Pump components, compressors and air conditioning equipment

Abstract

The present invention discloses a pump assembly, a compressor and an air conditioning device, and relates to the technical field of compressors, wherein the pump assembly comprises a primary cylinder body, the primary cylinder body is provided with a primary compression chamber, a first exhaust hole and a second exhaust hole which are arranged on the chamber wall of the primary compression chamber at intervals and communicated with the primary compression chamber, a first guide cutout which is communicated with the edge of the first exhaust hole and a second guide cutout which is communicated with the edge of the second exhaust hole are also provided on the chamber wall of the primary compression chamber, and a ratio between parameters (R1, D1, θ1, L1) related to the first exhaust hole and parameters (R2, D2, θ2, L2) related to the second exhaust hole is limited to 0.28≤(R1*D1 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.6. The two exhaust ports are optimized separately to ensure that the two exhaust back pressures in the measurement are basically equivalent to achieve synchronous exhaust, thereby improving the performance of the compressor.

Description

Technical Field

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

[0002] In order to achieve pressure ratio sharing of the compressor, two-stage or multi-stage compression technology can be used to improve volumetric efficiency.

[0003] Different levels of compression cylinders have different exhaust structure designs. For example, in a two-stage compressor, the displacement of the first-stage cylinder determines the basic displacement of the compressor, which is usually larger than the displacement of the second-stage cylinder. Therefore, optimizing the exhaust structure of the first-stage cylinder can improve the exhaust efficiency and performance of the compressor. Summary of the invention

[0004] The main purpose of the present invention is to propose a pump body assembly, a compressor and an air-conditioning device, aiming to optimize the exhaust structure design, adopt a double exhaust port method in the first-stage cylinder body, reduce the exhaust flow rate, and thus improve the performance of the compressor.

[0005] To achieve the above object, the pump body assembly proposed by the present invention comprises:

[0006] A primary cylinder body is provided with a primary compression chamber, a first exhaust hole and a second exhaust hole which are arranged on a chamber wall of the primary compression chamber at intervals and communicate with the primary compression chamber, and a first guide cutout which is communicated with an edge of the first exhaust hole and a second guide cutout which is communicated with an edge of the second exhaust hole are also provided on the chamber wall of the primary compression chamber; and

[0007] A secondary cylinder is disposed above the primary cylinder, and an air inlet of the secondary cylinder is connected to the first exhaust hole and the second exhaust hole; wherein,

[0008] The radius of the first guide cutout is R1, and the radius of the second guide cutout is R2;

[0009] The diameter of the first exhaust hole is D1, and the diameter of the second exhaust hole is D2;

[0010] The first-stage cylinder body has a central axis of rotation, and in an axial cross section of the first-stage cylinder body, the first guide cutout and the second guide cutout both have a farthest point and a closest point from the central axis of rotation in a radial direction, and angles formed between a line connecting the farthest point and the closest point and the central axis of rotation are θ1 and θ2 respectively;

[0011] The distance between the farthest point of the first guide cutout and the rotation center axis in the radial direction is L1, and the distance between the farthest point of the second guide cutout and the rotation center axis in the radial direction is L2, 0.28≤(R1*D1 2 *θ1*L1) / (R2*D2 2*θ2*L2)≤3.6.

[0012] In one embodiment, the first exhaust hole is arranged on the cavity wall of the primary compression cavity above the second exhaust hole.

[0013] In one embodiment, in an axial cross section of the primary cylinder, the first exhaust hole is disposed above the second exhaust hole.

[0014] In one embodiment, the pump body assembly also includes a partition and a lower bearing, the partition is arranged between the first-stage cylinder body and the second-stage cylinder body, the lower bearing is arranged below the first-stage cylinder body, the second exhaust hole is connected to the air inlet of the second-stage cylinder body through the lower bearing; the first exhaust hole is connected to the air inlet of the second-stage cylinder body through the partition.

[0015] In one embodiment, θ1 is 30° to 75°, and θ2 is 30° to 75°.

[0016] In one embodiment, θ2 ≥ θ1.

[0017] In one embodiment, R2 ≥ R1.

[0018] In one embodiment, D2 ≥ D1.

[0019] In one embodiment, the first-stage cylinder body has a rotation center axis; wherein, the distance between the first guide cutout and the farthest point of the rotation center axis in the radial direction is less than or equal to the distance between the first exhaust hole and the farthest point of the rotation center axis in the radial direction; the distance between the second guide cutout and the farthest point of the rotation center axis in the radial direction is less than or equal to the distance between the second exhaust hole and the farthest point of the rotation center axis in the radial direction.

[0020] The present invention further proposes a compressor, comprising a housing, a pump body assembly all arranged on the housing, and a motor assembly connected to a crankshaft of the pump body assembly, wherein the pump body assembly is the pump body assembly described above.

[0021] In one embodiment, the compressor further includes an enthalpy increasing component, and the pump body component is further provided with an enthalpy increasing port, and the enthalpy increasing component is connected to the pump body component via the enthalpy increasing port.

[0022] The present invention also provides an air conditioning device, comprising the compressor as described above.

[0023] The technical solution of the present invention can optimize the exhaust performance of the two exhaust holes by setting two exhaust holes, namely the first exhaust hole and the second exhaust hole, in the first-stage cylinder body, and limiting the ratio between the parameters related to the first exhaust hole (R1, D1, θ1, L1) and the parameters related to the second exhaust hole (R2, D2, θ2, L2), so that they can exhaust gas more evenly, reduce the flow resistance loss and volumetric efficiency loss caused by the difference in back pressure, that is, the difference in back pressure caused by the different positions and working environments of the two exhaust holes, which makes the two exhaust holes unable to open at the same time (back pressure also affects the volumetric efficiency of the compressor; volumetric efficiency refers to the ratio of the actual gas volume discharged by the compressor to the theoretical discharge volume. When the back pressure increases, the exhaust volume of the compressor will decrease, because part of the gas is compressed back into the compression chamber during the discharge process, resulting in a decrease in volumetric efficiency). In this way, by optimizing the design and performance of the two exhaust holes, the loss in the exhaust process can be reduced and the overall efficiency of the compressor can be improved. It helps to reduce energy consumption, extend service life and improve the market competitiveness of compressors. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0025] Figure 1 A schematic structural diagram of an embodiment of a pump assembly provided by the present invention;

[0026] Figure 2 for Figure 1 Schematic diagram of the local structure.

[0027] Figure 3 for Figure 1 Schematic diagram of the cross-sectional structure at AA in the middle.

[0028] Description of Figure Numbers:

[0029] 100, primary cylinder body; 110, primary compression chamber; 111, first exhaust hole; 112, second exhaust hole; 113, first guide cutout; 114, second guide cutout; 120, slide; 200, secondary cylinder body; 300, partition; 400, lower bearing; 500, upper bearing; 600, piston.

[0030] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0031] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0032] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0033] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features limited to "first" and "second" may explicitly or implicitly include at least one of the features. In addition, if "and / or" or "and / or" appears in the full text, its meaning includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or solutions that satisfy both A and B. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0034] The rotary compressor with two-stage cylinders realizes two compressions inside the shell. The displacement of the first-stage cylinder determines the basic displacement of the compressor, which is usually larger than the displacement of the second-stage cylinder. Therefore, the exhaust structure design of the second-stage cylinder is different from the exhaust design of the first-stage cylinder. In order to ensure that the exhaust loss of each stage of the compression cylinder is relatively reasonable, the exhaust flow rate of each stage should be similar, so that there will be no obvious bottleneck in the operation of the compressor, which will affect the performance of the compressor.

[0035] This patent optimizes the exhaust structure design and adopts a dual exhaust port method in the first-stage cylinder to reduce the exhaust flow rate. At the same time, in order to ensure that the two exhaust ports can smoothly participate in the exhaust process, the two exhaust ports are optimized separately to ensure that the two exhaust back pressures in the measurement are basically the same, so as to achieve synchronous exhaust and improve the performance of the compressor.

[0036] The present invention provides a pump body assembly, which is applied to a rotary compressor and can improve the exhaust efficiency and performance of the compressor by optimizing the exhaust structure of a first-stage cylinder.

[0037] It can be understood that the pump body assembly refers to the overall structure of the compressor including the compression cylinder, partition, bearing, muffler and other components, which is used to achieve gas compression.

[0038] See also Figures 1 to 3 In one embodiment of the present invention, the pump assembly includes a primary cylinder 100 and a secondary cylinder 200. A partition 300 is usually provided between the primary cylinder 100 and the secondary cylinder 200. In order to facilitate the fixing of the crankshaft, an upper bearing 500 and a lower bearing 400 are provided in the upper and lower directions of the primary cylinder 100 and the secondary cylinder 200. In some schemes, an upper muffler and a lower muffler are further provided. The piston 600 and the slide 120 in the cylinder separate the cavity of the cylinder into an air intake cavity and a compression cavity.

[0039] Specifically, the first-stage cylinder body 100 is provided with a first-stage compression chamber 110, a first exhaust hole 111 and a second exhaust hole 112 which are spaced apart on the wall of the first-stage compression chamber 110 and communicated with the first-stage compression chamber 110, and a first guide cutout 113 which is communicated with the edge of the first exhaust hole 111 and a second guide cutout 114 which is communicated with the edge of the second exhaust hole 112 are also provided on the wall of the first-stage compression chamber 110; the second-stage cylinder body 200 is provided above the first-stage cylinder body 100, and an air inlet of the second-stage cylinder body 200 is communicated with the first exhaust hole 111 and the second exhaust hole 112.

[0040] Reference Figure 2 , wherein the radius of the first guide cutout 113 is R1, and the radius of the second guide cutout 114 is R2; the diameter of the first exhaust hole 111 is D1, and the diameter of the second exhaust hole 112 is D2;

[0041] The first-stage cylinder body 100 has a central axis of rotation. In the axial cross section of the first-stage cylinder body 100, the first guide cutout 113 and the second guide cutout 114 have a farthest point and a closest point from the central axis of rotation in the radial direction, and the angles formed by the line between the farthest point and the closest point and the central axis of rotation are θ1 and θ2 respectively.

[0042] The first guide cutout 113 is at a radial distance L1 from the rotation center axis, and the second guide cutout 114 is at a radial distance L2 from the rotation center axis, satisfying the relationship 0.28≤(R1*D2 1*θ1*L1) / (R2*D2 2*θ2*L2)≤3.6.

[0043] It should be noted that the first-stage cylinder 100 is the cylinder that first compresses gas in the two-stage compressor; the second-stage cylinder 200 is the cylinder that further compresses gas after the first-stage cylinder 100 in the two-stage compressor; the exhaust hole is an opening on the cylinder for discharging compressed gas; the guide cut is connected to the exhaust hole, and is a structure for guiding the smooth discharge of gas, and is usually designed as an arc-shaped cut; rotation center axis: the center line of rotation of the compressor cylinder.

[0044] The meaning of each parameter in the formula is as follows:

[0045] R1, R2: the radius of the first guide cutout 113 and the second guide cutout 114, which affect the fluidity and back pressure of gas discharge.

[0046] D1, D2: diameters of the first exhaust hole 111 and the second exhaust hole 112, which determine the speed and flow rate of gas exhaust.

[0047] θ1, θ2: the angles formed by the lines connecting the farthest point and the nearest point of the first guide cutout 113 and the second guide cutout 114 and the central axis of rotation, reflecting the layout angle of the cutouts on the cylinder body.

[0048] L1, L2: the distances between the farthest points of the first guide cutout 113 and the second guide cutout 114 from the central axis of rotation in the radial direction, which affect the path length of gas discharge.

[0049] Formula 0.28≤(R1*D1 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.6. It is used to describe the relative relationship between the design parameters of the two exhaust holes and their guide cutouts to ensure that the two exhaust holes can smoothly participate in the exhaust process and achieve synchronous exhaust. Here, the diameter of the exhaust holes (D1 and D2) is directly related to the gas flow rate, because the flow rate is usually proportional to the area of ​​the pipe or orifice, and the area is proportional to the square of the diameter. This reflects the influence of the exhaust hole diameter on the gas flow rate, thereby ensuring the optimal design of the exhaust structure.

[0050] It can be understood that the first exhaust hole 111 and the second exhaust hole 112 are arranged at intervals because when the two exhaust holes are arranged closely together, the airflows therebetween may interfere with each other, resulting in poor exhaust or generation of vortices; the interval arrangement makes the gas flow in the cylinder more uniform, reducing the energy loss caused by airflow turbulence.

[0051] The purpose of setting the first guide cutout 113 and the second guide cutout 114 is mainly to optimize the gas discharge process and improve the performance and efficiency of the compressor; it can be understood that the design of the guide cutout provides a clear path for gas discharge, ensuring that the gas can be discharged smoothly along the preset path after being compressed in the compression chamber, reducing gas eddy currents and turbulence. By optimizing the geometric parameters of the exhaust hole, such as the cutout radius, diameter, angle, etc., the gas can flow more smoothly at the exhaust hole, reduce local resistance, and further reduce the exhaust flow rate.

[0052] The first guide cutout 113 and the second guide cutout 114 can increase the exhaust flow of the gas, and can exhaust more gas in a shorter time, thereby improving its exhaust efficiency; thus, the exhaust back pressure between the first exhaust hole 111 and the second exhaust hole 112 can be better adjusted to ensure that the first exhaust hole 111 and the second exhaust hole 112 can exhaust synchronously, thereby reducing the flow rate, thereby reducing the exhaust loss and improving the efficiency of the compressor. By adjusting the parameters of the guide cutout (such as radius, angle, etc.), the exhaust process can be made more stable and the exhaust efficiency can be improved.

[0053] 0.28 is a lower limit value, which ensures that the design parameter combination of the two exhaust holes is not too different, so as to avoid poor exhaust or high back pressure of one of the exhaust holes. 3.6 is an upper limit value, which prevents the design parameter combination of the two exhaust holes from being too close, resulting in mutual interference or imbalance in the exhaust process.

[0054] The specific value is related to the relative position of the first exhaust hole 111 and the second exhaust hole 112. The first exhaust hole 111 is arranged above the second exhaust hole 112 on the wall of the first-stage compression chamber 110; or, the first exhaust hole 111 and the second exhaust hole 112 are axially spaced on the wall of the first-stage compression chamber 110, etc., which will affect the design of the first exhaust hole 111 and the second exhaust hole 112.

[0055] Reference Figure 2Specifically, in one embodiment, in the axial cross section of the primary cylinder 100, the first exhaust hole 111 is arranged above the second exhaust hole 112, and the axial cross section is also the cross section perpendicular to the radial cross section of the primary cylinder 100; the first exhaust hole 111 and the second exhaust hole 112 are on a straight line; it is not difficult to understand that the first exhaust hole 111 is closer to the secondary cylinder 200 than the second exhaust hole 112, so that the two exhaust holes can effectively increase the flow area of ​​the primary exhaust compared to the conventional single exhaust hole solution, thereby reducing the exhaust flow rate and reducing the loss. The refrigerant discharged downward through the second exhaust hole 112 and discharged upward through the first exhaust hole 111 of the primary cylinder 100 will eventually be sucked into the secondary cylinder, and discharged from the compressor after secondary compression. Therefore, the refrigerant discharged downward will have a greater loss along the way; when the gas is discharged from the compression chamber of the compressor, it needs to overcome the back pressure at the exhaust hole to flow out. If the back pressure is high, the gas will be subject to greater resistance during the outflow process, resulting in an increase in flow resistance loss. This loss is converted into heat energy, which increases the temperature of the gas and reduces the efficiency of the compressor.

[0056] In this way, by adjusting the ratio of the formula, the exhaust performance of the two exhaust holes can be optimized, so that they can exhaust gas more evenly, reducing the flow resistance loss and volumetric efficiency loss caused by the back pressure difference (back pressure also affects the volumetric efficiency of the compressor; volumetric efficiency refers to the ratio of the actual gas volume discharged by the compressor to the theoretical discharge volume. When the back pressure increases, the exhaust volume of the compressor will decrease, because part of the gas is compressed back into the compression chamber during the discharge process, resulting in a decrease in volumetric efficiency). Optimizing the design and performance of the two exhaust holes can reduce the loss in the exhaust process and improve the overall efficiency of the compressor. This helps to reduce energy consumption, extend service life and improve the market competitiveness of the compressor.

[0057] The technical solution of the present invention can optimize the exhaust performance of the two exhaust holes by setting two exhaust holes, namely the first exhaust hole 111 and the second exhaust hole 112, in the first-stage cylinder 100, and limiting the ratio between the parameters (R1, D1, θ1, L1) related to the first exhaust hole 111 and the parameters (R2, D2, θ2, L2) related to the second exhaust hole 112, so that they can exhaust gas more evenly, reduce the flow resistance loss and volumetric efficiency loss caused by the difference in back pressure, that is, the difference in the back pressure caused by the different positions and working environments of the two exhaust holes, which makes the two exhaust holes unable to open at the same time (back pressure also affects the volumetric efficiency of the compressor; volumetric efficiency refers to the ratio of the actual gas volume discharged by the compressor to the theoretical discharge volume. When the back pressure increases, the exhaust volume of the compressor will decrease, because part of the gas is compressed back into the compression chamber during the discharge process, resulting in a decrease in volumetric efficiency). In this way, by optimizing the design and performance of the two exhaust holes, the loss in the exhaust process can be reduced and the overall efficiency of the compressor can be improved. It helps to reduce energy consumption, extend service life and improve the market competitiveness of the compressor.

[0058] Specifically, the pump assembly further includes a partition 300 and a lower bearing 400. The partition 300 is disposed between the primary cylinder 100 and the secondary cylinder 200. The lower bearing 400 is disposed below the primary cylinder 100. The second exhaust hole 112 is communicated with the air inlet of the secondary cylinder 200 through the lower bearing 400. The first exhaust hole 111 is communicated with the air inlet of the secondary cylinder 200 through the partition 300. In this way, by reasonably setting the size and position of the first exhaust hole 111 and the second exhaust hole 112, the gas can be evenly distributed to the air inlet of the secondary cylinder 200 during the exhaust process.

[0059] Specifically, the larger the cut angle is, the closer the vertical angle is to the cavity wall, and the smaller the optimization effect on the exhaust hole is. θ1 is limited to 30°~75°, and θ2 is limited to 30°~75°. In the above embodiment, if the exhaust hole and the corresponding exhaust structure are not designed properly, the exhaust valve sheet on one side cannot be opened. The exhaust cut angle close to the secondary cylinder body 200 is θ1, and the exhaust cut angle away from the secondary cylinder is θ2, and θ2≥θ1.

[0060] When the gas is discharged from the primary cylinder 100, if the exhaust cutout angle θ1 is less than 30°, the gas is more likely to form eddies and turbulence during the outflow process.

[0061] The setting of θ2≥θ1 can make the exhaust cutout far away from the secondary cylinder 200 (i.e., the cutout corresponding to θ2) have a larger opening angle, which helps the gas to flow out more smoothly and reduce the formation of vortices and turbulence; a larger exhaust cutout angle (θ2) can make the gas have a larger flow area during the outflow process, thereby reducing the flow resistance. In addition, due to the difference in pressure between the primary cylinder 100 and the secondary cylinder 200, the design of the exhaust cutout needs to take this difference into account. The setting of θ2≥θ1 can make the exhaust cutout far away from the secondary cylinder 200 have a greater flow capacity, thereby balancing the effect of the back pressure difference on the gas flow to a certain extent. In addition, the setting of θ2≥θ1 makes the design of the exhaust cutout more flexible, and the angle of the exhaust cutout can be adjusted according to different working conditions and gas types to meet different compression requirements.

[0062] The relationship between the radius R1 of the first guide cutout 113 close to the secondary cylinder body 200 and the radius R2 of the second guide cutout 114 far from the secondary cylinder body 200, as well as the relationship between the diameters D1 and D2 of the two exhaust holes (the first exhaust hole 111 and the second exhaust hole 112) in the primary cylinder body 100, are all based on considerations such as optimizing gas flow, improving exhaust efficiency, enhancing structural stability and adapting to different working conditions.

[0063] Furthermore, the radius of the first guide cutout 113 close to the secondary cylinder 200 is R1, and the radius of the second guide cutout 114 far from the secondary cylinder 200 is R2. The main function of the guide cutout is to guide the gas to be discharged smoothly from the compression chamber. When R2≥R1, the second guide cutout 114 far from the secondary cylinder 200 has a larger radius, which helps the gas to transition more smoothly during the outflow process and reduce the formation of vortices and turbulence.

[0064] Furthermore, of the two exhaust holes in the primary cylinder 100, the diameter of the first exhaust hole 111 close to the secondary cylinder 200 is D1, and the diameter of the second exhaust hole 112 far from the secondary cylinder 200 is D2, and D2≥D1. The diameter of the exhaust hole directly affects the exhaust flow rate of the gas. When D2≥D1, the second exhaust hole 112 far from the secondary cylinder 200 has a larger diameter, which can make the gas have a larger flow area during the exhaust process, thereby increasing the exhaust flow rate.

[0065] Specifically, the first-stage cylinder body 100 has a central axis of rotation; wherein the distance of the first guide cutout 113 from the farthest point of the central axis of rotation in the radial direction is less than or equal to the distance of the first exhaust hole 111 from the farthest point of the central axis of rotation in the radial direction; the distance of the second guide cutout 114 from the farthest point of the central axis of rotation in the radial direction is less than or equal to the distance of the second exhaust hole 112 from the farthest point of the central axis of rotation in the radial direction. By limiting the positions of the guide cutout and the exhaust hole, the gas can maintain a relatively stable flow state during the outflow process. Secondly, when the distance of the guide cutout and the exhaust hole from the central axis of rotation in the radial direction is reasonably limited, it can ensure that the flow resistance encountered by the gas during the outflow process is minimized.

[0066] The present invention also proposes a compressor, which includes a housing, a pump assembly all arranged on the housing, and a motor assembly connected to the crankshaft of the pump assembly. The specific structure of the pump assembly refers to the above embodiment. Since the compressor adopts all the technical solutions of all the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be repeated here. Among them, the compressor also includes an enthalpy increase component (not shown in the figure), and the pump assembly is also provided with an enthalpy increase port (not shown in the figure), and the enthalpy increase component is connected to the pump assembly through the enthalpy increase port.

[0067] In one embodiment, the enthalpy injection port is arranged on the primary cylinder 100; in one embodiment, the enthalpy injection port is arranged on the partition 300; the enthalpy increasing component generally includes components such as a refrigerant injection device and a control valve, which are used to inject the refrigerant into the compression chamber of the pump body component, thereby achieving the enthalpy increasing effect. During the compression process, the pressure and temperature of the gas in the compression chamber can be increased by replenishing gas into the compression chamber through the enthalpy increasing port, thereby improving the heating efficiency of the compressor.

[0068] The present invention also provides an air conditioning device, which includes the above compressor. The air conditioning device can be a household air conditioner, a commercial air conditioner, a car air conditioner, etc. It provides cooling and heating services for families to meet people's demand for comfortable indoor temperature.

[0069] The above description is only an exemplary embodiment of the present invention, and does not limit the patent scope of the present invention. All equivalent structural changes made by using the contents of the present invention specification and drawings under the technical concept of the present invention, or directly / indirectly applied in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A pump assembly, characterized in that: include: A primary cylinder body is provided with a primary compression chamber, a first exhaust hole and a second exhaust hole which are arranged on the chamber wall of the primary compression chamber at intervals and communicated with the primary compression chamber, and a first guide cutout which is communicated with the edge of the first exhaust hole and a second guide cutout which is communicated with the edge of the second exhaust hole are also provided on the chamber wall of the primary compression chamber; and A secondary cylinder is disposed above the primary cylinder, and an air inlet of the secondary cylinder is connected to the first exhaust hole and the second exhaust hole; wherein, The radius of the first guide cutout is R1, and the radius of the second guide cutout is R2; The diameter of the first exhaust hole is D1, and the diameter of the second exhaust hole is D2; The first-stage cylinder body has a central axis of rotation, and in an axial cross section of the first-stage cylinder body, the first guide cutout and the second guide cutout both have a farthest point and a closest point from the central axis of rotation in a radial direction, and angles formed between a line connecting the farthest point and the closest point and the central axis of rotation are θ1 and θ2 respectively; The distance between the farthest point of the first guide cutout and the rotation center axis in the radial direction is L1, and the distance between the farthest point of the second guide cutout and the rotation center axis in the radial direction is L2, 0.28≤(R1*D1 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.

6.

2. The pump assembly according to claim 1, characterized in that: The first exhaust hole is arranged on the cavity wall of the primary compression cavity above the second exhaust hole.

3. The pump assembly according to claim 2, characterized in that: In an axial cross section of the primary cylinder, the first exhaust hole is arranged above the second exhaust hole.

4. The pump assembly according to claim 1, characterized in that: The pump body assembly also includes a partition and a lower bearing, the partition is arranged between the first-stage cylinder body and the second-stage cylinder body, the lower bearing is arranged below the first-stage cylinder body, the second exhaust hole is connected to the air inlet of the second-stage cylinder body through the lower bearing; the first exhaust hole is connected to the air inlet of the second-stage cylinder body through the partition.

5. The pump assembly according to claim 1, characterized in that: θ1 is 30°~75°, and θ2 is 30°~75°.

6. The pump assembly according to claim 1, characterized in that: θ2≥θ1.

7. The pump assembly according to claim 1, characterized in that: R2≥R1.

8. The pump assembly according to claim 1, characterized in that: D2≥D1.

9. The pump assembly according to claim 1, characterized in that: The first-stage cylinder body has a central axis of rotation; wherein the distance between the first guide cutout and the farthest point of the central axis of rotation in the radial direction is less than or equal to the distance between the first exhaust hole and the farthest point of the central axis of rotation in the radial direction; the distance between the second guide cutout and the farthest point of the central axis of rotation in the radial direction is less than or equal to the distance between the second exhaust hole and the farthest point of the central axis of rotation in the radial direction.

10. A compressor, characterized in that: It comprises a housing, a pump body assembly arranged on the housing, and a motor assembly connected to a crankshaft of the pump body assembly, wherein the pump body assembly is the pump body assembly according to any one of claims 1 to 9.

11. The compressor according to claim 10, characterized in that The compressor further comprises an enthalpy increasing component, and the pump body component is further provided with an enthalpy increasing port, and the enthalpy increasing component is connected to the pump body component via the enthalpy increasing port.

12. An air conditioning device, characterized in that: Comprising a compressor as claimed in claim 10 or 11.

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