CN117516977A - Liquid-cooled volute cooling power testing method - Google Patents
Liquid-cooled volute cooling power testing method Download PDFInfo
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- CN117516977A CN117516977A CN202410009123.5A CN202410009123A CN117516977A CN 117516977 A CN117516977 A CN 117516977A CN 202410009123 A CN202410009123 A CN 202410009123A CN 117516977 A CN117516977 A CN 117516977A
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- 238000001816 cooling Methods 0.000 title claims abstract description 86
- 238000012360 testing method Methods 0.000 title claims abstract description 76
- 239000000110 cooling liquid Substances 0.000 claims abstract description 91
- 238000000034 method Methods 0.000 claims abstract description 20
- 230000008569 process Effects 0.000 claims abstract description 15
- 238000012544 monitoring process Methods 0.000 claims abstract description 11
- 239000007788 liquid Substances 0.000 claims description 25
- 239000002826 coolant Substances 0.000 claims description 23
- 238000009835 boiling Methods 0.000 claims description 17
- 238000010998 test method Methods 0.000 claims description 6
- 239000012809 cooling fluid Substances 0.000 claims description 3
- 230000007423 decrease Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims description 3
- 239000007789 gas Substances 0.000 description 18
- 239000012071 phase Substances 0.000 description 13
- 238000001514 detection method Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 238000009834 vaporization Methods 0.000 description 6
- 230000008016 vaporization Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000007791 liquid phase Substances 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000008859 change Effects 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000002156 mixing Methods 0.000 description 2
- 238000012935 Averaging Methods 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M99/00—Subject matter not provided for in other groups of this subclass
- G01M99/002—Thermal testing
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
- G01D21/00—Measuring or testing not otherwise provided for
- G01D21/02—Measuring two or more variables by means not covered by a single other subclass
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M99/00—Subject matter not provided for in other groups of this subclass
- G01M99/005—Testing of complete machines, e.g. washing-machines or mobile phones
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The liquid-cooled volute cooling power testing method comprises the following steps of: s10: the heat exchange system provides cooling liquid with set temperature and is used for cooling the turbocharger in the test, and the cooling liquid flows out of the liquid-cooled volute and flows back to the heat exchange system through a return pipeline; s20: in the test process, the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time; monitoring the flow, temperature and pressure of the cooling liquid in the return pipeline in real time; s30: when the turbocharger power at the time of the test is less than or equal to 40% of full power, the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of cooling liquid, Q is total mass flow, dT is temperature difference between an output pipeline and a return pipeline; s40: when the power of the turbocharger at the time of test is greater than 40% of full power, the output pipeline is divided into a branch pipe L1 and a branch pipe L2 before entering the liquid-cooled volute, and the cooling liquid in the branch pipe L1 is used for cooling the turbocharger at the time of test and returns to the return pipeline after flowing out of the liquid-cooled volute.
Description
Technical Field
The invention belongs to the technical field of turbocharger detection, and particularly relates to a liquid-cooled volute cooling power testing method.
Background
Turbochargers on automobiles increase combustion efficiency by supplying more air to the engine, producing more power. The turbine box is an important structure on the turbocharger, and the turbine box utilizes the exhaust gas discharged by the engine to pass through a turbine wheel to drive a compressor on the turbocharger while rotating at a high speed, so that the air inflow is increased, and the purpose of increasing the output power of the engine is achieved.
The temperature of the turbine box of the traditional gasoline engine is above 900 ℃, the volute is required to be used for cooling, and a liquid-cooled volute is generally adopted. The cooling power of the liquid-cooled volute needs to be measured to better perform the cooling operation.
In actual cooling power measurement, the temperature of the working wall surface of the liquid cooling volute is higher, a large amount of liquid vaporization process exists in the cooling process of the cooling liquid, the vaporization process can absorb a large amount of heat, and meanwhile fluctuation of system flow is caused, so that the cooling capacity is difficult to accurately measure. Secondly, the thermal power output of the liquid cooling turbine end has a plurality of directions, the axial work of a rotor is output through a turbine rotating shaft, the cooling work taken away by cooling liquid through a wall surface, the preheating work discharged through waste gas and the like, and the measurement of the power has certain difficulty. Finally, the cooling power is an important index for the turbocharger product, and relates to the burden of the product on the whole vehicle radiator in the use process, the calculation deviation leads to insufficient radiator capacity, the heat balance operation of the whole vehicle can be seriously influenced, and serious consequences such as part failure occur.
Therefore, based on the above-mentioned current situation, the present application has further studied the liquid-cooled volute cooling power test method.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a liquid-cooled volute cooling power testing method, and the accurate test of the cooling power of the water-cooled volute is realized through a set of closed circulation system.
The invention is solved by the following technical scheme.
The liquid-cooled volute cooling power testing method comprises the following steps of: s10: the heat exchange system provides cooling liquid with set temperature, the cooling liquid is conveyed to the liquid-cooled volute through an output pipeline and a pump, the cooling liquid is used for cooling the turbocharger in the test, and the cooling liquid flows out of the liquid-cooled volute and flows back to the heat exchange system through a return pipeline; s20: in the test process, the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time; monitoring the flow, temperature and pressure of the cooling liquid in the return pipeline in real time; s30: when the turbocharger power at the time of the test is less than or equal to 40% of full power, the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of cooling liquid, Q is total mass flow, dT is temperature difference between an output pipeline and a return pipeline; s40: when the power of the turbocharger in the test is more than 40% of full power, the output pipeline is divided into a branch pipe L1 and a branch pipe L2 before entering the liquid-cooled volute, and the cooling liquid in the branch pipe L1 is used for cooling the turbocharger in the test and returns to the return pipeline after flowing out of the liquid-cooled volute; the cooling liquid in the branch pipe L2 directly returns to the return pipeline and is used for cooling the temperature of the gas-liquid coexisting state in the L1, and the gas content in the return pipeline is lower than 1%; ensuring the consistent flow of the cooling liquid in the output pipeline and the return pipeline; the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of the cooling liquid, Q is total mass flow, dT is temperature difference between the output pipeline and the return pipeline.
According to the test method, when the power of the turbocharger in the test is less than or equal to 40% of full power, the cooling liquid is vaporized in a certain high-temperature area, a gas phase is generated, but the gas phase is not high in proportion, the gas phase is converted into a liquid phase after internal temperature transfer along with the flow of the cooling liquid, the cooling effect can be met, the gas phase in proportion at a detection position after flowing out is little or basically not, flow monitoring is not affected, and the cooling power can be calculated through P=C×Q×dT. When the power of the turbocharger in the test is more than 40% of full power, the temperature of the turbine box is high, the liquid vaporization process exists in the cooling process of the cooling liquid, a large amount of heat is absorbed in the vaporization process, the cooling effect is good, but the cooling liquid in the return pipeline contains a large amount of bubbles, and is in a gas-liquid two-phase coexistence state, so that the detection data of the flow of the cooling liquid in the return pipeline becomes meaningless, and the cooling power calculated by P=C×Q×dT in the state is also unreal.
Based on this condition, when testing under the high power in this application, output pipeline divide into two-way, branch pipe L1 is arranged in the turbo charger in the cooling test, branch pipe L2 directly gets back to in the return line, after two-way coolant liquid after the test mixes, the low temperature coolant liquid in branch pipe L2 is arranged in the coolant liquid that the high temperature two-phase in cooling branch pipe L1 coexist for the temperature of return line coolant liquid after merging is less than its boiling point, all become liquid phase basically, then go to detect the coolant liquid flow among them again, its data is true, can apply the formula to calculate cooling power.
In a preferred embodiment, the method further comprises the steps of: s50: when the power of the turbocharger during the test is more than 40% of full power, the flow ratio of the cooling fluid in the branch pipe L1 and the branch pipe L2 is adjusted through the opening degree of the valve F1 arranged in the branch pipe L2, meanwhile, the flow monitoring is carried out through the flow meter Q1 arranged in the branch pipe L1, the power of the pump in the output pipeline is controlled, the flow in the branch pipe L1 is ensured to be kept constant, the stable cooling effect can be provided, and the test progress is improved.
In a preferred embodiment, the method further comprises the steps of: s60: when the power of the turbocharger at the time of the test is > 40% of full power, the coolant flow rate ratio in the branch pipe L1 and the branch pipe L2 is determined by: the estimated cooling power value is P cool The flow rate of L1 is Q L1 According to formula P cool =C*Q L1 * The dT calculation can obtain the fluid temperature rise dT in the branch pipe L1, at the moment, the estimated temperature T4 in the return pipeline is the temperature T0+dT of the cooling liquid in the output pipeline, and the T4 is higher than the boiling point of the cooling liquid; then the flow in the branch pipe L2 is estimated to be Q L2 After merging with the cooling liquid in the branch pipe L1, the temperature rise dT decreases due to the increase of the flow rate, so that T4 is lower than the boiling point of the cooling liquid; in the estimated state, Q L1 And Q L2 The ratio of (2) is the ratio of the coolant flows in the branch pipe L1 and the branch pipe L2.
Step S60 is for pre-determination before testingAnd the flow ratio of the cooling liquid in the branch pipe L1 and the branch pipe L2 is determined, so that after the cooling liquid in the branch pipe L1 and the cooling liquid in the branch pipe L2 are mixed, the temperature of the cooling liquid in the return pipeline is lower than the boiling point of the cooling liquid and the gas content of the cooling liquid is lower than 1%, and the testing precision is ensured. In this step, P cool The temperature rise dT of the mixed branch pipe L1 and the mixed branch pipe L2 can be estimated by taking the average value or fitting the data of multiple tests, and the temperature of the mixed cooling liquid is ensured to be lower than the boiling point of the mixed cooling liquid.
In a preferred embodiment, T4 is lower than the boiling point of the coolant by 0.95, which is a good guarantee for a gas content in the return line of less than 1%.
Compared with the prior art, the invention has the following beneficial effects: the method for testing the cooling power of the liquid-cooled volute is characterized in that two branch pipes are connected in parallel to convey cooling liquid through a closed circulation system, the temperature of the cooling liquid can be guaranteed to be lower than the boiling point of the cooling liquid after the cooling liquid is mixed, a gas phase is eliminated, the accuracy of monitoring the cooling liquid flow under high-power testing is guaranteed, and the accurate testing of the cooling power of the water-cooled volute is realized.
Drawings
Fig. 1 is a schematic diagram of a cooling power test system in the present application.
Fig. 2 is a schematic diagram of a cooling power test system in the prior art.
Fig. 3 is a graph of temperature flow rate change at the time of testing of the prior art test system of fig. 2.
FIG. 4 is a graph of the change in turbine box temperature field during testing of the prior art test system of FIG. 2.
Fig. 5 is a schematic diagram of another cooling power testing system in the prior art.
Detailed Description
The invention is described in further detail below with reference to the drawings and the detailed description.
In the following embodiments, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout, and the embodiments described below by referring to the drawings are exemplary only for explaining the present invention and are not to be construed as limiting the present invention.
In the description of the present invention, it is to be understood that the terms: the directions of the center, the longitudinal, the lateral, the length, the width, the thickness, the upper, the lower, the front, the rear, the left, the right, the vertical, the horizontal, the top, the bottom, the inner, the outer, the clockwise, the counterclockwise, etc. indicate the directions or the positional relationship based on the directions or the positional relationship shown in the drawings, are merely for convenience of description and simplification of the description, and therefore, should not be construed as limiting the present invention. Furthermore, the term: first, second, etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of features shown. In the description of the present invention, unless explicitly specified and defined otherwise, the terms: mounting, connecting, etc. are to be construed broadly and the specific meaning of the terms herein described will be understood by those skilled in the art in view of the specific circumstances.
The liquid-cooled volute cooling power testing system in the application, as shown in fig. 1, comprises a heat exchange system, wherein the heat exchange system is used for providing constant-temperature cooling liquid and is adjustable in temperature, and the heat exchange system can be of a conventional structure in the prior art. An output pipeline L0 is led out of the heat exchange system, and a pump, which can be a variable frequency pump, is arranged on the output pipeline L0, so that the flow, the flow speed and the pressure can be controlled. The output pipeline L0 is divided into a branch pipe L1 and a branch pipe L2, the branch pipe L1 is connected to the turbocharger in the cooling test and then flows out through a pipeline H3, and a valve F1 is arranged on the branch pipe L2 and used for controlling opening, closing and adjusting the opening. After converging with the pipeline H3, the branch pipe L2 is connected into a return pipeline H4, and the return pipeline H4 is connected to a heat exchange system, so that a circulation loop is formed.
Further, in the test system, a monitoring point 1 is arranged on an output pipeline L0, and the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time; and a monitoring point 2 is arranged on the return pipeline H4, and the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time. The branch pipe L1 is provided with a flowmeter Q1, and the return line H4 is provided with a gas content detection unit.
The liquid-cooled volute cooling power testing method comprises the following steps.
S10: the heat exchange system provides cooling liquid with set temperature, the cooling liquid is conveyed to the liquid-cooled volute through the output pipeline and the pump, the cooling liquid is used for cooling the turbocharger in the test, and the cooling liquid flows out of the liquid-cooled volute and flows back to the heat exchange system through the return pipeline.
S20: in the test process, the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time; and monitoring the flow, the temperature and the pressure of the cooling liquid in the return pipeline in real time.
S30: when the turbocharger power at the time of the test is less than or equal to 40% of full power, the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of the cooling liquid, Q is total mass flow, dT is temperature difference between the output pipeline and the return pipeline.
S40: when the power of the turbocharger in the test is more than 40% of full power, the output pipeline is divided into a branch pipe L1 and a branch pipe L2 before entering the liquid-cooled volute, and the cooling liquid in the branch pipe L1 is used for cooling the turbocharger in the test and returns to the return pipeline after flowing out of the liquid-cooled volute; the cooling liquid in the branch pipe L2 directly returns to the return pipeline and is used for cooling the temperature of the gas-liquid coexisting state in the L1, and the gas content in the return pipeline is lower than 1%; ensuring the consistent flow of the cooling liquid in the output pipeline and the return pipeline; the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of the cooling liquid, Q is total mass flow, dT is temperature difference between the output pipeline and the return pipeline.
S50: when the power of the turbocharger during the test is more than 40% of full power, the flow ratio of the cooling fluid in the branch pipe L1 and the branch pipe L2 is adjusted through the opening degree of the valve F1 arranged in the branch pipe L2, meanwhile, the flow monitoring is carried out through the flow meter Q1 arranged in the branch pipe L1, the power of the pump in the output pipeline is controlled, the flow in the branch pipe L1 is ensured to be kept constant, the stable cooling effect can be provided, and the test progress is improved.
S60: when the power of the turbocharger at the time of the test is > 40% of full power, the coolant flow rate ratio in the branch pipe L1 and the branch pipe L2 is determined by: the estimated cooling power value is P cool Flow rate of L1Is Q L1 According to formula P cool =C*Q L1 * The dT calculation can obtain the fluid temperature rise dT in the branch pipe L1, at the moment, the estimated temperature T4 in the return pipeline is the temperature T0+dT of the cooling liquid in the output pipeline, and the T4 is higher than the boiling point of the cooling liquid; then the flow in the branch pipe L2 is estimated to be Q L2 After merging with the cooling liquid in the branch pipe L1, the temperature rise dT decreases due to the increase of the flow rate, so that T4 is lower than the boiling point of the cooling liquid; in the estimated state, Q L1 And Q L2 The ratio of (2) is the ratio of the coolant flows in the branch pipe L1 and the branch pipe L2. Preferably, T4 is lower than the boiling point of the coolant by 0.95, which can well ensure that the gas content in the return line is lower than 1%.
According to the test method, when the power of the turbocharger in the test is less than or equal to 40% of full power, the cooling liquid does not generate gas phase in the cooling process, the cooling effect can be met only by the temperature rise of the liquid cooling liquid, and the cooling power can be calculated through P=C×Q×dT.
The test method is particularly suitable for testing in high-power operation. When the power of the turbocharger in the test is more than 40% of full power, the temperature of the turbine box is high, the liquid vaporization process exists in the cooling process of the cooling liquid, a large amount of heat is absorbed in the vaporization process, the cooling effect is good, but the cooling liquid in the return pipeline contains a large amount of bubbles, and is in a gas-liquid two-phase coexistence state, so that the detection data of the flow of the cooling liquid in the return pipeline becomes meaningless, and the cooling power calculated by P=C×Q×dT in the state is also unreal.
Based on this condition, during the test under the high power in this application, output pipeline L0 divide into two-way, branch pipe L1 is arranged in the turbo charger in the cooling test, branch pipe L2 directly gets back to in the return line, after two-way coolant liquid after the test mixes, low temperature coolant liquid in the branch pipe L2 is arranged in the coolant liquid that the high temperature two-phase in cooling branch pipe L1 coexist for the return line coolant liquid after merging's temperature is less than its boiling point, basically all become liquid phase state, then can guarantee that the flow of return line H4 and output pipeline L0 keeps unanimous, then go to detect coolant liquid flow wherein again, its data is true, can apply the formula to calculate cooling power.
In the high-power test, in order to ensure that the coolant in the return line H4 is in a liquid phase, it is necessary to ensure that the coolant in the branch line L2 is able to sufficiently cool the high-temperature coolant in the branch line L1, and thus it is necessary to achieve a sufficient proportion of the coolant flow split. In the application, step S60 is used for predetermining the flow ratio of the cooling liquid in the branch pipe L1 and the branch pipe L2 before the test, ensuring that the temperature of the cooling liquid in the return pipeline is lower than the boiling point thereof and the air content is lower than 1% after the cooling liquid in the branch pipe L1 and the branch pipe L2 are mixed, and ensuring the test precision. In this step, P cool The reduction amplitude of the temperature rise dT after mixing the branch pipe L1 and the branch pipe L2 can be estimated by averaging or fitting the data of a plurality of tests, and the temperature of the mixed cooling liquid is ensured to be lower than the boiling point 0.95, for example, lower than 95 ℃ when water is used as the cooling liquid.
Fig. 2 is a schematic diagram of a cooling power test system in the prior art, in which a low power test can be performed, but when the system is operated in a high-speed and high-power state, the cooling liquid is vaporized, two phases of gas and liquid exist in a return pipeline H4, and the cooling system is severely fluctuated (flow, temperature and water supply pipeline vibration) at this time, as can be seen from fig. 3 and fig. 4, the water supply temperature, outlet water temperature, flow and the like of the cooling system are severely fluctuated, so that normal detection is difficult, and after the cooling liquid of the two phases of gas and liquid at high temperature is returned to the heat exchange system, the cooling capability and the constant temperature capability of the heat exchange system are also a test, which clearly increases the cost of the heat exchange system.
Fig. 5 is a schematic diagram of another cooling power test system in the prior art, in which an exhaust pipeline of a turbocharger cooling system is added, after the exhaust function is added, a fixed position (an upper condensing box) is provided for high-temperature gas of cooling liquid generated in the system, the cooling system can be liquefied in the condensing box, and when the pressure of the system is increased due to severe generation of gas, a pressure relief valve can be used for releasing and stabilizing the pressure. Thereby guaranteeing the working stability of the system. However, this system mode belongs to a semi-open system, and there is loss of substances and energy, and still it is still impossible to accurately evaluate the cooling power of the supercharger in real time, and the test accuracy is completely inferior to that of the closed test system in the present application.
In the above, the invention provides a method for testing the cooling power of the liquid-cooled volute, which adopts two branch pipes in parallel to convey the cooling liquid through a set of closed circulation system, and after mixing, the temperature of the cooling liquid can be ensured to be lower than the boiling point of the cooling liquid, the gas phase is eliminated, the accuracy of monitoring the cooling liquid flow under high-power test is ensured, and the accurate test of the cooling power of the water-cooled volute is realized.
The scope of the present invention includes, but is not limited to, the above embodiments, and any alterations, modifications, and improvements made by those skilled in the art are intended to fall within the scope of the invention.
Claims (4)
1. The liquid-cooled volute cooling power testing method is characterized by comprising the following steps of:
s10: the heat exchange system provides cooling liquid with set temperature, the cooling liquid is conveyed to the liquid-cooled volute through an output pipeline and a pump, the cooling liquid is used for cooling the turbocharger in the test, and the cooling liquid flows out of the liquid-cooled volute and flows back to the heat exchange system through a return pipeline;
s20: in the test process, the flow, the temperature and the pressure of the cooling liquid in the output pipeline are monitored in real time; monitoring the flow, temperature and pressure of the cooling liquid in the return pipeline in real time;
s30: when the turbocharger power at the time of the test is less than or equal to 40% of full power, the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of cooling liquid, Q is total mass flow, dT is temperature difference between an output pipeline and a return pipeline;
s40: when the power of the turbocharger in the test is more than 40% of full power, the output pipeline is divided into a branch pipe L1 and a branch pipe L2 before entering the liquid-cooled volute, and the cooling liquid in the branch pipe L1 is used for cooling the turbocharger in the test and returns to the return pipeline after flowing out of the liquid-cooled volute; the cooling liquid in the branch pipe L2 directly returns to the return pipeline and is used for cooling the temperature of the gas-liquid coexisting state in the L1, and the gas content in the return pipeline is lower than 1%; ensuring the consistent flow of the cooling liquid in the output pipeline and the return pipeline; the cooling power is calculated by the formula p=c×q×dt, wherein: p is cooling power, C is specific heat capacity of the cooling liquid, Q is total mass flow, dT is temperature difference between the output pipeline and the return pipeline.
2. The method of testing the cooling power of a liquid cooled volute of claim 1, further comprising the steps of:
s50: when the power of the turbocharger at the time of the test is more than 40% of full power, the flow rate ratio of the coolant in the branch pipe L1 and the branch pipe L2 is adjusted by the opening degree of the valve F1 arranged in the branch pipe L2, and meanwhile, the flow rate is monitored by the flowmeter Q1 arranged in the branch pipe L1, the power of the pump in the output pipeline is controlled, and the flow rate in the branch pipe L1 is ensured to be kept constant.
3. The method of testing the cooling power of a liquid cooled scroll casing according to claim 2, further comprising the steps of:
s60: when the power of the turbocharger at the time of the test is > 40% of full power, the coolant flow rate ratio in the branch pipe L1 and the branch pipe L2 is determined by: the estimated cooling power value is P cool The flow rate of L1 is Q L1 According to formula P cool =C*Q L1 * The dT calculation can obtain the fluid temperature rise dT in the branch pipe L1, at the moment, the estimated temperature T4 in the return pipeline is the temperature T0+dT of the cooling liquid in the output pipeline, and the T4 is higher than the boiling point of the cooling liquid; then the flow in the branch pipe L2 is estimated to be Q L2 After merging with the cooling liquid in the branch pipe L1, the temperature rise dT decreases due to the increase of the flow rate, so that T4 is lower than the boiling point of the cooling liquid; in the estimated state, Q L1 And Q L2 The ratio of (2) is the ratio of the coolant flows in the branch pipe L1 and the branch pipe L2.
4. A method according to claim 3, wherein in step S60, T4 is lower than the boiling point of the cooling fluid by 0.95.
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