CN112576359B - Low-temperature cooling system, vehicle and control method of low-temperature cooling system - Google Patents
Low-temperature cooling system, vehicle and control method of low-temperature cooling system Download PDFInfo
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- CN112576359B CN112576359B CN202011299938.XA CN202011299938A CN112576359B CN 112576359 B CN112576359 B CN 112576359B CN 202011299938 A CN202011299938 A CN 202011299938A CN 112576359 B CN112576359 B CN 112576359B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/14—Indicating devices; Other safety devices
- F01P11/16—Indicating devices; Other safety devices concerning coolant temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0493—Controlling the air charge temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/33—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage controlling the temperature of the recirculated gases
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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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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
The invention belongs to the technical field of engines, and particularly relates to a low-temperature cooling system, a vehicle and a control method of the low-temperature cooling system. The low-temperature cooling system comprises a low-temperature circulating radiator, an electric control water pump, an electric control proportional valve, an intercooler set and an expansion water tank, wherein the liquid outlet end of the low-temperature circulating radiator is communicated with the liquid inlet end of the electric control water pump, the liquid outlet end of the electric control water pump is communicated with the liquid inlet end of the electric control proportional valve, the liquid outlet end of the electric control proportional valve is communicated with the liquid inlet end of the intercooler set, the liquid inlet end of the expansion water tank is communicated with the liquid outlet end of the intercooler set, and the liquid outlet end of the expansion water tank is communicated with the liquid inlet end of the low-temperature circulating radiator. Through using the cryogenic cooling system in the technical scheme, the intelligent proportion distribution is carried out on the intercooler group by adopting the electric control proportional valve, the waste phenomenon of cooling intensity is reduced, and meanwhile, the energy consumption of the whole cryogenic cooling system is saved by adopting the electric control water pump to control the flow of cooling liquid.
Description
Technical Field
The invention belongs to the technical field of engines, and particularly relates to a low-temperature cooling system, a vehicle and a control method of the low-temperature cooling system.
Background
The traditional interstage intercooler adopts an air-air cooling mode, the cooling efficiency is low, the cooling intensity is influenced by the vehicle speed and is uncontrollable, in addition, the cooling intensity requirements of the two stages of intercoolers are different, and if only a single cooling pipeline is adopted for cooling, the problem of supercooling or overheating is easy to occur. If an LP-EGR (low-pressure exhaust gas recirculation) system is cooled by engine cooling water, the cooled temperature cannot meet the requirement of low oil consumption, the arrangement of a water path is complex, in addition, the traditional control method has weak control capacity on inter-stage intercooling, main intercooling and LP-EGR, the cooling water flow of each cooling part cannot be intelligently distributed through calibration, and a large amount of cooling intensity is wasted.
Disclosure of Invention
The invention aims to at least solve the problems of weak control capability and waste of cooling strength of a low-temperature cooling system in the prior art. The purpose is realized by the following technical scheme:
a first aspect of the invention provides a cryogenic cooling system comprising:
a low temperature circulating radiator;
the liquid outlet end of the low-temperature circulating radiator is communicated with the liquid inlet end of the electric control water pump;
the liquid outlet end of the electric control water pump is communicated with the liquid inlet end of the electric control proportional valve;
the liquid outlet end of the electric control proportional valve is communicated with the liquid inlet end of the intercooler group;
and the liquid inlet end of the expansion water tank is communicated with the liquid outlet end of the intercooler group, and the liquid outlet end of the expansion water tank is communicated with the liquid inlet end of the low-temperature circulating radiator.
By using the low-temperature cooling system in the technical scheme, the electric control proportional valve is adopted to carry out intelligent proportional distribution on the intercooler group, the cooling capacity of each cooler in the intercooler group can be fully exerted, the waste phenomenon of cooling intensity is reduced, meanwhile, the electric control water pump is adopted to control the flow of cooling liquid, the cooling intensity of the intercooler group can be ensured on the premise of low energy consumption, and the energy consumption of the whole low-temperature cooling system is saved.
In addition, the cryogenic cooling system according to the present invention may have the following additional features:
in some embodiments of the invention, the intercooler bank includes an interstage cooler, a main cooler, and a low pressure EGR cooler, the interstage cooler, the main cooler, and the low pressure EGR cooler being arranged in parallel.
In some embodiments of the invention the outlet side of the main cooler is provided with a first temperature sensor, the outlet side of the low pressure EGR cooler is provided with a second temperature sensor and the outlet side of the inter-stage cooler is provided with a third temperature sensor.
The invention also provides a vehicle with the low-temperature cooling system.
The invention also proposes a method for controlling a cryogenic cooling system, implemented according to the above cryogenic cooling system, comprising:
obtaining the rotating speed of an engine and the circulating fuel injection quantity of the engine;
obtaining a first opening final value of an electric control proportional valve based on a main cooler and a second opening final value of the electric control proportional valve based on a low-pressure EGR cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
obtaining a third opening final value of an electric control proportional valve based on the interstage cooler according to the first opening final value and the second opening final value;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine.
In some embodiments of the present invention, the step of deriving a final value of a first opening degree of an electrically controlled proportional valve based on a main cooler based on the engine speed and the engine cycle fuel injection amount comprises:
obtaining a first temperature set value of the main cooler and a first opening initial value of an electric control proportional valve based on the main cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
acquiring a first temperature value of a first temperature sensor;
obtaining a first temperature difference value of the main cooler according to the first temperature value and the first temperature set value;
and obtaining a first opening final value of the electric control proportional valve based on the main cooler according to the first temperature difference value and the first opening initial value.
In some embodiments of the invention, the step of deriving a final value of a second opening degree of an electronically controlled proportional valve based on a low-pressure EGR cooler from the engine speed and the engine cycle injection quantity comprises:
obtaining a second temperature set value of the low-pressure EGR cooler and a second opening initial value of an electric control proportional valve based on the low-pressure EGR cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
acquiring a second temperature value of a second temperature sensor;
obtaining a second temperature difference value of the low-pressure EGR cooler according to the second temperature value and the second temperature set value;
and obtaining a second opening final value of the electric control proportional valve based on the low-pressure EGR cooler according to the second temperature difference value and the second opening initial value.
In some embodiments of the present invention, the step of obtaining a final rotation speed value of the electronically controlled water pump according to the engine rotation speed and the engine cycle fuel injection amount comprises:
obtaining an initial rotating speed value of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine;
acquiring a first correction coefficient;
obtaining a rotating speed correction value of the electric control water pump according to the rotating speed initial value and the first correction coefficient;
acquiring a second correction coefficient;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed correction value and the second correction coefficient.
In some embodiments of the present invention, a method of obtaining a first correction coefficient includes:
acquiring a speed value of a current vehicle;
and obtaining a first correction coefficient according to the vehicle speed value.
In some embodiments of the present invention, the method of obtaining the second correction coefficient includes:
obtaining a third temperature set value of the interstage cooler according to the engine speed and the engine cycle fuel injection quantity;
acquiring a third temperature of a third temperature sensor;
obtaining a third temperature difference value according to the third temperature and the third temperature set value;
and obtaining a second correction coefficient according to the third temperature difference value and the third temperature set value.
Drawings
Various other advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the invention. Also, like parts are designated by like reference numerals throughout the drawings. In the drawings:
FIG. 1 schematically illustrates an overall structural schematic of a cryogenic cooling system according to an embodiment of the invention;
fig. 2 schematically shows a flowchart of a method of calculating a final value of opening degree of each cooler of the intercooler bank of the control method of the low-temperature cooling system according to the embodiment of the present invention;
FIG. 3 schematically illustrates a flow chart of a method for calculating a final value of a rotational speed of an electronically controlled water pump of a method for controlling a cryogenic cooling system according to an embodiment of the present disclosure;
FIG. 4 schematically illustrates a flow chart of a method of calculating a final value of a first opening degree of a main cooler of a method of controlling a cryogenic cooling system according to an embodiment of the present invention;
fig. 5 schematically shows a flowchart of a method of calculating a final value of a second opening degree of the low-pressure EGR cooler in the control method of the low-temperature cooling system according to the embodiment of the invention;
FIG. 6 schematically illustrates a flowchart of a particular method of calculating a final value of a rotational speed of an electronically controlled water pump of a method of controlling a cryogenic cooling system according to an embodiment of the present disclosure;
FIG. 7 schematically illustrates a flow chart of a method of calculating a first correction factor for an electronically controlled water pump of a method of controlling a cryogenic cooling system according to an embodiment of the present disclosure;
fig. 8 schematically shows a flowchart of a method for calculating a second correction factor for an electronically controlled water pump of a method for controlling a cryogenic cooling system according to an embodiment of the invention.
The reference numbers are as follows:
10: a first temperature sensor;
20: a second temperature sensor;
30: a third temperature sensor.
Detailed Description
Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.
It is to be understood that the terminology used herein is for the purpose of describing particular example embodiments only, and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" may be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises," "comprising," "including," and "having" are inclusive and therefore specify the presence of stated features, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and/or groups thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order described or illustrated, unless specifically identified as an order of performance. It should also be understood that additional or alternative steps may be used.
Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as "first," "second," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
For convenience of description, spatially relative terms, such as "inner", "outer", "lower", "below", "upper", "above", and the like, may be used herein to describe one element or feature's relationship to another element or feature as illustrated in the figures. Such spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "below" or "beneath" other elements or features would then be oriented "above" or "over" the other elements or features. Thus, the example term "below … …" can include both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
Fig. 1 schematically shows an overall structural view of a cryogenic cooling system according to an embodiment of the present invention. The invention provides a low-temperature cooling system, a vehicle and a control method of the low-temperature cooling system. As shown in fig. 1, the cryogenic cooling system of the present invention includes a low temperature circulating radiator, an electric control water pump, an electric control proportional valve, an intercooler set and an expansion tank, wherein a liquid outlet end of the low temperature circulating radiator is communicated with a liquid inlet end of the electric control water pump, a liquid outlet end of the electric control water pump is communicated with a liquid inlet end of the electric control proportional valve, a liquid outlet end of the electric control proportional valve is communicated with a liquid inlet end of the intercooler set, a liquid inlet end of the expansion tank is communicated with a liquid outlet end of the intercooler set, and a liquid outlet end of the expansion tank is communicated with a liquid inlet end of the low temperature circulating radiator.
By using the low-temperature cooling system in the technical scheme, the electric control proportional valve is adopted to carry out intelligent proportional distribution on the intercooler group, the cooling capacity of each cooler in the intercooler group can be fully exerted, the waste phenomenon of cooling intensity is reduced, meanwhile, the electric control water pump is adopted to control the flow of cooling liquid, the cooling intensity of the intercooler group can be ensured on the premise of low energy consumption, and the energy consumption of the whole low-temperature cooling system is saved.
In some embodiments of the invention, the intercooler bank includes an interstage cooler, a main cooler, and a low pressure EGR cooler, the interstage cooler, the main cooler, and the low pressure EGR cooler being arranged in parallel. Because the cooling intensity of each intercooler of the intercooler group is different, the parallel arrangement can respectively realize the full play of the cooling capacity of each cooler, the waste phenomenon of the cooling intensity is greatly reduced, and the working efficiency of the low-temperature cooling system is improved.
In some embodiments of the present invention, the liquid outlet end of the main cooler is provided with a first temperature sensor 10 for monitoring the temperature value of the liquid outlet end of the main cooler, so as to facilitate the subsequent correction and feedback of the initial value of the first opening degree. And the liquid outlet end of the low-pressure EGR cooler is provided with a second temperature sensor 20 for monitoring the temperature value of the liquid outlet end of the low-pressure EGR cooler, so that the second opening initial value can be corrected and fed back conveniently. And a third temperature sensor 30 is arranged at the liquid outlet end of the interstage cooler and used for monitoring the temperature value of the liquid outlet end of the interstage cooler, so that a second correction value can be conveniently calculated subsequently, and the final rotating speed value of the electric control water pump can be obtained.
The invention also provides a vehicle with the low-temperature cooling system.
By using the vehicle in the technical scheme, the electric control proportional valve is adopted to carry out intelligent proportional distribution on the intercooler group, the cooling capacity of each cooler in the intercooler group can be fully exerted, the waste phenomenon of cooling intensity is reduced, meanwhile, the electric control water pump is adopted to control the flow of cooling liquid, the cooling intensity of the intercooler group can be ensured on the premise of low energy consumption, and the energy consumption of the whole low-temperature cooling system is saved.
The present invention also proposes a method for controlling a cryogenic cooling system, as shown in fig. 2 and 3, implemented according to the above cryogenic cooling system, the method comprising:
obtaining the rotating speed of an engine and the circulating fuel injection quantity of the engine;
obtaining a first opening final value of an electric control proportional valve based on a main cooler and a second opening final value of the electric control proportional valve based on a low-pressure EGR cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
obtaining a third opening final value of the interstage cooler according to the first opening final value and the second opening final value;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine.
By using the control method of the low-temperature cooling system in the technical scheme, the opening degree is intelligently and proportionally distributed to the intercooler group by adopting the electric control proportional valve, the cooling capacity of each cooler in the intercooler group can be fully exerted, the waste phenomenon of cooling intensity is reduced, meanwhile, the rotating speed of the electric control water pump is accurately calculated so as to control the flow of cooling liquid, the cooling intensity of the intercooler group can be ensured on the premise of low energy consumption, and the energy consumption of the whole low-temperature cooling system is saved.
Specifically, since the opening of the electronically controlled proportional valve has a certain limit value, when the first opening final value and the second opening final value are known, the corresponding third opening final value can be obtained by sequentially subtracting the first opening final value and the second opening final value from the total opening.
As shown in fig. 4, the step of obtaining a final value of a first opening degree of the electrically controlled proportional valve based on the main cooler according to the engine speed and the engine cycle fuel injection amount includes:
obtaining a first temperature set value of a main cooler and a first opening initial value of an electric control proportional valve based on the main cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
acquiring a first temperature value of a first temperature sensor;
obtaining a first temperature difference value of the main cooler according to the first temperature value and the first temperature set value;
and obtaining a final first opening value of the electric control proportional valve based on the main cooler according to the first temperature difference value and the initial first opening value.
Specifically, according to the method and the device, the first temperature set value of the main cooler can be obtained through the measured engine speed and the engine circulating fuel injection quantity and according to the query of the main cooler rear temperature MAP. And obtaining a first opening initial value of the electronic control proportional valve based on the main cooler through the measured engine speed and the engine circulating fuel injection quantity and according to the query of the main cooler electronic control proportional valve opening MAP (MAP). And calculating a first temperature difference value through a first temperature set value and a first temperature value, then correcting and feeding back a first opening initial value through a PID (proportion integration differentiation) controller, further obtaining a first opening final value of the electric control proportional valve based on the main cooler, and transmitting the parameter to the electric control proportional valve, so that the corresponding proportional opening is performed on the main cooler, and the cooling capacity of the main cooler is fully exerted.
As shown in fig. 5, the step of obtaining a final value of a second opening degree of the electrically controlled proportional valve based on the low-pressure EGR cooler according to the engine speed and the engine cycle fuel injection amount includes:
obtaining a second temperature set value of the low-pressure EGR cooler and a second opening initial value of an electric control proportional valve based on the low-pressure EGR cooler according to the rotating speed of the engine and the circulating fuel injection quantity of the engine;
acquiring a second temperature value of a second temperature sensor;
obtaining a second temperature difference value of the low-pressure EGR cooler according to the second temperature value and the second temperature set value;
and obtaining a second opening final value of the electric control proportional valve based on the low-pressure EGR cooler according to the second temperature difference value and the second opening initial value.
Specifically, according to the invention, the second temperature set value of the low-temperature EGR cooler can be obtained through the measured engine speed and the engine circulating fuel injection quantity and according to the query of the temperature MAP after the low-temperature EGR cooler. And obtaining a second opening initial value of the electric control proportional valve based on the low-temperature EGR cooler through the measured engine rotating speed and the engine circulating fuel injection quantity and according to the query of the MAP of the opening MAP of the electric control proportional valve of the low-temperature EGR cooler. And calculating a second temperature difference value through a second temperature set value and a second temperature value, then correcting and feeding back a second opening initial value through a PID (proportion integration differentiation) controller, further obtaining a second opening final value based on an electric control proportional valve of the low-temperature EGR cooler, and transmitting the parameter to the electric control proportional valve, so that the corresponding proportional opening is carried out on the low-temperature EGR cooler, and the cooling capacity of the low-temperature EGR cooler is fully exerted.
As shown in fig. 6, the step of obtaining the final rotation speed value of the electronically controlled water pump according to the engine rotation speed and the engine cycle fuel injection amount includes:
obtaining an initial value of the rotating speed of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine;
acquiring a first correction coefficient;
obtaining a rotating speed correction value of the electric control water pump according to the rotating speed initial value and the first correction coefficient;
acquiring a second correction coefficient;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed correction value and the second correction coefficient.
Specifically, the initial value of the rotating speed of the electric control water pump can be obtained through the measured rotating speed of the engine and the circulating fuel injection quantity of the engine and according to the query of the MAP of the rotating speed MAP of the electric control water pump. The rotation speed initial value and the first correction coefficient are multiplied to obtain a rotation speed correction value, then the rotation speed correction value and the second correction coefficient are multiplied to obtain a final rotation speed value, and the final rotation speed value is transmitted to the electric control water pump.
As shown in fig. 7, the method of acquiring the first correction coefficient includes:
acquiring a speed value of a current vehicle;
and obtaining a first correction coefficient according to the vehicle speed value.
Specifically, in the invention, the first correction coefficient can be obtained by measuring the current vehicle speed value and correcting the query of the CUR map according to the radiator efficiency. And obtaining a rotation speed correction value through multiplication of the rotation speed initial value and the first correction coefficient. Therefore, the rotating speed of the electric control water pump can be corrected more accurately, and the accuracy and the working efficiency of the whole low-temperature cooling system are improved.
As shown in fig. 8, the method of acquiring the second correction coefficient includes:
obtaining a third temperature set value of the low-pressure EGR cooler according to the rotating speed of the engine and the circulating fuel injection quantity of the engine;
acquiring a third temperature of a third temperature sensor;
obtaining a third temperature difference value according to the third temperature and a third temperature set value;
and obtaining a second correction coefficient according to the third temperature difference value and the third temperature set value.
Specifically, in the present invention, the third temperature setting for the intercooler is derived from the measured engine speed and engine cycle fuel injection and from a lookup of the after-intercooler temperature MAP. And calculating a third temperature difference value according to the third temperature set value and the third temperature value, dividing the third temperature difference value by the third temperature set value, and according to the post-intercooler temperature correction CUR map, performing corresponding query to obtain a second correction coefficient. And the final rotating speed value is obtained through multiplication of the rotating speed correction value and the second correction coefficient. Therefore, the rotating speed of the electric control water pump can be corrected more accurately, and the accuracy and the working efficiency of the whole low-temperature cooling system are improved.
Further, the main cooler rear temperature MAP MAP, the main cooler electronic control proportional valve opening MAP MAP, the low-temperature EGR cooler rear temperature MAP MAP, the low-temperature EGR cooler electronic control proportional valve opening MAP MAP, the electronic control water pump rotating speed MAP MAP, the radiator efficiency correction CUR MAP, the inter-stage cooler rear temperature MAP MAP and the inter-stage cooler rear temperature correction CUR MAP are obtained by carrying out corresponding calibration tests, and the calibration tests belong to common knowledge in the field, so the invention is not elaborated.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (6)
1. A method of controlling a cryogenic cooling system, the method being practiced with a cryogenic cooling system comprising:
a low temperature circulating radiator;
the liquid outlet end of the low-temperature circulating radiator is communicated with the liquid inlet end of the electric control water pump;
the liquid outlet end of the electric control water pump is communicated with the liquid inlet end of the electric control proportional valve;
the liquid outlet end of the electric control proportional valve is communicated with the liquid inlet end of the intercooler group;
the liquid inlet end of the expansion water tank is communicated with the liquid outlet end of the intercooler group, and the liquid outlet end of the expansion water tank is communicated with the liquid inlet end of the low-temperature circulating radiator;
the intercooler bank including an interstage cooler, a main cooler, and a low pressure EGR cooler, the interstage cooler, the main cooler, and the low pressure EGR cooler arranged in parallel;
the control method comprises the following steps:
obtaining the rotating speed of an engine and the circulating fuel injection quantity of the engine;
obtaining a first opening final value of an electric control proportional valve based on a main cooler and a second opening final value of the electric control proportional valve based on a low-pressure EGR cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
obtaining a third opening final value of an electric control proportional valve based on the interstage cooler according to the first opening final value and the second opening final value;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine.
2. The method of claim 1, wherein deriving a final value for a first opening of a main cooler-based electronically controlled proportional valve based on the engine speed and the engine cycle injection comprises:
obtaining a first temperature set value of the main cooler and a first opening initial value of an electric control proportional valve based on the main cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
acquiring a first temperature value of a first temperature sensor;
obtaining a first temperature difference value of the main cooler according to the first temperature value and the first temperature set value;
and obtaining a first opening final value of the electric control proportional valve based on the main cooler according to the first temperature difference value and the first opening initial value.
3. The method of claim 1, wherein deriving a final value for a second opening of an electronically controlled proportional valve based on the low-pressure EGR cooler based on the engine speed and the engine cycle charge comprises:
obtaining a second temperature set value of the low-pressure EGR cooler and a second opening initial value of an electric control proportional valve based on the low-pressure EGR cooler according to the engine rotating speed and the engine circulating fuel injection quantity;
acquiring a second temperature value of a second temperature sensor;
obtaining a second temperature difference value of the low-pressure EGR cooler according to the second temperature value and the second temperature set value;
and obtaining a second opening final value of the electric control proportional valve based on the low-pressure EGR cooler according to the second temperature difference value and the second opening initial value.
4. The method of claim 1, wherein the step of deriving a final speed value for the electronically controlled water pump based on the engine speed and the engine cycle charge comprises:
obtaining an initial rotating speed value of the electric control water pump according to the rotating speed of the engine and the circulating fuel injection quantity of the engine;
acquiring a first correction coefficient;
obtaining a rotating speed correction value of the electric control water pump according to the rotating speed initial value and the first correction coefficient;
acquiring a second correction coefficient;
and obtaining a final rotating speed value of the electric control water pump according to the rotating speed correction value and the second correction coefficient.
5. The method of claim 4, wherein the step of deriving the first correction factor comprises:
acquiring a speed value of a current vehicle;
and obtaining a first correction coefficient according to the vehicle speed value.
6. The method of claim 4, wherein the step of deriving the second correction factor comprises:
obtaining a third temperature set value of the interstage cooler according to the engine speed and the engine cycle fuel injection quantity;
acquiring a third temperature of a third temperature sensor;
obtaining a third temperature difference value according to the third temperature and the third temperature set value;
and obtaining a second correction coefficient according to the third temperature difference value and the third temperature set value.
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| CN114763762B (en) * | 2021-06-02 | 2023-06-23 | 长城汽车股份有限公司 | Vehicle inter-cooling system control method and system |
| CN114233459B (en) * | 2021-11-08 | 2023-03-24 | 潍柴动力股份有限公司 | Engine cooling system and control method |
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| CN108223097A (en) * | 2017-12-08 | 2018-06-29 | 中国北方发动机研究所(天津) | A kind of engine high/low temperature dual cycle cooling system |
| JP7000262B2 (en) * | 2018-06-19 | 2022-01-19 | トヨタ自動車株式会社 | Cooling control device |
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