Sealing element, scroll plate assembly, compressor and vehicle

Abstract

The utility model relates to a sealing element, a scroll plate assembly, a compressor and a vehicle, the sealing element is used for a scroll plate of the compressor, and the width of the sealing element tends to decrease in the extending direction of the sealing element. According to the sealing element provided by the invention, the size change of the sealing element is adaptively adjusted, and when the sealing element is integrated in equipment represented by a scroll compressor for use, the width of each part of the sealing element can be configured according to the distribution condition of pressure intensity in the equipment; the structural strength provided by the thickness of the sealing element is adapted to differentiated pressure distribution existing in a sealed area, so that the material of the sealing element is more reasonably configured, the sealing requirement in a use scene with larger pressure difference is met, and the sealing effect is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of sealing structures, in particular to a sealing element, a scroll disc assembly, a compressor and a vehicle. BACKGROUND

[0002] In the related art, scroll compressors are often used on vehicles and other equipment as devices for pressurizing working medium such as refrigerant. The dynamic scroll and the static scroll of the scroll compressor form a crescent-shaped compression chamber, and the working medium in the compression chamber is pressurized when the dynamic scroll rotates relative to the static scroll. However, there is axial movement between the dynamic scroll and the static scroll, so a sealing groove is often formed on the part of the dynamic scroll and / or the static scroll where the compression chamber is formed, and a sealing strip is arranged in the sealing groove to seal the compression chamber. However, since there is a pressure difference between the central region and the peripheral region of the compression chamber in the scroll compressor, and the existing sealing strip is not designed for this pressure characteristic in the compression chamber of the scroll compressor, it is difficult for the sealing strip to stably play a sealing role, and the sealing requirements of the equipment are difficult to meet. CONTENT OF THE UTILITY MODEL

[0003] The embodiments of the present application provide a sealing element, a scroll disc assembly, a compressor and a vehicle, which improve the sealing effect of the sealing element on the corresponding chamber to at least partially solve the above technical problems.

[0004] In order to achieve the above-mentioned purpose, according to the first aspect of the present application, a sealing element is provided for a scroll disc of a compressor, and the width of the sealing element tends to decrease along the extension direction of the sealing element.

[0005] Optionally, in some embodiments of the present application, the ratio of the maximum width to the minimum width of the sealing element is in the range of 0.2 to 1.

[0006] Optionally, in some embodiments of the present application, the maximum width of the sealing element is in the range of 1.5 to 7.5 mm.

[0007] And / or, the minimum width of the sealing element is in the range of 0.5 to 1.5 mm.

[0008] Optionally, in some embodiments of the present application, the width of at least part of the sealing element gradually decreases along the extension direction of the sealing element.

[0009] According to the second aspect of the present application, a scroll disc assembly is provided, comprising:

[0010] a scroll disc having a profile portion, an end portion of the profile portion being provided with a sealing groove extending along the profile portion;

[0011] a sealing element arranged in the sealing groove;

[0012] The width of the sealing member tends to decrease in the extending direction of the profile portion from inside to outside.

[0013] Optionally, in some embodiments of the present application, the ratio of the maximum width to the minimum width of the sealing member in the extending direction of the profile portion is in the range of 0.2 to 1.

[0014] Optionally, in some embodiments of the present application, the ratio of the maximum slot width to the minimum slot width of the sealing groove in the extending direction of the profile portion is in the range of 0.2 to 1.

[0015] Optionally, in some embodiments of the present application, the maximum width of the sealing member is in the range of 1.5 to 7.5 mm.

[0016] Optionally, in some embodiments of the present application, the maximum slot width of the sealing groove is in the range of 1.5 to 7.5 mm.

[0017] Optionally, in some embodiments of the present application, the minimum width of the sealing member is in the range of 0.5 to 1.5 mm.

[0018] Optionally, in some embodiments of the present application, the minimum slot width of the sealing groove is in the range of 0.5 to 1.5 mm.

[0019] Optionally, in some embodiments of the present application, the profile portion extends along a scroll line.

[0020] Optionally, in some embodiments of the present application, the sealing member is adapted to the sealing groove.

[0021] Optionally, in some embodiments of the present application, the width of the sealing member and / or the slot width of the sealing groove gradually decreases in the extending direction of the profile portion from inside to outside.

[0022] According to a third aspect of the present application, there is further provided a compressor comprising the scroll set as described above.

[0023] Optionally, in some embodiments of the present application, the scroll set comprises a moving scroll and a stationary scroll.

[0024] The moving scroll and / or the stationary scroll is / are formed with the sealing groove, so that the sealing member is arranged between the moving scroll and the stationary scroll.

[0025] Optionally, in some embodiments of the present application, the moving scroll and the stationary scroll mutually enclose a compression chamber for containing a compressed working medium; the sealing member is arranged between the moving scroll and the stationary scroll and located at the periphery of the compression chamber to seal the compression chamber.

[0026] Optionally, in some embodiments of the present application, the compressor is provided with:

[0027] a scroll inlet formed between the static scroll and the dynamic scroll;

[0028] a scroll outlet formed on the static scroll;

[0029] wherein the scroll inlet and the scroll outlet are in communication through the compression cavity; and the scroll inlet is located at the periphery of the scroll outlet in the extension direction of the profiled portion.

[0030] Optionally, in some embodiments of the present application, the groove wall of the sealing groove is spaced apart from the end surface of the sealing member at an end close to the scroll outlet in the extension direction of the profiled portion.

[0031] Optionally, in some embodiments of the present application, the sealing member is located between the groove bottom of the sealing groove and the cavity bottom wall of the compression cavity.

[0032] Optionally, in some embodiments of the present application, at least one of the groove bottom of the sealing groove and the cavity bottom wall of the compression cavity is in contact with the sealing member.

[0033] According to a fourth aspect of the present application, there is also provided a vehicle comprising the sealing member as described above, or comprising the scroll assembly as described above, or comprising the compressor as described above.

[0034] The present application has the beneficial effect of providing a sealing member, a scroll assembly, a compressor and a vehicle with improved sealing performance.

[0035] More specifically, some embodiments of the present application can have the following specific beneficial effects:

[0036] The sealing member provided by the present application can adaptively adjust the size change of the sealing member, and when used in devices represented by scroll compressors, the width of each part of the sealing member can be configured according to the distribution of the internal pressure of the device, so that the structural strength provided by the thickness of the sealing member is adapted to the differentiated pressure distribution existing in the sealed area, thereby more reasonably configuring the material of the sealing member itself, meeting the sealing requirements in use scenarios with large pressure differences, and thus improving the sealing effect.

[0037] Other features and advantages of the present application will be described in detail in the following specific embodiments. BRIEF DESCRIPTION OF DRAWINGS

[0038] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0039] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0040] Figure 1 This is a cross-sectional view of the vortex disk provided in an exemplary embodiment of this application;

[0041] Figure 2 This is a cross-sectional view of the seal provided in an exemplary embodiment of this application;

[0042] Figure 3 This is a schematic diagram of the projection outline of the seal provided in the exemplary embodiment of this application on the projection plane s;

[0043] Figure 4 yes Figure 1 An enlarged schematic diagram of part A in the middle;

[0044] Figure 5 yes Figure 1 A schematic diagram of a portion of the structure provided in the vortex disk shown;

[0045] Figure 6 This is a schematic diagram showing the fit relationship of some structures in the vortex disk provided in an exemplary embodiment of this application;

[0046] Figure 7 yes Figure 6 Enlarged schematic diagram of part B in the middle;

[0047] Figure 8 This is a schematic diagram of the overall structure of the vehicle provided in an exemplary embodiment of this application.

[0048] Explanation of reference numerals in the attached figures:

[0049] 1. Vehicles;

[0050] 10a. Compression chamber; 10b. Working fluid outlet; 10c. First region; 10d. Second region; 10e. Bottom wall of the compression chamber;

[0051] 100. Seal; 110. Body; 111. First end; 112. Second end;

[0052] 200. Scroll disk assembly;

[0053] 210, vortex disk; 210a, sealing groove; 210b, vortex inlet; 2, vortex outlet; 210d, bottom of the sealing groove;

[0054] 211, profile section; 211a, first vortex protrusion; 211b, second vortex protrusion;

[0055] 212. Moving scroll plate;

[0056] 213. Static vortex disk;

[0057] a. Width of the seal; b. Groove width of the seal; c. Seal thickness; L. Centerline of the eccentric shaft; s. Projection plane. Detailed Implementation

[0058] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0059] Reference Figures 1 to 7 As shown, in a first aspect, some embodiments of this application provide a seal 100 that can be installed on a compressor. For example, the seal 100 can be used in a scroll assembly 200 of a compressor. Based on the application of the seal 100 provided in this application, a second aspect of this application also provides a scroll assembly 200 that is suitable for installation on equipment such as a scroll compressor. The scroll assembly 200 includes a scroll 210 and the seal 100.

[0060] As an illustrative example of the functions that the scroll disk assembly 200 can achieve, refer to Figures 1 to 4 As shown, the seal 100 can be used, for example, to seal the compression chamber 10a of a scroll compressor. Depending on the application, the seal 100 can also be used to seal other equipment, and this application does not impose any limitations on this. The seal 100 is, for example, strip-shaped, that is, the seal 100 can be a sealing strip.

[0061] The scroll plate 210 can be integrated into equipment such as a scroll compressor as a component forming the compression chamber 10a. Specifically, the scroll plate 210 has a profile portion 211 formed thereon, which constitutes at least a portion of the cavity wall of the compression chamber 10a.

[0062] To address the aforementioned problem that current seals are insufficient to meet usage requirements, this application defines that the width 'a' of the seal element tends to decrease along the extension direction of the seal element 100. A description of the width 'a' of the seal element will be provided later. In this solution, the surface on the seal element 100 defining its width is adapted to contact the portion of the equipment to be sealed by the seal element 100, or the surface on the seal element 100 defining its width is adapted to contact the part of the equipment used for installing the seal element 100, thereby achieving contact sealing or positioning installation. By defining that the width 'a' of the seal element tends to decrease along the extension direction of the seal element 100, the material of the seal element 100 can be adaptively configured outside the sealed portion.

[0063] By adopting the above solution and adapting the size of the seal 100, when integrated into equipment such as a scroll compressor, the width of the seal 100 can be configured according to the pressure distribution inside the equipment. This allows the structural strength provided by the thickness of the seal 1001 to adapt to the differential pressure distribution in the sealed area, thus enabling a more reasonable configuration of the material used in the seal 100 and meeting the sealing requirements in applications with large pressure differences, thereby improving the sealing effect.

[0064] Based on the integration of the seal 100 into the scroll assembly 200, a sealing groove 210a extending along the profile 211 of the scroll 210 is provided at the end of the profile 211. Considering the practical application scenario of the scroll 210 integrated into a scroll compressor, the profile 211 often extends in a scroll direction. Correspondingly, at least a portion of the sealing groove 210a can also extend in the scroll direction. The seal 100 is disposed in the sealing groove 210a, and at least a portion of the seal 100 can also extend in the scroll direction. The width 'a' of the seal tends to decrease in the direction of extension from the inside to the outside along the profile 211. The scroll assembly 200 provided in this application, due to the integration of the seal 100, possesses the beneficial effects of the seal 100, which will not be elaborated further here.

[0065] Taking the sealing member 100 as an example, which is configured as a sealing strip with a quadrilateral cross-sectional shape and the profile portion 211 extending in a spiral shape, on the central plane with the center line of the spiral line along which the profile portion 211 extends as the normal, the projection of at least a portion of the outline of the profile portion 211, the groove wall of the sealing groove 210a, and the outline of the sealing member 100 extends in a spiral line. At the same time, the distance between the two opposite groove walls located on both sides of the bottom 210d of the sealing groove defines the width of the sealing groove 210a, and the distance between the two opposite surfaces of the sealing groove 210a that respectively mate with the two opposite groove walls defines the width a of the sealing member. Thus, the width a of the sealing member tends to decrease in the direction of extension from the inside to the outside along the profile portion 211, that is, when the sealing member 100 extends along the spiral line, its width near the center of the spiral line is greater than its width away from the center of the spiral line.

[0066] Of course, the above is only a specific example of the inventive concept of this application. In fact, this application does not impose specific limitations on the cross-sectional shape of the sealing element 100 and the sealing groove 210a. For example, it can be a polygon, a circle, an ellipse, etc. Taking the cross-section of the sealing element 100 as an example, based on the inventive concept of this application, the radial dimension of the circular cross-section is different in the extending direction of the sealing element 100.

[0067] It should be noted that the extension direction of the seal 100 can be flexibly configured according to the usage requirements of the device. In some embodiments, at least a portion of the seal 100 is made of a flexible material. As examples, flexible materials include copolymers, silicone, polyethylene, polypropylene, thermoplastic elastomers, etc., and other materials may also be used. The seal made of flexible material has plastic deformation capability, thereby enabling the seal to be configured into various shapes according to the specific needs of the sealed part.

[0068] For example, the seal 100 is configured to have at least a switchable first state and a second state. When the seal 100 is in the first state, at least a portion of the seal 100 extends in a straight line. The seal in the first state can be used for sealing some devices. Alternatively, the seal 100 can be molded into the first state during manufacturing, facilitating switching to other shapes. When the seal 100 is in the second state, at least a portion of the seal 100 extends along a spiral curve. The seal 100 in the second state is, for example, suitable for use in the aforementioned spiral-extending sealing groove 210a to seal the aforementioned compression chamber 10a.

[0069] The scroll plate assembly 200 adapts to the size variations of the seal 100 and the sealing groove 210a. When integrated into equipment such as scroll compressors, the width of the seal 100 and the width of the corresponding sealing groove 210a can be configured according to the pressure distribution inside the equipment. This allows the structural strength provided by the thickness of the seal 100 to adapt to the differential pressure distribution in the sealed area, thus enabling a more rational configuration of the material used in the seal 100. This meets the sealing requirements in applications with large pressure differences, thereby improving the sealing effect.

[0070] As an exemplary illustration of how the seal 100 achieves the above-mentioned effects, in some embodiments, the seal 100 includes a body 110. The body 110 has a first end 111 and a second end 112, which are two distinct portions of the body 110. Specifically, when the seal 100 is used for sealing a scroll compressor, refer to... Figure 2 and Figure 6 As shown, the first end 111 is disposed in a first region 10c relatively close to the working fluid outlet 10b of the scroll compressor, and the second end 112 is disposed in a second region 10d relatively far from the working fluid outlet 10b of the scroll compressor. In some embodiments, the sealing groove 210a extends along the scroll line; the first region 10c is located at one end of the sealing groove 210a near the working fluid outlet 10b; the second region 10d is located on the periphery of the first region 10c, that is, the second region 10d is located at one end of the sealing groove 210a far from the working fluid outlet 10b, that is, along the extension direction of the compression chamber 10a, the first region 10c is closer to the working fluid outlet 10b than the second region 10d.

[0071] The working fluid outlet 10b of the scroll compressor mentioned in this application refers to the opening formed by the pressurized working fluid, such as refrigerant, flowing out of the compression chamber 10a that pressurizes the working fluid in the scroll compressor. More specifically, the working fluid outlet 10b is formed at the center of the compression chamber 10a, which extends in a vortex shape between the moving scroll 212 and the stationary scroll 213 of the scroll compressor. When the scroll compressor is working, the working fluid in the compression chamber 10a is pressurized, so that the pressure of the working fluid near the working fluid outlet 10b is greater than the pressure of the working fluid far from the working fluid outlet 10b. That is, the pressure of the working fluid in the first region 10c of the compressor is greater than the pressure of the working fluid in the second region 10d.

[0072] In some embodiments, the aforementioned first region 10c and second region 10d are configured as two different parts of the sealing groove 210a along its extension direction. That is, the first region 10c and the second region 10d are two different parts of the space defined by the groove wall of the sealing groove 210a. In other words, the first region 10c and the second region 10d belong to two different parts of the sealing groove 210a. Further, the first end 111 and the second end 112 are both at least partially embedded in the sealing groove 210a, thereby realizing the positioning and installation of the seal 100 on the scroll plate 210.

[0073] To accommodate pressure differences in different sealed areas, the first end 111 and the second end 112 in this application have different sealing thicknesses c. It can be understood that the sealing thickness c is the width a of the seal mentioned above.

[0074] By differentiating the sealing thickness c of the first end 111 and the second end 112, the sealing element 100 matches the structural strength of itself with the pressure difference of the sealed area when in use, enabling the sealing element 100 to achieve a more stable sealing effect.

[0075] In a specific embodiment, the seal 100 can be configured to fit the sealing groove 210a, and correspondingly, the width b of the sealing groove tends to decrease in the direction of extension from the inside to the outside along the profile portion 211. Specifically, the width of the sealing groove 210a near the center of the spiral line is greater than its width away from the center of the spiral line.

[0076] Based on the inventive concept of this application, the width b of the sealing groove tends to decrease in the direction of extension from the inside to the outside along the profile portion 211, so that the sealing thickness c of the first end 111 is greater than the sealing thickness c of the second end 112. In a specific embodiment, when the sealing member 100 is used to seal the sealing cavity of a scroll compressor, the first end 111 can be used to seal the end of the scroll-shaped compression cavity 10a near the working fluid outlet 10b, and the second end 112 can be used to seal the end of the scroll-shaped compression cavity 10a away from the working fluid outlet 10b.

[0077] Therefore, in the first region 10c with relatively high pressure, the sealing thickness c of the first end 111 is thicker, and in the second region 10d with relatively low pressure, the sealing thickness c of the second end 112 is thinner. This configuration is adapted to the pressure distribution of the compressed working fluid inside the scroll compressor, thereby providing a stable sealing effect for the compression chamber 10a.

[0078] As a specific solution, the body 110 extends along the scroll line, such that the extension direction of the body 110 is adapted to the protrusions extending along the scroll line on the moving scroll 212 and stationary scroll 213 of the scroll compressor for forming the compression chamber 10a, which facilitates sealing of the compression chamber 10a. It can be understood that when the scroll assembly 200 is integrated into the scroll compressor, the scroll 210 includes the moving scroll 212 and the stationary scroll 213, that is, the sealing element 100 mentioned above is disposed in the sealing groove 210a, that is, the sealing groove 210a is formed on the moving scroll 212 and / or the stationary scroll 213, so that the sealing element 100 is disposed between the moving scroll 212 and the stationary scroll 213. In a more specific embodiment, the first end 111 and the second end 112 are integrally formed, that is, the first end 111 and the second end 112 are two different parts of the body 110 connected to each other along its extension direction, so that the sealing element 100 can surround the compression cavity 10a and thus provide a stable seal to the compression cavity 10a.

[0079] In some embodiments, the profile portion 211 extends along the scroll line, making the profile portion 211 suitable for integration into a scroll compressor to define the compression chamber 10a of the scroll compressor. Of course, this does not mean that the scroll assembly 200 is only suitable for integration into a scroll compressor. In some devices not illustrated in this application where the scroll assembly 200 can be applied, the scroll assembly 200 provided in this application can also be used to meet the sealing requirements of these devices.

[0080] It should be noted that although some embodiments of this application emphasize that the body 110 extends along the scroll line to ensure the sealing effect on the compression chamber 10a, the pressurization effect provided to the working medium at the end of the compression chamber 10a away from the working medium outlet 10b is weak when the scroll compressor is working. Therefore, the length of the body 110 along the extension direction does not need to be consistent with the length of the protrusion extending in the scroll line direction on the moving scroll 212 or stationary scroll 213 of the scroll compressor. For example, the length of the body 110 in the extension direction is less than the length of the protrusion extending in the scroll line direction. When the negative impact on the pressurization effect of the compressor is negligible, the material used for the body 110 can be reduced.

[0081] The aforementioned difference in sealing thickness c between the first end 111 and the second end 112 helps improve the sealing effect of the seal 100 on the sealed area. However, if the difference in sealing thickness c between the first end 111 and the second end 112 is too small, the adaptability to pressure differences in different sealed areas will not be significant. Conversely, if the difference in sealing thickness c between the first end 111 and the second end 112 becomes large, there will be material redundancy in the portion with larger sealing thickness c, resulting in excessive rigidity of the body 110, which will hinder the relative movement between the moving scroll 212 and the stationary scroll 213. Alternatively, in the portion with smaller sealing thickness c, wear is likely to occur during the relative movement of the moving scroll 212 and the stationary scroll 213, thus affecting the normal use of the equipment and the service life of the seal 100 itself. Furthermore, the difference in sealing thickness c between the first end 111 and the second end 112 also affects the thickness of the profile portion 211, thereby limiting the volume of the compression chamber 10a.

[0082] In some embodiments, the ratio of the maximum width to the minimum width of the seal ranges from 0.2 to 1.

[0083] As a specific example, when the seal is integrated into the aforementioned scroll plate assembly, the ratio of the maximum width to the minimum width of the seal 100 in the extension direction along the profile portion 211 ranges from 0.2 to 1. Alternatively, the ratio of the maximum groove width to the minimum groove width of the sealing groove 210a in the extension direction along the profile portion 211 ranges from 0.2 to 1.

[0084] Of course, based on the cooperative use of the sealing groove 210a and the sealing element 100, the above requirements for the width a of the sealing element and the groove width b of the sealing groove can be configured simultaneously.

[0085] It is understandable that the above configuration of the width 'a' of the seal can also be interpreted as the ratio of the sealing thickness 'c' of the second end 112 to the sealing thickness 'c' of the first end 111 ranging from 0.2 to 1. Based on the technical concept of this application, this value does not include 1, that is, the ratio of the sealing thickness 'c' of the first end 111 to the sealing thickness 'c' of the second end 112 ranging from greater than or equal to 0.2 to less than 1. More specifically, this range could be, for example, 0.2 to 0.4, 0.4 to 0.6, 0.6 to 0.8, 0.8 to 1, etc.

[0086] By configuring the width of the sealing groove 210a and / or the groove width of the sealing element 100 within the above-mentioned range, the variation value of the groove width b of the sealing groove and / or the variation value of the width a of the sealing element in the extension direction along the profile portion 211 is within a reasonable range, which is beneficial to ensuring the stable operation of the equipment integrated with the scroll plate assembly 200.

[0087] As an example of a specific solution, considering the influence of the sealing thickness c of the body 110 on the volume of the portion of the compression chamber 10a of the scroll compressor located in the first region 10c, the sealing thickness c of the first end 111 can range from 1.5 to 7.5 mm, that is, the maximum width of the seal 100 can range from 1.5 to 7.5 mm. More specifically, the sealing thickness c of the first end 111 can range from 1.5 to 2.5 mm, 2.5 to 4 mm, 4 to 5 mm, 5 to 6 mm, 6 to 7 mm, etc.

[0088] Understandably, the maximum width of the sealing groove 210a can range from 1.5 to 7.5 mm. More specifically, the maximum width of the sealing groove 210a can range from 1.5 to 2.5 mm, 2.5 to 4 mm, 4 to 5 mm, 5 to 6 mm, 6 to 7 mm, etc.

[0089] As an example of a specific solution, considering the influence of the sealing thickness c of the body 110 on the volume of the portion of the compression chamber 10a of the scroll compressor located in the second region 10d, the sealing thickness c of the second end 112 ranges from 0.5 to 1.5 mm, that is, the minimum width of the seal 100 ranges from 0.5 to 1.5 mm. More specifically, the sealing thickness c of the second end 112 may range from, for example, 0.5 to 0.65 mm, 0.65 to 0.8 mm, 0.8 to 1 mm, 1 to 1.5 mm, etc.

[0090] The minimum width of the sealing groove 210a can be between 0.5 and 1.5 mm. More specifically, the maximum width of the sealing groove 210a can be between 0.5 and 0.65 mm, 0.65 and 0.8 mm, 0.8 and 1 mm, 1 and 1.5 mm, etc.

[0091] In some embodiments, refer to Figure 2 and Figure 3 As shown, at least a portion of the width of the seal gradually decreases along its extension direction. Specifically, when the seal is integrated into the scroll plate assembly, the width 'a' of the seal gradually decreases in the outward extension direction along the profile 211, causing the sealing thickness 'c' of the body 110 to change continuously along its extension direction. More specifically, the sealing thickness 'c' of the body 110 gradually decreases from the first end 111 to the second end 112 along its extension direction. In this way, the change in the width 'a' of the seal is continuous, and there are no regions on the surface of the body 110 where the sealing thickness 'c' changes abruptly, adapting to specific application scenarios where the pressure within the compression chamber 10a gradually changes, providing a stable sealing effect for the device.

[0092] Furthermore, the above-mentioned scheme also enables the body 110 of the seal 100 to generate a certain amount of peristalsis when the moving scroll 212 of the scroll compressor moves relative to the stationary scroll 213, due to compression or the influence of the air pressure in the compression chamber 10a. This peristalsis allows the side of the body 110 to adhere tightly to the groove wall of the sealing groove 210a, thereby further improving the sealing effect.

[0093] It is understood that, based on the inventive concept of this application, the width b of the sealing groove can also be configured to gradually decrease in the direction of extension from the inside to the outside along the profile portion 211.

[0094] In some embodiments, the sealing groove 210a extends along the scroll line to adapt to the shape of the compression chamber 10a of the scroll compressor and the body 110 of the seal 100 described above.

[0095] In some embodiments, the width of the sealing groove 210a varies continuously along its extension direction. When it is engaged with the aforementioned seal 100, the width of the sealing groove 210a at the end near the working medium outlet 10b is greater than the width of the end away from the working medium outlet 10b, so as to adapt to the shape of the body 110. In this way, due to the relative rotation of the moving scroll 212 and the stationary scroll 213 of the scroll compressor, for example, the moving scroll 212 swings relative to the stationary scroll 213 under the drive of a crankshaft transmission mechanism, the seal 100 located between the moving scroll 212 and the stationary scroll 213 forms a contact seal with the moving scroll 212 and is squeezed during the relative movement of the moving scroll 212 and the stationary scroll 213. According to the change of the groove width b of the sealing groove, this compression causes the body 110 to creep toward the end of the sealing groove 210a away from the working fluid outlet 10b, and makes the side wall of the body 110 used to limit the sealing width fit more tightly with the groove wall of the sealing groove 210a, reducing the possibility of the working fluid leaking from the gap between the groove wall of the sealing groove 210a and the body 110, thereby improving the sealing effect.

[0096] According to a third aspect of this application, a compressor is provided, including the scroll assembly 200 described above. The compressor has the beneficial effects of the scroll assembly 200 described above, which will not be repeated here.

[0097] In specific applications, the compressor can be configured as a scroll compressor, for example. This article mainly describes the specific implementation scheme when the compressor is specifically configured as a scroll compressor, so as to facilitate understanding of the inventive concept of this case.

[0098] The scroll disk assembly 200 includes a moving scroll disk 210 and a stationary scroll disk 213. The moving scroll disk 212 and the stationary scroll disk 213 are movably arranged relative to each other. That is, the scroll disk assembly 200 may include multiple scroll disks 210, with the moving scroll disk 212 configured as one of the scroll disks 210 and the stationary scroll disk 213 configured as another scroll disk 210.

[0099] As a specific embodiment, a sealing groove 210a is formed on the moving scroll 212 and / or the stationary scroll 213, allowing the seal 100 to be disposed between the moving scroll 212 and the stationary scroll 213. It is understood that, referring to the preceding description, the moving scroll 212 / stationary scroll 213 can each be part of the aforementioned scroll disk 210, that is, the scroll disk 210 of the scroll disk assembly 200 includes the moving scroll 212 and the stationary scroll 213. The seal 100 can be located between the moving scroll 212 and the stationary scroll 213 along the axial direction of the moving scroll 212 / stationary scroll 213, thereby allowing the seal 100 to stably exist between the moving scroll 212 and the stationary scroll 213 and provide a sealing effect for the compression chamber 10a.

[0100] The moving scroll 212 and the stationary scroll 213 enclose each other to form a compression chamber 10a for containing the compressed working fluid. In a scroll compressor, the compression chamber 10a may, for example, be configured in a scroll shape. A seal 100 is located around the compression chamber 10a to form a seal on the compression chamber 10a, thereby sealing the compression chamber 10a by means of the seal 100 when the scroll compressor is operating.

[0101] Reference Figure 5 As will be understood by those skilled in the art, the scroll-shaped compression chamber 10a of the scroll compressor mentioned in this application refers to the space defined by the scroll-shaped protrusions on the moving scroll 212 or stationary scroll 213 of the scroll compressor, through which a working fluid such as a refrigerant passes. During operation of the scroll compressor, due to the movement of the moving scroll 212 relative to the stationary scroll 213, the scroll-shaped compression chamber 10a can be divided into several relatively small chambers. These chambers are, for example, crescent-shaped. The working fluid is pressurized during the volume change of the compression chamber 10a. Therefore, the scroll-shaped compression chamber 10a in this application can also refer to a combination of these crescent-shaped chambers in practical applications, without limitation.

[0102] The compressor is equipped with a scroll inlet 210b and a scroll outlet 210c. The scroll inlet 210b communicates with the compression chamber 10a to allow the working fluid to flow into the compression chamber 10a, and is formed between the stationary scroll plate 213 and the moving scroll plate 212. The scroll outlet 210c communicates with the compression chamber 10a to allow the working fluid to flow out of the compression chamber 10a, and is formed on the stationary scroll plate 213. It can be understood that the scroll outlet 210c is the working fluid outlet 10b mentioned earlier.

[0103] In the specific plan, refer to Figure 1 and Figure 5As shown, the vortex inlet 210b and the vortex outlet 210c are connected through the compression chamber 10a. In the extension direction along the profile 211, the vortex inlet 210b is located on the periphery of the vortex outlet 210c. The compressed working fluid enters the compression chamber 10a from the vortex inlet 210b, and is gradually pushed into the middle of the compression chamber 10a and pressurized during the relative motion of the moving vortex disk 212 and the stationary vortex disk 213. Finally, it flows out of the compression chamber 10a from the vortex outlet 210c.

[0104] In some embodiments, refer to Figure 1 and Figure 7 As shown, at one end of the profile 211 near the vortex inlet 210b, the wall of the sealing groove 210a is spaced apart from the end face of the seal 100. That is, the wall of the sealing groove 210a at one end near the working fluid outlet 10b along its extension direction is spaced apart from the first end 111 of the seal 100, so that the end of the sealing groove 210a near the working fluid outlet 10b along its extension direction is connected to the end of the compression chamber 10a near the working fluid outlet 10b.

[0105] In this way, the pressurized working medium in the compression chamber 10a near the working medium outlet 10b can enter the sealing groove 210a near the working medium outlet 10b, and then the working medium can apply pressure to the seal 100. With the gradual decrease in the width a of the seal, the surface of the seal 100 can fit more tightly with the groove wall of the sealing groove 210a, further improving the sealing effect.

[0106] In some embodiments, the seal 100 is located between the bottom 210d of the sealing groove and the bottom wall 10e of the compression chamber. That is, the seal 100 is located between the bottom 210d of the sealing groove and the bottom wall 10e of the compression chamber along the axial direction of the moving scroll 212 / stationary scroll 213. Considering that there is axial movement between the moving scroll 212 and the stationary scroll 213 during the relative movement of the moving scroll 212 and the stationary scroll 213, the above arrangement utilizes the seal 100 to form a seal between the moving scroll 212 and the stationary scroll 213. The seal 100 can be further made of a material with plastic deformation ability such as rubber to counteract the axial movement between the moving scroll 212 and the stationary scroll 213 and achieve the sealing of the compression chamber 10a.

[0107] In some embodiments, at least one of the bottom 210d of the sealing groove and the bottom wall 10e of the compression chamber contacts the seal 100. Specifically, in use, there may be a certain gap between the bottom 210d of the sealing groove and the seal 100. The working fluid, such as refrigerant, in the compression chamber 10a can enter the sealing groove 210a from the end of the sealing groove 210a near the working fluid outlet 10b and enter the gap, lifting the seal 100 so that the seal 100 can fit against the bottom wall 10e of the compression chamber that is set relative to the bottom 110d of the sealing groove. In this way, the axial movement of the moving scroll 212 relative to the stationary scroll 213 is compensated, ensuring the sealing performance of the scroll compressor.

[0108] In some embodiments, a first vortex protrusion 211a is formed at one end of the moving vortex 212 near the stationary vortex 213, and a second vortex protrusion 211b is formed at one end of the stationary vortex 213 near the moving vortex 212. At least one of the first vortex protrusion 211a and the second vortex protrusion 211b is formed with a sealing groove 210a to provide a seal 100 between the first vortex protrusion 211a and the stationary vortex 213 and / or between the second vortex protrusion 211b and the moving vortex 212. It is understood that the first vortex protrusion 211a and the second vortex protrusion 211b may extend in a vortex shape and be configured to form at least a portion of the cavity wall of the compression cavity 10a, that is, the compression cavity 10a is formed in the space enclosed by the first vortex protrusion 211a and the second vortex protrusion 211b. It is understandable that the first vortex protrusion 211a is the profile portion 211 of one of the vortex disk assemblies 200 mentioned above, and the second vortex protrusion 211b is the profile portion 211 of the other vortex disk assembly 200 mentioned above.

[0109] In practical applications, the seal 100 can be installed on the first vortex protrusion 211a or the second vortex protrusion 211b, or the seal 100 can be installed on both the first vortex protrusion 211a and the second vortex protrusion 211b at the same time. That is, this application does not impose a specific limit on the number of seals 100 installed on the vortex disk 210, and can be flexibly configured according to actual usage requirements.

[0110] Reference Figure 5 and Figure 6 As shown, the scroll disk 210 further includes a base portion 214. The base portion 214 is adapted to form or connect to the profile portion 211. Specifically, the profile portion 211 protrudes from the base portion 214, such that the compression cavity 10a is located between the base portion 214 and the profile portion 211, that is, at least a portion of the base portion 214 forms the cavity bottom wall 10e of the compression cavity. The cavity bottom wall 10e of the compression cavity can be defined by the base portion 214, thus limiting the sealing member 100.

[0111] According to the third aspect of this application, referring to Figure 8As shown, a vehicle 1 is also provided, including the aforementioned scroll assembly 200 / compressor. This vehicle 1 possesses the beneficial effects of the aforementioned scroll assembly 200 / compressor, which will not be elaborated further here.

[0112] The vehicle 1 can be a gasoline-powered vehicle, a plug-in hybrid electric vehicle, or a new energy vehicle, etc., and this application does not make any specific restrictions on it.

[0113] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0114] In the above embodiments, the descriptions of each embodiment have their own emphasis. Parts not described in detail in a particular embodiment can be referred to in the relevant descriptions of other embodiments. The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0115] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A seal for a scroll plate of a compressor, characterized in that, The width of the seal tends to decrease along the extension direction of the seal.

2. The seal according to claim 1, characterized in that, The ratio of the maximum width to the minimum width of the seal is between 0.2 and 1.

3. The seal according to claim 1, characterized in that, The maximum width of the seal is in the range of 1.5 to 7.5 mm; And / or, the minimum width of the seal is in the range of 0.5 to 1.5 mm.

4. The seal according to any one of claims 1 to 3, characterized in that, The width of at least a portion of the seal gradually decreases along the extension direction of the seal.

5. A scroll disk assembly, characterized in that, include: A scroll plate has a profiled section, and the end of the profiled section is provided with a sealing groove that extends along the profiled section; A sealing element is disposed in the sealing groove; The width of the seal tends to decrease in the direction of extension from the inside to the outside along the profile portion.

6. The scroll disk assembly according to claim 5, characterized in that, The ratio of the maximum width to the minimum width of the seal in the extension direction along the profile portion ranges from 0.2 to 1; and / or, The ratio of the maximum width to the minimum width of the sealing groove along the extension direction of the profile portion ranges from 0.2 to 1.

7. The scroll disk assembly according to claim 5, characterized in that, The maximum width of the seal is in the range of 1.5 to 7.5 mm; and / or, The maximum width of the sealing groove ranges from 1.5 to 7.5 mm.

8. The scroll disk assembly according to claim 5, characterized in that, The minimum width of the seal is in the range of 0.5 to 1.5 mm; and / or, The minimum width of the sealing groove ranges from 0.5 to 1.5 mm.

9. The scroll disk assembly according to any one of claims 5 to 8, characterized in that, The profiled section extends along the vortex line.

10. The scroll disk assembly according to any one of claims 5 to 8, characterized in that, The seal is adapted to the sealing groove.

11. The scroll disk assembly according to any one of claims 5 to 8, characterized in that, The width of the seal and / or the width of the sealing groove gradually decreases in the direction of extension from the inside to the outside along the profile portion.

12. A compressor, characterized in that, include: The scroll disk assembly as described in any one of claims 5 to 11.

13. The compressor according to claim 12, characterized in that, The scroll disk assembly includes: a moving scroll disk and a stationary scroll disk; The sealing groove is formed on the moving scroll and / or the stationary scroll, so that the sealing element is disposed between the moving scroll and the stationary scroll.

14. The compressor according to claim 13, characterized in that, The moving scroll and the stationary scroll surround each other to form a compression cavity for containing the compressed working fluid; the sealing element is disposed between the moving scroll and the stationary scroll and is located on the periphery of the compression cavity to form a seal for the compression cavity.

15. The compressor according to claim 14, characterized in that, The compressor is equipped with: The vortex inlet is formed between the stationary vortex disk and the moving vortex disk; The vortex outlet is formed on the stationary vortex disk; The vortex inlet and the vortex outlet are connected through the compression chamber; the vortex inlet is located on the periphery of the vortex outlet along the extension direction of the profile portion.

16. The compressor according to claim 15, characterized in that, At one end near the vortex outlet along the extension direction of the profile portion, the wall of the sealing groove is spaced apart from the end face of the seal.

17. The compressor according to claim 15, characterized in that, The seal is located between the bottom of the sealing groove and the bottom wall of the compression chamber.

18. The compressor according to claim 17, characterized in that, At least one of the bottom of the sealing groove and the bottom wall of the compression chamber is in contact with the sealing element.

19. A vehicle, characterized in that, It includes the seal as described in any one of claims 1 to 4, or the scroll plate assembly as described in any one of claims 5 to 11, or the compressor as described in any one of claims 12 to 18.

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