Compressor and refrigeration apparatus

Abstract

The utility model provides a kind of compressor and refrigeration equipment, compressor includes: shell, shell includes suction chamber and exhaust chamber;Compression component is located in suction chamber, and compression component includes static disc and moving disc, and moving disc and static disc form compression chamber, and compression chamber can be communicated with exhaust chamber, and static disc is equipped with suction port, and suction port is communicated with compression chamber;Suction pipe is located in shell, and suction pipe includes flow guide pipe section, and flow guide pipe section is located in suction chamber, and extends to the side where suction port is, and at least a portion of the pipe opening of flow guide pipe section is oppositely arranged with suction port, and is communicated with suction port, when compressor operates, refrigerant from flow guide pipe section can directly and as much as possible flow to suction port, effectively reduce the flow resistance loss caused by refrigerant due to needing to cross static disc convex part, significantly increase suction volume, improve suction efficiency, to further facilitate the energy efficiency of compressor is improved.

Description

Technical Field

[0001] This utility model relates to the field of compressor equipment technology, and more specifically, to a compressor and refrigeration equipment. Background Technology

[0002] Currently, in low back pressure scroll compressors, the suction pipe is generally located below the suction port of the stationary scroll. When the scroll compressor is running, the suction airflow needs to overcome the obstruction of the raised part of the stationary scroll before being sucked in by the suction port, which reduces the suction volume of the scroll compressor, results in greater flow path loss, and thus reduces the energy efficiency of the scroll compressor. Utility Model Content

[0003] The embodiments of this utility model are intended to solve at least one of the technical problems existing in the prior art.

[0004] Therefore, a first aspect of the embodiments of this utility model provides a compressor.

[0005] A second aspect of the present invention provides a refrigeration device.

[0006] In view of the above, according to a first aspect of the present invention, a compressor is provided, the compressor comprising: a housing, the housing including an intake chamber and an exhaust chamber; a compression assembly disposed within the intake chamber, the compression assembly including a stationary disc and a moving disc, the moving disc and the stationary disc forming a compression chamber, the compression chamber being able to communicate with the exhaust chamber, the stationary disc having an intake port, the intake port communicating with the compression chamber; and an intake pipe disposed within the housing, the intake pipe including a guide pipe section located within the intake chamber and extending toward the side where the intake port is located, at least a portion of the opening of the guide pipe section being disposed opposite to the intake port and communicating with the intake port.

[0007] The compressor provided in this embodiment includes a housing, a compression assembly, and a suction pipe. Specifically, the compression assembly includes a moving disc and a stationary disc, which together form a compression chamber. Specifically, when the compressor is running, the moving disc rotates relative to the stationary disc. Refrigerant is drawn in through the suction pipe and enters the compression chamber through the suction port on the stationary disc. During the rotation of the moving disc relative to the stationary disc, the refrigerant in the compression chamber is compressed. When the pressure of the compressed refrigerant reaches the discharge pressure, the compressed high-temperature, high-pressure refrigerant is discharged from the discharge port on the stationary disc into the discharge chamber, and then discharged outside the housing.

[0008] In related technologies, the suction pipe is generally located below the suction port. When the compressor is running, the refrigerant flowing out of the suction pipe needs to pass over the protruding part (end plate) of the stationary plate and then enter the compression chamber from the suction port of the stationary plate. During this process, a certain flow resistance loss will be generated, thereby reducing the suction volume of the compressor and thus reducing the energy efficiency of the compressor.

[0009] The suction pipe includes a guide pipe section, which is located within the suction chamber and extends towards the suction port. In other words, a portion of the suction pipe extends inwards towards the suction port as a guide path, shortening the distance between the suction pipe and the suction port. This allows the refrigerant flowing from the guide pipe section to be directly introduced into the suction port. Furthermore, since at least a portion of the guide pipe section's opening is positioned opposite the suction port, when the compressor is running, the refrigerant flowing from the guide pipe section can flow directly and as much as possible towards the suction port. This effectively reduces flow resistance losses caused by the refrigerant needing to overcome the raised portion of the stationary disc, significantly increasing the suction volume and improving suction efficiency, thereby enhancing the compressor's energy efficiency.

[0010] Furthermore, by extending the suction pipe inward and moving that part upward to face the suction port, the suction efficiency of the compressor is significantly improved with minimal changes to the original compressor structure. The structure is simple, and while improving the compressor's energy efficiency and ensuring its reliability, it also helps to reduce the compressor's production cost.

[0011] It should be noted that, since the compression assembly is located within the intake chamber, the compressor is a low back-pressure scroll compressor. Optionally, the compressor also includes a partition plate disposed within the housing, dividing the housing into an intake chamber and an exhaust chamber.

[0012] In some technical solutions, optionally, the stationary disc has a recess on the side away from the moving disc, and the compression assembly also includes a back pressure plate, which is located in the recess; wherein, the outer diameter of the recess is d1, the inner diameter of the shell is d2, the length of the guide tube section is L, and 2mm≤(d2-d1) / 2-L≤6mm.

[0013] In this technical solution, by limiting (d2-d1) / 2-L to between 2mm and 6mm, it is possible to avoid interference between the guide tube section and the stationary plate while bringing the inlet of the guide tube section closer to the suction port, thereby reducing flow path losses, increasing suction volume, improving suction efficiency, and thus helping to improve the energy efficiency of the compressor.

[0014] In some technical solutions, optionally, along the axial direction of the stationary disc, the height difference between the center line of the air intake in the radial direction of the stationary disc and the central axis of the guide pipe section is h, where h≤5mm.

[0015] In this technical solution, since the height difference between the center line of the suction port in the radial direction of the stationary plate and the central axis of the guide pipe section in the axial direction of the stationary plate is less than or equal to 5mm, the pipe opening of the guide pipe section is as close as possible to the suction port. This reduces the flow resistance loss caused by the refrigerant having to pass over the raised part of the stationary plate, while also increasing the suction volume and improving the energy efficiency of the compressor.

[0016] In some technical solutions, optionally, along the axial direction of the stationary disc, the central axis of the guide tube section is higher than the center line of the intake port in the radial direction of the stationary disc.

[0017] In this technical solution, since the central axis of the guide pipe section is higher than the center line of the suction port in the radial direction of the stationary plate along the axial direction of the stationary plate, that is, under the premise that at least a part of the pipe opening of the guide pipe section is set opposite to the suction port, the guide pipe section is set slightly higher. This can reduce flow path losses, increase suction volume, and thus improve suction efficiency, while avoiding interference between the guide pipe section and the protruding part (end plate) of the stationary plate. This helps to reduce wear on the guide pipe section and the stationary plate, and further improve the reliability of the compressor.

[0018] In some technical solutions, the stationary disc may optionally include a disc body and an end plate, wherein the end plate is located on the disc body and extends radially along the stationary disc, and the end plate, the disc body, and the moving disc enclose a compression chamber, and a portion of the air intake is located on the disc body and another portion is located on the end plate; wherein the guide pipe section has an avoidance notch on the side facing the end plate.

[0019] In this technical solution, since the guide pipe section has a clearance notch on the side facing the end plate, the refrigerant flowing out of the guide pipe section can be directly introduced into the suction port, thereby reducing flow resistance loss, increasing suction volume, and avoiding interference between the guide pipe section and the end plate. This helps to reduce wear on the guide pipe section and stationary plate, and improve the reliability of the compressor.

[0020] In some technical solutions, the gap can be optionally connected to the inlet of the diversion pipe section.

[0021] In this technical solution, since the clearance notch is connected to the pipe opening of the guide pipe section, when the compressor is running, the refrigerant flowing into the guide pipe section can flow out through the clearance notch in addition to flowing out through the pipe opening. This increases the amount of refrigerant flowing from the guide pipe section to the suction port, which increases the gas output of the guide pipe section. This is beneficial to further increase the suction volume of the suction port, improve the suction efficiency, and thus improve the energy efficiency of the compressor.

[0022] In some technical solutions, optionally, along the radial direction of the stationary disc, the distance between the end of the clearance notch near the intake port and the inner wall of the housing is greater than the distance between the end of the clearance notch away from the intake port and the inner wall of the housing.

[0023] In this technical solution, since the distance between the end of the clearance notch near the intake port and the inner wall of the housing in the radial direction of the stationary plate is greater than the distance between the end of the clearance notch away from the intake port and the inner wall of the housing in the radial direction of the stationary plate, that is, the clearance notch extends at an angle, thereby increasing the gas flow area of ​​the clearance notch while avoiding interference between the guide pipe section and the end plate. This is conducive to further increasing the intake volume, improving the intake efficiency, and thus improving the energy efficiency of the compressor.

[0024] In some technical solutions, optionally, along the axial direction of the stationary disc, the side of the guide tube section closest to the end plate is higher than the side of the end plate facing the moving disc.

[0025] In this technical solution, because the side of the guide pipe section near the end plate along the axial direction of the stationary plate is higher than the side of the end plate facing the moving plate, that is, the height of the bottom wall of the guide pipe section is higher than the height of the bottom surface of the end plate. Under the premise that at least a part of the pipe opening of the guide pipe section is set opposite to the suction port, the guide pipe section is set slightly higher, which can reduce flow path loss, increase suction volume, and thus improve suction efficiency, while avoiding interference between the guide pipe section and the end plate, thereby improving the reliability of the compressor.

[0026] In some technical solutions, optionally, at least a portion of the guide tube section extends radially along the stationary disc; and / or the guide tube section includes at least one bend.

[0027] In this technical solution, at least a portion of the guide pipe section extends radially along the stationary disc, meaning the shape of the guide pipe section is straight. Since at least a portion of the inlet of the guide pipe section is opposite to the suction port, extending the guide pipe section radially helps to reduce its length, thereby reducing the overall length of the suction pipe and consequently lowering the compressor's production cost.

[0028] The guide pipe section includes at least one bend, meaning the guide pipe section is curved. It is understandable that due to limitations imposed by various internal and external structural components of the compressor, there may be situations where the guide pipe section cannot extend directly radially to align with the suction port. Therefore, at least one bend can be provided in the guide pipe section so that at least a portion of the guide pipe section's opening aligns with the suction port. This reduces flow resistance losses, increases suction volume, and avoids other structural components, thereby meeting the design requirements of all compressor components.

[0029] In some technical solutions, optionally, along the radial direction of the stationary disc, the guide tube section includes a first end and a second end facing away from each other, with the first end being closer to the intake port than the second end; wherein, the inner diameter of the first end is equal to the inner diameter of the second end; or the inner diameter of the first end is greater than the inner diameter of the second end; or the inner diameter of the first end is smaller than the inner diameter of the second end.

[0030] In this technical solution, when the inner diameter of the first end is equal to the inner diameter of the second end, the guide pipe section is a straight pipe section. It can be understood that setting the guide pipe section as a straight pipe section is beneficial to reducing production costs.

[0031] When the inner diameter of the first end is larger than the inner diameter of the second end, at least a part of the guide tube section is trumpet-shaped, that is, the end of the guide tube section near the air inlet is flared, which is beneficial to increase the air intake volume and improve the air intake efficiency.

[0032] When the inner diameter of the first end is smaller than the inner diameter of the second end, at least a portion of the guide tube section is tapered, which allows the size of the guide tube section opening to be matched with the intake port, thus reducing intake loss and ensuring compressor efficiency.

[0033] In some technical solutions, the compressor may optionally include a cooling hole, which is located in the guide tube section. One end of the cooling hole is connected to the guide tube section, and the other end of the cooling hole penetrates the outer wall of the guide tube section.

[0034] In this technical solution, the compressor also includes cooling holes, which are located in the guide pipe section. One end of the cooling hole is connected to the guide pipe section, and the other end penetrates the outer wall of the guide pipe section. In other words, the low-temperature refrigerant drawn in from the guide pipe section can flow into the housing through the cooling holes, thereby cooling the heating elements (e.g., motor assembly) inside the housing, reducing the temperature rise of the heating elements, and thus improving the reliability of the compressor.

[0035] In some technical solutions, the compressor may optionally include a crankshaft and a motor assembly, wherein the crankshaft is located in the intake chamber and connected to the moving plate, the motor assembly is located in the intake chamber and connected to the crankshaft, and the cooling holes are configured to face the motor assembly.

[0036] In this technical solution, it is understood that the motor assembly generally generates heat during the operation of the compressor. By setting the cooling holes toward the motor assembly, the low-temperature refrigerant drawn in by the self-priming pipe can flow directly to the motor assembly through the cooling holes, thereby improving the cooling effect on the motor assembly and further enhancing the reliability of the compressor.

[0037] In some technical solutions, optionally, there are multiple cooling holes, which are arranged at intervals on the guide pipe section.

[0038] In this technical solution, there are multiple cooling holes, and these holes are spaced apart on the guide pipe section. Specifically, during compressor operation, the low-temperature refrigerant drawn into the suction pipe can flow into the casing through multiple cooling holes. This increases the amount of low-temperature refrigerant flowing from the suction pipe to the heating elements inside the compressor, thereby improving the cooling effect of the compressor's heating elements and further enhancing the compressor's reliability.

[0039] In some technical solutions, optionally, the diameter of the cooling hole is d3, and the minimum inner diameter of the intake pipe is d4, where 0.1 ≤ d3. 2 / d4 2 ≤0.3.

[0040] In this technical solution, by using d3 2 and d4 2The ratio is limited to between 0.1 and 0.3, which can effectively cool the heating elements inside the housing while ensuring the amount of refrigerant drawn in through the suction port, thereby ensuring the suction efficiency of the compressor.

[0041] In some technical solutions, the inhalation tube may optionally include an inhalation tube segment connected to the flow guide tube segment and located at least partially outside the housing; wherein the end of the flow guide tube segment away from the inhalation port is detachably connected to the inhalation tube segment; or the flow guide tube segment and the inhalation tube segment are an integral structure.

[0042] In this technical solution, the end of the guide pipe section furthest from the suction port is detachably connected to the suction pipe section; that is, the guide pipe section is externally connected to the suction pipe section. Alternatively, the guide pipe section and the suction pipe section can be an integral structure. The specific configuration can be determined according to actual needs. It is understood that when the guide pipe section and the suction pipe section are an integral structure, the sealing of the suction pipe can be ensured, preventing refrigerant leakage and thus helping to ensure the compressor's energy efficiency.

[0043] According to a second aspect of this utility model, a refrigeration device is provided, including a compressor as provided in any of the above technical solutions, and thus possesses all the beneficial technical effects of the compressor, which will not be repeated here.

[0044] Additional aspects and advantages of the present invention will be set forth in the description which follows, in part will be obvious from the description, or may be learned by practice of the present invention. Attached Figure Description

[0045] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0046] Figure 1 A partial structural schematic diagram of a compressor according to an embodiment of the present invention is shown;

[0047] Figure 2 It shows Figure 1 An enlarged view of the compressor at point A in the illustrated embodiment.

[0048] in, Figure 1 and Figure 2 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0049] 1 Compressor, 10 Housing, 12 Intake Chamber, 14 Exhaust Chamber, 20 Compression Assembly, 22 Stationary Disc, 222 Intake Port, 224 Recess, 226 Disc Body, 228 End Plate, 24 Moving Disc, 26 Back Pressure Plate, 28 Compression Chamber, 30 Intake Pipe, 32 Guide Pipe Section, 322 Pipe Port, 324 Clearance Notch, 34 Intake Pipe Section, 40 Cooling Hole, 50 Crankshaft, 60 Motor Assembly, 70 Centerline, 80 Center Axis. Detailed Implementation

[0050] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model 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.

[0051] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0052] The following reference Figure 1 and Figure 2 The present invention will be described in some embodiments of the compressor 1 and refrigeration equipment provided.

[0053] In one embodiment according to this application, such as Figure 1 and Figure 2 As shown, a compressor 1 is proposed. The compressor 1 includes: a housing 10, which includes an intake chamber 12 and an exhaust chamber 14; a compression assembly 20 disposed in the intake chamber 12, which includes a stationary disc 22 and a moving disc 24, which together form a compression chamber 28. The compression chamber 28 is connected to the exhaust chamber 14. The stationary disc 22 is provided with an intake port 222, which is connected to the compression chamber 28; and an intake pipe 30 disposed in the housing 10, which includes a guide pipe section 32 located in the intake chamber 12 and extending toward the side where the intake port 222 is located. At least a portion of the pipe opening 322 of the guide pipe section 32 is opposite to and connected to the intake port 222.

[0054] The compressor 1 provided in this embodiment includes a housing 10, a compression assembly 20, and a suction pipe 30. Specifically, the compression assembly 20 includes a moving disc 24 and a stationary disc 22, wherein the moving disc 24 and the stationary disc 22 form a compression chamber 28. Specifically, when the compressor 1 is running, the moving disc 24 rotates relative to the stationary disc 22. Refrigerant is drawn in from the suction pipe 30 and enters the compression chamber 28 through the suction port 222 on the stationary disc 22. During the rotation of the moving disc 24 relative to the stationary disc 22, the refrigerant in the compression chamber 28 is compressed. When the pressure of the compressed refrigerant reaches the discharge pressure, the compressed high-temperature and high-pressure refrigerant is discharged from the discharge port on the stationary disc 22 into the discharge chamber 14, and then discharged outside the housing 10.

[0055] In related technologies, the suction pipe is generally located below the suction port. When the compressor is running, the refrigerant flowing out of the suction pipe needs to pass over the protruding part (end plate) of the stationary plate and then enter the compression chamber from the suction port of the stationary plate. During this process, a certain flow resistance loss will be generated, thereby reducing the suction volume of the compressor and thus reducing the energy efficiency of the compressor.

[0056] The suction pipe 30 includes a guide pipe section 32, which is located within the suction chamber 12 and extends towards the side where the suction port 222 is located. In other words, the suction pipe 30 extends inward and towards the suction port 222 as a guide path to shorten the distance between the suction pipe 30 and the suction port 222, allowing the refrigerant flowing from the guide pipe section 32 to be directly introduced into the suction port 222. Furthermore, since at least a portion of the opening 322 of the guide pipe section 32 is positioned opposite the suction port 222, when the compressor 1 is running, the refrigerant flowing from the guide pipe section 32 can flow directly and as much as possible towards the suction port 222. This effectively reduces the flow resistance loss caused by the refrigerant needing to cross the protruding portion of the stationary disc 22, significantly increases the suction volume, improves suction efficiency, and thus helps improve the energy efficiency of the compressor 1.

[0057] Furthermore, by extending the suction pipe 30 inward and moving this part upward to face the suction port 222, the suction efficiency of the compressor 1 is significantly improved with minimal changes to the original compressor structure. The structure is simple, and while improving the energy efficiency and ensuring the reliability of the compressor 1, it also helps to reduce the production cost of the compressor 1.

[0058] It should be noted that, since the compression assembly 20 is located within the intake chamber 12, the compressor 1 is a low back pressure scroll compressor. Optionally, the compressor 1 also includes a partition plate disposed within the housing 10, dividing the housing 10 into the intake chamber 12 and the exhaust chamber 14.

[0059] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the stationary disc 22 has a recess 224 on the side opposite to the moving disc 24, and the compression assembly 20 also includes a back pressure plate 26, which is disposed in the recess 224; wherein, the outer diameter of the recess 224 is d1, the inner diameter of the housing 10 is d2, the length of the guide pipe section 32 is L, and 2mm≤(d2-d1) / 2-L≤6mm.

[0060] In this embodiment, the compression assembly 20 further includes a back pressure plate 26, which is disposed within the recess 224 of the stationary disc 22. Optionally, the compression assembly 20 also includes a float assembly, wherein the float assembly, the recess 224, and the back pressure plate 26 enclose a back pressure cavity, which communicates with the compression cavity 28. This allows a medium pressure to be introduced into the back pressure cavity during compressor 1 operation. Under the action of this medium pressure, a certain axial force can be applied to the side of the stationary disc 22 facing the moving disc 24, ensuring a seal between the moving disc 24 and the stationary disc 22, preventing leakage, and thus ensuring the efficiency of the compressor 1.

[0061] Since (d2-d1) / 2-L is between 2mm and 6mm, the radial distance between the inlet 322 of the guide tube section 32 and the suction port 222 on the stationary plate 22 is limited to between 2mm and 6mm. It is understandable that if (d2-d1) / 2-L is too small, i.e., less than 2mm, meaning the radial distance between the inlet 322 of the guide tube section 32 and the suction port 222 on the stationary plate 22 is too close, interference can easily occur if the stationary plate 22 generally has a certain amount of axial movement during compressor 1 operation, affecting the reliability of compressor 1. If (d2-d1) / 2-L is too large, i.e., greater than 6mm, meaning the radial distance between the inlet 322 of the guide tube section 32 and the suction port 222 on the stationary plate 22 is too large, flow path losses will increase, suction volume will decrease, and thus the energy efficiency of compressor 1 will be reduced.

[0062] By limiting (d2-d1) / 2-L to between 2mm and 6mm, it is possible to avoid interference between the guide tube section 32 and the stationary plate 22, while bringing the pipe opening 322 of the guide tube section 32 closer to the suction port 222, thereby reducing flow path loss, increasing suction volume, improving suction efficiency, and thus helping to improve the energy efficiency of the compressor 1.

[0063] Optionally, (d2-d1) / 2-L can be any one of 2mm, 3mm, 4mm, 5mm and 6mm.

[0064] like Figure 1 As shown, in some embodiments, optionally, along the axial direction of the stationary disc 22, the height difference between the centerline 70 of the air intake 222 in the radial direction of the stationary disc 22 and the central axis 80 of the guide tube section 32 is h, wherein h≤5mm.

[0065] In this embodiment, since the height difference between the centerline 70 of the suction port 222 in the radial direction of the stationary plate 22 and the central axis 80 of the guide pipe section 32 in the axial direction of the stationary plate 22 is less than or equal to 5mm, the pipe opening 322 of the guide pipe section 32 is as close as possible to the suction port 222. This reduces the flow resistance loss caused by the refrigerant needing to pass over the protruding part of the stationary plate 22, while also increasing the suction volume and improving the energy efficiency of the compressor 1.

[0066] Optionally, h can be any one of 0mm, 1mm, 2mm, 3mm, 4mm and 5mm.

[0067] like Figure 1 As shown, in some embodiments, optionally, along the axial direction of the stationary disc 22, the central axis 80 of the guide tube section 32 is higher than the center line 70 of the intake port 222 in the radial direction of the stationary disc 22.

[0068] In this embodiment, since the central axis 80 of the guide tube section 32 is higher than the center line 70 of the suction port 222 in the radial direction of the stationary plate 22 along the axial direction of the stationary plate 22, that is, under the premise that at least a part of the pipe opening 322 of the guide tube section 32 is arranged opposite to the suction port 222, the guide tube section 32 is arranged slightly higher, which can reduce flow path loss, increase suction volume, and thus improve suction efficiency, while avoiding interference between the guide tube section 32 and the protruding part (end plate 228) of the stationary plate 22. This is beneficial to reduce wear on the guide tube section 32 and the stationary plate 22, and further improve the reliability of the compressor 1.

[0069] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the stationary disc 22 includes a disc body 226 and an end plate 228, wherein the end plate 228 is disposed on the disc body 226 and extends radially along the stationary disc 22, and the end plate 228, the disc body 226 and the moving disc 24 surround to form a compression cavity 28, and a portion of the air intake 222 is disposed on the disc body 226 and another portion is disposed on the end plate 228; wherein, the guide pipe section 32 is provided with an avoidance notch 324 on the side facing the end plate 228.

[0070] In this embodiment, the stationary plate 22 includes a plate body 226 and an end plate 228, wherein the end plate 228 extends radially along the plate body 226, that is, the end of the end plate 228 in the radial direction of the stationary plate 22 is the protruding part of the stationary plate 22. By providing a guide pipe section 32, and the pipe opening 322 of the guide pipe section 32 is arranged opposite to the suction port 222, the refrigerant flowing out from the guide pipe section 32 is directly introduced into the suction port 222. Compared with setting the suction pipe 30 at the lower part of the stationary plate 22, the flow resistance loss caused by the refrigerant having to cross the end plate 228 can be effectively reduced, the suction volume can be significantly increased, the suction efficiency can be improved, and thus the energy efficiency of the compressor 1 can be improved.

[0071] Because the guide pipe section 32 has a clearance notch 324 on the side facing the end plate 228, the refrigerant flowing out of the guide pipe section 32 can be directly introduced into the suction port 222, thereby reducing flow resistance loss, increasing suction volume, and avoiding interference between the guide pipe section 32 and the end plate 228. This helps to reduce wear on the guide pipe section 32 and the stationary plate 22, and improve the reliability of the compressor 1.

[0072] In some embodiments, the clearance notch 324 may optionally be connected to the port 322 of the guide pipe section 32.

[0073] In this embodiment, since the clearance notch 324 is connected to the port 322 of the guide pipe section 32, when the compressor 1 is running, the refrigerant flowing into the guide pipe section 32 can flow out through the clearance notch 324 in addition to flowing out through the port 322. This increases the amount of refrigerant flowing from the guide pipe section 32 to the suction port 222, which increases the gas output of the guide pipe section 32. This is beneficial to further increase the suction volume of the suction port 222, improve the suction efficiency, and thus improve the energy efficiency of the compressor 1.

[0074] Optionally, at least a portion of the clearance notch 324 is positioned opposite to the air intake 222.

[0075] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, along the radial direction of the stationary disc 22, the distance between the end of the clearance notch 324 near the air intake 222 and the inner wall of the housing 10 is greater than the distance between the end of the clearance notch 324 away from the air intake 222 and the inner wall of the housing 10.

[0076] In this embodiment, since the distance between the end of the clearance notch 324 near the intake port 222 and the inner wall of the housing 10 in the radial direction of the stationary plate 22 is greater than the distance between the end of the clearance notch 324 away from the intake port 222 and the inner wall of the housing 10 in the radial direction of the stationary plate 22, that is, the clearance notch 324 extends at an angle, thereby increasing the gas flow area of ​​the clearance notch 324 while avoiding interference between the guide pipe section 32 and the end plate 228. This is beneficial to further increase the intake volume, improve the intake efficiency, and thus improve the energy efficiency of the compressor 1.

[0077] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, along the axial direction of the stationary disk 22, the side of the guide tube section 32 near the end plate 228 is higher than the side of the end plate 228 facing the moving disk 24.

[0078] In this embodiment, since the side of the guide pipe section 32 near the end plate 228 along the axial direction of the stationary plate 22 is higher than the side of the end plate 228 facing the moving plate 24, that is, the height of the bottom wall of the guide pipe section 32 is higher than the height of the bottom surface of the end plate 228. Under the premise that at least a part of the pipe opening 322 of the guide pipe section 32 is arranged opposite to the suction port 222, the guide pipe section 32 is arranged slightly higher, which can reduce flow path loss, increase suction volume, and thus improve suction efficiency, while avoiding interference between the guide pipe section 32 and the end plate 228, thereby improving the reliability of the compressor 1.

[0079] In some embodiments, optionally, at least a portion of the flow guide section 32 extends radially along the stationary disc 22; and / or the flow guide section 32 includes at least one bend.

[0080] In this embodiment, at least a portion of the guide pipe section 32 extends radially along the stationary disc 22, meaning the shape of the guide pipe section 32 is straight. Since at least a portion of the inlet 322 of the guide pipe section 32 is opposite to the suction port 222, extending the guide pipe section 32 radially helps to reduce the length of the guide pipe section 32, thereby reducing the overall length of the suction pipe 30, and consequently reducing the production cost of the compressor 1.

[0081] The guide pipe section 32 includes at least one bend, meaning that the shape of the guide pipe section 32 is curved. It is understandable that, due to limitations imposed by various internal and external structural components of the compressor 1, there may be situations where the guide pipe section 32 cannot extend directly radially to face the suction port 222. Therefore, the guide pipe section 32 can be provided with at least one bend so that at least a portion of the pipe opening 322 faces the suction port 222. This reduces flow resistance loss, increases suction volume, and avoids other structural components, thereby meeting the design requirements of various structural components of the compressor 1.

[0082] In some embodiments, optionally, along the radial direction of the stationary disc 22, the guide tube section 32 includes a first end and a second end facing away from each other, the first end being closer to the air intake 222 than the second end; wherein, the inner diameter of the first end is equal to the inner diameter of the second end; or the inner diameter of the first end is greater than the inner diameter of the second end; or the inner diameter of the first end is smaller than the inner diameter of the second end.

[0083] In this embodiment, the guide tube section 32 includes a first end and a second end that are radially opposite to each other along the stationary disc 22, and the first end is closer to the intake port 222 than the second end.

[0084] When the inner diameter of the first end is equal to the inner diameter of the second end, the guide pipe section 32 is a straight pipe section. It is understandable that setting the guide pipe section 32 as a straight pipe section is beneficial to reducing production costs.

[0085] When the inner diameter of the first end is larger than the inner diameter of the second end, at least a part of the guide tube section 32 is trumpet-shaped, that is, the end of the guide tube section 32 near the air intake port 222 is flared, which is beneficial to increase the air intake volume and improve the air intake efficiency.

[0086] When the inner diameter of the first end is smaller than the inner diameter of the second end, at least a portion of the guide pipe section 32 is tapered, so that the size of the pipe opening 322 of the guide pipe section 32 can be adapted to the intake port 222, which helps to reduce intake loss and ensure the efficiency of the compressor 1.

[0087] like Figure 2 As shown, in some embodiments, the compressor 1 may optionally include a cooling hole 40, which is disposed in the guide pipe section 32. One end of the cooling hole 40 is connected to the guide pipe section 32, and the other end of the cooling hole 40 penetrates the outer wall of the guide pipe section 32.

[0088] In this embodiment, the compressor 1 also includes a cooling hole 40, which is disposed in the guide pipe section 32. One end of the cooling hole 40 is connected to the guide pipe section 32, and the other end penetrates the outer wall of the guide pipe section 32. In other words, the low-temperature refrigerant drawn in from the guide pipe section 32 can flow into the housing 10 through the cooling hole 40, thereby cooling the heating element (e.g., the motor assembly 60) inside the housing 10, reducing the temperature rise of the heating element, and thus improving the reliability of the compressor 1.

[0089] like Figure 1 and Figure 2 As shown, in some embodiments, the compressor 1 may optionally include a crankshaft 50 and a motor assembly 60, wherein the crankshaft 50 is disposed in the intake chamber 12 and connected to the moving plate 24, the motor assembly 60 is disposed in the intake chamber 12 and connected to the crankshaft 50, and the cooling hole 40 is configured to face the motor assembly 60.

[0090] In this embodiment, the compressor 1 also includes a crankshaft 50 and a motor assembly 60, wherein the motor assembly 60 is connected to the crankshaft 50, and the crankshaft 50 is connected to the moving disk 24. Specifically, when the compressor 1 is running, driven by the motor assembly 60, the crankshaft 50 drives the moving disk 24 to rotate relative to the stationary disk 22. Refrigerant is drawn in from the suction pipe 30 and enters the compression chamber 28 through the suction port 222 on the stationary disk 22. During the rotation of the moving disk 24 relative to the stationary disk 22, the refrigerant in the compression chamber 28 can be compressed. When the pressure of the compressed refrigerant reaches the discharge pressure, the compressed high-temperature and high-pressure refrigerant is discharged from the discharge port on the stationary disk 22.

[0091] Understandably, during the operation of compressor 1, motor assembly 60 will generally generate heat. By setting the cooling hole 40 toward motor assembly 60, the low-temperature refrigerant drawn into the self-priming pipe 30 can flow directly to motor assembly 60 through the cooling hole 40, thereby improving the cooling effect on motor assembly 60 and further enhancing the reliability of compressor 1.

[0092] Optionally, the motor assembly 60 is generally located at the bottom of the intake pipe 30, therefore, the cooling hole 40 is located at the bottom of the guide pipe section 32.

[0093] In some embodiments, the number of cooling holes 40 may be multiple, and the multiple cooling holes 40 are arranged at intervals on the guide tube section 32.

[0094] In this embodiment, there are multiple cooling holes 40, and these multiple cooling holes 40 are spaced apart on the guide pipe section 32. Specifically, when the compressor 1 is running, the low-temperature refrigerant drawn into the suction pipe 30 can flow into the housing 10 through the multiple cooling holes 40, which increases the amount of low-temperature refrigerant flowing from the suction pipe 30 to the heating element inside the compressor 1, thereby improving the cooling effect of the heating element of the compressor 1 and further improving the reliability of the compressor 1.

[0095] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the diameter of the cooling hole 40 is d3, and the minimum inner diameter of the suction pipe 30 is d4, wherein 0.1 ≤ d3 2 / d4 2 ≤0.3.

[0096] In this embodiment, it can be understood that if d3 2 and d4 2 If the ratio is too small, i.e., less than 0.1, it means that too little low-temperature refrigerant flows into the housing 10 through the cooling hole 40, which cannot effectively cool the heating elements of the housing 10, increasing the probability of compressor 1 malfunction. If d3 2 and d4 2 If the ratio is too large, i.e. greater than 0.3, it means that too much low-temperature refrigerant flows into the housing 10 through the cooling hole 40. Consequently, the amount of refrigerant drawn into the self-suction port 222 will be reduced, resulting in an insignificant improvement in suction efficiency and affecting the energy efficiency of the compressor 1.

[0097] By d3 2 and d4 2 The ratio is limited to between 0.1 and 0.3, which can effectively cool the heating element inside the housing 10 while ensuring the amount of refrigerant drawn into the self-suction port 222, thereby ensuring the suction efficiency of the compressor 1.

[0098] Optionally, d3 2 / d4 2 It can be any one of 0.1, 0.2, and 0.3.

[0099] like Figure 1 As shown, in some embodiments, the inhalation tube 30 may optionally include an inhalation tube segment 34, which is connected to the flow guide tube segment 32 and is at least partially located on the outside of the housing 10; wherein, the end of the flow guide tube segment 32 away from the inhalation port 222 is detachably connected to the inhalation tube segment 34; or the flow guide tube segment 32 and the inhalation tube segment 34 are an integral structure.

[0100] In this embodiment, the suction pipe 30 further includes a suction pipe section 34, which is connected to the guide pipe section 32, and at least a portion of the suction pipe section 34 is located outside the housing 10 for connecting the refrigerant. Specifically, when the compressor 1 is running, the refrigerant flows into the suction pipe 30 and enters the compression chamber 28 through the suction port 222 on the stationary plate 22. During the translational rotation of the moving plate 24 relative to the stationary plate 22, the refrigerant in the compression chamber 28 can be compressed. Since at least a portion of the port 322 of the guide pipe section 32 is positioned opposite to the suction port 222, when the compressor 1 is running, the refrigerant flowing out of the guide pipe section 32 can flow directly and as much as possible to the suction port 222, effectively reducing the flow resistance loss caused by the refrigerant needing to cross the protruding part of the stationary plate 22, significantly increasing the suction volume, improving the suction efficiency, and thus helping to improve the energy efficiency of the compressor 1.

[0101] The end of the guide tube section 32 furthest from the intake port 222 is detachably connected to the intake tube section 34, meaning that the guide tube section 32 is externally connected to the intake tube section 34. Alternatively, the guide tube section 32 and the intake tube section 34 can be integrated into one structure. The specific configuration can be determined according to actual needs.

[0102] It is understandable that when the guide pipe section 32 and the suction pipe section 34 are integrated into one structure, the sealing of the suction pipe 30 can be ensured, refrigerant leakage can be avoided, and the energy efficiency of the compressor 1 can be ensured.

[0103] According to a second aspect of the present invention, a refrigeration device is provided, including a compressor 1 as provided in any of the above embodiments, and thus possesses all the beneficial technical effects of the compressor 1, which will not be repeated here.

[0104] Optionally, compressor 1 is a scroll compressor. Specifically, the scroll compressor includes a housing 10, a compression assembly 20, and a suction pipe 30. Specifically, the compression assembly 20 includes a moving disc 24 and a stationary disc 22, which together form a compression chamber 28. Specifically, when the scroll compressor is running, the moving disc 24 rotates relative to the stationary disc 22. Refrigerant is drawn in through the suction pipe 30 and enters the compression chamber 28 through the suction port 222 on the stationary disc 22. During the rotation of the moving disc 24 relative to the stationary disc 22, the refrigerant in the compression chamber 28 is compressed. When the pressure of the compressed refrigerant reaches the discharge pressure, the compressed high-temperature, high-pressure refrigerant is discharged from the discharge port on the stationary disc 22 into the discharge chamber 14, and then discharged outside the housing 10.

[0105] In related technologies, the suction pipe is generally located below the suction port. When the compressor is running, the refrigerant flowing out of the suction pipe needs to pass over the protruding part (end plate) of the stationary plate and then enter the compression chamber from the suction port of the stationary plate. During this process, a certain flow resistance loss will be generated, thereby reducing the suction volume of the compressor and thus reducing the energy efficiency of the compressor.

[0106] The suction pipe 30 includes a guide pipe section 32, which is located within the suction chamber 12 and extends towards the side where the suction port 222 is located. In other words, the suction pipe 30 extends inward and towards the suction port 222 as a guide path to shorten the distance between the suction pipe 30 and the suction port 222, allowing the refrigerant flowing from the guide pipe section 32 to be directly introduced into the suction port 222. Furthermore, since at least a portion of the opening 322 of the guide pipe section 32 is positioned opposite the suction port 222, when the scroll compressor is running, the refrigerant flowing from the guide pipe section 32 can flow directly and as much as possible towards the suction port 222. This effectively reduces the flow resistance loss caused by the refrigerant needing to cross the protruding portion of the stationary disc 22, significantly increases the suction volume, improves suction efficiency, and thus helps improve the energy efficiency of the scroll compressor.

[0107] Furthermore, by extending the suction pipe 30 inward and moving it upward to face the suction port 222, the suction efficiency of the scroll compressor is significantly improved with minimal changes to the original scroll compressor structure. The structure is simple, and while improving the energy efficiency and ensuring the reliability of the scroll compressor, it also helps to reduce the production cost of the scroll compressor.

[0108] It should be noted that, since the compression assembly 20 is located within the intake chamber 12, the compressor 1 is a low back pressure scroll compressor. Optionally, the compressor 1 also includes a partition plate disposed within the housing 10, dividing the housing 10 into the intake chamber 12 and the exhaust chamber 14.

[0109] Alternatively, the refrigeration equipment may include air conditioners, refrigerators, or freezers.

[0110] 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 utility model according to the specific circumstances.

[0111] 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.

[0112] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor, characterized in that, include: A housing, the housing comprising an intake chamber and an exhaust chamber; A compression assembly is disposed within the intake chamber. The compression assembly includes a stationary disc and a moving disc, which together form a compression chamber. The compression chamber is connected to the exhaust chamber. The stationary disc is provided with an intake port, which is connected to the compression chamber. An air intake tube is disposed in the housing. The air intake tube includes a guide tube section located inside the air intake chamber and extending toward the side where the air intake port is located. At least a portion of the opening of the guide tube section is disposed opposite to the air intake port and communicates with the air intake port.

2. The compressor according to claim 1, characterized in that, The stationary disc has a recess on the side opposite to the moving disc, and the compression assembly also includes a back pressure plate, which is disposed in the recess. Wherein, the outer diameter of the recess is d1, the inner diameter of the shell is d2, and the length of the guide tube section is L, 2mm≤(d2-d1) / 2-L≤6mm.

3. The compressor according to claim 1, characterized in that, Along the axial direction of the stationary disc, the height difference between the center line of the air intake in the radial direction of the stationary disc and the central axis of the guide pipe section is h, where h ≤ 5 mm.

4. The compressor according to claim 1, characterized in that, Along the axial direction of the stationary disc, the central axis of the guide tube section is higher than the center line of the air intake in the radial direction of the stationary disc.

5. The compressor according to any one of claims 1 to 4, characterized in that, The static disk includes: Disk body; An end plate is disposed on the disk body and extends radially along the stationary disk. The end plate, the disk body, and the moving disk enclose the compression cavity. A portion of the air intake is disposed on the disk body, and another portion is disposed on the end plate. The guide pipe section has a clearance notch on the side facing the end plate.

6. The compressor according to claim 5, characterized in that, The clearance gap is connected to the opening of the guide pipe section.

7. The compressor according to claim 5, characterized in that, Along the radial direction of the stationary disc, the distance between the end of the clearance notch near the air intake and the inner wall of the housing is greater than the distance between the end of the clearance notch away from the air intake and the inner wall of the housing.

8. The compressor according to claim 5, characterized in that, Along the axial direction of the stationary disk, the side of the guide tube section closest to the end plate is higher than the side of the end plate facing the moving disk.

9. The compressor according to any one of claims 1 to 4, characterized in that, At least a portion of the flow guide section extends radially along the stationary disc; and / or the flow guide section includes at least one bend.

10. The compressor according to any one of claims 1 to 4, characterized in that, Along the radial direction of the stationary disc, the guide tube section includes a first end and a second end facing away from each other, with the first end being closer to the intake port than the second end. Wherein, the inner diameter of the first end is equal to the inner diameter of the second end; or the inner diameter of the first end is greater than the inner diameter of the second end; or the inner diameter of the first end is less than the inner diameter of the second end.

11. The compressor according to any one of claims 1 to 4, characterized in that, Also includes: A cooling hole is provided in the flow guide pipe section, one end of the cooling hole is connected to the flow guide pipe section, and the other end of the cooling hole penetrates the outer wall of the flow guide pipe section.

12. The compressor according to claim 11, characterized in that, Also includes: The crankshaft is located inside the intake chamber and is connected to the moving disc; A motor assembly is disposed within the intake chamber and connected to the crankshaft, and the cooling holes are configured to face the motor assembly.

13. The compressor according to claim 11, characterized in that, The cooling holes are multiple, and the multiple cooling holes are arranged at intervals on the guide pipe section.

14. The compressor according to claim 11, characterized in that, The diameter of the cooling hole is d3, and the minimum inner diameter of the intake pipe is d4, where 0.1 ≤ d3. 2 / d4 2 ≤0.

3.

15. The compressor according to any one of claims 1 to 4, characterized in that, The suction tube also includes: An intake tube section is connected to the flow guide tube section and is at least partially located on the outside of the housing; Wherein, the end of the guide tube segment away from the air inlet is detachably connected to the air inlet segment; or the guide tube segment and the air inlet segment are an integral structure.

16. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 15.

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