CN116988971A

CN116988971A - Scroll compression mechanism and scroll compressor comprising same

Info

Publication number: CN116988971A
Application number: CN202210439484.4A
Authority: CN
Inventors: 梁计; 钱源
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2022-04-25
Filing date: 2022-04-25
Publication date: 2023-11-03
Also published as: CN116988971A8

Abstract

The present application relates to a scroll compression mechanism including a fixed scroll and an orbiting scroll, the orbiting and fixed scroll head sections defining a discharge chamber in a state of: the discharge chamber is in an impending fluid communication with the compression chamber but not yet in fluid communication with the compression chamber, and an inwardly recessed flow guide groove is provided on an inner wall of the orbiting scroll head section to increase a flow rate of fluid from the compression chamber into the discharge chamber when the orbiting scroll head section and the fixed scroll head section are separated, the orbiting scroll head section being configured to prevent fluid communication of the compression chamber with the discharge chamber via the at least one discharge valve port by a top surface of the orbiting scroll head section covering at least a portion of the at least one discharge valve port during operation. The compression mechanism and the scroll compressor can reduce power loss, improve exhaust efficiency, avoid over-compression, relieve or eliminate pressure abrupt change in the exhaust process, improve scroll strength, and have simple structure and high cost efficiency.

Description

Scroll compression mechanism and scroll compressor comprising same

Technical Field

The present application relates to the field of scroll compressors, and more particularly, to a scroll compression mechanism and a scroll compressor including the same.

Background

This section provides background information related to the present application, which does not necessarily constitute prior art.

Scroll compressors may be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems. Scroll compressors include a scroll compression mechanism (also referred to simply as a "compression mechanism") for compressing a working fluid. The compression mechanism includes a fixed scroll and an orbiting scroll. The fixed scroll and the orbiting scroll are engaged to define a series of chambers therebetween moving from a radially outer side to a radially inner side and having a gradually decreasing volume, including a suction chamber that sucks in fluid, a compression chamber, and a discharge chamber that communicates with a discharge port so as to discharge the compressed fluid.

Those skilled in the art have been devoted to reducing the power loss of scroll compressors and/or improving the efficiency of the discharge.

Disclosure of Invention

The accompanying drawings are included to provide a general overview of the application and are not intended to provide a complete disclosure of the full scope of the application or all-character thereof.

It is an object of the present application to provide an improved scroll compression mechanism and scroll compressor which can reduce power loss and can improve the discharge efficiency.

It is another object of the present application to provide an improved scroll compression mechanism and scroll compressor which avoid power loss due to over-compression and which simultaneously alleviate or eliminate pressure spikes during the discharge process.

It is a further object of the present application to provide an improved scroll compression mechanism and scroll compressor which can ensure the strength of the wrap and improve the wrap. The scroll compression mechanism and the scroll compressor have simple structures, are easy to implement, and are relatively cost-effective.

According to one aspect of the present application, there is provided a scroll compression mechanism comprising:

a non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap extending from one side of the non-orbiting scroll end plate; and

an orbiting scroll including an orbiting scroll end plate and an orbiting scroll wrap extending from one side of the orbiting scroll end plate,

the fixed scroll is engaged with the movable scroll to define therebetween an open suction chamber, at least one closed compression chamber and a discharge chamber at the center arranged in this order from the radially outer side to the radially inner side,

the non-orbiting scroll end plate includes a discharge port in fluid communication with the discharge chamber and at least one discharge valve port in fluid communication with the compression chamber for early discharge,

the orbiting scroll includes an orbiting scroll head section, and the non-orbiting scroll includes a non-orbiting scroll head section, the orbiting scroll head section and the non-orbiting scroll head section defining the exhaust chamber in a state in which: the discharge chamber is in a state of being in fluid communication with the compression chamber but not yet in fluid communication with the compression chamber, a concave diversion trench is arranged on the inner wall of the movable scroll head section to increase the flow rate of fluid flowing into the discharge chamber from the compression chamber when the movable scroll head section and the fixed scroll head section are separated,

the orbiting scroll head section is configured to prevent fluid communication of the compression chamber with the discharge chamber via the at least one discharge valve port during operation by a top surface of the orbiting scroll head section covering at least a portion of the at least one discharge valve port.

Thus, the scroll compression mechanism and scroll compressor can reduce power loss and can improve the exhaust efficiency. And the scroll compression mechanism and scroll compressor can avoid power loss due to over-compression and can simultaneously alleviate or eliminate the situation of abrupt pressure change in the exhaust process.

According to one embodiment of the application, at least a portion of the flow guide groove extends to a top surface of the orbiting scroll head section.

According to one embodiment of the application, the flow guide groove is positioned at a predetermined distance from the top surface of the orbiting scroll head section.

According to one embodiment of the application, the flow guide groove is disposed closer to the top surface of the orbiting scroll head section than to the root of the orbiting scroll wrap connected to the orbiting scroll end plate. Thereby facilitating the improvement of the strength of the scroll root.

According to one embodiment of the application, the flow guide groove is arranged to extend a predetermined distance from a starting point towards an inner end of the head section of the orbiting scroll: the starting point is a location of the orbiting scroll head section that is engaged with the fixed scroll head section and is about to begin to disengage from the fixed scroll head section.

According to one embodiment of the application, the channels are configured with different recess depths at different locations and with a maximum recess depth at the starting point.

According to one embodiment of the present application, the extending height of the diversion trench in the axial direction of the scroll compression mechanism is 2/3 or less of the axial height of the orbiting scroll wrap to ensure the strength of the wrap.

According to one embodiment of the present application, the recessed depth of the flow guide groove is 7/8 or less of the thickness of the corresponding section of the head section of the orbiting scroll to ensure the strength of the scroll.

According to one embodiment of the present application, the thickness of the portion of the head section of the orbiting scroll where the flow guide groove is provided is 0.5mm or more.

According to one embodiment of the application, the flow guide groove is constructed to comprise at least one section. In order to avoid undesired advanced mixing of the compressed fluid while improving the exhaust gas flow efficiency.

According to another aspect of the present application there is provided a scroll compressor comprising a scroll compression mechanism as described above.

In summary, the scroll compression mechanism and the scroll compressor according to the present application provide at least the following advantages: the scroll compression mechanism and the scroll compressor according to the present application can reduce power loss and can improve exhaust efficiency, can avoid power loss due to over-compression and can simultaneously alleviate or eliminate the condition of abrupt pressure change in the exhaust process, can ensure the strength of the scroll, improve the scroll, and have a simple structure, are easy to implement, and have high cost effectiveness.

Drawings

The foregoing and additional features and characteristics of the present application will become more apparent from the following detailed description, taken in conjunction with the accompanying drawings, which are merely exemplary and not necessarily drawn to scale. Like reference numerals are used to designate like parts throughout the accompanying drawings, in which:

fig. 1 shows a schematic longitudinal cross-sectional view of a scroll compressor according to a first embodiment of the present application;

FIG. 2a shows an exploded view of a scroll compression mechanism of the scroll compressor of FIG. 1;

FIG. 2b shows a perspective view of the non-orbiting scroll of FIG. 2 a;

FIG. 2c shows a perspective view of the orbiting scroll of FIG. 2 a;

FIG. 2d illustrates a side view of the scroll compression mechanism of FIG. 2a in an assembled state and its corresponding K-K cross-sectional view;

FIG. 2e illustrates a schematic diagram of the change in discharge chamber defined by the orbiting scroll wrap and the non-orbiting scroll wrap during discharge of the scroll compressor;

FIG. 3a illustrates a perspective view of an orbiting scroll in a scroll compression mechanism according to a second embodiment of the present application showing a first side of the orbiting scroll;

FIG. 3b illustrates a side view and corresponding M-M cross-sectional view of an assembled state of a scroll compression mechanism according to a second embodiment of the present application; and

fig. 3c shows a side view and a corresponding L-L section view of an assembled state of a scroll compression mechanism according to a second embodiment of the present application.

Detailed Description

Preferred embodiments of the present application will now be described in detail with reference to fig. 1-3 c. The following description is merely exemplary in nature and is in no way intended to limit the application, its application, or uses.

In the following exemplary embodiments, a vertical scroll compressor is exemplified for convenience of description. However, the scroll compressor according to the application may also be any other suitable type of scroll compressor, such as a horizontal scroll compressor.

Fig. 1 to 2e show a first embodiment according to the present application. The first embodiment is described in detail below with reference to fig. 1 to 2 e.

As shown in fig. 1, scroll compressor 100 may include a housing 10, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 18, an orbiting scroll 24, and a non-orbiting scroll 22. The orbiting scroll 24 and the non-orbiting scroll 22 constitute a scroll compression mechanism (hereinafter also simply referred to as "compression mechanism") CM adapted to compress a working fluid (e.g., refrigerant), as better shown in fig. 2a and 2b, wherein the non-orbiting scroll 22 includes a non-orbiting scroll end plate 221, a non-orbiting scroll wrap 222, and a discharge port V located at the center of the non-orbiting scroll end plate 221; the orbiting scroll 24 includes an orbiting scroll end plate 241, an orbiting scroll wrap 242 and a hub 240, and an open suction chamber, at least one closed compression chamber for compressing a working fluid, and an open discharge chamber E, at least one closed discharge chamber E being in fluid communication with a discharge port V, are defined in the compression mechanism CM in this order from the radially outer side to the radially inner side (see fig. 2d and 2E). The number of closed compression chambers may be two or more. The radially inner compression chambers have a higher pressure than the radially outer compression chambers. Herein, for convenience of description, the compression chamber adjacent to the discharge chamber E is referred to as a high pressure chamber H. In particular, with respect to the discharge chamber E, it is noted that the discharge chamber E herein refers to a chamber defined by the fixed scroll wrap 222 and the movable scroll wrap 242 that is only in fluid communication with the discharge port V at a critical moment at which fluid communication with the high-pressure chamber H is to be performed, i.e., the current discharge is ended and the next discharge is to be performed, but is not yet in fluid communication with the high-pressure chamber H. The exhaust chamber E will be described in detail below in connection with "start point a".

The electric motor comprises a stator 14 and a rotor 15. The rotor 15 is used to drive the drive shaft 16 to rotate the drive shaft 16 about its rotational axis relative to the housing 10. The non-orbiting scroll 22 is fixed to the main bearing housing 18 and held in place, with the orbiting scroll 24 being driven by an electric motor via the drive shaft 16 so as to be able to perform translational rotation, i.e., orbit, with respect to the non-orbiting scroll 22 by means of the cross slide ring 17 (i.e., the axis of the orbiting scroll 24 orbits with respect to the axis of the non-orbiting scroll 22, but both the orbiting scroll 24 and the non-orbiting scroll 22 do not themselves rotate about their respective axes). Thus, the inlet of the compression mechanism CM draws in low pressure fluid and compresses the fluid through a series of closed compression chambers, then into the discharge chamber E and discharges the high pressure fluid through the discharge port V.

As shown in fig. 2d, during operation of the compression mechanism CM, a pair of high-pressure chambers H are defined in the compression mechanism CM, the two high-pressure chambers H adjoining the radially central venting chamber E, at which point the current venting process in the venting chamber E ends, i.e. is in fluid communication with the two high-pressure chambers H for the next venting process. When fluid is able to flow from the two high pressure chambers H into the discharge chamber E, the fluid is discharged through the discharge port V as the orbiting scroll 24 rotates. After the fluid in the high-pressure chamber H is discharged, the compression chamber radially outside the high-pressure chamber H is again about to communicate with the discharge chamber E for the next discharge process.

The inventors of the present application have studied the overall flow of fluid through a scroll compression mechanism and have found that significant pressure changes in the fluid, such as compression of the fluid to a pressure above the desired pressure under certain conditions, can occur during the transition from one discharge event to another. Based on these findings, the inventors of the present application have proposed a solution capable of simultaneously solving the power loss caused by these pressure changes.

In some conditions of the scroll compressor, the pressure of the discharge gas that may be required is less than the designed discharge pressure (i.e., the designed fluid pressure discharged via the discharge port V). Under these conditions, if the fluid is compressed to the discharge chamber E and discharged through the discharge port V, a phenomenon of over-compressing the fluid occurs. Excessive compression of the fluid causes the scroll compression mechanism CM to perform more unnecessary work, resulting in excessive power loss. To avoid excessive compression of fluid by the compression mechanism CM and loss of power, the non-orbiting scroll end plate 221 may include at least one discharge valve port P (see fig. 2 b) located adjacent the discharge chamber E, preferably but not limited to, in fluid communication with the high pressure chamber H (see fig. 2 d). The exhaust valve port P is preferably closed by a valve such as an electronic valve and opened under certain conditions (e.g., a predetermined pressure) to discharge the fluid in the high-pressure chamber H to the exhaust port V in advance before entering the exhaust chamber E, thereby avoiding unnecessary further compression of the fluid. It may be preferable to provide a plurality of exhaust ports P to communicate the two high-pressure chambers H to the exhaust chamber, respectively. For example, as shown in fig. 2b, 4 exhaust valve ports P are provided on diametrically opposite sides of the exhaust port V, respectively. By providing the discharge valve port P, power loss due to excessive compression can be avoided, and thus it is possible to exhibit a reduction in power consumption of the scroll compressor 100.

Further, as shown in fig. 2d and 2E, the orbiting scroll wrap 242 includes an orbiting scroll head section 246 and the fixed scroll wrap 222 includes a fixed scroll head section 226, the orbiting scroll head section 246 and the fixed scroll head section 226 together defining the above-described discharge chamber E, i.e., a chamber in fluid communication with only the discharge port V formed at a critical point when the current discharge ends but the next discharge is about to begin but is not yet in fluid communication with the high pressure chamber H. At this time, the orbiting scroll head section 246 is engaged with the fixed scroll head section 226 at the start point a, the fixed scroll head section 226 is engaged with the orbiting scroll head section 246 at the point B, that is, the orbiting scroll head section 246 is defined herein as a section from the start point a to the end (i.e., the radially inner end), the fixed scroll head section 226 is defined as a section from the point B to the end (i.e., the radially inner end), and both define the discharge chamber E.

In addition, it should be noted that, for convenience of description herein, the term names of the exhaust chamber E and the high pressure chamber H will not be changed before and after the transition of different exhaust processes, so as not to be confused or misunderstood, as shown in fig. 2d, 2E, 3b, and 3 c. Those of ordinary skill in the art will appreciate that in actual operation, each cavity is varied without the existence of a fixed demarcation point.

As fig. 2E illustrates a schematic diagram of the varying phase of the discharge chamber E defined by the orbiting and fixed scroll head sections 246, 226 during discharge of the scroll compressor 100, wherein the second configuration of the orbiting scroll head section 246 with the flow guide groove 2460 and the first configuration without the flow guide groove are illustrated, it is noted that the flow guide groove 2460 in fig. 2E is merely schematic and the actual shape and size of the flow guide groove 2460 is not specifically depicted. Specifically, as shown in the "first stage" in the first configuration, the movable scroll head section 246 and the fixed scroll head section 226 are engaged with each other to define the discharge chamber E, the "first stage" at this time means a critical stage before starting the discharge, at which the movable scroll head section 246 is engaged with the fixed scroll head section 226 at the start point a, and then the "second stage", i.e., a start of the discharge stage, at which the movable scroll head section 246 is disengaged from the fixed scroll head section 226 at the start point a, so that the fluid starts to flow from the high pressure chamber H into the discharge chamber E (as shown by an arrow in the drawing), whereby the discharge is started, but at this time, the discharge efficiency is low due to a very small gap between the movable scroll head section 246 and the fixed scroll head section 226, and an instantaneous pressure increase in the high pressure chamber H may be caused. As previously described, to improve the discharge efficiency of the discharge chamber E of the compression mechanism CM, and to mitigate the transient pressure surge in the high pressure chamber H, a flow guide groove 2460 may be provided on the inner wall 2466 of the orbiting scroll head section 246 facing the discharge chamber E, thereby accelerating the flow of fluid from the high pressure chamber H into the discharge chamber E to improve the discharge efficiency and the operation efficiency of the scroll compressor 100. As shown in the schematic view of the stages in the second configuration of FIG. 2e, the clearance between the orbiting scroll head 246 and the fixed scroll head 226 can be significantly enlarged by providing a flow guide groove 2460, thereby improving the exhaust efficiency.

The scroll compression mechanism provided by the application combines the technical problems of over-compression and abrupt pressure change in the fluid advancing process, so that the power consumption can be remarkably reduced, and the efficiency of the scroll compressor is improved. In general, the arrangement of the discharge port P restricts structural improvement of the scroll wrap (particularly, the orbiting scroll wrap) because it tends to cause leakage of fluid between adjacent cavities or decrease in wrap strength, etc. However, the present inventors have proposed a solution combining the discharge valve port P with the wrap improvement, eliminating the case where the scroll compression chamber (particularly, the high pressure chamber) communicates with the discharge chamber while optimizing the discharge passage and early mixing occurs before the start of discharge (i.e., in the case where the desired pressure level is not reached, compressed fluids in different chambers are early mixed via the discharge valve port P), further improving the efficiency of the scroll compressor; meanwhile, the root stress of the scroll is reduced by improving the structural design of the scroll.

Also, it is preferable that the flow guide groove 2460 is provided to extend from the above-described start point a, that is, the position on the orbiting scroll head section 246 that is in contact with the tip section 2260 when the tip section 2260 of the fixed scroll head section 226 is about to come out of engagement with the orbiting scroll head section 246, so that the fluid can be effectively accelerated from the high pressure chamber H into the discharge chamber E at the stage of just starting the discharge, that is, the above-described second stage, and the third stage, that is, the discharge stage in which the gap is further enlarged.

It should be noted herein that the tip section 2260 of the fixed scroll head section 226 is only shown herein as a section of the fixed scroll head section 226 near the terminal end, and is not intended to be specific to the terminal end, i.e., the tip section 2260 engaged with the point a of the movable scroll head section 246 may preferably be the terminal end thereof, or may be a position in the section at a distance from the terminal end, although in the embodiment of the present application, the portion engaged with the start point a of the movable scroll head section 246 is preferably the terminal end of the fixed scroll head section 226, it should be understood that there is no particular limitation thereto.

As described above, with the scroll compression mechanism CM and the scroll compressor 100 having both the discharge port P and the flow guide groove 2460, since the moving scroll head section 246 includes the flow guide groove 2460 so that the top surface 247 in the axial direction of the moving scroll head section 246 is narrowed, there may be the following technical problems in the process that the moving scroll 24 and the fixed scroll 22 abut against each other to perform the compression operation: the top surface 247 of the orbiting scroll head section 246 may not properly cover the exhaust port P at a certain instant to allow the exhaust port P to span across the orbiting scroll head section 246 to fluidly communicate the spaces on both sides, which may result in a reduction in compression efficiency. To address this technical problem, the present application improves upon the configuration of the flow guide groove 2460, and in general, the flow guide groove 2460 according to the present application is configured such that the top surface 247 of the orbiting scroll head section 246 can cover the exhaust valve port P during operation such that: each exhaust port P does not fluidly connect the spaces on either side, such as across the orbiting scroll head segment 246.

The configuration of the flow guide groove 2460 will be described in detail with reference to fig. 2c and 2 d.

As shown in fig. 2c and 2d, the flow guide groove 2460 is preferably provided in this embodiment to extend to the top surface 247 of the orbiting scroll head section 246, and is preferably provided in two sections, i.e., the flow guide groove 2460 includes a first groove section 2461 and a second groove section 2462 spaced apart from each other, that is, a spacer section 2463 between the first groove section 2461 and the second groove section 2462 including non-removed material. As previously described, the flow guide groove 2460 still preferably extends from the start point A described above, i.e., the first groove section 2461 extends from the start point A, to better accelerate the discharge of gas, and more preferably, the first groove section 2461 has a relatively greater recessed depth at the start point A-i.e., a depth recessed into the orbiting scroll head section 246 along the normal direction of the tangential plane to the inner wall 2466-to enable a more rapid acceleration of fluid into the discharge chamber E at the start point A, i.e., just prior to the start of discharge of gas. In general, the flow guide 2460 is preferably configured to have different recess depths at different locations, preferably a maximum recess depth near the start point a. More preferably, the recessed depth of the guide groove 2460 is less than or equal to 7/8 of the thickness of the orbiting scroll head section 246, i.e., the thickness of the portion of the orbiting scroll head section 246 including the guide groove 2460, i.e., the remaining portion after the material is removed, should be not less than 1/8 of its original thickness, and more preferably, the thickness of the portion of the orbiting scroll head section 246 including the guide groove 2460, i.e., the remaining portion after the material is removed, is greater than or equal to 0.5mm, thereby ensuring that the portion has a desired strength.

Also, it is preferable that the extending height of the flow guide groove 2460 in the axial direction of the scroll compression mechanism CM is 2/3 or less of the total axial height of the orbiting scroll wrap 246 to ensure a desired strength. And preferably, the flow guide groove 2460 is provided closer to the top surface 247 of the orbiting scroll head section 246 as a whole and away from the root of the orbiting scroll head section 246 connected to the orbiting scroll end plate 241 to secure the strength of the orbiting scroll head section 246.

With respect to second groove section 2462, as shown in FIGS. 2c and 2c, second groove section 2462 preferably extends to the terminal end of orbiting scroll head section 246 to better accelerate fluid flow into discharge chamber E throughout the discharge process. However, the present application is not limited thereto, that is, the length (radian) of the flow guide groove 2460 extending in the direction of the line of the moving scroll head section 246 may be set according to actual needs in order to ensure good coverage of the discharge valve port P while achieving an optimized discharge effect, and to ensure strength of the scroll.

As for the spacer 2463, the position and size thereof may be set according to the actual situation, for example, the position and size of the exhaust valve port P, the strength requirement of the scroll portion including the flow guide groove 2460, etc., with the purpose of: first, by providing the spacer section 2463, the exhaust valve port P can be better covered to improve compression efficiency; at the same time, spacer section 2463 facilitates further increasing the strength of the scroll portion including flow guide groove 2460, and in particular, facilitates reducing stress concentrations at the connection root of flow guide groove 2460 with the remaining scroll portion and at the connection root between orbiting scroll head section 246 and orbiting scroll end plate 241.

Also, for the purposes of the present application, ensuring good coverage of the exhaust valve port P, the recess depth of the flow guide groove 2460 at each of the different locations, such as shown in fig. 2d, may be flexibly set depending on the location and size of the exhaust valve port P, with the first and second groove sections 2461, 2462 each having different recess depths at the different locations; likewise, although the flow guide groove 2460 has a uniform axial height in the present embodiment, the present application is not limited thereto, and the flow guide groove 2460 may be flexibly provided to have different axial heights at different positions according to the above-described strength requirement or the like, and it is understood that the flow guide groove 2460 may also be multi-stage in the axial direction, that is, include a plurality of groove sections spaced apart in the axial direction.

Furthermore, while the above-described embodiment provides the flow guide groove 2460 as two-piece, i.e., including the first groove section 2461 and the second groove section 2462 spaced apart from each other, the present application is not limited thereto, it should be understood that in some cases the flow guide groove 2460 may also be provided to include more sections, such as three sections, four sections, etc., or be provided as a continuous single section with different recessed depths at different locations, as long as good coverage of the exhaust valve port P can be ensured. Also, the flow guide groove 2460 may have any suitable shape according to practical circumstances, and is not particularly limited.

Although the flow guide groove 2460 in the above-described embodiment is provided to extend to the top surface 247 of the orbiting scroll head section 246, it may be provided not to extend to the top surface 247 of the orbiting scroll head section 246. A second embodiment of the scroll compression mechanism CM according to the present application will be described below with reference to fig. 3a to 3c, wherein fig. 3a shows a perspective view of the orbiting scroll 24 in the scroll compression mechanism CM according to the second embodiment of the present application; fig. 3b shows a side view and a corresponding M-M cross-section of an assembled state of a scroll compression mechanism CM according to a second embodiment of the application; and fig. 3c shows a side view of an assembled state of the scroll compression mechanism CM according to the second embodiment of the application and its corresponding L-L cross-section. As shown in fig. 3a and 3b, the flow guide groove 2460 is provided in the form of a continuous single groove section, and as previously described, the flow guide groove 2460 also preferably extends from the start point a in this embodiment, except that the flow guide groove 2460 is provided so as not to extend to the top surface 247 of the orbiting scroll head section 246 so as not to occupy the area of the top surface 247. Specifically, as shown in FIG. 3b, a cross-sectional view taken at the M-M section closer to the orbiting scroll end plate 241, showing the flow guide groove 2460; as seen in fig. 3c, which shows a cross-sectional view taken at the L-L section closer to the top surface 247 of the orbiting scroll wrap 242, it can be seen from fig. 3c that the flow guide groove 2460 is not visible at the L-L section, and the top surface 247 is intact and not occupied by the flow guide groove 2460. This ensures that the exhaust valve port P is covered well, and the exhaust efficiency is improved effectively.

Of course, it is contemplated that the flow guide 2460 of the present embodiment may also be provided in a two-stage or more-stage configuration similar to that of the first embodiment, with the only difference being that the flow guide 2460 of the present embodiment does not extend to the top surface 247 of the orbiting scroll head section 246.

Furthermore, the present application provides a scroll compressor 100, the scroll compressor 100 comprising a scroll compression mechanism CM according to the present application, which may be, for example, the scroll compression mechanism CM in the above-described embodiments, or may have other possible modifications.

Experimental results show that by improving the diversion trench as described above, the working efficiency of the scroll compressor can be effectively improved by about 0.95%, the power loss is reduced by about 0.85%, and the capacity of the scroll compression mechanism CM can be slightly increased by about 0.16%.

Although the exemplary embodiments of the scroll compression mechanism and the scroll compressor according to the present application have been described in the foregoing embodiments, the present application is not limited thereto, but various modifications, substitutions and combinations may be made without departing from the scope of the present application.

It is obvious that various embodiments can be further devised by combining or modifying different embodiments, various technical features in different ways.

The scroll compression mechanism and scroll compressor according to the preferred embodiments of the present application are described above in connection with the specific embodiments. It will be understood that the above description is by way of example only and not by way of limitation, and that various modifications and alterations will occur to those skilled in the art in light of the above description without departing from the scope of the application. Such variations and modifications are intended to be included within the scope of the present application.

Claims

1. A scroll compression mechanism comprising:

2. The scroll compression mechanism of claim 1, wherein at least a portion of the flow guide groove extends to a top surface of the orbiting scroll head section.

3. The scroll compression mechanism of claim 1, wherein the flow guide groove is positioned a predetermined distance from a top surface of the orbiting scroll head section.

4. A scroll compression mechanism as claimed in claim 3, wherein the flow guide groove is disposed closer to the top surface of the orbiting scroll head section than to the root of the orbiting scroll end plate.

5. The scroll compression mechanism of claim 1, wherein the flow guide groove is configured to extend a predetermined distance from a starting point toward an inner end of the orbiting scroll head section: the starting point is a location of the orbiting scroll head section that is engaged with the fixed scroll head section and is about to begin to disengage from the fixed scroll head section.

6. The scroll compression mechanism of claim 5, wherein the flow channels are configured to have different recess depths at different locations and a maximum recess depth at the starting point.

7. The scroll compression mechanism of claim 1, wherein the height of extension of the flow guide groove in the axial direction of the scroll compression mechanism is 2/3 or less of the axial height of the orbiting scroll wrap.

8. The scroll compression mechanism of claim 1, wherein the recess depth of the flow guide groove is less than or equal to 7/8 of the thickness of the corresponding section of the orbiting scroll head section.

9. The scroll compression mechanism according to claim 1, wherein a thickness of a portion of the orbiting scroll head section where the flow guide groove is provided is 0.5mm or more.

10. A scroll compression mechanism as claimed in claim 2 or claim 3, wherein the flow guide groove is configured to include at least one section.

11. A scroll compressor comprising the scroll compression mechanism of any one of claims 1-10.