Cooling system for integrated compressor

Abstract

The utility model discloses a cooling system of integrated compressor relates to compressor technical field, wherein, the cooling system of integrated compressor includes compressor body, inverter module, rectifier module, refrigerant pipeline and controller component, and the refrigerant of refrigerant pipeline is in series and flows through inverter module, rectifier module and compressor body. Through above -mentioned technical scheme, the optimization integration of cooling flow channel is realized, and the pipeline redundancy caused by multiple independent cooling systems is eliminated. The heat of different components is absorbed in series flow channel in turn, and the refrigerant utilization efficiency is improved. Modular flow channel design makes the system can quickly adapt to different models compressor, reduces the equipment transformation cost. The controller grading regulation function of refrigerant flow effectively balances the cooling efficiency and energy consumption index, reduces the refrigerant consumption while maintaining the component working temperature.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a cooling system for an integrated compressor. Background Technology

[0002] In existing integrated compressors, the compressor, inverter module, and rectifier module each have independent cooling systems. However, these independent cooling systems are not interconnected, resulting in a complex piping layout. Furthermore, the existing integrated compressor cooling systems lack versatility, making them unsuitable for application between different compressor models. Utility Model Content

[0003] The main objective of this invention is to propose a cooling system for an integrated compressor, which aims to simplify the existing cooling systems for integrated compressors.

[0004] To achieve the above objectives, the integrated compressor cooling system proposed in this utility model includes:

[0005] The compressor body, wherein a compressor cooling channel is provided within the compressor body;

[0006] An inverter module is used to adjust the speed of the compressor body. The inverter module is provided with an inverter cooling channel, which is connected to the compressor cooling channel.

[0007] A rectifier module is used to supply power to the inverter module. The rectifier module is provided with a rectifier cooling channel, which is connected to the inverter cooling channel and the compressor cooling channel respectively.

[0008] Refrigerant piping, connected to the inverter cooling channel; and

[0009] A controller assembly for controlling the opening and closing of the refrigerant piping.

[0010] In one embodiment, the refrigerant piping includes a main pipeline and a first injection pipeline and a second injection pipeline branching from the main pipeline, both the first and second injection pipelines being connected to the inverter cooling channel; and the controller assembly includes:

[0011] A first solenoid valve is installed in the first liquid injection pipeline;

[0012] A second solenoid valve is installed in the second liquid injection pipeline;

[0013] A first controller and a second controller, wherein the first controller is electrically connected to the first solenoid valve to control the opening and closing of the first solenoid valve, and the second controller is electrically connected to the second solenoid valve to control the opening and closing of the second solenoid valve.

[0014] In one embodiment, the upstream of the rectifier cooling channel is connected to the downstream of the inverter cooling channel, and the downstream of the rectifier cooling channel is connected to the upstream of the compressor cooling channel.

[0015] In one embodiment, the inverter module includes a first temperature sensor, and the rectifier module includes a second temperature sensor. The first temperature sensor and the second temperature sensor are respectively used to transmit the measured temperature signal to the first controller.

[0016] In one embodiment, the compressor body is provided with a third temperature sensor, which is used to transmit the measured temperature signal to the second controller.

[0017] In one embodiment, the compressor body includes a first-stage impeller with an intake port, and the compressor cooling channel communicates with the intake port.

[0018] In one embodiment, a pressure regulating valve is provided at the front end of the compressor cooling channel at the suction port, and the pressure regulating valve is used to regulate the flow rate of refrigerant introduced into the suction port.

[0019] In one embodiment, the compressor body further includes a secondary impeller and a motor, wherein the secondary impeller and the primary impeller are located on the same side of the motor.

[0020] In one embodiment, the secondary impeller is closer to the motor than the primary impeller.

[0021] Through the above technical solution, this application achieves optimized integration of cooling channels, eliminating piping redundancy caused by multiple independent cooling systems. The refrigerant absorbs heat from different components sequentially in the series flow channels, improving refrigerant utilization efficiency. The modular flow channel design allows the system to quickly adapt to different compressor models, reducing equipment modification costs. The controller's graded adjustment function for refrigerant flow effectively balances cooling efficiency and energy consumption, reducing refrigerant consumption while maintaining component operating temperatures. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram of the cooling system of an integrated compressor.

[0024] Figure 2 for Figure 1 A schematic diagram of the structure in another embodiment.

[0025] Explanation of icon numbers:

[0026] 1. Compressor body; 11. Compressor cooling channel; 12. First stage impeller; 121. Inlet; 13. Second stage impeller; 14. Motor; 15. Third temperature sensor; 2. Inverter module; 21. Inverter cooling channel; 22. First temperature sensor; 3. Rectifier module; 31. Rectifier cooling channel; 32. Second temperature sensor; 4. Refrigerant pipeline; 41. Main pipeline; 42. First injection pipeline; 43. Second injection pipeline; 5. Controller assembly; 51. First solenoid valve; 52. Second solenoid valve; 53. First controller; 54. Second controller; 7. Pressure regulating valve.

[0027] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0028] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0029] It should be noted that if the embodiments of this utility model 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.

[0030] Furthermore, if the embodiments of this utility model 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 where both A and B are satisfied simultaneously. 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 by this utility model.

[0031] The cooling systems of existing integrated compressors are relatively simple and cannot meet the heat dissipation requirements of the compressor under various conditions.

[0032] Existing integrated compressor cooling systems lack versatility, making it difficult to reduce component costs. The cooling systems are not interchangeable between different compressor models, requiring redesigned cooling systems for new compressors, resulting in long system development cycles.

[0033] In view of this, the present invention proposes a cooling system for an integrated compressor.

[0034] Please see Figure 1 and Figure 2 In one embodiment of this utility model, the cooling system of the integrated compressor includes a compressor body 1, an inverter module 2, a rectifier module 3, a refrigerant pipeline 4, and a controller assembly 5. The compressor body 1 is provided with a compressor cooling channel 11. The inverter module 2 is used to adjust the speed of the compressor body 1. The inverter module 2 is provided with an inverter cooling channel 21, which is connected to the compressor cooling channel 11. The rectifier module 3 is used to supply power to the inverter module 2. The rectifier module 3 is provided with a rectifier cooling channel 31, which is connected to both the inverter cooling channel 21 and the compressor cooling channel 11. The refrigerant pipeline 4 is connected to the inverter cooling channel 21. The controller assembly 5 is used to control the opening and closing of the refrigerant pipeline 4.

[0035] In one embodiment, please refer to Figure 1 and Figure 2The refrigerant pipeline 4 includes a main pipeline 41 and a first spray pipeline 42 and a second spray pipeline 43 branched from the main pipeline 41. The first spray pipeline 42 and the second spray pipeline 43 are both connected to the inverter cooling channel 21. The controller assembly 5 includes a first solenoid valve 51, a second solenoid valve 52, a first controller 53, and a second controller 54. The first solenoid valve 51 is disposed in the first spray pipeline 42. The second solenoid valve 52 is disposed in the second spray pipeline 43. The first controller 53 and the first solenoid valve 51 are electrically connected to control the opening and closing of the first solenoid valve 51. The second controller 54 and the second solenoid valve 52 are electrically connected to control the opening and closing of the second solenoid valve 52.

[0036] To address the aforementioned issues, it was found that traditional cooling systems struggle to balance structural compactness and functional scalability. Dispersed cooling units not only increase manufacturing costs but also hinder the modular design of compressors. Observations of the thermal management requirements of industrial equipment revealed uneven refrigerant distribution in multi-heat-source collaborative heat dissipation. Further analysis showed that integrating the cooling circuits of the inverter and rectifier module 3 in series can achieve both gradient heat utilization and simplified piping architecture. Based on this, a multi-stage interconnected cooling channel system is proposed, allowing the refrigerant to flow sequentially through different heat-generating components, ultimately forming an integrated cooling network.

[0037] Therefore, this application proposes an integrated compressor cooling system, including a compressor body 1, an inverter module 2, a rectifier module 3, a refrigerant pipeline 4, and a controller assembly 5. The compressor body 1 has a compressor cooling channel 11; the inverter module 2 has an inverter cooling channel 21 and is connected to the compressor cooling channel 11; the rectifier module 3 has a rectifier cooling channel 31, which is connected to both the inverter cooling channel 21 and the compressor cooling channel 11; the refrigerant pipeline 4 is connected to the inverter cooling channel 21; and the controller assembly 5 controls the on / off state of the refrigerant pipeline 4.

[0038] Among them, the compressor cooling channel 11 refers to the fluid channel penetrating the compressor housing, which can be implemented using a serpentine pipe reserved during casting, used to guide the refrigerant to absorb the heat generated by the compressor operation. The inverter cooling channel 21 refers to the microchannel structure embedded in the inverter power unit substrate, which can be processed by etching, improving heat dissipation efficiency by increasing the contact area. The rectifier cooling channel 31 refers to the annular channel surrounding the rectifier semiconductor elements, which can be composed of split water-cooled plates to achieve uniform cooling of the rectifier module 3. The refrigerant pipeline 4 refers to the pipeline system that transports liquid or gaseous cooling media, which can be connected by copper pipes or pressure-resistant flexible hoses, and its branch structure can adapt to different flow distribution requirements.

[0039] Specifically, the refrigerant enters the inverter cooling channel 21 from the refrigerant line 4. After absorbing the heat generated by the inverter, it is divided into refrigerant flowing through the rectifier module 3 and then converging into the compressor cooling channel 11, forming a series cooling path. The controller assembly 5 adjusts the refrigerant flow rate according to the temperature sensor signal, for example, increasing the refrigerant supply when the inverter is overloaded, and closing part of the flow path to reduce energy consumption under low load conditions. The refrigerant finally mixes with the compressed medium at the compressor suction port 121, realizing residual heat recovery. The refrigerant for this compressor enters from the outside, and after cooling is completed, the refrigerant is discharged to the outside of the system.

[0040] Compared to existing technologies, traditional solutions require three sets of control valves and monitoring devices for three independent cooling systems. This solution reduces the control nodes to a single piping system through series flow channels. Existing technologies require redesigning cooling circuits for compressors of different power ratings, while the modular flow channel structure of this solution can be adapted to various models by adjusting the pipe diameter. In existing cooling systems, there is a refrigerant distribution conflict between the rectifier module 3 and the inverter cooling system. This solution achieves autonomous flow distribution through the parallel design of the rectifier cooling flow channel 31 and the compressor cooling flow channel 11.

[0041] Through the above technical solution, this application achieves optimized integration of the cooling channel topology, eliminating piping redundancy caused by multiple independent cooling systems. The refrigerant absorbs heat from different components sequentially in the series flow channel, improving refrigerant utilization efficiency. The modular flow channel design allows the system to quickly adapt to different compressor models, reducing equipment modification costs. The controller's graded adjustment function for refrigerant flow effectively balances cooling efficiency and energy consumption, reducing refrigerant consumption while maintaining component operating temperatures.

[0042] In one embodiment, please refer to Figure 1 and Figure 2 The upstream of the rectifier cooling channel 31 is connected to the downstream of the inverter cooling channel 21, and the downstream of the rectifier cooling channel 31 is connected to the upstream of the compressor cooling channel 11.

[0043] It should be noted that the main pipe 41 refers to the main channel for refrigerant delivery, which can be implemented using metal or pressure-resistant plastic pipes, used to distribute the refrigerant to different branches. The first injection pipe 42 and the second injection pipe 43 refer to two independent branches branching from the main pipe 41, which can be implemented using a branching pipe structure, used to guide the refrigerant to different areas of the inverter cooling channel 21. The first solenoid valve 51 and the second solenoid valve 52 are actuators that control the flow of fluid, which can be implemented using an electromagnetically driven valve structure, used to independently regulate the refrigerant flow rate of the two injection pipes. The first controller 53 and the second controller 54 are signal processing units, which can be implemented using a microprocessor or logic circuits, used to drive the corresponding solenoid valves to operate according to the temperature signal.

[0044] Specifically, the refrigerant is diverted from the main pipe 41 to the first spray pipe 42 and the second spray pipe 43, and then enters the inverter cooling channel 21. The first controller 53 receives a temperature signal from the inverter module 2. When local overheating is detected, it can independently open the first solenoid valve 51 to increase the refrigerant flow in that area. Similarly, the second controller 54 independently controls the opening and closing of the second solenoid valve 52 based on the temperature signal from the rectifier module 3. Thus, the operating states of the two spray pipes do not affect each other; they can be opened simultaneously to cope with high load conditions, or adjusted individually to meet the heat dissipation needs of different areas.

[0045] Compared to existing technologies, traditional integrated compressors use a single cooling pipe to cool the inverter and rectifier module 3 as a whole, resulting in a complex pipe layout and the inability to control temperature in different zones. This solution decomposes the cooling system into independently adjustable sub-modules by setting up two independent liquid injection pipes and corresponding control units, which simplifies the pipe structure and enables precise control of the cooling flow.

[0046] Through the above technical solution, this application solves the problems of redundant and insufficient versatility in the cooling system piping of the prior art. The independent control design of the two injection pipes reduces pipe crossings and redundant connections, making the cooling system layout more compact. At the same time, the cooperation of dual controllers and dual solenoid valves can adapt to the heat dissipation requirements of different models of compressors. By adjusting the opening combination of the injection pipes, various operating conditions can be matched, significantly improving the compatibility and scalability of the cooling system.

[0047] In one embodiment, please refer to Figure 2 The inverter module 2 includes a first temperature sensor 22, and the rectifier module 3 includes a second temperature sensor 32. The first temperature sensor 22 and the second temperature sensor 32 are respectively used to transmit the measured temperature signal to the first controller 53.

[0048] In this context, "upstream" refers to the leading edge of the fluid flow in the channel, which can be achieved by using the channel inlet section or the area near the fluid source, clearly defining the starting point of the cooling medium's flow. "Downstream" refers to the trailing edge of the fluid flow in the channel, which can be achieved by using the channel outlet section or the area near the fluid discharge direction, clearly defining the ending point of the cooling medium's flow. "Connectivity" refers to the connection between channels, which can be achieved through pipe docking, interface matching, or channel integration, ensuring continuous transfer of the cooling medium between different modules.

[0049] Specifically, the cooling medium first flows through the inverter cooling channel 21, absorbing the heat generated by the inverter module 2. Then, it enters the upstream of the rectifier cooling channel 31 from the downstream of the inverter cooling channel 21. It then flows through the rectifier cooling channel 31 to cool the rectifier module 3, and finally, it is transported downstream of the rectifier cooling channel 31 to the upstream of the compressor cooling channel 11 to cool the compressor body 1. Through this sequential flow path, the cooling medium sequentially cools the inverter module 2, the rectifier module 3, and the compressor body 1 in stages, forming a series cooling cycle.

[0050] Compared with existing technologies, the compressor, inverter module 2, and rectifier module 3 use independent cooling systems, resulting in complex piping layout and limited cooling efficiency. This solution integrates the originally dispersed cooling system into a single circulation path by connecting the rectifier cooling channel 31 in series with the inverter cooling channel 21 and the compressor cooling channel 11, reducing the number of pipes and space occupation, while making the heat absorption process of the cooling medium more continuous and balanced.

[0051] Through the above technical solution, this application solves the problem of redundant piping in existing independent cooling systems, realizes integrated design of cooling paths, and reduces system complexity. At the same time, the series-connected cooling channels can automatically allocate cooling medium flow according to the module's heat load, improving cooling efficiency. Furthermore, this structure is adaptable to the cooling needs of different compressor models, enhancing versatility.

[0052] In one embodiment, please refer to Figure 2 The compressor body 1 is equipped with a third temperature sensor 15, which is used to transmit the measured temperature signal to the second controller 54.

[0053] The third temperature sensor 15 refers to a temperature detection device installed on the compressor body 1, which can be implemented by a thermistor or a thermocouple, and is used to monitor the operating temperature of the compressor body 1 in real time.

[0054] The second controller 54 refers to the logic control unit that forms a signal connection with the third temperature sensor 15. Specifically, it can be implemented using a microprocessor or a programmable logic controller. It is used to receive temperature signals and control the opening and closing state of the corresponding solenoid valve based on preset logic.

[0055] Specifically, the third temperature sensor 15 is integrated into a critical heat-generating area of ​​the compressor body 1, such as near the bearing or the windings of the motor 14, to continuously collect temperature data. When the detected temperature exceeds a preset threshold, the third temperature sensor 15 generates an electrical signal and transmits it to the second controller 54. The second controller 54 triggers the second solenoid valve 52 to open based on the received signal, allowing refrigerant to enter the inverter cooling channel 21 through the second injection pipe 43 for cooling. If the temperature drops back to a safe range, the second controller 54 closes the second solenoid valve 52 to stop the refrigerant supply.

[0056] Compared to existing technologies, current integrated compressor cooling systems typically rely on a single controller to centrally process temperature signals from multiple modules, which can easily lead to control delays or signal interference. This solution, however, combines the temperature monitoring of the compressor body 1 with the independent control function of the second controller 54, achieving localized processing of the temperature signal and avoiding the problem of cross-interference between signals from multiple modules.

[0057] Through the above technical solution, this application can accurately adjust the refrigerant flow rate according to the actual temperature change of the compressor body 1, effectively preventing mechanical damage caused by excessive temperature, and at the same time improving the dynamic adjustment capability of the cooling system through the rapid response of the independent controller.

[0058] In one embodiment, please refer to Figure 2 The compressor body 1 includes a first-stage impeller 12, the first-stage impeller 12 has an air intake 121, and the compressor cooling channel 11 is connected to the air intake 121.

[0059] Among them, the first-stage impeller 12 refers to the rotating part in the compressor used to draw in and compress gas. Specifically, it can be implemented by a centrifugal impeller or an axial flow impeller. Its air intake 121 is located at the impeller inlet and is used to guide gas into the compression chamber.

[0060] The compressor cooling channel 11 refers to the internal channel used to transport refrigerant to reduce the temperature of the compressor. Specifically, it can be implemented by using an annular pipe or a spiral channel. Its connection with the suction port 121 can be achieved by welding, flange connection or integral molding process, so as to ensure that the refrigerant can directly enter the suction port 121 area.

[0061] Specifically, the compressor cooling channel 11 is connected to the intake port 121 of the first-stage impeller 12 via a pipeline or built-in channel. As the refrigerant flows through the compressor cooling channel 11, it absorbs the heat generated during compressor operation and then mixes with the intake gas before entering the compression chamber. During compression, the refrigerant further carries away heat through phase change or convection, thereby reducing the internal temperature of the compressor. For example, a pressure regulating valve 7 can be installed at the front end of the intake port 121 to dynamically adjust the refrigerant flow rate according to the compressor load, preventing excessive refrigerant from affecting gas compression efficiency.

[0062] Compared to existing technologies, in traditional integrated compressors, the cooling channel and suction port 121 are independent, requiring the refrigerant to indirectly cool the compressor through additional piping, resulting in a complex structure and limited cooling efficiency. This solution simplifies the refrigerant flow path by directly connecting the compressor cooling channel 11 to the suction port 121. The refrigerant mixes with the suction gas and directly participates in the compression process, improving heat exchange efficiency. Furthermore, this design eliminates the need for separate external connection structures for the cooling channel and suction port 121, reducing piping redundancy.

[0063] Through the above technical solution, this application solves the problems of redundant cooling system piping and low cooling efficiency in the prior art. The refrigerant directly enters the suction port 121 to mix with the gas, which can reduce the gas temperature in the initial stage of compression, avoiding thermal damage to the impeller and motor 14 caused by high-temperature gas, while also reducing pressure drop losses in the refrigerant circulation path. This design also improves the system's compactness and versatility, making it suitable for retrofitting or matching different compressor models.

[0064] In one embodiment, please refer to Figure 2 The compressor cooling channel 11 is provided with a pressure regulating valve 7 at the front end of the suction port 121. The pressure regulating valve 7 is used to regulate the flow rate of refrigerant entering the suction port 121.

[0065] The pressure regulating valve 7 is a control device that dynamically adjusts the refrigerant flow rate based on pressure or temperature signals. It can be implemented using an electric proportional valve or a pneumatic regulating valve. Its function is to maintain compressor operational stability by adjusting the refrigerant flow rate in real time, preventing abnormal pressure at the compressor suction port 121 due to flow fluctuations. The front end of the suction port 121 refers to the pipe area before the inlet of the first-stage impeller 12. It can be integrated with the compressor cooling channel 11 via flange connection or threaded fixing. Its function is to ensure that the refrigerant flow rate is regulated before entering the impeller, preventing unregulated refrigerant from directly impacting the impeller structure.

[0066] Specifically, the pressure regulating valve 7 automatically adjusts its opening by receiving signals from temperature sensors, such as temperature change data from the compressor body 1 or the cooling channel. When an increase in compressor load is detected, leading to a rise in cooling demand, the pressure regulating valve 7 increases its opening to increase refrigerant flow, allowing more refrigerant to enter the suction port 121 for cooling; conversely, it decreases its opening to limit the flow. Thus, the refrigerant flow always matches the actual cooling demand of the compressor, preventing excessive refrigerant from causing energy waste or insufficient flow from causing overheating.

[0067] Compared to existing technologies, traditional integrated compressor cooling systems typically employ a fixed refrigerant flow rate, which cannot dynamically adjust the flow rate according to the compressor's operating conditions, easily leading to low cooling efficiency or refrigerant waste. This solution achieves closed-loop control of the refrigerant flow rate by installing a pressure regulating valve 7 upstream of the suction port 121, thereby improving cooling efficiency and reducing system energy consumption.

[0068] Through the above technical solution, this application solves the problem that the refrigerant flow rate cannot dynamically adapt to the compressor operating status in the prior art, effectively improving the response speed and adaptability of the cooling system. At the same time, through precise flow control, it avoids excessive refrigerant consumption and enhances the economic efficiency of system operation.

[0069] In one embodiment, please refer to Figure 2 The compressor body 1 also includes a secondary impeller 13 and a motor 14, with the secondary impeller 13 and the primary impeller 12 located on the same side of the motor 14.

[0070] The secondary impeller 13 refers to the rotating component used in the second compression stage. It can be made of aluminum alloy and is connected to the output end of the motor 14 via a shaft to achieve secondary compression of the gas.

[0071] The first-stage impeller 12 is a rotating component used in the first compression stage. It can be made of stainless steel and is connected to the second-stage impeller 13 via a shaft to achieve the initial compression of the gas.

[0072] The term "same side of motor 14" means that the first-stage impeller 12 and the second-stage impeller 13 are both arranged on the same end of the output shaft of motor 14. For example, the positional relationship between the two can be achieved by coaxial series connection, thereby reducing the axial space occupation.

[0073] Specifically, in the compressor body 1, the motor 14 serves as the drive source, with its output shaft extending to the same side and sequentially connecting to the primary impeller 12 and the secondary impeller 13. The primary impeller 12 is located at the far end of the motor 14's output shaft and is responsible for drawing in and initially compressing the gas; the secondary impeller 13 is located between the primary impeller 12 and the motor 14 and is responsible for receiving the initially compressed gas and performing secondary pressurization. Thus, the two impellers form a series structure on the same side of the motor 14, allowing the compressed gas to flow axially and reducing pipeline detours.

[0074] Compared to existing technologies, traditional compressors typically have two-stage impellers distributed on both sides of the motor 14, resulting in a dispersed overall structure, large space occupation, and complex cooling channel layout. This solution, however, concentrates the two-stage impellers on the same side of the motor 14, shortening the compression path and making the flow channel more concentrated, thereby reducing the layout difficulty of the cooling system.

[0075] Through the above technical solutions, this application can optimize the internal space utilization of the compressor, reduce pressure loss in the gas flow path, simplify the connection structure of the cooling channel, and improve cooling efficiency and system reliability.

[0076] In one embodiment, please refer to Figure 2 The secondary impeller 13 is closer to the motor 14 than the primary impeller 12.

[0077] Specifically, within the compressor body 1, the primary impeller 12 and the secondary impeller 13 are arranged on the same side of the motor 14, with the secondary impeller 13 positioned closer to the motor 14 housing than the primary impeller 12. By placing the secondary impeller 13 closer to the motor 14, the compressed gas flow path can connect the two impellers with a shorter path, reducing flow path bends and pressure loss. Simultaneously, the heat generated by the motor 14 can be quickly dissipated through adjacent cooling channels, preventing heat accumulation in the impeller area.

[0078] In some specific embodiments, the distance between the secondary impeller 13 and the motor 14 can be smaller than the distance between the primary impeller 12 and the motor 14, for example, by adjusting the length of the impeller mounting shaft or by using a stepped shaft structure. Furthermore, the air inlet of the secondary impeller 13 can be connected to the exhaust port of the primary impeller 12 via a straight-through flow channel to further optimize the airflow path.

[0079] Compared to existing technologies, traditional compressors typically arrange multi-stage impellers equidistantly along the axial direction or distribute them on both sides of the motor 14, resulting in increased flow channel length and limited cooling efficiency. This solution, however, adjusts the relative position of the impellers and the motor 14 to achieve a more compact cooling flow channel layout, reducing refrigerant flow resistance, while also utilizing the installation space of the motor 14 to achieve structural integration.

[0080] Through the above technical solution, this application can effectively reduce the pressure loss in the internal flow channel of the compressor and improve the heat dissipation efficiency of the cooling medium to the motor 14 and impeller area. At the same time, the shortened flow channel design reduces the complexity of pipeline connections, making the system easier to adapt to different models of compressors and enhancing its versatility.

[0081] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A cooling system for an integrated compressor, characterized in that, include: The compressor body, wherein a compressor cooling channel is provided within the compressor body; An inverter module is used to adjust the speed of the compressor body. The inverter module is provided with an inverter cooling channel, which is connected to the compressor cooling channel. A rectifier module is used to supply power to the inverter module. The rectifier module is provided with a rectifier cooling channel, which is connected to the inverter cooling channel and the compressor cooling channel respectively. Refrigerant piping, connected to the inverter cooling channel; and A controller assembly for controlling the opening and closing of the refrigerant piping.

2. The cooling system of the integrated compressor as described in claim 1, characterized in that, The refrigerant piping includes a main pipeline and a first liquid injection pipeline and a second liquid injection pipeline branching from the main pipeline, both of which are connected to the inverter cooling channel; and the controller assembly includes: A first solenoid valve is installed in the first liquid injection pipeline; A second solenoid valve is installed in the second liquid injection pipeline; A first controller and a second controller, wherein the first controller is electrically connected to the first solenoid valve to control the opening and closing of the first solenoid valve, and the second controller is electrically connected to the second solenoid valve to control the opening and closing of the second solenoid valve.

3. The cooling system of the integrated compressor as described in claim 2, characterized in that, The upstream of the rectifier cooling channel is connected to the downstream of the inverter cooling channel, and the downstream of the rectifier cooling channel is connected to the upstream of the compressor cooling channel.

4. The cooling system of the integrated compressor as described in claim 3, characterized in that, The inverter module includes a first temperature sensor, and the rectifier module includes a second temperature sensor. The first temperature sensor and the second temperature sensor are respectively used to transmit the measured temperature signal to the first controller.

5. The cooling system of the integrated compressor as described in claim 4, characterized in that, The compressor body is equipped with a third temperature sensor, which is used to transmit the measured temperature signal to the second controller.

6. The cooling system of the integrated compressor as described in claim 3, characterized in that, The compressor body includes a first-stage impeller, the first-stage impeller has an air intake, and the compressor cooling channel is connected to the air intake.

7. The cooling system of the integrated compressor as described in claim 6, characterized in that, The compressor cooling channel is equipped with a pressure regulating valve at the front end of the air intake, and the pressure regulating valve is used to regulate the flow rate of refrigerant introduced into the air intake.

8. The cooling system of the integrated compressor as described in claim 6, characterized in that, The compressor body also includes a secondary impeller and a motor, with the secondary impeller and the primary impeller located on the same side of the motor.

9. The cooling system of the integrated compressor as described in claim 8, characterized in that, The secondary impeller is closer to the motor than the primary impeller.

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