Method and device for manufacturing a slot at the beginning of a scroll, and scroll compressor

Abstract

The application provides a manufacturing method and device of a start end slot of a scroll ring and a scroll compressor. The method comprises the following steps: determining the position and shape of an exhaust hole and the communication angle between a working chamber and the exhaust hole according to the motion state of a moving scroll ring and a stationary scroll ring, wherein the moving scroll ring and the stationary scroll ring enclose the working chamber; determining two meshing points of the start end when the moving scroll ring and the stationary scroll ring are engaged according to the communication angle between the working chamber and the exhaust hole; performing air pressure simulation in the working chamber to obtain the pressure distribution in the working chamber under the working state and analyzing the pressure unevenness of the innermost pair of working chambers; setting a start end slot on the start end of the moving scroll ring and the start end of the stationary scroll ring respectively, wherein the two meshing points are the two end points of the start end slot, and the depth and size of the start end slot are determined according to the pressure unevenness. The application solves the problem of the inner leakage caused by the uneven pressure of the innermost pair of working chambers in the prior art, which leads to the decrease of the volumetric efficiency of the compressor and the increase of the power consumption.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, and more particularly to a manufacturing method and device for a slot at a starting end of a scroll, and a scroll compressor. BACKGROUND

[0002] Scroll compressors have the characteristics of high efficiency, small vibration and low noise, and are widely used in the field of automotive air conditioning systems. In the working process of the scroll compressor, the volume of the working chamber is formed by the matching of the dynamic scroll and the static scroll. Due to the rotation of the dynamic scroll, the working chamber moves from the outside to the inside, and its volume also changes, thereby realizing the processes of suction, compression and discharge of refrigerant gas. The dynamic scroll and the static scroll are the core components of the scroll compressor, and the design of the scroll (dynamic scroll and static scroll) is the key to ensuring the high-efficiency and reliable operation of the compressor.

[0003] Under some specific working conditions, the traditional scroll and discharge hole design causes the most inside pair of working chambers to be unable to communicate with the discharge hole at the same time, resulting in a large pressure difference between them and causing internal leakage, thereby reducing the efficiency of the scroll compressor and increasing power consumption.

[0004] Therefore, the prior art still needs to be improved and developed. SUMMARY

[0005] The present application aims to provide a manufacturing method and device for a slot at a starting end of a scroll, and a scroll compressor, to solve the problem of internal leakage caused by uneven pressure of the most inside pair of working chambers in the prior art, which reduces the volumetric efficiency of the compressor and increases power consumption.

[0006] To achieve the above-mentioned purpose, the technical solution adopted by the present application is:

[0007] On the one hand, the present application provides a manufacturing method for a slot at a starting end of a scroll, the method comprising the steps of:

[0008] According to the movement state of the dynamic scroll and the static scroll, the position, shape and communication angle of the working chamber and the discharge hole are determined, wherein the dynamic scroll and the static scroll enclose the working chamber;

[0009] According to the communication angle of the working chamber and the discharge hole, the two meshing points of the starting end when the dynamic scroll and the static scroll are meshed are determined;

[0010] The gas pressure in the working chamber is simulated to obtain the pressure distribution in the working chamber under the working state, and the unevenness of the pressure of the most inside pair of working chambers is analyzed;

[0011] The initial end of the dynamic vortex ring and the initial end of the static vortex ring are respectively provided with initial end cutting grooves, and the two meshing points are the two end points of the initial end cutting grooves.

[0012] Optionally, before the step of determining the position, shape and communication angle of the exhaust hole according to the motion state of the dynamic vortex ring and the static vortex ring, the method further comprises the step of:

[0013] The inside profile line and the outside profile line of the dynamic vortex ring and the inside profile line and the outside profile line of the static vortex ring are formed in the form of involute of a circle, and the inside profile line and the outside profile line are connected by a modified circular arc line and a connecting circular arc line at the initial end of the dynamic vortex ring and the initial end of the static vortex ring.

[0014] Optionally, in the step of forming the inside profile line and the outside profile line of the dynamic vortex ring and the inside profile line and the outside profile line of the static vortex ring in the form of involute of a circle, and connecting the inside profile line and the outside profile line by a modified circular arc line and a connecting circular arc line at the initial end of the dynamic vortex ring and the initial end of the static vortex ring:

[0015] The profile line of the dynamic vortex ring is the same as the profile line of the static vortex ring, and is symmetrically arranged;

[0016] The coordinate equation of the inside profile line of the static vortex ring is:

[0017]

[0018] The coordinate equation of the outside profile line of the static vortex ring is:

[0019]

[0020] Wherein, a is the base circle radius, and a is the starting angle of the involute, is the central surface involute angle of the static vortex ring;

[0021] The coordinate equation of the connecting circular arc line is:

[0022]

[0023] The coordinate equation of the modified circular arc line is:

[0024]

[0025] Wherein, β is the modified angle, d and γ are the vortex ring initial end modified parameters, r is the connecting circular arc radius, R is the modified circular arc radius, and ξ is the angle variable.

[0026] Optionally, in the step of determining the position, shape and communication angle of the exhaust hole according to the motion state of the dynamic vortex ring and the static vortex ring:

[0027] The exhaust hole is a circular hole, the working chamber is a first working chamber and a second working chamber which are symmetrical to each other, the first working chamber is formed by the outer wall of the dynamic scroll and the inner wall of the static scroll, and the second working chamber is formed by the inner wall of the dynamic scroll and the outer wall of the static scroll;

[0028] The motion state of the dynamic scroll and the static scroll is that the exhaust hole is connected with the first working chamber and is not connected with the second working chamber, at this time, the rotation angle of the main shaft of the dynamic scroll is the connection angle of the working chamber and the exhaust hole, and the rotation angle of the main shaft when the outermost circle of the dynamic scroll is closed with the outermost circle of the static scroll is the start angle 0°.

[0029] Optionally, the step of simulating the gas pressure in the working chamber to obtain the pressure distribution in the working chamber in the working state and analyzing the pressure unevenness of the innermost pair of working chambers comprises the following steps:

[0030] drawing a digital three-dimensional model based on the static scroll and the dynamic scroll in the model making software;

[0031] simulating and calculating the flow and heat transfer of the working medium in the working chamber in the digital three-dimensional model by the simulation software, and obtaining the pressure distribution in the working chamber;

[0032] calculating the pressure unevenness of the innermost pair of working chambers according to the pressure distribution in the working chamber.

[0033] Optionally, in the step of calculating the pressure unevenness of the innermost pair of working chambers according to the pressure distribution in the working chamber, the method for calculating the pressure unevenness of the innermost pair of working chambers is as follows:

[0034]

[0035] wherein p1 is the average pressure of the working medium in the first working chamber, the calculation time range of the average pressure is from θ d to θ t ; p2 is the average pressure of the working medium in the second working chamber, the calculation time range of the average pressure is from θ d to θ t , wherein θ d is the rotation angle of the main shaft of the dynamic scroll at the time when the first working chamber is connected with the exhaust hole, θ t is the rotation angle of the main shaft of the dynamic scroll at the time when the dynamic scroll is completely disengaged with the static scroll; and ε is the equivalent pressure unevenness.

[0036] Optionally, a start cutting groove is arranged at the start end of the dynamic scroll and the start end of the static scroll, respectively, wherein the two engagement points are the two end points of the start cutting groove, and the depth and size of the start cutting groove are determined according to the pressure unevenness.

[0037] The formula for determining the depth and size of the start end slot according to the pressure unevenness is:

[0038]

[0039] wherein h is the depth of the start end slot, H is the height of the dynamic scroll, R c is the radius of the arc of the start end slot, and l AB is the distance between the two meshing points.

[0040] Optionally, the start end slot is arranged on both the dynamic scroll and the static scroll, and the shapes of the start end slots are the same.

[0041] In another aspect, the application further provides a device for manufacturing a start end slot of a scroll, which comprises a memory and a processor, and the memory stores a manufacturing program of the start end slot of the scroll, and the manufacturing program of the start end slot of the scroll is run on the processor to realize the manufacturing method of the start end slot of the scroll as described above.

[0042] In a third aspect, the application further provides a scroll compressor, which comprises a dynamic scroll and a static scroll, and the dynamic scroll and the static scroll are matched to form a scroll compression structure.

[0043] The dynamic scroll is provided with a dynamic scroll, and the static scroll is provided with a static scroll, and the dynamic scroll and the static scroll are both provided with a start end slot, and the start end slot is manufactured by the manufacturing method of the start end slot of the scroll as described above.

[0044] The manufacturing method, device and scroll compressor of the start end slot of the scroll provided by the application have at least the following beneficial effects: the shape contour of the dynamic scroll and the static scroll is designed according to the working condition, the air pressure simulation of the working medium in the working chamber is performed by using the simulation software, the flow and heat transfer simulation calculation in the working chamber is realized, the pressure distribution in the working chamber is obtained, the equivalent pressure unevenness of the innermost pair of working chambers is obtained according to the pressure distribution, the depth and size of the start end slot of the scroll are determined according to the pressure unevenness, the disengagement position of the scroll is changed by the start end slot, the innermost pair of working chambers are simultaneously communicated with the exhaust hole to meet the exhaust requirement, the internal leakage caused by the pressure unevenness of the working chambers is reduced, and the operation efficiency of the scroll compressor is improved. The depth and size of the start end slot are determined according to the pressure unevenness of the two working chambers, accurate design basis is formed, the depth and size of the start end slot are more in line with practical requirements, and the stability of the dynamic scroll and the static scroll during scroll compression is enhanced. The working chamber pressure simulation calculation is performed by using the simulation software, and compared with the traditional design-experiment-design method, the method has the advantages of low cost and short cycle. BRIEF DESCRIPTION OF DRAWINGS

[0045] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or prior art description will be briefly introduced. Obviously, the drawings in the following description only constitute some embodiments of the present application, and for those skilled in the art, other drawings can also be obtained without creative labor.

[0046] Figure 1 An outline of the static scroll in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0047] Figure 2 An outline of the initial end of the static scroll in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0048] Figure 3 A schematic view of the moment when the first working cavity in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application is just communicated with the exhaust hole;

[0049] Figure 4 A schematic view of the moment when the dynamic scroll and the static scroll disengage in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0050] Figure 5 A schematic view of the position of the initial end slot set on the dynamic scroll and the static scroll in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0051] Figure 6 A schematic view of the moment when the outermost circle of the dynamic scroll and the static scroll in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application is fully opened; Figure 5

[0052] A schematic view of the moment when the initial angle is 0° in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application; Figure 7

[0053] A schematic view of the moment when the initial angle is 0° in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application; Figure 8

[0054] A schematic view of the moment when the initial angle is 0° in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application; Figure 9 Figure 8 A schematic view of the moment when the initial angle is 0° in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0055] Figure 10 A schematic view of the moment when the initial angle is 0° in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application;

[0056] Figure 11 A schematic view of the main flow in the manufacturing method of the initial end slot of the scroll in the first embodiment of the present application. ​

[0057] The following are the labeling elements in the figure:

[0058] 10. Static vortex ring; 11. Inner profile; 12. Outer profile; 13. Connecting arc; 14. Correction arc; 20. Moving vortex ring; 21. First working chamber; 22. Second working chamber; 23. Exhaust chamber; 30. Exhaust hole; 40. Starting groove. Detailed Implementation

[0059] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0060] Example 1

[0061] like Figure 11 As shown, this embodiment provides a method for manufacturing a groove at the beginning of a scroll ring, used to manufacture or design a moving scroll and a stationary scroll. In actual use, the stationary scroll is fixed, while the moving scroll rotates eccentrically relative to the stationary scroll under the drive of the main shaft. Figure 3 , Figure 4 As shown, during eccentric rotation, multiple working chambers are formed by the cooperation of the moving volute 20 on the moving volute disk and the stationary volute 10 on the stationary volute disk. The size of the working chambers changes during the movement, thereby achieving the compression of gas or liquid. In this embodiment, the volute includes a moving volute 20 and a stationary volute 10. Both the moving volute 20 and the stationary volute 10 are provided with an initial end groove 40. The method for manufacturing the initial end groove of this volute mainly includes the following steps:

[0062] Step S10: Determine the position and shape of the exhaust port and the connection angle between the working chamber and the exhaust port based on the motion state of the moving vortex and the stationary vortex, wherein the moving vortex and the stationary vortex form the working chamber.

[0063] like Figure 3 , Figure 4 , Figure 5 , Figure 6 As shown, the shapes of the moving scroll 20 and the stationary scroll 10 are designed according to the compressor's usage requirements. Once the shapes of the moving scroll 20 and the stationary scroll 10 are determined, the exhaust port 30 is designed, specifying its position and shape. This is typically related to the operating conditions of the compressor and needs to meet requirements such as pressure ratio and exhaust gas velocity. Furthermore, the communication angle between the working chamber and the exhaust port 30 needs to be determined in advance. Because the moving scroll 20 forms various working chambers with the stationary scroll 10 during rotation, such as... Figure 7As shown, for example, when the outermost circle of the movable scroll 20 and the fixed scroll 10 is fully open, the working medium (gas or liquid) can enter the inside of the movable scroll 20 and the fixed scroll 10 from the open openings. At this moment, a pair of working chambers (a first working chamber 21 and a second working chamber 22) are formed at the innermost side of the movable scroll 20 and the fixed scroll 10, and an exhaust chamber 23 is formed separately from the two working chambers. The exhaust chamber 23 is in communication with the exhaust hole 30. As shown in Figure 8 Then, the main shaft drives the movable scroll 20 to rotate. During the rotation of the movable scroll 20, the outermost circle of the movable scroll 20 and the fixed scroll 10 is slowly closed. When the outermost circle is fully closed, the rotation angle of the main shaft at this moment is the start angle 0° (0° start of suction, because after the closure, the circle is slowly opened, which is the starting point of suction). The main shaft continues to drive the movable scroll 20 to rotate, the exhaust chamber 23 is slowly reduced, and the two symmetrical working chambers at the innermost side are enlarged. When the first working chamber 21 is in communication with the exhaust hole 30, the rotation angle of the main shaft at this moment is the communication angle of the working chamber and the exhaust hole 30 (for example, as shown in Figure 3 The main shaft drives the movable scroll 20 to rotate, so that the exhaust hole 30 is in communication with the first working chamber 21 (for example, as shown in Figure 4 The main shaft drives the movable scroll 20 to rotate, so that the exhaust hole 30 is in communication with the first working chamber 21 (for example, as shown in Figure 5 、 Figure 6 and Figure 8 、 Figure 9 As can be seen from

[0064] Step S20, determining the two meshing points of the start end of the meshing of the movable scroll and the fixed scroll according to the communication angle of the working chamber and the exhaust hole.

[0065] During the rotation of the movable scroll, the start end of the movable scroll abuts against the inner wall of the fixed scroll, and the start end of the fixed scroll abuts against the inner wall of the movable scroll. At this moment, the two meshing points of the start end of the meshing of the movable scroll and the fixed scroll are formed (for example, points A and B in Figure 5 、 Figure 6 The two meshing points are the two end points of the start end slot.

[0066] Step S30, simulating the gas pressure in the working chamber to obtain the pressure distribution in the working chamber under the working state, and analyzing the pressure non-uniformity of the innermost pair of working chambers.

[0067] The working fluid in the working chamber is simulated using simulation software to realize the flow and heat transfer simulation calculations in the working chamber, and the pressure distribution in the working chamber is obtained. Then, based on the pressure distribution, the equivalent pressure non-uniformity of the innermost pair of working chambers is obtained.

[0068] Step S40: Set the starting end grooves at the beginning of the moving volute and the beginning of the stationary volute respectively, where the two meshing points are the two endpoints of the starting end grooves, and determine the depth and size of the starting end grooves according to the pressure non-uniformity.

[0069] like Figure 5 , Figure 6 As shown, the external contours of the moving scroll 20 and the stationary scroll 10 are designed according to the above-mentioned working conditions. Simulation software is used to perform gas pressure simulation on the working fluid inside the working chamber, realizing flow and heat transfer simulation calculations within the working chamber to obtain the pressure distribution. Based on this pressure distribution, the equivalent pressure non-uniformity of the innermost pair of working chambers is obtained. This pressure non-uniformity is used to determine the depth and size of the scroll's initial end groove 40. The initial end groove 40 alters the disengagement position of the scroll, allowing the innermost pair of working chambers to simultaneously connect with the exhaust port 30, achieving the exhaust requirements. This reduces internal leakage caused by the pressure non-uniformity in these two working chambers, thereby improving the operating efficiency of the scroll compressor. Determining the depth and size of the initial end groove 40 based on the pressure non-uniformity of the two working chambers provides a precise design basis, making the depth and size of the initial end groove 40 more in line with practical needs and enhancing the stability of the moving and stationary scrolls during scroll compression. This method utilizes simulation software to perform pressure simulation calculations in the working chamber, which has the advantages of low cost and short cycle compared to the traditional design-experiment-design method.

[0070] The detailed steps of this embodiment are as follows:

[0071] Step S100: By adopting the form of an involute circle, the inner and outer profiles of the moving vortex ring and the inner and outer profiles of the stationary vortex ring are formed, and the inner and outer profiles are connected by a modified circular arc and a connecting circular arc at the beginning of both the moving and stationary vortex rings.

[0072] like Figure 1 , Figure 2 As shown, since the moving volute 20 and the stationary volute 10 need to be matched while rotating, the moving volute 20 and the stationary volute 10 have the same contour lines as the stationary volute 10 and are symmetrically arranged. For example, when the rotation angle of the main shaft is the initial angle of 0°, the moving volute 20 and the stationary volute 10 are centrally symmetrical. Taking the contour of the stationary volute 10 as an example, the coordinate equation of the inner profile 11 of the stationary volute 10 in the rectangular coordinate system is:

[0073]

[0074] The coordinate equation of the outer profile line 12 of the static scroll 10 is:

[0075]

[0076] wherein a is the base circle radius, and a is the start angle of the involute, is the involute development angle of the central surface of the static scroll.

[0077] After the profile line of the inner wall and the profile line of the outer wall are formed, the initial end needs to be corrected and connected, so the correction arc 14 is added to modify the inner profile line of the static scroll, and the connecting arc 13 is added to connect the correction arc and the outer profile line at the initial end. The specific method is as follows:

[0078] The coordinate equation of the connecting arc 13 is:

[0079]

[0080] The coordinate equation of the correction arc 14 is:

[0081]

[0082] wherein β is the correction angle, d and γ are the initial end correction parameters of the scroll, r is the connecting arc radius, R is the correction arc radius, and ξ is the angle variable.

[0083] Step S200, according to the motion state of the static scroll and the static scroll, the position and shape of the circular exhaust hole, and the communication angle of the working chamber and the exhaust hole are determined.

[0084] As shown in Figure 7 , the exhaust hole 30 is a circular hole, wherein the working chamber includes the innermost symmetrical first working chamber 21 and the second working chamber 22, wherein the first working chamber 21 is formed by the outer wall of the dynamic scroll 20 and the inner wall of the static scroll 10, and the second working chamber 22 is formed by the inner wall of the dynamic scroll 20 and the outer wall of the static scroll 10. As shown in Figure 3 , the motion state of the dynamic scroll 20 and the static scroll 10 is that the exhaust hole 30 is in communication with the first working chamber 21 and not in communication with the second working chamber 22, which is also the moment when the dynamic scroll 20 is just in communication with the first working chamber 21 through rotation. The rotation angle of the main shaft of the dynamic scroll 20 is the communication angle θ of the working chamber and the exhaust hole 30 d , and the reference standard of the angle is that the rotation angle of the main shaft when the outermost circle of the dynamic scroll 20 is closed with the outermost circle of the static scroll 10 is the start angle 0°.

[0085] As shown in Figure 3 , when the rotation angle of the dynamic disc is θ dAt that moment, the exhaust port 30 is connected to the first working chamber 21, but not to the second working chamber 22. The working fluid in the first working chamber 21 enters the exhaust chamber 23 directly through the exhaust port 30. As the moving scroll rotates, the exhaust chamber 23 shrinks, and the pressure inside the exhaust chamber 23 does not continue to rise. The second working chamber 22 is not connected to the exhaust port 30, and as the moving scroll rotates, the pressure will further increase, eventually exceeding the pressure inside the first exhaust chamber 23. Figure 4 , Figure 10 As shown, the moving scroll continues to rotate until it completely disengages from the stationary scroll. The rotation angle of the main shaft of the moving scroll at the moment of complete disengagement is θ. t During this period, if the initial end groove 40 is not provided, due to the axial clearance between the moving and stationary volutes 10, the working fluid in the second working chamber 22 will leak into the first working chamber 21 under the action of pressure difference, and will also leak more rapidly into its corresponding secondary compression chamber, resulting in internal leakage and energy loss. After providing the initial end groove 40, the disengagement position of the volutes is changed by the initial end groove 40, so that the innermost pair of working chambers can simultaneously communicate with the exhaust port 30, thus meeting the exhaust requirements.

[0086] Step 310: Draw a digital 3D model based on the physical static and dynamic vortex rings in the model-making software;

[0087] Step 320: Simulate and calculate the flow and heat transfer of the working fluid in the working chamber of the digital three-dimensional model using simulation software, and obtain the pressure distribution in the working chamber.

[0088] Step 330: Calculate the pressure non-uniformity of the innermost pair of working chambers based on the pressure distribution within the working chamber.

[0089] In the specific process, during the vortex compression, multiple pairs of working chambers exist simultaneously in both the moving and stationary vortex disks. The formation and disappearance of a pair of working chambers constitutes one compression process. In this embodiment, the rotation angle at the start of a compression process for a pair of working chambers is 0°, and the rotation angle at the end is 1080° (one cycle is from the start of intake to the end of exhaust). When the moving vortex rotates, it forms multiple pairs of working chambers with the stationary vortex disk, and the volume of the working chambers changes accordingly with the change of rotation angle. In this embodiment, the innermost pair of working chambers are the first working chamber and the second working chamber. The method for calculating the pressure non-uniformity between the first and second working chambers is as follows:

[0090]

[0091] Where p1 is the average pressure of the working fluid in the first working chamber, and the calculation time range of this average pressure is from the rotation angle of the moving vortex from θ. d to θ t p2 represents the average pressure of the working fluid in the second working chamber. The calculation time range for this average pressure is from the rotation angle of the moving vortex to θ.d to θ t where θ d is the rotation angle of the main shaft of the dynamic vortex ring at the moment when the first working chamber is communicated with the exhaust hole, θ t is the rotation angle of the main shaft of the dynamic vortex ring at the moment when the dynamic vortex ring is completely disengaged from the static vortex ring; and ε is the equivalent pressure unevenness.

[0092] Step 400, taking the two meshing points as two endpoints, determining the depth and size of the initial end cut groove according to the pressure unevenness, and setting the initial end cut groove on the initial end of the dynamic vortex ring and the initial end of the static vortex ring respectively.

[0093] In the specific process, the calculation formula for determining the depth and size of the initial end cut groove according to the pressure unevenness is as follows:

[0094]

[0095] where h is the depth of the initial end cut groove, H is the height of the dynamic vortex ring, R c is the circular arc radius of the initial end cut groove, l AB is the distance between the two meshing points. f3 is a functional relationship between the cut groove depth and the pressure unevenness ε (the pressure unevenness between the first working chamber and the second working chamber), and f4 is a functional relationship between the cut groove circular arc radius and the pressure unevenness ε (the pressure unevenness between the first working chamber and the second working chamber); the functions of the two functions are mainly to calculate h and Rc according to the obtained pressure unevenness.

[0096] The functional relationship between h and ε and the functional relationship between Rc and ε are obtained by calculating the cloud diagram and the pressure unevenness ε under multiple sets of different cut groove sizes, and then by comparison to determine which set of cut groove sizes corresponds to the smallest pressure unevenness ε, and then by the smallest pressure unevenness ε to select the corresponding h and Rc as the optimal initial end cut groove size to design the groove.

[0097] Step 500, cutting the initial end of the dynamic vortex ring and the initial end of the static vortex ring according to the calculated depth and height to obtain the initial end cut groove, and the shapes of the initial end cut grooves on the initial end of the dynamic vortex ring and the initial end of the static vortex ring are the same.

[0098] According to the above method, the embodiment provides a specific size of the dynamic vortex disc and the static vortex disc, which is as follows:

[0099] The wall thickness of the vortex ring of the dynamic vortex disc and the static vortex disc is t = 4 mm; the height of the vortex ring is h = 6.2 mm; the intercept of the vortex ring is Pt = 15 mm; the height intercept ratio is 0.4133; the maximum expansion angle is The scroll diameter Dm is 76.5225 mm; the exhaust hole position is 720°; the correction angle parameter d is 0.6691 mm; the correction parameter γ is 0.2061 rad; the connecting circular arc radius r is 1.8309; and the correction circular arc radius R is 5.3309 mm.

[0100] Embodiment two

[0101] On the basis of embodiment one, the embodiment provides a device for manufacturing a start-end slot of a scroll, which comprises a memory and a processor, and the memory stores a manufacturing program of the start-end slot of the scroll, and the manufacturing program of the start-end slot of the scroll runs on the processor to realize the manufacturing method of the start-end slot of the scroll.

[0102] Embodiment three

[0103] On the basis of embodiment one, the embodiment provides a scroll compressor, which comprises a moving scroll and a stationary scroll, and the moving scroll and the stationary scroll are matched to form a scroll compression structure; the moving scroll has a moving scroll, and the stationary scroll has a stationary scroll; the moving scroll and the stationary scroll are both provided with a start-end slot, and the start-end slot is manufactured by the manufacturing method of the start-end slot of the scroll.

[0104] Compared with the prior art, the manufacturing method of the start-end slot of the scroll, the device and the scroll compressor provided by the application can obtain the equivalent pressure unevenness of the innermost pair of working cavities according to the pressure distribution, determine the depth and size of the start-end slot of the scroll according to the pressure unevenness, change the disengagement position of the scroll through the start-end slot, make the innermost pair of working cavities simultaneously communicate with the exhaust hole, meet the exhaust requirement, reduce the internal leakage caused by the pressure unevenness of the working cavities, and improve the operation efficiency of the scroll compressor. The depth and size of the start-end slot are determined according to the pressure unevenness of the two working cavities, accurate design basis is formed, the depth and size of the start-end slot are more in line with practical requirements, and the stability of the moving scroll and the stationary scroll during scroll compression is enhanced. The method uses simulation software to perform working cavity pressure simulation calculation, and has the advantages of low cost and short cycle compared with the traditional design-experiment-design method.

[0105] The above only describes preferred embodiments of the application and is not intended to limit the application. Any modification, equivalent replacement and improvement made within the spirit and principle of the application shall be included in the protection scope of the application.

Claims

1. A method for manufacturing a groove at the beginning of a vortex ring, characterized in that, The method includes the following steps: Based on the motion states of the moving and stationary vortex rings, the position and shape of the exhaust port and the communication angle between the working chamber and the exhaust port are determined, wherein the moving and stationary vortex rings enclose the working chamber. Based on the connection angle between the working chamber and the exhaust port, determine the two initial meshing points when the moving vortex and the stationary vortex mesh. Perform air pressure simulation in the working chamber to obtain the pressure distribution in the working chamber under working conditions, and analyze the pressure non-uniformity of the innermost pair of working chambers. Initial end grooves are set at the beginning of the moving vortex and the beginning of the stationary vortex respectively, with the two meshing points being the two endpoints of the initial end grooves. The depth and size of the initial end grooves are determined based on the pressure non-uniformity. The steps of performing air pressure simulation within the working chamber to obtain the pressure distribution within the working chamber under working conditions and analyzing the pressure non-uniformity of the innermost pair of working chambers specifically include: In model-making software, create digital 3D models based on physical static and dynamic vortices; The flow and heat transfer of the working fluid in the working chamber of the digital three-dimensional model are simulated and calculated using simulation software, and the pressure distribution in the working chamber is obtained. Based on the pressure distribution within the working chambers, the pressure non-uniformity of the innermost pair of working chambers is calculated. The method for calculating the pressure non-uniformity of the innermost pair of working chambers is as follows: in, The average pressure of the working fluid in the first working chamber is given, and the calculation time range for this average pressure is from the rotation angle of the moving vortex. arrive ; The average pressure of the working fluid in the second working chamber is calculated over a time period from the rotation angle of the moving vortex. arrive ,in The rotation angle of the main shaft of the moving vortex at the moment when the first working chamber is connected to the exhaust port. ε is the rotation angle of the main axis of the moving volute at the moment when the moving volute and the stationary volute are completely disengaged; ε is the equivalent pressure non-uniformity. In the step of setting initial end grooves at the beginning of the moving vortex and the beginning of the stationary vortex respectively, where the two meshing points are the two endpoints of the initial end grooves, and determining the depth and size of the initial end grooves based on the pressure non-uniformity: The formula for determining the depth and size of the initial groove based on pressure non-uniformity is as follows: Where h is the depth of the initial groove and H is the height of the moving vortex. The radius of the arc of the initial groove. The distance between two meshing points, the functional relationship between h and ε, and the functional relationship between Rc and ε are all determined by calculating the cloud diagrams and pressure non-uniformity ε under multiple sets of different groove sizes. Then, the minimum pressure non-uniformity ε is determined by comparison. Finally, the corresponding h and Rc are selected as the size of the starting groove for groove design based on the minimum pressure non-uniformity ε.

2. The method for manufacturing the starting groove of the vortex ring as described in claim 1, characterized in that, Before the step of determining the position and shape of the exhaust port and the communication angle between the working chamber and the exhaust port based on the motion states of the moving and stationary vortices, the method further includes the following step: By adopting the form of an involute circle, the inner and outer profiles of the moving vortex ring and the inner and outer profiles of the stationary vortex ring are formed. At the beginning of both the moving and stationary vortex rings, modified circular arcs and connecting circular arcs are used to connect the inner and outer profiles.

3. The method for manufacturing the starting groove of the vortex ring as described in claim 2, characterized in that, The step of forming the inner and outer profiles of the moving vortex and the stationary vortex by using the involute shape of a circle, and connecting the inner and outer profiles with modified circular arcs and connecting circular arcs at the beginning of both the moving and stationary vortexes: The outline of the moving vortex is the same as that of the stationary vortex, and they are arranged symmetrically. The coordinate equations of the inner profile of the stationary vortex are as follows: The coordinate equations of the outer profile of the stationary vortex ring are: Where a is the base circle radius, α is the involute initiation angle, and Ø is the involute development angle of the center plane of the static vortex; The coordinate equations of the connecting arcs are: The corrected coordinate equation of the arc is: in, β For the correction angle, d and Here are the correction parameters for the vortex start, where r is the radius of the connecting arc. To correct the radius of the arc, For angle variables.

4. The method for manufacturing the starting groove of the vortex ring as described in claim 1, characterized in that, In the step of determining the position and shape of the exhaust port and the communication angle between the working chamber and the exhaust port based on the motion states of the moving and stationary vortexes: The exhaust port is a circular hole, and the working chamber includes an innermost symmetrical first working chamber and a second working chamber. The first working chamber is formed by the outer wall of the moving vortex and the inner wall of the stationary vortex surrounding each other, and the second working chamber is formed by the inner wall of the moving vortex and the outer wall of the stationary vortex surrounding each other. The motion state of the moving vortex and the stationary vortex is such that the exhaust port is connected to the first working chamber but not to the second working chamber. At this time, the rotation angle of the main shaft of the moving vortex is the connection angle between the working chamber and the exhaust port. The rotation angle of the main shaft at the moment when the outermost ring of the moving vortex and the outermost ring of the stationary vortex are closed is the starting angle of 0°.

5. The method for manufacturing the starting groove of the vortex ring as described in any one of claims 1-4, characterized in that, Both the starting ends of the moving vortex and the starting ends of the stationary vortex are provided with starting end grooves, and the shapes of the starting end grooves are the same.

6. An apparatus for fabricating a starting groove for a vortex ring, characterized in that, The device includes a memory and a processor. The memory stores a program for creating the starting groove of a vortex ring. The program for creating the starting groove of a vortex ring runs on the processor to implement the method for creating the starting groove of a vortex ring as described in any one of claims 1-5.

7. A scroll compressor, characterized in that, include: A moving vortex disk and a stationary vortex disk, wherein the moving vortex disk and the stationary vortex disk are matched to form a vortex compression structure; The moving volute has a moving volute ring, and the stationary volute has a stationary volute ring. Both the moving volute ring and the stationary volute ring have an initial end groove. The initial end groove is made by the method for making an initial end groove of a volute ring as described in any one of claims 1-5.

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