seal assembly may be disposed in the recess 222 to form a back pressure chamber that provides an axial sealing force to the non-orbiting scroll. A spacer 250 is disposed between cover plate 220 and non-orbiting scroll end plate 144.

However, in the compressor according to the second comparative example, since the additional cover plate 220, the gasket 250, and the corresponding fasteners need to be used, the structure is complicated, and the component cost and the installation time are increased. And because the discharge area between cover plate 220 and non-orbiting scroll end plate 144 has a significant pressure, there is a risk that the threaded connection of cover plate 220 to non-orbiting scroll end plate 144 will fail to achieve a complete seal and fluid leakage will occur.

In order to solve the above problems, the present inventors have devised an improved compressor structure that is not only capable of being free from the restriction of the installation space but also capable of realizing the VVR function in a structurally simple manner.

A compressor having a VVR function according to the present disclosure will be described in further detail with reference to fig. 4 to 14B, in which like reference numerals refer to like parts and detailed descriptions thereof will be omitted.

As shown in fig. 4, the compressor according to the first embodiment of the present disclosure includes a fixed scroll 40A and an orbiting scroll 50A, and a wrap 46 of the fixed scroll 40A and a wrap 56 of the orbiting scroll 50A are engaged with each other to form a series of compression pockets therebetween, of which volume is gradually decreased from a radially outer side to a radially inner side and pressure is gradually increased, similarly to the fixed scroll 40 and the orbiting scroll 50 according to the first comparative example. The pressure in the radially outermost compression chamber is the smallest, the pressure in the radially innermost compression chamber, i.e., the central compression chamber at the central position of the scroll, is the largest, and a plurality of intermediate compression chambers between the radially outermost position and the innermost position have intermediate pressures between the largest pressure and the smallest pressure.

End plate 44A of non-orbiting scroll 40A is provided with a central exhaust port 42 and a variable volume orifice 64. The central discharge port 42 may be in fluid communication with the central one of the compression chambers C1, and the variable volume orifice 64 may be in fluid communication with the first intermediate compression chamber C2 located radially outward (to the right in fig. 4) of the central compression chamber. A second intermediate compression chamber C3 is formed at the opposite side (i.e., the left side in fig. 4) of the central compression chamber, and the second intermediate compression chamber C3 may be symmetrical to the first intermediate compression chamber C2 with respect to the central compression chamber C1. It should be noted that, in the description of the present application, the intermediate compression cavities having substantially the same pressure and cavity volume during the operation of the compressor are referred to as a group of first intermediate compression cavities and second intermediate compression cavities, and the group of intermediate compression cavities simultaneously exhausts air to avoid over-compression or under-compression of a certain compression cavity caused by different exhausts of air, so as to reduce the loss of isochoric compression of the compressor. In a symmetrical single-scroll compressor, the compression chambers are symmetrical with respect to the central compression chamber, and the pressures and volumes in the two symmetrical compression chambers are substantially the same and can be used as a set of intermediate compression chambers. In a twin-scroll compressor, there may be two sets (i.e., four) of intermediate compression chambers of approximately the same pressure and volume. In the asymmetric scroll design, the compression pockets formed by the non-orbiting and orbiting scrolls are asymmetric with respect to the central compression pocket, and therefore, the first intermediate compression pocket C2 is also asymmetric with respect to the second intermediate compression pocket C3. However, it should be understood that the technical idea of providing a fluid channel as described below according to the invention is equally applicable in the asymmetric case.

The compressor according to the first embodiment of the present disclosure is provided with the fluid passage 300 between the first intermediate compression chamber C2 and the second intermediate compression chamber C3 to directly communicate the two compression chambers. As shown in fig. 4, fluid passage 300 may be formed in end plate 54A of orbiting scroll 50A, and fluid passage 300 may include a first section 310, a second section 330, and a transverse connecting section 320. The first and

second sections

310 and 330 may extend in an axial direction of the compressor and communicate with the first and second intermediate compression pockets C2 and C3, respectively, and the transverse connecting section 320 may extend in a transverse direction perpendicular to the axial direction of the compressor and connect the first and second

axial sections

310 and 330. Thus, fluid in the second intermediate compression pocket C3 may flow sequentially through the second axial section 330, the transverse connecting section 320, and the first axial section 310 to the first intermediate compression pocket C2, and may then be discharged from the first intermediate compression pocket C2 via the variable volume orifice 64 to the discharge region defined by the annular wall 43. Preferably, the transverse connecting section 320 of the fluid channel 300 may be formed as a single section to reduce the clearance volume of the compressor. Further, although the first and

second sections

310 and 330 are described herein as extending in the axial direction of the compressor, it should be understood that the first and

second sections

310 and 330 may also extend in a slightly oblique direction. Axially extending first and

second sections

310 and 330 are preferably employed to reduce the clearance volume of the compressor.

In the compressor according to the first embodiment of the present disclosure, one VVR valve 200 may be provided on the variable volume orifice 64. The VVR valve 200 may include a valve sheet 220 covering the variable volume ratio orifice 64 and a valve stop 230 that prevents the valve sheet 220 from being excessively deformed. The valve plate 220 may have a movable portion 226 and a fixed portion 224, the movable portion 226 being displaceable relative to the fixed portion 224 between an open position, in which the valve plate 220 closes the variable volume orifice 64, and a closed position, in which the valve plate 220 opens the variable volume orifice 64 and allows fluid flow from the first intermediate compression chamber C2 to the discharge area defined by the annular wall 43. VVR valve 200 may be fixed to a valve fixing hole formed in end plate 44A of non-orbiting scroll 40A by a fastener such as a screw.

During operation of the compressor according to the first embodiment of the present disclosure, working fluid is drawn into the compression mechanism and compressed as it flows from the radially outermost position to the radially innermost position, and the compressed fluid is discharged through the discharge port 42 to the discharge area defined by the inner annular wall 43 and then discharged through the check valve provided at the center of the partition plate 30 to the discharge chamber 23. In the event of over-compression, fluid may be prematurely discharged through the VVR valve 200 to a discharge region before reaching the radially innermost central compression pocket C1. Specifically, when the pressure of the fluid in the first and second intermediate compression chambers C2 and C3 in the radially intermediate position is greater than the pressure of the fluid in the discharge chamber 23 (i.e., excessive compression occurs), the pressure of the lower side of the valve sheet 220 is greater than the pressure of the upper side, and the movable portion 226 of the valve sheet 220 moves toward the open position by the pressure difference, thereby allowing the fluid to be discharged in advance from the intermediate compression chambers C2, C3 to the discharge region through the variable volume ratio orifice 64. When the pressure of the fluid in the first and second intermediate compression chambers C2 and C3 is less than the pressure of the fluid in the discharge chamber 23, the valve sheet 220 returns to the closed position by the elastic restoring force and the pressure difference, thereby sealing the variable volume ratio orifice 64.

The compressor according to the first embodiment of the present disclosure exemplarily shows the case of having a set of intermediate compression chambers C2, C3, in which only a single variable volume orifice 64 may be formed in the end plate 44A, and only a single valve sheet having a single movable part is needed to achieve selective opening and closing of the variable volume orifice 64, thereby enabling a large reduction in the installation size of the VVR valve as compared with the compressor according to the first comparative example, avoiding the inability to achieve the VVR function due to the size limitation. Further, the compressor according to the first embodiment of the present disclosure may avoid the use of an additional cover plate 220, a gasket 250, and a corresponding fastener, reduce manufacturing costs and component costs, and prevent fluid leakage from a high pressure discharge area between the cover plate and the non-orbiting scroll end plate, as compared to the compressor according to the second comparative example. In addition, since the VVR valve 200 according to the first embodiment of the disclosure, which has a simple structure and has been conceived by the inventor, for example, does not require development of new parts, the difficulty of development of implementing the VVR function in the compressor is low and the development speed is high. And the structure compatibility according to the first embodiment of the present disclosure is high, and the present disclosure is applicable to most scrolls, and the compressor can be rapidly improved to have the VVR function by machining an orifice and the like on the original scroll.

According to one embodiment of the present disclosure, a plug reducing clearance volume is provided in the transverse connecting section 320. As shown in fig. 5, since the first axial segment 310 and the second axial segment 330 intersect the transverse connecting segment 320 at the first position P1 and the second position P2, respectively, located inside the end plate, it is difficult for the conventional machining method to directly punch a hole from the positions P1 and P2 inside the end plate 54A to form a transverse passage, but the transverse connecting passage 320 must be extended to the point P1 intersecting the first axial segment 310 by punching a hole from the outboard end of the end plate 54A (e.g., the left end shown in fig. 5). Therefore, only a portion of the transverse connecting section 320 between the intersection points P1, P2 is necessary to form the connecting passage 300 (hereinafter referred to as a first portion), and the remaining portion between the end perforated from the left side and the intersection point P2 (hereinafter referred to as a second portion) is an ineffective portion due to a manufacturing process. Since there will be residual exhaust gas in the transverse connecting section 320 after the VVR valve is closed, the ineffective second portion will cause the clearance volume of the compressor to increase, thereby reducing the efficiency of the compressor. According to an embodiment of the present disclosure, a choke plug may be provided in the transverse connecting section 320 to separate the first and second portions to reduce the clearance volume of the compressor.

With reference to fig. 5-8, a specific embodiment including a transverse connecting section with an attached bulkhead according to the present disclosure is illustrated. In the embodiment shown in fig. 5, the plug 400 has a short stud shape, and a tool engagement groove 410 is formed on one end surface of the plug 400. An internal thread is formed on the entire length of the second portion of the lateral connecting section 320, and the length of the plug 400 is smaller than that of the second portion, and a tool such as a screwdriver can be engaged with the tool engagement groove 410 of the plug 400, thereby screwing and fixing the plug 400 into the second portion at a portion where the second portion is adjacent to the first portion to isolate the first portion from the second portion. In the embodiment shown in fig. 7 and 8, the plug 500 is elongated and stepped, the transverse connecting section 320 is formed with an internal thread only at the left end position thereof, the plug 500 includes a first cylindrical portion 510 formed with an external thread on the outer peripheral surface thereof for engagement with the internal thread, and a second cylindrical portion 520 having a diameter slightly smaller than that of the first cylindrical portion and having a length capable of filling the second portion.

Referring to fig. 9 and 10, there is provided a scroll mechanism of a compressor according to a second embodiment of the present disclosure, in which the non-orbiting scroll 40 according to the first comparative example is replaced with a non-orbiting scroll 40B described in fig. 9 to 10, and other configurations of the scroll compressor are substantially unchanged.

A fluid passage that directly communicates the first intermediate compression chamber with the second intermediate compression chamber is provided in an end plate 44B of the non-orbiting scroll 40B. The fluid passage of the end plate 44B may include a first axial section 310, a second axial section 330, and a transverse connecting section 320B, similar to the fluid passage 300 according to the first embodiment, wherein the first and second axial sections may extend in an axial direction of the compressor and communicate with the first and second intermediate compression chambers, respectively, and the transverse connecting section 320B may extend in a transverse direction perpendicular to the axial direction of the compressor and connect the first and second axial sections. The transverse connecting section 320B according to the second embodiment may be formed as a single section similar to the transverse connecting section 320 according to the first embodiment. However, since the exhaust port 42 is formed in the end plate 44B of the non-orbiting scroll 40B, in order to prevent the lateral connection section 320B from being affected by the exhaust port 42 in the end plate 44B, the lateral connection section 320B may include a first lateral connection section 322B and a second lateral connection section 324B respectively disposed at both sides of the exhaust port 42 such that the lateral connection section 320B is disposed to bypass the exhaust port 42. First and second transverse connecting

segments

322B, 324B may intersect at an outer end P3 of end plate 44B of non-orbiting scroll 40B, and a seal 326B may be provided at the intersecting P3 to prevent fluid from exiting the first and second intermediate compression pockets via outer end P3.

The operation principle and advantages of the compressor according to the second embodiment of the present disclosure are the same as those of the compressor according to the first embodiment of the present disclosure, and thus, no further description is given herein.

A scroll mechanism of a compressor according to a third embodiment of the present disclosure is described below with reference to fig. 12 to 14B. In a third embodiment according to the present disclosure, a fluid passage 300C1 is provided in a wrap 46C of a non-orbiting scroll 40C, the fluid passage 300C1 including a first notch 310C1, a second notch 330C1, and a connecting section (i.e., corresponding to a channel according to the present invention) 320C1, wherein the first notch 310C1 and the second notch 330C1 may communicate with the first intermediate compression chamber C2 and the second intermediate compression chamber C3, respectively, and the transverse connecting section 320C1 may extend along the spiral wrap 46C and connect the first notch 310 and the second notch 330. Similarly, a fluid passage 300C2 is provided in scroll wrap 56C of orbiting scroll 50C according to the third embodiment of the present disclosure, and fluid passage 300C2 includes first and second notches 310C2 and 330C2 communicating with first and second intermediate compression pockets C2 and C3, respectively, and a connecting section (i.e., corresponding to a channel according to the present invention) 320C2 extending along spiral scroll wrap 56C and connecting first and second notches 310C2 and 330C 2. Preferably, in the third embodiment of the present disclosure, the fluid passages 300C1 and 300C2 are formed at the free end of the wrap, thereby facilitating machining of the fluid passages and reducing the influence on the strength of the wrap on the one hand.

Although in the third embodiment according to the present disclosure, it is shown that the first and second intermediate compression pockets are communicated by both of the fluid passage 300C1 formed in the non-orbiting scroll wrap 46C and the fluid passage 300C2 formed in the orbiting scroll wrap 56C, it will be understood by those skilled in the art that the fluid passage may be formed only on one of the non-orbiting scroll wrap 46C and the orbiting scroll wrap 56C to achieve the fluid communication of the first and second intermediate compression pockets.

The operation principle and advantages of the compressor according to the third embodiment of the present disclosure are the same as those of the compressor according to the first embodiment of the present disclosure, and thus, no further description is given herein.

In the embodiments described above, the exhaust port 42 is provided in the center of the end plate 44 of the non-orbiting scroll 40, and in the case where the space defined by the inner annular wall 43 is very limited, such a centrally disposed exhaust port may interfere with the provision of the VVR valve such that the VVR valve extends at least partially through the central exhaust port 42, which may cause the high-pressure fluid discharged through the central exhaust port 42 to act on the valve plate of the VVR valve, thereby possibly causing the VVR valve to discharge the under-compressed fluid in advance without the occurrence of over-compression. In order to solve the above-described problem, referring to fig. 14A and 14B, in one embodiment according to the present disclosure, the exhaust port 42 includes a first exhaust port portion 42A and a second exhaust port portion 42B communicating with each other. First discharge port portion 42A is centrally located in end plate 44 of non-orbiting scroll 40 and is in fluid communication with central compression chamber C1, and second discharge port portion 42B is offset in a radial direction from first discharge port portion 42A and is in fluid communication with a discharge region defined by inner annular wall 43. In the compressor according to the present disclosure, since the second discharge port portion 42B located axially upward is offset from the first discharge port portion 42A located centrally of the end plate below, interference of the discharge port 42 with the VVR valve is reduced, and a larger installation space is provided for the VVR valve.

Although various embodiments and modifications of the present disclosure have been specifically described above, it will 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 one 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 may be replaced by other technically equivalent components.

Claims

1. A scroll compressor, comprising:

an orbiting scroll including an orbiting scroll end plate and an orbiting wrap formed at one side of the orbiting scroll end plate; and

a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap formed on one side of the non-orbiting scroll end plate, the non-orbiting scroll and the orbiting scroll cooperating to form a series of compression chambers therebetween, the series of compression chambers including a central compression chamber and an intermediate compression chamber located radially outward of the central compression chamber, the intermediate compression chamber including at least a set of first and second intermediate compression chambers;

wherein a fluid passage is provided between the first and second intermediate compression chambers which is selectively in communication with a discharge region, the first and second intermediate compression chambers being in direct communication through the fluid passage.

2. The scroll compressor of claim 1,

the scroll compressor includes:

a primary discharge port and a secondary discharge port disposed at the non-orbiting scroll end plate, the primary discharge port in fluid communication with the central compression chamber, and the secondary discharge port common to the first and second intermediate compression chambers selectively in fluid communication with a discharge region.

3. The scroll compressor of claim 2, wherein,

the fluid passage includes a first section communicating to the first intermediate compression pocket, a second section communicating to the second intermediate compression pocket, and a connecting section connecting the first and second sections.

4. The scroll compressor of claim 3,

the fluid passage is disposed in the non-orbiting scroll end plate, the connection section includes a first connection section in communication with the first section and a second connection section in communication with the second section, the first connection section and the second connection section intersect, the secondary discharge port is in direct fluid communication with one of the first intermediate compression chamber and the second intermediate compression chamber.

5. The scroll compressor of claim 3,

the fluid passage is provided in the orbiting scroll end plate, and the connection section is formed as a single section, and the sub-discharge port is in direct fluid communication with one of the first intermediate compression chamber and the second intermediate compression chamber.

6. The scroll compressor of claim 4 or 5,

the connecting section has a first end that runs through decide vortex end plate or move the vortex end plate, first end department is provided with the end cap that prevents the fluid and reveal.

7. The scroll compressor of claim 1,

the fluid passage is provided on at least one of the fixed scroll and the movable scroll.

8. The scroll compressor of claim 7,

the fluid passage includes a channel provided at a free-end surface of the fixed wrap and/or the movable wrap, and first and second notches extending from the channel and communicating to the first and second intermediate compression pockets, respectively.

9. The scroll compressor of claim 2, wherein,

the fixed scroll end plate is formed with an inner annular wall on a side opposite to the fixed scroll, the main discharge port and the auxiliary discharge port are disposed radially inside the inner annular wall, and the discharge region is defined by the inner annular wall; and a variable volume ratio valve is provided at the secondary discharge port, the variable volume ratio valve allowing fluid flow from the first and second intermediate compression chambers to the discharge region and preventing fluid flow from the discharge region to the first and second intermediate compression chambers.

10. The scroll compressor of claim 9, wherein,

the variable volume ratio valve includes a single valve plate covering the variable volume ratio orifice and a valve stop controlling a maximum range of motion of the valve plate, the valve plate including a fixed portion and a single movable portion movable relative to the fixed portion between an open position and a closed position.