Static volute, compressor and refrigeration device

Abstract

The application provides a static scroll, a compressor and a refrigeration device. The static scroll comprises a disc body, the disc body is provided with a suction port for communicating with the outside; a static scroll tooth is arranged on one side of the disc body and forms a suction passage with the disc body, the suction passage communicates with the suction port, the suction passage comprises a first suction section and a second suction section connected with each other, and the first suction section is arranged closer to the suction port than the second suction section; wherein along the radial direction of the disc body, the width of the first suction section is greater than the width of the second suction section.

Description

Technical Field

[0001] This invention relates to the field of stationary scroll plate technology, and more specifically, to a stationary scroll plate, a compressor, and a refrigeration device. Background Technology

[0002] Scroll compressors are widely used in air conditioning and heat pump systems due to their high efficiency, small size, light weight, and stable operation. In a scroll compressor, the moving and stationary scroll plates are the most crucial components. The meshing of the profiles on the moving and stationary scroll plates forms a series of crescent-shaped compression chambers. With the eccentric revolution of the moving scroll plate, these crescent-shaped compression chambers continuously move from the periphery towards the center. As a result, the refrigerant within the chambers is pushed towards the center, its volume continuously decreasing and its pressure continuously increasing until it connects with the central exhaust port. The refrigerant then becomes a high-pressure gas and is discharged from the compression chamber, completing the compression process.

[0003] Currently, with the market demand for large displacement and high speed, the maximum operating frequency of scroll compressors is also increasing. However, under high speed conditions, the centrifugal force of the moving scroll increases sharply. Under the action of deformation and centrifugal force, the contact stress between the tail of the moving scroll and the side wall of the stationary scroll also increases sharply, which can easily lead to scroll breakage in extreme cases. Summary of the Invention

[0004] The embodiments of the present invention are intended to at least solve one of the technical problems existing in the prior art.

[0005] Therefore, a first aspect of the embodiments of the present invention provides a static vortex disk.

[0006] A second aspect of the present invention provides a compressor.

[0007] A third aspect of the present invention provides a refrigeration device.

[0008] In view of the above, according to a first aspect of the present invention, a static vortex disk is provided, the static vortex disk comprising: a disk body having an air intake port for communicating with the outside; and static vortex teeth disposed on one side of the disk body and forming an air intake channel with the disk body, the air intake channel communicating with the air intake port, the air intake channel including a first air intake section and a second air intake section connected thereto, the first air intake section being disposed closer to the air intake port than the second air intake section; wherein, along the radial direction of the disk body, the width of the first air intake section is greater than the width of the second air intake section.

[0009] The static vortex disk provided in this embodiment of the invention includes a disk body and static vortex teeth. Specifically, the static vortex teeth are disposed on one side of the disk body, and the static vortex teeth and the disk body form an air intake channel, which is connected to the air intake port on the disk body.

[0010] In addition, the compressor also includes a moving scroll. The moving scroll teeth of the moving scroll insert into the intake channel and cooperate with the stationary scroll to form multiple crescent-shaped compression chambers. The compression chambers are connected to the intake port, which is connected to the compressor's intake pipe. Specifically, the refrigerant enters the intake port through the intake pipe and then enters the compression chamber through the intake port. As the moving scroll rotates relative to the stationary scroll, the compression chamber moves continuously from the periphery to the center, its volume continuously decreasing, causing the refrigerant pressure inside the compression chamber to continuously increase. Finally, the compressed high-pressure refrigerant is discharged from the compression chamber through the exhaust port on the scroll body, completing the process of refrigerant intake, compression, and exhaust.

[0011] Understandably, under high-speed conditions, the centrifugal force of the moving scroll increases sharply, and the tail of the moving scroll tooth is a cantilever beam structure. That is, the end of the moving scroll tooth near the intake port is a cantilever beam structure. When the moving scroll rotates relative to the stationary scroll, the tail of the moving scroll tooth is deformed and subjected to centrifugal force, which causes the contact stress between the tail of the moving scroll tooth and the channel wall of the intake channel to increase sharply, making the moving scroll prone to breakage under extreme conditions.

[0012] Furthermore, during compressor operation, stress concentration also occurs at the connection between the tail of the moving scroll tooth and the end plate of the moving scroll. When the compressor is running at high speed, if the stress at the connection between the tail of the moving scroll tooth and the end plate exceeds the fatigue strength of the moving scroll tooth, it may also break.

[0013] The intake channel includes a first intake section and a second intake section. Specifically, the first intake section is connected to the second intake section, and the first intake section is located close to the intake port. That is to say, when the moving volute and the stationary volute cooperate to form a compression chamber, at least a portion of the cantilever end of the moving volute is located in the first intake section.

[0014] Along the radial direction of the disk body, the width of the first suction section is greater than the width of the second suction section. In other words, the width of the first suction section that mates with the cantilever end of the moving scroll tooth is increased. This results in a certain gap being formed between at least a portion of the cantilever end and the channel wall of the first suction section during the rotation of the moving scroll tooth relative to the stationary scroll tooth. This effectively improves the stress on the cantilever end of the moving scroll tooth under high-speed conditions, significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the channel wall of the first suction section, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. This improves the strength of the moving scroll tooth, extends the service life of the stationary scroll tooth, the moving scroll tooth, and the compressor with the stationary scroll tooth, and improves the stability and reliability of the compressor during high-speed operation, thereby meeting the requirements of high-speed operation of the compressor.

[0015] Among them, it can meet the high-speed operation requirements of compressors of 140 rpm and above.

[0016] Furthermore, by increasing the radial width of the first intake section that mates with the cantilever end of the moving scroll, the strength of the moving scroll that mates with the stationary scroll is improved. Compared to manufacturing the moving scroll with high-strength materials in related technologies, this reduces the processing difficulty of both the stationary and moving scrolls, thereby reducing the processing cost of the compressor and making it suitable for mass production.

[0017] In addition, the static vortex disk provided by the above-described technical solution of the present invention also has the following additional technical features:

[0018] In some embodiments, optionally, the width d1 of the first suction section and the width d2 of the second suction section, along the radial direction of the disc body, satisfy 0.01mm≤d1-d2≤0.2mm.

[0019] In this embodiment, the range of values ​​for the difference between the width of the first suction section and the width of the second suction section along the radial direction of the disc body is defined.

[0020] Understandably, during the rotation of the moving scroll relative to the stationary scroll, the cantilever end of the moving scroll tooth contacts both opposite channel walls of the first intake section, increasing the radial width of the first intake section. This can be achieved by having one channel wall of the first intake section concave radially inward or outward, or by having one channel wall concave radially inward and the other channel wall concave radially outward. The specific configuration can be determined according to actual needs.

[0021] By limiting the range of the difference between the width of the first intake section and the width of the second intake section, the width of the gap formed when the cantilever end of the moving volute mates with the channel wall of the first intake section is limited. This improves the stress on the cantilever end of the moving volute mate under high compressor speed operation, significantly reduces the contact stress between the cantilever end of the moving volute mate and the channel wall of the first intake section, and avoids stress concentration that could cause the cantilever end of the moving volute mate to break. This increases the strength of the moving volute mate while preventing excessive gap between the cantilever end of the moving volute mate and the channel wall of the first intake section, thus ensuring the stable operation of the compressor.

[0022] In some embodiments, optionally, along the radial direction of the disc body, the stationary vortex includes a first sidewall and a second sidewall disposed opposite to each other, the first sidewall being located radially outside the second sidewall, the first sidewall and the second sidewall forming an air intake channel; the first sidewall extends along a first spiral line; and / or the second sidewall extends along a second spiral line.

[0023] In this embodiment, along the radial direction of the disk body, the stationary volute includes a first sidewall and a second sidewall, and the first sidewall and the second sidewall are arranged opposite to each other, forming an air intake channel. The first sidewall is located radially outside the second sidewall, that is, the first sidewall is the inner sidewall of the air intake channel, and the second sidewall is the outer sidewall of the air intake channel. Specifically, the first sidewall can be composed of a circular involute or an algebraic spiral, and the second sidewall can be composed of a circular involute or an algebraic spiral.

[0024] Understandably, if the first and second sidewalls are composed of involutes, their base circle radii will be different. Similarly, if they are composed of algebraic spirals, their eccentric radii will be different. The specific settings can be configured according to actual needs.

[0025] Optionally, the first sidewall extends along a first helix. Alternatively, the second sidewall extends along a second helix. Or, the first sidewall extends along the first helix, and the second sidewall extends along the second helix. It is understood that the eccentric radii of the first and second helices are different.

[0026] In some embodiments, the first sidewall may optionally include a first channel wall located in the first intake section and a second channel wall located in the second intake section, the second channel wall being connected to the first channel wall; wherein, along the radial direction of the disc body, the first channel wall is located outside the extension wall of the second channel wall and has a first gap between it and the extension wall of the second channel wall.

[0027] In this embodiment, the first sidewall includes a first channel wall and a second channel wall. Specifically, the first channel wall is located in the first intake section, and the second channel wall is located in the second intake section. That is, the first channel wall is closer to the intake port than the second channel wall.

[0028] Along the radial direction of the disc body, the first channel wall is located outside the extension wall of the second channel wall. That is, a portion of the first sidewall near the air intake is recessed radially outward to increase the radial width of the first air intake section.

[0029] When the moving volute of the moving scroll is inserted into the intake channel and the moving scroll rotates relative to the stationary scroll, and the moving volute contacts the first side wall, a gap with a first distance is formed between the cantilever end of the moving volute and the first channel wall. This effectively improves the stress on the cantilever end of the moving volute under high speed conditions, significantly reduces the contact stress between the cantilever end of the moving volute and the first channel wall, and also avoids stress concentration that could cause the cantilever end of the moving volute to break. This improves the strength of the moving volute, extends the service life of the stationary scroll, the moving scroll, and the compressor with the stationary scroll, and improves the stability and reliability of the compressor during high-speed operation, thereby meeting the requirements of high-speed operation of the compressor.

[0030] In some embodiments, the first spacing H1 may optionally satisfy 0.01mm ≤ H1 ≤ 0.1mm.

[0031] In this embodiment, the range of the first spacing is defined, that is, the range of the width of the gap formed between the cantilever end of the moving vortex and the first channel wall is defined.

[0032] By setting the first gap between 0.01mm and 0.1mm, the stress on the cantilever end of the moving scroll tooth can be improved when the compressor is running at high speed. This significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the first channel wall, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. This improves the strength of the moving scroll tooth and avoids leakage caused by an excessive gap between the cantilever end of the moving scroll tooth and the first channel wall, thus further ensuring the stable operation of the compressor.

[0033] In some embodiments, optionally, the expansion angle β1 of the first channel wall and the expansion angle β2 of the second channel wall satisfy 10°≤β1-β2≤90°.

[0034] In this embodiment, the range of the difference between the unfolding angle of the first channel wall and the unfolding angle of the second channel wall is defined. That is, the length of the first channel wall along the circumferential direction of the disk body is defined, which is also the arc length of the first channel wall.

[0035] By limiting the circumferential length of the first channel wall, that is, limiting the circumferential length of the gap formed between the cantilever end of the moving scroll tooth and the first channel wall, the stress condition of the cantilever end of the moving scroll tooth can be improved when the compressor is running at high speed. This significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the first channel wall, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. While improving the strength of the moving scroll tooth, this also avoids leakage caused by an excessively large circumferential length of the gap formed between the cantilever end of the moving scroll tooth and the first channel wall, thus further ensuring the stable operation of the compressor.

[0036] In some embodiments, the second sidewall may optionally include a third channel wall located in the first intake section and a fourth channel wall located in the second intake section, the third channel wall being connected to the fourth channel wall, and the first channel wall being located outside the third channel wall in the radial direction of the disc body; wherein, in the radial direction of the disc body, the third channel wall is located inside the extension wall of the fourth channel wall and has a second distance between it and the extension wall of the fourth channel wall.

[0037] In this embodiment, the second sidewall includes a third channel wall and a fourth channel wall. Specifically, the third channel wall is located in the first intake section, and the fourth channel wall is located in the second intake section. That is, the third channel wall is closer to the intake port than the fourth channel wall.

[0038] Along the radial direction of the disc body, the third channel wall is located inside the extension wall of the fourth channel wall. That is, a portion of the second sidewall near the intake port is recessed radially inward to increase the radial width of the first intake section.

[0039] When the moving scroll tooth of the moving scroll is inserted into the intake channel and the moving scroll rotates relative to the stationary scroll, and the moving scroll tooth contacts the second side wall, a gap with a second spacing is formed between the cantilever end of the moving scroll tooth and the third channel wall. This effectively improves the stress on the cantilever end of the moving scroll tooth under high speed conditions, significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the third channel wall, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. This improves the strength of the moving scroll tooth, extends the service life of the stationary scroll, the moving scroll, and the compressor with the stationary scroll, and improves the stability and reliability of the compressor during high-speed operation, thereby meeting the requirements of high-speed operation of the compressor.

[0040] In some embodiments, the second spacing H2 may optionally satisfy 0.01mm ≤ H2 ≤ 0.1mm.

[0041] In this embodiment, the range of the second spacing is defined, which is to say, the range of the width of the gap formed between the cantilever end of the moving vortex and the third channel wall is defined.

[0042] By setting the second gap between 0.01mm and 0.1mm, the stress on the cantilever end of the moving scroll tooth can be improved when the compressor is running at high speed. This significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the third channel wall, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. This improves the strength of the moving scroll tooth and avoids leakage caused by an excessive gap between the cantilever end of the moving scroll tooth and the third channel wall, thus further ensuring the stable operation of the compressor.

[0043] In some embodiments, optionally, the expansion angle α1 of the third channel wall and the expansion angle α2 of the fourth channel wall satisfy 10°≤α1-α2≤90°.

[0044] In this embodiment, the range of the difference between the unfolding angle of the third channel wall and the unfolding angle of the fourth channel wall is defined. That is, the length of the third channel wall along the circumferential direction of the disk body is defined, which is also the arc length of the third channel wall.

[0045] By limiting the circumferential length of the third channel wall, that is, limiting the circumferential length of the gap formed between the cantilever end of the moving scroll tooth and the third channel wall, the stress condition of the cantilever end of the moving scroll tooth can be improved when the compressor is running at high speed. This significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the third channel wall, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. While improving the strength of the moving scroll tooth, this also avoids leakage caused by an excessively large circumferential length of the gap formed between the cantilever end of the moving scroll tooth and the third channel wall, thus further ensuring the stable operation of the compressor.

[0046] In some embodiments, the first sidewall may optionally include a first transition wall, and the first channel wall and the second channel wall are connected through the first transition wall; and / or the second sidewall may also include a second transition wall, and the third channel wall and the fourth channel wall are connected through the second transition wall.

[0047] In this embodiment, the first sidewall further includes a first transition wall. Specifically, the first channel wall and the second channel wall are connected by the first transition wall.

[0048] Alternatively, the second sidewall may also include a second transition wall, and the third channel wall and the fourth channel wall may be connected by the second transition wall.

[0049] Alternatively, the first sidewall may further include a first transition wall, the second sidewall may further include a second transition wall, the first channel wall may be connected to the second channel wall via the first transition wall, and the third channel wall may be connected to the fourth channel wall via the second transition wall, thereby forming an intake channel.

[0050] Understandably, the static vortex also includes the intake-side arc section located at the intake port, and the correction section located at the center of the disk body.

[0051] It is worth noting that the first transition wall is constructed as an arc-shaped wall or a straight wall, and / or the second transition wall is constructed as an arc-shaped wall or a straight wall. The specific configuration can be determined according to actual needs.

[0052] In some embodiments, the first transition wall is optionally configured as a first arcuate wall, which is tangent to the first channel wall and / or the second channel wall; and / or the second transition wall is configured as a second arcuate wall, which is tangent to the third channel wall and / or the fourth channel wall.

[0053] In this embodiment, the first transition wall is a first arc-shaped wall, which is tangent to the first channel wall. Alternatively, the first arc-shaped wall is tangent to the second channel wall, or both the first arc-shaped wall and the first and second channel walls are tangent. This ensures a smooth transition at the connection between the first arc-shaped wall and the first and / or second channel walls, reducing wear on the moving scroll during rotation relative to the stationary scroll and further extending the compressor's service life.

[0054] The second transition wall is a second arc-shaped wall, which is tangent to the third channel wall. Alternatively, the second arc-shaped wall is tangent to the fourth channel wall, or it is tangent to both the third and fourth channel walls. This ensures a smooth transition at the connection between the second arc-shaped wall and the third and / or fourth channel walls, reducing wear on the moving scroll during rotation relative to the stationary scroll and further extending the compressor's service life.

[0055] Furthermore, the first transition wall is a first arc-shaped wall, and the second transition wall is a second arc-shaped wall. The specific configuration can be adjusted according to actual needs.

[0056] In some embodiments, the equation of the first helix is ​​optionally:

[0057] x=-a×λ k ×cosλ-r1×cos(λ-arctan(k / λ));y=a×λ k ×sinλ+r1×sin(λ-arctan(k / λ));

[0058] Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r1 is the eccentric radius.

[0059] In this embodiment, the equation of the first helix is ​​defined. Specifically, at least a portion of the first sidewall extends along the first helix. It is understood that the eccentric radius of the same helix remains unchanged, but the unfolding angle is different at different positions.

[0060] For example, the second channel wall and its extension have different unfolding angles, while other parameters are the same. The first channel wall and its extension have the same unfolding angle, but different eccentric radii. Specifically, since the first channel wall is located radially outside the extension of the second channel wall, the eccentric radius of the first channel wall is larger than that of the second channel wall.

[0061] The equation of the first spiral is given by a Cartesian coordinate system with the center of the disk body as the origin. It can be understood that the unfolding angle and the unfolding angle in radians can be converted to each other. Specifically, λ = β ÷ 180° × π, where β is the unfolding angle of the first sidewall.

[0062] Furthermore, a and k are constants.

[0063] In some embodiments, the equation of the second helix is ​​optionally:

[0064] x=a×λ k ×cosλ-r2×cos(λ-arctan(k / λ));y=-a×λ k×sinλ+r2×sin(λ-arctan(k / λ));

[0065] Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r2 is the eccentric radius.

[0066] In this embodiment, the equation of the second helix is ​​defined. Specifically, at least a portion of the second sidewall extends along the second helix. It is understood that the eccentric radius of the same helix remains unchanged, but the unfolding angle is different at different positions.

[0067] For example, the fourth channel wall and its extension wall have different unfolding angles, but the other parameters are the same. The third channel wall and its extension wall have the same unfolding angle, but different eccentric radii. Specifically, since the third channel wall is located inside the radial direction of the fourth channel wall's extension wall, that is, the eccentric radius of the third channel wall is smaller than that of the fourth channel wall.

[0068] The equation of the second spiral is given in a Cartesian coordinate system with the center of the disk body as the origin. It can be understood that the unfolding angle and the unfolding angle in radians can be converted to each other; specifically, λ = α ÷ 180° × π, where α is the unfolding angle of the second sidewall.

[0069] Furthermore, a and k are constants.

[0070] According to a second aspect of the present invention, a compressor is provided, comprising a static scroll plate as provided by any of the above-described technical solutions, and thus possessing all the beneficial technical effects of the static scroll plate, which will not be elaborated further here.

[0071] Furthermore, the compressor also includes a moving scroll, which includes an end plate and moving scroll teeth. The moving scroll teeth are located on the side of the end plate facing the stationary scroll and can be inserted into the intake passage so that the moving scroll and the stationary scroll cooperate to form a compression chamber, which is connected to the intake port. The moving scroll teeth include a cantilever end away from the center of the end plate, and at least a portion of the cantilever end is located in the first intake section.

[0072] The compressor provided in this embodiment of the invention includes a stationary scroll and a moving scroll. Specifically, the moving scroll includes a connected end plate and moving scroll teeth. The moving scroll teeth are located on the side of the end plate facing the stationary scroll and can be inserted into the intake channel so that the stationary scroll and the moving scroll cooperate to form a compression chamber.

[0073] Specifically, the refrigerant enters the intake port through the intake pipe and then enters the compression chamber through the intake port. As the moving scroll rotates relative to the stationary scroll, the compression chamber moves continuously from the periphery to the center, and its volume continuously decreases, causing the refrigerant pressure in the compression chamber to continuously increase. Finally, the compressed high-pressure refrigerant is discharged from the compression chamber through the exhaust port on the scroll body, completing the process of refrigerant intake, compression and exhaust.

[0074] Understandably, under high-speed conditions, the centrifugal force of the moving scroll increases sharply, and the tail of the moving scroll tooth is a cantilever beam structure. That is, the end of the moving scroll tooth near the intake port is a cantilever beam structure. When the moving scroll rotates relative to the stationary scroll, the tail of the moving scroll tooth is deformed and subjected to centrifugal force, which causes the contact stress between the tail of the moving scroll tooth and the channel wall of the intake channel to increase sharply, making the moving scroll prone to breakage under extreme conditions.

[0075] Furthermore, during compressor operation, stress concentration also occurs at the connection between the tail of the moving scroll tooth and the end plate of the moving scroll. When the compressor is running at high speed, if the stress at the connection between the tail of the moving scroll tooth and the end plate exceeds the fatigue strength of the moving scroll tooth, it may also break.

[0076] The intake channel includes a first intake section and a second intake section. Specifically, the first intake section is connected to the second intake section, and the first intake section is located close to the intake port. That is to say, when the moving volute and the stationary volute cooperate to form a compression chamber, at least a portion of the cantilever end of the moving volute is located in the first intake section.

[0077] Along the radial direction of the disk body, the width of the first suction section is greater than the width of the second suction section. In other words, the width of the first suction section that mates with the cantilever end of the moving scroll tooth is increased. This results in a certain gap being formed between at least a portion of the cantilever end and the channel wall of the first suction section during the rotation of the moving scroll tooth relative to the stationary scroll tooth. This effectively improves the stress on the cantilever end of the moving scroll tooth under high-speed conditions, significantly reduces the contact stress between the cantilever end of the moving scroll tooth and the channel wall of the first suction section, and also avoids stress concentration that could cause the cantilever end of the moving scroll tooth to break. This improves the strength of the moving scroll tooth, extends the service life of the stationary scroll tooth, the moving scroll tooth, and the compressor with the stationary scroll tooth, and improves the stability and reliability of the compressor during high-speed operation, thereby meeting the requirements of high-speed operation of the compressor.

[0078] Among them, it can meet the high-speed operation requirements of compressors of 140 rpm and above.

[0079] Furthermore, by increasing the radial width of the first intake section that mates with the cantilever end of the moving scroll, the strength of the moving scroll that mates with the stationary scroll is improved. Compared to manufacturing the moving scroll with high-strength materials in related technologies, this reduces the processing difficulty of both the stationary and moving scrolls, thereby reducing the processing cost of the compressor and making it suitable for mass production.

[0080] It is worth noting that the compressor also includes a cross-shaped slip ring, main frame, crankshaft, stator, rotor, auxiliary frame, housing, upper cover, and lower cover. Specifically, after compression, the high-pressure refrigerant discharged through the exhaust port of the compressor body is discharged into the exhaust chamber, which is formed by the connection between the housing, upper cover, and lower cover. The high-pressure refrigerant flows downward to the motor formed by the stator and rotor to cool the motor, and finally is discharged through the exhaust pipe on the housing.

[0081] In addition, there is an oil sump between the housing and the lower cover. The oil sump contains lubricating oil. During the operation of the compressor, the lubricating oil is supplied from the oil sump along the central oil hole of the crankshaft to the upper part under the action of the oil guide component at the bottom of the crankshaft. After lubricating the bearing, it enters the oil storage part of the main frame and flows out from the oil return hole back to the bottom oil sump. Some of the lubricating oil also enters the compression chamber to lubricate the moving scroll and stationary scroll, thus achieving lubrication of the moving parts.

[0082] It is worth noting that compressors include, but are not limited to, scroll compressors.

[0083] According to a third aspect of the present invention, a refrigeration device is provided, comprising a static scroll as provided in the first aspect or a compressor as provided in the second aspect, and thus possessing all the beneficial technical effects of the static scroll or the compressor, which will not be elaborated further here.

[0084] Refrigeration equipment includes, but is not limited to, air conditioners.

[0085] Additional aspects and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description or may be learned by practice of the invention. Attached Figure Description

[0086] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0087] Figure 1 A schematic diagram of a static vortex disk according to an embodiment of the present invention is shown;

[0088] Figure 2 It shows Figure 1 An enlarged view of the stationary vortex disk in the illustrated embodiment at point A;

[0089] Figure 3 One of the schematic diagrams of a partial structure of a compressor according to an embodiment of the present invention is shown;

[0090] Figure 4 A second schematic diagram of a partial structure of a compressor according to an embodiment of the present invention is shown;

[0091] Figure 5A third schematic diagram of a partial structure of a compressor according to an embodiment of the present invention is shown;

[0092] Figure 6 A schematic diagram of a compressor according to an embodiment of the present invention is shown.

[0093] in, Figures 1 to 6 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0094] 100 Static scroll, 110 Scroll body, 111 Intake port, 120 Static scroll teeth, 121 First side wall, 1211 First channel wall, 1212 Second channel wall, 1213 First transition wall, 122 Second side wall, 1221 Third channel wall, 1222 Fourth channel wall, 1223 Second transition wall, 130 Intake channel, 131 First intake section, 132 Second intake section, 200 Compressor, 210 Moving scroll, 211 End plate, 212 Moving scroll teeth, 220 Compression chamber, 230 Cantilever end. Detailed Implementation

[0095] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0096] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0097] The following reference Figures 1 to 6 This describes a static scroll 100, a compressor 200, and a refrigeration device provided according to some embodiments of the present invention.

[0098] In one embodiment according to this application, such as Figure 1 and Figure 2 As shown, a static vortex disk 100 is proposed. The static vortex disk 100 includes: a disk body 110, which has an air intake port 111 for communicating with the outside; and static vortex teeth 120, which are disposed on one side of the disk body 110 and form an air intake channel 130 with the disk body 110. The air intake channel 130 is connected to the air intake port 111 and includes a first air intake section 131 and a second air intake section 132 connected to each other. The first air intake section 131 is disposed closer to the air intake port 111 than the second air intake section 132. In the radial direction of the disk body 110, the width of the first air intake section 131 is greater than the width of the second air intake section 132.

[0099] The static vortex disk 100 provided in this embodiment of the invention includes a disk body 110 and static vortex teeth 120. Specifically, the static vortex teeth 120 are disposed on one side of the disk body 110, and the static vortex teeth 120 and the disk body 110 form an air intake channel 130, which is connected to the air intake port 111 on the disk body 110.

[0100] In addition, such as Figure 3 , Figure 4 and Figure 5 As shown, the compressor 200 also includes a moving scroll 210. The moving scroll teeth 212 of the moving scroll 210 are inserted into the intake channel 130 and cooperate with the stationary scroll 100 to form multiple crescent-shaped compression chambers 220. The compression chambers 220 are connected to the intake port 111, which is connected to the intake pipe of the compressor 200. Specifically, the refrigerant enters the intake port 111 through the intake pipe and then enters the compression chamber 220 through the intake port 111. As the moving scroll 210 rotates relative to the stationary scroll 100, the compression chamber 220 moves continuously from the periphery to the center, and its volume continuously decreases, causing the refrigerant pressure in the compression chamber 220 to continuously increase. Finally, the compressed high-pressure refrigerant is discharged from the compression chamber 220 through the exhaust port on the scroll body 110, completing the process of refrigerant intake, compression, and exhaust.

[0101] Understandably, under high-speed conditions, the centrifugal force of the moving volute 210 increases sharply, and the tail of the moving volute 212 is a cantilever beam structure. That is, the end of the moving volute 212 near the intake port 111 is a cantilever beam structure. When the moving volute 210 rotates relative to the stationary volute 100, the tail of the moving volute 212 is deformed and subjected to centrifugal force, which causes the contact stress between the tail of the moving volute 212 and the channel wall of the intake channel 130 to increase sharply, making the moving volute 210 prone to breakage under extreme conditions.

[0102] Moreover, during the operation of the compressor 200, stress concentration also occurs at the connection between the tail of the moving scroll 212 and the end plate 211 of the moving scroll 210. When the compressor 200 is running at high speed, if the stress at the connection between the tail of the moving scroll 212 and the end plate 211 exceeds the fatigue strength of the moving scroll 212, it may also break.

[0103] The intake channel 130 includes a first intake section 131 and a second intake section 132. Specifically, the first intake section 131 is connected to the second intake section 132, and the first intake section 131 is located close to the intake port 111. That is, when the moving volute 210 and the stationary volute 100 cooperate to form a compression chamber 220, at least a portion of the cantilever end 230 of the moving volute 212 is located in the first intake section 131.

[0104] Along the radial direction of the disk body 110, the width of the first suction section 131 is greater than the width of the second suction section 132. This means that the width of the first suction section 131, which engages with the cantilever end 230 of the moving scroll gear 212, is increased. This results in at least a portion of the cantilever end 230 forming a certain gap with the channel wall of the first suction section 131 during the rotation of the moving scroll 210 relative to the stationary scroll 100. This effectively improves the performance of the compressor 200 at high speeds, particularly at the cantilever end 230 of the moving scroll gear 212. The stress distribution of 30 significantly reduces the contact stress between the cantilever end 230 of the moving scroll 212 and the channel wall of the first intake section 131, and also avoids stress concentration causing the cantilever end 230 of the moving scroll 212 to break, thereby improving the strength of the moving scroll 212, extending the service life of the stationary scroll 100, the moving scroll 210 and the compressor 200 with the stationary scroll 100, improving the stability and reliability of the compressor 200 during high-speed operation, and thus meeting the requirements of the compressor 200 for high-speed operation.

[0105] Among them, it can meet the high-speed operation requirements of compressor 200 at 140 rpm and above.

[0106] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0107] In some embodiments, optionally, along the radial direction of the disc body 110, the width d1 of the first suction section 131 and the width d2 of the second suction section 132 satisfy 0.01mm≤d1-d2≤0.2mm.

[0108] In this embodiment, the range of values ​​for the difference between the width of the first suction section 131 and the width of the second suction section 132 along the radial direction of the disk body 110 is defined.

[0109] Understandably, during the rotation of the moving scroll 210 relative to the stationary scroll 100, the cantilever end 230 of the moving scroll tooth 212 contacts both opposite channel walls of the first intake section 131, increasing the radial width of the first intake section 131. This can be achieved by having one channel wall of the first intake section 131 concave radially inward or outward, or by having one channel wall of the first intake section 131 concave radially inward and the other channel wall concave radially outward. The specific configuration can be determined according to actual needs.

[0110] By limiting the range of the difference between the width of the first suction section 131 and the width of the second suction section 132, the width of the gap formed when the cantilever end 230 of the moving volute 212 mates with the channel wall of the first suction section 131 is limited. This improves the stress on the cantilever end 230 of the moving volute 212 when the compressor 200 is running at high speed, significantly reduces the contact stress between the cantilever end 230 of the moving volute 212 and the channel wall of the first suction section 131, and also avoids stress concentration that could cause the cantilever end 230 of the moving volute 212 to break. This improves the strength of the moving volute 212 while avoiding excessive gap between the cantilever end 230 of the moving volute 212 and the channel wall of the first suction section 131, thus ensuring the stable operation of the compressor 200.

[0111] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0112] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, along the radial direction of the disk body 110, the stationary volute 120 includes a first sidewall 121 and a second sidewall 122 disposed opposite to each other, the first sidewall 121 being located radially outside the second sidewall 122, the first sidewall 121 and the second sidewall 122 forming an air intake channel 130; the first sidewall 121 extends along a first spiral line; and / or the second sidewall 122 extends along a second spiral line.

[0113] In this embodiment, along the radial direction of the disk body 110, the stationary volute 120 includes a first sidewall 121 and a second sidewall 122, with the first sidewall 121 and the second sidewall 122 arranged opposite to each other, forming an air intake channel 130. The first sidewall 121 is located radially outside the second sidewall 122, that is, the first sidewall 121 is the inner sidewall of the air intake channel 130, and the second sidewall 122 is the outer sidewall of the air intake channel 130. Specifically, the first sidewall 121 can be composed of a circular involute or an algebraic spiral, and the second sidewall 122 can be composed of a circular involute or an algebraic spiral.

[0114] It is understandable that if the first sidewall 121 and the second sidewall 122 are formed by an involute, then the base circle radii of the first sidewall 121 and the second sidewall 122 will be different. If the first sidewall 121 and the second sidewall 122 are formed by an algebraic spiral, then the eccentric radii of the first sidewall 121 and the second sidewall 122 will be different. The specific settings can be configured according to actual needs.

[0115] Optionally, the first sidewall 121 extends along a first helix. Alternatively, the second sidewall 122 extends along a second helix. Or, the first sidewall 121 extends along the first helix, and the second sidewall 122 extends along the second helix. It is understood that the eccentric radii of the first and second helices are different.

[0116] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the first sidewall 121 includes a first channel wall 1211 located in the first intake section 131 and a second channel wall 1212 located in the second intake section 132, the second channel wall 1212 being connected to the first channel wall 1211; wherein, along the radial direction of the disk body 110, the first channel wall 1211 is located outside the extension wall of the second channel wall 1212 and has a first gap with the extension wall of the second channel wall 1212.

[0117] In this embodiment, the first sidewall 121 includes a first channel wall 1211 and a second channel wall 1212. Specifically, the first channel wall 1211 is located in the first intake section 131, and the second channel wall 1212 is located in the second intake section 132. That is, the first channel wall 1211 is closer to the intake port 111 than the second channel wall 1212.

[0118] Along the radial direction of the disc body 110, the first channel wall 1211 is located outside the extension wall of the second channel wall 1212. That is, a portion of the first side wall 121 near the air intake 111 is recessed radially outward to increase the radial width of the first air intake section 131.

[0119] When the moving scroll tooth 212 of the moving scroll 210 is inserted into the suction channel 130 and the moving scroll 210 rotates relative to the stationary scroll 100, and the moving scroll tooth 212 contacts the first side wall 121, a gap with a first distance is formed between the cantilever end 230 of the moving scroll tooth 212 and the first channel wall 1211. This effectively improves the stress on the cantilever end 230 of the moving scroll tooth 212 under high speed conditions of the compressor 200, significantly reduces the contact stress between the cantilever end 230 of the moving scroll tooth 212 and the first channel wall 1211, and also avoids stress concentration causing the cantilever end 230 of the moving scroll tooth 212 to break. This improves the strength of the moving scroll tooth 212, extends the service life of the stationary scroll 100, the moving scroll 210, and the compressor 200 with the stationary scroll 100, improves the stability and reliability of the compressor 200 during high-speed operation, and thus meets the requirements of high-speed operation of the compressor 200.

[0120] Among them, it can meet the high-speed operation requirements of compressor 200 at 140 rpm and above.

[0121] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0122] In some embodiments, the first spacing H1 may optionally satisfy 0.01mm ≤ H1 ≤ 0.1mm.

[0123] In this embodiment, the range of the first spacing is defined, that is, the range of the width of the gap formed between the cantilever end 230 of the moving vortex 212 and the first channel wall 1211 is defined.

[0124] By setting the first gap between 0.01mm and 0.1mm, the stress on the cantilever end 230 of the moving scroll gear 212 can be improved when the compressor 200 is running at high speed. This significantly reduces the contact stress between the cantilever end 230 of the moving scroll gear 212 and the first channel wall 1211, and also avoids stress concentration that could cause the cantilever end 230 of the moving scroll gear 212 to break. This improves the strength of the moving scroll gear 212 and avoids leakage caused by an excessive gap between the cantilever end 230 of the moving scroll gear 212 and the first channel wall 1211, further ensuring the stable operation of the compressor 200.

[0125] In some embodiments, optionally, the expansion angle β1 of the first channel wall 1211 and the expansion angle β2 of the second channel wall 1212 satisfy 10°≤β1-β2≤90°.

[0126] In this embodiment, the range of the difference between the unfolding angle of the first channel wall 1211 and the unfolding angle of the second channel wall 1212 is defined. That is, the length of the first channel wall 1211 along the circumferential direction of the disk body 110 is defined, which is also the arc length of the first channel wall 1211.

[0127] By limiting the circumferential length of the first channel wall 1211, that is, limiting the circumferential length of the gap formed between the cantilever end 230 of the moving scroll tooth 212 and the first channel wall 1211, the stress condition of the cantilever end 230 of the moving scroll tooth 212 can be improved when the compressor 200 is running at high speed. This significantly reduces the contact stress between the cantilever end 230 of the moving scroll tooth 212 and the first channel wall 1211, and also avoids stress concentration causing the cantilever end 230 of the moving scroll tooth 212 to break. While improving the strength of the moving scroll tooth 212, it also avoids the problem of leakage caused by the excessive circumferential length of the gap formed between the cantilever end 230 of the moving scroll tooth 212 and the first channel wall 1211, further ensuring the stable operation of the compressor 200.

[0128] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the second sidewall 122 includes a third channel wall 1221 located in the first intake section 131 and a fourth channel wall 1222 located in the second intake section 132. The third channel wall 1221 is connected to the fourth channel wall 1222. Along the radial direction of the disk body 110, the first channel wall 1211 is located outside the third channel wall 1221. In the radial direction of the disk body 110, the third channel wall 1221 is located inside the extension wall of the fourth channel wall 1222 and has a second distance between it and the extension wall of the fourth channel wall 1222.

[0129] In this embodiment, the second sidewall 122 includes a third channel wall 1221 and a fourth channel wall 1222. Specifically, the third channel wall 1221 is located in the first intake section 131, and the fourth channel wall 1222 is located in the second intake section 132. That is, the third channel wall 1221 is closer to the intake port 111 than the fourth channel wall 1222.

[0130] Along the radial direction of the disc body 110, the third channel wall 1221 is located inside the extension wall of the fourth channel wall 1222. That is, a portion of the second side wall 122 near the air intake 111 is radially recessed inward to increase the radial width of the first air intake section 131.

[0131] When the moving scroll tooth 212 of the moving scroll 210 is inserted into the intake channel 130 and the moving scroll 210 rotates relative to the stationary scroll 100, and the moving scroll tooth 212 contacts the second side wall 122, a gap with a second spacing is formed between the cantilever end 230 of the moving scroll tooth 212 and the third channel wall 1221. This effectively improves the stress on the cantilever end 230 of the moving scroll tooth 212 under high speed conditions of the compressor 200, significantly reduces the contact stress between the cantilever end 230 of the moving scroll tooth 212 and the third channel wall 1221, and also avoids stress concentration causing the cantilever end 230 of the moving scroll tooth 212 to break. This improves the strength of the moving scroll tooth 212, extends the service life of the stationary scroll 100, the moving scroll 210, and the compressor 200 with the stationary scroll 100, improves the stability and reliability of the compressor 200 during high-speed operation, and thus meets the requirements of high-speed operation of the compressor 200.

[0132] Among them, it can meet the high-speed operation requirements of compressor 200 at 140 rpm and above.

[0133] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0134] In some embodiments, the second spacing H2 may optionally satisfy 0.01mm ≤ H2 ≤ 0.1mm.

[0135] In this embodiment, the range of the second spacing is defined, that is, the range of the width of the gap formed between the cantilever end 230 of the moving vortex 212 and the third channel wall 1221 is defined.

[0136] By setting the second gap between 0.01mm and 0.1mm, the stress on the cantilever end 230 of the moving scroll gear 212 can be improved when the compressor 200 is running at high speed. This significantly reduces the contact stress between the cantilever end 230 of the moving scroll gear 212 and the third channel wall 1221, and also avoids stress concentration that could cause the cantilever end 230 of the moving scroll gear 212 to break. This improves the strength of the moving scroll gear 212 and avoids leakage caused by an excessive gap between the cantilever end 230 of the moving scroll gear 212 and the third channel wall 1221, further ensuring the stable operation of the compressor 200.

[0137] In some embodiments, optionally, the expansion angle α1 of the third channel wall 1221 and the expansion angle α2 of the fourth channel wall 1222 satisfy 10°≤α1-α2≤90°.

[0138] In this embodiment, the range of the difference between the unfolding angle of the third channel wall 1221 and the unfolding angle of the fourth channel wall 1222 is defined. That is, the length of the third channel wall 1221 along the circumferential direction of the disk body 110 is defined, which is also the arc length of the third channel wall 1221.

[0139] By limiting the circumferential length of the third channel wall 1221, that is, limiting the circumferential length of the gap formed between the cantilever end 230 of the moving scroll tooth 212 and the third channel wall 1221, the stress condition of the cantilever end 230 of the moving scroll tooth 212 can be improved when the compressor 200 is running at high speed. This significantly reduces the contact stress between the cantilever end 230 of the moving scroll tooth 212 and the third channel wall 1221, and also avoids stress concentration causing the cantilever end 230 of the moving scroll tooth 212 to break. While improving the strength of the moving scroll tooth 212, it also avoids the problem of leakage caused by the excessive circumferential length of the gap formed between the cantilever end 230 of the moving scroll tooth 212 and the third channel wall 1221, thus further ensuring the stable operation of the compressor 200.

[0140] like Figure 2 As shown, in some embodiments, optionally, the first sidewall 121 further includes a first transition wall 1213, the first channel wall 1211 and the second channel wall 1212 are connected through the first transition wall 1213; and / or the second sidewall 122 further includes a second transition wall 1223, the third channel wall 1221 and the fourth channel wall 1222 are connected through the second transition wall 1223.

[0141] In this embodiment, the first sidewall 121 further includes a first transition wall 1213. Specifically, the first channel wall 1211 and the second channel wall 1212 are connected through the first transition wall 1213.

[0142] Alternatively, the second sidewall 122 may also include a second transition wall 1223, and the third channel wall 1221 and the fourth channel wall 1222 may be connected through the second transition wall 1223.

[0143] Alternatively, the first sidewall 121 may further include a first transition wall 1213, the second sidewall 122 may further include a second transition wall 1223, the first channel wall 1211 may be connected to the second channel wall 1212 via the first transition wall 1213, and the third channel wall 1221 may be connected to the fourth channel wall 1222 via the second transition wall 1223, thereby forming an intake channel 130.

[0144] It is understandable that the stationary vortex 120 also includes an intake-side arc portion located at the intake port 111, and a correction section located at the center of the disk body 110.

[0145] It is worth noting that the first transition wall 1213 is constructed as an arc-shaped wall or a straight wall, and / or the second transition wall 1223 is constructed as an arc-shaped wall or a straight wall. The specific configuration can be determined according to actual needs.

[0146] Along the radial direction of the disk body 110, the width of the first suction section 131 is greater than the width of the second suction section 132. This means that the width of the first suction section 131, which engages with the cantilever end 230 of the moving scroll gear 212, is increased. This results in at least a portion of the cantilever end 230 forming a certain gap with the channel wall of the first suction section 131 during the rotation of the moving scroll 210 relative to the stationary scroll 100. This effectively improves the performance of the compressor 200 at high speeds, particularly at the cantilever end 230 of the moving scroll gear 212. The stress distribution of 30 significantly reduces the contact stress between the cantilever end 230 of the moving scroll 212 and the channel wall of the first intake section 131, and also avoids stress concentration causing the cantilever end 230 of the moving scroll 212 to break, thereby improving the strength of the moving scroll 212, extending the service life of the stationary scroll 100, the moving scroll 210 and the compressor 200 with the stationary scroll 100, improving the stability and reliability of the compressor 200 during high-speed operation, and thus meeting the requirements of the compressor 200 for high-speed operation.

[0147] Among them, it can meet the high-speed operation requirements of compressor 200 at 140 rpm and above.

[0148] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0149] like Figure 2 As shown, in some embodiments, optionally, the first transition wall 1213 is configured as a first arcuate wall, the first arcuate wall being tangent to the first channel wall 1211 and / or the second channel wall 1212; and / or the second transition wall 1223 is configured as a second arcuate wall, the second arcuate wall being tangent to the third channel wall 1221 and / or the fourth channel wall 1222.

[0150] In this embodiment, the first transition wall 1213 is a first arc-shaped wall, which is tangent to the first channel wall 1211. Alternatively, the first arc-shaped wall is tangent to the second channel wall 1212, or the first arc-shaped wall is tangent to both the first channel wall 1211 and the second channel wall 1212. This ensures a smooth transition at the connection between the first arc-shaped wall and the first channel wall 1211 and / or the second channel wall 1212, reducing wear on the moving scroll 210 during rotation relative to the stationary scroll 100, and further extending the service life of the compressor 200.

[0151] The second transition wall 1223 is a second arc-shaped wall, which is tangent to the third channel wall 1221. Alternatively, the second arc-shaped wall is tangent to the fourth channel wall 1222, or the second arc-shaped wall is tangent to both the third channel wall 1221 and the fourth channel wall 1222. This ensures a smooth transition at the connection between the second arc-shaped wall and the third channel wall 1221 and / or the fourth channel wall 1222, reducing wear on the moving scroll 210 during rotation relative to the stationary scroll 100, and further extending the service life of the compressor 200.

[0152] Furthermore, the first transition wall 1213 is a first arc-shaped wall, and the second transition wall 1223 is a second arc-shaped wall. The specific configuration can be adjusted according to actual needs.

[0153] In some embodiments, the equation of the first helix is ​​optionally:

[0154] x=-a×λ k ×cosλ-r1×cos(λ-arctan(k / λ));y=a×λ k ×sinλ+r1×sin(λ-arctan(k / λ));

[0155] Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r1 is the eccentric radius.

[0156] In this embodiment, the equation of the first helix is ​​defined. Specifically, at least a portion of the first sidewall 121 extends along the first helix. It can be understood that the eccentric radius of the same helix remains unchanged, but the unfolding angle is different at different positions. That is, the unfolding angle is different at different positions of the first sidewall 121.

[0157] For example, the second channel wall 1212 and its extension wall have different unfolding angles, while other parameters are the same. The first channel wall 1211 and its extension wall have the same unfolding angle, but different eccentric radii. Specifically, since the first channel wall 1211 is located outside the radial direction of the extension wall of the second channel wall 1212, that is, the eccentric radius of the first channel wall 1211 is larger than that of the second channel wall 1212.

[0158] The equation of the first spiral is given by a Cartesian coordinate system with the center of the disk body 110 as the origin. It can be understood that the unfolding angle and the unfolding angle in radians can be converted to each other. Specifically, λ = β ÷ 180° × π, where β is the unfolding angle of the first sidewall.

[0159] Furthermore, a and k are constants.

[0160] In some embodiments, the equation of the second helix is ​​optionally:

[0161] x=a×λ k ×cosλ-r2×cos(λ-arctan(k / λ));y=-a×λ k ×sinλ+r2×sin(λ-arctan(k / λ));

[0162] Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r2 is the eccentric radius.

[0163] In this embodiment, the equation of the second helix is ​​defined. Specifically, at least a portion of the second sidewall 122 extends along the second helix. It is understood that the eccentric radius of the same helix remains unchanged, but the unfolding angle is different at different positions. That is, the unfolding angle is different at different positions of the second sidewall 122.

[0164] For example, the fourth channel wall 1222 and its extension wall have different unfolding angles, but the other parameters are the same. The third channel wall 1221 and its extension wall have the same unfolding angle, but different eccentric radii. Specifically, since the third channel wall 1221 is located inside the radial direction of the extension wall of the fourth channel wall 1222, that is, the eccentric radius of the third channel wall 1221 is smaller than that of the fourth channel wall 1222.

[0165] The equation of the second spiral is given by a Cartesian coordinate system with the center of the disk body 110 as the origin. It can be understood that the unfolding angle and the unfolding angle in radians can be converted to each other. Specifically, λ = α ÷ 180° × π, where α is the unfolding angle of the second sidewall.

[0166] Furthermore, a and k are constants.

[0167] According to a second aspect of the present invention, a compressor 200 is provided, including a static scroll 100 as provided in any of the above embodiments, and thus possessing all the beneficial technical effects of the static scroll 100, which will not be repeated here.

[0168] like Figure 3 , Figure 4 , Figure 5 and Figure 6As shown, the compressor 200 further includes a moving scroll 210, which includes an end plate 211 and moving scroll teeth 212. The moving scroll teeth 212 are located on the side of the end plate 211 facing the stationary scroll 100 and can be inserted into the intake channel 130 so that the moving scroll 210 and the stationary scroll 100 cooperate to form a compression chamber 220, which is connected to the intake port 111. The moving scroll teeth 212 include a cantilever end 230 away from the center of the end plate 211, and at least a portion of the cantilever end 230 is located in the first intake section 131.

[0169] The compressor 200 provided in this embodiment of the invention includes a stationary scroll 100 and a moving scroll 210. Specifically, the moving scroll 210 includes a connected end plate 211 and a moving scroll tooth 212. The moving scroll tooth 212 is disposed on the side of the end plate 211 facing the stationary scroll 100, and the moving scroll tooth 212 can be inserted into the intake channel 130 so that the stationary scroll 100 and the moving scroll 210 cooperate to form a compression chamber 220.

[0170] Specifically, the refrigerant enters the intake port 111 through the intake pipe and then enters the compression chamber 220 through the intake port 111. As the moving scroll 210 rotates relative to the stationary scroll 100, the compression chamber 220 moves continuously from the periphery to the center, and its volume continuously decreases, causing the refrigerant pressure in the compression chamber 220 to continuously increase. Finally, the compressed high-pressure refrigerant is discharged from the compression chamber 220 through the exhaust port on the scroll body 110, completing the process of refrigerant intake, compression and exhaust.

[0171] Understandably, under high-speed conditions, the centrifugal force of the moving volute 210 increases sharply, and the tail of the moving volute 212 is a cantilever beam structure. That is, the end of the moving volute 212 near the intake port 111 is a cantilever beam structure. When the moving volute 210 rotates relative to the stationary volute 100, the tail of the moving volute 212 is deformed and subjected to centrifugal force, which causes the contact stress between the tail of the moving volute 212 and the channel wall of the intake channel 130 to increase sharply, making the moving volute 210 prone to breakage under extreme conditions.

[0172] Moreover, during the operation of the compressor 200, stress concentration also occurs at the connection between the tail of the moving scroll 212 and the end plate 211 of the moving scroll 210. When the compressor 200 is running at high speed, if the stress at the connection between the tail of the moving scroll 212 and the end plate 211 exceeds the fatigue strength of the moving scroll 212, it may also break.

[0173] The intake channel 130 includes a first intake section 131 and a second intake section 132. Specifically, the first intake section 131 is connected to the second intake section 132, and the first intake section 131 is located close to the intake port 111. That is, when the moving volute 210 and the stationary volute 100 cooperate to form a compression chamber 220, at least a portion of the cantilever end 230 of the moving volute 212 is located in the first intake section 131.

[0174] Along the radial direction of the disk body 110, the width of the first suction section 131 is greater than the width of the second suction section 132. This means that the width of the first suction section 131, which engages with the cantilever end 230 of the moving scroll gear 212, is increased. This results in at least a portion of the cantilever end 230 forming a certain gap with the channel wall of the first suction section 131 during the rotation of the moving scroll 210 relative to the stationary scroll 100. This effectively improves the performance of the compressor 200 at high speeds, particularly at the cantilever end 230 of the moving scroll gear 212. The stress distribution of 30 significantly reduces the contact stress between the cantilever end 230 of the moving scroll 212 and the channel wall of the first intake section 131, and also avoids stress concentration causing the cantilever end 230 of the moving scroll 212 to break, thereby improving the strength of the moving scroll 212, extending the service life of the stationary scroll 100, the moving scroll 210 and the compressor 200 with the stationary scroll 100, improving the stability and reliability of the compressor 200 during high-speed operation, and thus meeting the requirements of the compressor 200 for high-speed operation.

[0175] Among them, it can meet the high-speed operation requirements of compressor 200 at 140 rpm and above.

[0176] Furthermore, by increasing the radial width of the first intake section 131 that mates with the cantilever end 230 of the moving scroll 212, the strength of the moving scroll 210 that mates with the stationary scroll 100 is improved. Compared to manufacturing the moving scroll 210 with high-strength materials in related technologies, this reduces the processing difficulty of the stationary scroll 100 and the moving scroll 210, thereby reducing the processing cost of the compressor 200 and making it suitable for mass production.

[0177] It is worth noting that the compressor 200 also includes a cross-slip ring, main frame, crankshaft, stator, rotor, auxiliary frame, housing, upper cover, and lower cover. Specifically, after compression, the high-pressure refrigerant discharged through the exhaust port of the disc body 110 is discharged into the exhaust chamber, where the housing, upper cover, and lower cover are connected to form the exhaust chamber. The high-pressure refrigerant flows downward to the motor formed by the stator and rotor to cool the motor, and finally is discharged through the exhaust pipe on the housing.

[0178] In addition, there is an oil sump between the housing and the lower cover. The oil sump contains lubricating oil. During the operation of the compressor 200, the lubricating oil is supplied from the oil sump along the central oil hole of the crankshaft to the upper part under the action of the oil guide component at the lower part of the crankshaft. After lubricating the bearing, it enters the oil storage part of the main frame and flows out from the oil return hole back to the bottom oil sump. Some of the lubricating oil also enters the compression chamber 220 to lubricate the moving scroll 210 and the stationary scroll 100, thus achieving lubrication of the moving pair.

[0179] It is worth noting that compressor 200 includes, but is not limited to, scroll compressors.

[0180] According to a third aspect of the present invention, a refrigeration device is provided, comprising the static scroll 100 as provided in the first aspect above or the compressor 200 as provided in the second aspect above, and thus possessing all the beneficial technical effects of the static scroll 100 or the compressor 200, which will not be elaborated further here.

[0181] Refrigeration equipment includes, but is not limited to, air conditioners.

[0182] In the description of this specification, the terms "connection," "installation," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0183] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0184] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A static scroll disk, characterized in that, include: The disc body is provided with an air intake port for communicating with the outside. A stationary vortex is located on one side of the disk body and forms an air intake channel with the disk body. The air intake channel is connected to the air intake port. The air intake channel includes a first air intake section and a second air intake section connected to each other. The first air intake section is located closer to the air intake port than the second air intake section. Wherein, along the radial direction of the disk body, the width of the first suction section is greater than the width of the second suction section, and at least a portion of the cantilever end of the compressor's moving scroll forms a gap with the channel wall of the first suction section. Along the radial direction of the disk body, the static vortex includes a first sidewall and a second sidewall disposed opposite to each other, the first sidewall being the inner sidewall of the air intake channel and the second sidewall being the outer sidewall of the air intake channel; The first sidewall includes a first channel wall located in the first intake section and a second channel wall located in the second intake section, wherein the second channel wall is connected to the first channel wall through a first transition wall; The expansion angle β1 of the first channel wall and the expansion angle β2 of the second channel wall satisfy 10°≤β1-β2≤90°; Along the radial direction of the disk body, the width d1 of the first suction section and the width d2 of the second suction section satisfy 0.01mm≤d1-d2≤0.2mm; Along the radial direction of the disk body, the first channel wall is located outside the extension wall of the second channel wall and has a first distance between them; The first spacing H1 satisfies 0.01mm≤H1≤0.1mm.

2. The static scroll plate according to claim 1, characterized in that, The first sidewall is located radially outside the second sidewall, and the first sidewall and the second sidewall form the air intake channel; The first sidewall extends along a first helix; and / or the second sidewall extends along a second helix.

3. The static scroll plate according to claim 2, characterized in that, The second sidewall includes a third channel wall located in the first intake section and a fourth channel wall located in the second intake section. The third channel wall is connected to the fourth channel wall. Along the radial direction of the disc body, the first channel wall is located outside the third channel wall. Wherein, along the radial direction of the disk body, the third channel wall is located inside the extension wall of the fourth channel wall, and has a second distance between it and the extension wall of the fourth channel wall.

4. The static vortex disk according to claim 3, characterized in that, The second spacing H2 satisfies 0.01mm≤H2≤0.1mm.

5. The static scroll plate according to claim 3, characterized in that, The expansion angle α1 of the third channel wall and the expansion angle α2 of the fourth channel wall satisfy 10°≤α1-α2≤90°.

6. The static scroll plate according to claim 3, characterized in that, The second sidewall also includes a second transition wall, and the third channel wall and the fourth channel wall are connected through the second transition wall.

7. The stationary vortex disk according to claim 6, characterized in that, The first transition wall is configured as a first arcuate wall, which is tangent to the first channel wall and / or the second channel wall; and / or The second transition wall is configured as a second arcuate wall, which is tangent to the third channel wall and / or the fourth channel wall.

8. The static scroll disk according to any one of claims 2 to 7, characterized in that, The equation of the first helix is: x=-a×λ k ×cosλ-r1×cos(λ-arctan(k / λ)); y=a×λ k ×sinλ+r1×sin(λ-arctan(k / λ)); Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r1 is the eccentric radius.

9. The static scroll plate according to any one of claims 2 to 7, characterized in that, The equation of the second helix is: x=a×λ k ×cosλ-r2×cos(λ-arctan(k / λ)); y=-a×λ k ×sinλ+r2×sin(λ-arctan(k / λ)); Where a is a coefficient, λ is the expansion angle in radians, k is the polytropic index, and r2 is the eccentric radius.

10. A compressor, characterized in that, include: Static vortex disk as described in any one of claims 1 to 9; A moving scroll plate, comprising an end plate and moving scroll teeth, wherein the moving scroll teeth are disposed on the side of the end plate facing the stationary scroll plate and can be inserted into the air intake channel so that the moving scroll plate and the stationary scroll plate cooperate to form a compression chamber, the compression chamber being connected to the air intake port; The moving vortex includes a cantilever end that is away from the center of the end plate, and at least a portion of the cantilever end is located within the first intake section.

11. A refrigeration device, characterized in that, include: Static vortex disk as described in any one of claims 1 to 9; or The compressor as described in claim 10.

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