Pump body assembly for a compressor and compressor having the same

Abstract

The application discloses a pump body assembly for a compressor and a compressor with the same. The pump body assembly comprises a sound attenuation passage, which comprises a first passage section formed on a first bearing, a second passage section formed on a cylinder assembly and a third passage section formed on a second bearing. The first passage section is in communication with a sound attenuation cavity. The second passage section is in communication between the first passage section and the third passage section. The sound attenuation passage is multiple and spaced along the circumference of the pump body assembly. The second bearing is provided with a communication passage for communicating every two adjacent third passage sections along the circumference. According to the pump body assembly, the structure is simple, small and low in cost. The sound attenuation effect can be improved, and the problem of oil deposition in the sound attenuation passage and the communication passage can be effectively solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a pump body assembly for a compressor and a compressor having the same. Background Art

[0002] Some compressors in the related art use mufflers as the primary means of exhaust silencing. However, due to increasing requirements for low-noise standards for compressors and restrictions on compressor size, the ability to increase the muffler cavity in both the axial and radial directions is limited. To address this issue, the related art typically uses a double-layer muffler. However, the double-layer muffler structure increases flow resistance, reducing compressor performance. A balance needs to be struck between noise and energy efficiency. Furthermore, the double-layer muffler increases material costs, assembly steps, and difficulty. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a pump assembly for a compressor, which can improve the noise reduction effect and reduce the flow resistance.

[0004] The present invention also provides a compressor having the pump body assembly.

[0005] According to an embodiment of a first aspect of the present invention, a pump body assembly for a compressor includes: a cylinder assembly having a compression chamber; a bearing assembly including a first bearing and a second bearing disposed on axial sides of the cylinder assembly, the first bearing having an exhaust hole communicating with the compression chamber; a muffler assembly including a muffler disposed on a side of the first bearing away from the cylinder assembly, a muffler chamber communicating with the exhaust hole formed between the muffler and the first bearing, and an outlet hole communicating with the muffler chamber; and a muffler channel including a first channel section formed on the first bearing, a second channel section formed on the cylinder assembly, and a third channel section formed on the second bearing, the first channel section communicating with the muffler chamber, and the second channel section communicating between the first channel section and the third channel section, wherein the muffler channels are multiple and spaced apart along the circumferential direction of the pump body assembly, and the second bearing has a connecting channel for connecting every two adjacent third channel sections along the circumferential direction.

[0006] The pump body assembly for a compressor according to an embodiment of the present invention has a simple and compact structure, low cost, low assembly difficulty, and fewer assembly steps. It can reduce flow resistance and improve the silencer effect, and can more effectively improve the problem of oil deposition in the airflow in the silencer channel and the connecting channel.

[0007] In some embodiments, the multiple silencer channels include at least one air inlet channel and at least one air outlet channel, and the air outlet channel is arranged circumferentially away from the exhaust hole relative to the air inlet channel, and is projected onto the cross section of the pump body assembly. The air inlet channel is located in a first area, and the first area is a minor arc fan-shaped area located between the first radial line and the second radial line. The line connecting the center of the exhaust hole and the center of the pump body assembly is a baseline of 0°, the first radial line is at an angle of -30° to the baseline, and the second radial line is at an angle of 90° to the baseline.

[0008] In some embodiments, when a positive projection is made onto the cross section of the pump body assembly, the air outlet channel is located in the second area, and the second area is a major arc fan-shaped area located between the third radial line and the fourth radial line. The third radial line is at an angle of 100° to the baseline, and the fourth radial line is at an angle of -60° to the baseline.

[0009] In some embodiments, the angle β1 between the air inlet channel and the air outlet channel that are closest to each other in the circumferential direction is 30° to 90°.

[0010] In some embodiments, there are at least two air outlet channels, and the angle β2 between any two adjacent air outlet channels in the circumferential direction is smaller than the angle β1.

[0011] In some embodiments, the number of the outlet channels is greater than the number of the inlet channels, and / or the total volume of all the outlet channels is greater than the total volume of all the inlet channels.

[0012] In some embodiments, the volume of each of the air inlet channels is smaller than the volume of any of the air outlet channels.

[0013] In some embodiments, there are at least two air outlet channels, and the air outlet channels that are farther away from the exhaust hole in the circumferential direction have larger volumes.

[0014] In some embodiments, a cross-sectional area of ​​a first channel section of at least one of the muffler channels is smaller than a cross-sectional area of ​​a corresponding second channel section.

[0015] In some embodiments, the cross-sectional area of ​​the third channel section of at least one of the muffler channels is smaller than the cross-sectional area of ​​the corresponding second channel section.

[0016] In some embodiments, at least one of the connecting channel and the third channel section is constructed as a blind groove formed on the surface of the second bearing facing the cylinder assembly, and the side of the blind groove facing the cylinder assembly is a groove top and is open.

[0017] In some embodiments, the connecting channel and the third channel section are both blind grooves, and the bottom wall of the third channel section is smoothly transitioned to the bottom wall of the connecting channel.

[0018] In some embodiments, the width of the connecting channel is smaller than the equivalent diameter of the third channel segment.

[0019] In some embodiments, the blind groove has a depth of 0.5 mm to 5 mm.

[0020] In some embodiments, the cylinder assembly includes one cylinder, or includes multiple cylinders and a partition disposed between every two adjacent cylinders.

[0021] The compressor according to the second embodiment of the present invention comprises a drive assembly and a pump body assembly for the compressor according to the first embodiment of the present invention, wherein the pump body assembly is connected to the drive assembly via a crankshaft.

[0022] According to the compressor of the embodiment of the present invention, the exhaust noise of the compressor is improved by providing the pump body assembly of the embodiment of the first aspect.

[0023] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 is a cross-sectional view of a pump assembly according to one embodiment of the present invention;

[0025] Figure 2 yes Figure 1 A perspective view of the first bearing shown in ;

[0026] Figure 3 yes Figure 1 A perspective view of the cylinder shown in ;

[0027] Figure 4 yes Figure 1 A perspective view of the second bearing shown in ;

[0028] Figure 5 yes Figure 1 The cross-sectional view of the pump assembly shown in FIG, wherein some holes and other structures are omitted;

[0029] Figure 6 is a cross-sectional view of a compressor according to one embodiment of the present invention.

[0030] Reference numerals:

[0031] Compressor 1000;

[0032] Pump body assembly 100;

[0033] Cylinder assembly 1; cylinder 10; compression chamber 11; second channel section 12; second connecting hole 13;

[0034] First bearing 2; exhaust hole 21; first channel section 22; first connecting hole 23; mounting hole 24;

[0035] Second bearing 3; third channel section 31; connecting channel 32; third connecting hole 33;

[0036] Muffler 4; muffler chamber 41; crankshaft 5; slide vane 6; piston 7; compression spring 8;

[0037] Silence channel R; air inlet channel R1; air outlet channel R2;

[0038] Baseline L0; first radial line L1; second radial line L2; third radial line L3; fourth radial line L4;

[0039] First zone Z1; second zone Z2;

[0040] Drive assembly 200; rotor 201; stator 202;

[0041] Upper shell 301; main shell 302; lower shell 303. DETAILED DESCRIPTION

[0042] The following describes embodiments of the present invention in detail, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and are not to be construed as limiting the present invention.

[0043] The disclosure below provides many different embodiments or examples for realizing different structures of the present invention. In order to simplify the disclosure of the present invention, the components and settings of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. In addition, the present invention may repeat reference numbers and / or letters in different examples. This repetition is for the purpose of simplicity and clarity and does not in itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present invention provides examples of various specific processes and materials, but those skilled in the art will appreciate the applicability of other processes and / or the use of other materials.

[0044] Hereinafter, a pump body assembly 100 for a compressor 1000 according to an embodiment of the first aspect of the present invention will be described with reference to the accompanying drawings.

[0045] like Figure 1As shown, the pump body assembly 100 may include: a cylinder assembly 1, a bearing assembly and a muffler assembly, the cylinder assembly 1 having a compression chamber 11, the bearing assembly including a first bearing 2 and a second bearing 3 arranged on both axial sides of the cylinder assembly 1, the first bearing 2 having an exhaust hole 21 connected to the compression chamber 11, the muffler assembly including a muffler 4 arranged on a side of the first bearing 2 away from the cylinder assembly 1, a muffler chamber 41 connected to the exhaust hole 21 is formed between the muffler 4 and the first bearing 2, and the muffler 4 has an air outlet connected to the muffler chamber 41.

[0046] That is to say, the bearing assembly includes a first bearing 2 and a second bearing 3, and the first bearing 2 and the second bearing 3 are respectively arranged on both sides of the axial direction of the cylinder assembly 1. For example, when the compressor 1000 is a vertical compressor, the axial direction of the cylinder assembly 1 can be the up and down direction, and one of the first bearing 2 and the second bearing 3 is located on the upper side of the cylinder assembly 1, and the other is located on the lower side of the cylinder assembly 1. For another example, when the compressor 1000 is a horizontal compressor, the axial direction of the cylinder assembly 1 can be the left and right direction, and one of the first bearing 2 and the second bearing 3 is located on the left side of the cylinder assembly 1, and the other is located on the right side of the cylinder assembly 1.

[0047] Furthermore, the silencer assembly includes a silencer 4, which is arranged on a side of the first bearing 2 away from the cylinder assembly 1. For example, when the first bearing 2 is arranged on the upper side of the cylinder assembly 1, the silencer 4 is arranged on the upper side of the first bearing 2. For another example, when the first bearing 2 is arranged on the lower side of the cylinder assembly 1, the silencer 4 is arranged on the lower side of the first bearing 2. For another example, when the first bearing 2 is arranged on the left side of the cylinder assembly 1, the silencer 4 is arranged on the left side of the first bearing 2. For another example, when the first bearing 2 is arranged on the right side of the cylinder assembly 1, the silencer 4 is arranged on the right side of the first bearing 2.

[0048] Furthermore, the cylinder assembly 1 has a compression chamber 11, a silencer chamber 41 is formed between the muffler 4 and the first bearing 2, the first bearing 2 has an exhaust hole 21, and the muffler 4 has an outlet hole. The exhaust hole 21 is in communication with the compression chamber 11, the silencer chamber 41 is in communication with the exhaust hole 21, and the outlet hole is in communication with the silencer chamber 41. Thus, the high-pressure refrigerant compressed in the compression chamber 11 can be discharged into the silencer chamber 41 through the exhaust hole 21, and the high-pressure refrigerant entering the silencer chamber 41 can be discharged out of the silencer chamber 41 through the outlet hole.

[0049] like Figure 1-Figure 4As shown, the pump body assembly 100 according to an embodiment of the present invention further includes a silencer channel R, which includes a first channel section 22 formed on the first bearing 2, a second channel section 12 formed on the cylinder assembly 1, and a third channel section 31 formed on the second bearing 3. The first channel section 22 is in communication with the silencer chamber 41, and the second channel section 12 is in communication between the first channel section 22 and the third channel section 31. In other words, the pump body assembly 100 has a plurality of silencer channels R, each of which includes a first channel section 22, a second channel section 12, and a third channel section 31. An end of the first channel section 22 facing the silencer 4 is in communication with the silencer chamber 41, an end of the first channel section 22 facing the cylinder assembly 1 is in communication with an end of the second channel section 12 facing the first bearing 2, and an end of the second channel section 12 facing the second bearing 3 is in communication with the third channel section 31.

[0050] There are multiple silencer channels R spaced apart along the circumference of the pump assembly 100. The second bearing 3 has a communication channel 32, which is used to connect two adjacent third channel segments 31 along the circumferential direction. However, it is worth noting that the radial distances between the communication channels 32 and the center of the pump assembly 100 are not required to be equal, that is, they can be equal or unequal. In other words, the multiple communication channels 32 can be located on the same circular trajectory coaxial with the pump assembly 100, or at least two communication channels can be located on different circular trajectory coaxial with the pump assembly 100.

[0051] Therefore, when the pressure at the first channel section 22 is greater than the pressure at the third channel section 31, the airflow can pass through the silencer channel R along the first channel section 22, to the second channel section 12, and to the third channel section 31, and when the pressure at the third channel section 31 is greater than the pressure at the first channel section 22, the airflow can pass through the silencer channel R along the third channel section 31, to the second channel section 12, and to the first channel section 22.

[0052] Furthermore, since there are multiple silencer passages R, multiple first channel sections 22 are formed on the first bearing 2, multiple second channel sections 12 are formed on the cylinder assembly 1, and multiple third channel sections 31 are formed on the second bearing 3. The multiple third channel sections 31 on the second bearing 3 are connected through the communication passage 32 on the second bearing 3. Since the multiple silencer passages R are spaced apart along the circumference of the pump body assembly 100, the multiple third channel sections 31 are also spaced apart along the circumference of the pump body assembly 100. Therefore, in the circumferential direction of the pump body assembly 100, every two adjacent third channel sections 31 are connected through the communication passage 32.

[0053] Specifically, since multiple silencer channels R are spaced apart along the circumference of the pump body assembly 100, the circumferential distance between each silencer channel R and the exhaust hole 21 is different. In the circumference of the pump body assembly 100, the pressure at the first channel section 22 of the silencer channel R that is closer to the exhaust hole 21 is greater, and the pressure at the first channel section 22 of the silencer channel R that is farther away from the exhaust hole 21 is smaller. Therefore, the silencer channel R with a relatively higher pressure at the first channel section 22 can be defined as a high-pressure channel, and the silencer channel R with a relatively lower pressure at the first channel section 22 can be defined as a low-pressure channel.

[0054] When the pump body assembly 100 is working, after the high-pressure refrigerant airflow in the compression chamber 11 is discharged from the exhaust hole 21 to the silencer chamber 41, due to the different circumferential distances between each silencer channel R and the exhaust hole 21, part of the airflow enters the high-pressure channel relatively close to the exhaust hole 21, and flows through the first channel section 22 and the second channel section 12 of the high-pressure channel in sequence, and reaches the third channel section 31 on the second bearing 3. Then, this part of the airflow will enter the third channel section 31 corresponding to the low-pressure channel through the connecting channel 32 on the second bearing 3, and then flow through the second channel section 12 and the first channel section 22 of the low-pressure channel in sequence, and return to the silencer chamber 41.

[0055] As this portion of airflow passes through multiple silencer channels R, the noise in the airflow (i.e., exhaust noise) is consumed and reduced by the silencer channels R, thereby achieving the effect of exhaust noise reduction. In other words, the energy of the noise is weakened as the airflow passes through multiple silencer channels R, thereby achieving the effect of silencer.

[0056] Moreover, since the air flow enters from the high-pressure channel and returns from the low-pressure channel, the lubricating oil accumulated in the silencer channel R and the connecting channel 32 can be taken away with the return of the air flow and discharged to the outside of the silencer chamber 41 through the air outlet on the silencer 4, thereby effectively avoiding the problem of lubricating oil accumulating in the silencer channel R and the connecting channel 32, and avoiding the lubricating oil occupying a certain volume of the silencer channel R and the connecting channel 32, resulting in increased air flow resistance and weakened silencer effect, thereby ensuring the silencer effect.

[0057] Furthermore, according to the pump body assembly 100 of the embodiment of the present invention, since the high-pressure channel and the low-pressure channel are connected through the connecting channel 32 on the second bearing 3, the need for an additional muffler cover on the side of the second bearing 3 away from the cylinder assembly 1 is eliminated, thereby simplifying the structure, reducing costs, and improving the compactness of the pump body. Furthermore, since the high-pressure channel and the low-pressure channel are connected not through the muffler cover, but through the relatively small connecting channel 32 on the second bearing 3, the airflow can more effectively ensure that the lubricating oil is carried back to the muffler chamber 41, effectively avoiding problems such as the accumulation of lubricating oil in the muffler passage R. Conversely, if a muffler cover is used to connect the high-pressure channel and the low-pressure channel, due to the larger space within the muffler cover, the airflow from the high-pressure channel into the larger space within the muffler cover is prone to gas-liquid separation. The lubricating oil separated from the gas easily accumulates at the bottom of the muffler cover and is difficult to return to the muffler chamber 41 through the low-pressure channel with the airflow. As a result, there is a certain amount of lubricating oil loss, and the lubricating oil also occupies space within the muffler cover, affecting the muffler effect.

[0058] In addition, the pump body assembly 100 according to the embodiment of the present invention has a plurality of circumferentially spaced silencer channels R, so that the airflow can flow along certain silencer channels R to the second bearing 3 and then promptly return along the remaining silencer channels R, thereby reducing the possibility of gas-liquid separation and allowing the gas to carry the lubricating oil and return promptly, thereby improving the problem of lubricating oil and gas being separated and accumulated in the silencer channels R. If there is only one silencer channel R, the airflow needs to switch between the two states of entry and return according to the pressure change at one end of the silencer channel R that is connected to the silencer chamber 41 (i.e., the pressure change in the silencer chamber 41). Since these two states are intermittent rather than continuous as the cylinder assembly 1 alternates between compression and suction, the problem of gas-liquid separation is easily generated, resulting in the accumulation of lubricating oil in the silencer channel R and only the return of gas.

[0059] Therefore, the pump body assembly 100 according to the embodiment of the present invention has a simple, compact structure and low cost, can improve the noise reduction effect, and can relatively effectively alleviate the problem of oil in the airflow being deposited in the noise reduction channel R and the connecting channel 32. In addition, compared with the technical solution using a double-layer muffler in the related art, the flow resistance is reduced, which is less likely to adversely affect the performance of the compressor 1000. Moreover, since the double-layer muffler is omitted, material costs are also saved, the assembly process is simplified, and the assembly difficulty is reduced.

[0060] In some embodiments of the present invention, Figure 1 and Figure 5As shown, the multiple silencer channels R include at least one inlet channel R1 and at least one outlet channel R2. The outlet channel R2 is arranged circumferentially away from the exhaust hole 21 relative to the inlet channel R1, that is, the absolute value of the angle a2 between any outlet channel R2 and the exhaust hole 21 is greater than the absolute value of the angle a1 between any inlet channel R1 and the exhaust hole 21. Figure 5 The air inlet passage R1 is located in the first area Z1, and the first area Z1 is a minor arc fan-shaped area between the first radial line L1 and the second radial line L2, so that the first area Z1 is an area covering the exhaust hole 21, that is, the exhaust hole 21 is located in the first area Z1, and the line connecting the center of the exhaust hole 21 and the center of the pump body assembly 100 is a reference line L0 of 0°, the first radial line L1 forms an angle of -30° with the reference line L0, and the second radial line L2 forms an angle of 90° with the reference line L0.

[0061] It is worth noting that, combined with Figure 2 and Figure 5 , while the exhaust hole 21 is formed on the first bearing 2, a valve plate can also be provided corresponding to the exhaust hole 21, wherein one end of the valve plate is fixed to the first bearing 2 through the mounting hole 24 on the first bearing 2, and the other end of the valve plate is free and blocks the exhaust hole 21, wherein the side of the reference line L0 where the mounting hole 24 is located is the negative side, that is, the reference line L0 is facing the negative direction (for example Figure 5 By rotating the pump body assembly 100 by an angle less than 180° (in the clockwise direction shown in FIG), the connection line between the center of the mounting hole 24 and the center of the pump body assembly 100 can be reached.

[0062] Therefore, by limiting the air intake channel R1 to be located in the first area Z1, and in the circumferential direction of the pump body assembly 100, the air outlet channel R2 is arranged relative to the air intake channel R1 away from the exhaust hole 21, so that the air intake channel R1 can be used as a high-pressure channel, so that the air flow in the silencer chamber 41 flows to the connecting channel 32 of the second bearing 3 through the air intake channel R1, and the air outlet channel R2 can be used as a low-pressure channel, so that the air flow in the connecting channel 32 of the second bearing 3 returns to the silencer chamber 41 through the air outlet channel R2, thereby effectively achieving the effect of silencing and preventing oil accumulation.

[0063] In some embodiments of the present invention, Figure 2 and Figure 5 As shown, the cross-section of the pump body assembly 100 is projected forward, and the air outlet channel R2 is located in the second area Z2. The second area Z2 is a major arc fan-shaped area between the third radial line L3 and the fourth radial line L4. Therefore, the second area Z2 excludes the exhaust hole 21, that is, the exhaust hole 21 is located outside the second area Z2. The third radial line L3 forms an angle of 100° with the reference line L0, and the fourth radial line L4 forms an angle of -60° with the reference line L0.

[0064] Thus, by limiting the outlet channel R2 to be located within the second zone Z2, the outlet channel R2 can be better ensured to function as a low-pressure channel, allowing the airflow within the communication channel 32 of the second bearing 3 to return to the muffler chamber 41 through the outlet channel R2, thereby effectively achieving the effects of silencing and preventing oil accumulation. This improves the problem of airflow within the muffler chamber 41 flowing through the outlet channel R2 to the communication channel 32 of the second bearing 3, ensures smooth flow of air, and further enhances the muffler effect.

[0065] In some embodiments of the present invention, Figure 2 and Figure 5 As shown, the angle β1 between the circumferentially adjacent inlet channel R1 and the outlet channel R2 is 30° to 90°. That is, along the circumference of the pump body assembly 100, the angle β1 between the lines connecting the circumferentially adjacent inlet channel R1 and the outlet channel R2 and the center of the pump body assembly 100 is greater than or equal to 30° and less than or equal to 90°. For example, β1 can be 30°, 40°, 50°, 60°, 70°, 80°, 90°, etc.

[0066] Therefore, by limiting the angle β1 between the circumferentially adjacent and nearest air inlet channel R1 and air outlet channel R2 to 30°~90°, it can be better ensured that the air outlet channel R2 can be used as a low-pressure channel, so that the air flow in the connecting channel 32 of the second bearing 3 can return to the silencer chamber 41 through the air outlet channel R2, thereby improving the problem of the air flow in the silencer chamber 41 flowing to the connecting channel 32 of the second bearing 3 through the air outlet channel R2, thereby effectively ensuring the smoothness of the air flow and further improving the silencing effect and the effect of preventing oil accumulation.

[0067] In some embodiments of the present invention, Figure 5 As shown, there are at least two air outlet channels R2, thereby dispersing the backflow, reducing the resistance of each air outlet channel R2, improving the smoothness of the backflow, and allowing the airflow to carry out the oil more smoothly, further improving the oil accumulation problem.

[0068] Alternatively, as Figure 5 As shown, the angle β2 between any two adjacent outlet channels R2 in the circumferential direction is smaller than the angle β1. This more effectively ensures that each outlet channel R2 can be used for return flow, and can minimize the return flow path of the airflow, reduce return flow resistance, and improve the smoothness of the return flow, allowing the airflow to more smoothly carry out the oil, further improving the problem of oil accumulation.

[0069] In some embodiments of the present invention, Figure 5As shown, the number of outlet channels R2 is greater than the number of inlet channels R1. Thus, the intake air can be concentrated and the return air can be dispersed, thereby improving the flow smoothness of the airflow and reducing the return resistance, so that the airflow can carry out the oil more smoothly, further improving the oil accumulation problem.

[0070] In some embodiments of the present invention, Figure 5 As shown, regardless of the number of outlet channels R2 and inlet channels R1, the total volume of all outlet channels R2 is greater than the total volume of all inlet channels R1. This reduces backflow resistance and improves backflow smoothness, allowing the airflow to more smoothly carry out the oil, further alleviating the problem of oil accumulation.

[0071] In some embodiments of the present invention, Figure 5 As shown, the number of outlet channels R2 is greater than the number of inlet channels R1, and the total volume of all outlet channels R2 is greater than the total volume of all inlet channels R1. This disperses the backflow, reduces the resistance of each outlet channel R2, and improves the smoothness of the backflow. The airflow can more smoothly carry out the oil, further improving the problem of oil accumulation.

[0072] In some embodiments of the present invention, Figure 5 As shown, the volume of each air inlet channel R1 is smaller than the volume of any air outlet channel R2. This can reduce the backflow resistance and improve the smoothness of the backflow, allowing the airflow to more smoothly carry out the oil, further improving the oil accumulation problem.

[0073] In some embodiments of the present invention, Figure 5 As shown, there are at least two outlet channels R2, and the volume of the outlet channels R2 increases the further they are circumferentially from the exhaust hole 21. This can effectively reduce the backflow resistance of the outlet channels R2 at distant low-pressure locations, improve the smoothness of the backflow, and enable the airflow to more smoothly carry out the oil, further improving the problem of oil accumulation.

[0074] In order to ensure that the relationship between the volumes meets the above requirements, when the cross-sectional areas of the first channel section 22 and the third channel section 31 are both smaller than the cross-sectional area of ​​the second channel section 12, and the axial heights of the first channel section 22 and the third channel section 31 are both smaller than the axial height of the second channel section 12, it means that the second channel section 12 has a greater impact on the volume of the silencer channel R. Therefore, the relationship between the volumes can be set to meet the requirements.

[0075] For example, when the volume of each inlet channel R1 is smaller than the volume of any outlet channel R2, the cross-sectional area of ​​the second channel segment 12 of each inlet channel R1 can be designed to be smaller than the cross-sectional area of ​​the second channel segment 12 of any outlet channel R2. For another example, when the volume of the outlet channel R2 increases the further it is circumferentially from the exhaust hole 21, the cross-sectional area of ​​the second channel segment 12 of the outlet channel R2 can be increased the further it is circumferentially from the exhaust hole 21. This simplifies design and processing. Of course, the present invention is not limited to this, and the above requirements can also be met through the coordinated design of the first channel segment 22, the third channel segment 31, etc., which will not be described in detail here.

[0076] In some embodiments of the present invention, Figure 2 As shown, the cross-sectional area of ​​the first channel section 22 of at least one silencer channel R is smaller than the cross-sectional area of ​​the corresponding second channel section 12, that is, the cross-sectional area of ​​the second channel section 12 of at least one silencer channel R is larger than the cross-sectional area of ​​the first channel section 22. In this way, when the airflow flows from the first channel section 22 to the second channel section 12, the cross-sectional area expands due to the sudden change in cross-section, thereby further improving the sound insulation effect.

[0077] In some embodiments of the present invention, Figure 2 As shown, the cross-sectional area of ​​the third channel section 31 of at least one of any silencer channels R is smaller than the cross-sectional area of ​​the corresponding second channel section 12, that is, the cross-sectional area of ​​the second channel section 12 of at least one of the silencer channels R is larger than the cross-sectional area of ​​the third channel section 31. In this way, when the airflow flows from the third channel section 31 to the second channel section 12, the cross-sectional area expands due to the sudden change in cross-section, thereby further improving the silencer effect.

[0078] In some embodiments of the present invention, Figure 2 As shown, the cross-sectional area of ​​the first channel section 22 and the cross-sectional area of ​​the third channel section 31 of at least one silencer channel R are both smaller than the cross-sectional area of ​​the corresponding second channel section 12, that is, the cross-sectional area of ​​the second channel section 12 of at least one silencer channel R is larger than the cross-sectional area of ​​the corresponding first channel section 22 and the cross-sectional area of ​​the third channel section 31, so that multiple cross-sectional mutations can be achieved. Whether the airflow flows from the first channel section 22 to the second channel section 12 or from the third channel section 31 to the second channel section 12, it can achieve a relatively effective silencer effect.

[0079] In some embodiments of the present invention, Figure 1 and Figure 4As shown, the connecting channel 32 is constructed as: a blind groove formed on the surface of the side of the second bearing 3 facing the cylinder assembly 1, and the side of the blind groove facing the cylinder assembly 1 is a groove top and is open. As a result, processing and molding are facilitated, processing difficulty is reduced, processing costs are reduced, and the depth of the connecting channel 32 can be ensured to be relatively shallow, so that the airflow can more smoothly carry out the oil, further improving the oil accumulation problem. Of course, the present invention is not limited to this. For example, in other embodiments of the present invention, the connecting channel 32 can also be constructed as a through hole that passes through the two end faces of the second bearing 3, and the end away from the cylinder assembly 1 is blocked by a blocking member. For example, in other embodiments of the present invention, the connecting channel 32 can also be constructed as a hole opened at the axial center position of the second bearing 3.

[0080] In some embodiments of the present invention, Figure 1 and Figure 4 As shown, the third channel section 31 is constructed as: a blind groove formed on the surface of the second bearing 3 on the side facing the cylinder assembly 1, and the side of the blind groove facing the cylinder assembly 1 is a groove top and is open. This facilitates processing and molding, reduces processing difficulty and processing costs, and can ensure that the depth of the third channel section 31 is relatively shallow, so that the airflow can more smoothly carry out the oil, further improving the oil accumulation problem. Of course, the present invention is not limited to this. For example, in other embodiments of the present invention, the third channel section 31 can also be constructed as a through hole that passes through the two end surfaces of the second bearing 3, and the end away from the cylinder assembly 1 is blocked by a blocking member.

[0081] In some embodiments of the present invention, Figure 1 and Figure 4 As shown, both the connecting channel 32 and the third channel section 31 are constructed as blind grooves formed on the surface of the second bearing 3 facing the cylinder assembly 1. The side of the blind groove facing the cylinder assembly 1 is open and has a top. This facilitates processing and molding, reduces processing difficulty and cost, and ensures that the depths of the connecting channel 32 and the third channel section 31 are relatively shallow, allowing the airflow to more smoothly carry out the oil, further alleviating the problem of oil accumulation.

[0082] In some embodiments of the present invention, Figure 4As shown, when both the connecting channel 32 and the third channel section 31 are constructed as blind grooves formed on the side surface of the second bearing 3 facing the cylinder assembly 1, the groove bottom wall of the third channel section 31 (i.e., the side wall surface opposite the groove top of the blind groove) and the groove bottom wall of the connecting channel 32 (i.e., the side wall surface opposite the groove top of the blind groove) are smoothly transitioned to each other. Smooth transitions include coplanar, co-inclined, curved surfaces connected by smooth curved surfaces, curved surfaces connected by smooth curved surfaces, and straight surfaces connected by smooth curved surfaces. This prevents the formation of a step at the junction of the groove bottom wall of the third channel section 31 and the groove bottom wall of the connecting channel 32, which could cause gas-liquid separation. This ensures that the oil can be returned along with the airflow, further alleviating the problem of oil accumulation.

[0083] In some embodiments of the present invention, Figure 4 As shown, the blind groove depth is 0.5mm-5mm. For example, the blind groove depth can be 0.5mm, 1mm, 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, etc. This ensures that the blind groove depth is relatively shallow, allowing the airflow to more smoothly carry out the oil, further improving the oil accumulation problem. In addition, the rigidity and reliability of the second bearing 3 can be better guaranteed.

[0084] In some embodiments of the present invention, Figure 4 As shown, the width of the connecting channel 32 is smaller than the equivalent diameter of the third channel segment 31. Therefore, by setting the width of the connecting channel 32 smaller than the equivalent diameter of the third channel segment 31, the connecting channel 32 can be used to accelerate the airflow reaching the second bearing 3 more quickly and smoothly to the multiple third channel segments 31, improving the smoothness and reliability of the return airflow. Furthermore, the rigidity and reliability of the second bearing 3 can be better guaranteed.

[0085] In addition, it is worth noting that the cross-sectional shape of the third channel section 31 can be circular, but is not limited to a circle. For example, it can also be polygonal, elliptical, etc. Therefore, the equivalent diameter is introduced here to compare the size of the third channel section 31 and the width of the connecting channel section 32. The concept of "equivalent diameter" is well known to those skilled in the art and will not be elaborated here.

[0086] In some embodiments of the present invention, Figure 4 As shown, the groove depth of the connecting channel 32 gradually decreases in the circumferential direction away from the exhaust hole 21. This can achieve a gradual acceleration effect, allowing the airflow to effectively reach the third channel section 31 relatively farther from the exhaust hole 21, thereby improving the smoothness and reliability of the return air.

[0087] Of course, the present invention is not limited thereto. For example, in other embodiments of the present invention, the connecting channel 32 may further include a plurality of sub-segments, with each adjacent third channel segment 31 connected via a sub-segment. The width of the sub-segment decreases as it moves away from the exhaust hole 21 in the circumferential direction of the pump body assembly 100. This can achieve a gradual acceleration effect, allowing the airflow to effectively reach the third channel segment 31 that is relatively farther from the exhaust hole 21, thereby improving the smoothness and reliability of air return.

[0088] In some embodiments of the present invention, Figure 1 and Figure 5 As shown, the pump body assembly 100 can be used for a single-cylinder compressor. In this case, the number of cylinders 10 in the cylinder assembly 1 is one, that is, the cylinder assembly 1 only includes one cylinder 10. However, the structure of the cylinder assembly 1 is not limited to this. In addition to including one cylinder 10, it can also include a piston 7, a slide 6, etc. that cooperate with the cylinder 10 (for example, in combination with Figure 6 ).

[0089] In other embodiments of the present invention, the pump body assembly 100 can also be used in a multi-cylinder compressor (this example is not shown in the figure). In this case, the pump body assembly 100 can include multiple cylinders 10 and a partition plate provided between each two adjacent cylinders 10. For example, when there are two cylinders 10, the two cylinders 10 are arranged in sequence along the axial direction of the cylinder assembly 1, with the cylinder 10 closer to the first bearing 2 being defined as the first cylinder 10 and the cylinder 10 closer to the second bearing 3 being defined as the second cylinder 10. A partition plate is provided between the first cylinder 10 and the second cylinder 10, and the second channel section 12 passes through the first cylinder 10, the partition plate, and the second cylinder 10.

[0090] When the pump body assembly 100 is working, the high-pressure refrigerant compressed in the second cylinder 10 enters the first cylinder 10 through the partition. The refrigerant continues to be compressed in the first cylinder 10 and is discharged into the silencer chamber 41 through the exhaust hole 21 on the first bearing 2. Part of the refrigerant airflow in the silencer chamber 41 enters the corresponding silencer channel R through the first channel section 22 on the high-pressure side, and passes through the first bearing 2, the first cylinder 10, the partition, and the second cylinder 10 in turn, and then reaches the third channel section 31 of the second bearing 3, and then flows to the third channel section 31 on the low-pressure side through the connecting channel 32, and then passes through the silencer channel R corresponding to the third channel section 31 on the low-pressure side, and passes through the second cylinder 10, the partition, the first cylinder 10, and the first bearing 2 in turn, and then returns to the silencer chamber 41, and is discharged through the air outlet on the muffler 4.

[0091] In some embodiments, the first bearing 2, the cylinder 10 and the second bearing 3 can be connected by bolts, etc. For example, the first bearing 2 has a first connecting hole 23, the cylinder 10 has a second connecting hole 13, and the second bearing 3 has a third connecting hole 33. The bolts pass through the first connecting hole 23, the second connecting hole 13 and the third connecting hole 33 and are fastened by nuts, etc., thereby simplifying the structure and connection.

[0092] Hereinafter, a compressor 1000 according to a second embodiment of the present invention will be described with reference to the accompanying drawings.

[0093] like Figure 1 and Figure 6 As shown, compressor 1000 may include a drive assembly 200 and a pump assembly 100 for compressor 1000 according to the first embodiment of the present invention. Pump assembly 100 is connected to drive assembly 200 via a crankshaft 5. Drive assembly 200 drives crankshaft 5 to rotate, thereby driving pump assembly 100 to perform refrigerant compression. The compressor 1000 according to the embodiment of the present invention, because it is provided with the pump assembly 100 for compressor 1000 according to the embodiment of the present invention, can reduce the exhaust noise of the compressor 1000.

[0094] It is worth noting that the specific structure of the drive assembly 200 is not limited. For example, it can be a drive assembly 200. The drive assembly 200 can be an inner rotor drive motor or an outer rotor drive motor. The inner rotor drive motor can include a rotor 201 and a stator 202 provided outside the rotor. The rotor is connected to the crankshaft 5 (for example, Figure 6 As shown), the outer rotor drive motor may include a rotor and a stator arranged inside the rotor (this example is not shown in the figure), and the rotor is connected to the crankshaft 5, which will not be described here.

[0095] Of course, the compressor 1000 according to the embodiment of the present invention is not limited thereto, and may further include a housing assembly, wherein the pump assembly 100 and the drive assembly 200 are both disposed within the housing assembly, wherein the specific structure of the housing assembly is also not limited, and may be composed of multiple housing sections, for example Figure 6 In the example shown in FIG, the housing assembly may include three housing sections: an upper housing 301, a main housing 302, and a lower housing 303, which are not described in detail here. Furthermore, it is understood that the other components and operations of the compressor 1000 according to the embodiment of the present invention are well known to those skilled in the art and will not be described in detail here.

[0096] Some compressors in the related art use mufflers as the primary means of exhaust silencing. However, due to increasing requirements for low-noise standards for compressors and restrictions on compressor size, the ability to increase the muffler cavity in both the axial and radial directions is limited. To address this issue, the related art typically uses a double-layer muffler. However, the double-layer muffler structure increases flow resistance, reducing compressor performance. A balance needs to be struck between noise and energy efficiency. Furthermore, the double-layer muffler increases material costs, assembly steps, and difficulty.

[0097] In order to at least solve the above technical problems, the present application proposes a compressor 1000 , which effectively improves the silencing effect by providing a plurality of silencing channels R at different distances from the exhaust hole 21 .

[0098] Next, a compressor 1000 according to a specific embodiment of the present invention will be described.

[0099] like Figures 1-6 As shown, the compressor 1000 of this embodiment is a single-cylinder vertical compressor. The compressor 1000 includes a pump body assembly 100 and a drive assembly 200 arranged in a shell assembly. The pump body assembly 100 includes a cylinder 10, a piston 7 that rotates eccentrically in the compression chamber 11 of the cylinder 10, a crankshaft 5 that drives the piston 7 to rotate, a first bearing 2 that supports the crankshaft 5 and seals the compression chamber 11, a second bearing 3, a sliding vane 6 whose back end is connected to the outer circumference of the piston 7 through a compression spring 8, and a muffler 4 connected to the first bearing 2. The cavity between the muffler 4 and the first bearing 2 is a muffler chamber 41.

[0100] The first bearing 2 has a plurality of first channel sections 22 that pass through the upper and lower end surfaces of the first bearing 2, the cylinder 10 has a plurality of second channel sections 12 that pass through the upper and lower end surfaces of the cylinder 10, and the second bearing 3 has a blind groove formed on the upper end surface of the second bearing 3, the blind groove includes a plurality of third channel sections 31 and a connecting channel 32 that connects each two adjacent third channel sections 31.

[0101] The first channel section 22 on the first bearing 2 communicates with the muffler chamber 41. The lower surface of the first channel section 22 communicates with the upper surface of the second channel section 12. The lower surface of the second channel section 12 communicates with the third channel section 31. The third channel sections 31 are connected to each other via a connecting channel 32. Ultimately, the corresponding connected first channel sections 22, second channel sections 12, and third channel sections 31 form a muffler channel R, which communicates with the muffler chamber 41. This increases the volume of the muffler chamber 41, improves the noise level of the compressor 1000, and resolves the oil accumulation problem.

[0102] The compressed gas in cylinder 10 is discharged from exhaust port 21 and enters muffler chamber 41. Simulations of compressor 1000 operation show that, when compressor 1000 exhausts gas, high pressure forms in the area of ​​exhaust port 21 and low pressure forms in the area away from exhaust port 21 for a short period of time due to the location of exhaust port 21 on one side of muffler 4. The pressure created by the high and low pressures allows the refrigerant in muffler chamber 41 to flow, reducing the risk of oil accumulation in muffler chamber 41. Moreover, in the silencer chamber 41, due to the different positions of the multiple first channel sections 22, the pressure in the area is slightly different. The airflow in the silencer chamber 41 enters the corresponding silencer channel R from the first channel section 22 of the silencer channel R (i.e., the high-pressure channel) close to the exhaust hole 21, moves to the second bearing 3, passes through the connecting channel 32, and returns from the silencer channel R (i.e., the low-pressure channel) away from the exhaust hole 21, consuming the noise in the airflow. In the process of airflow movement, the accumulated liquid in the silencer channel R can be brought out, maintaining the silencer volume and shape, and ensuring the silencer effect.

[0103] This embodiment can be used to reduce the sound intensity of a specific noise frequency band, thereby reducing the overall noise level. For example, simulation analysis results show that when the design frequency band is 1600 Hz, the transmission loss increases in the 1600 Hz region, resulting in a better noise reduction effect at 1600 Hz.

[0104] In addition, the cross-sectional area of ​​the second channel section 12 can be set to be larger than the cross-sectional areas of the first channel section 22 and the third channel section 31 to increase the silencer volume, thereby expanding the silencer effect and improving the silencer effect.

[0105] In addition, it is worth noting that, in the embodiment of the present invention, the cross-sectional shapes of the first channel segment 22, the second channel segment 12 and the third channel segment 31 are not limited, for example, they can be circular, square, long, conical, etc. In addition, the processing methods of the first channel segment 22, the second channel segment 12 and the third channel segment 31 are not limited, for example, machining, powder metallurgy processing, die casting, etc. can be used, which will not be elaborated here.

[0106] In the description of the present invention, it should be understood that the terms "upper", "lower", "axial", "radial", "circumferential", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0107] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature identified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.

[0108] In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, they may refer to fixed connection, detachable connection, or integration; they may refer to direct connection or indirect connection through an intermediate medium; they may refer to internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0109] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0110] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0111] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A pump assembly for a compressor, characterized in that: include: A cylinder assembly having a compression chamber; a bearing assembly, the bearing assembly comprising a first bearing and a second bearing disposed on both axial sides of the cylinder assembly, the first bearing having an exhaust hole communicating with the compression chamber; a muffler assembly, the muffler assembly comprising a muffler disposed on a side of the first bearing away from the cylinder assembly, a muffler cavity communicating with the exhaust hole being formed between the muffler and the first bearing, and an air outlet hole communicating with the muffler cavity being formed on the muffler; a silencer channel, the silencer channel comprising a first channel segment formed on the first bearing, a second channel segment formed on the cylinder assembly, and a third channel segment formed on the second bearing, the first channel segment communicating with the silencer chamber, the second channel segment communicating between the first channel segment and the third channel segment, wherein the silencer channels are multiple and spaced apart along the circumference of the pump body assembly, the second bearing having a communication channel, the communication channel being used to communicate between every two adjacent third channel segments along the circumferential direction; The plurality of silencer channels include at least one air inlet channel and at least one air outlet channel, the air outlet channel being arranged circumferentially away from the exhaust hole relative to the air inlet channel, and being projected orthographically onto the cross section of the pump body assembly, the air inlet channel is located in a first area, the first area being a minor arc fan-shaped area between a first radial line and a second radial line, with a line connecting the center of the exhaust hole and the center of the pump body assembly as a reference line of 0°, the first radial line forming an angle of -30° with the reference line, and the second radial line forming an angle of 90° with the reference line; Taking an orthographic projection onto the cross section of the pump body assembly, the air outlet channel is located in the second area, which is a major arc fan-shaped area located between the third radial line and the fourth radial line. The third radial line forms an angle of 100° with the baseline, and the fourth radial line forms an angle of -60° with the baseline.

2. The pump assembly for a compressor according to claim 1, characterized in that: The angle β1 between the air inlet channel and the air outlet channel that are closest to each other in the circumferential direction is 30° to 90°.

3. The pump assembly for a compressor according to claim 2, characterized in that: There are at least two air outlet channels, and the angle β2 between any two adjacent air outlet channels in the circumferential direction is smaller than the angle β1.

4. The pump assembly for a compressor according to claim 1, characterized in that The number of the air outlet channels is greater than the number of the air inlet channels, and / or the total volume of all the air outlet channels is greater than the total volume of all the air inlet channels.

5. The pump assembly for a compressor according to claim 1, characterized in that: The volume of each of the air inlet channels is smaller than the volume of any of the air outlet channels.

6. The pump assembly for a compressor according to claim 1, characterized in that: There are at least two air outlet channels, and the air outlet channels that are farther away from the exhaust hole in the circumferential direction have larger volumes.

7. The pump assembly for a compressor according to claim 1, characterized in that: The cross-sectional area of ​​the first channel section of at least one of the muffler channels is smaller than the cross-sectional area of ​​the corresponding second channel section.

8. The pump assembly for a compressor according to claim 1, characterized in that: The cross-sectional area of ​​the third channel section of at least one of the muffler channels is smaller than the cross-sectional area of ​​the corresponding second channel section.

9. The pump assembly for a compressor according to any one of claims 1 to 8, characterized in that: At least one of the communicating channel and the third channel section is configured as a blind groove formed on a surface of the second bearing facing the cylinder assembly, wherein the side of the blind groove facing the cylinder assembly is a groove top and is open.

10. The pump body assembly for a compressor according to claim 9, characterized in that: The communicating channel and the third channel section are both blind grooves, and the bottom wall of the third channel section is smoothly transitionally connected to the bottom wall of the communicating channel.

11. The pump assembly for a compressor according to claim 9, characterized in that: The width of the communication channel is smaller than the equivalent diameter of the third channel section.

12. The pump body assembly for a compressor according to claim 9, characterized in that The blind groove has a depth of 0.5 mm to 5 mm.

13. The pump body assembly for a compressor according to claim 1, characterized in that The cylinder assembly includes one cylinder, or includes multiple cylinders and a partition plate arranged between every two adjacent cylinders.

14. A compressor, characterized in that: The invention comprises a drive assembly and a pump body assembly for a compressor according to any one of claims 1 to 13, wherein the pump body assembly is connected to the drive assembly via a crankshaft.

Images