Patent Application
20230349381
This application claims priorities to the following two Chinese patent applications: Chinese Patent Application No. 202010731522.4 titled “FIXED SCROLL AND SCROLL COMPRESSOR”, filed with the China National Intellectual Property Administration on Jul. 27, 2020; and Chinese Patent Application No. 202021507746.9, titled “FIXED SCROLL AND SCROLL COMPRESSOR”, filed with the China National Intellectual Property Administration on Jul. 27, 2020. These applications are incorporated herein by reference in their entirety.
The present application relates to the technical field of compressors, and in particular to a fixed scroll and a scroll compressor including the same.
This section only provides background information relating to the present application, which may not necessarily constitute the prior art.
A compressor (such as a scroll compressor) may be applied in, for example, a refrigeration system, an air conditioning system, and a heat pump system. The scroll compressor includes a compression mechanism which includes a non-orbiting scroll and an orbiting scroll, the non-orbiting scroll and the orbiting scroll are engaged with each other to define an open suction cavity and a series of closed compression cavities. In addition, for a low-pressure side scroll compressor, an air inlet is generally defined in a peripheral wall of the non-orbiting scroll, the air inlet is communicated to the suction cavity, and a refrigerant enters the suction cavity through the air inlet and is supplied to the series of closed compression cavities inside the compression mechanism to compress the refrigerant.
However, in the scroll compressor of the conventional technology, the refrigerant may produce turbulence or vortex and velocity gradient when it enters the suction cavity through the air inlet, which may cause pressure loss, reduce the enthalpy difference of the refrigerant, and thus reduce the refrigeration efficiency of the scroll compressor. Therefore, it is necessary to further improve the scroll compressor, so as to improve the utilization efficiency of the refrigerant and thus improve the refrigeration efficiency of the scroll compressor.
A general summary of the present application, rather than a full scope or a full disclosure of all features of the present application, is provided in this section.
An object of the present application is to improve one or more technical problems mentioned above. In general, a non-orbiting scroll and a scroll compressor including the non-orbiting scroll as described below are provided according to the present application, which can optimize the flow guiding of a refrigerant into a compression mechanism, thereby significantly reducing the pressure loss and enthalpy difference of the refrigerant, and thus improving the refrigeration efficiency of the scroll compressor.
According to one aspect of the present application, a non-orbiting scroll of a scroll compressor is provided, which includes:
The above two-stage design with different curved directions is specially designed for the flow of the refrigerant in the flow-guiding passage, which can significantly reduce the turbulence and pressure loss of the refrigerant, thereby providing better flow-guiding effect for the refrigerant.
According to a preferred embodiment of the present application, the first section extends from the starting end to about ⅕ to ⅔ of a length of the first side wall, and a curvature change value of the first section is larger than a curvature change value of the second section, which has a better inhibition effect on turbulence and can reduce the pressure loss of the refrigerant.
According to a preferred embodiment of the present application, in the flow-guiding passage, a largest curvature is defined at the starting end.
According to a preferred embodiment of the present application, a distance between the peripheral wall and the non-orbiting scroll wrap at the engagement position is a first radial width Xm, the starting end is formed as a filleted corner, and a radius of curvature Rc of the filleted corner satisfies: 2 mm≤Rc≤0.4Xm.
The starting end with the filleted corner with such curvature is combined with the first side wall and the second side wall of the above streamlined design, so that the refrigerant does not form vortex at the starting end when it enters the flow-guiding passage through the air inlet, and can significantly reduce the turbulence in the flow-guiding passage, thereby reducing the pressure gradient of the refrigerant in the flow-guiding passage, reducing the pressure loss, and thus improving the refrigeration efficiency of the scroll compressor.
According to a preferred embodiment of the present application, along a direction from the engagement position to the starting end, a first radial thickness of a flow-guiding wrap section, defining the flow-guiding passage, of the wrap section increases progressively, and the first radial thickness is larger than or equal to a second radial thickness of the non-orbiting scroll wrap at the engagement position and is smaller than or equal to 3 times of the second radial thickness.
According to a preferred embodiment of the present application, the flow-guiding passage includes a recessed portion recessed relative to the first side surface, the recessed portion includes a recessed bottom wall, and a recessed depth L of the recessed bottom wall relative to the first side surface satisfies: L≤0.3H, in which H is an axial height of the non-orbiting scroll wrap. An internal volume and a related flow-guiding effect of the flow-guiding passage can be better adjusted by further adjusting the depth of the flow-guiding passage along an axial direction of the non-orbiting scroll.
According to a preferred embodiment of the present application, the recessed depth increases toward the starting end. Thus, the refrigerant can be smoothly guided into the subsequent suction cavity, which is beneficial to reducing the formation of turbulence and vortex, and can reduce the pressure gradient of the refrigerant in different areas of the flow-guiding passage.
According to a preferred embodiment of the present application, the recessed bottom wall includes an inclined surface, a horizontal surface, a curved surface or a combination thereof.
According to a preferred embodiment of the present application, a distance between the peripheral wall and the non-orbiting scroll wrap at the engagement position is a first radial width Xm, a third radial width K of the recessed portion satisfies: 0.7Xm≤K<Xm, the flow-guiding passage has a second radial width, the third radial width of at least a part of the recessed portion is smaller than the second radial width of the flow-guiding passage at a corresponding position along an extending direction of the non-orbiting scroll wrap to form a step portion on the first side surface.
According to a preferred embodiment of the present application, a recessed angle of the recessed bottom wall relative to the first side surface is less than or equal to 70°.
According to a preferred embodiment of the present application, at least one ventilation opening is provided in the peripheral wall, so that refrigerant can enter the flow-guiding passage through the at least one ventilation opening.
According to a preferred embodiment of the present application, the peripheral wall includes a bridging portion located at an axial tail end of the peripheral wall and adjacent to the air inlet, and the at least one ventilation opening is provided at the bridging portion.
With this branched flow path, the possible turbulence or vortex in the flow-guiding passage can be dispersed, and the pressure gradient in areas of the flow-guiding passage can be balanced, which improves the refrigeration efficiency of the scroll compressor.
According to a preferred embodiment of the present application, a circumferential side of the air inlet is substantially flush with the starting end.
According to another aspect of the present application, a scroll compressor is provided, which includes the non-orbiting scroll as described above.
In summary, at least the following beneficial technical effects are provided by the non-orbiting scroll and the scroll compressor according to the present application: the non-orbiting scroll and the scroll compressor according to the present application can optimize the flow guiding of the refrigerant into the compression mechanism by providing the flow-guiding passage and the ventilation opening with the above structure, thereby significantly reducing the pressure loss and enthalpy difference of the refrigerant, thus improving the refrigeration efficiency of the scroll compressor, which has high cost efficiency due to the simple structure and easy processing and manufacturing.
The foregoing and additional features and characteristics of the present application will become clearer from the following detailed description with reference to the accompanying drawings, which are merely examples and are not necessarily drawn to scale. Same reference numerals in the drawings indicate same parts. In the drawings:
Reference numerals are as follows:
Preferred embodiments of the present application will be described in detail hereinafter in conjunction with
In the following exemplary embodiments, the scroll compressor is exemplarily shown as a vertical scroll compressor. However, the scroll compressor according to the present application is not limited to this type, but can be any suitable type of scroll compressor, such as a horizontal scroll compressor.
As shown in
A cover 26 at the top of the housing 12 and a seat 28 located at the bottom of the housing 12 may be mounted to the housing 12, so as to define an internal volume of the scroll compressor 1. A lubricant, such as lubricating oil can be stored in an oil pool OR at the bottom of the housing 12 to lubricate various components of the scroll compressor 1.
The electric motor includes a stator 14 and a rotor 15. The rotor 15 is used to drive the drive shaft 16, so as to rotate the drive shaft 16 about its rotation axis relative to the housing 12. The drive shaft 16 may include an eccentric pin, which is mounted to a first end (a top end) of the drive shaft 16 or is integrally formed with the first end of the drive shaft 16. The drive shaft 16 may further include a central hole 52 and an eccentric hole (not shown), the central hole 52 is formed at a second end (a bottom end) of the drive shaft 16, and the eccentric hole extends upward from the central hole 52 to an end surface of the eccentric pin. An end (a lower end) of the central hole 52 can be immersed in the oil pool OR at the bottom of the housing 12 of the scroll compressor 1, so that for example, under the centrifugal force generated by the rotation of the drive shaft 16, the lubricating oil can be conveyed from the oil pool OR at the bottom of the housing 12, and the lubricating oil can flow upward through the central hole 52 and the eccentric hole and flow out from the end surface of the eccentric pin. The lubricating oil flowing out from the end surface of the eccentric pin can flow to lubricating oil supply zones, for example, formed between the eccentric pin and the orbiting scroll 24 and between the main bearing housing 11 and the orbiting scroll 24. The lubricating oil in the lubricating oil supply zones can lubricate rotating joints and sliding surfaces, for example, between the eccentric pin and the orbiting scroll 24 and between the main bearing housing 11 and the orbiting scroll 24.
The non-orbiting scroll 22 is mounted to the main bearing housing 11, for example, by using mechanical fasteners such as screw fastening members. The orbiting scroll 24 is axially supported by the main bearing housing 11 and is capable of orbiting supported by the main bearing housing 11. Specifically, a hub G of the orbiting scroll 24 can be rotatably connected to the eccentric pin of the drive shaft 16, the orbiting scroll 24 is driven by the electric motor via the drive shaft 16 (specifically the eccentric pin), so as to be able to perform translational rotation relative to the non-orbiting scroll 22 with the help of an Oldham ring, that is, the orbiting motion (that is, an axis of the orbiting scroll 24 orbits about an axis of the non-orbiting scroll 22, but the orbiting scroll 24 and the non-orbiting scroll 22 themselves do not rotate around their respective axes).
The orbiting scroll 24 and the non-orbiting scroll 22 form a compression mechanism CM suitable for compressing a working fluid (such as a refrigerant), in which the non-orbiting scroll 22 includes a non-orbiting scroll end plate 221, a non-orbiting scroll wrap 220 and an exhaust port V located at the center of the non-orbiting scroll 22; the orbiting scroll 24 includes an orbiting scroll end plate 241, an orbiting scroll wrap 240 and the hub G, and the compression mechanism CM includes an air inlet S (two configurations of the air inlet S are shown in
As for the refrigerant source, as shown in
In addition, as shown in
As described above, in the conventional technology, the refrigerant may produce turbulence or vortex and velocity gradient when it enters the suction cavity of the compression mechanism through the air inlet, which may cause pressure loss, reduce the enthalpy difference of the refrigerant, and thus reduce the refrigeration efficiency of the scroll compressor. In order to solve the above problems, the present application improves the non-orbiting scroll 22 of the scroll compressor 1. Specifically, a flow-guiding passage P is designed between the air inlet S and the suction cavity, and a streamlined design and designs for preventing turbulence, vortex and pressure loss are applied to the flow-guiding passage P, so as to significantly improve the refrigeration efficiency of the scroll compressor.
The preferred embodiments of the non-orbiting scroll 22 of the scroll compressor 1 according to the present application will be described in detail with reference to
As shown in
In this embodiment, preferably, the flow-guiding passage P extends from the starting end C to the engagement position A, and two inner side walls of the flow-guiding passage P are a first side wall W1 located on the non-orbiting scroll wrap 220 and a second side wall W2 located on the peripheral wall 223, the first side wall W1 and the second side wall W2 (including the bridging portion Q) converge from the engagement position A to the starting end C, that is, a second radial width X of the flow-guiding passage P defined by the first side wall W1 and the second side wall W2 (including the bridging portion Q) integrally decreases from the engagement position A toward the starting end C. It should be noted that this is not limited to the case that the second radial width X always progressively decreases from the engagement position A to the starting end C (which will be detailed below), and the second radial width X of the flow-guiding passage P is smaller than a first radial width Xm of an adjacent section adjacent to the flow-guiding passage P, that is, an extension section from the engagement position A in
It can be seen that the first section W11 and the second section W112 are curved in opposite directions as shown in the figure, and the curvature change value of the first section W11 is larger than the curvature change value of the second section W12. Therefore, although the second radial width X of the flow-guiding passage P integrally decreases from the engagement position A to the starting end C, the second radial width X does not always progressively decrease from the engagement position A to the starting end C. According to the different design of the streamline curved radian of the first side wall W1 and the second side wall W2 of the flow-guiding passage P in practical application, the value of the second radial width X of the flow-guiding passage P may fluctuate locally, for example, especially near point B, but may not always progressively decrease.
However, in the first embodiment, the second radial width X progressively decreases from the engagement position A to the starting end C to form a smooth and gradual streamline, which reduces the flow resistance of the refrigerant and the pressure gradient of the refrigerant. In addition, the above two-stage design with different curved directions and different curvature is specially designed for the flow of the refrigerant in the flow-guiding passage P, which can significantly reduce the turbulence and pressure loss of the refrigerant, thus providing better flow-guiding effect for the refrigerant.
It should be noted here that, as described above, in this embodiment, the air inlet S in the peripheral wall 223 has the configuration in
More preferably, with regard to the first section W11 and the second section W12 taking the position of point B as the boundary, the position of point B can be adjusted according to the actual application requirements to adjust the flow of the refrigerant, for example, according to the different requirements of an intake volume, a flow rate and a pressure of the refrigerant, point B can be located at a position extending from the starting end C to about ⅕ to ⅔ of a length of the first side wall W1, that is, the first section W11 accounts for about ⅕ to ⅔ of the length of the first side wall W1. Preferably, in this embodiment, point B can be located at a position from the starting end C to about ⅓ of the length of the first side wall W1, that is, the first section W11 accounts for about ⅓ of the length of the first side wall W1, and the second section W12 accounts for about ⅔ of the length of the first side wall W1, which has a better inhibition effect on turbulence and can reduce the pressure loss of the refrigerant.
In addition, based on the above streamlined design of the first side wall W1, a first radial thickness Y of the flow-guiding wrap section P20 at the flow-guiding passage P increases from the engagement position A to the starting end C, and the first radial thickness Y satisfies: Ym≤Y≤3Ym, where Ym represents a second radial thickness of the non-orbiting scroll wrap 220 at the above adjacent section (including the engagement position A) adjacent to the flow-guiding passage P.
In addition, preferably, as shown in
In addition, it should be pointed out that although in the above embodiments and the embodiments described below, the flow-guiding passage P extends from the starting end C to the engagement position A, as described above, the flow-guiding passage P can also be limited to extending only along a part of the wrap section from the starting end C to the engagement position A of the non-orbiting scroll wrap 220. That is to say, although in the specific embodiment herein, the flow-guiding passage P extends from the starting end C to the engagement position A, and the engagement position A is used to describe the relevant features in the flow-guiding passage P, it should be clear that all relevant features described herein about the flow-guiding passage P, such as the corresponding proportional value, etc., are limited by an extension range of the flow-guiding passage P itself, that is, compared with the case where the flow-guiding passage P extends from the starting end C to the engagement position A, when the flow-guiding passage P only extends along a part of the wrap section from the starting end C to the engagement position A of the non-orbiting scroll wrap 220 and does not extend to the engagement position A, some features that may originally be located at, adjacent to or extended to the engagement position A may be also far away from the engagement position A.
In the above embodiments, the curved directions and streamline design of the two side walls of the flow-guiding passage P and the adjustment of the width of the flow-guiding passage P are mainly adopted to realize the optimal flow-guiding effect for the refrigerant. However, the present application is not limited thereto, and the internal volume and related flow-guiding effect of the flow-guiding passage P can be better adjusted by further adjusting the depth of the flow-guiding passage P along the axial direction of the non-orbiting scroll 22, for example,
As shown in
Preferably, in this embodiment, the recessed portion P1 extends along a full length of the flow-guiding passage P, that is, extends form the starting end C to the engagement position A. However, the present application is not limited thereto, and corresponding adjustments can be made according to the actual application requirements. For example, the recessed portion P1 can extend from the starting end C to ¾ length, ½ length, ⅓ length of the flow-guiding passage P, and can be flexibly selected.
In addition, as best shown in
Further, in order to better adjust the flow-guiding effect of the flow-guiding passage P on the refrigerant, a value of a third radial width K of the recessed bottom wall P10 of the recessed portion P1 can be specially designed to preferably satisfy: 0.7Xm≤K≤Xm, where Xm represents the above first radial width. In addition, considering that if the second radial width X of the flow-guiding passage P described in the first embodiment is also smaller than the first radial width Xm, it can be further arranged that the third radial width K of at least a part of the recessed portion P1 is smaller than the corresponding second radial width X at the same position along the non-orbiting scroll wrap 220, to form a step portion T on the first side surface 222 of the non-orbiting scroll end plate 221 (as best shown in
In addition, for the recessed bottom wall P10, it is preferable to control a recessed angle G formed relative to the first side surface 222 of the non-orbiting scroll end plate 221, that is, it is preferable to set the recessed angle G less than or equal to 70°, that is, the recessed angles G formed by portions of the recessed bottom wall P10 relative to the first side surface 222 are less than or equal to 70°, so as to control the formation of turbulence and vortex, and adjust the pressure gradient of the refrigerant at each place.
It should be understood that although in the above second embodiment, the design of the recessed portion P1 is combined with the streamline design of the flow-guiding passage P disclosed in the first embodiment, the present application is not limited thereto. In some cases, the design of the recessed portion P1 disclosed in the second embodiment can be completely applied independently, and can also achieve the technical effect of reducing the formation of turbulence and vortex and reducing the pressure gradient of the refrigerant in different areas to a certain extent.
Other further modifications according to the present application are described below in conjunction with
This embodiment is a further improvement based on the combination of the streamline design of the flow-guiding passage P described in the first embodiment and the design of the recessed portion P1 described in the second embodiment. As shown in
In addition, preferably, turbulence, vortex or pressure gradient are more likely to occur in the second section W12 of the flow-guiding passage P, so as shown in the figure, the ventilation opening Q10 can preferably be defined at the position corresponding to the second section W12 to better play its role.
Similarly, other forms of ventilation openings can be defined according to actual application requirements to achieve similar object.
As shown in
As shown in
It should also be understood that such ventilation openings can also be similarly arranged in other parts of the peripheral wall 223 of the non-orbiting scroll 22 except for the bridging portion Q to achieve similar technical effects.
The design of this ventilation opening has a simple structure, and it can be processed into holes with various other shapes by various common methods such as drilling, milling, and 3D printing and drilling. In addition, this design can also be adopted independently, without in combination with the streamline design of the flow-guiding passage P described in the first embodiment and the design of the recessed portion P1 described in the second embodiment.
In order to better illustrate the beneficial technical effects of the present application, the inventor took the scroll compressor of 29 cc model as the research object and carried out the following comparative experiments: CFD comparative analysis was carried out with the scroll compressor using the non-orbiting scroll in the third embodiment of the present application and the scroll compressor using the non-orbiting scroll in the conventional technology. The results are shown in Table 1 below. The results show that: under the same working condition, the pressure loss at the air inlet of the scroll compressor using the non-orbiting scroll in the third embodiment of the present application can be reduced by 25.7% compared with the scroll compressor using the non-orbiting scroll in the conventional technology, which has fully verified the significant technical progress brought by the non-orbiting scroll and the scroll compressor according to the present application.
Apparently, various implementations can be further designed by combining or modifying different embodiments and each technical feature in different ways.
The non-orbiting scroll and the scroll compressor according to the preferred embodiment of the present application are described above in conjunction with the specific implementations. It can be understood that, the above description is merely exemplary rather than restrictive, and those skilled in the art can conceive various variations and modifications without departing from the scope of the present application with reference to the above description. These variations and modifications shall still fall in the protection scope of the present application.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202010731522.4 | Jul 2020 | CN | national |
| 202021507746.9 | Jul 2020 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2020/127716 | 11/10/2020 | WO |
