Pump assembly, compressor, and air conditioning device
By setting dual exhaust ports in the first-stage cylinder of the compressor and optimizing the guide cut parameters, the problem of unbalanced exhaust structure in the two-stage compression cylinder was solved, achieving more efficient exhaust and lower energy consumption compressor performance.
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- GUANGDONG MEIZHI COMPRESSOR
- Filing Date
- 2025-12-26
- Publication Date
- 2026-07-23
Smart Images
Figure CN2025146247_23072026_PF_FP_ABST
Abstract
Description
Pump components, compressors and air conditioning equipment
[0001] Related applications
[0002] This application claims priority to Chinese patent application No. 202510067108.0, filed on January 16, 2025, the entire contents of which are incorporated herein by reference. Technical Field
[0003] This application relates to the field of compressor technology, and in particular to a pump assembly, a compressor, and an air conditioning device. Background Technology
[0004] To achieve pressure distribution in a compressor, two-stage or multi-stage compression technology can be employed to improve volumetric efficiency. Different stages of the compressor cylinder have different exhaust structure designs. For example, in a two-stage compressor, the displacement of the first-stage cylinder determines the compressor's basic displacement, which is typically larger than that of the second-stage cylinder. Therefore, optimizing the exhaust structure of the first-stage cylinder can improve the compressor's exhaust efficiency and performance. Summary of the Invention
[0005] The main purpose of this application is to propose a pump body assembly, compressor and air conditioning equipment, which aims to optimize the exhaust structure design by adopting a dual exhaust port in the first-stage cylinder to reduce the exhaust flow rate and thereby improve the performance of the compressor.
[0006] To achieve the above objectives, the pump assembly proposed in this application includes:
[0007] A primary cylinder block includes a primary compression chamber, a first exhaust port and a second exhaust port spaced apart on the chamber wall and communicating with the primary compression chamber. The chamber wall of the primary compression chamber also has a first guide cut communicating with the edge of the first exhaust port and a second guide cut communicating with the edge of the second exhaust port.
[0008] A secondary cylinder block is located above the primary cylinder block, and the intake port of the secondary cylinder block communicates with the first exhaust port and the second exhaust port; wherein...
[0009] The radius of the first guide cut is R1, and the radius of the second guide cut is R2;
[0010] The diameter of the first vent is D1, and the diameter of the second vent is D2;
[0011] The first-stage cylinder has a rotation axis. In the axial cross-section of the first-stage cylinder, the first guide cut and the second guide cut have a farthest point and a closest point in the radial direction from the rotation axis, and the angles formed by the line connecting the farthest point and the closest point with the rotation axis are θ1 and θ2, respectively.
[0012] The distance from the radially furthest point of the first guide cut to the central axis of rotation is L1, and the distance from the radially furthest point of the second guide cut to the central axis of rotation is L2, where 0.28 ≤ (R1 * D1) 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.6.
[0013] In one embodiment, the first exhaust port is disposed on the cavity wall of the primary compression chamber above the second exhaust port.
[0014] In one embodiment, in the axial cross-section of the first-stage cylinder, the first exhaust port is disposed above the second exhaust port.
[0015] In one embodiment, the pump body assembly further includes a partition and a lower bearing. The partition is disposed between the primary cylinder and the secondary cylinder, and the lower bearing is disposed below the primary cylinder. The second exhaust port is connected to the air inlet of the secondary cylinder through the lower bearing. The first exhaust port is connected to the air inlet of the secondary cylinder through the partition.
[0016] In one embodiment, θ1 is 30°~75° and θ2 is 30°~75°.
[0017] In one embodiment, θ2 ≥ θ1.
[0018] In one embodiment, R2 ≥ R1.
[0019] In one embodiment, D2 ≥ D1.
[0020] In one embodiment, the first-stage cylinder block has a rotational axis; wherein the distance of the first guide cut from the radially furthest point of the rotational axis is less than or equal to the distance of the first exhaust port from the radially furthest point of the rotational axis; and the distance of the second guide cut from the radially furthest point of the rotational axis is less than or equal to the distance of the second exhaust port from the radially furthest point of the rotational axis.
[0021] This application also proposes a compressor, including a housing, a pump assembly disposed in the housing, and a motor assembly connected to the crankshaft of the pump assembly, wherein the pump assembly is the pump assembly described above.
[0022] In one embodiment, the compressor further includes an enthalpy-increasing component, and the pump body assembly is further provided with an enthalpy-increasing port, the enthalpy-increasing component being connected to the pump body assembly through the enthalpy-increasing port.
[0023] This application also proposes an air conditioning device, including the compressor described above.
[0024] The technical solution of this application optimizes the exhaust performance of the two exhaust ports by setting two exhaust ports (a first exhaust port and a second exhaust port) in the first-stage cylinder block and defining the ratio between the parameters related to the first exhaust port (R1, D1, θ1, L1) and the parameters related to the second exhaust port (R2, D2, θ2, L2). This allows for more balanced gas discharge and reduces losses due to back pressure differences (which can occur due to differences in the location and working environment of the two exhaust ports, preventing them from opening simultaneously). Back pressure also affects the compressor's volumetric efficiency (the ratio of the actual volume of gas discharged to the theoretical volume discharged; increased back pressure reduces the compressor's discharge volume as some gas is compressed back into the compression chamber during discharge, leading to decreased volumetric efficiency). Therefore, by optimizing the design and performance of the two exhaust ports, losses during the exhaust process can be reduced, improving the overall efficiency of the compressor. This helps reduce energy consumption, extend service life, and enhance the compressor's market competitiveness. Attached Figure Description
[0025] To more clearly illustrate the technical solutions in the embodiments or related technologies of this application, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.
[0026] Figure 1 is a structural schematic diagram of an embodiment of the pump body assembly provided in this application;
[0027] Figure 2 is a partial structural diagram of Figure 1;
[0028] Figure 3 is a schematic diagram of the cross-sectional structure at point AA in Figure 1.
[0029] Explanation of icon numbers:
[0030] 100, First-stage cylinder block; 110, First-stage compression chamber; 111, First exhaust port; 112, Second exhaust port; 113, First guide cut; 114, Second guide cut; 120, Sliding vane; 200, Second-stage cylinder block; 300, Partition plate; 400, Lower bearing; 500, Upper bearing; 600, Piston.
[0031] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings.
[0032] Specific Implementation
[0033] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.
[0034] It should be noted that if the embodiments of this application involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.
[0035] Furthermore, if the embodiments of this application involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution that simultaneously satisfies A and B. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed in this application.
[0036] A two-stage rotary compressor achieves two compression cycles within the housing. The displacement of the first-stage cylinder determines the compressor's basic displacement, which is typically larger than that of the second-stage cylinder. Therefore, the exhaust structure design of the second-stage cylinder differs from that of the first-stage cylinder. To ensure reasonable exhaust losses in each compression stage, the exhaust velocity of each stage should be similar to avoid significant bottlenecks during compressor operation and thus prevent impacting compressor performance.
[0037] This patent optimizes the exhaust structure design by employing a dual exhaust port in the first-stage cylinder to reduce the exhaust flow rate. Simultaneously, to ensure smooth participation of both exhaust ports in the exhaust process, each port is individually optimized to guarantee that the measured back pressures of the two exhaust ports are essentially equal, achieving synchronized exhaust and thus improving compressor performance.
[0038] This application proposes a pump body assembly for use in a rotary compressor, which can improve the compressor's exhaust efficiency and performance by optimizing the exhaust structure of the first-stage cylinder.
[0039] Understandably, the pump assembly refers to the overall structure of a compressor that includes components such as a compression cylinder, diaphragm, bearings, and silencer, used to compress gas.
[0040] Referring to Figures 1 to 3, in one embodiment of this application, the pump assembly includes a primary cylinder 100 and a secondary cylinder 200. A partition 300 is typically provided between the primary cylinder 100 and the secondary cylinder 200. To facilitate crankshaft fixation, an upper bearing 500 and a lower bearing 400 are provided vertically on the primary cylinder 100 and the secondary cylinder 200. In some designs, an upper muffler and a lower muffler are further provided. The piston 600 and the vane 120 within the cylinder body divide the cylinder cavity into an intake chamber and a compression chamber.
[0041] In one embodiment, the primary cylinder 100 is provided with a primary compression chamber 110, a first exhaust port 111 and a second exhaust port 112 spaced apart on the cavity wall of the primary compression chamber 110 and communicating with the primary compression chamber 110. The cavity wall of the primary compression chamber 110 is also provided with a first guide cut 113 communicating with the edge of the first exhaust port 111 and a second guide cut 114 communicating with the edge of the second exhaust port 112. The secondary cylinder 200 is provided above the primary cylinder 100, and the air inlet of the secondary cylinder 200 is communicating with the first exhaust port 111 and the second exhaust port 112.
[0042] Referring to Figure 2, the radius of the first guide cut 113 is R1, the radius of the second guide cut 114 is R2, the diameter of the first vent hole 111 is D1, and the diameter of the second vent hole 112 is D2.
[0043] The first-stage cylinder block 100 has a rotation axis. In the axial cross-section of the first-stage cylinder block 100, the first guide cut 113 and the second guide cut 114 have a farthest point and a closest point to the rotation axis in the radial direction, and the angles formed by the line connecting the farthest point and the closest point and the rotation axis are θ1 and θ2, respectively.
[0044] The distance from the farthest point of the first guide cut 113 to the central axis of rotation in the radial direction is L1, and the distance from the farthest point of the second guide cut 114 to the central axis of rotation in the radial direction is L2, satisfying the relationship 0.28≤(R1*D2 1*θ1*L1) / (R2*D2 2*θ2*L2)≤3.6.
[0045] It should be noted that the first-stage cylinder 100 is the cylinder in the two-stage compressor that first compresses the gas; the second-stage cylinder 200 is the cylinder in the two-stage compressor that further compresses the gas after the first-stage cylinder 100; the exhaust port is an opening on the cylinder for discharging the compressed gas; the guide cut is connected to the exhaust port and is a structure used to guide the gas to be discharged smoothly, usually designed as an arc-shaped cut; the rotation axis is the center line of rotation of the compressor cylinder.
[0046] The meanings of the parameters in the formula are as follows:
[0047] R1, R2: The radii of the first guide cut 113 and the second guide cut 114, which affect the smoothness of gas discharge and back pressure.
[0048] D1, D2: The diameters of the first exhaust port 111 and the second exhaust port 112, which determine the speed and flow rate of gas discharge.
[0049] θ1, θ2: The angles formed by the line connecting the farthest and nearest points of the first guide cut 113 and the second guide cut 114 with the rotation axis, reflecting the layout angle of the cuts on the cylinder block.
[0050] L1, L2: The distances between the first guide cut 113 and the second guide cut 114 in the radial direction from the farthest point of the rotation axis, which affect the path length of gas discharge.
[0051] Formula 0.28≤(R1*D1 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.6. This describes the relative relationship between the design parameters of two vent holes and their guide cuts, ensuring that both vent holes can smoothly participate in the venting process and achieve synchronous venting. Here, the diameters of the vent holes (D1 and D2) are 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 vent hole diameter on the gas flow rate, thus ensuring the optimized design of the venting structure.
[0052] Understandably, the first exhaust port 111 and the second exhaust port 112 are spaced apart because when the two exhaust ports are placed close together, the airflow between them may interfere with each other, resulting in poor exhaust or the generation of turbulence; the spaced arrangement makes the gas flow in the cylinder more uniform and reduces the energy loss caused by airflow turbulence.
[0053] The primary purpose of the first guide cut 113 and the second guide cut 114 is to optimize the gas discharge process and improve the performance and efficiency of the compressor. Understandably, the guide cut design provides a clear path for gas discharge, ensuring that after compression within the compression chamber, the gas can be smoothly discharged along the predetermined path, reducing gas eddies and turbulence. By optimizing the geometric parameters of the exhaust port, such as the cut radius, diameter, and included angle, the gas flow at the exhaust port can be made smoother, reducing local resistance and further lowering the exhaust velocity.
[0054] The first guide cut 113 and the second guide cut 114 can increase the gas discharge flow rate, enabling more gas to be discharged in a shorter time and improving its exhaust efficiency. This also allows for better regulation of the exhaust back pressure between the first exhaust port 111 and the second exhaust port 112, ensuring synchronous exhaust from both ports, thereby reducing flow velocity, exhaust losses, and improving compressor efficiency. Adjusting the parameters of the guide cuts (such as radius and angle) can make the exhaust process more stable and improve exhaust efficiency.
[0055] 0.28 is a lower limit to ensure that the design parameters of the two exhaust ports are not too disparate, thus preventing poor exhaust or excessive back pressure in one of the exhaust ports. 3.6 is an upper limit to prevent the design parameters of the two exhaust ports from being too similar, which could lead to mutual interference or imbalance during the exhaust process.
[0056] The specific values are related to the relative positions of the first exhaust port 111 and the second exhaust port 112. The first exhaust port 111 is located on the cavity wall of the primary compression chamber 110 above the second exhaust port 112; or the first exhaust port 111 and the second exhaust port 112 are axially spaced on the cavity wall of the primary compression chamber 110, etc., which will affect the design of the first exhaust port 111 and the second exhaust port 112.
[0057] Referring to Figure 2, in one embodiment, in the axial cross-section of the first-stage cylinder 100, the first exhaust port 111 is positioned above the second exhaust port 112. This axial cross-section is also the cross-section perpendicular to the radial direction of the first-stage cylinder 100. The first exhaust port 111 and the second exhaust port 112 are on a straight line. It is easy to understand that the first exhaust port 111 is closer to the second-stage cylinder 200 than the second exhaust port 112. This arrangement, compared to a conventional single exhaust port design, effectively increases the flow area of the first-stage exhaust, thereby reducing the exhaust velocity and minimizing losses. The refrigerant discharged downwards through the second exhaust port 112 and upwards through the first exhaust port 111 from the first-stage cylinder 100 is ultimately drawn into the second-stage cylinder, undergoes secondary compression, and is then discharged from the compressor. Therefore, the refrigerant discharged downwards experiences greater losses along the flow path. When the gas exits the compressor's compression chamber, it needs to overcome the back pressure at the exhaust port to flow out. If the back pressure is high, the gas will encounter greater resistance during its outflow, leading to increased flow resistance losses. This loss is converted into heat energy, causing the gas temperature to rise and reducing the efficiency of the compressor.
[0058] Thus, by adjusting the ratio in the formula, the exhaust performance of the two exhaust ports can be optimized, allowing them to discharge gas more evenly. This reduces flow resistance losses and volumetric efficiency losses caused by back pressure differences (back pressure also affects the compressor's volumetric efficiency; volumetric efficiency refers to the ratio of the actual volume of gas discharged by the compressor to the theoretical volume discharged. When back pressure increases, the compressor's discharge volume decreases because some gas is compressed back into the compression chamber during the discharge process, leading to a decrease in volumetric efficiency). Optimizing the design and performance of the two exhaust ports can reduce losses during the exhaust process and improve the overall efficiency of the compressor. This helps reduce energy consumption, extend service life, and enhance the compressor's market competitiveness.
[0059] The technical solution of this application optimizes the exhaust performance of the two exhaust ports by setting two exhaust ports, namely a first exhaust port 111 and a second exhaust port 112, in the first-stage cylinder block 100 and defining the ratio between the parameters (R1, D1, θ1, L1) related to the first exhaust port 111 and the parameters (R2, D2, θ2, L2) related to the second exhaust port 112. This allows for more balanced gas discharge and reduces losses due to back pressure differences (i.e., differences in back pressure caused by the different locations and working environments of the two exhaust ports, which can prevent them from opening simultaneously). Back pressure also affects the compressor's volumetric efficiency (the ratio of the actual volume of gas discharged to the theoretical volume discharged; when back pressure increases, the compressor's discharge volume decreases because some gas is compressed back into the compression chamber during discharge, leading to a decrease in volumetric efficiency). Therefore, by optimizing the design and performance of the two exhaust ports, losses during the exhaust process can be reduced, improving the overall efficiency of the compressor. This helps reduce energy consumption, extend service life, and enhance the compressor's market competitiveness.
[0060] In one embodiment, 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, and the lower bearing 400 is disposed below the primary cylinder 100. The second exhaust port 112 is connected to the air inlet of the secondary cylinder 200 through the lower bearing 400; the first exhaust port 111 is connected to the air inlet of the secondary cylinder 200 through the partition 300. Thus, by reasonably setting the size and position of the first exhaust port 111 and the second exhaust port 112, the gas can be evenly distributed to the air inlet of the secondary cylinder 200 during the exhaust process.
[0061] In one embodiment, the larger the cut angle and the closer the vertical angle is to the cavity wall, the smaller the optimization effect on the exhaust port. θ1 is limited to 30°~75°, and θ2 is limited to 30°~75°. In the above embodiment, if the exhaust port and corresponding exhaust structure design are unreasonable, the exhaust valve plate on one side may fail to open. The exhaust cut angle closer to the secondary cylinder block 200 is θ1, and the exhaust cut angle farther from the secondary cylinder is θ2, where θ2 ≥ θ1.
[0062] When gas is discharged from the first-stage cylinder 100, if the exhaust cut angle θ1 is less than 30°, the gas is more likely to form eddies and turbulence during the outflow process.
[0063] Setting θ2 ≥ θ1 allows the exhaust port furthest from the second-stage cylinder 200 (i.e., the port corresponding to θ2) to have a larger opening angle, facilitating smoother gas flow and reducing the formation of eddies and turbulence. A larger exhaust port angle (θ2) also provides a larger flow area for the gas during flow, thus reducing flow resistance. Furthermore, due to the pressure difference between the first-stage cylinder 100 and the second-stage cylinder 200, the exhaust port design must consider this difference. Setting θ2 ≥ θ1 allows the exhaust port furthest from the second-stage cylinder 200 to have greater flow capacity, thereby balancing the impact of back pressure differences on gas flow to some extent. Moreover, setting θ2 ≥ θ1 makes the exhaust port design more flexible, allowing the angle to be adjusted according to different operating conditions and gas types to meet different compression requirements.
[0064] The relationship between the radius R1 of the first guide cut 113 near the second stage cylinder block 200 and the radius R2 of the second guide cut 114 far from the second stage cylinder block 200, as well as the relationship between the diameters D1 and D2 of the two exhaust ports (first exhaust port 111 and second exhaust port 112) in the first stage cylinder block 100, are all based on considerations such as optimizing gas flow, improving exhaust efficiency, enhancing structural stability, and adapting to different working conditions.
[0065] Furthermore, the radius of the first guide cut 113 near the secondary cylinder block 200 is R1, and the radius of the second guide cut 114 away from the secondary cylinder block 200 is R2. The main function of the guide cuts is to guide the gas to be smoothly discharged from the compression chamber. When R2≥R1, the second guide cut 114 away from the secondary cylinder block 200 has a larger radius, which helps the gas to transition more smoothly during the outflow process and reduces the formation of eddies and turbulence.
[0066] Furthermore, in the first-stage cylinder block 100, the diameter of the first exhaust port 111, which is closer to the second-stage cylinder block 200, is D1, and the diameter of the second exhaust port 112, which is farther from the second-stage cylinder block 200, is D2, where D2 ≥ D1. The diameter of the exhaust port directly affects the exhaust flow rate. When D2 ≥ D1, the second exhaust port 112, which is farther from the second-stage cylinder block 200, has a larger diameter, which allows for a larger flow area for the gas during exhaust, thereby increasing the exhaust flow rate.
[0067] In one embodiment, the first-stage cylinder block 100 has a rotational axis; wherein the radial distance of the first guide cut 113 from the farthest point of the rotational axis is less than or equal to the radial distance of the first exhaust port 111 from the farthest point of the rotational axis; and the radial distance of the second guide cut 114 from the farthest point of the rotational axis is less than or equal to the radial distance of the second exhaust port 112 from the farthest point of the rotational axis. By defining the positions of the guide cuts and exhaust ports, a relatively stable flow state can be maintained during the gas outflow process. Furthermore, when the radial distances of the guide cuts and exhaust ports from the rotational axis are reasonably defined, the flow resistance encountered by the gas during the outflow process can be minimized.
[0068] This application also proposes a compressor, which includes a housing, a pump assembly disposed in the housing, and a motor assembly connected to the crankshaft of the pump assembly. The specific structure of the pump assembly is as described in the above embodiments. Since this compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, and will not be described in detail here. The compressor also includes an enthalpy-increasing component (not shown in the figure), and the pump assembly is also provided with an enthalpy-increasing port (not shown in the figure). The enthalpy-increasing component is connected to the pump assembly through the enthalpy-increasing port.
[0069] In one embodiment, the enthalpy injection port is located in the first-stage cylinder 100; in another embodiment, the enthalpy injection port is located in the baffle 300. The enthalpy-enhancing assembly typically includes components such as a refrigerant injection device and a control valve, used to inject refrigerant into the compression chamber of the pump assembly, thereby achieving the enthalpy-enhancing effect. During compression, by supplying gas into the compression chamber through the enthalpy-enhancing port, the pressure and temperature of the gas in the compression chamber can be increased, thereby improving the heating efficiency of the compressor.
[0070] This application also proposes an air conditioning device including the aforementioned compressor. The air conditioning device can be a household air conditioner, a commercial air conditioner, an automotive air conditioner, etc. It provides cooling and heating services to households to meet people's comfortable indoor temperature needs.
[0071] The above description is merely an exemplary embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the technical concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.
Claims
1. A pump body assembly, wherein, The pump assembly includes: A primary cylinder block includes a primary compression chamber, a first exhaust port and a second exhaust port spaced apart on the chamber wall and communicating with the primary compression chamber. The chamber wall of the primary compression chamber also has a first guide cut communicating with the edge of the first exhaust port and a second guide cut communicating with the edge of the second exhaust port. A secondary cylinder block is located above the primary cylinder block, and the intake port of the secondary cylinder block communicates with the first exhaust port and the second exhaust port; wherein... The radius of the first guide cut is R1, and the radius of the second guide cut is R2; The diameter of the first vent is D1, and the diameter of the second vent is D2; The first-stage cylinder has a rotation axis. In the axial cross-section of the first-stage cylinder, the first guide cut and the second guide cut have a farthest point and a closest point in the radial direction from the rotation axis, and the angles formed by the line connecting the farthest point and the closest point with the rotation axis are θ1 and θ2, respectively. The distance from the radially furthest point of the first guide cut to the central axis of rotation is L1, and the distance from the radially furthest point of the second guide cut to the central axis of rotation is L2, where 0.28 ≤ (R1 * D1) 2 *θ1*L1) / (R2*D2 2 *θ2*L2)≤3.
6.
2. The pump body assembly as claimed in claim 1, wherein, The first exhaust port is located on the cavity wall of the primary compression chamber above the second exhaust port.
3. The pump body assembly as claimed in claim 1 or 2, wherein, In the axial cross-section of the first-stage cylinder, the first exhaust port is located above the second exhaust port.
4. The pump body assembly as claimed in any one of claims 1 to 3, wherein, The pump assembly also includes a partition and a lower bearing. The partition is located between the first-stage cylinder and the second-stage cylinder, and the lower bearing is located below the first-stage cylinder. The second exhaust port is connected to the air inlet of the second-stage cylinder through the lower bearing. The first exhaust port is connected to the air inlet of the second-stage cylinder through the partition.
5. The pump body assembly as claimed in any one of claims 1 to 4, wherein, θ1 is 30°~75°, and θ2 is 30°~75°.
6. The pump body assembly as claimed in any one of claims 1 to 5, wherein, θ2≥θ1.
7. The pump body assembly as claimed in any one of claims 1 to 6, wherein, R2≥R1.
8. The pump body assembly as claimed in any one of claims 1 to 7, wherein, D2≥D1.
9. The pump body assembly as claimed in any one of claims 1 to 8, wherein, The first-stage cylinder block has a rotational axis; wherein, the distance of the first guide cut from the radially furthest point of the rotational axis is less than or equal to the distance of the first exhaust port from the radially furthest point of the rotational axis; the distance of the second guide cut from the radially furthest point of the rotational axis is less than or equal to the distance of the second exhaust port from the radially furthest point of the rotational axis.
10. A compressor, wherein, The compressor includes a housing, a pump assembly disposed in the housing, and a motor assembly connected to the crankshaft of the pump assembly, wherein the pump assembly is the pump assembly according to any one of claims 1 to 9.
11. The compressor of claim 10, wherein, The compressor also includes an enthalpy-increasing component, and the pump body assembly is further provided with an enthalpy-increasing port. The enthalpy-increasing component is connected to the pump body assembly through the enthalpy-increasing port.
12. An air conditioning device, wherein, The air conditioning equipment includes the compressor as described in claim 10 or 11.