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 first cylinder with a suction channel, comprising a main channel and a branch channel, the axis of the main channel being inclined relative to the axis of the compressor; a connecting channel on a partition member, the axis of the connecting channel being inclined relative to the axis of the compressor; and an intake channel on a second cylinder, the axis of the intake channel being inclined relative to the axis of the compressor. The main channel, the connecting channel, and the intake channel are sequentially connected. The intake end of the main channel is located on the side of the first cylinder and / or on the end face of the first cylinder facing away from the partition member. The intake channel communicates with the chamber of the second cylinder, and the branch channel connects the main channel and the chamber of the first cylinder. The technical solution of this invention solves the problem of high suction resistance in the second cylinder of the compressor in the prior art, which leads to reduced overall energy efficiency.

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 machined parts, complex manufacturing processes, and long processing times complicate manufacturing and installation, increasing costs. Therefore, a single-suction structure was proposed. However, with its development, it was found that the single-suction structure is less energy efficient than the twin-suction structure. This is mainly due to insufficient suction in the lower cylinder of existing single-suction twin-cylinder compressors. Furthermore, the suction pipe in a single-suction structure is located on the upper cylinder, and its axis is horizontal. (i.e., the suction pipe axis is perpendicular to the compressor axis). Starting from the distributor, the refrigerant accelerates through a horizontal straight suction channel. Under the action of inertia, the refrigerant preferentially enters the upper cylinder. When the suction volume of the lower cylinder is small, it is impossible to draw enough refrigerant from the lower cylinder. When the suction volume of the lower cylinder is large, the suction volume of the upper cylinder is small. A large amount of refrigerant enters the upper cylinder by inertia, causing overpressure rebound, forming eddies and pressure pulsations. The utilization rate of the suction section is reduced, resulting in insufficient suction in the lower cylinder. This leads to high suction resistance in the lower cylinder, which in turn leads to a decrease in the cooling capacity of the lower cylinder, ultimately resulting in a reduction in the overall energy efficiency of the unit. Summary of the Invention

[0003] The main objective of this invention is to provide a pump body assembly and a compressor to solve the problem of high suction resistance in the second cylinder of the compressor in the prior art, which leads to a reduction in the overall energy efficiency of the machine.

[0004] To achieve the above objectives, the present invention provides a pump body assembly for a compressor, comprising: a first cylinder having an intake channel, the intake channel including a main channel and a branch channel, the axis of the main channel being inclined relative to the axis of the compressor; a partition member having a connecting channel, the axis of the connecting channel being inclined relative to the axis of the compressor; a second cylinder located on one side of the first cylinder, the partition member being disposed between the first and second cylinders, the second cylinder having an intake channel, the axis of the intake channel being inclined relative to the axis of the compressor, the main channel, the connecting channel, and the intake channel being sequentially connected, wherein the intake end of the main channel is disposed on the side of the first cylinder and / or on the end face of the first cylinder opposite to the partition member, the intake channel communicating with the chamber of the second cylinder, and the branch channel being used to connect the main channel and the chamber of the first cylinder.

[0005] Furthermore, the axis of the main channel and the axis of the compressor have an included angle α1, which satisfies: 15°≤α1≤75°.

[0006] Furthermore, the axis of the branch channel and the axis of the compressor have an included angle β, which satisfies: 90°≥β>α1≥15°.

[0007] Furthermore, the axis of the connecting channel and the axis of the compressor have an included angle α2, which satisfies: 15°≤α2≤75°; and / or,

[0008] The axis of the intake passage and the axis of the compressor are at an angle α3, which satisfies the following condition: 15°≤α3≤75°.

[0009] Furthermore, the main passage, connecting passage, and intake passage are arranged coaxially.

[0010] Furthermore, the main channel includes a mating orifice section and a branch orifice section. One end of the branch orifice section is connected to the mating orifice section, and the other end of the branch orifice section is connected to the connecting channel. The branch channel is connected to the branch orifice section and is set at an angle. The mating orifice section is constructed to mate with the inhalation tube.

[0011] Furthermore, the diameter of the matching orifice section is d1, the radius of the diversion orifice section is R1, and the radius of the branch channel is R2. The diameter d1, radius R1, and radius R2 satisfy: d1 / 2≥R1≥R2.

[0012] Furthermore, the diameter of the matching orifice section is d1, the radius of the diversion orifice section is R1, the diameter of the connecting channel is d2, and the diameter of the intake channel is d3. The diameters d1 and R1, d2 and d3 satisfy: d1≥R1≥d2=d3.

[0013] Furthermore, the intake end of the main channel is located on the end face of the first cylinder away from the partition member, and the pump body assembly of the compressor also includes an intake pipe, which extends into the mating hole section through the intake end and mates with the mating hole section.

[0014] According to another aspect of the present invention, a compressor is provided, including the pump body assembly of the compressor described above.

[0015] By applying the technical solution of this invention, compared with the traditional horizontally arranged intake pipe, the main channel, connecting channel, and intake channel used to connect the intake end and the second cylinder chamber are all inclined relative to the compressor axis L (adopting an inclined downward intake channel). In this way, the acceleration of the inclined intake channel (main channel, connecting channel, and intake channel) from the distributor to the cylinder, under the action of gravity and inertia, the refrigerant preferentially rushes into the second cylinder. When the intake volume of the second cylinder is small, due to gravity and inertia, some refrigerant still reaches the second cylinder, which satisfies the small intake volume of the second cylinder at this time. When the intake volume of the second cylinder is large, the first cylinder takes in a small amount of air to avoid compression rebound, which can reduce the probability of eddies and pulsations, making the intake of the second cylinder sufficient and smooth. In summary, this invention employs an inclined intake channel, utilizing gravity and inertia to preferentially increase the intake volume of the second cylinder, reducing the impact of the first cylinder's intake on the second cylinder's intake, effectively reducing flow losses during the intake process, thereby reducing intake resistance and effectively improving the utilization rate of the intake cross-section. This increases the intake volume of the second cylinder, thereby increasing its cooling capacity and improving the compressor's energy efficiency. Attached Figure Description

[0016] 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:

[0017] Figure 1 A schematic diagram of an embodiment of the pump body assembly of the compressor of the present invention is shown;

[0018] Figure 2 It shows Figure 1 A partial structural diagram of the pump body assembly of the compressor;

[0019] Figure 3 It shows Figure 2 A schematic diagram of the structure of the first cylinder of the compressor's pump body assembly;

[0020] Figure 4 It shows Figure 3 A top view of the first cylinder;

[0021] Figure 5 It shows Figure 3 A bottom view of the first cylinder;

[0022] Figure 6 It shows Figure 1 A partial structural diagram of the pump body assembly of the compressor.

[0023] The above figures include the following reference numerals:

[0024] 1. First cylinder; 2. Separating component; 3. Second cylinder; 4. Mating hole section; 5. Flow dividing hole section; 6. Branch channel; 7. Connecting channel; 8. Intake channel; 9. Crankshaft; 10. Upper flange; 11. Upper roller; 12. Lower roller; 13. Lower flange; 14. Intake pipe; 15. Main channel. Detailed Implementation

[0025] 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.

[0026] like Figures 1 to 6 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 first cylinder 1, which has an intake channel including a main channel 15 and a branch channel 6, the axis of the main channel 15 being inclined relative to the axis L of the compressor; a partition member 2, which has a connecting channel 7, the axis of the connecting channel 7 being inclined relative to the axis L of the compressor; a second cylinder 3, located on one side of the first cylinder 1, the partition member 2 being disposed between the first cylinder 1 and the second cylinder 3, the second cylinder 3 having an intake channel 8, the axis of the intake channel 8 being inclined relative to the axis L of the compressor, the main channel 15, the connecting channel 7 and the intake channel 8 being sequentially connected, wherein the intake end of the main channel 15 is disposed on the side of the first cylinder 1 and / or on the end face of the first cylinder 1 facing away from the partition member 2, the intake channel 8 is connected to the chamber of the second cylinder 3, and the branch channel 6 is used to connect the main channel 15 and the chamber of the first cylinder 1.

[0027] In the above technical solution, compared with the traditional horizontally arranged suction pipe, the main channel 15, connecting channel 7 and intake channel 8 used to connect the intake end and the second cylinder 3 chamber are all inclined relative to the compressor axis L (adopting an inclined downward suction channel). In this way, the acceleration of the inclined suction channel (main channel 15, connecting channel 7 and intake channel 8) from the distributor to the cylinder causes the refrigerant to preferentially rush into the second cylinder 3 under the action of gravity and inertia. When the suction volume of the second cylinder 3 is small, some refrigerant still reaches the second cylinder 3 due to gravity and inertia, which satisfies the small suction volume of the second cylinder 3 at this time. When the suction volume of the second cylinder 3 is large, the first cylinder 1 takes in a small amount of air to avoid compression rebound, which can reduce the probability of eddy current and pulsation, so that the second cylinder 3 has sufficient and smooth suction. In summary, this invention employs an inclined suction channel, utilizing gravity and inertia to preferentially increase the suction volume of the second cylinder 3, reducing the impact of the intake of the first cylinder 1 on the suction of the second cylinder 3. This effectively reduces flow losses during the suction process, thereby reducing suction resistance and improving the utilization rate of the suction cross-section. Consequently, it increases the suction volume of the second cylinder 3, thereby increasing its cooling capacity and improving the compressor's energy efficiency.

[0028] Furthermore, the main channel 15, connecting channel 7, and intake channel 8 used to connect the intake end and the second cylinder 3 are all inclined relative to the compressor axis L. This allows the refrigerant to flow directly into the second cylinder 3, reducing the degree of refrigerant turning when entering the second cylinder 3, thereby reducing the flow resistance during the suction process and increasing the suction volume of the second cylinder 3. It also avoids the formation of low-speed vortices during the process of entering the second cylinder 3, allowing the refrigerant to flow into the second cylinder 3 more smoothly, effectively reducing flow losses during the suction process, and prioritizing the increase of the suction volume of the second cylinder 3. In this way, while taking into account the suction of the first cylinder 1, the suction volume of the second cylinder 3 is increased, thereby increasing the cooling capacity of the second cylinder 3 and improving the compressor's energy efficiency.

[0029] Preferably, in an embodiment of the present invention, the separating member 2 is a partition.

[0030] Preferably, in an embodiment of the present invention, the second cylinder 3 is a lower cylinder, the first cylinder 1 is an upper cylinder, and the second cylinder 3 is located below the first cylinder 1.

[0031] like Figure 6 As shown, in an embodiment of the present invention, the axis of the main channel 15 and the axis L of the compressor have an included angle α1, which satisfies: 15°≤α1≤75°.

[0032] In the above technical solution, when the main channel 15 is inclined relative to the compressor axis L, the refrigerant will not directly impact the cylinder wall of the first cylinder 1 when entering the main channel 15. This reduces flow loss and thus reduces energy loss during the suction process. Furthermore, due to gravity and inertia, the refrigerant preferentially enters the connecting channel 7 from the main channel 15, and then enters the second cylinder 3 from the connecting channel 7 and the intake channel 8. This increases the suction volume of the second cylinder 3, thereby reducing the impact of the suction of the first cylinder 1 on the suction of the second cylinder 3. This effectively reduces flow loss during the suction process, increases the suction volume of the second cylinder 3, and ensures that the second cylinder 3 can draw in sufficient air, thereby increasing the compressor's cooling capacity and improving the compressor's energy efficiency.

[0033] Furthermore, by controlling the included angle α1 within a specific range, the flow path and speed of the refrigerant can be optimized, allowing the refrigerant to enter the intake chamber inside the cylinder more effectively, thereby improving the intake volume and intake efficiency.

[0034] Preferably, in an embodiment of the present invention, α1 is 30°.

[0035] like Figure 6 As shown, in an embodiment of the present invention, the axis of the branch channel 6 and the axis L of the compressor have an included angle β, which satisfies: 90°≥β>α1≥15°.

[0036] In the above technical solution, the inclined setting of the branch channel 6 relative to the main channel 15 and the compressor axis L can more effectively guide the refrigerant into the chamber of the first cylinder 1. The angle β between the axis of the branch channel 6 and the axis of the compressor is greater than the angle α1. In this way, the refrigerant turns more gently when entering the branch channel 6, which helps to reduce the resistance when the refrigerant flows, thereby improving the refrigerant distribution efficiency. While ensuring that the intake volume of the second cylinder 3 is sufficient, it can also ensure that the first cylinder 1 can obtain a more sufficient and more uniform refrigerant supply.

[0037] Furthermore, by controlling the included angle β between 90° and α1, strong vortices are avoided when the refrigerant enters the branch channel 6 at a relatively sharp angle, reducing energy loss during the suction stage. This helps to improve the efficiency of the entire suction process, thereby enhancing the compressor's refrigeration performance and energy efficiency.

[0038] Preferably, in an embodiment of the present invention, β = 2α1.

[0039] like Figure 6 As shown, in an embodiment of the present invention, the axis of the connecting channel 7 and the axis L of the compressor have an included angle α2, which satisfies: 15°≤α2≤75°.

[0040] In the above technical solution, an included angle α2 is set between the connecting channel 7 and the compressor axis L, and is maintained between 15° and 75°. This helps to maintain sufficient flow area between the first cylinder 1 and the partition member 2, ensuring that the refrigerant can be smoothly distributed from the main channel 15 to the first cylinder 1 and the second cylinder 3, avoiding excessive flow resistance during the suction process, which would affect the compressor's refrigeration efficiency. Furthermore, due to gravity and inertia, the refrigerant in the main channel 15 can preferentially enter the second cylinder 3 through the connecting channel 7 and the intake channel 8, thereby increasing the suction volume of the second cylinder 3. This reduces the impact of the suction of the first cylinder 1 on the suction of the second cylinder 3, effectively reducing flow loss during the suction process, increasing the suction volume of the second cylinder 3, and ensuring that the second cylinder 3 can draw in sufficient air to increase the compressor's refrigeration capacity, thereby improving the compressor's energy efficiency.

[0041] Furthermore, a reasonable setting of the included angle α2 helps to reduce the impact of the refrigerant when it enters the connecting channel 7, reduce the vortex phenomenon during the intake flow process, thereby reducing energy loss and improving intake efficiency.

[0042] Preferably, in an embodiment of the present invention, α2 = α1.

[0043] like Figure 6 As shown, in an embodiment of the present invention, the axis of the intake channel 8 and the axis of the compressor L have an included angle α3, and the included angle α3 satisfies: 15°≤α3≤75°.

[0044] In the above technical solution, an angle α3 is set between the intake channel 8 and the compressor axis L, and is maintained between 15° and 75°. This helps to maintain sufficient flow area between the separator 2 and the second cylinder 3, ensuring that the refrigerant can be smoothly distributed from the main channel 15 to the first cylinder 1 and the second cylinder 3, avoiding excessive flow resistance during the suction process, which would affect the compressor's refrigeration efficiency. Furthermore, due to gravity and inertia, the refrigerant in the connecting channel 7 can preferentially enter the second cylinder 3 through the intake channel 8, thereby increasing the suction volume of the second cylinder 3. This reduces the impact of the suction of the first cylinder 1 on the suction of the second cylinder 3, effectively reducing flow loss during the suction process, increasing the suction volume of the second cylinder 3, and ensuring that the second cylinder 3 can draw in sufficient air to increase the compressor's refrigeration capacity, thereby improving the compressor's energy efficiency.

[0045] Furthermore, the reasonable setting of the included angle α3 helps to reduce the impact of the refrigerant when entering the intake channel 8, reduce the vortex phenomenon during the intake flow process, thereby reducing energy loss and improving intake efficiency.

[0046] Furthermore, the inclined intake channel 8 allows the refrigerant to be distributed more evenly within the chamber of the second cylinder 3, preventing refrigerant from flowing out of the cylinder and helping to improve the compressor's operating efficiency and cooling effect.

[0047] Preferably, in the embodiments of the present invention, α3 = α2 = α1.

[0048] like Figure 6 As shown, in an embodiment of the present invention, the main channel 15, the connecting channel 7, and the intake channel 8 are coaxially arranged.

[0049] In the above technical solution, by setting the main channel 15, connecting channel 7 and intake channel 8 with the same inclined axis, the intake volume of the second cylinder 3 can be increased preferentially by utilizing gravity and inertia to reduce the influence of the intake of the first cylinder 1 on the intake of the second cylinder 3. This can effectively reduce the flow loss during the intake process, thereby increasing the intake volume of the second cylinder 3 and ensuring that the second cylinder 3 can intake sufficiently to increase the cooling capacity of the compressor and thus improve the compressor's energy efficiency.

[0050] Furthermore, by coaxially arranging the main channel 15, connecting channel 7, and intake channel 8 and tilting them relative to the compressor axis L, the utilization rate of the intake cross-sectional area is maximized. This reduces the intake resistance during the intake process, balances the intake distribution of the two cylinders, reduces the impact of the intake of the first cylinder 1 on the intake of the second cylinder 3, increases the intake volume of the second cylinder 3, and ensures that the second cylinder 3 can intake sufficiently, thereby increasing the compressor's cooling capacity and improving the compressor's energy efficiency.

[0051] In one embodiment, the axes of the main channel 15, the connecting channel 7, and the intake channel 8 can be arranged in parallel, but not on the same axis.

[0052] like Figures 3 to 5 As shown, in an embodiment of the present invention, the main channel 15 includes a mating hole section 4 and a diversion hole section 5. One end of the diversion hole section 5 is connected to the mating hole section 4, and the other end of the diversion hole section 5 is connected to the connecting channel 7. The branch channel 6 is connected to the diversion hole section 5 and is set at an angle. The mating hole section 4 is constructed to mate with the suction pipe 14.

[0053] With the above configuration, utilizing gravity and inertia, the diversion orifice section 5 can guide the refrigerant entering from the suction pipe 14 from the main channel 15 to the connecting channel 7 and the branch channel 6, and then distribute it to the second cylinder 3 through the connecting channel 7, and introduce it into the first cylinder 1 through the branch channel 6. In this way, the suction volume of the second cylinder 3 can be increased first, so as to reduce the influence of the suction of the first cylinder 1 on the suction of the second cylinder 3. This not only avoids the excessive concentration of refrigerant in a certain cylinder, but also effectively reduces the flow loss during the suction process, thereby increasing the suction volume of the second cylinder 3, allowing the second cylinder 3 to have sufficient suction, and improving the overall refrigeration efficiency of the compressor.

[0054] Preferably, in an embodiment of the present invention, the axes of the mating orifice section 4 and the diversion orifice section 5 are the same.

[0055] like Figure 2 As shown, in the embodiment of the present invention, the diameter of the mating orifice 4 is d1, the radius of the diversion orifice 5 is R1, and the radius of the branch channel 6 is R2. The diameter d1, radius R1, and radius R2 satisfy: d1 / 2≥R1≥R2.

[0056] By setting d1 / 2≥R1 as described above, it helps to maintain a sufficient flow area between the suction pipe 14 and the branch orifice section 5, allowing the refrigerant discharged from the suction pipe 14 to smoothly enter the branch orifice section 5. The radius R1 of the branch orifice section 5 is greater than or equal to the radius R2 of the branch channel 6, which helps to maintain a high flow velocity when the refrigerant is split, thereby ensuring the uniform distribution of the refrigerant in the subsequent flow process and improving the refrigeration efficiency.

[0057] Preferably, in the embodiments of the present invention, the cross-sectional shape of the branch channel 6 is not limited to a circle, and can be elliptical, arched, or other shapes. The radius R2 of the branch channel 6 is half the equivalent diameter of the branch channel 6.

[0058] Preferably, in an embodiment of the present invention, the cross-sections of the mating orifice 4, the diversion orifice 5, the connecting channel 7, and the intake channel 8 are circular.

[0059] like Figure 2As shown, in the embodiment of the present invention, the diameter of the mating orifice 4 is d1, the radius of the diversion orifice 5 is R1, the diameter of the connecting channel 7 is d2, and the diameter of the intake channel 8 is d3. The diameter d1, radius R1, diameter d2, and diameter d3 satisfy: d1≥R1≥d2=d3.

[0060] In the above technical solution, the radius R1 ensures that the flow divider section 5 can smoothly transition the refrigerant from the mating section 4 to the connecting channel 7, avoiding turbulence or vortex formation at the turning point, reducing energy loss, and improving the refrigerant distribution efficiency between cylinders. Furthermore, the diameters d2 and d3 are kept equal and their dimensions are less than or equal to R1. This maintains the connectivity between the connecting channel 7 and the intake channel 8, while reducing the resistance of the refrigerant when passing through these channels, ensuring that the refrigerant can be smoothly and unobstructedly distributed to the two cylinders.

[0061] like Figure 1 and Figure 2 As shown, in an embodiment of the present invention, the air inlet end of the main channel 15 is disposed on the end face of the first cylinder 1 away from the separation member 2, and the pump body assembly of the compressor also includes an air intake pipe 14, which extends into the mating hole section 4 through the air inlet end and mates with the mating hole section 4.

[0062] With the above configuration, the air inlet end of the suction pipe 14 is located on the end face of the first cylinder 1 away from the partition member 2. This ensures that the refrigerant directly enters the mating hole section 4, avoiding additional turns when the refrigerant enters the compressor pump body, reducing flow resistance during the suction process, and thus improving suction efficiency. Furthermore, the suction pipe 14 and the mating hole section 4 are tightly fitted together, ensuring smooth refrigerant introduction, which helps to evenly distribute the refrigerant to the subsequent branch hole section 5 and branch channel 6, thereby improving the efficiency of the entire refrigeration cycle.

[0063] In one embodiment, the intake end of the main channel 15 can also be located on the circumferential sidewall of the first cylinder 1.

[0064] It should be noted that, in the embodiments of the present invention, the pump body assembly of the compressor solves the problems of long suction pipe and high flow resistance of the lower cylinder (second cylinder 3) of the traditional single-suction dual-cylinder compressor, as well as the problem of insufficient suction of the lower cylinder (second cylinder 3) of the traditional single-suction dual-cylinder compressor, which leads to reduced energy efficiency.

[0065] It should be noted that, in the embodiments of the present invention, the pump body assembly of the compressor solves the problem of insufficient air intake in the lower cylinder (second cylinder 3) and reduced energy efficiency caused by the horizontal setting of the intake channel of the traditional single-intake dual-cylinder compressor.

[0066] It should be noted that, in the embodiments of the present invention, the dual-cylinder dual-intake compressor has a large number of parts and high cost, while the dual-cylinder single-intake compressor has insufficient intake and low energy efficiency. Based on this situation, the present invention provides a pump body assembly of an inclined single-intake compressor, which has fewer parts and a shorter total length of intake pipeline, thus saving materials and reducing the manufacturing cost of the compressor. Furthermore, by setting the included angle between the intake channel, the connecting channel 7 and the intake channel 8, the intake resistance during the intake process can be reduced, the utilization rate of the intake cross section can be increased, and the intake volume of the second cylinder 3 can be improved, allowing the second cylinder 3 to intake sufficiently, increasing the cooling capacity of the compressor, and thus improving the energy efficiency of the compressor.

[0067] It should be noted that, as Figure 1 As shown, in an embodiment of the present invention, the pump body assembly of the compressor further includes a crankshaft 9, an upper flange 10, an upper roller 11, a lower roller 12, and a lower flange 13. The axis of the crankshaft 9 is the axis L of the compressor. The first cylinder 1, the separator 2, and the second cylinder 3 are located on the outer periphery of the crankshaft 9, and the upper roller 11 is located between the first cylinder 1 and the upper crank of the crankshaft 9, and the lower roller 12 is located between the second cylinder 3 and the lower crank of the crankshaft 9.

[0068] An embodiment of the present invention provides a compressor, including the pump body assembly of the compressor described above.

[0069] The compressor described above has all the advantages of the pump body assembly of the compressor described above, which will not be repeated here.

[0070] From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects: Compared with the traditional horizontally arranged suction pipe, the main channel, connecting channel and intake channel used to connect the intake end and the second cylinder chamber are all inclined relative to the compressor axis L (adopting an inclined downward suction channel). In this way, the acceleration of the inclined suction channel (main channel, connecting channel and intake channel) to the cylinder via the distributor, under the action of gravity and inertia, the refrigerant preferentially rushes into the second cylinder. When the suction volume of the second cylinder is small, due to the action of gravity and inertia, some refrigerant still reaches the second cylinder, which satisfies the small suction volume of the second cylinder at this time. When the suction volume of the second cylinder is large, the first cylinder draws in a small amount of air to avoid compression rebound, which can reduce the probability of eddy current and pulsation, so that the second cylinder draws in sufficient and smooth air. In summary, this invention employs an inclined intake channel, utilizing gravity and inertia to preferentially increase the intake volume of the second cylinder, reducing the impact of the first cylinder's intake on the second cylinder's intake, effectively reducing flow losses during the intake process, thereby reducing intake resistance and effectively improving the utilization rate of the intake cross-section. This increases the intake volume of the second cylinder, thereby increasing its cooling capacity and improving the compressor's energy efficiency.

[0071] The above description is merely a preferred embodiment of the present invention and is not intended to limit the 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 first cylinder (1) is provided with an air intake channel, which includes a main channel (15) and a branch channel (6). The axis of the main channel (15) is inclined relative to the axis (L) of the compressor. A partition member (2) is provided with a connecting channel (7), the axis of which is inclined relative to the axis (L) of the compressor; The second cylinder (3) is located on one side of the first cylinder (1). The partition member (2) is disposed between the first cylinder (1) and the second cylinder (3). The second cylinder (3) is provided with an air intake channel (8). The axis of the air intake channel (8) is inclined relative to the axis (L) of the compressor. The main channel (15), the connecting channel (7) and the air intake channel (8) are connected in sequence. The air intake end of the main channel (15) is disposed on the side of the first cylinder (1) and / or on the end face of the first cylinder (1) away from the partition member (2). The air intake channel (8) is connected to the chamber of the second cylinder (3). The branch channel (6) is used to connect the main channel (15) and the chamber of the first cylinder (1).

2. The pump body assembly of the compressor according to claim 1, characterized in that, The axis of the main channel (15) and the axis (L) of the compressor have an angle α1, which satisfies: 15°≤α1≤75°.

3. The pump body assembly of the compressor according to claim 2, characterized in that, The axis of the branch channel (6) has an angle β with the axis (L) of the compressor, and the angle β satisfies: 90°≥β>α1≥15°.

4. The pump body assembly of the compressor according to claim 1, characterized in that, The axis of the connecting channel (7) and the axis (L) of the compressor have an angle α2, which satisfies: 15°≤α2≤75°; and / or, The axis of the intake passage (8) and the axis of the compressor (L) are at an angle α3, which satisfies: 15°≤α3≤75°.

5. The pump body assembly of the compressor according to any one of claims 1 to 4, characterized in that, The main channel (15), the connecting channel (7), and the air intake channel (8) are arranged coaxially.

6. The pump body assembly of the compressor according to any one of claims 1 to 4, characterized in that, The main channel (15) includes a mating hole section (4) and a diversion hole section (5). One end of the diversion hole section (5) is connected to the mating hole section (4), and the other end of the diversion hole section (5) is connected to the connecting channel (7). The branch channel (6) is connected to the diversion hole section (5) and is set at an angle. The mating hole section (4) is constructed to mate with the suction pipe (14).

7. The pump body assembly of the compressor according to claim 6, characterized in that, The diameter of the mating hole section (4) is d1, the radius of the diversion hole section (5) is R1, and the radius of the branch channel (6) is R2. The diameter d1, radius R1, and radius R2 satisfy: d1 / 2≥R1≥R2.

8. The pump body assembly of the compressor according to claim 6, characterized in that, The diameter of the mating hole section (4) is d1, the radius of the diversion hole section (5) is R1, the diameter of the connecting channel (7) is d2, and the diameter of the air intake channel (8) is d3. The diameter d1, radius R1, diameter d2, and diameter d3 satisfy: d1≥R1≥d2=d3.

9. The pump body assembly of the compressor according to claim 6, characterized in that, The air inlet of the main channel (15) is located on the end face of the first cylinder (1) away from the partition member (2). The pump body assembly of the compressor also includes a suction pipe (14), which extends into the mating hole section (4) through the air inlet and mates with the mating hole section (4).

10. A compressor, characterized in that, The pump body assembly of the compressor as described in any one of claims 1 to 9.

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