Pump body assembly of compressor and compressor

Abstract

This invention provides a pump body assembly for a compressor and a compressor. The pump body assembly includes a pump body having a first chamber and a second chamber. The pump body has an intake channel and a connecting channel arranged at an angle. The connecting channel is inclined relative to the compressor's axis. One end of the intake channel forms an intake port for introducing refrigerant, and the other end of the intake channel communicates with the first chamber and forms an outlet. One end of the connecting channel communicates with the intake channel, and the other end of the connecting channel communicates with the second chamber. A transition channel is provided between the connecting channel and the intake channel. The transition channel is inclined relative to the compressor's axis and is constructed to disrupt the sharp angle structure at the junction of the connecting channel and the intake channel. The technical solution of this invention solves the problem of eddy current loss and gas impact on the inner wall of the channel in existing compressors, resulting in low intake efficiency of the lower cylinder.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a pump body assembly and a compressor. Background Technology

[0002] Rotary twin-cylinder compressors typically require two suction pipes. The short distance between these pipes makes welding prone to failure, resulting in a high failure rate. The large number of parts required for machining, coupled with complex and time-consuming processes, complicates manufacturing and installation, increasing costs. This led to the development of single-suction compressor technology. However, with advancements in this technology, it has been found that single-suction compressors are less energy-efficient than twin-suction compressors. This is primarily due to the reduced suction cross-sectional area, increased suction resistance, and insufficient suction, leading to a decrease in cooling capacity and consequently, lower compressor efficiency.

[0003] like Figures 10 to 12 The diagram shows a cross-sectional view of a compressor with an inclined suction channel. The upper cylinder 4-3 has a horizontal suction channel 4-8 and an inclined upper cylinder gas channel 4-9. A partition gas channel 4-10, communicating with the upper cylinder gas channel 4-9, is opened on the partition 4-4. The lower cylinder 4-5 has a lower cylinder gas channel 4-11. This single suction channel arrangement often results in insufficient suction in the lower cylinder. This phenomenon is particularly pronounced in variable frequency compressors at high frequencies, leading to insufficient cooling capacity, reduced volumetric efficiency, and overall compressor performance.

[0004] Chinese patent CN102748198B discloses a rotary compressor intake structure, Chinese patent CN114001028A discloses a compression device and a rotary compressor, and Chinese patent CN213144703U discloses a compressor intake channel and its compressor. All of the above patents involve single-intake structure compressors, which numerically limit and protect the channel angle and diameter. However, the above technical solutions still have eddy current losses and gas impact on the inner wall of the channel, resulting in low intake efficiency of the lower cylinder. Summary of the Invention

[0005] The main objective of this invention is to provide a pump body assembly and a compressor for a compressor, so as to solve the problem that the compressor in the prior art has eddy current loss and gas impact on the inner wall of the channel, which leads to low intake efficiency of the lower cylinder.

[0006] To achieve the above objectives, the present invention provides a pump body assembly for a compressor, comprising: a pump body having a first chamber and a second chamber; the pump body having an intake channel and a connecting channel arranged at an angle; the connecting channel being inclined relative to the axis of the compressor; one end of the intake channel forming an intake port for introducing refrigerant; the other end of the intake channel communicating with the first chamber and forming an outlet; one end of the connecting channel communicating with the intake channel; the other end of the connecting channel communicating with the second chamber; a transition channel being provided between the connecting channel and the intake channel; the transition channel being inclined relative to the axis of the compressor; and the transition channel being constructed to disrupt the sharp angle structure at the junction of the connecting channel and the intake channel.

[0007] Furthermore, a transition channel is provided on a portion of the circumferential inner wall at the junction of the connecting channel and the intake channel, and the transition channel is located on the side of the connecting channel closer to the intake port.

[0008] Furthermore, one or more transition channels are provided between the connecting channel and the intake channel, and the multiple transition channels are connected in sequence. The first transition channel among the multiple transition channels is connected to the intake channel, and the last transition channel among the multiple transition channels is connected to the connecting channel.

[0009] Furthermore, the pump body includes: a first cylinder, the interior of which forms a first chamber; a second cylinder, the interior of which forms a second chamber; and a separating member located between the first and second cylinders. The first cylinder has an air intake passage, a first channel, a second channel, and a third channel. The first, second, and third channels are sequentially connected to form a connecting channel. The first channel is connected to the air intake passage, a transition channel is provided at the junction of the first and air intake passages, and the third channel is connected to the second chamber.

[0010] Furthermore, the second channel includes a first through hole and a second through hole that are connected to each other. The inner diameter of the first through hole is larger than the inner diameter of the second through hole. The second through hole is connected to the first channel, and the first through hole is connected to the third channel.

[0011] Furthermore, the transition channel has an angle θ with the end face of the first cylinder, the second through hole has an angle α with the end face of the partition member, and the first through hole has an angle β with the end face of the partition member; the included angles θ, α and β satisfy: 10°<θ<α≤β≤90°.

[0012] Furthermore, the inner diameter D of the intake port, the angle α between the second through hole and the end face of the partition member, the angle β between the first through hole and the end face of the partition member, the inner diameter d1 of the first through hole, and the inner diameter d2 of the second through hole satisfy the formula:

[0013]

[0014] Furthermore, the inner diameter d4 of the transition channel, the included angle α between the second through hole and the end face of the partition member, the included angle θ between the transition channel and the end face of the first cylinder, the inner diameter d2 of the second through hole, the inner diameter D of the intake port, and the inner diameter d3 of the outlet port satisfy the following formula: d2≥d3.

[0015] Furthermore, the second channel also includes a third through hole for connecting the second through hole and the first through hole, with the inner diameter of the third through hole gradually increasing from the second through hole to the first through hole.

[0016] Furthermore, the inner diameter D of the intake port and the height H of the first cylinder satisfy the formula:

[0017] Further, the pump body includes: a first cylinder, the interior of which forms a first chamber; a second cylinder, the interior of which forms a second chamber; and a separating member located between the first and second cylinders. The second cylinder has an air intake channel, a first channel, a second channel, and a third channel. The first, second, and third channels are sequentially connected to form a connecting channel. The first channel is connected to the air intake channel, a transition channel is provided at the junction of the first channel and the air intake channel, and the third channel is connected to the first chamber.

[0018] According to another aspect of the present invention, a compressor is provided, including the pump body assembly of the compressor described above.

[0019] By applying the technical solution of this invention, the sharp corner structure at the junction of the connecting channel and the suction channel can be destroyed by setting a transition channel, which can make the refrigerant turn smoothly. This not only reduces the formation of eddies, but also reduces the phenomenon of gas impacting the inner wall of the channel, thereby reducing the suction resistance of the second cylinder. Due to the reduction of suction resistance, the refrigerant can enter the connecting channel from the suction channel more smoothly, and then enter the second chamber. In this way, the second cylinder can receive more refrigerant, thereby increasing the suction volume and improving the overall cooling capacity and energy efficiency of the compressor. Attached Figure Description

[0020] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0021] Figure 1 A schematic diagram of an embodiment of the compressor of the present invention is shown;

[0022] Figure 2 It shows Figure 1 A schematic diagram of the structure of the first cylinder of the compressor;

[0023] Figure 3 It shows Figure 1 A schematic diagram of the structure of one embodiment of the second cylinder of the compressor;

[0024] Figure 4 It shows Figure 1 A schematic diagram of the separator components of the compressor;

[0025] Figure 5 It shows Figure 1 A schematic diagram of the structure of the first cylinder of the compressor;

[0026] Figure 6 It shows Figure 1 A schematic diagram of the separator components of the compressor;

[0027] Figure 7 A sensitivity analysis diagram of refrigerant flow through each connected channel of the intake passage in a prior art compressor is shown.

[0028] Figure 8 A velocity vector comparison diagram of the pump body assembly of a compressor in the prior art and the pump body assembly of the compressor of the present invention is shown.

[0029] Figure 9 A schematic diagram of the Laval nozzle structure and a diagram illustrating the fluid acceleration principle are shown.

[0030] Figure 10 A schematic diagram of the structure of a compressor in the prior art is shown;

[0031] Figure 11 It shows Figure 10 A schematic diagram of the upper cylinder of the compressor;

[0032] Figure 12 It shows Figure 10 A schematic diagram of the structure of one embodiment of the lower cylinder of the compressor.

[0033] The above figures include the following reference numerals:

[0034] 1. Distributor; 11. Air inlet; 12. Straight pipe; 2. Housing; 21. Exhaust pipe; 3. Motor; 31. Motor stator; 32. Motor rotor; 4. Pump body assembly; 41. Upper silencer; 42. Upper flange; 43. First cylinder; 44. Separator; 45. Second cylinder; 46. Lower flange; 47. Lower silencer; 48. Intake channel; 49. First channel; 410. Second channel; 411. Third channel; 412. Transition channel; 413. Connecting channel; 414. First through hole; 415. Second through hole; 416. Third through hole; 4-3. Upper cylinder; 4-4. Baffle; 4-5. Lower cylinder; 4-8. Intake channel; 4-9. Upper cylinder gas channel; 4-10. Baffle gas channel; 4-11. Lower cylinder gas channel. Detailed Implementation

[0035] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0036] like Figures 1 to 4 As shown, an embodiment of the present invention provides a pump body assembly for a compressor. The pump body assembly for the compressor includes: a pump body having a first chamber and a second chamber; the pump body is provided with an intake passage 48 and a connecting passage 413 arranged at an angle; the connecting passage 413 is inclined relative to the axis of the compressor; one end of the intake passage 48 forms an intake port for introducing refrigerant; the other end of the intake passage 48 communicates with the first chamber and forms an outlet; one end of the connecting passage 413 communicates with the intake passage 48; the other end of the connecting passage 413 communicates with the second chamber; a transition passage 412 is provided between the connecting passage 413 and the intake passage 48; the transition passage 412 is inclined relative to the axis of the compressor; the transition passage 412 is constructed to disrupt the sharp angle structure at the junction of the connecting passage 413 and the intake passage 48.

[0037] In the above technical solution, by setting a transition channel 412, the sharp corner structure at the junction of the connecting channel 413 and the suction channel 48 can be broken, allowing the refrigerant to turn smoothly. This not only reduces the formation of eddies but also reduces the phenomenon of gas impacting the inner wall of the channel, thereby reducing the suction resistance of the second cylinder 45. Due to the reduction in suction resistance, the refrigerant can enter the connecting channel 413 more smoothly from the suction channel 48 and then enter the second chamber. In this way, the second cylinder can receive more refrigerant, thereby increasing the suction volume and improving the overall cooling capacity and energy efficiency of the compressor.

[0038] Preferably, in an embodiment of the present invention, the intake channel 48 extends in a direction perpendicular to the axis of the compressor.

[0039] like Figure 2As shown, in an embodiment of the present invention, a transition channel 412 is provided on a portion of the circumferential inner wall at the junction of the connecting channel 413 and the suction channel 48. The transition channel 412 is located on the side of the connecting channel 413 near the suction port.

[0040] In the above technical solution, the transition channel 412 allows the airflow to smoothly transition when it turns from the intake channel 48 into the connecting channel 413, which can avoid direct impact on the wall of the connecting channel 413, thereby reducing the energy loss caused by airflow impact and thus reducing the conversion between dynamic and static pressure. The transition channel 412 can break the sharp corner structure at the junction to reduce the sudden change of the airflow turning angle at this point, which helps to reduce the generation of vortices, thereby improving the intake efficiency and overall energy efficiency of the compressor.

[0041] In one embodiment, a transition channel 412 is provided on the side of the inner wall surface near the air outlet at the junction of the connecting channel 413 and the intake channel 48.

[0042] like Figure 2 As shown, in an embodiment of the present invention, a connection is provided between the connecting channel 413 and the suction channel 48. This helps to reduce the generation of vortices, thereby improving the suction efficiency and overall energy efficiency of the compressor.

[0043] In one embodiment, multiple transition channels 412 may be provided between the connecting channel 413 and the intake channel 48. The multiple transition channels 412 are connected in sequence. The first transition channel 412 of the multiple transition channels 412 is connected to the intake channel 48, and the last transition channel 412 of the multiple transition channels 412 is connected to the connecting channel 413.

[0044] like Figure 1 and Figure 2 As shown, in an embodiment of the present invention, the pump body includes: a first cylinder 43, the interior of which forms a first chamber; a second cylinder 45, the interior of which forms a second chamber; and a separating member 44 located between the first cylinder 43 and the second cylinder 45. The first cylinder 43 is provided with a suction channel 48 and a first channel 49. The separating member 44 is provided with a second channel 410, and the second cylinder 45 is provided with a third channel 411. The first channel 49, the second channel 410, and the third channel 411 are sequentially connected to form a connecting channel 413. The first channel 49 is connected to the suction channel 48, a transition channel 412 is provided at the junction of the first channel 49 and the suction channel 48, and the third channel 411 is connected to the second chamber.

[0045] In the above technical solution, by connecting the second channel 410 on the separating component 44, the first channel 49 of the first cylinder 43, and the third channel 411 of the second cylinder 45, a transition channel 412 is set at the junction of the first channel 49 and the suction channel 48. This not only enables effective suction distribution from the suction channel 48 to the first and second chambers, but also reduces ineffective eddy current losses and significantly reduces the resistance when the refrigerant enters the second chamber. In this way, it ensures that the refrigerant can enter the two cylinders smoothly and evenly, thereby improving the suction efficiency and operational stability of the compressor.

[0046] Specifically, in the embodiments of the present invention, the inclined transition channel 412 can disrupt the sharp corner structure, allowing the refrigerant gas to turn more smoothly, thereby reducing the energy loss caused by the refrigerant gas impacting the wall of the second channel 410 of the separator 44 during the intake process; and since some static pressure is converted into dynamic pressure when the refrigerant gas flows through the sharp corner structure, the inclined arrangement of the transition channel 412 in the embodiments can reduce this conversion, thereby helping to reduce the dynamic and static pressure conversion loss when the gas turns, so as to improve the operating efficiency of the compressor.

[0047] Preferably, in an embodiment of the present invention, the partition member 44 is a partition plate.

[0048] like Figure 3 As shown, in one embodiment, the pump body includes: a first cylinder 43, the interior of which forms a first chamber; a second cylinder 45, the interior of which forms a second chamber; and a separating member 44 located between the first cylinder 43 and the second cylinder 45. The second cylinder 45 has a suction channel 48 and a first channel 49. The separating member 44 has a second channel 410, and the first cylinder 43 has a third channel 411. The first channel 49, the second channel 410, and the third channel 411 are sequentially connected to form a connecting channel 413. The first channel 49 is connected to the suction channel 48, and a transition channel 412 is provided at the junction of the first channel 49 and the suction channel 48. The third channel 411 is connected to the first chamber. Alternatively, the suction channel 48 can be provided on the separating member 44. That is, suction methods such as suction from the second cylinder 45 and suction from the separating member 44 are also applicable.

[0049] like Figure 4 As shown, in an embodiment of the present invention, the second channel 410 includes a first through hole 414 and a second through hole 415 that are connected to each other. The inner diameter of the first through hole 414 is larger than the inner diameter of the second through hole 415. The second through hole 415 is connected to the first channel 49, and the first through hole 414 is connected to the third channel 411.

[0050] In the above technical solution, the second through hole 415 is connected to the first channel 49, and the first through hole 414 is connected to the third channel 411. The inner diameter of the first through hole 414 is larger than the inner diameter of the second through hole 415, forming a contraction-expansion channel structure. This utilizes the characteristics of a convergent-expanding tube in fluid mechanics, where the fluid velocity increases as it passes through the contraction section and decreases while the pressure increases in the expansion section. Therefore, when the refrigerant passes through the second through hole 415, its velocity increases, helping to reduce suction resistance; while entering the first through hole 414, the fluid velocity gradually decreases and the pressure increases, which helps to improve suction efficiency and reduce flow losses.

[0051] Furthermore, the expansion of the first through hole 414 helps to increase the intake volume of the second cylinder 45. As the refrigerant flow rate increases in the expansion section, this ensures that the second cylinder 45 can obtain a more sufficient refrigerant supply during the intake process, especially under high-frequency operating conditions, thereby improving the overall cooling capacity and energy efficiency of the unit.

[0052] like Figure 9 As shown, one-dimensional steady isentropic flow exhibits expansion-acceleration or compression-deceleration characteristics. The subsonic flow in the converging pipe A1 is expansion-accelerating, with velocity continuously increasing along the pipe while pressure, density, and temperature continuously decrease. The supersonic flow in the expanding pipe A2 is compression-decelerating, with velocity continuously decreasing along the flow path while pressure, density, and temperature continuously increase. The velocity of the one-dimensional steady isentropic flow in the converging pipe A1 can only continuously change to a critical state, which is its limit. After this point, the velocity cannot increase or decrease; this phenomenon in the converging pipe A1 is called flow congestion. Similarly, supersonic flow cannot continuously decelerate to subsonic flow through the expanding pipe A2. If the pipe is expanded after the critical section, then when the downstream physical boundary conditions at the pipe outlet section meet certain requirements, the flow can change from sonic to supersonic, thereby increasing the outlet fluid velocity and flow rate, and ultimately increasing the fluid velocity. Where A1 is the cross-sectional area at the inlet of the contraction tube, A2 is the cross-sectional area at the outlet of the expansion tube, Akr is the cross-sectional area at the narrowest point of the contraction tube, i.e., the area of ​​the throat, w is the fluid velocity, wkr is the fluid velocity at the throat, P is the fluid pressure, Pkr is the fluid pressure at the throat, and x is the distance along the flow direction.

[0053] Therefore, as Figure 6 As shown, the present invention provides an expansion structure on the separating member 44. By providing this expansion structure, the conditions for eddy current generation are disrupted, further reducing the risk of eddy currents. Figure 8 The eddy current loss at mark 1 and the impact velocity at mark 2 are shown. In this way, the intake eddy current is significantly reduced, and the flow rate and volume of the intake gas of the first cylinder 43 can be increased, thereby increasing the intake volume of the first cylinder 43 and further improving the energy efficiency of the dual-cylinder single intake.

[0054] like Figure 5 and Figure 6 As shown, in an embodiment of the present invention, the transition channel 412 and the end face of the first cylinder 43 have an included angle θ, the second through hole 415 and the end face of the partition member 44 have an included angle α, and the first through hole 414 and the end face of the partition member 44 have an included angle β; the included angles θ, α and β satisfy: 10°<θ<α≤β≤90°.

[0055] In the above technical solution, by precisely controlling the sizes of the included angles θ, α, and β, the flow resistance of the refrigerant at the channel turning points can be reduced. In particular, the introduction of the included angle θ can smooth the process of the refrigerant turning from the intake channel 48 to the first channel 49, reducing airflow collisions and vortex formation at sharp corners, thereby reducing intake resistance; and it can also allow the refrigerant to turn more smoothly and enter the second cylinder 45 during the flow process from the second through hole 415 to the first through hole 414. This helps to increase the intake volume of the second cylinder 45, especially during high-frequency operation, which can further improve the insufficient intake phenomenon in the dual-cylinder structure.

[0056] Specifically, in the embodiments of the present invention, since the included angle θ is smaller than the included angle α, the local eddy current loss when the refrigerant enters the connecting channel 413 from the intake channel 48 of the first cylinder 43 can be reduced. At the same time, the setting of the included angle β can ensure the optimized flow of the refrigerant from the first through hole 414 to the third channel 411 and reduce the formation of secondary eddies.

[0057] It should be noted that, in the embodiments of the present invention, the included angle θ is the included angle between the inner wall of the transition channel 412 and the end face of the first cylinder 43.

[0058] It should be noted that, in the embodiments of the present invention, the included angle α is the included angle between the axis of the second through hole 415 and the end face of the partition member 44, and the included angle β is the included angle between the axis of the first through hole 414 and the end face of the partition member 44.

[0059] like Figure 5 and Figure 6 As shown, in the embodiment of the present invention, the inner diameter D of the air intake, the angle α between the second through hole 415 and the end face of the partition member 44, the angle β between the first through hole 414 and the end face of the partition member 44, the inner diameter d1 of the first through hole 414, and the inner diameter d2 of the second through hole 415 satisfy the formula:

[0060] In the above technical solution, by controlling the inner diameter d2 of the second through hole 415 and the inner diameter d1 of the first through hole 414, as well as the included angles α and β between them and the end face of the separating member 44, the intake efficiency of the refrigerant from the suction port to the connecting channel 413 and finally to the second cylinder 45 can be optimized. Precise adjustment of dimensions and angles can ensure the smoothness and uniformity of refrigerant flow, thereby improving the intake volume and the overall efficiency of the compressor.

[0061] Furthermore, when the above parameters meet the conditions of the above formula, the turbulence and eddy currents of the refrigerant can be reduced, and the resistance of the refrigerant flowing through the intake port and various channels can be effectively reduced, thereby reducing energy loss and improving the fluid dynamics performance during the intake process.

[0062] Furthermore, when the above parameters meet the above formula conditions, the distribution of refrigerant in the pump body assembly can be improved, ensuring that the refrigerant flow from the suction port to the first cylinder 43 and the second cylinder 45 is more uniform, thus avoiding the problem of compressor performance degradation caused by uneven refrigerant distribution.

[0063] Preferably, in an embodiment of the present invention, the inner diameter of the first channel 49 is equal to the inner diameter of the second through hole 415, and the inclination angles of the first channel 49 and the second through hole 415 are the same. In this way, the refrigerant can enter the second through hole 415 from the first channel 49, and the refrigerant can be prevented from overflowing between the first channel 49 and the second through hole 415.

[0064] like Figure 5 and Figure 6 As shown, in the embodiment of the present invention, the inner diameter d4 of the transition channel 412, the included angle α between the second through hole 415 and the end face of the partition member 44, the included angle θ between the transition channel 412 and the end face of the first cylinder 43, the inner diameter d2 of the second through hole 415, the inner diameter D of the intake port, and the inner diameter d3 of the outlet port satisfy the following formula:

[0065]

[0066] With the above settings, the refrigerant can smoothly change direction when passing through the transition channel 412, reducing airflow collision and vortex formation, thereby reducing flow resistance and energy loss. Furthermore, by controlling the inner diameter D of the intake port, the inner diameter d3 of the outlet port, the inner diameter d4 of the transition channel 412, and the inner diameter d2 of the second through hole 415, the smooth flow of refrigerant gas during intake and exhaust can be ensured, reducing flow loss and improving the intake and exhaust efficiency of the compressor, thereby improving the overall performance of the compressor.

[0067] It should be noted that in the embodiments of the present invention, the cross-sections of the first through hole 414, the second through hole 415, the air intake, the transition channel 412, and the air outlet are all circular; or, the cross-sections of the first through hole 414, the second through hole 415, the air intake, the transition channel 412, and the air outlet are all irregular shapes, in which case the inner diameters d1, d2, d3, d4, and D are all equivalent diameters of the corresponding channels.

[0068] like Figure 4 As shown, in an embodiment of the present invention, the second channel 410 further includes a third through hole 416 for connecting the second through hole 415 and the first through hole 414. The inner diameter of the third through hole 416 gradually increases from the second through hole 415 to the first through hole 414.

[0069] In the above technical solution, as the inner diameter of the third through hole 416 gradually increases, the flow rate of the refrigerant will gradually decrease while the pressure will gradually increase when it passes through the channel. This helps to optimize the fluid dynamics performance of the entire intake and connection process, reduce flow losses, and improve the operating efficiency of the compressor.

[0070] Furthermore, the expansion of the third through hole 416 helps to increase the intake volume of the first cylinder 43. As the fluid pressure increases in the expansion section, it helps to push more refrigerant into the first cylinder 43, ensuring that the second cylinder 45 can obtain sufficient intake volume under various operating conditions, thereby improving the overall cooling capacity and energy efficiency of the unit.

[0071] Furthermore, the gradual change in the inner diameter of the third through-hole 416 helps to achieve a smooth flow of refrigerant gas from the second through-hole 415 to the first through-hole 414, reducing flow losses and improving the uniformity of airflow distribution.

[0072] In one embodiment, the third through hole 416 may be omitted, allowing the second through hole 415 and the first through hole 414 to be directly connected.

[0073] like Figure 5 As shown, in an embodiment of the present invention, the inner diameter D of the intake port and the height H of the first cylinder 43 satisfy the formula:

[0074]

[0075] In the above technical solution, by precisely controlling the ratio of the inner diameter D of the intake port to the height H of the first cylinder, the efficiency of the refrigerant gas entering the first cylinder 43 can be optimized. An appropriate D / H ratio can ensure that the refrigerant is evenly distributed when entering the first cylinder 43, avoiding insufficient intake or excessive turbulence caused by excessive local flow velocity, thereby improving intake efficiency.

[0076] It should be noted that, in the embodiments of the present invention, the height H of the first cylinder is the distance between the two end faces of the first cylinder on the axis of the compressor.

[0077] The embodiments of the present invention can reduce the suction resistance of a dual-cylinder single-suction compressor and increase the suction volume of the lower cylinder. Compared with the problem of insufficient suction in the lower cylinder of a dual-cylinder dual-suction compressor, the embodiments of the present invention can in particular improve the problem of insufficient suction when the dual-cylinder single-suction compressor is running at high flow rate, so as to narrow the high-frequency energy efficiency gap between single-suction and dual-suction compressors, improve the energy efficiency of the dual-cylinder single-suction compressor, and further amplify the cost advantage of single-suction compressors, providing more options in the product development process where the demand for cost reduction and efficiency improvement is constantly increasing.

[0078] It should be noted that, as Figure 1 As shown, in an embodiment of the present invention, the pump body assembly 4 further includes an upper silencer 41, an upper flange 42, a lower flange 46, and a lower silencer 47, with the pump body located between the upper flange 42 and the lower flange 46.

[0079] like Figure 1 As shown, an embodiment of the present invention provides a compressor. The compressor includes the pump body assembly 4 of the compressor described above.

[0080] Specifically, such as Figure 1 As shown, in an embodiment of the present invention, the compressor further includes a distributor 1, a housing 2, an exhaust pipe 21, and a motor 3. The pump assembly 4 is located inside the housing 2. The motor 3 includes a motor stator 31 and a motor rotor 32. The mixed gas of refrigerant and refrigeration oil enters the distributor 1 through the inlet 11 of the distributor and completes gas-liquid separation in the distributor 1. The refrigerant flows through the straight pipe 12 of the distributor and enters the pump assembly 4.

[0081] In existing technologies, dual-cylinder single-intake compressors, such as Figures 10 to 12 As shown, the refrigerant enters the suction channel 4-8 through the straight pipe of the distributor to complete the gas distribution between the upper and lower cylinders. The upper cylinder is directly suctioned with low suction resistance. The refrigerant entering the lower cylinder 4-5 needs to pass through the upper cylinder gas channel 4-9, the partition gas channel 4-10, and the lower cylinder gas channel 4-11. During the process of gas moving from the upper cylinder to the lower cylinder, the direction of gas movement changes. For example... Figure 7 As shown, a structural sensitivity analysis of suction resistance was performed using simulation tools. It was found that the suction resistance is greatest at the junction of the two channels. The simulation yielded a vector diagram of the suction velocity in a conventional dual-cylinder single-suction system. The results showed that during the refrigerant's transition from the upper cylinder to the lower cylinder, the gas impacts the baffle plate 4-4, causing significant flow losses at this point. Figure 8 Mark 2 in the diagram. At the same time, the vortex loss at mark 1 is also greater for the twin-cylinder single-intake configuration.

[0082] In this application, a transition channel 412 is added to the first cylinder 43, which reduces the vortex range at the corner and can reduce... Figure 8 Eddy current loss at mark 1 in the diagram, to form Figure 8 The eddy current loss at mark 1 can be reduced. Figure 8 The impact velocity at mark 2 in the diagram is used to form Figure 8 The vortex impact velocity at mark 2 can be reduced, thereby decreasing the dynamic and static pressure conversion at this point, reducing losses, and lowering the suction resistance from 102 Pa to 64 Pa, a 40% reduction. Table 1 below compares the conventional compressor and the compressor of this invention in practical applications. As shown in Table 1, the improvement effect of this invention in practical applications is significant.

[0083] Table 1

[0084]

[0085] The compressor described above has all the advantages of the pump body assembly of the compressor described above, which will not be repeated here.

[0086] As can be seen from the above description, the above embodiments of the present invention achieve the following technical effects: by setting a transition channel, the sharp corner structure at the junction of the connecting channel and the suction channel can be destroyed, allowing the refrigerant to turn smoothly. This not only reduces the formation of eddies but also reduces the phenomenon of gas impacting the inner wall of the channel, thereby reducing the suction resistance of the second cylinder. Due to the reduction in suction resistance, the refrigerant can more smoothly enter the connecting channel from the suction channel and then enter the second chamber. In this way, the second cylinder can receive more refrigerant, thereby increasing the suction volume and improving the overall cooling capacity and energy efficiency of the compressor.

[0087] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A pump body assembly for a compressor, characterized in that, include: The pump body has a first chamber and a second chamber. The pump body is provided with an intake channel (48) and a connecting channel (413) arranged at an angle. The connecting channel (413) is inclined relative to the axis of the compressor. One end of the intake channel (48) forms an intake port for introducing refrigerant. The other end of the intake channel (48) is connected to the first chamber and forms an outlet. One end of the connecting channel (413) is connected to the intake channel (48). The other end of the connecting channel (413) is connected to the second chamber. A transition channel (412) is provided between the connecting channel (413) and the intake channel (48). The transition channel (412) is inclined relative to the axis of the compressor. The transition channel (412) is constructed to break the sharp corner structure at the junction of the connecting channel (413) and the intake channel (48).

2. The pump body assembly of the compressor according to claim 1, characterized in that, The transition channel (412) is provided on a portion of the inner circumferential wall at the junction of the connecting channel (413) and the air intake channel (48). The transition channel (412) is located on the side of the connecting channel (413) near the air intake.

3. The pump body assembly of the compressor according to claim 1, characterized in that, One or more transition channels (412) are provided between the connecting channel (413) and the intake channel (48). The multiple transition channels (412) are connected in sequence. The first of the multiple transition channels (412) is connected to the intake channel (48), and the last of the multiple transition channels (412) is connected to the connecting channel (413).

4. The pump body assembly of the compressor according to any one of claims 1 to 3, characterized in that, The pump body includes: The first cylinder (43) has the first chamber formed inside the first cylinder (43); The second cylinder (45) has the second chamber formed inside it; A partition member (44) is located between the first cylinder (43) and the second cylinder (45). The first cylinder (43) is provided with the intake channel (48) and the first channel (49). The partition member (44) is provided with the second channel (410) and the second cylinder (45) is provided with the third channel (411). The first channel (49), the second channel (410) and the third channel (411) are sequentially connected to form the connecting channel (413). The first channel (49) is connected to the intake channel (48). The transition channel (412) is provided at the junction of the first channel (49) and the intake channel (48). The third channel (411) is connected to the second chamber.

5. The pump body assembly of the compressor according to claim 4, characterized in that, The second channel (410) includes a first through hole (414) and a second through hole (415) that are connected to each other. The inner diameter of the first through hole (414) is larger than the inner diameter of the second through hole (415). The second through hole (415) is connected to the first channel (49), and the first through hole (414) is connected to the third channel (411).

6. The pump body assembly of the compressor according to claim 5, characterized in that, The transition channel (412) has an angle θ with the end face of the first cylinder (43), the second through hole (415) has an angle α with the end face of the partition member (44), and the first through hole (414) has an angle β with the end face of the partition member (44). The included angles θ, α, and β satisfy the following condition: 10° < θ < α ≤ β ≤ 90°.

7. The pump body assembly of the compressor according to claim 5, characterized in that, The inner diameter D of the air intake, the included angle α between the second through hole (415) and the end face of the partition member (44), the included angle β between the first through hole (414) and the end face of the partition member (44), the inner diameter d1 of the first through hole (414), and the inner diameter d2 of the second through hole (415) satisfy the formula:

8. The pump body assembly of the compressor according to claim 5, characterized in that, The inner diameter d4 of the transition channel (412), the included angle α between the second through hole (415) and the end face of the partition member (44), the included angle θ between the transition channel (412) and the end face of the first cylinder (43), the inner diameter d2 of the second through hole (415), the inner diameter D of the intake port, and the inner diameter d3 of the outlet port satisfy the following formula:

9. The pump body assembly of the compressor according to claim 5, characterized in that, The second channel (410) further includes a third through hole (416) for connecting the second through hole (415) and the first through hole (414), and the inner diameter of the third through hole (416) gradually increases from the second through hole (415) to the first through hole (414).

10. The pump body assembly of the compressor according to claim 4, characterized in that, The inner diameter D of the air intake and the height H of the first cylinder (43) satisfy the formula:

11. The pump body assembly of the compressor according to any one of claims 1 to 3, characterized in that, The pump body includes: The first cylinder (43) has the first chamber formed inside the first cylinder (43); The second cylinder (45) has the second chamber formed inside it; A partition member (44) is located between the first cylinder (43) and the second cylinder (45). The second cylinder (45) is provided with the intake channel (48) and the first channel (49). The partition member (44) is provided with the second channel (410) and the first cylinder (43) is provided with the third channel (411). The first channel (49), the second channel (410) and the third channel (411) are sequentially connected to form the connecting channel (413). The first channel (49) is connected to the intake channel (48). The transition channel (412) is provided at the junction of the first channel (49) and the intake channel (48). The third channel (411) is connected to the first chamber.

12. A compressor, characterized in that, The pump body assembly (4) of the compressor according to any one of claims 1 to 11.

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