CN217152298U

CN217152298U - Scroll compression mechanism and scroll compressor comprising same

Info

Publication number: CN217152298U
Application number: CN202220969524.1U
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: 2022-08-09
Anticipated expiration: 2032-04-25

Abstract

The utility model relates to a scroll compression mechanism and scroll compressor including it, scroll compression mechanism include decide the vortex and move the vortex, move scroll head section and decide the exhaust chamber that scroll head section injectd following state: the discharge plenum is in a state to be in fluid communication with the compression plenum but not yet in fluid communication with the compression plenum, an inwardly concave 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 plenum into the discharge plenum when the orbiting and fixed scroll head sections are separated, the orbiting scroll head section is configured to prevent fluid communication of the compression plenum with the discharge plenum 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 excessive compression, relieve or eliminate pressure mutation in the exhaust process, improve scroll strength, and have simple structure and high cost benefit.

Description

Scroll compression mechanism and scroll compressor comprising same

Technical Field

The utility model relates to a scroll compressor field, more specifically relates to a scroll compression mechanism and scroll compressor including it.

Background

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

Scroll compressors may be used in applications such as refrigeration systems, air conditioning systems, and heat pump systems. The scroll compressor includes a scroll compression mechanism (also simply referred to as "compression mechanism") for compressing a working fluid. The compression mechanism includes a fixed scroll and an orbiting scroll. The non-orbiting and orbiting scrolls engage to define therebetween a series of chambers moving from a radially outer side to a radially inner side and gradually decreasing in volume, including a suction chamber that sucks a 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 working on reducing the power consumption of scroll compressors and/or improving the discharge efficiency.

SUMMERY OF THE UTILITY MODEL

The general outline of the present invention is provided in this section, not a full scope of the invention or a full disclosure of all the features of the invention.

An object of the utility model is to provide an improved scroll compression mechanism and scroll compressor, this scroll compression mechanism and scroll compressor can reduce the power loss and can improve exhaust efficiency.

Another object of the present invention is to provide an improved scroll compression mechanism and scroll compressor, which can avoid the power loss caused by excessive compression and can simultaneously alleviate or eliminate the condition of pressure sudden change in the exhaust process.

Another object of the present invention is to provide an improved scroll compression mechanism and scroll compressor, which can ensure the strength of the scroll and improve the scroll. The scroll compression mechanism and the scroll compressor have simple structures, are easy to realize and have higher cost effectiveness.

According to an aspect of the utility model, a vortex compression mechanism is provided, include:

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 non-orbiting scroll being engaged with the orbiting scroll to define therebetween an open suction chamber, at least one closed compression chamber, and a discharge chamber at a center, which are sequentially arranged from a radially outer side to a radially inner side,

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

the orbiting scroll includes an orbiting scroll head section, the non-orbiting scroll includes a non-orbiting scroll head section, the orbiting scroll head section and the non-orbiting scroll head section define the discharge plenum in a state: said discharge chamber being in a state of being in immediate fluid communication with said compression chamber but not yet in fluid communication with said compression chamber, an inwardly concave flow guide groove being provided on an inner wall of said orbiting scroll head section to increase a flow rate of fluid from said compression chamber into said discharge chamber when said orbiting scroll head section and said fixed scroll head section are separated,

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

Thereby, the scroll compression mechanism and the scroll compressor can reduce power loss and can improve exhaust efficiency. And the scroll compression mechanism and the scroll compressor can avoid power loss caused by over-compression and can simultaneously relieve or eliminate the condition of pressure sudden change in the exhaust process.

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

According to an embodiment of the invention, the guiding gutter is positioned at a predetermined distance from the top surface of the orbiting scroll head section.

According to an embodiment of the invention, the guiding groove is arranged closer to the top surface of the orbiting scroll head section than to the distance of the orbiting scroll wrap connected to the root of the orbiting scroll end plate. Thereby improving the strength of the root of the scroll.

According to an embodiment of the present invention, the guiding groove is arranged to extend a predetermined distance towards the inner end of the orbiting scroll head section starting from the following starting point: the starting point is a position of the orbiting scroll head section that is engaged with the fixed scroll head section and about to start disengaging from the fixed scroll head section.

According to an embodiment of the invention, the flow channels are configured to have different recess depths at different positions and to have a maximum recess depth at the starting point.

According to the utility model discloses an embodiment, the guiding gutter is in the axial direction of scroll compression mechanism extends highly less than or equal to move the axial height 2/3 of vortex scroll to ensure the intensity of scroll.

According to an embodiment of the present invention, the recessed depth of the guiding groove is less than or equal to 7/8 of the thickness of the corresponding section of the head section of the orbiting scroll to ensure the strength of the scroll.

According to an embodiment of the present invention, the thickness of the portion of the orbiting scroll head section provided with the guide groove is 0.5mm or more.

According to an embodiment of the invention, the flow guide is configured to comprise at least one section. In order to avoid undesired early mixing of the compressed fluid while improving the exhaust gas flow-through efficiency.

According to another aspect of the present invention, there is provided a scroll compressor including the scroll compression mechanism as described above.

To sum up, according to the utility model discloses a scroll compression mechanism and scroll compressor provide following beneficial effect at least: according to the utility model discloses a scroll compression mechanism and scroll compressor can reduce power loss and can improve exhaust efficiency, can avoid because of the power loss that excessive compression caused and can alleviate or eliminate the condition of the pressure sudden change in the exhaust process simultaneously, can ensure scrollwork intensity, improve the scrollwork simultaneously to have simple structure, easily realize, have higher cost-effectiveness.

Drawings

The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description, taken with reference to the accompanying drawings, which are given by way of example only and which are not necessarily drawn to scale. Like reference numerals are used to indicate like parts in the accompanying drawings, in which:

figure 1 shows a schematic longitudinal cross-sectional view of a scroll compressor according to a first embodiment of the present invention;

FIG. 2a shows an exploded view of the 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 a corresponding K-K cross-sectional view thereof;

FIG. 2e is a schematic diagram showing the variation of the discharge chambers defined by the orbiting and non-orbiting scroll wraps during discharge of the scroll compressor;

fig. 3a shows a perspective view of an orbiting scroll in a scroll compression mechanism according to a second embodiment of the present invention, which shows a first side of the orbiting scroll;

figure 3b shows a side view of an assembled state of a scroll compression mechanism according to a second embodiment of the present invention and its corresponding M-M cross-sectional view; and

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

Detailed Description

A preferred embodiment of the present invention will now be described in detail with reference to fig. 1-3 c. The following description is merely exemplary in nature and is not intended to limit the present disclosure, 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 present invention 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 invention. The first embodiment is described in detail below with reference to fig. 1 to 2 e.

As shown in fig. 1, a 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, in which the non-orbiting scroll 22 includes a non-orbiting scroll end plate 221, a non-orbiting scroll wrap 222, and a discharge port V 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 boss portion 240, and an open suction chamber, at least one closed compression chamber for compressing a working fluid, and an open discharge chamber E (see fig. 2d and 2E) in fluid communication with a discharge port V are sequentially defined by the stationary scroll wrap 222 and the orbiting scroll wrap 242 from a radially outer side to a radially inner side within the compression mechanism CM. The number of closed compression chambers may be two or more. The radially inner compression pockets are at a higher pressure than the radially outer compression pockets. 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 exhaust chamber E, it should be noted that the exhaust chamber E is defined herein as a chamber defined by the fixed scroll wrap 222 and the orbiting scroll wrap 242, which is formed at a critical time immediately before fluid communication with the high pressure chamber H, that is, immediately before the current exhaust is finished and the next exhaust is performed, but is not yet in fluid communication with the high pressure chamber H, and is in fluid communication with only the exhaust port V. The exhaust chamber E will be described in detail below in connection with the "starting point a".

The electric motor includes 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 axis of rotation relative to the housing 10. The non-orbiting scroll 22 is fixed to the main bearing housing 18 to be held in place, and the orbiting scroll 24 is driven by an electric motor via the drive shaft 16 to be capable of translational rotation, i.e., orbiting, relative to the non-orbiting scroll 22 (i.e., the axis of the orbiting scroll 24 orbits relative 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) by means of the oldham ring 17. Thus, the intake port of the compression mechanism CM draws in low pressure fluid and compresses it through a series of closed compression chambers, and then into the exhaust chamber E and discharges the high pressure fluid through the exhaust port V.

As shown in fig. 2d, during operation of the compression mechanism CM, pairs of high-pressure chambers H are defined in the compression mechanism CM, two high-pressure chambers H adjoining the radially central exhaust chamber E, at which point the current exhaust process in the exhaust chamber E is ended, i.e. is about to be in fluid communication with both high-pressure chambers H for the next exhaust process. When fluid can flow from the two high-pressure chambers H into the exhaust chamber E, the fluid is discharged through the exhaust port V as the orbiting scroll 24 rotates. After the fluid in the high pressure chamber H is discharged, the compression chamber on the radial outer side of the high pressure chamber H is communicated with the exhaust chamber E again to perform the next exhaust process.

The utility model discloses a research has been carried out to the whole flow process of fluid in vortex compression mechanism, has found the fluidic apparent pressure variation condition, and for example, under some operating modes, the fluid is compressed to the pressure that is higher than required pressure, in addition, when transitioning from one exhaust process to another exhaust process, can produce the pressure sudden change. Based on these findings, the utility model of the present application proposes a solution that can simultaneously address the power loss caused by these pressure changes.

Under certain conditions of the scroll compressor, a discharge gas pressure that may be required is less than the design discharge pressure (i.e., the design fluid pressure discharged via discharge port V). Under these conditions, if fluid is compressed into the exhaust chamber E and discharged through the exhaust port V, a phenomenon of over-compressing the fluid occurs. Over-compressing the fluid causes the scroll compression mechanism CM to do more work than necessary, resulting in excessive power consumption. To avoid power loss from over-compression of fluid by compression mechanism CM, non-orbiting scroll end plate 221 may include at least one exhaust valve port P (see fig. 2b) located adjacent to exhaust chamber E, preferably, but not limited to, in fluid communication with high pressure chamber H (see fig. 2 d). The exhaust valve port P may preferably be closed by a valve such as an electronic valve or the like 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. A plurality of exhaust valve ports P may be preferably provided 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 over-compression can be avoided, thereby reducing power consumption of the scroll compressor 100.

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

In addition, it should be noted that for the convenience of the description herein, the nomenclature of the exhaust chamber E and the high pressure chamber H will not be changed before and after the transition of the different exhaust processes, so as not to be confused or misunderstood, as shown in fig. 2d, 2E, 3b, 3 c. Those skilled in the art will appreciate that in practice, the individual cavities are varied without a fixed demarcation point.

While fig. 2E shows a schematic illustration of the stages of change of the discharge plenum E defined by orbiting scroll head section 246 and fixed scroll head section 226 during discharge of scroll compressor 100, wherein the second configuration of orbiting scroll head section 246 with guide slots 2460 and the first configuration without guide slots is shown, it is noted that guide slots 2460 in fig. 2E are merely schematic and the actual shape and size of guide slots 2460 are not specifically depicted. Specifically, as shown in the "first stage" of the first configuration, the orbiting scroll head section 246 and the fixed scroll head section 226 are engaged with each other to define the exhaust chamber E, where the "first stage" means a critical stage before exhaust is started, where the orbiting scroll head section 246 is engaged with the fixed scroll head section 226 at the starting point a, and then a "second stage", i.e., an exhaust start stage, where the orbiting scroll head section 246 is disengaged from the fixed scroll head section 226 at the starting point a, so that fluid starts to flow from the high pressure chamber H into the exhaust chamber E (as shown by an arrow in the drawing) to start exhaust, but at this time, since a gap between the orbiting scroll head section 246 and the fixed scroll head section 226 is very small, exhaust efficiency is low, and an instantaneous pressure surge 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 alleviate the transient pressure surge in the high pressure chamber H, a guide groove 2460 may be provided on an inner wall 2466 of the orbiting scroll head section 246 facing the discharge chamber E to accelerate the flow of fluid from the high pressure chamber H into the discharge chamber E to improve the discharge efficiency and the operating efficiency of the scroll compressor 100. As shown schematically in the stages of the second configuration of FIG. 2e, the gap between orbiting scroll head section 246 and fixed scroll head section 226 can be significantly enlarged by providing a flow guide groove 2460, thereby improving exhaust efficiency.

According to the scroll compression mechanism, the technical problem that pressure suddenly changes in the process of excessive compression and fluid advancing is taken into consideration, so that power consumption can be remarkably reduced, and the efficiency of the scroll compressor is improved. In general, the provision of the exhaust valve port P limits structural improvement of the scroll wrap (particularly, the orbiting scroll wrap) because it tends to cause fluid leakage between adjacent chambers or decrease in strength of the wrap, etc. However, the utility model discloses the people of this application has proposed the scheme that combines exhaust valve port P with the scroll improvement, while optimizing exhaust passage, has eliminated the condition that the scroll compression chamber (especially, high pressure chamber) communicates with the exhaust chamber and appears mixing in advance before beginning to exhaust (i.e. in the condition that has not reached the expected pressure level, the compressed fluid in different chambers mixes in advance via exhaust valve port P), has further improved the efficiency of scroll compressor; meanwhile, the root stress of the scroll is reduced through the improvement of the scroll structure design.

Also, preferably, the flow guide groove 2460 is provided to extend from the above-mentioned starting point a, i.e., the starting point a is a position on the orbiting scroll head section 246 where the tip section 2260 is in contact with the tip section 2260 when the tip section 2260 of the fixed scroll head section 226 is about to start to disengage from the orbiting scroll head section 246, so that the flow of fluid from the high pressure chamber H into the exhaust chamber E can be effectively accelerated both at the stage of starting exhaust, i.e., the above-mentioned second stage, and at the third stage, i.e., the exhaust stage where the gap is further enlarged.

It should be noted here that the tip 2260 of the fixed scroll head section 226 only represents one section of the fixed scroll head section 226 near the terminal end, and is not meant to refer to the terminal end specifically, i.e., the tip 2260 engaged with the point a of the movable scroll head section 246 may preferably be a terminal end point thereof, or a certain position in a section at a certain distance from the terminal end point, although in the embodiment of the present invention, the portion engaged with the starting point a of the movable scroll head section 246 is preferably a terminal end point of the fixed scroll head section 226, but it should be understood that there is no particular limitation thereto.

As previously described, with respect to scroll compressor 100 and scroll compressor mechanism CM having both discharge valve port P and baffle 2460, since orbiting scroll head section 246 includes baffle 2460 to narrow axial top surface 247 of orbiting scroll head section 246, the following technical problems may exist during the process of abutting orbiting and

non-orbiting scrolls

24 and 22 against each other for compression operation: top surface 247 of orbiting scroll head section 246 may not cover exhaust valve port P properly at some instant and exhaust valve port P spans two sides of orbiting scroll head section 246 to fluidly communicate spaces of the two sides, possibly resulting in a reduction in compression efficiency, which is undesirable. In order to solve the technical problem, the utility model discloses the configuration to guiding gutter 2460 is improved, generally speaking, according to the utility model discloses a guiding gutter 2460 sets up to make the top surface 247 that moves whirlpool book head section 246 can cover exhaust valve port P during the operation so: each exhaust valve port P does not fluidly communicate the spaces on either side, for example, across both sides of the orbiting scroll head section 246.

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

As shown in FIGS. 2c and 2d, flow guide groove 2460 is preferably provided in this embodiment to extend to top surface 247 of orbiting scroll head section 246, and is preferably provided in two segments, i.e., flow guide groove 2460 includes first and

second groove segments

2461 and 2462 that are spaced apart from each other, i.e., first and

second groove segments

2461 and 2462 include an unremoved material spacer segment 2463 therebetween. As previously described, the guide groove 2460 still preferably extends from the above-described start point a, i.e., the first groove section 2461 extends from the start point a, to better accelerate the exhaust gas, and more preferably, the first groove section 2461 has a relatively greater concave depth at the start point a, i.e., a depth recessed into the orbiting scroll head section 246 in a normal direction of the tangential plane of the inner wall 2466, to enable more rapid acceleration of the fluid into the exhaust chamber E at the start point a, i.e., immediately after the start of the exhaust gas. In general, flow channels 2460 are preferably configured to have different recess depths at different locations, preferably a maximum recess depth near start point a. More preferably, the recessed depth of guide groove 2460 is equal to or less than 7/8 the thickness of orbiting scroll head section 246, i.e., the thickness of the portion of orbiting scroll head section 246 including guide groove 2460, i.e., the remaining portion after material removal, should be no less than 1/8 its original thickness, and more preferably, the thickness of the portion of orbiting scroll head section 246 including guide groove 2460, i.e., the remaining portion after material removal, is equal to or greater than 0.5mm, thereby ensuring that the portion has the required strength.

Also, preferably, the extension height of pilot groove 2460 in the axial direction of scroll compression mechanism CM is equal to or less than 2/3, which is the total axial height of orbiting scroll wrap 246, to ensure the required strength. And preferably, flow guide groove 2460 is disposed closer to top surface 247 of orbiting scroll head section 246 as a whole and away from the root of orbiting scroll head section 246 that is connected to orbiting scroll end plate 241 to ensure the strength of orbiting scroll head section 246.

With respect to second slot section 2462, as shown in fig. 2c and 2c, second slot section 2462 preferably extends to the terminal end of orbiting scroll head section 246 to better accelerate the flow of fluid into exhaust pocket E throughout the exhaust process. However, the present invention is not limited thereto, that is, the length (radian) of the guide groove 2460 extending along the profile line direction of the orbiting scroll head portion 246 may be set according to actual requirements, so as to ensure good coverage of the exhaust valve port P while achieving an optimized exhaust effect, and to ensure strength of the scroll.

As for the spacing section 2463, the position and size thereof may be set according to actual conditions, for example, the position and size of the exhaust valve port P, the strength requirement of the scroll portion including the guide groove 2460, and the like, with the purpose of: firstly, by providing the spacing section 2463, the exhaust valve port P can be better covered to improve compression efficiency; meanwhile, the partition portion 2463 is advantageous to further improve the strength of the scroll portion including the guide groove 2460, and particularly, to reduce stress concentration at a connection root of the guide groove 2460 and the remaining scroll portion and stress concentration at a connection root between the orbiting scroll head portion 246 and the orbiting scroll end plate 241.

Also, with the object of the present invention, ensuring good coverage of the exhaust valve port P, the depth of recess of the flow guide groove 2460 at various different locations may be flexibly set depending on the position and size of the exhaust valve port P, e.g., as shown in fig. 2d, the first groove section 2461 and the second groove section 2462 each have different depths of recess at different locations; also, although in the present embodiment guide 2460 has a uniform axial height, the present invention is not limited thereto, and guide 2460 may be flexibly configured to have different axial heights at different locations, depending on, for example, the strength requirements described above, etc., and it will be appreciated that guide 2460 may also be multi-segmented in the axial direction, i.e., include a plurality of slot segments spaced apart in the axial direction.

Further, although the guide groove 2460 is provided in two stages, i.e., including the first groove section 2461 and the second groove section 2462 spaced apart from each other in the above-described embodiment, the present invention is not limited thereto, and it should be understood that the guide groove 2460 may be provided to include more stages, e.g., three stages, four stages, etc., or to be provided in a single stage in succession with different recessed depths at different positions, as long as good coverage of the exhaust valve port P can be ensured. Also, the guide groove 2460 may have any suitable shape according to practical circumstances, and there is no particular limitation thereto.

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

Of course, it is contemplated that guide groove 2460 in this embodiment may be configured similarly to the two-or more-segment configuration of the first embodiment, except that guide groove 2460 in this embodiment does not extend to top surface 247 of orbiting scroll head section 246.

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

The experimental result shows that the working efficiency of the scroll compressor can be effectively improved by about 0.95%, the power loss can be reduced by about 0.85%, and the capacity of the scroll compression mechanism CM can be slightly increased by about 0.16% by improving the guide grooves.

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

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

The scroll compression mechanism and the scroll compressor according to the preferred embodiments of the present invention have been described above with reference to the specific embodiments. It will be understood that the above description is intended to be illustrative and not restrictive, and that various changes and modifications may be suggested to one skilled in the art in view of the above description without departing from the scope of the invention. Such variations and modifications are also intended to be included within the scope of the present invention.

Claims

1. A scroll compression mechanism, comprising:

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

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

4. The scroll compression mechanism of claim 3, wherein the baffle slot is disposed closer to a top surface of the orbiting scroll head section than to a root of the orbiting scroll wrap connected to the orbiting scroll end plate.

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

6. The scroll compression mechanism of claim 5, wherein the baffle is 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 baffle slot extends in an axial direction of the scroll compression mechanism to a height equal to or less than 2/3 of an axial height of the orbiting scroll wrap.

8. The scroll compression mechanism of claim 1, wherein the recessed depth of the flow deflector is less than or equal to 7/8 the thickness of the respective section of the orbiting scroll head section.

9. The scroll compression mechanism of claim 1, wherein a thickness of the portion of the orbiting scroll head section where the baffle groove is disposed is 0.5mm or greater.

10. The scroll compression mechanism of claim 2 or 3, wherein the baffle slot is configured to include at least one section.

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