A compressor device for a high pressure ratio boosting system and a control method thereof

Abstract

The present invention belongs to the technical field of compressors and discloses a compressor device for a high-pressure ratio supercharging system, including a turbocharger. A compressor casing and a turbine casing are respectively provided on both sides of the turbocharger. A compressor impeller is installed in the compressor casing. A cooling water channel is integrally connected to the outer surface of the compressor casing. The water inlet of the cooling water channel is connected to a low-temperature circulating water channel. The low-temperature circulating water channel is used to pass the cooling water of the engine into the turbine casing cooling water channel, and to perform heat conduction and heat convection on the high-temperature compressor casing and compressor impeller to achieve cooling. The present invention is used to solve the problem in traditional technology that the reliability of the high-pressure ratio supercharging system of a high-power engine decreases due to the increase in intake pressure demand.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and in particular relates to a compressor device for a high-pressure ratio supercharging system and a control method thereof. Background Art

[0002] At present, engines including diesel engines are continuously being miniaturized, and the specific power is continuously increasing. The intake pressure demand is increasing, which puts higher and higher requirements on the supercharging system.

[0003] Existing booster systems such as Figure 1 As shown, it includes a turbocharger 5, and a compressor housing 7 and a turbine housing 19 are respectively provided on both sides of the turbocharger 5. A compressor impeller 6 and a turbine rotor 20 are respectively installed in the compressor housing 7 and the turbine housing 19. The compressor impeller 6 and the turbine rotor 20 are respectively fixedly connected through an intermediate shaft to realize the transmission of torque and rotation.

[0004] The compressor casing inlet 31 of the compressor casing 7 is connected to an air filter 10, and the compressor casing outlet 32 ​​of the compressor casing 7 is connected to the engine intake pipe 2 of the engine 1 through a pipeline. An intercooler 4 is installed on the pipeline between the compressor casing outlet 32 ​​and the engine intake pipe 2.

[0005] The engine exhaust pipe 3 of the engine 1 is connected to the turbine housing 19 through a pipeline.

[0006] In the existing supercharging system, the air entering the engine intake pipe 2 is cooled by the intercooler 4. However, as the supercharging pressure ratio of the supercharging system increases, the compressor temperature also increases.

[0007] In summer or when the ambient temperature of the engine is high, such as when the ambient temperature exceeds 35°C, the temperature after compression is higher than normal, further increasing the temperature of components such as the compressor casing.

[0008] If there are no cooling measures for the compressor, the existing materials cannot meet the reliability requirements of the supercharging system. The compressor casing is switched to cast iron material, and the compressor impeller of the high-pressure stage supercharger is switched to a titanium alloy impeller. Switching the compressor impeller to a titanium alloy impeller will affect the movement of the core rotor shaft, and the shaft system needs to be redesigned.

[0009] For a two-stage turbocharged engine, if the compressed air at the outlet of the low-pressure compressor is not cooled by an intercooler, the temperature of the high-pressure turbocharger compressor after supercharging is often such that the existing material cannot meet the reliability requirements. It is also necessary to switch the material of at least the high-pressure compressor; at the same time, it also increases the cooling load of the intercooler after the high-pressure turbocharger.

[0010] If an intercooler is added after the low-pressure stage supercharger, it will take up a larger space in the engine compartment and require a separate support to be designed on the engine, which significantly increases the cost. Summary of the Invention

[0011] The main technical problem to be solved by the present invention is to provide a compressor device for a high-pressure ratio supercharging system and a control method thereof, so as to solve the problem that the reliability of the high-pressure ratio supercharging system of a high-power engine in traditional technology decreases due to the increase in intake pressure demand.

[0012] In order to solve the above technical problems, the present invention provides the following technical solutions:

[0013] A compressor device for a high-pressure ratio supercharging system includes a turbocharger. A compressor casing and a turbine casing are respectively provided on both sides of the turbocharger. A compressor impeller is installed in the compressor casing. A cooling water channel is integrally connected to the outer surface of the compressor casing. The water inlet of the cooling water channel is connected to a low-temperature circulating water channel. The low-temperature circulating water channel is used to pass engine cooling water into the turbine casing cooling water channel, thereby performing heat conduction and heat convection on the high-temperature compressor casing and compressor impeller to achieve cooling.

[0014] The following is a further optimization of the above technical solution by the present invention:

[0015] The compressor casing outlet of the compressor casing is connected to the engine intake pipe of the engine through the intake main pipe;

[0016] An intercooler is installed on the air intake main pipe, and an intercooler water inlet and an intercooler water outlet are respectively provided on one side of the intercooler.

[0017] Further optimization: the arrangement direction of the cooling water channel is the same as the direction of the charge air flow channel in the compressor casing; the cross-sectional shape of the cooling water channel is an arc runway;

[0018] A cooling water channel inlet is provided on the compressor casing near the compressor casing outlet, and a cooling water channel outlet is provided on the compressor casing near the small cross-section of the pressurized air flow channel. The cooling water channel inlet and the cooling water channel outlet are respectively connected to the cooling water channels.

[0019] Further optimization: the outer dimension L2 of the cooling water channel is smaller than or larger than the outer dimension L1 of the compressor casing;

[0020] As the cross section of the charge air flow channel in the compressor casing becomes smaller, the width L3 of the cooling water channel also becomes smaller;

[0021] The cooling water channel height L4 of the cooling water channel is smaller than the cooling water channel width L3.

[0022] Further optimization: the cooling water channel inlet and outlet are connected to water channel joints respectively;

[0023] The water channel joints on the cooling water channel inlet and the cooling water channel outlet are respectively connected to the corresponding low-temperature circulating water channel and the water channel outlet pipeline, and the other end of the water channel outlet pipeline is connected to the intercooler water inlet of the intercooler.

[0024] Further optimization: the other end of the low-temperature circulating water circuit is connected to an electric three-way valve, and the liquid inlet end of the electric three-way valve is connected to the external engine water pump through a pipeline;

[0025] The other liquid outlet end of the electric three-way valve is connected to a cooling water channel, and the other end of the cooling water channel is connected to an intercooler water inlet of the intercooler.

[0026] Further optimization: a plurality of outlet inner wall spiral protrusions are integrally connected to the inner wall of the compressor casing outlet, and the plurality of outlet inner wall spiral protrusions are annular and arranged at intervals.

[0027] Further optimization: A temperature sensor is installed in the air intake main pipe near the compressor casing outlet, and the temperature sensor is used to detect the real-time temperature of the compressed air in the air intake main pipe;

[0028] A pressure sensor is installed in the intake main pipe near the engine intake pipe. The pressure sensor is used to detect the real-time pressure of the compressed air in the intake main pipe.

[0029] Further optimization: also includes a control system for controlling whether cooling water flows into the cooling water channel;

[0030] The control system includes an engine ECU, wherein an input terminal of the engine ECU is electrically connected to output terminals of a temperature sensor and a pressure sensor;

[0031] The output terminal of the engine ECU is electrically connected to the control terminal of the electric three-way valve;

[0032] The engine ECU is provided with temperature setting parameters and pressure setting parameters.

[0033] The present invention further provides a method for controlling a compressor for a high-pressure ratio supercharging system, based on the above-mentioned compressor device for a high-pressure ratio supercharging system, comprising the following steps:

[0034] S1. First, the temperature sensor is used to detect the real-time temperature of the high-pressure air in the intake main pipe and send it to the engine ECU. The engine ECU compares the real-time temperature with the temperature setting parameter;

[0035] S2. When the real-time temperature is greater than the temperature setting parameter, the engine ECU controls the electric three-way valve to connect the low-temperature circulating water circuit to it. At this time, cooling water is transported to the cooling water channel through the warm circulating water circuit, and then transported to the intercooler through the water channel outlet pipe to reduce the temperature of the high-pressure air.

[0036] S3. When the real-time temperature is lower than the temperature setting parameter, the engine ECU controls the electric three-way valve to connect the cooling water channel to it. At this time, the cooling water flows directly to the intercooler through the cooling water channel.

[0037] S4, the pressure sensor is used to detect the real-time pressure of the high-pressure air in the intake main pipe and send it to the engine ECU, which compares the real-time pressure with the pressure setting parameter;

[0038] S5. When the real-time pressure is greater than the pressure setting parameter, and the engine ECU determines whether the electric three-way valve is connected to the low-temperature circulating water circuit, if not, the electric three-way valve is controlled to operate so that the low-temperature circulating water circuit is connected to it. At this time, the cooling water is transported to the cooling water channel through the warm circulating water channel, and then transported to the intercooler through the water channel outlet pipe.

[0039] The present invention adopts the above-mentioned technical solution, which is ingenious in conception and reasonable in structure. It can introduce engine cooling water into the cooling water channel on the compressor casing, and reduce the temperature of the compressor casing and the compressor impeller without making obvious changes to the engine compartment layout, thereby preventing high-temperature failure of the compressor material and ensuring the reliable and normal operation of the supercharging system for high-power engines.

[0040] The present invention does not modify the existing turbocharger shaft system structure, only slightly changes the compressor casing mold outer mold, and the engine compartment layout remains basically unchanged, thereby achieving reliable and normal operation of the supercharging system for high-power engines; the present invention also has a simple and compact structure, is easy to implement, and has low product production and use costs; the assembly process steps are simple; and the reliability of the supercharging system is improved, which can significantly extend its service life.

[0041] The present invention will be further described below with reference to the accompanying drawings and examples. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] Figure 1 It is a structural principle diagram of an existing supercharging system in the background technology;

[0043] Figure 2 This is a schematic diagram of a high-pressure ratio single-stage supercharging system in Example 1 of the present invention;

[0044] Figure 3 This is a control system diagram in Example 1 of the present invention;

[0045] Figure 4 is a cross-sectional view of the compressor casing in Example 1 of the present invention;

[0046] Figure 5 This is a front view of the compressor casing in Example 1 of the present invention;

[0047] Figure 6This is a schematic diagram of the compressor casing outlet in Example 1 of the present invention;

[0048] Figure 7 A cross-sectional view of the compressor casing outlet in Example 1 of the present invention;

[0049] Figure 8 This is an axonometric view of the compressor casing outlet in Example 1 of the present invention;

[0050] Figure 9 This is a cross-sectional view of the cooling water channel inlet in Example 1 of the present invention;

[0051] Figure 10 This is a cross-sectional view of the cooling water channel outlet in Example 1 of the present invention;

[0052] Figure 11 This is a cloud diagram of the compressor casing wall temperature field at a speed of 2 for the solution without cooling water channels in Example 1 of the present invention;

[0053] Figure 12 This is a cloud diagram of the compressor casing wall temperature field at a speed of 2 in Example 1 of the present invention;

[0054] Figure 13 This is a comparison chart of the compressed air temperature at the compressor casing outlet in Example 1 of the present invention;

[0055] Figure 14 This is a schematic diagram of the high-pressure ratio two-stage supercharging system in Example 2 of the present invention.

[0056] In the figure: 1-engine; 2-engine intake pipe; 3-engine exhaust pipe; 4-intercooler; 5-turbocharger; 6-compressor impeller; 7-compressor casing; 8-cooling water channel; 9-low-temperature circulating water channel; 10-air filter; 11-water channel outlet pipe; 12-intercooler water inlet; 13-intercooler water outlet; 141-engine cooling water channel inlet; 142-engine cooling water channel outlet; 15-engine cooling water channel; 16-high-pressure stage turbocharger; 17-high-pressure stage turbine casing; 18-high-pressure stage turbine rotor; 19 -turbine casing; 20-turbine rotor; 21-high-pressure stage compressor casing; 22-high-pressure stage compressor impeller; 23-electric three-way valve; 24-engine ECU; 25-temperature sensor; 26-pressure sensor; 27-water channel connector; 28-hoop; 29-cooling water channel inlet; 30-cooling water channel outlet; 31-compressor casing inlet; 32-compressor casing outlet; 33-high-pressure stage compressor inlet pipe; 34-high-pressure stage compressor outlet pipe; 35-spiral protrusion on the inner wall of the outlet; 36-cooling water channel; 37-intake main pipe. Implementation Method

[0057] like Figure 1-10As shown: A compressor device for a high-pressure ratio supercharging system includes a turbocharger 5, with a compressor casing 7 and a turbine casing 19 provided on both sides of the turbocharger 5 respectively. A compressor impeller 6 is installed in the compressor casing 7, and a cooling water channel 8 is integrally connected to the outer surface of the compressor casing 7. The water inlet of the cooling water channel 8 is connected to a low-temperature circulating water channel 9. The low-temperature circulating water channel 9 is used to pass the cooling water of the engine 1 into the casing cooling water channel 8, so as to achieve effective cooling by heat conduction and heat convection of the high-temperature compressor casing 7 and the compressor impeller 6.

[0058] In this embodiment 1, the shell cooling water channel 8 is flat and integrally connected to the compressor shell 7. Cooling water flows through the cooling water channel 8. The cooling water in the cooling water channel 8 cools the compressor shell 7 and the compressor impeller 6 in the compressor shell 7 through heat conduction.

[0059] The high-temperature air after pressurization in the compressor casing 7 is cooled by heat convection near a circle of the compressor casing 7 , thereby improving the use effect.

[0060] In this embodiment, a turbine rotor 20 is installed in the turbine housing 19 , and the compressor impeller 6 and the turbine rotor 20 are fixedly connected via an intermediate shaft in the turbocharger 5 to achieve torque and rotation transmission.

[0061] The compressor casing inlet 31 of the compressor casing 7 is connected to the air filter 10 , and the compressor casing outlet 32 ​​of the compressor casing 7 is connected to the intake pipe 37 . The other end of the intake pipe 37 is connected to the engine intake pipe 2 of the engine 1 .

[0062] An intercooler 4 is installed on the air intake main pipe 37 , and an intercooler water inlet 12 and an intercooler water outlet 13 are respectively provided on one side of the intercooler 4 .

[0063] The external cooling water is delivered to the intercooler 4 through the intercooler water inlet 12 , and is discharged from the intercooler water outlet 13 after the cooling water circulates in the intercooler 4 . When the cooling water circulates in the intercooler 4 , it can cool the compressed air in the intake main pipe 37 .

[0064] The other end of the intercooler water outlet 13 is communicated with an external cooling water source.

[0065] The engine exhaust pipe 3 of the engine 1 is connected to the turbine housing 19 through a pipeline.

[0066] The engine 1 is provided with an engine cooling water channel 15 , and both ends of the engine cooling water channel 15 are respectively provided with an engine cooling water channel inlet 141 and an engine cooling water channel outlet 142 .

[0067] In addition to the present embodiment 1, the shell cooling water channel 8 is opened in the inner wall of the compressor shell 7 , and the outer side of the air channel in the compressor shell 7 is a part of the shell of the cooling water channel 8 .

[0068] This design can improve the heat exchange effect between the shell cooling water channel 8 and the pressurized air in the compressor shell 7, thereby improving the use effect.

[0069] The arrangement direction of the cooling water channel 8 is the same as the direction of the charge air flow channel in the compressor casing 7 .

[0070] A cooling water channel inlet 29 is provided on the compressor casing 7 at a position close to the compressor casing outlet 32 ​​, and the cooling water channel inlet 29 is communicated with the cooling water channel 8 .

[0071] A cooling water channel outlet 30 is provided on the compressor casing 7 at a position close to the small cross-section of the pressurized air flow channel thereof, and the cooling water channel outlet 30 is communicated with the cooling water channel 8 .

[0072] In addition to the present embodiment 1, the cooling water channel inlet 29 and the cooling water channel outlet 30 can also be used interchangeably.

[0073] The cross-sectional space of the cooling water channel inlet 29 is large, which reduces flow resistance.

[0074] In the first embodiment, the outer dimension L2 of the cooling water channel 8 is smaller than the outer dimension L1 of the compressor casing 7. However, in the first embodiment, the outer dimension L2 of the cooling water channel 8 is increased as much as possible.

[0075] In addition to the present embodiment 1, the outer dimension L2 of the cooling water channel 8 may also be larger than the outer dimension L1 of the compressor casing 7 , that is, the outer periphery of the cooling water channel 8 extends to the outer surface of the compressor casing 7 .

[0076] The cross-section of the cooling water channel 8 is in the shape of an arc runway.

[0077] As the cross-section of the pressurized air flow channel in the compressor casing 7 decreases, the cooling water channel width L3 also decreases.

[0078] The cooling water channel height L4 of the cooling water channel 8 is smaller than the cooling water channel width L3, and the cooling water channel heights L4 at different cross sections of the cooling water channel 8 are arranged at the same height.

[0079] In addition to the present embodiment 1, the cooling water channel height L4 may also be increased continuously as the cross section of the pressurized air flow channel in the compressor casing 7 becomes smaller.

[0080] The cooling water channel inlet 29 and the cooling water channel outlet 30 are respectively connected to the water channel connector 27. The water channel connector 27 is a thin-walled metal part and is installed on the compressor casing 7 by press-fitting.

[0081] In addition to the present embodiment 1, the water channel joint 27 can also be fixedly mounted on the compressor casing 7 by threaded connection.

[0082] The bottom of the connection portion between the water channel joint 27 on the cooling water channel inlet 29 and the cooling water channel outlet 30 and the compressor casing 7 should not exceed the water channel wall, that is, the distances L5>0 and L6>0 between the lower end surface of the water channel joint 27 and the water channel wall of the compressor casing 7. At the same time, for a compact structural arrangement, the distances L5 and L6 should not be greater than D1 / 3, where D1 is the inner hole diameter of the water channel joint 27.

[0083] The water channel joint 27 on the cooling water channel inlet 29 is connected to the low-temperature circulating water channel 9 , and the water channel joint 27 on the cooling water channel outlet 30 is connected to the water channel outlet pipeline 11 .

[0084] The low-temperature circulating water channel 9 and the water channel outlet pipe 11 are respectively connected to the corresponding water channel joints 27 through ring hoops 28.

[0085] The low-temperature circulating water channel 9 and the water outlet pipeline 11 are both heat-resistant pipelines.

[0086] The other end of the water outlet pipe 11 is communicated with an intercooler water inlet 12 of the intercooler 4 .

[0087] The other end of the low-temperature circulating water circuit 9 is connected to an electric three-way valve 23 , and the liquid inlet end of the electric three-way valve 23 is connected to an external engine water pump through a pipeline.

[0088] The other liquid outlet end of the electric three-way valve 23 is connected to a cooling water path 36 , and the other end of the cooling water path 36 is connected to the intercooler water inlet 12 of the intercooler 4 .

[0089] With this design, the external engine water pump is used to absorb cooling water and pressurize it to be transported to the position of the electric three-way valve 23 through the pipeline. At this time, the electric three-way valve 23 is used to control the flow direction of the cooling water.

[0090] When the electric three-way valve 23 controls the low-temperature circulating water path 9 to be connected thereto and controls the cooling water path 36 to be disconnected therefrom, the cooling water delivered by the external engine water pump enters the low-temperature circulating water path 9 .

[0091] At this time, the cooling water in the low-temperature circulating water channel 9 is diverted to the cooling water channel 8, and then the cooling water flows in the cooling water channel 8 and is diverted to the intercooler 4 through the water channel outlet pipe 11. After the cooling water circulates in the intercooler 4, it is discharged through the intercooler outlet 13.

[0092] When the electric three-way valve 23 controls the low-temperature circulating water path 9 to be disconnected from it and controls the cooling water path 36 to be connected to it, the cooling water delivered by the external engine water pump enters the cooling water path 36 .

[0093] At this time, the cooling water in the cooling water channel 36 is directed to the intercooler 4 , and after the cooling water circulates in the intercooler 4 , it is discharged through the intercooler water outlet 13 .

[0094] The low-temperature circulating water channel 9 and the water outlet pipe 11 are laid out so as to avoid high-temperature components such as the supercharger engine exhaust pipe and the supercharger turbine as much as possible.

[0095] like Figure 6-7 As shown, the cooling water channel 8 on the compressor casing 7 is in a region A close to the compressor casing outlet 31 , and the cooling water channel 8 extends toward a side close to the compressor casing outlet 31 .

[0096] The cooling water channel 8 on the compressor casing 7 is within the region B, and the cooling water channel 8 extends toward the side of the compressor casing inlet 32 ​​by a cross-sectional height L4 and a total width L2.

[0097] A plurality of outlet inner wall surface spiral protrusions 35 are integrally connected to the inner wall of the compressor casing outlet 32 ​​. The plurality of outlet inner wall surface spiral protrusions 35 are annular and arranged at intervals.

[0098] This design allows the compressed air flowing through the spiral protrusion 35 on the inner wall of the outlet to flow in the same direction as the compressed air flowing at the compressor casing outlet 32, while increasing the contact area between the casing and the compressed air, thereby enhancing heat convection, and improving cooling efficiency and use effect.

[0099] A temperature sensor 25 is installed in the intake main pipe 37 near the compressor casing outlet 32 ​​. The temperature sensor 25 is used to detect the real-time temperature of the compressed air in the intake main pipe 37 .

[0100] A pressure sensor 26 is installed in the intake main pipe 37 at a position close to the engine intake pipe 2 . The pressure sensor 26 is used to detect the real-time pressure of the compressed air in the intake main pipe 37 .

[0101] The compressor device for the high-pressure ratio supercharging system further includes a control system, which controls whether cooling water flows into the cooling water channel 8.

[0102] The control system includes an engine ECU 24 , and an input terminal of the engine ECU 24 is electrically connected to output terminals of a temperature sensor 25 and a pressure sensor 26 .

[0103] The output terminal of the engine ECU 24 is electrically connected to the control terminal of the electric three-way valve 23 .

[0104] The engine ECU 24 is provided with temperature setting parameters and pressure setting parameters.

[0105] The temperature sensor 25 is used to detect the real-time temperature of the high-pressure air in the intake main pipe 37 and send the real-time temperature signal to the engine ECU 24 .

[0106] The pressure sensor 26 is used to detect the real-time pressure of the high-pressure air in the intake main pipe 37 and send the real-time pressure signal to the engine ECU 24 .

[0107] The engine ECU 24 outputs a control signal for controlling the electric three-way valve 23 to operate.

[0108] The present invention also provides a method for controlling a compressor for a high pressure ratio supercharging system, comprising the following steps:

[0109] S1. First, the temperature sensor 25 is used to detect the real-time temperature of the high-pressure air in the intake main pipe 37 and send the real-time temperature signal to the engine ECU 24. At this time, the engine ECU 24 compares the real-time temperature with the temperature setting parameter.

[0110] S2. When the real-time temperature is greater than the temperature setting parameter, it indicates that the air temperature in the compressor casing 7 is too high. At this time, the engine ECU 24 controls the electric three-way valve 23 to operate, connecting the low-temperature circulating water path 9 to it. At this time, the cooling water in the electric three-way valve 23 is transported to the cooling water channel 8 through the warm circulating water path 9, and then transported to the intercooler 4 through the water channel outlet pipe 11.

[0111] At this time, when the cooling water flows in the cooling water channel 8 and the intercooler 4, it can cool the high-pressure air in the compressor casing 7 and the intake main pipe 37, thereby reducing the temperature of the high-pressure air.

[0112] S3. When the real-time temperature detected by the temperature sensor 25 is lower than the temperature setting parameter, it indicates that the air temperature in the compressor casing 7 is normal. At this time, the engine ECU 24 controls the electric three-way valve 23 to operate, so that the cooling water path 36 is connected to it. At this time, the cooling water in the electric three-way valve 23 is directly passed to the intercooler 4 through the cooling water path 36.

[0113] At this time, when the cooling water flows in the intercooler 4 , it can cool the high-pressure air in the intake main pipe 37 , thereby reducing the temperature of the high-pressure air.

[0114] In this embodiment 1, the real-time temperature of the high-pressure air is used as the main parameter for controlling the operation of the electric three-way valve 23. When the real-time temperature detected by the temperature sensor 25 is greater than the temperature setting parameter, the electric three-way valve 23 is controlled to operate so that the low-temperature circulating water path 9 introduces cooling water into the cooling water channel 8 to cool the high-pressure air.

[0115] S4. The pressure sensor 26 is used to detect the real-time pressure of the high-pressure air in the intake main pipe 37 and send the real-time pressure signal to the engine ECU 24. At this time, the engine ECU 24 compares the real-time pressure with the pressure setting parameter.

[0116] S5. When the real-time pressure is greater than the pressure setting parameter, it indicates that the pressure in the intake main pipe 37 is too high, and the engine ECU 24 determines whether the electric three-way valve 23 is working to control the low-temperature circulating water channel 9 to be connected thereto. If not, the electric three-way valve 23 is controlled to work to control the low-temperature circulating water channel 9 to be connected thereto. At this time, the cooling water in the electric three-way valve 23 is transported to the cooling water channel 8 through the warm circulating water channel 9, and then transported to the intercooler 4 through the water channel outlet pipe 11.

[0117] At this time, when the cooling water flows in the cooling water channel 8 and the intercooler 4, it can cool the high-pressure air in the compressor casing 7 and the intake main pipe 37, thereby reducing the temperature of the high-pressure air.

[0118] In this embodiment 1, the real-time pressure of the high-pressure air is used as a secondary parameter to control the operation of the electric three-way valve 23. When the real-time pressure detected by the pressure sensor 25 exceeds the normal value range and the electric three-way valve 23 is not started to control the cooling water in the low-temperature circulating water circuit 9 to flow into the cooling water channel 8, the electric three-way valve 23 is started to control the cooling water in the low-temperature circulating water circuit 9 to flow into the cooling water channel 8, which is then used to cool the high-pressure air.

[0119] Simulation analysis of the compressor device used in the high pressure ratio boosting system:

[0120] Taking the atmospheric temperature of 30°C as an example, the three design schemes of the present invention, namely, the scheme without cooling water channel, the scheme with cooling water channel and the scheme with enlarged cooling water channel, were subjected to fluid-solid coupling CFD simulation analysis under multiple working conditions. The simulation results are as follows: Figure 11-13 shown.

[0121] like Figure 11 It can be seen that when the turbocharger speed is 2 and there is no cooling water channel, the compressor casing wall temperature is much higher than the allowable temperature of the aluminum material, and the maximum temperature reaches 259°C.

[0122] like Figure 12 It can be seen that at a supercharger speed of 2 and when the compressor casing with the enlarged cooling water channel solution of the present invention is used, the compressor casing wall temperature is much lower than the allowable temperature of the aluminum material, with the maximum temperature being only 127°C.

[0123] like Figure 13It can be seen that the cooling water channel solution in the present invention and the enlarged cooling water channel solution in the present invention have significantly reduced the compressed air temperature at the compressor casing outlet compared with the solution without cooling water channels. Among them, the enlarged cooling water channel solution has a more obvious effect, especially when the supercharger intake flow rate is small at the same speed, such as when the speed is 1 / 0.38kg / s, the outlet temperature drops from 200.4℃ to 156.5℃.

[0124] In summary, this integrated compressor assembly structure can effectively reduce the maximum operating temperature of the compressor casing of high-power engines, thereby ensuring the reliability of the engine's supercharging system and alleviating the load on the engine intercooler. Further improvements to the system structure can also meet more demanding application requirements.

[0125] Example 2: Figure 14 As shown, the compressor device for the high pressure ratio boosting system can also be used Figure 14 As shown in the structure, the compressor device for the high-pressure ratio supercharging system includes a turbocharger 5 and a high-pressure stage supercharger 16, and a high-pressure stage compressor casing 21 and a high-pressure stage turbine casing 17 are respectively provided on both sides of the high-pressure stage supercharger 16.

[0126] The high-pressure stage compressor housing 21 and the high-pressure stage turbine housing 17 are respectively provided with a high-pressure stage compressor impeller 22 and a high-pressure stage turbine rotor 18. The high-pressure stage compressor impeller 22 and the high-pressure stage turbine rotor 18 are respectively connected through a central shaft provided in the high-pressure stage supercharger 16, and transmit torque to rotate synchronously.

[0127] The overall structure of the turbocharger 5 is the same as that of the first embodiment.

[0128] The difference is that the compressor casing outlet 32 ​​of the compressor casing 7 is connected to the air inlet of the high-pressure stage compressor casing 21 through the high-pressure stage compressor inlet pipe 33, and the air outlet of the high-pressure stage compressor casing 21 is connected to the engine intake pipe 2 of the engine 1 through the high-pressure stage compressor outlet pipe 33.

[0129] The intercooler 4 is installed on the high-pressure compressor outlet pipeline 33 , and the temperature sensor 25 and the pressure sensor 26 are also installed on the high-pressure compressor outlet pipeline 33 .

[0130] The engine exhaust pipe 3 of the engine 1 is connected to the air inlet of the high-pressure stage turbine housing 17 through a pipeline, and the air outlet of the high-pressure stage turbine housing 17 is connected to the air inlet of the turbine housing 19 through a pipeline.

[0131] In this embodiment 2, the cooling water channel 8 is arranged on the outer surface of the compressor casing 7, and can also be arranged on the outer surface of the high-pressure stage compressor casing 21 as needed, or arranged on the outer surface of the compressor casing 7 and the outer surface of the high-pressure stage compressor casing 21 at the same time.

[0132] For those skilled in the art, according to the teachings of the present invention, without departing from the principles and spirit of the present invention, changes, modifications, substitutions and variations made to the implementation methods are still within the scope of protection of the present invention.

Claims

1. A compressor device for a high-pressure ratio supercharging system, comprising a turbocharger (5), a compressor housing (7) and a turbine housing (19) being provided on either side of the turbocharger (5), a compressor impeller (6) being installed in the compressor housing (7), and characterized in that: A cooling water channel (8) is integrally connected to the outer surface of the compressor casing (7), and a water inlet of the cooling water channel (8) is connected to a low-temperature circulating water channel (9). The low-temperature circulating water channel (9) is used to pass the cooling water of the engine (1) into the compressor casing cooling water channel (8), and to conduct heat conduction and heat convection on the high-temperature compressor casing (7) and the compressor impeller (6) to achieve cooling; the cross-sectional shape of the cooling water channel (8) is an arc runway; a plurality of outlet inner wall spiral protrusions (35) are integrally connected to the inner wall of the compressor casing outlet (32), and the plurality of outlet inner wall spiral protrusions (35) are annular and arranged at intervals; the arrangement direction of the spiral protrusions (35) is the same as the flow direction of the compressed air flowing at the compressor casing outlet (32), so as to improve the heat exchange efficiency.

2. The compressor device for a high pressure ratio supercharging system according to claim 1, characterized in that: The compressor casing outlet (32) of the compressor casing (7) is connected to the engine intake pipe (2) of the engine (1) through an intake main pipe (37); an intercooler (4) is installed on the intake main pipe (37), and an intercooler water inlet (12) and an intercooler water outlet (13) are respectively provided on one side of the intercooler (4).

3. The compressor device for a high pressure ratio supercharging system according to claim 2, characterized in that: The arrangement direction of the cooling water channel (8) is the same as the direction of the pressurized air flow channel in the compressor casing (7); the cooling water channel inlet (29) and the cooling water channel outlet (30) are respectively connected to the cooling water channel (8).

4. The compressor device for a high pressure ratio supercharging system according to claim 3, characterized in that: The outer dimension L2 of the cooling water channel (8) is smaller than or larger than the outer dimension L1 of the compressor casing (7); As the cross section of the pressurized air flow channel in the compressor casing (7) decreases, the width L3 of the cooling water channel (8) also decreases. The cooling water channel (8) has a cooling water channel height L4 that is smaller than a cooling water channel width L3.

5. The compressor device for a high pressure ratio supercharging system according to claim 4, characterized in that: The cooling water channel inlet (29) and the cooling water channel outlet (30) are respectively connected to the water channel connector (27); The water channel connectors (27) on the cooling water channel inlet (29) and the cooling water channel outlet (30) are respectively connected to the corresponding low-temperature circulating water channel (9) and the water channel outlet pipe (11), and the other end of the water channel outlet pipe (11) is connected to the intercooler water inlet (12) of the intercooler (4).

6. The compressor device for a high pressure ratio supercharging system according to claim 5, characterized in that: The other end of the low-temperature circulating water circuit (9) is connected to an electric three-way valve (23), and the liquid inlet end of the electric three-way valve (23) is connected to an external engine water pump through a pipeline; The other liquid outlet end of the electric three-way valve (23) is connected to a cooling water path (36), and the other end of the cooling water path (36) is connected to an intercooler water inlet (12) of the intercooler (4).

7. The compressor device for a high pressure ratio supercharging system according to claim 6, characterized in that: A temperature sensor (25) is installed in the air intake main pipe (37) at a position close to the compressor casing outlet (32), and the temperature sensor (25) is used to detect the real-time temperature of the compressed air in the air intake main pipe (37); A pressure sensor (26) is installed in the intake main pipe (37) at a position close to the engine intake pipe (2). The pressure sensor (26) is used to detect the real-time pressure of the compressed air in the intake main pipe (37).

8. The compressor device for a high pressure ratio supercharging system according to claim 7, characterized in that: Also included is a control system for controlling whether cooling water flows into the cooling water channel (8); The control system includes an engine ECU (24), an input end of the engine ECU (24) being electrically connected to output ends of a temperature sensor (25) and a pressure sensor (26); The output end of the engine ECU (24) is electrically connected to the control end of the electric three-way valve (23); The engine ECU (24) is provided with temperature setting parameters and pressure setting parameters.

9. A method for controlling a compressor for a high-pressure ratio supercharging system, based on the compressor device for a high-pressure ratio supercharging system according to any one of claims 1 to 8, characterized in that: The steps include: S1. First, the temperature sensor (25) is used to detect the real-time temperature of the high-pressure air in the intake main pipe (37) and send it to the engine ECU (24). The engine ECU (24) compares the real-time temperature with the temperature setting parameter; S2. When the real-time temperature is greater than the temperature setting parameter, the engine ECU (24) controls the electric three-way valve (23) to operate, so that the low-temperature circulating water path (9) is connected to it. At this time, the cooling water is transported to the cooling water channel (8) through the low-temperature circulating water path (9), and then transported to the intercooler (4) through the water channel outlet pipe (11) to reduce the temperature of the high-pressure air; S3. When the real-time temperature is lower than the temperature setting parameter, the engine ECU (24) controls the electric three-way valve (23) to operate, so that the cooling water path (36) is connected to the electric three-way valve, and the cooling water is directly led to the intercooler (4) through the cooling water path (36); S4, a pressure sensor (26) is used to detect the real-time pressure of the high-pressure air in the intake main pipe (37) and send it to the engine ECU (24), and the engine ECU (24) compares the real-time pressure with the pressure setting parameter; S5. When the real-time pressure is greater than the pressure setting parameter, and the engine ECU (24) determines whether the electric three-way valve (23) is connected to the low-temperature circulating water path (9), if it is not connected, the electric three-way valve (23) is controlled to work so that the low-temperature circulating water path (9) is connected to it. At this time, the cooling water is transported to the cooling water channel (8) through the low-temperature circulating water path (9), and then transported to the intercooler (4) through the water path outlet pipe (11).

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