Pump body structure of a single-suction compressor, compressor and air conditioner

Abstract

The present invention provides a pump body structure, a compressor, and an air conditioner of a single-suction compressor. The pump body structure includes: a first cylinder, a partition plate, and a second cylinder; an air suction passage, a first air intake passage, a first flow-dividing passage, and a first sliding vane groove are provided on the first cylinder, a second flow-dividing passage is provided on the partition plate, and a second air intake passage is provided on the second cylinder; the first air intake passage is a groove formed on the inner peripheral wall of the first cylinder, one end of the first air intake passage communicates with the air suction passage, and the other end communicates with the inner peripheral wall of the first cylinder; in the circumferential direction, the minimum distance between the first air intake passage and the first sliding vane groove is less than the minimum distance between the air suction passage and the first sliding vane groove. According to the present invention, the air suction starting angle of the first cylinder can be effectively reduced, the time when the compressor starts to suck air can be effectively advanced, thereby effectively increasing the air suction volume, further effectively improving the refrigeration performance of the first cylinder, and thus improving the reliability, stability, and service life of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a pump body structure, a compressor, and an air conditioner of a single-suction compressor. Background Art

[0002] Rotary compressors are currently mainly used in household air conditioning systems as power devices to drive refrigerants to circulate and exchange heat in pipelines to meet the cooling and heating requirements.

[0003] With the skyrocketing prices of raw material commodities used in current air conditioning systems, the entire industry is conducting cost reduction designs for air conditioning systems. There are various cost reduction design options for compressors: changing from double-cylinder suction to single-cylinder suction, selecting cheaper materials for parts, making the housing thinner, reducing the amount of refrigerating oil, replacing the refrigerant, etc. Here, for the design of changing from double-cylinder suction to single-cylinder suction, there are currently two main improvement methods: diaphragm intake and upper cylinder intake.

[0004] When using diaphragm intake, the starting angle of suction for the upper and lower cylinders can be adjusted by adjusting the angle between the center line of the diaphragm suction hole and the center of the vane slot. However, the thickness of the diaphragm is much smaller than that of the cylinder. Therefore, if the suction hole is set on the middle diaphragm, the middle diaphragm must be thickened. In this way, on the one hand, the room for cost reduction is limited, and more importantly, the height of the entire compression structure will increase, and this change will deteriorate the reliability of the compression structure.

[0005] Due to the problems in the prior art that when a double-cylinder compressor adopts a single-suction structure, the starting angle of suction is relatively large, resulting in a delay in the start of suction of the compressor, a decrease in the suction volume, and a reduction in refrigeration capacity and performance, etc., the present invention researches and designs a pump body structure, a compressor, and an air conditioner of a single-suction compressor. Summary of the Invention

[0006] Therefore, the technical problem to be solved by the present invention is to overcome the defect that when a double-cylinder compressor in the prior art adopts a single-suction structure, the starting angle of suction is relatively large, resulting in a delay in the start of suction of the compressor, a decrease in the suction volume, and an impact on the refrigeration performance, so as to provide a pump body structure, a compressor, and an air conditioner of a single-suction compressor.

[0007] To solve the above problems, the present invention provides a pump body structure of a single-suction compressor, which includes:

[0008] A first cylinder, a diaphragm, and a second cylinder, the diaphragm is located between the first cylinder and the second cylinder; an air suction channel, a first air intake channel, a first diversion channel, and a first vane slot are provided on the first cylinder, a second diversion channel is provided on the diaphragm, and a second air intake channel is provided on the second cylinder;

[0009] The intake passage extends from the outer peripheral wall of the first cylinder to a predetermined distance from the inner peripheral wall of the first cylinder. The first intake passage is a groove structure formed on the inner peripheral wall of the first cylinder. One end of the first intake passage is connected to the intake passage, and the other end is connected to the inner peripheral wall of the first cylinder for intake. In addition, a minimum distance between the first intake passage and the first vane groove in the circumferential direction is smaller than a minimum distance between the intake passage and the first vane groove.

[0010] The second intake channel is a groove structure opened on the inner wall of the second cylinder, the first diversion channel is connected to the intake channel, one end of the second diversion channel is connected to the first diversion channel, and the other end is connected to the second intake channel, so as to intake air into the second cylinder through the second intake channel.

[0011] In some embodiments, the first air intake channel is a U-shaped groove structure, the angle between the center line of the air intake channel and the center line of the first vane groove is A2, and the angle between the center line of the first air intake channel and the center line of the first vane groove is less than A2.

[0012] In some embodiments, in the projection plane of the connecting end surface of the intake channel and the outer peripheral wall of the first cylinder, the projection of the first intake channel and the intake channel in the projection plane is a trapezoidal structure, the top length, bottom length and height of the trapezoid are a, b and h respectively, and the cross-sectional area of the first intake channel is and / or,

[0013] The minimum distance between the first air inlet channel and the first vane groove in the circumferential direction is T2, and 1mm≤T2≤2mm.

[0014] In some embodiments, the first intake channel extends from one axial end face of the first cylinder facing away from the partition toward the other axial end face where the first cylinder is connected to the partition, and the minimum axial distance between the first intake channel and the partition is greater than the minimum axial distance between the intake channel and the partition; the axial depth of the first intake channel is d1, which is less than the axial depth of the intake channel.

[0015] In some embodiments, the air intake channel includes a first air intake channel and a second air intake channel connected in sequence along the air intake direction, and the aperture of the first air intake channel is larger than the aperture of the second air intake channel to form a step at the junction of the two, and the length of the first air intake channel is L1, the length of the second air intake channel is L2, the first air intake channel is connected to the second air intake channel, and the first diversion channel is also connected to the second air intake channel.

[0016] In some embodiments, a second sliding vane groove is further provided on the second cylinder, and the second flow dividing channel can conduct the airflow towards the direction close to the second sliding vane groove, so that in the projection plane in the axial direction and in the circumferential direction, the minimum distance between the second air inlet channel and the second sliding vane groove is less than the minimum distance between the first flow dividing channel and the second sliding vane groove.

[0017] In some embodiments, the second flow dividing channel includes a third flow dividing channel and a fourth flow dividing channel that are sequentially connected along the airflow direction. The fourth flow dividing channel is connected between the third flow dividing channel and the second air inlet channel. And in the projection plane of the axial end face where the first cylinder is connected to the partition board, the included angle between the central connection line of the centers of the third flow dividing channel and the first cylinder and the center line of the first sliding vane groove is A1, and the included angle between the central connection line of the centers of the fourth flow dividing channel and the first cylinder and the center line of the first sliding vane groove is B1, A1 > B1; when the included angle between the center line of the air suction channel and the center line of the first sliding vane groove is A2, A1 = A2.

[0018] In some embodiments, the third flow dividing channel is a counterbore extending from the axial end face where the partition board is connected to the first cylinder towards the axial end face where the partition board is connected to the second cylinder, and the length of the counterbore along its axis is H2; the fourth flow dividing channel is a through hole extending from the axial end face where the partition board is connected to the first cylinder towards the axial end face where the partition board is connected to the second cylinder, and the length of the through hole along its axis is H1; and H1 > H2.

[0019] In some embodiments, in the longitudinal section of the partition board, the included angle between the central axis of the third flow dividing channel and the axial end face of the partition board is C1, and the included angle between the central axis of the fourth flow dividing channel and the axial end face of the partition board is also C1, and the range of C1 is or; the aperture diameters of the third flow dividing channel and the fourth flow dividing channel are both d3.

[0020] In some embodiments, the fourth flow dividing channel is arranged closer to the center line of the partition board than the third flow dividing channel; the distance between the point where the central axis of the third flow dividing channel is connected to the axial end face of the first cylinder and the center line of the partition board is M1, and the distance between the point where the central axis of the fourth flow dividing channel is connected to the axial end face of the second cylinder and the center line of the partition board is N, M1 > N.

[0021] In some embodiments, the second intake passage has a U-shaped groove structure. The second intake passage extends from the axial end face where the second cylinder is connected to the partition plate in a direction away from the partition plate. And within the projection plane of the axial end face where the second cylinder is connected to the partition plate, the included angle B2 between the center line connecting the center of the second intake passage and the center of the second cylinder and the center line of the second sliding vane groove is such that B2 = B1.

[0022] In some embodiments, the included angle C3 between the central axis of the second intake passage and the axial end face of the second cylinder is such that the range of C3 is (0, 90°) or (90°, 180°); the aperture diameter of the second intake passage is d4; the cross-sectional area of the second intake passage is In the longitudinal section, the distance N2 between the point where the center line of the second intake passage meets the axial end face of the partition plate and the central axis of the second cylinder.

[0023] In some embodiments, the aperture diameter of the first diversion passage is d2; and there is d2 = d3 = d4 or d3 ≥ d2 + 0.1 mm or d3 ≥ d4 + 0.1 mm.

[0024] In some embodiments, the first diversion passage is not in communication with the first intake passage; the included angle C2 is formed between the central axis of the first diversion passage and the axial end face of the first cylinder, and the range of C2 is (0, 90°) or (90°, 180°), such that the first diversion passage extends in a direction approaching the central axis of the first cylinder;

[0025] The minimum distance T between the first diversion passage and the inner wall surface of the first cylinder is such that T > 1 mm; and the distance M2 between the point where the center line of the first diversion passage meets the axial end face of the partition plate and the central axis of the first cylinder; the inner circle radius of the first cylinder is D.

[0026] In some embodiments, the range of C2 is (90°, 180°), and there is

[0027] The present invention also provides a compressor, which includes the pump body structure of the single-suction compressor described in any one of the previous items.

[0028] The present invention also provides an air conditioner, which includes the compressor described above.

[0029] The pump body structure, compressor and air conditioner of the single-suction compressor provided by the present invention have the following beneficial effects:

[0030] 1. The present invention provides a suction passage on the first cylinder of a compressor with a double-cylinder structure for suction, a first intake passage for introducing gas into the first cylinder. The first diversion passage can divert a part of the suction gas into the second diversion passage on the partition plate and further into the second intake passage of the second cylinder to complete the intake of the second cylinder. Moreover, the minimum distance between the first intake passage and the first vane slot in the circumferential direction is less than the minimum distance between the suction passage and the first vane slot. This enables the opening position of the first intake passage to move a certain distance towards the first vane slot compared to the suction passage, effectively reducing the suction start angle of the first cylinder, advancing the start time of the compressor's suction, thereby effectively increasing the suction volume, further enhancing the refrigeration performance of the first cylinder, improving the reliability, stability, and service life of the compressor, effectively reducing the compressor cost without changing the compressor capacity, and ensuring that the refrigeration capacity does not decrease.

[0031] 2. The present invention also sets a second diversion structure on the partition plate, preferably through the third diversion passage and the fourth diversion passage. The angle B1 between the center line connecting the center of the fourth diversion passage and the center of the first cylinder and the center line of the first vane slot is less than the angle A1 between the center line connecting the third diversion passage and the center line of the first vane slot. This effectively changes the flow path through the third and fourth diversion passages, causing the intake towards the second cylinder to tilt and shift towards the second vane slot, effectively reducing the suction start angle of the second cylinder, advancing the start time of the compressor's suction, thereby effectively increasing the suction volume, further enhancing the refrigeration performance of the first cylinder, improving the reliability, stability, and service life of the compressor, effectively reducing the compressor cost without changing the compressor capacity, and ensuring that the refrigeration capacity does not decrease. And by setting the diversion passage on the partition plate to reduce the suction start angle, compared with the structure of opening a U-shaped groove on the second cylinder, there is no need to open redundant U-shaped grooves similar to those on the first cylinder in the narrow space of the second cylinder, effectively preventing the intersection with the diversion passage from damaging the flow path or the structure in the second vane slot, and preventing the relative position of the spring in the vane slot and the housing from being exposed, etc., which may affect the normal compression operation. Thus, it further effectively improves the operating stability and refrigeration performance of the second cylinder. Brief Description of the Drawings

[0032] Figure 1 is an assembled structure sectional view of the pump body structure of the single-suction compressor of the present invention;

[0033] Figure 2 is a top view structure diagram of the first cylinder in the pump body structure of the single-suction compressor of the present invention;

[0034] Figure 2a isFigure 2 Partial sectional view along E-E in

[0035] Figure 2b is Figure 2 Front view in direction A in

[0036] Figure 2c is Figure 2b Enlarged partial view of part A of

[0037] Figure 3 Top view structure diagram of the partition in the pump body structure of the single-suction compressor of the present invention

[0038] Figure 3a is Figure 3 Partial sectional view along A-A in

[0039] Figure 3b is Figure 3 Partial sectional view along C-C in

[0040] Figure 4 Top view structure diagram of the partition in the pump body structure of the single-suction compressor of the present invention

[0041] Figure 4a is Figure 4 Partial sectional view along F-F in

[0042] Figure 5 Combined structure diagram of the suction channel, intake channel and diversion channel in the pump body structure of the present invention

[0043] Figure 6 Top view structure diagram of the partition of the alternative embodiment of the present invention

[0044] Figure 6a is Figure 6 Front sectional view in

[0045] Figure 6b is Figure 6 Stereoscopic sectional view in

[0046] Figure 7 Assembly structure diagram of the first cylinder and the housing of the present invention.

[0047] Reference numerals are shown as:

[0048] 1. Crankshaft; 2. Upper flange; 3. First cylinder; 31. Suction passage; 32. First shunt passage; 33. First intake passage; 34. First exhaust passage; 35. First combination screw hole; 36. First valve rivet hole; 37. First vane slot; 4. Partition; 41. Second shunt passage; 411. Third shunt passage; 412. Fourth shunt passage; 42. Second combination screw hole; 43. Second exhaust passage; 5. Second cylinder; 51. Second intake passage; 52. Third exhaust passage; 53. Lower flange positioning screw hole; 54. Third combination screw hole; 55. Second valve rivet counterbore; 56. Second vane slot; 57. Exhaust resonance cavity; 6. Lower flange; 7. Roller; 8. Housing. Detailed implementation manner

[0049] As Figures 1-7 shown, the present invention provides a pump body structure of a single-suction compressor, which includes:

[0050] A first cylinder 3, a partition 4 and a second cylinder 5, the partition 4 is located between the first cylinder 3 and the second cylinder 5; a suction passage 31, a first intake passage 33, a first shunt passage 32 and a first vane slot 37 are provided on the first cylinder 3, a second shunt passage 41 is provided on the partition 4, and a second intake passage 51 is provided on the second cylinder 5;

[0051] The suction passage 31 extends (preferably radially) from the outer peripheral wall of the first cylinder 3 to a preset distance from the inner peripheral wall of the first cylinder 3, the first intake passage 33 is a groove structure formed on the inner peripheral wall of the first cylinder 3, one end of the first intake passage 33 is communicated with the suction passage 31, and the other end is communicated with the inner peripheral wall of the first cylinder 3 for intake; and in the circumferential direction, the minimum distance between the first intake passage 33 and the first vane slot 37 is less than the minimum distance between the suction passage 31 and the first vane slot 37;

[0052] The second intake passage 51 is a groove structure formed on the inner peripheral wall of the second cylinder 5, the first shunt passage 32 is communicated with the suction passage 31, one end of the second shunt passage 41 is communicated with the first shunt passage 32, and the other end is communicated with the second intake passage 51 to intake air into the second cylinder 5 through the second intake passage 51.

[0053] In the present invention, an air intake passage is opened on the first cylinder of a compressor with a double-cylinder structure for air intake, a first air inlet passage is used for introducing air into the interior of the first cylinder, and a first diversion passage can divert a part of the intake air into a second diversion passage on a partition plate and further into a second air inlet passage of a second cylinder to complete the air intake of the second cylinder. Moreover, the minimum distance between the first air inlet passage and the first sliding vane groove in the circumferential direction is smaller than the minimum distance between the air intake passage and the first sliding vane groove in the present application, which can make the opening position of the first air inlet passage move a certain distance towards the direction close to the first sliding vane groove compared with the air intake passage, thereby effectively reducing the initial air intake angle of the first cylinder, effectively advancing the time when the compressor starts to intake air, effectively increasing the air intake volume, further effectively improving the refrigeration performance of the first cylinder, thereby improving the reliability, stability and service life of the compressor, and being able to effectively reduce the cost of the compressor without changing the capacity of the compressor and ensuring that the refrigerating capacity does not decrease.

[0054] The present invention can change the double-cylinder air intake to single-cylinder air intake without significantly modifying the original structure, and simultaneously solve the problems of the initial air intake angles of the upper and lower cylinders in single-cylinder air intake and the exposure problem of the upper cylinder spring; or in other words, it can effectively reduce the cost of the compressor without changing the capacity of the compressor. The refrigerating capacity does not decrease, and the reliability, stability and service life of the compressor are improved.

[0055] The embodiment of the present invention includes a new structure crankshaft and a pump body structure having the same, which are composed of six major components: a cylinder, a sliding vane, a roller, an upper flange, a lower flange, and a crankshaft. The crankshaft is divided into the following parts: a long shaft, a short shaft, an eccentric part, and an oil passage part. The upper end of the long shaft is connected to the motor rotor, the lower end of the long shaft is assembled with the aperture of the upper flange, the eccentric part is nested and assembled with the roller, and the short shaft is assembled with the aperture of the lower flange. The cylinder (which can be a single cylinder, a double cylinder or a triple cylinder) and the sliding vane are nested and assembled through a cylinder sliding vane groove, and the upper and lower flanges and the upper and lower end faces of the cylinder are fixed by screws through positioning holes. The upper and lower flanges serve as bearings of the crankshaft to support the rotation of the crankshaft, and the eccentric part of the crankshaft drives the roller to rotate in the cylinder to intake, compress and exhaust the refrigerant. The overall matching diagram of the six major components is as Figure 1 shown.

[0056] Please refer to Figure 2 、 Figure 3 Figure 4 Figure 5 wherein, Figure 2 is the front view and cross-sectional view of the two-dimensional structure of the upper cylinder cooperating with the partition plate structure provided by an embodiment of the present invention, Figure 3 is the front view and cross-sectional view of the two-dimensional structure of the partition plate provided by an embodiment of the present invention, Figure 4 is the front view and cross-sectional view of the two-dimensional structure of the lower cylinder cooperating with the partition plate structure provided by an embodiment of the present invention, Figure 5The 2D front view and cross-sectional view of the combination assembly of the partition plate and the cylinder provided by an embodiment of the present invention. The cross-sectional view of the above structure is mainly to facilitate the display of the refrigerant flow path.

[0057] In some embodiments, the first intake passage 33 has a U-shaped groove structure. The included angle between the center line of the intake passage 31 and the center line of the first sliding vane groove 37 is A2, and the included angle between the center line of the first intake passage 33 and the center line of the first sliding vane groove 37 is less than A2. This is the preferred structural form of the first intake passage of the present invention. Through the first intake passage with a U-shaped groove structure, it is convenient to process from the axial end face of the first cylinder by stamping or cutting. And the included angle between the first intake passage and the center line of the first sliding vane groove is less than the included angle A2 between the intake passage and the center line of the first sliding vane groove, effectively offsetting the first intake passage towards the direction of the first sliding vane groove, thereby reducing the intake starting angle, effectively improving the intake volume of the first cylinder, and improving the refrigeration capacity and refrigeration efficiency.

[0058] The first inventive point of the present invention: The present invention designs a single intake pump body with a new flow channel structure. The pump body adopts the upper cylinder intake method. The intake passage of the upper cylinder changes the intake starting angle through a special U-shaped groove. There is a minimum value T2 for the distance between the U-shaped groove and the sliding vane groove. There is a new structure shunt channel with a variable cross-section on the partition plate. Through this shunt channel, a part of the refrigerant inhaled by the upper cylinder can be effectively transferred to the intake passage of the lower cylinder through this structure. The shunt channels of the upper and lower cylinders and the partition plate form a new flow channel structure. In this new flow channel structure, the center line of the shunt channel of the upper cylinder and the center line of the intake passage of the lower cylinder respectively form a coplanar line with the crankshaft center line, and the two planes intersect.

[0059] In some embodiments, within the projection plane of the joint end face of the intake passage 31 and the outer peripheral wall of the first cylinder 3, the first intake passage 33 is connected to the intake passage 31 and its projection within this projection plane is a trapezoidal structure. The top surface length, bottom surface length, and height of the trapezoid are a, b, and h respectively, and the cross-sectional area of the first intake passage is and / or,

[0060] The minimum distance between the first intake passage 33 and the first sliding vane groove 37 in the circumferential direction is T2, and 1mm ≤ T2 ≤ 2mm.

[0061] This is the preferred calculation method for the cross-sectional area of the first channel of the present invention. The area formed by the connection between the first air inlet channel and the air intake channel is the area of the air intake. Therefore, in order to increase the air intake volume, the present invention can start from the parameters a, b and h. By increasing their values, the air intake volume can be effectively increased. There is a minimum distance T2 between the first air inlet channel and the first vane groove, and 1mm≤T2≤2mm, which can prevent the distance from being too small to cause the first air inlet channel to be connected to the first vane groove and affect the air intake, as well as the structure of the first vane groove, so that the spring and the vane are exposed. It can also ensure that T2 is not too large and the starting angle of air intake is not too large to affect the air intake volume and the cooling capacity. That is, it can ensure that normal air intake is not affected and structures such as the vane spring are not exposed while effectively increasing the air intake volume and improving the cooling capacity.

[0062] Invention point 2 of the present invention: Adjust the U-shaped groove structure of the upper cylinder. The U-shaped groove is a hole with a certain depth. The hole formed by the intersection with the upper cylinder suction channel is the intake channel of the upper cylinder. The cross section of the upper cylinder intake channel is approximately The minimum distance between the U-shaped groove and the sliding plate groove is T2, 2mm≥T2≥1mm.

[0063] The cross section of the upper cylinder intake passage is an irregular circle. Figure 2 As shown in view A, in order to calculate the cross-sectional area, it can be viewed as a T-shape, so the cross-sectional area of the upper cylinder intake passage is Among them, a and b are related to the U-shaped groove depth d1, and h is related to the U-shaped groove radius.

[0064] In some embodiments, the first intake channel 33 extends from the axial end face of the first cylinder 3 that faces away from the partition 4 toward the axial end face of the first cylinder 3 that connects to the partition 4. The minimum axial distance between the first intake channel 33 and the partition 4 is greater than the minimum axial distance between the intake channel 31 and the partition 4. The axial depth of the first intake channel 33 is d1, which is less than the axial depth of the intake channel 31. This is a further preferred structural form of the first intake channel of the present invention, that is, the lower end of the first intake channel extends to a certain distance from the lower end of the intake channel, so that the distance portion can be used to connect with the first diversion channel, thereby effectively intake the second cylinder, preventing the first intake channel from connecting with the first diversion channel to cause blowby, and avoiding the situation where the two cylinders or either cylinder cannot normally take in air.

[0065] In some embodiments, the air intake passage 31 includes a first air intake passage and a second air intake passage that are sequentially connected in the air intake direction, and the aperture of the first air intake passage is larger than that of the second air intake passage to form a step at the junction therebetween. The length of the first air intake passage is L1, and the length of the second air intake passage is L2. The first intake passage 33 communicates with the second air intake passage, and the first diversion passage 32 also communicates with the second air intake passage. The air intake passage of the present invention is preferably arranged as two passages with a stepped structure, which enables the first air intake passage to be used for sealing connection with the intake pipe, and the second air intake passage to be used for communicating with the first intake passage, the first diversion passage, etc.

[0066] As Figure 3 shown, the air intake passage 31 of the upper cylinder (the first cylinder 3) is of a three-step type. The length of the first step is L1, which is mainly the sealing length for assembling with the suction pipe. L2 is the length of the second step, and the third step is the intake section of the upper cylinder. The first diversion passage 32 is opened on the surface that cooperates with the partition plate and is a circular hole with a diameter of d2 and the central line forms an angle C2 with the end face of the cylinder. The distance between the intersection point formed by the central line and the end face and the midpoint of the cylinder is M2. The diameter d2 of the first diversion passage 32 is less than or equal to the length L2 of the second step of the air intake passage 31 (to prevent damage to the sealing performance of the first step). The intake passage is the third step of the air intake passage formed by the intersection of the U-shaped groove and the air intake passage 31. The central lines of the first and second steps of the air intake passage coincide and form an angle A2 with the central line of the sliding vane groove. T is the shortest distance from the first diversion passage 32 to the inner wall surface of the first cylinder 3, and D is the inner radius of the first cylinder 3.

[0067] In some embodiments, a second sliding vane groove 56 is further provided on the second cylinder 5. The second diversion passage 41 can conduct the airflow in the direction close to the second sliding vane groove 56, so that in the projection plane in the axial direction and in the circumferential direction, the minimum distance between the second intake passage 51 and the second sliding vane groove 56 is less than the minimum distance between the first diversion passage 32 and the second sliding vane groove 56. The present invention also makes the second intake passage offset in the direction of the second sliding vane groove relative to the first diversion passage through the unique setting form of the second diversion passage, so as to be able to reduce the intake starting angle of the second cylinder, increase the intake volume of the second cylinder, and improve its refrigeration capacity; and it also avoids the narrow space caused by setting a U-shaped groove similar to that of the first cylinder to reduce the intake starting angle, avoids interference due to being too close to the second sliding vane groove, and also avoids interference with the second diversion passage, resulting in the exposure of structures such as springs and sliding vanes in the second sliding vane groove, thereby improving the operation stability and refrigeration performance of the second cylinder.

[0068] In some embodiments, the second shunt channel 41 includes a third shunt channel 411 and a fourth shunt channel 412 that are sequentially connected along the air flow direction. The fourth shunt channel 412 is connected between the third shunt channel 411 and the second intake channel 51, and within the projection plane of the axial end face where the first cylinder 3 is in contact with the partition 4. The included angle between the center line connecting the center of the third shunt channel 411 and the center of the first cylinder 3 and the center line of the first sliding vane groove 37 is A1, and the included angle between the center line connecting the center of the fourth shunt channel 412 and the center of the first cylinder 3 and the center line of the first sliding vane groove 37 is B1, where A1 > B1; when the included angle between the center line of the intake channel 31 and the center line of the first sliding vane groove 37 is A2, A1 = A2.

[0069] As Figure 6 shown, another form of the structural partition is provided here. The shunt channel is a through-channel with a diameter d3, and the included angles between the center lines of the holes at the upper and lower end faces are A and B respectively. This is an inclined channel. Except for the inconsistent shunt channel structure with Figure 2 the partition structure shown, the rest of the structures are all the same.

[0070] The present invention preferably sets the third shunt channel and the fourth shunt channel. The included angle B1 between the center line connecting the center of the fourth shunt channel and the center of the first cylinder and the center line of the first sliding vane groove is smaller than the included angle A1 between the center line connecting the third shunt channel and the center of the first cylinder and the center line of the first sliding vane groove. Thereby, the flow path can be effectively changed through the third shunt channel and the fourth shunt channel, so that the intake air towards the second cylinder can be inclined and offset towards the direction of the second sliding vane groove, effectively reducing the starting intake angle of the second cylinder, effectively advancing the starting time of the compressor to start sucking air, thereby effectively increasing the intake air volume, further effectively improving the refrigeration performance of the second cylinder, thereby improving the reliability, stability and service life of the compressor, and can effectively reduce the cost of the compressor without changing the compressor capacity, ensuring that the refrigeration capacity does not decrease; and by setting the shunt channel on the partition to reduce the starting intake angle, compared with the structure of opening a U-shaped groove on the second cylinder, there is no need to open redundant U-shaped grooves similar to the first cylinder in the narrow space of the second cylinder, thereby effectively preventing the intersection with the shunt channel from damaging the flow path, or damaging the structure in the second sliding vane groove, preventing the relative position of the spring in the sliding vane groove and the housing from being exposed, etc., which may affect the normal compression operation; thereby further effectively improving the operating stability and refrigeration performance of the second cylinder.

[0071] Inventive point 3: The central line of the air intake hole of the upper cylinder and the central line of the shunt channel are in the same plane, and this plane passes through the central line of the crankshaft. This plane intersects with the plane formed by the central line of the air intake hole of the lower cylinder and the central line of the crankshaft, and there is an included angle α between the two planes, that is, α = A1 - B1 (A1 = A2, B1 = B2) > 0°.

[0072] Since there is an included angle α between the two planes, and the included angle between the central line of the air intake hole of the lower cylinder and the sliding vane slot is smaller than the included angle between the central line of the air intake channel of the upper cylinder and the sliding vane slot, by this design, the starting angle of air intake of the lower cylinder is changed. And it can ensure that the relative position of the sliding vane spring of the upper cylinder and the housing is not exposed.

[0073] Inventive point 4: The new structure flow channel on the partition board of the present invention is composed of a through hole and a non-through hole. The central line of the non-through hole is coaxial with the central line of the shunt channel of the upper cylinder, and the central line of the through hole is coaxial with the central line of the air intake hole of the lower cylinder. The through hole and the non-through hole have the same radius, and are slightly larger than or equal to the shunt radius of the upper cylinder and the radius of the air intake channel of the lower cylinder, that is, d2 = d3 = d4, or d3 ≥ d2 + 0.1 mm, or d3 ≥ d4 + 0.1 mm. Or the new structure flow channel of the partition board is a channel with a variable cross-section.

[0074] The present invention only makes minor modifications to the internal structures of the cylinder and the partition board, and completes the structural design of changing the double-cylinder air intake to single-cylinder air intake on the premise of ensuring that the overall structure of the compressor does not change significantly, which can effectively reduce the later inspection time of the compressor.

[0075] The present invention provides a design idea for changing a double-cylinder to a single-cylinder. By adopting this design idea, the design difficulty can be effectively reduced, and the project time, manpower and material costs can be saved.

[0076] As Figure 7 shown, the figure is a schematic assembly diagram of the upper cylinder and the housing. It can be seen from the figure that the included angle between the center line of the sliding vane slot and the center line of the inlet is A2. At this time, the spring in the sliding vane slot in the figure is perfectly matched with the housing and is not exposed. If the angle A2 is adjusted (becomes smaller), it will cause the spring to be exposed, affecting the reliability of the compressor.

[0077] As Figure 5 shown, whether it is the central line of the first shunt channel 32 of the upper cylinder (the first cylinder 3), the second shunt channel 41 of the partition board 4, or the second air intake channel 51 of the lower cylinder (the second cylinder 5), they are all on the same line when viewed from the front, minimizing the flow resistance as much as possible. But in fact, the central line of the shunt channel of the upper cylinder and the central line of the sunken part of the second shunt channel 41 of the partition board 4 are in the same plane and coaxial, while the central line of the through hole part of the second shunt channel 41 and the central line of the second air intake channel 51 of the lower cylinder 5 are in the same plane and coaxial.

[0078] In some embodiments, the third flow dividing channel 411 is a counterbore extending from the axial end face where the partition plate 4 is connected to the first cylinder 3 towards the axial end face where the partition plate 4 is connected to the second cylinder 5, and the length of the counterbore along its axial direction is H2; the fourth flow dividing channel 412 is a through hole extending from the axial end face where the partition plate 4 is connected to the first cylinder 3 towards the axial end face where the partition plate 4 is connected to the second cylinder 5, and the length of the through hole along its axial direction is H1; and H1 > H2. The present invention further preferably sets the third flow dividing channel as a counterbore structure, which can be used to suck gas from the first flow dividing channel. However, the lower end of the third flow dividing structure is not opposite to the second intake channel of the second cylinder. Then, the fourth flow dividing channel in the form of a through hole is used to communicate with the third flow dividing channel, so as to introduce the gas in the third flow dividing channel and conduct it into the second intake channel to complete the intake of the second cylinder. H1 > H2 indicates that the axial length of the third flow dividing channel is less than the length of the fourth flow dividing channel.

[0079] As Figure 2 , a hole with a variable cross-section is formed on the end face of the partition plate 4 as the second flow dividing channel 41. The second flow dividing channel 41 is composed of a through hole with a diameter of d3 and a counterbore with a diameter of d3. It can be seen from the cross-sectional view that the included angle between the center line of the flow dividing channel and the two end faces is C1, the distances from the intersection point to the center of the partition plate are M1 and N. The end face where M1 is located is the contact surface between the partition plate and the upper cylinder, and the end face where N is located is the contact surface between the partition plate and the lower cylinder. The coordinate system is as shown in the figure. The included angle of the center line of the counterbore is A1, the included angle of the center line of the through hole is B1, the length of the through hole is H1, and the depth of the counterbore is H2.

[0080] In some embodiments, within the longitudinal section of the partition plate 4, the included angle between the central axis of the third flow dividing channel 411 and the axial end face of the partition plate 4 is C1, and the included angle between the central axis of the fourth flow dividing channel 412 and the axial end face of the partition plate 4 is also C1, and the range of C1 is (0, 90°) or (90°, 180°); the diameters of both the third flow dividing channel 411 and the fourth flow dividing channel 412 are d3. There is a non-zero included angle C1 between the third flow dividing channel of the present invention and the axial end face, so that the third flow dividing channel extends towards the center direction of the second cylinder (along the gas flow direction). By the same principle, the fourth flow dividing channel also extends towards the center direction of the second cylinder (along the gas flow direction), so that the second flow dividing channel on the partition plate can extend to communicate with the second intake channel at the inner circle of the second cylinder.

[0081] In some embodiments, the fourth shunt channel 412 is arranged closer to the center line of the partition plate 4 than the third shunt channel 411; the distance between the point where the central axis of the third shunt channel 411 meets the axial end face of the first cylinder 3 and the center line of the partition plate 4 is M1, and the distance between the point where the central axis of the fourth shunt channel 412 meets the axial end face of the second cylinder 5 and the center line of the partition plate 4 is N, and M1 > N. The fourth shunt channel of the present invention is closer to the center of the second cylinder than the third shunt channel, so that the gas can be guided towards the center of the second cylinder, and thus can be conducted to the second intake channel to complete the intake.

[0082] In some embodiments, the second intake channel 51 has a U-shaped groove structure. The second intake channel 51 extends from the axial end face on one side where the second cylinder 5 is connected to the partition plate 4 in a direction away from the partition plate 4. And in the projection plane of the axial end face where the second cylinder 5 is connected to the partition plate 4, the included angle B2 between the center line connecting the center of the second intake channel 51 and the center of the second cylinder 5 and the center line of the second sliding vane groove 56 is B2 = B1. The second intake channel of the present invention is also preferably of a U-shaped groove structure, and the included angle B2 between the center line connecting the center of the second intake channel and the center of the second cylinder and the center line of the second sliding vane groove is B2 = B1, which shows that the flow path can be effectively changed through the second shunt channel, so that the intake towards the second cylinder can be inclined and offset towards the direction of the second sliding vane groove, effectively reducing the starting intake angle of the second cylinder, effectively advancing the time when the compressor starts to intake, thereby effectively increasing the intake volume, further effectively improving the refrigeration performance of the second cylinder, and thus improving the reliability, stability and service life of the compressor. It can effectively reduce the cost of the compressor without changing the capacity of the compressor and ensure that the refrigeration capacity does not decrease.

[0083] In some embodiments, the included angle C3 between the central axis of the second intake channel 51 and the axial end face of the second cylinder 5 is C3, and the range of C3 is (0, 90°) or (90°, 180°); the aperture of the second intake channel 51 is d4; the cross-sectional area of the second intake channel 51 is In the longitudinal section, the distance between the point where the center line of the second intake channel 51 meets the axial end face of the partition plate 4 and the central axis of the second cylinder 5 is N2. This is the preferred structural form of the second intake channel of the present invention, that is, the intake is carried out in an inclined direction.

[0084] In some embodiments, the aperture of the first diversion channel 32 is d2; and d2 = d3 = d4 or d3 ≥ d2 + 0.1 mm or d3 ≥ d4 + 0.1 mm. Preferably in the present invention, A1 = A2, d2 = d3 or d3 ≥ d2 + 0.1, M1 = M2, C2 = C1.

[0085] As Figure 4 shown, the central line of the second air intake channel 51 of the lower cylinder forms an angle B2 with the central line of the sliding vane groove and an angle C3 with the end face. The distance between the intersection point on the end face and the midpoint of the cylinder is N2, and the diameter of the air intake channel is d4.

[0086] Preferably, B1 = B2, d3 = d4 or d3 ≥ d4 + 0.1 mm or d3 ≥ d2 + 0.1 mm, N = N2, C3 = C1. Then the cross-section of the air intake channel of the lower cylinder The cross-section of the upper cylinder is an irregular figure, and the cross-section S1 calculated after approximately regarding it as a T shape is only an approximate value. Therefore, S1 ≈ S2 here, and the difference between the two cannot be too large.

[0087] In some embodiments, the first diversion channel 32 is not communicated with the first air intake channel 33; an angle C2 is formed between the central axis of the first diversion channel 32 and the axial end face of the first cylinder 3, and the range of C2 is (0, 90°) or (90°, 180°), so that the first diversion channel 32 extends in a direction close to the central axis of the first cylinder 3;

[0088] The minimum distance between the first diversion channel 32 and the inner wall surface of the first cylinder 3 is T, T > 1 mm; and the distance between the point where the central line of the first diversion channel 32 is connected to the axial end face of the partition plate 4 and the central axis of the first cylinder 3 is M2; the inner circle radius of the first cylinder 3 is D.

[0089] There is a non-zero angle C2 between the first diversion channel of the present invention and the axial end face, so that the first diversion channel extends towards the center of the first cylinder (along the air flow direction), so that it can be communicated with the second air intake channel located at the inner circle of the second cylinder, which is beneficial to the air intake of the second cylinder. The minimum distance T between the first diversion channel and the inner wall surface of the first cylinder can ensure effective sealing and ensure the normal air intake of the second cylinder.

[0090] The present invention provides a new structure of partition plate and a pump body structure having the same. During the design process of the double-cylinder single-suction compressor, factors such as the exposure of the cylinder spring, the starting angle of suction, the size of the intake passage and the shunt passage are fully considered. The intake passage of the upper cylinder is stepped, and a shunt passage communicating with the suction cavity is opened at the second step. The shunt passage forms a certain angle with the cylinder plane. The diameter of the shunt passage depends on the length of the second step. The lower cylinder has only a cylindrical intake passage, and the diameter of the intake passage is the same as that of the shunt passage of the upper cylinder, and the angle formed with the cylinder surface is the same as that of the shunt passage of the upper cylinder (the same angle is to reduce the suction resistance). However, the angles formed by the shunt passages and the intake passages of the upper and lower cylinders with the sliding vane groove are different (in the upper cylinder, this is to ensure that the spring is not exposed relative to the housing, and in the lower cylinder, this is to change the starting angle of suction, thereby improving the refrigerating capacity and performance volume of the compressor). The center lines of the shunt passage of the upper cylinder and the intake passage of the lower cylinder intersect with the plane formed by the center line of the crankshaft respectively, that is, there is a certain angle difference between the two planes. Here, a new structure of shunt passage is started on the partition plate to receive the refrigerant shunted from the upper cylinder and shunt it into the lower cylinder. And the intake passage of the upper cylinder is a hole formed by the intersection of a U-shaped groove and the intake passage, and the cross-sectional area of the hole is the cross-sectional area of the intake passage. The U-shaped groove is equivalent to a counterbore drilled on the inner wall of the cylinder.

[0091] During the assembly process of the suction pipe and the cylinder, there is a concept of an effective sealing length K. This sealing length should be greater than K, so L1≥K, which can improve the insertion reliability between the intake passage 31 and the suction pipe, prevent the suction pipe from loosening at the intake passage 31, thereby avoiding the leakage of compressed gas. At the same time, the shortest distance from the first shunt passage 32 to the inner wall surface of the first cylinder 3 should meet the requirement of T≥1mm, which ensures the mechanical strength of the first cylinder 3 and the sealing effect of the first shunt passage 32.

[0092] In some embodiments, the range of C2 is 90°, 180°, and there is

[0093] The included angle C2 between the center line of the first shunt passage 32 of the upper cylinder and the end face of the cylinder can refer to the following calculation formula. The specific data is determined according to the data of M2, D and T. Generally, C2∈(90°-150°). Such a design considers mechanics, and the force received is the resultant force, which effectively improves the speed of the refrigerant entering the shunt passage, the cylinder compression efficiency, and improves the compression energy efficiency. The following formula can facilitate the calculation of C2 for cylinders of different specifications.

[0094]

[0095] The present invention also provides a compressor, which includes the pump body structure of the single-suction compressor described in any one of the preceding items.

[0096] For the detailed process, refer toFigure 5 After the attraction generated by the rotation of the crankshaft 1 drives the roller 8 to rotate and sucks the refrigerant from the external liquid distributor through the suction passage 31 of the upper cylinder (the first cylinder 3), part of the refrigerant enters the compression chamber of the upper cylinder through the first intake passage 33 of the upper cylinder, and another part of the refrigerant flows into the second shunt passage 41 of the partition plate 4 through the first shunt passage 32 of the first cylinder 3, and finally enters the compression chamber of the lower cylinder through the second intake passage 51 of the lower cylinder (the second cylinder 5). Thus, single suction of the double-cylinder compressor is achieved.

[0097] The rotary double-cylinder compressor arranges the suction passage 31 for single suction of the double cylinders in the first cylinder 3. In this way, no modification is needed to the outer shape of the partition plate of the original double-cylinder double-suction compressor. Only a second shunt passage 41 needs to be opened on the partition plate. Compared with the method of using the partition plate for air intake, it saves the design cost and manufacturing cost while ensuring reliability.

[0098] Both the first shunt passage 32 of the upper cylinder, the first intake passage 33 of the upper cylinder, the second shunt passage 41 of the partition plate 4, and the second intake passage 51 of the lower cylinder are composed of circular holes, and the surrounding surfaces are all smooth, without any other structures, so as to reduce the flow resistance loss as much as possible.

[0099] In an embodiment of the present invention, a double-cylinder single-suction compressor is provided. The specific structure of the rotary double-cylinder single-suction compressor refers to the above embodiment. Since the rotary double-cylinder single-suction compressor adopts all the technical solutions of the above all embodiments, it also has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated here one by one.

[0100] The present invention also provides an air conditioner, which includes the compressor described above. For the refrigeration equipment provided by the embodiments of the present invention, due to the use of the variable-frequency compressors of the above various embodiments, the manufacturing cost of the refrigeration equipment is reduced, and the operation of the refrigeration equipment is more stable, the refrigeration effect is more stable, the operation energy consumption is lower, and the service life is longer.

[0101] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and modifications can still be made, and these improvements and modifications should also be regarded as the protection scope of the present invention.

Claims

1. The pump body structure of a single-suction compressor, characterized in that: Including: A first cylinder (3), a partition plate (4) and a second cylinder (5), the partition plate (4) being located between the first cylinder (3) and the second cylinder (5); an air intake passage (31), a first air inlet passage (33), a first diversion passage (32) and a first sliding vane groove (37) are provided on the first cylinder (3), a second diversion passage (41) is provided on the partition plate (4), and a second air inlet passage (51) is provided on the second cylinder (5); The air intake passage (31) extends from the outer peripheral wall of the first cylinder (3) to a preset distance from the inner peripheral wall of the first cylinder (3), the first air inlet passage (33) is a groove structure opened on the inner peripheral wall of the first cylinder (3), one end of the first air inlet passage (33) communicates with the air intake passage (31) and the other end communicates with the inner peripheral wall of the first cylinder (3) for air intake; and in the circumferential direction, the minimum distance between the first air inlet passage (33) and the first sliding vane groove (37) is less than the minimum distance between the air intake passage (31) and the first sliding vane groove (37); The second air inlet passage (51) is a groove structure opened on the inner peripheral wall of the second cylinder (5), the first diversion passage (32) communicates with the air intake passage (31), and one end of the second diversion passage (41) communicates with the first diversion passage (32) and the other end communicates with the second air inlet passage (51) to intake air into the second cylinder (5) through the second air inlet passage (51).

2. The pump body structure of the single-intake compressor according to claim 1, characterized in that: The first air inlet passage (33) is a U-shaped groove structure, the included angle between the center line of the air intake passage (31) and the center line of the first sliding vane groove (37) is A2, and the included angle between the center line of the first air inlet passage (33) and the center line of the first sliding vane groove (37) is less than A2.

3. The pump body structure of the single-intake compressor according to claim 1, characterized in that: In the projection plane of the joint end face between the suction passage (31) and the outer peripheral wall of the first cylinder (3), the first intake passage (33) is joined to the suction passage (31) and has a trapezoidal structure in the projection in this projection plane. The lengths of the top surface, bottom surface, and height of the trapezoid are a, b, and h respectively, and the cross-sectional area of the first intake passage is and / or, The minimum distance between the first air inlet passage (33) and the first sliding vane groove (37) in the circumferential direction is T2, and 1mm ≤ T2 ≤ 2mm.

4. The pump body structure of the single-intake compressor according to claim 1, characterized in that: The first air inlet passage (33) extends from the axial one-side end face of the first cylinder (3) facing away from the partition plate (4) to the axial other-side end face where the first cylinder (3) is in contact with the partition plate (4), the minimum axial distance between the first air inlet passage (33) and the partition plate (4) is greater than the minimum axial distance between the air intake passage (31) and the partition plate (4); the axial depth of the first air inlet passage (33) is d1, which is less than the axial depth of the air intake passage (31).

5. The pump body structure of the single-intake compressor according to any one of claims 1-4, characterized in that: The intake passage (31) includes a first intake passage and a second intake passage that are connected in sequence along the intake direction, and the aperture of the first intake passage is larger than that of the second intake passage to form a step at the junction thereof. The length of the first intake passage is L1, the length of the second intake passage is L2, the first intake passage (33) is connected to the second intake passage, and the first diversion passage (32) is also connected to the second intake passage.

6. The pump body structure of the single-intake compressor according to any one of claims 1-4, characterized in that: A second sliding vane groove (56) is further provided on the second cylinder (5), and the second diversion passage (41) can conduct the airflow in a direction close to the second sliding vane groove (56), so that in the projection plane in the axial direction and in the circumferential direction, the minimum distance between the second intake passage (51) and the second sliding vane groove (56) is less than the minimum distance between the first diversion passage (32) and the second sliding vane groove (56).

7. The pump body structure of the single-intake compressor according to claim 6, characterized in that: The second diversion passage (41) includes a third diversion passage (411) and a fourth diversion passage (412) that are connected in sequence along the airflow direction. The fourth diversion passage (412) is connected between the third diversion passage (411) and the second intake passage (51). In the projection plane of the axial end face where the first cylinder (3) and the partition plate (4) are joined, the included angle between the center line connecting the center of the third diversion passage (411) and the center of the first cylinder (3) and the center line of the first sliding vane groove (37) is A1, and the included angle between the center line connecting the center of the fourth diversion passage (412) and the center of the first cylinder (3) and the center line of the first sliding vane groove (37) is B1, and A1 > B1; when the included angle between the center line of the intake passage (31) and the center line of the first sliding vane groove (37) is A2, A1 = A2.

8. The pump body structure of the single-intake compressor according to claim 7, characterized in that: The third diversion passage (411) is a counterbore extending from the axial end face where the partition plate (4) and the first cylinder (3) are joined to the axial end face where the partition plate (4) and the second cylinder (5) are joined, and the length of the counterbore along its axis is H2; the fourth diversion passage (412) is a through hole extending from the axial end face where the partition plate (4) and the first cylinder (3) are joined to the axial end face where the partition plate (4) and the second cylinder (5) are joined, and the length of the through hole along its axis is H1; and H1 > H2.

9. The pump body structure of the single-intake compressor according to claim 7, characterized in that: In the longitudinal section of the partition plate (4), the included angle between the central axis of the third shunt channel (411) and the axial end face of the partition plate (4) is C1, and the included angle between the central axis of the fourth shunt channel (412) and the axial end face of the partition plate (4) is also C1, and the range of C1 is (0, 90°) or (90°, 180°); the aperture diameters of the third shunt channel (411) and the fourth shunt channel (412) are both d3.

10. The pump body structure of the single-suction compressor according to claim 7, characterized in that: The fourth shunt channel (412) is arranged closer to the center line of the partition plate (4) than the third shunt channel (411); the distance between the point where the central axis of the third shunt channel (411) meets the axial end face of the first cylinder (3) and the center line of the partition plate (4) is M1, and the distance between the point where the central axis of the fourth shunt channel (412) meets the axial end face of the second cylinder (5) and the center line of the partition plate (4) is N, and M1 > N.

11. The pump body structure of the single-suction compressor according to claim 7, characterized in that: The second air inlet channel (51) has a U-shaped groove structure. The second air inlet channel (51) extends from the axial end face on one side where the second cylinder (5) is connected to the partition plate (4) in a direction away from the partition plate (4). And in the projection plane of the axial end face where the second cylinder (5) is connected to the partition plate (4), the included angle B2 between the center line connecting the center of the second air inlet channel (51) and the center of the second cylinder (5) and the center line of the second sliding vane groove (56) is B2 = B1.

12. The pump body structure of the single-suction compressor according to claim 9, characterized in that: The included angle between the central axis of the second intake passage (51) and the axial end face of the second cylinder (5) is C3, and the range of C3 is (0, 90°) or (90°, 180°); the aperture of the second intake passage (51) is d4; the cross-sectional area of the second intake passage (51) is In the longitudinal section, the distance between the point where the center line of the second intake passage (51) meets the axial end face of the partition plate (4) and the central axis of the second cylinder (5) is N2.

13. The pump body structure of the single-suction compressor according to claim 12, characterized in that: The aperture diameter of the first shunt channel (32) is d2; and there is d2 = d3 = d4 or d3 ≥ d2 + 0.1 mm or d3 ≥ d4 + 0.1 mm.

14. The pump body structure of the single-suction compressor according to claim 9, characterized in that: The first shunt channel (32) is not communicated with the first air inlet channel (33); an included angle C2 is formed between the central axis of the first shunt channel (32) and the axial end face of the first cylinder (3), and the range of C2 is (0, 90°) or (90°, 180°), so that the first shunt channel (32) extends in a direction close to the central axis of the first cylinder (3); The minimum distance between the first shunt channel (32) and the inner wall surface of the first cylinder (3) is T, T > 1 mm; and the distance between the point where the center line of the first shunt channel (32) meets the axial end face of the partition plate (4) and the central axis of the first cylinder (3) is M2; the inner circle radius of the first cylinder (3) is D.

15. The pump body structure of the single-suction compressor according to claim 14, characterized in that: The range of C2 is (90°, 180°), and there is 16. A compressor, characterized in that: The pump body structure of a single-suction compressor according to any one of claims 1-15.

17. An air conditioner, characterized in that: The compressor according to claim 16.

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