Pump body assembly flow guide structure, compressor and air conditioner

Abstract

The invention provides a pump body assembly flow guide structure, a compressor and an air conditioner. The pump body assembly flow guide structure comprises a first support and a flow guide assembly. The first support is installed between the pump body assembly and the motor, and a circulation groove is formed in the first support and used for guiding a working medium discharged by the pump body assembly; the motor is provided with a first cavity close to the pump body assembly and a second cavity away from the pump body assembly, the flow guide assembly is installed on the first support and located in the first cavity, the flow guide assembly and a rotating part of the motor are relatively static, and the flow guide assembly guides a working medium from the circulation groove to enable the working medium to form rotational flow in the first cavity; and guiding to the second cavity. In the invention, the flow guide assembly and the rotating part of the motor are relatively static, so that extra energy loss caused by the rotating part can be effectively avoided, and the flow guide assembly can effectively guide the working medium from the circulating groove.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically relating to a pump body assembly flow guiding structure, a compressor, and an air conditioner. Background Technology

[0002] As scroll compressors evolve towards higher frequencies and larger displacements, the high-speed discharge of the refrigerant and lubricating oil mixture exacerbates lubricant loss, leading to decreased system efficiency and reliability. Therefore, incorporating a highly efficient oil-gas separation structure in the compressor's exhaust path is crucial. Currently, common oil-gas separation technologies struggle to effectively guide and constrain the airflow path to ensure adequate separation without introducing significant additional power consumption or flow resistance.

[0003] Existing structures employ rotating guide vanes or oil-blocking structures, which, while enhancing turbulence through agitation, inevitably generate continuous parasitic power consumption due to oil churning as rotating components. This directly increases the compressor's energy loss, contradicting the goal of high energy efficiency. Other existing structures utilize stationary guide sheet metal parts or alter the stator structure. While these can avoid rotational power consumption, their ability to guide and constrain airflow is limited. Some high-speed airflow may still not fully participate in the separation process along the intended path and instead short-circuit into the exhaust pipe, resulting in low separation efficiency. Adding filters or other structures to further improve separation significantly increases exhaust flow resistance, also causing energy loss. Therefore, existing gas-liquid separation structures cannot achieve a solution that, while remaining stationary and completely avoiding rotational power consumption, effectively guides and strictly constrains the flow path of the mixed working fluid to ensure a thorough separation process, all without introducing significant flow resistance. Summary of the Invention

[0004] This invention provides a pump body assembly flow guiding structure, a compressor, and an air conditioner, which can solve the technical problems of existing gas-liquid separation structures generating rotational power consumption and failing to effectively constrain the flow path of the mixed working fluid.

[0005] This invention provides a flow guiding structure for a pump body assembly, including a first support and a flow guiding assembly; The first bracket is installed between the pump body assembly and the motor, and a flow groove is provided on the first bracket for guiding the working fluid discharged by the pump body assembly. The motor has a first cavity near the pump body assembly and a second cavity away from the pump body assembly. The flow guiding assembly is mounted on the first bracket and located in the first cavity. The flow guiding assembly is stationary relative to the rotating part of the motor. The flow guiding assembly guides the working fluid from the flow channel, causing the working fluid to form a swirling flow in the first cavity and then guide it to the second cavity.

[0006] In some embodiments, the flow channel is formed on the outer peripheral wall of the first support, and the flow channel extends obliquely relative to the rotation axis of the motor, so that the working fluid passing through the flow channel obtains a tangential velocity component. The direction of the tangential velocity component is the same as the rotation direction of the swirling flow in the first cavity, so as to change the movement direction of the working fluid and complete the first gas-liquid separation.

[0007] In some embodiments, the flow guiding assembly includes a plurality of flow guiding blades, which are spaced apart around the rotation axis of the motor and form a flow channel for guiding the working fluid to generate swirling flow, so that the working fluid rotates circumferentially to complete the second gas-liquid separation.

[0008] In some embodiments, the guide vanes are inclined relative to the radial plane of the rotation axis, and the guide vanes guide the working fluid to generate a tangential velocity so that the working fluid forms a swirling flow in the first cavity.

[0009] In some embodiments, the flow guiding assembly further includes an annular axial guide vane mounted at the bottom of the first support, the axial guide vane having an annular flow channel surrounding the axis of rotation, and a plurality of the flow guiding blades disposed within the annular flow channel.

[0010] In some embodiments, the axial guide vane includes an inner guide ring and an outer guide ring arranged radially opposite each other; the inner guide ring and the outer guide ring are mounted on the bottom of the first bracket, the inner guide ring and the outer guide ring are coaxially arranged around the rotation axis, the inner guide ring and the outer guide ring define the annular flow channel, and the two sides of each guide vane are respectively connected to the outer wall surface of the inner guide ring and the inner wall surface of the outer guide ring.

[0011] In some embodiments, the inner wall of the inner guide ring is provided with an annular balance cover, the balance cover is provided with a shaft hole, the crankshaft of the pump body assembly passes through the shaft hole and is driven and connected to the motor, and an annular balance cavity surrounding the rotation axis is formed between the inner guide ring and the balance cover.

[0012] In some embodiments, an exhaust pipe is also included, the inlet of which is located in the flow guiding assembly and communicates with the first cavity, the outlet of which is communicated with the external environment, the centerline of the inlet of which is perpendicular to the rotation direction of the swirling flow in the first cavity, the working fluid in the first cavity flows into the stator tangential gap of the motor and is guided from top to bottom to the second cavity, the working fluid in the second cavity flows into the stator-rotor gap of the motor and flows from bottom to top into the inlet of the exhaust pipe, so that the working fluid is discharged from the exhaust pipe.

[0013] In some embodiments, a housing is also included, in which the pump body assembly, the first bracket, the flow guide assembly, and the motor are arranged sequentially from top to bottom in the housing. The crankshaft of the pump body assembly passes through the flow guide assembly and the first bracket in sequence and is drivenly connected to the motor. The inner wall surface of the housing and the outer end face of the motor form the first cavity and the second cavity, which are spaced apart along the axial direction of the motor shaft.

[0014] A compressor includes a pump body assembly flow guide structure, wherein the pump body assembly flow guide structure is the aforementioned pump body assembly flow guide structure.

[0015] An air conditioner includes a compressor, said compressor being the compressor described above.

[0016] The present invention provides a body component airflow guiding structure, a compressor, and an air conditioner, which have the following beneficial effects: In this invention, the flow guiding component is relatively stationary compared to the rotating parts of the motor. This means that unlike traditional rotating guide vanes or oil-blocking structures, it does not generate continuous parasitic power consumption from oil churning. Therefore, it effectively avoids additional energy loss caused by rotating parts. The flow guiding component effectively guides the working fluid from the flow channel, causing it to form a vortex within the first cavity of the motor. Centrifugal force is used to separate the refrigerant and lubricating oil. The formation of this vortex is a key step in achieving efficient oil-gas separation. The flow guiding component not only guides the working fluid to form a vortex but also strictly constrains its flow path, ensuring that the working fluid fully participates in the separation process according to the set path. This prevents some high-speed airflow from directly short-circuiting into the exhaust pipe instead of flowing along the set path. This strict constraint on the flow path is an important guarantee for improving separation efficiency. Compared with existing technologies that add filters and other structures, the flow guiding component achieves efficient separation without significantly increasing exhaust flow resistance. Through reasonable setting and layout, the flow path of the working fluid is optimized, thereby achieving efficient oil-gas separation without introducing significant additional power consumption. The flow guiding component guides the working fluid to form a swirling flow, using centrifugal force to throw the lubricating oil against the inner wall of the first chamber, thereby achieving effective separation of refrigerant and lubricating oil. This separation method can significantly improve separation efficiency, ensure that the lubricating oil can be fully recovered and reused, and at the same time, the refrigerant can be smoothly discharged from the compressor. Attached Figure Description

[0017] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the flow guiding structure of the pump body assembly according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the first support according to an embodiment of the present invention; Figure 3 This is an isometric schematic diagram of the flow guiding component according to an embodiment of the present invention; Figure 4 This is a top view of the flow guiding component according to an embodiment of the present invention; Figure 5 This is a longitudinal cross-sectional view of the flow guiding component according to an embodiment of the present invention; Figure 6 This is a schematic diagram of the exhaust pipe according to an embodiment of the present invention; Figure 7 This is a schematic diagram of a compressor according to an embodiment of the present invention.

[0019] Attached Figures: 1-First Support; 101-Flow Channel; 2-Flow Guide Assembly; 201-Flow Guide Blade; 202-Axial Guide Vane; 221-Annular Flow Channel; 222-Inner Guide Ring; 223-Outer Guide Ring; 224-Balance Cover; 225-Mounting Groove; 226-Pipe Clearance Groove; 227-Exhaust Pipe Mounting Groove; 3-Pump Body Assembly; 301-Crankshaft; 4-Motor; 41-First Chamber; 42-Second Chamber; 5-Exhaust Pipe; 6-Housing Shell; 7-Return Oil Pipe. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0021] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0022] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used here to describe the spatial positional relationship of a device or feature as shown in the figure with other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device as described in the figure. For example, if a device in the figure is inverted, a device described as "above" or "on top of" other devices or structures will subsequently be positioned as "below" or "under" other devices or structures.

[0023] See also Figures 1 to 6 As shown, according to an embodiment of the present invention, a pump body assembly flow guiding structure is provided, including a first support 1 and a flow guiding component 2. The first support 1 is installed between the pump body assembly 3 and the motor 4. A flow channel 101 is provided on the first support 1 for guiding the working fluid discharged from the pump body assembly 3. The motor 4 has a first cavity 41 close to the pump body assembly 3 and a second cavity 42 away from the pump body assembly 3. The flow guiding component 2 is installed on the first support 1 and located in the first cavity 41. The flow guiding component 2 is relatively stationary with respect to the rotating parts of the motor 4. The flow guiding component 2 guides the working fluid from the flow channel 101, causing the working fluid to form a swirling flow in the first cavity 41 and guide it to the second cavity 42. The structure of the flow guiding component 2 can be a flow guiding blade 201 or a flow guiding channel to constrain and guide the working fluid, causing the working fluid to rotate in the first cavity 41.

[0024] It is worth noting that, in this embodiment, the first cavity 41 and the second cavity 42 are preferably formed by the motor 4 being disposed inside the housing 6. In other embodiments, the cavities formed by the corresponding swirling flow can also be formed when the rotor and shaft of the motor 4 rotate.

[0025] Specifically, the mixed working fluid evaporates and absorbs heat in the evaporator of the air conditioning system, becoming a low-temperature, low-pressure superheated refrigerant. It then enters the pump assembly 3 of the scroll compressor through the suction pipe. During operation, the pump assembly 3 discharges a mixture of refrigerant and lubricating oil. This mixture is first received by the flow channel 101 on the first support 1. The flow channel 101 initially guides the flow direction of the working fluid, allowing it to enter the subsequent separation area, i.e., the flow guide assembly 2, along a predetermined path. The working fluid is guided through the flow channel 101 into the first cavity 41 of the motor 4. The first cavity 41 is the part of the motor 4 closest to the pump assembly 3, providing space for further separation of the working fluid. Before entering the first cavity 41, the working fluid has a high flow velocity and contains a large amount of lubricating oil. The flow guide assembly 2 is mounted on the first support 1 and located in the first cavity 41 of the motor 4. The flow guide assembly 2 is relatively stationary with respect to the rotating parts of the motor 4, meaning that the flow guide assembly 2 itself does not participate in rotational motion. The main function of the flow guide assembly 2 is to guide the working fluid to form a swirling flow within the first cavity 41. Guided by the flow guiding component 2, the working fluid forms a swirling flow within the first chamber 41. This swirling flow causes the refrigerant and lubricating oil in the working fluid to separate due to their density difference. The lubricating oil, being denser, is thrown towards the inner wall of the first chamber 41 by the swirling flow, thus separating from the refrigerant. The refrigerant continues to flow in the central region of the swirling flow. The working fluid (mainly the refrigerant) after swirling separation is further guided by the flow guiding component 2 to flow into the second chamber 42 of the motor 4. The second chamber 42 is the part of the motor 4 that is away from the pump body assembly 3. Guided by the flow guiding component 2, the refrigerant can smoothly enter the second chamber 42 and be discharged from it or re-flow into the first chamber 41 for discharge. The separated lubricating oil accumulates on the inner wall of the first chamber 41 and returns to the compressor's lubrication system through a dedicated oil return channel, achieving lubricant recovery and reuse.

[0026] In this embodiment, the flow guide assembly 2 is relatively stationary compared to the rotating parts of the motor 4. This means that unlike traditional rotating guide vanes or oil baffle structures, it does not generate continuous parasitic power consumption from oil churning. Therefore, it can effectively avoid additional energy loss caused by rotating parts. The flow guide assembly 2 can effectively guide the working fluid from the flow channel 101, causing the working fluid to form a vortex within the first cavity 41 of the motor 4. Centrifugal force is used to separate the refrigerant and lubricating oil. The formation of this vortex is a key step in achieving efficient oil-gas separation. The flow guide assembly 2 not only guides the working fluid to form a vortex but also strictly constrains the flow path of the working fluid, ensuring that the working fluid fully participates in the separation process according to the set path. This prevents some high-speed airflow from directly short-circuiting into the exhaust pipe 5 instead of flowing along the set path. This strict constraint on the flow path is an important guarantee for improving separation efficiency. Compared with the addition of filters and other structures in existing technologies, the flow guiding component 2 achieves efficient separation without significantly increasing exhaust flow resistance. Through reasonable setting and layout, the flow path of the working fluid is optimized, thereby achieving efficient oil-gas separation without introducing significant additional power consumption. The flow guiding component 2 guides the working fluid to form a swirling flow and uses centrifugal force to throw the lubricating oil towards the inner wall of the first chamber 41, thereby achieving effective separation of refrigerant and lubricating oil. This separation method can significantly improve separation efficiency, ensure that the lubricating oil can be fully recovered and reused, and at the same time, the refrigerant can be smoothly discharged from the compressor.

[0027] In this embodiment, the flow channel 101 is located on the first support 1, ensuring that all compressed high-pressure gas (working fluid) can flow smoothly into the flow channel 101. This arrangement avoids disordered diffusion of the working fluid before entering the separation area, reduces energy loss, and provides a stable initial flow condition for the subsequent separation process. The flow channel 101 provides a clear flow path for the working fluid, allowing it to smoothly enter the first cavity 41. This creates favorable conditions for further guidance and separation by the flow guiding component 2, ensuring that the working fluid can enter the effective range of the flow guiding component 2 according to the set path. The flow guiding component 2 is installed on the first support 1 and located in the first cavity 41 of the motor 4, guiding the working fluid to form a vortex. Centrifugal force is used to achieve effective separation of the refrigerant and lubricating oil. After the flow channel 101 smoothly introduces the working fluid into the first cavity 41, the flow guiding component 2 takes over and further optimizes the flow path. The guiding effect of the flow channel 101 ensures that the working fluid enters the flow guiding component 2 at a suitable speed and direction, enabling it to efficiently form a vortex. This synergistic effect makes the formation of the vortex more stable and efficient, thereby significantly improving the separation efficiency. The flow channel 101 ensures that all working fluid flows into the first cavity 41, avoiding short-circuiting of the working fluid before entering the separation area. This allows all working fluid to participate in the separation process, improving the integrity of the separation. The flow guide component 2 strictly constrains the flow path of the working fluid, ensuring that the working fluid fully participates in the swirling separation process within the first cavity 41, preventing some high-speed airflow from directly short-circuiting into the exhaust pipe 5. The combination of the flow channel 101 and the flow guide component 2 ensures the orderly flow of the working fluid during entry and separation. The flow channel 101 avoids short-circuiting of the working fluid at the inlet, while the flow guide component 2 ensures efficient separation of the working fluid within the separation area. Together, they minimize energy loss and the unseparated lubricating oil. The flow channel 101 optimizes the initial flow path of the working fluid and reduces the flow resistance when entering the separation region. The flow guide component 2 avoids the additional power consumption caused by the rotating parts through its static structure. At the same time, by reasonably guiding the flow of the working fluid, it reduces the flow resistance during the separation process. The combination of the flow channel 101 and the flow guide component 2 not only avoids the power consumption of the rotating parts, but also further reduces the overall flow resistance of the system by optimizing the flow path. This synergistic effect makes the separation process more efficient and reduces energy loss.

[0028] See also Figures 1 to 6 As shown, it also includes a housing 6, a pump body assembly 3, a first bracket 1, a flow guide assembly 2 and a motor 4 arranged sequentially from top to bottom in the housing 6. The crankshaft 301 of the pump body assembly 3 passes through the flow guide assembly 2 and the first bracket 1 in sequence and is driven and connected to the motor 4. A first cavity 41 and a second cavity 42 are formed between the inner wall surface of the housing 6 and the outer end face of the motor 4. The first cavity 41 and the second cavity 42 are spaced apart along the axial direction of the rotating shaft of the motor 4.

[0029] In this embodiment, the pump body assembly 3, the first bracket 1, the flow guide assembly 2, and the motor 4 are sequentially installed in the housing 6 to form a compact overall structure. The space inside the housing 6 is divided to form a first cavity 41 and a second cavity 42, providing a clear flow path for the gas-liquid separation of the working fluid. The first cavity 41 is used for preliminary separation and swirling flow formation. The working fluid forms a swirling flow under the action of the flow guide assembly 2, completing the first and second gas-liquid separations. The second cavity 42 is used for further separation and stable flow. The working fluid completes the third gas-liquid separation in the stator tangent gap and the stator-rotor gap.

[0030] See also Figures 1 to 6 As shown, a flow channel 101 is formed on the outer peripheral wall of the first support 1. The flow channel 101 extends obliquely relative to the rotation axis of the motor 4, so that the working fluid passing through the flow channel 101 obtains a tangential velocity component. The direction of the tangential velocity component is the same as the rotation direction of the swirling flow in the first cavity 41, thereby changing the motion direction of the working fluid to complete the first gas-liquid separation. It is worth noting that the oblique flow channel 101 changes the airflow direction from the original vertical downward to oblique downward flow. Here, the total velocity of the oblique downward flow can be decomposed into a vertically downward axial velocity component and a wall-attached circumferential tangential velocity component. After the gas enters the guide vane, since the turbulence effect is positively correlated with the circumferential velocity component, the circumferential velocity component is further enhanced, thus increasing the turbulence effect.

[0031] Specifically, the pump assembly 3 of the scroll compressor (including a moving scroll plate and a stationary scroll plate) compresses the mixture of refrigerant and lubricating oil through scroll motion. The compressed high-pressure working fluid is discharged from the exhaust channel on the stationary scroll plate and flows into the flow groove 101 on the first support 1. The flow groove 101 extends at an inclination relative to the rotation axis of the motor 4. This inclination allows the working fluid to acquire a tangential velocity component when passing through the flow groove 101. The direction of the tangential velocity component is the same as the rotation direction of the swirling flow in the first cavity 41. This means that the working fluid has been given an initial tangential velocity consistent with the swirling flow direction before entering the first cavity 41. After the working fluid enters the first cavity 41 with the tangential velocity component, it can be more naturally guided into the swirling state because the tangential velocity is consistent with the swirling flow direction. Under the action of the swirling flow, the refrigerant and lubricating oil in the working fluid begin to separate due to their density difference. The lubricating oil (with a higher density) is thrown towards the inner wall of the first chamber 41 under the action of centrifugal force, while the refrigerant (with a lower density) concentrates in the central region of the swirling flow. This process completes the first gas-liquid separation, and the lubricating oil is initially separated and adheres to the inner wall of the first chamber 41. After the first separation, the refrigerant (main component) continues to flow in the central region of the swirling flow and is further guided by the flow guiding component 2 to flow into the second chamber 42 of the motor 4.

[0032] In this embodiment, the inclined arrangement of the flow channel 101 allows the working medium to acquire a tangential velocity component consistent with the swirling direction inside the first cavity 41 before entering the first cavity 41. This tangential velocity component provides the initial conditions for the working medium to enter the swirling separation process. When the working medium enters the first cavity 41 with tangential velocity, it can be guided into the swirling state more naturally, reducing the transition time of the working medium entering the swirling flow and improving the stability and efficiency of the swirling flow. This creates favorable conditions for subsequent gas-liquid separation. The direction of the tangential velocity component is consistent with the swirling direction, enabling the working fluid to quickly form a stable swirling flow after entering the first cavity 41. This swirling flow uses centrifugal force to throw the lubricating oil against the inner wall of the cavity, thereby achieving efficient separation of the refrigerant and lubricating oil. By pre-imposing a tangential velocity on the working fluid, the formation of the swirling flow is more efficient, and the separation efficiency is significantly improved. Compared with directly introducing the working fluid into the cavity and then forming a swirling flow, this setting can make fuller use of centrifugal force and ensure more thorough separation of the lubricating oil and refrigerant. The inclined setting of the flow channel 101 allows the working fluid to transition to the swirling flow state more smoothly when entering the first cavity 41, reducing turbulence and energy loss when the working fluid enters the cavity. This setting avoids disordered diffusion and energy waste when the working fluid enters the separation area, improving the overall energy efficiency of the system. At the same time, because the working fluid can enter the swirling flow state more smoothly, the additional power consumption caused by turbulence is reduced. Furthermore, the tangential velocity component is introduced by the inclined setting of the flow channel 101, eliminating the need for additional rotating parts or complex structures to achieve the formation of vortex. This setting simplifies the system structure and reduces the risk of failure caused by complex structures.

[0033] As a specific implementation, the cross-section of the flow channel 101 on the first support 1 is arc-shaped and inclined downward. When the mixed working medium flows through this channel, it will change its original vertical downward movement direction under the structural constraints. Under the action of the difference in inertia between the two phases, the oil and gas will be initially separated. Then the mixed working medium will be discharged from the outlet of the flow channel 101 and enter the upper cavity of the motor 4 inclined downward. That is, the working medium in the flow channel 101 obtains the tangential velocity component.

[0034] In one specific implementation, the pump body assembly 3 includes a stationary vortex disk and a moving disk. In this embodiment, the stationary vortex disk has two exhaust channels. The compressed high-pressure gas flows from the exhaust channels into the flow channel 101. The inlet area of ​​the flow channel 101 completely covers the downward-facing exhaust channel, meaning that all the working fluid in the exhaust channel flows into the flow channel 101. The inlet of the flow channel 101 of the first support 1 is aligned with the exhaust channel of the stationary vortex disk, ensuring that all exhaust flows into the flow channel 101 of the first support 1 for oil-gas separation. The pump body assembly 3 is installed on the top of the first support 1, which is also an upper support. The outer periphery of the first support 1 is welded to the housing 6. Since the flow channel 101 is formed on the outer peripheral wall of the first support 1, the space formed between the flow channel 101 and the housing 6 is used for the flow of the working fluid. The number and position of the exhaust channels and flow channels 101 of the stationary vortex disk are corresponding, with two of each.

[0035] See also Figures 1 to 6 As shown, the flow guiding assembly 2 includes multiple flow guiding blades 201, which are spaced apart around the rotation axis of the motor 4. The multiple flow guiding blades 201 form a flow channel for guiding the working fluid to generate swirling flow, so that the working fluid rotates circumferentially to complete the second gas-liquid separation. The extension direction of the flow channel 101 on its outer peripheral wall is consistent with the inclination direction of the flow guiding blades 201 relative to the radial plane. In this embodiment, the flow guiding blades 201 can be installed in various ways. When the flow guiding blades 201 are installed as independent fixed components on the first bracket 1, the flow guiding assembly 2 is an independent annular component, which includes an annular component and multiple flow guiding blades 201 extending from the annular component. The annular component is directly fixedly installed on the first bracket 1. Alternatively, the guide vanes 201 can be integrally formed with the first support 1. The guide vanes 201 are not independent parts, but rather multiple guide vanes 201 are integrally formed on the corresponding parts of the first support 1 (such as the lower surface facing the motor 4 cavity or the annular sidewall) during the manufacturing of the first support 1 through casting, machining, or additive manufacturing. Since it is an integral structure, there are no additional assembly and fixing links, and the guide vanes 201 are part of the first support 1. Alternatively, the guide assembly 2 can be fixedly installed on the inner wall of the compressor housing 6 or other stationary parts that are rigidly connected to the housing 6 and whose position is fixed relative to the first support 1.

[0036] Specifically, after the first separation, the refrigerant (main component) continues to flow in the central region of the vortex and enters the effective range of the flow guiding component 2. The flow guiding component 2 consists of multiple flow guiding blades 201, which are spaced apart around the rotation axis of the motor 4 to form a flow channel for guiding the working fluid to generate a vortex. Under the action of the flow guiding blades 201, the remaining lubricating oil particles in the working fluid are thrown towards the inner wall of the first chamber 41 under the action of centrifugal force, achieving a more thorough separation. This process completes the second gas-liquid separation, further improving the separation efficiency and ensuring that the lubricating oil content in the discharged refrigerant is extremely low. After the two separations, the refrigerant continues to flow along the flow channel under the guidance of the flow guiding component 2 and is finally guided to the second chamber 42 of the motor 4.

[0037] In this embodiment, the guide vanes 201 are spaced around the rotation axis of the motor 4 to form a flow channel for guiding the working fluid to generate a swirling flow. When the working fluid enters the guide assembly 2, the guide vanes 201 guide the working fluid into a circumferentially rotating swirling flow through their shape and layout. This swirling flow uses centrifugal force to throw the lubricating oil (which has a higher density) toward the inner wall of the first cavity 41, while the refrigerant (which has a lower density) is concentrated in the central area of ​​the swirling flow, thereby achieving efficient gas-liquid separation. The arrangement of the guide vanes 201 ensures the stability and continuity of the swirling flow and improves the separation efficiency. The guide vane 201 further guides the working fluid to form a swirling flow, enhancing the effect of centrifugal force and enabling lubricating oil particles to be separated more thoroughly from the refrigerant. Compared to relying solely on the tangential velocity component introduced by the flow channel 101, the guide vane 201 can more effectively enhance the swirling flow intensity and achieve a more thorough separation effect. This ensures that the lubricating oil content in the discharged refrigerant is extremely low, improving the system's energy efficiency and reliability. The flow channel formed by the guide vane 201 can strictly constrain the flow path of the working fluid, ensuring that the working fluid flows according to the set path and avoiding disordered diffusion or short-circuiting of the working fluid in the separation area. This optimized flow path reduces the energy loss of the working fluid during the separation process and improves the overall efficiency of the system. At the same time, the setting of the guide vane 201 ensures that the working fluid can fully participate in the swirling separation process, preventing some of the working fluid from directly entering the exhaust pipe 5 without flowing according to the set path. The guide vanes 201 optimize the flow path of the working fluid through reasonable settings (such as the shape, angle, and spacing of the vanes), reducing flow resistance. This design achieves efficient separation while avoiding significant increases in flow resistance caused by complex structures or additional components, thereby reducing energy loss and improving system energy efficiency. The guide vanes 201 are stationary components, relatively stationary compared to the rotating components of the motor 4. Therefore, they do not generate continuous parasitic power consumption from oil churning, unlike rotating guide vanes or oil-blocking structures.

[0038] See also Figures 1 to 6As shown, the guide vane 201 is inclined to the radial plane relative to the axis of rotation. The guide vane 201 guides the working fluid to generate a tangential velocity so that the working fluid forms a swirling flow in the first cavity 41.

[0039] In this embodiment, the guide vane 201 is inclined relative to the radial plane of the rotation axis. The guide vane 201 guides the working fluid to generate a tangential velocity, causing the working fluid to form a swirling flow within the first cavity 41. This arrangement makes the formation of the swirling flow more rapid and stable, reducing the transition time and turbulence after the working fluid enters the first cavity 41. The stable swirling flow can more effectively utilize centrifugal force for gas-liquid separation, improving separation efficiency. The tangential velocity component causes the working fluid to form a stronger swirling flow within the first cavity 41, making the centrifugal force more significant. The lubricating oil (with a higher density) is thrown towards the inner wall of the first cavity 41 under the action of centrifugal force, while the refrigerant (with a lower density) concentrates in the central region of the swirling flow. This enhanced swirling effect makes the separation of lubricating oil and refrigerant more thorough, reducing the amount of lubricating oil residue in the refrigerant, thereby improving separation efficiency. The inclined arrangement of the guide vanes 201 not only guides the working fluid to generate tangential velocity, but also optimizes the flow path of the working fluid through its shape and layout, ensuring that the working fluid can flow smoothly along the predetermined flow channel and avoiding disordered diffusion or short-circuiting. This optimized flow path reduces the energy loss of the working fluid during the separation process and improves the overall efficiency of the system. At the same time, it ensures that all working fluids can fully participate in the swirling separation process and prevents some working fluids from flowing directly into the exhaust pipe 5 without following the set path.

[0040] As a specific implementation, the guide vanes 201 are evenly arranged around the center of the shell 6 at 45° intervals, and the vane tips are rounded to minimize the losses caused by gas impacting the vanes. The cross-sectional area of ​​the flow channel formed between the vanes gradually decreases, which can increase the flow velocity of the working fluid when it passes through the flow channel, forming a high-speed vortex at the guide vane outlet, enhancing the centrifugal force field at that point, and improving the oil-gas separation efficiency.

[0041] See also Figures 1 to 6 As shown, the flow guiding assembly 2 also includes an annular axial guide vane 202, which is installed at the bottom of the first support 1. The axial guide vane 202 has an annular flow channel 221 surrounding the axis of rotation, and a plurality of guide vanes 201 are disposed in the annular flow channel 221.

[0042] Specifically, the compressed high-pressure working fluid flows from the exhaust channel of the stationary vortex disk into the flow groove 101 on the first support 1. The flow groove 101 extends at an angle relative to the rotation axis of the motor 4, so that the working fluid acquires a tangential velocity component when passing through the flow groove 101. The working fluid, carrying the tangential velocity component, enters the first cavity 41 and forms a vortex. The refrigerant (main component) after the first separation continues to flow in the central region of the vortex and enters the working range of the axial guide vane 202. The axial guide vane 202 is installed at the bottom of the first support 1 and has an annular flow channel 221 around the rotation axis, providing a stable flow space for the working fluid. After the working fluid enters the annular flow channel 221, the guide vane 201 further guides the working fluid to form a vortex. The guide vanes 201 are inclined relative to the radial plane of the rotation axis, causing the working fluid to generate a tangential velocity in the flow channel, further enhancing the swirling effect. Under the action of the guide vanes 201, the working fluid forms a stronger swirling flow in the first cavity 41, and the centrifugal force is more significant. The lubricating oil particles are further thrown towards the inner wall of the first cavity 41, achieving more thorough separation. After two separations, the refrigerant continues to flow along the annular flow channel 221 under the guidance of the guide vanes 201, and is finally guided to the second cavity 42 of the motor 4.

[0043] In this embodiment, the axial guide vane 202 is installed at the bottom of the first support 1 and has an annular flow channel 221 surrounding the axis of rotation. When the working fluid enters the first cavity 41 from the flow channel 101, it first passes through the annular flow channel 221 of the axial guide vane 202. The annular flow channel 221 of the axial guide vane 202 can initially regulate the flow direction of the working fluid, reducing turbulence and disordered flow when the working fluid enters the first cavity 41, allowing the working fluid to enter the subsequent separation area more smoothly. This stable flow state creates favorable conditions for efficient gas-liquid separation. The annular flow channel 221 of the axial guide vane 202 can evenly distribute the working fluid throughout the entire annular area, avoiding excessively large or small local flow rates. This uniform distribution ensures that the working fluid can smoothly and evenly enter the effective range of the guide vane 201, avoiding a decrease in separation efficiency due to uneven local flow rates. The uniform flow distribution helps to form a stable vortex within the entire first cavity 41, improving the separation effect. The annular flow channel 221 of the axial guide vane 202 provides a stable transition space for the working fluid, allowing it to achieve a more suitable flow state before entering the guide vane 201. By optimizing the flow conditions before the working fluid enters the guide vane 201, the axial guide vane 202 further enhances the swirling effect. This optimization makes the swirling more stable and intense, increasing the effect of centrifugal force and thus achieving more efficient gas-liquid separation. By stabilizing the flow of the working fluid and optimizing the swirling formation conditions, the axial guide vane 202 reduces turbulence and disordered flow of the working fluid when entering the first cavity 41. This design reduces energy loss caused by turbulence and improves the overall energy efficiency of the system. At the same time, the annular flow channel 221 of the axial guide vane 202 can guide the smooth flow of the working fluid, avoiding additional power consumption caused by unstable flow. In addition, as a stationary component, the axial guide vane 202 has a simple structure, reducing the risk of failure caused by complex structures or rotating components.

[0044] See also Figures 1 to 6 As shown, the axial guide vane 202 includes an inner guide ring 222 and an outer guide ring 223 arranged radially opposite to each other. The inner guide ring 222 and the outer guide ring 223 are installed at the bottom of the first support 1, and the inner guide ring 222 and the outer guide ring 223 are coaxially arranged around the rotation axis, defining an annular flow channel 221 between the inner guide ring 222 and the outer guide ring 223. A plurality of guide vanes 201 are disposed in the annular flow channel 221, and the two sides of each guide vane 201 are respectively connected to the outer wall surface of the inner guide ring 222 and the inner wall surface of the outer guide ring 223, and the motor 4. In this embodiment, the tops of the inner guide ring 222 and the outer guide ring 223 are both connected to the first support 1, and the outer peripheral wall of the outer guide ring 223 contacts the housing 6, so that the working fluid flowing out of the flow groove 101 flows into the annular flow and then contacts the guide vane 201, causing the working fluid to swirl.

[0045] In this embodiment, the inner guide ring 222 and the outer guide ring 223 support the annular flow channel 221 from the inside and outside, respectively, providing a stable mounting base for the guide vane 201. This structural arrangement ensures the stability and fixation of the guide vane 201 within the annular flow channel 221, preventing displacement or deformation of the guide vane 201 during the working fluid flow, thereby ensuring that the guide vane 201 can function stably for a long period of time. The inner guide ring 222 and the outer guide ring 223 together define a stable annular flow channel 221, allowing the working fluid to flow along a fixed path before entering the guide vane 201. This arrangement optimizes the flow path of the working fluid, reduces turbulence and disordered flow before the working fluid enters the guide vane 201, and ensures that the working fluid can smoothly enter the effective range of the guide vane 201, thereby improving the swirl formation efficiency and stability. The annular flow channel 221 between the inner guide ring 222 and the outer guide ring 223 provides a stable transition space for the working fluid, allowing it to achieve a more suitable flow state before entering the guide vane 201. By optimizing the flow path and flow state of the working fluid, the inner guide ring 222 and the outer guide ring 223 further enhance the swirling effect. This enhanced swirling can more effectively utilize centrifugal force for gas-liquid separation, improving separation efficiency. By stabilizing the annular flow channel 221 and optimizing the flow path of the working fluid, the inner guide ring 222 and the outer guide ring 223 enable the guide vane 201 to more effectively guide the working fluid to form a swirling flow. This configuration improves the intensity and stability of the swirling flow, allowing the lubricating oil (with a higher density) to be more thoroughly thrown towards the inner wall of the first cavity 41, while the refrigerant (with a lower density) concentrates in the central region of the swirling flow, thereby achieving more efficient gas-liquid separation.

[0046] See also Figures 1 to 6 As shown, the inner wall of the inner guide ring 222 is provided with an annular balance cover 224. The balance cover 224 is provided with a shaft hole, through which the crankshaft 301 of the pump body assembly 3 passes and is driven and connected to the motor 4. An annular balance cavity surrounding the axis of rotation is formed between the inner guide ring 222 and the balance cover 224. A balance block is sleeved on the crankshaft 301, and the balance block is located in the balance cover 224.

[0047] Specifically, the compressed high-pressure working fluid flows from the exhaust channel of the static vortex disk into the flow groove 101 on the first support 1. The flow groove 101 extends at an inclination relative to the rotation axis of the motor 4, so that the working fluid obtains a tangential velocity component when passing through the flow groove 101. After the working fluid with the tangential velocity component enters the first cavity 41, it forms a vortex. The refrigerant (main component) after the first separation continues to flow in the central region of the vortex and enters the working range of the axial guide vane 202. After the working fluid enters the annular flow channel 221, the guide vanes 201 further guide the working fluid to form a swirling flow. The guide vanes 201 are set at an inclination relative to the radial plane of the rotation axis, so that the working fluid generates a tangential velocity in the flow channel. Under the action of the guide vanes 201, the working fluid forms a stronger swirling flow in the first cavity 41. The balance cover 224 reduces the dynamic unbalanced force generated by the crankshaft 301 during rotation through the annular balance cavity. The balance block sleeved on the crankshaft 301 is located inside the balance cover 224. By adjusting the position and mass distribution of the balance block, the unbalanced force generated by the crankshaft 301 during rotation can be accurately compensated.

[0048] In this embodiment, the balance block reduces the vibration generated by the crankshaft 301 during high-speed rotation by compensating for unbalanced forces. This reduction in vibration directly lowers the system's noise level. This configuration significantly reduces vibration and jitter during crankshaft 301 rotation, improving the system's dynamic balance performance. Optimized dynamic balance reduces mechanical wear and energy loss caused by unbalanced forces, extending the service life of the crankshaft 301 and related components. Through optimized dynamic balance, the combination of the balance block and balance cover 224 reduces the dynamic stress generated by the crankshaft 301 during rotation. This reduced stress makes the entire system more stable, improving system stability and reducing component loosening or damage caused by vibration, ensuring the compressor maintains high efficiency and stable performance during long-term operation. The annular balance chamber can serve as a temporary storage area for lubricating oil, which circulates within the chamber, lubricating and cooling the crankshaft 301. This configuration reduces wear on the crankshaft 301, extending its service life. Simultaneously, the circulating lubricating oil removes heat generated by the crankshaft 301 during rotation, further improving the system's operating efficiency and reliability.

[0049] In one specific implementation, an annular balance cover 224 is provided on the inner wall of the inner guide ring 222. A relatively closed axial guide vane 202 is formed between the inner guide ring 222, the outer guide ring 223, and the balance cover 224. The balance block rotates with the crankshaft 301, while the balance cover 224 remains stationary, reducing vibration and unbalanced force when the crankshaft 301 rotates. Since the flow groove 101 is located on the outer peripheral wall of the first support 1, there is no direct channel for the working fluid to flow into the area near the center of the motor 4. Therefore, after the working fluid enters the first cavity 41, it mainly forms a swirling flow in the area near the outer periphery of the motor 4. The swirling flow of the working fluid in the first cavity 41 is mainly concentrated in the outer peripheral area of ​​the motor 4. This swirling flow is formed by the action of the guide vane 201. Under the action of the swirling flow, the lubricating oil and refrigerant begin to separate. The stator of the motor 4 is mounted on the housing 6, and there is a certain gap between the stator and the housing 6, which is called the stator tangential gap. This gap is part of the working fluid flow path. Under the action of swirling flow, the working fluid preferentially flows into the stator tangential gap between the stator of motor 4 and the housing 6. This gap is the channel for the working fluid to flow from the first cavity 41 to the second cavity 42. Under the action of swirling flow, the working fluid flows from top to bottom into the stator tangential gap. During this process, the working fluid continues to be subjected to centrifugal force, further separating the lubricating oil and refrigerant. Below the stator tangential gap is the second cavity 42 of motor 4, which is the transition area for the working fluid to flow from the first cavity 41 to the exhaust pipe 5. After the working fluid flows into the second cavity 42 from the stator tangential gap, it continues to be subjected to centrifugal force. Due to the stator-rotor gap between the stator and rotor of motor 4, the working fluid continues to flow in the second cavity 42. There is a certain gap between the stator and rotor of motor 4, called the stator-rotor gap. This gap is part of the working fluid flow path. During the rotation of crankshaft 301 and motor 4 rotor, the working fluid in the second chamber 42 flows into the stator-rotor gap. The working fluid is subjected to centrifugal force in the stator-rotor gap, further separating the lubricating oil and refrigerant. The working fluid flows out of the stator-rotor gap from bottom to top, completing the third gas-liquid separation. After three gas-liquid separations, the refrigerant finally enters the exhaust pipe 5, is discharged from the compressor, and enters the subsequent stages of the refrigeration system. It is worth noting that the annular gap between the outer circumference of motor 4 stator and the inner wall of compressor housing 6 is the main channel connecting the high-pressure oil-gas mixture area in the upper chamber of motor 4 and the relatively low-pressure area in the lower chamber of motor 4.

[0050] See also Figures 1 to 6 As shown, it also includes an exhaust pipe 5. The air inlet of the exhaust pipe 5 is located in the flow guide assembly 2 and is connected to the first cavity 41. The air outlet of the exhaust pipe 5 is connected to the external environment. The center line of the air inlet of the exhaust pipe 5 is perpendicular to the rotation direction of the swirling flow in the first cavity 41. The working fluid in the first cavity 41 flows into the stator tangent gap of the motor 4 and is guided from top to bottom to the second cavity 42. The working fluid in the second cavity 42 flows into the stator-rotor gap of the motor 4 and flows from bottom to top into the air inlet of the exhaust pipe 5 so that the working fluid is discharged from the exhaust pipe 5.

[0051] Specifically, the compressed high-pressure working fluid flows from the exhaust channel of the static vortex disk into the flow groove 101 on the first support 1. Since the inlet area of ​​the flow groove 101 completely covers the exhaust channel, all the discharged working fluid can smoothly enter the flow groove 101, ensuring that there is no working fluid leakage or flow outside the set path. The flow groove 101 extends at an angle relative to the rotation axis of the motor 4, so that the working fluid obtains a tangential velocity component when passing through the flow groove 101. After the working fluid enters the first cavity 41 with the tangential velocity component, it forms a swirling flow. This process completes the first gas-liquid separation, and the lubricating oil initially adheres to the inner wall of the first cavity 41. After the first separation, the refrigerant (main component) continues to flow in the central region of the vortex and enters the working range of the axial guide vane 202. After the working fluid enters the annular flow channel 221, the guide vane 201 further guides the working fluid to form a vortex. The guide vane 201 is set at an inclination relative to the radial plane of the rotation axis, so that the working fluid generates a tangential velocity in the flow channel. Under the action of the guide vane 201, the working fluid forms a stronger vortex in the first cavity 41. The balance block sleeved on the crankshaft 301 is located in the balance cover 224. By adjusting the position and mass distribution of the balance block, the unbalanced force generated by the crankshaft 301 during rotation can be accurately compensated. In this process, the second gas-liquid separation is also completed. Under the action of the guide vanes 201, the working fluid in the first cavity 41 preferentially flows into the stator tangential gap between the stator of the motor 4 and the housing 6. The working fluid then flows from the stator tangential gap into the second cavity 42, and from the second cavity 42 into the stator-rotor gap between the stator and rotor of the motor 4. During the rotation of the crankshaft 301 and the rotor of the motor 4, the working fluid flows from bottom to top and is further subjected to centrifugal force, completing the third gas-liquid separation. After the three gas-liquid separations, the refrigerant enters the air inlet of the exhaust pipe 5. The centerline of the air inlet of the exhaust pipe 5 is perpendicular to the rotation direction of the swirling flow in the first cavity 41. This arrangement ensures that the working fluid can smoothly enter the exhaust pipe 5.

[0052] In one specific implementation, the outer guide ring 223 is provided with an exhaust pipe mounting groove 227. The air inlet of the exhaust pipe 5 is flush with the bottom of the outer guide ring 223. The air inlet of the exhaust pipe 5 is close to the stator-rotor gap and the inner wall of the housing 6 at a certain distance, that is, at a certain distance from the stator tangential gap. No working fluid flows into the exhaust pipe mounting groove 227, and the exhaust pipe mounting groove 227 is also isolated from the annular flow channel 221. The exhaust pipe 5 is also stationary. After this arrangement, the working fluid flows between the stationary guide vanes 201 and does not flow directly into the exhaust pipe 5. When the working fluid in the second cavity 42 flows out along the stator-rotor gap, even if it flows into the first cavity 41, this part of the first cavity 41 will not have a large amount of working fluid flowing, so that the working fluid in the stator-rotor gap can flow into the air inlet of the exhaust pipe 5.

[0053] In one specific implementation, the air inlet of the exhaust pipe 5 is set vertically downward, the exhaust pipe 5 is S-shaped, and the exhaust pipe 5 extends out of the housing 6 after being bent at a certain angle.

[0054] In one specific embodiment, the outer wall of the outer guide ring 223 is provided with a mounting groove 225. The outer guide ring 223 can also be installed on a socket on the inner wall of the housing 6. The housing 6 is also provided with an oil return pipe 7. One end of the oil return pipe 7 extends upward to the flow groove 101 or any connection point between the first bracket 1 and the axial guide vane 202, and the other end extends downward to the oil groove. In order to better install the oil return pipe 7, a pipe clearance groove 226 is also provided on the outer wall of the outer guide ring 223. The oil return pipe 7 does not directly extend into the flow guiding assembly 2 to avoid affecting the flow guiding assembly 2 in forming swirl in the first cavity 41.

[0055] See also Figures 1 to 7 As shown, a compressor includes a pump body assembly 3 flow guide structure, which is the pump body assembly 3 flow guide structure described above.

[0056] Specifically, after the mixed working fluid evaporates and absorbs heat in the evaporator of the air conditioning system, it becomes a low-temperature, low-pressure superheated gas. It then enters the scroll compressor pump body through the suction pipe. Driven by the crankshaft 301, the moving scroll plate performs translational motion around the stationary scroll plate, continuously reducing the volume of the compression chamber within the pump body. Once the mixed working fluid is compressed to the target pressure, it is discharged through the pressure relief port and the central outlet of the pump body into the cavity formed by the upper chamber. It then moves downwards along the flow channel 101 of the stationary scroll plate towards the lower part of the compressor. At this time, the mixed working fluid contains a large amount of lubricating oil discharged from the pump body assembly 3 along with the refrigerant. To reduce the oil circulation rate, this embodiment modifies the vertically downward flow channel 101 of the first support 1 into an arc-shaped inclined section. The direction of movement of the working fluid is forced to change at this point, and the difference in inertia allows for a single separation of oil and gas. The downward-moving working fluid then enters the first cavity 41 of the motor 4. Under the guidance of the retaining component, the working fluid moves in a ring around the center of the housing 6, enhancing the turbulence effect. Due to the significant density difference between the refrigerant and lubricating oil, the centrifugal force generated by the rotation of the working fluid separates the oil, which has greater inertia, to the wall of the casing 6, while leaving the refrigerant, which has less inertia, in a position relatively closer to the center, thus completing the secondary separation of oil and gas. The mixed working fluid in the flow guiding assembly 2 cannot flow directly out of the compressor from the downward-facing exhaust pipe 5; it needs to flow downward along the stator tangent of the motor 4 and enter the second chamber 42 of the motor 4. At the same time, the lubricating oil continuously accumulates on the wall of the casing 6, gradually forming an oil film. Driven by the mixed working fluid, it also flows downward along the stator tangent. During this process, small oil droplets carried in the mixed working fluid are also adsorbed onto the oil film, further increasing the thickness of the oil film. After entering the second chamber 42, the oil film flows into the bottom oil sump under its own gravity, while the refrigerant moves upward from the gap between the stator and rotor of the motor 4 under the push of the airflow and is discharged from the compressor through the exhaust pipe 5, completing the third separation of oil and gas.

[0057] An air conditioner includes a compressor, wherein the compressor is the compressor described above.

[0058] It will be readily understood by those skilled in the art that the aforementioned advantageous methods can be freely combined and superimposed without conflict.

[0059] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A pump body assembly flow guide structure, characterized by, The utility model relates to a pump body assembly and motor cooling system, including: First support (1) and flow guide assembly (2); The first support (1) is installed between pump body assembly (3) and motor (4), be provided with flow passage (101) on first support (1), flow passage (101) is used to guide the working medium that pump body assembly (3) discharged; The motor (4) has the first cavity (41) close to the pump body assembly (3) and the second cavity (42) away from the pump body assembly (3), the flow guide assembly (2) is installed on the first support (1) and is located in the first cavity (41), the flow guide assembly (2) is opposite static with the rotating part of motor (4), the flow guide assembly (2) guides the working medium from flow passage (101), makes working medium form the swirl in the first cavity (41), and is guided to the second cavity (42).

2. The pump body assembly flow guide of claim 1, wherein, The flow passage (101) is opened on the outer peripheral wall of the first support (1), and the flow passage (101) extends obliquely relative to the rotation axis of the motor (4), so that the working medium passing through the flow passage (101) obtains a tangential velocity component, the direction of the tangential velocity component is the same as the rotation direction of the swirl in the first cavity (41), to change the motion direction of the working medium to complete the first gas-liquid separation.

3. The pump body assembly flow guide of claim 1, wherein, The flow guide assembly (2) includes a plurality of flow guide vanes (201), and the plurality of flow guide vanes (201) are arranged at intervals around the rotation axis of the motor (4). The plurality of flow guide vanes (201) form a flow channel for guiding the working medium to generate a swirl, so that the working medium rotates circumferentially to complete the second gas-liquid separation.

4. The pump body assembly flow guide of claim 3, wherein, The flow guide vane (201) is arranged obliquely relative to the radial plane of the rotation axis, and the flow guide vane (201) guides the working medium to generate a tangential velocity to form a swirl in the first cavity (41).

5. The pump body assembly flow guide of claim 3, wherein, The flow guide assembly (2) further includes an annular axial guide vane (202), and the axial guide vane (202) is installed at the bottom of the first support (1). The axial guide vane (202) has an annular flow channel (221) surrounding the rotation axis, and the plurality of flow guide vanes (201) are arranged in the annular flow channel (221).

6. The pump body assembly flow guide structure of claim 5, wherein, The axial guide vane (202) includes an inner guide ring (222) and an outer guide ring (223) arranged opposite in the radial direction. The inner guide ring (222) and the outer guide ring (223) are installed at the bottom of the first support (1) and are coaxially arranged around the rotation axis. The annular flow channel (221) is defined between the inner guide ring (222) and the outer guide ring (223), and the two sides of each flow guide vane (201) are connected to the outer wall surface of the inner guide ring (222) and the inner wall surface of the outer guide ring (223), respectively.

7. The pump body assembly flow guide of claim 6, wherein, The inner wall of the inner guide ring (222) is provided with an annular balance cover (224) provided with a shaft hole, a crankshaft (301) of the pump body assembly (3) is arranged in the shaft hole and is drivingly connected with the motor (4), and an annular balance cavity surrounding the rotation axis is formed between the inner guide ring (222) and the balance cover (224).

8. The pump body assembly flow guide of claim 1, wherein, Further comprising an exhaust pipe (5), an air inlet of the exhaust pipe (5) is located in the flow guide assembly (2) and communicates with the first cavity (41), an air outlet of the exhaust pipe (5) communicates with the external environment, a center line of the air inlet of the exhaust pipe (5) is perpendicular to the rotation direction of the rotation flow in the first cavity (41), the working medium in the first cavity (41) flows into the stator undercut gap of the motor (4) and is guided from top to bottom to the second cavity (42), the working medium in the second cavity (42) flows into the stator-rotor gap of the motor (4) and flows into the air inlet of the exhaust pipe (5) from bottom to top, so that the working medium is discharged from the exhaust pipe (5).

9. The pump body assembly flow guide of claim 1, wherein, Further comprising a shell (6), the pump body assembly (3), the first support (1), the flow guide assembly (2) and the motor (4) are sequentially arranged in the shell (6) from top to bottom, the crankshaft (301) of the pump body assembly (3) sequentially passes through the flow guide assembly (2) and the first support (1) and is drivingly connected with the motor (4); the inner wall surface of the shell (6) and the outer end surface of the motor (4) surround to form the first cavity (41) and the second cavity (42), and the first cavity (41) and the second cavity (42) are arranged in the axial direction of the rotation shaft of the motor (4).

10. A compressor comprising a pump body assembly flow guide structure, characterized by, The pump body assembly flow guide structure is the pump body assembly flow guide structure in any one of claims 1 to 9.

11. An air conditioner comprising a compressor, characterized by The compressor is the compressor in claim 10.

Images