Fixed Vortex and Scroll Compressor

Abstract

The present invention provides a stationary scroll and a scroll compressor. The stationary scroll includes: a stationary scroll end plate; a stationary scroll wrap; and an outer peripheral wall in which an air inlet is provided. The stationary scroll wrap includes a starting end joined to the outer peripheral wall, a joining position to be joined to the radially outermost end of the orbiting scroll wrap of the orbiting scroll of the scroll compressor, and a wrap section extending from the starting end to the joining position. The stationary scroll further includes a guiding flow passage in fluid communication with the air inlet, the guiding flow passage extending from the starting end and along at least a part of the wrap section. The wrap section includes a first side wall located in the guiding flow passage, and the first side wall includes a first section having a first center of curvature and a second section having a second center of curvature respectively located on opposite sides of the first side wall in the radial direction. The stationary scroll and the scroll compressor can optimize the guiding of the refrigerant, improve the refrigeration efficiency of the scroll compressor, and have a simple structure and are easy to process and manufacture.

Description

Technical Field

[0001] The present invention relates to the field of compressors, and particularly to a stationary scroll and a scroll compressor including the stationary scroll. Background Art

[0002] This section provides background information related to the present invention, which does not necessarily constitute prior art.

[0003] Compressors (such as scroll compressors) can be applied in, for example, refrigeration systems, air-conditioning systems, and heat pump systems. A scroll compressor includes a compression mechanism, and the compression mechanism includes a stationary scroll and an orbiting scroll. The stationary scroll and the orbiting scroll engage with each other to define an open suction chamber and a series of closed compression chambers. And for a low-pressure-side scroll compressor, an air inlet is usually provided in the outer peripheral wall of the stationary scroll, and the air inlet is in fluid communication with the suction chamber. Refrigerant enters the suction chamber through the air inlet and is supplied to a series of closed compression chambers inside the compression mechanism to compress the refrigerant.

[0004] However, in the scroll compressors of the prior art, when the refrigerant enters the suction chamber through the air inlet, turbulence or eddy currents and velocity gradients may be generated, resulting in pressure loss, reducing the enthalpy difference of the refrigerant, and thus reducing the refrigeration efficiency of the scroll compressor. Therefore, it is necessary to further improve the scroll compressor to improve the utilization efficiency of the refrigerant and further improve the refrigeration efficiency of the scroll compressor. Summary of the Invention

[0005] This section provides a general overview of the present invention, rather than a full disclosure of the entire scope of the present invention or all features of the present invention.

[0006] The object of the present invention is to improve in one or more of the above-mentioned technical problems. Generally speaking, the present invention provides a stationary scroll as described below and a scroll compressor including the stationary scroll, which can optimize the flow of the refrigerant during the process of entering the compression mechanism, thereby significantly reducing the pressure loss of the refrigerant and the reduction of the enthalpy difference, and thus improving the refrigeration efficiency of the scroll compressor.

[0007] According to one aspect of the present invention, there is provided a stationary scroll of a scroll compressor, comprising:

[0008] A stationary scroll end plate;

[0009] A stationary scroll spiral extending from a first side surface of the stationary scroll end plate; and

[0010] An outer peripheral wall extending from the first side surface and located radially outside the stationary scroll spiral, surrounding the stationary scroll spiral, and an air inlet is provided in the outer peripheral wall.

[0011] The stationary scroll wrap includes a starting end joined to the outer peripheral wall and a joining position to be joined to the radially outermost end of the orbiting scroll wrap of the orbiting scroll of the scroll compressor, and the stationary scroll wrap includes a scroll section extending from the starting end to the joining position.

[0012] Characterized in that, the stationary scroll further includes a flow guiding passage fluidly connected to the air inlet, the flow guiding passage extends from the starting end and extends along at least a part of the scroll section.

[0013] The scroll section includes a first side wall located in the flow guiding passage, the first side wall includes a first section extending from the starting end with a first center of curvature and a second section extending from the first section with a second center of curvature, and the first center of curvature and the second center of curvature are respectively located on the radially opposite sides of the first side wall.

[0014] The above design of two sections with different bending directions is specifically designed for the flow of the refrigerant in the flow guiding passage, which can significantly reduce the turbulence and pressure loss of the refrigerant, so as to provide a better flow guiding effect for the refrigerant.

[0015] According to a preferred embodiment of the present invention, the first section extends from the starting end to about 1 / 5 to 2 / 3 of the length of the first side wall, and the curvature change value of the first section is greater than that of the second section, so as to have a better inhibitory effect on turbulence and reduce the pressure loss of the refrigerant.

[0016] According to a preferred embodiment of the present invention, in the flow guiding passage, the maximum curvature is at the starting end.

[0017] According to a preferred embodiment of the present invention, the spacing between the outer peripheral wall and the stationary scroll wrap is a first radial width Xm at the joining position, the starting end forms a fillet, and the radius of curvature Rc of the fillet satisfies: 2mm ≤ Rc ≤ 0.4Xm.

[0018] The starting end of the fillet with such a curvature is combined with the first side wall and the second side wall of the aforementioned streamlined design, so that when the refrigerant enters the flow guiding passage through the air inlet, no eddy current is formed at the starting end, and the turbulence in the flow guiding passage can be significantly reduced, thereby reducing the pressure gradient of the refrigerant in the flow guiding passage, reducing the pressure loss, and further improving the refrigeration efficiency of the scroll compressor.

[0019] According to a preferred embodiment of the present invention, along the direction from the joint position to the starting end, the first radial thickness of the guiding scroll section that defines the guiding flow passage of the scroll section increases, and the first radial thickness is greater than or equal to the second radial thickness of the fixed vortex scroll at the joint position and less than or equal to 3 times the second radial thickness.

[0020] According to a preferred embodiment of the present invention, the guiding flow passage includes a recessed portion recessed with respect to the first side surface. The recessed portion includes a recessed bottom wall, and the recessed depth L of the recessed bottom wall with respect to the first side surface satisfies: L ≤ 0.3H, where H is the axial height of the fixed vortex scroll. The internal volume of the guiding flow passage and the related guiding effect can be better adjusted by further adjusting the depth dimension of the guiding flow passage along the axial direction of the fixed vortex.

[0021] According to a preferred embodiment of the present invention, the recessed depth increases towards the starting end. Thereby, the refrigerant can be smoothly guided into the subsequent suction cavity, which is beneficial to reducing the formation of turbulence and eddy currents, and can reduce the pressure gradient of the refrigerant in different regions of the guiding flow passage.

[0022] According to a preferred embodiment of the present invention, the recessed bottom wall includes an inclined slope, a horizontal plane, a curved surface or a combination thereof.

[0023] According to a preferred embodiment of the present invention, the distance between the outer peripheral wall and the fixed vortex scroll is the first radial width Xm at the joint position. The third radial width K of the recessed portion satisfies: 0.7Xm ≤ K < Xm, and the guiding flow passage has a second radial width. The third radial width of at least a part of the recessed portion is less than the second radial width at the corresponding position of the guiding flow passage along the extending direction of the fixed vortex scroll, so as to form a stepped portion on the first side surface.

[0024] According to a preferred embodiment of the present invention, the recessed angle of the recessed bottom wall with respect to the first side surface is less than or equal to 70°.

[0025] According to a preferred embodiment of the present invention, at least one ventilation opening is provided in the outer peripheral wall, so that the refrigerant can enter the guiding flow passage through the at least one ventilation opening.

[0026] According to a preferred embodiment of the present invention, the outer peripheral wall includes a bridging portion adjacent to the air inlet at the axial end of the outer peripheral wall, and the at least one ventilation opening is provided at the bridging portion.

[0027] Through the flow path of this branch, it is possible to disperse the turbulent flow or eddy current that may occur in the flow guiding passage and balance the pressure gradient in each region of the flow guiding passage, thereby improving the refrigeration efficiency of the scroll compressor.

[0028] According to a preferred embodiment of the present invention, one circumferential side of the air inlet is substantially flush with the starting end.

[0029] According to another aspect of the present invention, a scroll compressor is provided, which includes the fixed scroll as described above.

[0030] In summary, the fixed scroll and the scroll compressor according to the present invention at least provide the following beneficial technical effects: By providing the flow guiding passage and the ventilation opening with the above configurations, the fixed scroll and the scroll compressor according to the present invention can optimize the flow of the refrigerant during the process of entering the compression mechanism, thereby significantly reducing the pressure loss and enthalpy difference reduction of the refrigerant, and thus improving the refrigeration efficiency of the scroll compressor. Moreover, its structure is simple, easy to process and manufacture, and has high cost-effectiveness. Description of the Drawings

[0031] According to the following detailed description with reference to the drawings, the foregoing and additional features and characteristics of the present invention will become clearer. These drawings are only for illustration and are not necessarily drawn to scale. The same reference numerals are used in the drawings to indicate the same components. In the drawings:

[0032] Figure 1 A longitudinal sectional view of a scroll compressor according to the present invention is shown;

[0033] Figure 2a Shown Figure 1 A perspective view of the fixed scroll in, in which an air inlet cover installed at the air inlet of the fixed scroll is shown;

[0034] Figure 2b Shown Figure 2a A perspective view of another angle of the fixed scroll in, in which the air inlet cover is removed to show the air inlet of the fixed scroll;

[0035] Figure 2c Another configuration of the air inlet of the fixed scroll of the scroll compressor according to the present invention is shown;

[0036] Figure 3 A plan view of the fixed scroll according to the first embodiment of the present invention is shown, in which the engagement between the fixed scroll spiral and the moving scroll spiral is schematically shown;

[0037] Figure 4 Shown Figure 3 A partial enlarged view of the fixed scroll in;

[0038] Figure 5Shows a three-dimensional view of a fixed scroll according to a second embodiment of the present invention;

[0039] Figure 6 Shows Figure 5 A partially enlarged view of the fixed scroll in;

[0040] Figure 7 Shows Figure 5 A partial longitudinal sectional view of the fixed scroll in;

[0041] Figure 8 Shows Figure 5 Another partial longitudinal sectional view of the fixed scroll in from another angle;

[0042] Figure 9 Shows a three-dimensional view of a fixed scroll according to a third embodiment of the present invention;

[0043] Figure 10 Shows a three-dimensional view of a fixed scroll according to a fourth embodiment of the present invention; and

[0044] Figure 11 Shows a three-dimensional view of a fixed scroll according to a fifth embodiment of the present invention.

[0045] List of reference numerals

[0046] Scroll compressor 1; housing 12; including stator 14; rotor 15; drive shaft 16; main bearing seat 11; orbiting scroll 24; fixed scroll 22; cover 26; base 28; oil sump OR; center hole 52

[0047] Hub portion M; compression mechanism CM; fixed scroll end plate 221; fixed scroll spiral 220; exhaust port V

[0048] Orbiting scroll end plate 241; orbiting scroll spiral 240; outer peripheral wall 223; intake port S

[0049] Refrigerant inlet 120; intake hood D; bridging portion Q; flow guiding passage P; first side wall W1

[0050] Second side wall W2; starting end C; joining position A; second radial width X; first radial width Xm; first segment W11; second segment W12; point B; bottom radial width X'; outer edge S10

[0051] First radial thickness Y; second radial thickness Ym; curvature radius Rc of the rounded corner; recessed portion P1

[0052] Recessed bottom wall P10; recessed depth L; axial height H of the fixed scroll spiral; inclined surface segment P12

[0053] Flat surface segment P14; third radial width K; stepped portion T; recessed angle G

[0054] Ventilation openings Q10, Q20, Q30; Deflector scroll section P20 Detailed implementation manners

[0055] The following will be combined with the attached Figures 1-11 The preferred implementation manners of the present invention will be described in detail. The following description is merely exemplary in nature and is not intended to limit the present invention and its application or use.

[0056] In the following exemplary implementation manners, the scroll compressor is exemplarily shown as a vertical scroll compressor. However, the scroll compressor according to the present invention is not limited to this type and can be any suitable type of scroll compressor, for example, a horizontal scroll compressor, etc.

[0057] Figure 1 A longitudinal sectional view of a scroll compressor according to the present invention is shown; Figure 2a Shown Figure 1 A perspective view of the fixed scroll 1 in [], in which an intake hood D installed at the intake port S of the fixed scroll 22 is shown; Figure 2b Shown Figure 2a Another perspective view of the fixed scroll 22 in [], in which the intake hood D is removed to show the intake port S of the fixed scroll 22; Figure 2c Another configuration of the intake port S of the fixed scroll 22 of the scroll compressor 1 is shown. First, the overall structure of the scroll compressor 1 according to the present invention will be described schematically with reference to Figures 1 to 2c The overall structure of the scroll compressor 1 according to the present invention will be described schematically.

[0058] As Figure 1 shown, the scroll compressor 1 may include a housing 12 in a generally cylindrical shape, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 11, a moving scroll 24, and a fixed scroll 22.

[0059] A cover 26 located at the top of the housing 12 and a base 28 located at the bottom of the housing 12 may be installed to the housing 12, thereby defining the internal volume of the scroll compressor 1. A lubricant such as lubricating oil may be stored in an oil sump OR inside the bottom of the housing 12 for lubricating various components of the scroll compressor 1.

[0060] The electric motor includes a stator 14 and a rotor 15. The rotor 15 is used to drive a drive shaft 16 to rotate the drive shaft 16 relative to the housing 12 about its axis of rotation. The drive shaft 16 may include an eccentric pin, which is mounted to the first end (top end) of the drive shaft 16 or integrally formed with the first end of the drive shaft 16. The drive shaft 16 may include a central hole 52 and an eccentric hole (not shown in the figure), the central hole 52 being formed at the second end (bottom end) of the drive shaft 16, and the eccentric hole extending upward from the central hole 52 to the end surface of the eccentric pin. The end (lower end) of the central hole 52 may be immersed in an oil sump OR at the bottom of the housing 12 of the scroll compressor 1, so that, for example, under the action of centrifugal force generated by the rotation of the drive shaft 16, lubricating oil can be transported from the oil sump 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 may flow into, for example, a lubricating oil supply area formed between the eccentric pin and the orbiting scroll 24 and between the main bearing seat 11 and the orbiting scroll 24. The lubricating oil in this lubricating oil supply area can lubricate, for example, the rotating joints and sliding surfaces between the eccentric pin and the orbiting scroll 24 and between the main bearing seat 11 and the orbiting scroll 24.

[0061] The stationary scroll 22 is mounted to the main bearing seat 11, for example, using mechanical fasteners such as screw fastening members. The orbiting scroll 24 is axially supported by the main bearing seat 11 and is supported by the main bearing seat 11 to be capable of performing an orbiting motion. Specifically, the hub M of the orbiting scroll 24 may be rotatably coupled to the eccentric pin of the drive shaft 16, and the orbiting scroll 24 is driven by the electric motor via the drive shaft 16 (specifically, the eccentric pin), so that it can perform a translational rotation relative to the stationary scroll 22 by means of a cross slip ring - that is, the orbiting (i.e., the axis of the orbiting scroll 24 revolves relative to the axis of the stationary scroll 22, but neither the orbiting scroll 24 nor the stationary scroll 22 rotates about their respective axes).

[0062] The orbiting scroll 24 and the stationary scroll 22 constitute a compression mechanism CM adapted to compress a working fluid (such as a refrigerant). Among them, the stationary scroll 22 includes a stationary scroll end plate 221, a stationary scroll spiral 220, and an exhaust port V located at the center of the stationary scroll 22; the orbiting scroll 24 includes an orbiting scroll end plate 241, an orbiting scroll spiral 240, and the above-mentioned hub M. The compression mechanism CM includes an intake port S located on the outer peripheral wall 223 of the stationary scroll 22 ( Figure 2b and Figure 2cThe intake port S of the two configurations shown, the open suction chamber defined by the fixed scroll 22 and the moving scroll 24, and a series of closed compression chambers for compressing a working fluid (such as a refrigerant), wherein the intake port S is in fluid communication with the suction chamber and in fluid communication with a refrigerant source outside the compression mechanism CM, so as to supply the refrigerant from the refrigerant source to the suction chamber of the compression mechanism CM and a series of closed compression chambers via the intake port S, thereby compressing the refrigerant, and discharging the compressed refrigerant from the exhaust port V at the center of the fixed scroll 22 to the outside of the compression mechanism CM.

[0063] Regarding the refrigerant source, as Figure 1 shown, on one side of the housing 12 of the scroll compressor 1, there is provided a refrigerant inlet 120, and in Figure 1 the shown scroll compressor 1, there is an intake hood D extending from the inlet 120 to the intake port S of the fixed scroll 22. In Figure 2a and 2b the perspective view of the fixed scroll 22 shown, the intake port S of the fixed scroll 22 and the intake hood D installed at the intake port S are clearly shown. The intake hood D can play a role in transporting and guiding the refrigerant, so that the refrigerant can directly flow from the inlet 120 into the intake port S, thereby preventing the refrigerant from staying in the environment outside the housing 12 and outside the compression mechanism CM to absorb heat and cause a reduction in enthalpy difference, thereby improving the refrigeration efficiency of the scroll compressor 1. However, it should be understood that although the following embodiments of the present invention and the drawings are described by taking the scroll compressor 1 with such an intake hood D as an example, the configuration of the present invention is not limited thereto, but also applicable to a scroll compressor without an intake hood D.

[0064] In addition, as shown in Figure 2b , the intake port S is an opening provided in the outer peripheral wall 223 of the fixed scroll 22, and the intake port S extends upward along the axial direction of the fixed scroll 22 from the bottom of the outer peripheral wall 223 to the top of the outer peripheral wall 223. However, the present invention is not limited thereto. Figure 2c shows another configuration of the intake port S of the fixed scroll 22 of the scroll compressor 1 according to the present invention. As shown in Figure 2c , compared with the configuration in Figure 2b , the intake port S does not extend upward to the top of the outer peripheral wall 223, but a part of the outer peripheral wall 223 is reserved above the intake port S to form a bridging portion Q. For these two configurations of the intake port S, they will be involved in the following specific embodiments and described in further detail.

[0065] As described above, in the prior art, when the refrigerant enters the suction chamber of the compression mechanism through the air inlet, turbulence or eddy currents and velocity gradients may occur, resulting in pressure loss, reducing the enthalpy difference of the refrigerant, and thus reducing the refrigeration efficiency of the scroll compressor. To solve the above problems, the present invention improves the fixed scroll 22 of the scroll compressor 1. Specifically, a flow guiding passage P is designed between the air inlet S and the suction chamber, and a streamline design is carried out for the flow guiding passage P, as well as designs for preventing turbulence, eddy currents, and pressure loss, thereby significantly improving the refrigeration efficiency of the scroll compressor.

[0066] The following will refer to Figures 3 to 11 Describe in detail each preferred embodiment of the fixed scroll 22 of the scroll compressor 1 according to the present invention to specifically describe the optimized design of various aspects of the flow guiding passage P.

[0067] Figure 3 A plan view of the fixed scroll 22 according to the first embodiment of the present invention is shown, which schematically shows the engagement between the fixed scroll spiral 220 and the moving scroll spiral 240; Figure 4 Shows Figure 3 A partial enlarged view of the fixed scroll 22 in

[0068] As Figure 3 Shown in Figure 2c The fixed scroll 22 includes: a fixed scroll end plate 221; a fixed scroll spiral 220 extending from the first side surface 222 of the fixed scroll end plate 221; and an outer peripheral wall 223 extending from the first side surface 222 of the fixed scroll end plate 221 and surrounding the outer periphery of the fixed scroll spiral 220 at the radial outside of the fixed scroll spiral 220. The fixed scroll 22 further includes a flow guiding passage P located in the space defined by the fixed scroll spiral 220, the fixed scroll end plate 221, and the outer peripheral wall 223. The flow guiding passage P extends from the starting end C where the fixed scroll spiral 220 engages with the outer peripheral wall 223, and along at least a part of the spiral section of the fixed scroll spiral 220 from the starting end C to the engagement position A where the fixed scroll spiral 220 is to engage with the radially outermost end of the moving scroll spiral 240 of the moving scroll 24 of the scroll compressor 1. An air inlet S is provided in the outer peripheral wall 223, and the flow guiding passage P is in fluid communication with the air inlet S. In this embodiment, the air inlet S in the outer peripheral wall 223 has the Figure 3 configuration as described above, and a bridging portion Q located above the air inlet S is shown in Figure 4 and

[0069] In this embodiment, preferably, the flow guiding passage P extends from the starting end C to the joining position A, and the two inner sidewalls of the flow guiding passage P are the first sidewall W1 located on the fixed vortex scroll 220 and the second sidewall W2 located on the outer peripheral wall 223. The first sidewall W1 and the second sidewall W2 (including the bridging portion Q) converge from the joining position A towards the starting end C. That is, the second radial width X of the flow guiding passage P defined by the first sidewall W1 and the second sidewall W2 (including the bridging portion Q) decreases as a whole from the joining position A towards the starting end C. It should be noted that this is not limited to the case where the second radial width X always decreases from the joining position A towards the starting end C (which will be described in detail below), and the second radial width X of the flow guiding passage P is smaller than the first radial width Xm of the adjacent section adjacent to the flow guiding passage P - that is, Figure 3 and Figure 4 the extension section starting from and including the joining position A in Figure 3 and Figure 4 As shown in

[0070] It can be seen that since the first section W11 and the second section W12 are curved arcs bending in opposite directions as shown in the figure, and the curvature change value of the first section W11 is greater than that of the second section W12, therefore, although as a whole, the second radial width X of the flow guiding passage P decreases from the joining position A towards the starting end C, the second radial width X does not necessarily always decrease from the joining position A towards the starting end C. Depending on the design of the streamlined bending arcs of the first sidewall W1 and the second sidewall W2 of the flow guiding passage P in practical applications, the value of the second radial width X of the flow guiding passage P may fluctuate locally - for example, especially near point B, rather than always decreasing.

[0071] However, in this first embodiment, the second radial width X decreases from the engagement position A towards the starting end C, thereby forming a smoothly tapered streamlined shape to reduce the resistance of refrigerant flow and the refrigerant pressure gradient. Moreover, the above-described design with two sections having different bending directions and different curvatures is also specifically designed for the flow of refrigerant in the flow guiding passage P, which can significantly reduce the turbulence and pressure loss of the refrigerant, thus providing a better flow guiding effect for the refrigerant.

[0072] It should be noted here that, as described above, in this embodiment, the air inlet S in the outer peripheral wall 223 has the configuration as described above Figure 2c in, and as shown in Figure 3 and Figure 4 the outer peripheral wall 223 includes a bridging portion Q located above the air inlet S, and the bridging portion Q will play a role in guiding the flow of the refrigerant. Therefore, the second radial width X of the flow guiding passage P mentioned above mainly refers to the second radial width X defined by the first side wall W1 and the second side wall W2 (the side wall of the section including the bridging portion Q). However, it should be understood that the second radial width X of the flow guiding passage P mentioned above actually also covers the radial width X' of the bottom of the flow guiding passage P adjacent to the air inlet S, which is defined by the outer edge S10 of the bottom of the flow guiding passage P and the first side wall W1. Specifically, as shown in Figure 3 and Figure 4 in order to provide a larger flow guiding space for the flow of the refrigerant, the second side wall W2 inside the bridging portion Q expands radially outwards, that is, when looking down from the first side surface 222 of the fixed vortex end plate 221 of the fixed vortex 22 as shown in Figure 3 and Figure 4 it is possible to see the outer edge S10 of the bottom of the flow guiding passage P through the second side wall W2 inside the bridging portion Q, that is, a part of the air inlet S can be seen. That is to say, the second radial width X defined by the first side wall W1 and the second side wall W2 is slightly larger than the radial width X' of the bottom of the flow guiding passage P. For the design of the radial width X', it can be similar to the design of the second radial width X defined by the first side wall W1 and the second side wall W2, that is, the radial width X' of the bottom of the flow guiding passage P is made smaller than the first radial width Xm of the adjacent section, and preferably, the radial width X' decreases or tapers from the engagement position A towards the starting end C. It should be understood that for the air inlet S having a configuration without the bridging portion Q as shown in, for example, Figure 2b in, the above design is also applicable.

[0073] More preferably, regarding the first segment W11 and the second segment W12 with the position of point B as the demarcation, the position of point B can be adjusted according to actual application requirements to adjust the flow of the refrigerant. For example, according to different requirements such as the intake volume, flow rate, and pressure of the refrigerant, point B can be located at a position approximately 1 / 5 to 2 / 3 of the length of the first side wall W1 extending from the starting end C - that is, the first segment W11 accounts for approximately 1 / 5 to 2 / 3 of the length of the first side wall W1. Preferably, in this embodiment, point B can be located at a position approximately 1 / 3 of the length of the first side wall W1 extending from the starting end C - that is, the first segment W11 accounts for approximately 1 / 3 of the length of the first side wall W1, and the second segment W12 accounts for approximately 2 / 3 of the length of the first side wall W1, thereby having a better inhibitory effect on turbulence and being able to reduce the pressure loss of the refrigerant.

[0074] In addition, based on the above streamline design of the first side wall W1, from the joint position A to the starting end C, the first radial thickness Y of the diversion scroll section P20 in the diversion passage P increases, and the first radial thickness Y satisfies: Ym ≤ Y ≤ 3Ym, where Ym represents the second radial thickness of the fixed vortex scroll 220 at the adjacent section (including the joint position A) adjacent to the diversion passage P.

[0075] And, preferably, as Figure 3 and Figure 4 shown in, in the diversion passage P, at the starting end C, it has the maximum curvature - that is, the minimum radius of curvature. And more preferably, a fillet is formed at the starting end C, and the radius of curvature Rc of the fillet satisfies: 2mm ≤ Rc ≤ 0.4Xm, where Xm represents the aforementioned first radial width. The starting end C of the fillet with such a radius of curvature is combined with the first side wall W1 and the second side wall W2 of the aforementioned streamline design, so that the refrigerant passes through as shown in 2c and Figures 3-4When the refrigerant enters the guiding flow passage P through the air inlet S shown in the figure, no eddy current is formed at the starting end C, and the turbulence in the guiding flow passage P can be significantly reduced, thereby reducing the pressure gradient of the refrigerant in the guiding flow passage P, reducing the pressure loss, and further improving the refrigeration efficiency of the scroll compressor 1. And it should be noted that although in the illustrated preferred embodiment, one side of the air inlet S perpendicular to the air inlet direction of the air inlet S is flush with the starting end C, the present invention is not limited thereto. In practical applications, the air inlet S can also be set to be farther away from the starting end C, that is, one side of the air inlet S perpendicular to the air inlet direction is not flush with the starting end C and is at a certain distance from the starting end C. Even in this case, due to the special design of the fillet and its curvature radius at the starting end C in the present invention, and combined with the aforementioned streamlined first side wall W1 and second side wall W2, the formation of eddy currents or turbulence in the guiding flow passage P, especially at the fillet of the starting end C, can be avoided or improved. Of course, preferably, as in the preferred embodiment of the present invention, setting the air inlet S such that one side of the air inlet S perpendicular to the air inlet direction is flush with the starting end C can best avoid the situation of eddy currents or turbulence.

[0076] In addition, it should be pointed out that although in the above embodiments and the embodiments to be described below, the guiding flow passage P extends from the starting end C to the joining position A, as described above, the guiding flow passage P can also be defined as extending only along a part of the spiral section of the fixed vortex scroll 220 from the starting end C to the joining position A. That is to say, although in the specific implementation manner herein, it is default that the guiding flow passage P extends from the starting end C to the joining position A, and the joining position A is used to describe the relevant features in the guiding flow passage P, it should be clear that each relevant feature described herein about the guiding flow passage P - such as the corresponding proportional value, etc. - is limited by the extension range of the guiding flow passage P itself. That is to say, compared with the situation where the guiding flow passage P extends from the starting end C to the joining position A, when the guiding flow passage P only extends along a part of the spiral section of the fixed vortex scroll 220 from the starting end C to the joining position A and does not extend to the joining position A, some feature parts that may originally be located at, adjacent to, or extend to the joining position A will also be away from the joining position A.

[0077] In the above embodiments, the optimized guiding effect on the refrigerant is mainly achieved by adjusting the orientation and streamlined design of the two side walls of the guiding flow passage P and the width dimension of the guiding flow passage P. However, the present invention is not limited thereto, and the internal volume of the guiding flow passage P and the related guiding effect can also be better adjusted by further adjusting the depth dimension of the guiding flow passage P along the axial direction of the fixed vortex 22, for example Figures 5-8 shows the fixed vortex 22 according to the second embodiment of the present invention. The second embodiment will be described in detail below in conjunction with Figures 5-8 Describe the second embodiment in detail.

[0078] Figure 5 A perspective view of the fixed scroll 22 of the second embodiment is shown; Figure 6 Shown is Figure 5 A partially enlarged view of the fixed scroll 22 in Figure 7 Shown is Figure 5 A partial longitudinal sectional view of the fixed scroll 22 in Figure 8 Shown is Figure 5 Another partial longitudinal sectional view of the fixed scroll 22 in

[0079] As Figure 5 shown, in this embodiment, the air inlet S in the outer peripheral wall 223 of the fixed scroll 22 has the configuration as described above, that is, there is no bridging portion above the air inlet S. And, in this embodiment, the flow guiding passage P has a streamlined design similar to that of the flow guiding passage P in the aforementioned first embodiment along the radial direction of the fixed scroll 22. The difference is that: in this embodiment, the flow guiding passage P further includes a recessed portion P1 recessed with respect to the first side surface 222 of the fixed scroll end plate 221. The recessed portion P1 includes a recessed bottom wall P10, and the recessed depth L of the recessed bottom wall P10 with respect to the first side surface 222 satisfies: L ≤ 0.3H, where H is the axial height of the fixed scroll scroll 220 (as best shown in Figure 2b ), and preferably, the recessed depth L increases from the aforementioned joint position A towards the starting end C, thereby enabling the first segment W11 extending from the starting end C to have a relatively larger axial space for receiving more refrigerant, which is beneficial for alleviating the impact of the refrigerant when entering the flow guiding passage P. Subsequently, with the recessed depth L gradually decreasing as it extends from point B to the joint position A, the refrigerant can be smoothly diverted into the subsequent suction chamber, which is beneficial for reducing the formation of turbulence and eddies, and can reduce the pressure gradient of the refrigerant in different regions of the flow guiding passage P. Figure 7

[0080] Preferably, in this embodiment, the recessed portion P1 extends along the entire length of the fluid passage P, that is, from the starting end C to the joint position A. However, the present invention is not limited thereto, and corresponding adjustments can be made according to actual application requirements. For example, the recessed portion P1 can extend 3 / 4 length, 1 / 2 length, 1 / 3 length, etc. of the fluid passage P from the starting end C, and can be flexibly selected.

[0081] In addition, as Figure 6 and Figure 8 ​As best shown in [reference], the recessed bottom wall P10 includes an inclined surface segment P12 extending from the joining position A and the remaining planar segment P14 extending to the starting end C. Regarding the respective lengths of the inclined surface segment P12 and the planar segment P14, they can both be adjusted according to actual application requirements, as long as the formation of turbulence and eddy currents can be reduced, and the pressure gradient of the refrigerant in different regions of the flow passage P can be reduced. For example, the recessed bottom wall P10 can also only include an inclined surface extending from the starting end C to the joining position A, without including a planar segment. Or, the recessed bottom wall P10 can also include a curved surface or various possible combinations of a curved surface with an inclined inclined surface or a horizontal plane.

[0082] Furthermore, in order to facilitate better adjustment of the guiding effect of the flow passage P on the refrigerant, the value of the third radial width K of the recessed bottom wall P10 of the recessed portion P1 can be specifically designed to preferably make 0.7Xm ≤ K < Xm, where Xm represents the aforementioned first radial width. And considering that, as mentioned in the first embodiment, the second radial width X of the flow passage P is also smaller than the first radial width Xm, it can be further set such 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 fixed vortex scroll 220, thereby forming a step portion T on the first side surface 222 of the fixed vortex end plate 221 (as best shown in [reference]). Figure 7 in [reference] Figure 6 The corresponding step portion T is also shown in [reference]. In the figure, the step portion T is located on one side of the first side wall W1, and extends from the joining position A to a segment of the first side wall W1 and gradually narrows without extending to the starting end C. Regarding the third radial width K and the corresponding step portion T, they can be flexibly adjusted according to actual application requirements. And it should be understood that the step portion T can also be located on one side of the second side wall W2.

[0083] In addition, for the recessed bottom wall P10, it is preferably necessary to control the recessed angle G formed with respect to the first side surface 222 of the fixed vortex end plate 221, that is, preferably make the recessed angle G less than or equal to 70°. That is to say, the recessed angle G formed by each part of the recessed bottom wall P10 with respect to the first side surface 222 is less than or equal to 70°, so as to control the formation of turbulence and eddy currents and adjust the pressure gradient of the refrigerant at each place.

[0084] It should be understood that although in the above second embodiment, the design of the recessed portion P1 is combined with the streamlined design of the fluid passage P disclosed in the first embodiment, however, the present invention is not limited thereto. In some cases, the design of the recessed portion P1 disclosed in the second embodiment can be completely independently applied, and can also achieve the technical effects of reducing the formation of turbulence and eddy currents and reducing the pressure gradient of the refrigerant in different regions to a certain extent.

[0085] The following will be combined with the attached drawings Figures 9-11 to describe other further modifications according to the present invention.

[0086] Figure 9 Fig. shows a perspective view of the fixed scroll 22 according to the third embodiment of the present invention.

[0087] This embodiment is a further improvement based on the combination of the streamline design of the fluid passage P described in the first embodiment and the design of the recessed portion P1 described in the second embodiment. As Figure 9 shown, in this embodiment, the air inlet S in the outer peripheral wall 223 has the configuration as described above Figure 2c and the bridging portion Q located above the air inlet S is shown in Figure 9 . The improvement of this embodiment mainly lies in that a long ventilation opening Q10 is provided in the bridging portion Q, so that a part of the refrigerant can enter the flow guiding passage P through the ventilation opening Q10. By means of this branched flow path, the turbulence or eddy current that may appear in the flow guiding passage P can be dispersed, and the pressure gradient in each region of the flow guiding passage P can be balanced, thereby improving the refrigeration efficiency of the scroll compressor 1.

[0088] And preferably, turbulence, eddy current or pressure gradient are more likely to occur in the second section W12 of the flow guiding passage P. Therefore, as shown in the figure, preferably, the ventilation opening Q10 can be arranged at a position corresponding to the second section W12 to better play a role.

[0089] Similarly, other forms of ventilation openings can be set according to actual application requirements to achieve similar purposes. As Figure 10 shown, Fig. shows a perspective view of the fixed scroll according to the fourth embodiment of the present invention; and Figure 11 Fig. shows a perspective view of the fixed scroll according to the fifth embodiment of the present invention.

[0090] In Figure 10 it is shown that two circular ventilation openings Q20 are adopted, and the spacing between the two ventilation openings Q20 can be adjusted according to needs to achieve the best technical effect, and the number of the ventilation openings Q20 can also be set according to needs.

[0091] As in Figure 11 it is shown that rows of honeycomb-shaped ventilation openings Q30 can enable more refrigerant to flow into the flow guiding passage P through the ventilation openings Q30, and these three rows of ventilation openings Q30 can also be positioned as shown in the figure to respectively correspond to the first section W11 and the second section W12, which can be set according to needs.

[0092] It should also be understood that such ventilation openings can similarly be provided in other parts of the outer peripheral wall 223 of the fixed scroll 22 except for the bridging portion Q to achieve a similar technical effect.

[0093] The design structure of such ventilation openings is simple, and various common methods such as punching, milling slots, 3D printing drilling, etc. can be used to process and form holes with various other shapes. And this design can also be used alone without being combined with the streamlined design of the fluid passage P described in the first embodiment and the design of the recessed portion P1 described in the second embodiment.

[0094] To better illustrate the beneficial technical effects of the present invention, the inventor took a 29cc model scroll compressor as the research object and conducted the following comparative experiments: a CFD comparative analysis was carried out on a scroll compressor with the fixed scroll in the third embodiment of the present invention and a scroll compressor with the fixed scroll of the prior art. The results are shown in Table 1 below. The results show that: under the same working conditions, compared with the scroll compressor with the fixed scroll of the prior art, the scroll compressor with the fixed scroll in the third embodiment of the present invention can reduce the pressure loss at the air inlet by 25.7%. This fully verifies the significant technical progress brought by the fixed scroll and the scroll compressor of the present invention.

[0095]

[0096] Obviously, by combining different embodiments and various technical features in different ways or modifying them, various different embodiments can be further designed.

[0097] The fixed scroll and the scroll compressor according to the preferred embodiments of the present invention have been described above in conjunction with specific embodiments. It can be understood that the above description is only exemplary and not restrictive. Without departing from the scope of the present invention, those skilled in the art can think of various variations and modifications with reference to the above description. These variations and modifications are also included in the protection scope of the present invention.

Claims

1. A fixed scroll (22) of a scroll compressor (1), comprising: A fixed scroll end plate (221); A fixed scroll spiral (220) extending from a first side surface (222) of the fixed scroll end plate; And An outer peripheral wall (223) extending from the first side surface and located radially outside the fixed scroll spiral, around the fixed scroll spiral, and an air inlet (S) is provided in the outer peripheral wall. The fixed scroll spiral includes a starting end (C) joined to the outer peripheral wall and a joining position (A) to be joined to a radially outermost end of a moving scroll spiral of a moving scroll of the scroll compressor, and the fixed scroll spiral includes a spiral section extending from the starting end to the joining position. Characterized in that the fixed scroll further includes a flow guiding passage (P) in fluid communication with the air inlet, the flow guiding passage extends from the starting end and extends along at least a part of the spiral section. The spiral section includes a first side wall located in the flow guiding passage, the first side wall includes a first section (W11) extending from the starting end and having a first center of curvature and a second section (W12) extending from the first section and having a second center of curvature, and the first center of curvature and the second center of curvature are respectively located on opposite sides of the first side wall in the radial direction. The first section extends from the starting end to about 1 / 5 to 2 / 3 of the length of the first side wall, and the curvature change value of the first section is greater than the curvature change value of the second section.

2. The fixed scroll according to claim 1, wherein In the flow guiding passage, the curvature is the largest at the starting end.

3. The fixed scroll according to claim 1, characterized in that, The spacing between the outer peripheral wall and the fixed scroll spiral is a first radial width Xm at the joining position, the starting end forms a rounded corner, and the radius of curvature Rc of the rounded corner satisfies: 2 mm ≤ Rc ≤ 0.4Xm.

4. The fixed scroll according to claim 1, characterized in that, Along the direction from the joining position to the starting end, the first radial thickness (Y) of the spiral section defining the flow guiding passage (P20) of the fixed scroll spiral increases, and the first radial thickness is greater than or equal to the second radial thickness (Ym) of the fixed scroll spiral at the joining position and less than or equal to 3 times the second radial thickness.

5. The fixed scroll according to claim 1, wherein The flow guiding passage includes a recessed portion (P1) recessed with respect to the first side surface, the recessed portion includes a recessed bottom wall (P10), and the recessed depth L of the recessed bottom wall with respect to the first side surface satisfies: L ≤ 0.3H, where H is the axial height of the fixed scroll spiral.

6. The fixed scroll according to claim 5, wherein The recessed depth increases towards the starting end.

7. The fixed scroll according to claim 5, wherein The recessed bottom wall includes an inclined slope, a horizontal plane, a curved surface or a combination thereof.

8. The fixed scroll according to claim 5, wherein The spacing between the outer peripheral wall and the fixed scroll spiral is a first radial width Xm at the joining position, the third radial width K of the recessed portion satisfies: 0.7Xm ≤ K < Xm, and the flow guiding passage has a second radial width (X), and the third radial width of at least a part of the recessed portion is less than the second radial width at the corresponding position of the flow guiding passage along the extending direction of the fixed scroll spiral to form a stepped portion (T) on the first side surface.

9. The fixed scroll according to claim 5, characterized in that, The depression angle (G) of the bottom wall of the depression relative to the first side surface is less than or equal to 70°.

10. The fixed scroll according to any one of claims 1-9, characterized in that, At least one ventilation opening is provided in the outer peripheral wall so that the refrigerant can enter the flow guiding passage through the at least one ventilation opening.

11. The fixed scroll according to claim 10, wherein, The outer peripheral wall includes a bridging portion adjacent to the air inlet at the axial end of the outer peripheral wall, and the at least one ventilation opening is provided at the bridging portion.

12. The fixed scroll according to claim 1, wherein One circumferential side of the air inlet is substantially flush with the starting end.

13. A scroll compressor, characterized in that, Comprising a fixed scroll as claimed in any one of claims 1-12.

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