Patent Publication Number: US-11022024-B2

Title: Vehicle thermal management system applying an integrated thermal management valve and a cooling circuit control method thereof

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application claims priority to Korean Patent Application No. 10-2019-0133838, filed on Oct. 25, 2019, which is incorporated herein by reference in its entirety. 
     BACKGROUND OF THE DISCLOSURE 
     Field of the Disclosure 
     The present disclosure relates to a vehicle thermal management system, and more particularly, to a cooling circuit control of a vehicle thermal management system. The cooling circuit control of the vehicle thermal management system may control the flow rate of coolant for a turbocharger by an electronic water pump and a smart control valve in addition to a variable separation cooling control of an integrated thermal management valve, thereby preventing turbo boiling during the engine stop (for example, IG Key Off) together with the fast warm-up of the coolant at the warm-up of an engine. 
     Description of Related Art 
     In general, simultaneously satisfying both high fuel economy and high performance is a representative trade-off problem of the fuel economy-performance of gasoline-diesel vehicles. One method for solving the trade-off problem is, for example, to improve the performance of a Vehicle Thermal Management System (VTMS). 
     The reason to improve the performance of the VTMS to solve the trade-off problem is because the VTMS may be constructed to associate an engine cooling system, an Exhaust Gas Recirculation (EGR) system, an Auto Transmission Fluid (ATF) system, and a heater system with an engine. The VTMS may effectively distribute and control high temperature coolant of the engine transmitted to each of the systems according to the vehicle or the engine operating condition, thereby simultaneously satisfying high fuel economy and high performance. 
     Therefore, the VTMS is a design factor in which the efficiency of an engine coolant distribution control is very important. To this end, some of a plurality of heat exchange systems associated with the engine maintains a high coolant temperature while others maintain a low coolant temperature, such that it is necessary to use an Integrated Thermal Management Valve (ITM, hereinafter referred to as ITM) for the coolant distribution control to efficiently control the plurality of heat exchange systems at the same time. 
     For example, the ITM has an inlet into which the engine coolant flows and has four ports so that the received engine coolant flows out in different directions. The cooling system, the Exhaust Gas Recirculation (EGR) system, the Auto Transmission Fluid (ATF) system, and the heater system may be associated in four ways by four ports, thereby optimizing the heat exchange effect of the engine coolant in which the temperature varies according to the operating state of the engine. 
     In this case, the cooling system may be a radiator for lowering the engine coolant temperature by exchanging heat with the outside air. The EGR system may be an EGR cooler for lowering the temperature of the EGR gas transmitted to the engine among the exhaust gas by exchanging heat with the engine coolant. The ATF system may be an oil warmer for raising the ATF temperature by exchanging heat with the engine coolant. The heater system may be a heater core for raising the outside air by exchanging heat with the engine coolant. 
     Furthermore, the ITM performs an ITM valve opening control by using a temperature detection value of a coolant temperature sensor provided at the coolant inlet/outlet sides of the engine in the respective coolant controls of the EGR cooler, the oil warmer, and the heater core, such that it is more effective to reduce the fuel consumption while enhancing the entire cooling efficiency of the engine. 
     The contents described in Description of Related Art are to help the understanding of the background of the present disclosure and may include what is not previously known to those of ordinary skill in the art to which the present disclosure pertains. 
     However, in recent years, fuel economy improvement demands that are further strengthened for gasoline/diesel vehicles require VTMS performance improvement, which leads to the performance improvement demand for an engine coolant distribution control of an ITM. 
     The reason for the performance improvement demand is because the ITM may further enhance the efficiency of the engine coolant distribution control by changing an ITM layout that connects an engine and a system. 
     For example, the ITM layout is more effective to be configured to firstly enable a variable flow pattern control of engine coolant in an engine, to secondly enable the position optimization of any one among the cooling/EGR/ATF/heater systems, and to thirdly enable the optimization of the exhaust heat recovery control performance. 
     SUMMARY OF THE DISCLOSURE 
     Therefore, an object of the present disclosure considering the above point is to provide a vehicle thermal management system that applies an integrated thermal management valve and a cooling circuit control method thereof, which may apply a layer valve body to the integrated thermal management valve. Thereby, the ITM layout capable of a variable flow pattern control of the engine coolant in the engine, the optimal position selection of the engine-associated system, and the exhaust heat recovery optimal control are implemented. In particular, the vehicle thermal management system and the cooling circuit control method may control the flow rate of coolant for a turbocharger by associating an electronic water pump with a Smart Single Valve (SSV) in the four-port ITM layout, thereby preventing turbo boiling during the engine stop (for example, IG Key Off) together with the fast warm-up of the coolant at the warm-up of an engine. 
     A vehicle thermal management system according to the present disclosure includes an Integrated Thermal Management Valve (ITM) for receiving engine coolant through a coolant inlet connected to an engine coolant outlet of an engine, and for distributing the coolant flowing out toward a High Temperature (HT) radiator through a coolant outlet flow path connected to a heat exchange system. The heat exchanger system includes at least one among a heater core, an EGR cooler, an oil warmer, an ATF warmer, and the HT radiator; a mechanic water pump positioned at the front end of an engine coolant inlet of the engine. The thermal management system includes a coolant branch flow path branched at the front end of the engine coolant inlet to be connected to a turbocharger, an SSV for adjusting a coolant flow flowing out from the turbocharger on the coolant branch flow path, and a bypass coolant flow path connected with the coolant branch flow path through the SSV, and comprising an electronic water pump. 
     In an embodiment, the heat exchange system may further include a Low Temperature (LT) radiator and an intercooler installed on the bypass coolant flow path to be received the coolant of the turbocharger through the electronic water pump. 
     In an embodiment, the coolant outlet flow path may include a radiator outlet flow path connected to the HT radiator, a first distribution flow path connected to the heater core or the EGR cooler, and a second distribution flow path connected to the oil warmer or the ATF warmer. 
     In an embodiment, the first distribution flow path may form a leak hole out of which some flow is supplied to an EGR cooler directional outlet flow path port. 
     In an embodiment, the engine coolant outlet may include an engine head coolant outlet and an engine block coolant outlet. The coolant inlet may include an engine head coolant inlet connected with the engine head coolant outlet and an engine block coolant inlet connected with the engine block coolant outlet. 
     In an embodiment, the valve opening of the ITM may form the opening or closing of the engine head coolant inlet and the engine block coolant inlet oppositely. 
     In an embodiment, the opening of the engine head coolant inlet may form a Parallel Flow, in which the coolant flows out to the engine head coolant outlet, inside an engine. The opening of the engine block coolant inlet may form a Cross Flow, in which the coolant flows out to the engine block coolant outlet, inside an engine. 
     Further, a cooling circuit control method of a vehicle thermal management system according to the present disclosure includes: distributing the engine coolant flowing out toward a HT radiator to a heat exchange system including at least one among a heater core, a LT radiator, an EGR cooler, an oil warmer, an ATF warmer, and an intercooler by flowing the coolant of an engine circulated to a mechanic water pump and the HT radiator from an ITM into an engine head coolant inlet and an engine block coolant inlet, and joining the coolant having passed through the turbocharger in a coolant branch flow path branched from the mechanic water pump side to be connected to the turbocharger; connecting a bypass coolant flow path, in which an electronic water pump, the intercooler, and the LT radiator are disposed, with the coolant branch flow path by a SSV; and performing any one among a STATE  1 , a STATE  2 , a STATE  3 , a STATE  4 , a STATE  5 , a STATE  6 , a STATE  7 , and a STATE  8  as an engine coolant control mode of a vehicle thermal management system under a valve opening control of the ITM and the SSV by a valve controller. 
     In an embodiment, the valve controller may determine the operating condition with vehicle operating information detected through a vehicle thermal management system. The operating condition may be applied as a transition condition for switching a STATE while determining an operation of controlling the STATE  1 , the STATE  2 , the STATE  3 , the STATE  4 , the STATE  5 , the STATE  6 , and the STATE  7 . 
     In an embodiment, in the STATE  1 , the ITM may open the engine head coolant inlet while it closes the engine block coolant inlet, the radiator outlet flow path, the first distribution flow path, and the second distribution flow path, and the SSV opens the coolant branch flow path to the mechanic water pump side. 
     In an embodiment, in the STATE  2 , the ITM may partially open the first distribution flow path and the second distribution flow path while opening the engine head coolant inlet while it closes the engine block coolant inlet and the radiator outlet flow path. The SSV may open the coolant branch flow path to the mechanic water pump side. 
     In an embodiment, in the STATE  3 , the ITM may partially open the second distribution flow path while opening the engine head coolant inlet and the first distribution flow path while it closes the engine block coolant inlet and the radiator outlet flow path. The SSV may open the coolant branch flow path to the mechanic water pump side. 
     In an embodiment, in the STATE  4 , the ITM may partially open the radiator outlet flow path while opening the engine head coolant inlet  3 A- 1 , the first distribution flow path, and the second distribution flow path while it closes the engine block coolant inlet. The SSV may open the coolant branch flow path to the mechanic water pump side. 
     In an embodiment, in the STATE  5 , the ITM  1  may close the engine head coolant inlet while it partially opens the radiator outlet flow path, the first distribution flow path, and the second distribution flow path while opening the engine block coolant inlet. The SSV may open the coolant branch flow path to the mechanic water pump side while it closes it to the electronic water pump side. 
     In an embodiment, in the STATE  6 , the ITM may close the engine head coolant inlet while it opens the engine block coolant inlet, the radiator outlet flow path, the first distribution flow path, and the second distribution flow path. The SSV may open the coolant branch flow path to the mechanic water pump side while it closes it to the electronic water pump side. 
     In an embodiment, in the STATE  7 , the ITM may close the engine head coolant inlet, the radiator outlet flow path, and the second distribution flow path while it opens the engine block coolant inlet and the first distribution flow path. The SSV may open the coolant branch flow path to the mechanic water pump side while it closes it to the electronic water pump side. 
     In an embodiment, the STATE  1 -the STATE  4  may form a Parallel Flow inside the engine by opening the engine head coolant inlet and closing the engine block coolant inlet. The Parallel Flow may use the engine head coolant outlet, through which the coolant is communicated with the engine head coolant inlet, as a main circulation passage. 
     In an embodiment, the STATE  5 -the STATE  7  may form a Cross Flow inside the engine by opening the engine block coolant inlet and closing the engine head coolant inlet. The Cross Flow may use the engine block coolant outlet, through which the coolant is communicated with the engine block coolant inlet, as a main circulation passage. 
     In an embodiment, in the STATE  8 , the ITM may close the engine head coolant inlet, the first distribution flow path, and the second distribution flow path while it opens the engine block coolant inlet and the radiator outlet flow path to open it to the maximum cooling position according to the engine stop. The SSV may close the coolant branch flow path to the mechanic water pump side while it opens it to the electronic water pump side so that the coolant flows to the turbocharger during an operating time of the electronic water pump. 
     Further, an integrated thermal management valve according to the present disclosure flows in and out engine coolant flowing out from an engine by the rotation of first, second, and third layer balls inside a valve housing. The valve housing includes: a housing heater port forming a second direction flow path flowing out the engine coolant to an EGR cooler or a heater core side; an oil warmer port forming a third direction flow path flowing out to an oil warmer or an ATF warmer side; and a radiator port forming a first direction flow path flowing out to a radiator side. 
     In an embodiment, the first layer ball and the second layer ball may flow the engine coolant from the inside of the valve housing to the outside thereof. The third layer ball may flow the engine coolant from the outside of the valve housing to the inside thereof. 
     In an embodiment, the first layer ball may form a channel flow path communicated with the oil warmer port, the second layer ball may form a channel flow path communicated with the heater port, and the third layer ball may form a channel flow path communicated with the radiator outlet. 
     In an embodiment, the channel flow path of the third layer ball may be formed in the shape having one end tapered toward the channel end. The channel flow path may form a head flow path in the head direction through an engine head coolant inlet connected to an engine head coolant outlet of the engine, and a block flow path in the block direction through an engine block coolant inlet connected to an engine block coolant outlet of the engine. The opening and closing of the head directional flow path and the block directional flow path may be formed oppositely from each other. 
     In an embodiment, the first layer ball, the second layer ball, and the third layer ball may be rotated by an actuator to be controlled by the valve opening of the ITM. The ITM valve opening control may form an engine coolant control mode that applies any one among STATES  1 ,  2 ,  3 ,  4 ,  5 ,  6 ,  7 , and  8  as a variable cooling control by changing the opening and closing of the first directional flow path, the second directional flow path, and the third directional flow path. 
     In an embodiment, the engine coolant control mode may be implemented by performing the ITM valve opening control by a valve controller that uses, as input data, an engine coolant temperature outside an engine detected by a first WTS and an engine coolant temperature inside the engine detected by a second WTS. 
     The present disclosure has the following advantages by improving the integrated thermal management valve and the vehicle thermal management system at the same time. 
     For example, the operations and effects that occur in the integrated thermal management valve are described below. First, it is possible to constitute the layer ball having a cylindrical structure, thereby implementing the four-port ITM layout capable of the variable flow pattern control of the engine coolant in the engine, the optimal position selection of the engine-associated system, and the exhaust heat recovery optimal control. Second, it is possible to implement the engine fast warm-up in the flow stop control mode of the STATE  1  and the micro flow rate control mode of the STATE  2 , and the air-conditioning fast warm-up in the heating control mode of the STATE  3 , and the maximum heating control mode of the STATE  7  with respect to the warm-up mode of the STATES  1  and  2  or the STATE  7  among the coolant control mode classified into the STATES  1 - 8 . Third, it is possible to implement the temperature adjustment mode in the temperature adjustment control mode of the STATE  4  and the high speed/high load control mode of the STATE  6  among the coolant control modes classified into the STATES  1 - 8 . Fourth, it is possible to prevent the turbo boiling during the engine stop (for example, IG Key Off) together with the fast warm-up of the coolant at the warm-up of the engine in the turbocharger side coolant flow rate control associating the electronic water pump with the SSV. 
     For example, the operations and effects that occur in the vehicle thermal management system applying the ITM layout of the layer ball type integrated thermal management valve are described below. First, it is possible to improve the fuel economy in the normal load condition by performing the variable flow pattern control in the engine in the Parallel Flow, in which the cylinder block temperature is raised to be advantage for the friction improvement, to improve the knocking in the high load condition in the Cross Flow, in which the cylinder block temperature is lowered, and to improve the performance/fuel economy/durability at the same time by improving the knocking and the friction. Second, it is possible to associate the SSV and the Electric Water Pump (EWP) of a water-cooled intercooler with the ITM of the four-port ITM layout, thereby implementing the fast warm-up of the coolant at the warm-up of the engine and preventing the turbo boiling at Key Off. Third, it is possible to improve the heating performance by the fast warm-up, thereby deleting the Positive Temperature Coefficient Heater (PTC heater) to save in costs, and further, to improve the warm-up performance of the coolant/engine oil/transmission oil at the same time, thereby also enhancing the merchantability of the vehicle through the display of the grade improvement of the label fuel economy (for example, indication of the energy consumption efficiency grade). 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a diagram illustrating an example of a vehicle thermal management system applying a layer ball type integrated thermal management valve according to the present disclosure. 
         FIG. 2  is a diagram illustrating an example according to the present disclosure in which a layer ball of the integrated thermal management valve constitutes a triple layer as first, second, and third layer balls. 
         FIG. 3  is a diagram illustrating an example according to the present disclosure in which the opening/closing of outlet ports of an engine head and an engine block at rotation of the third layer ball are applied oppositely. 
         FIG. 4  is a diagram illustrating a state where engine coolant flows out to an ITM while forming a Parallel Flow or a Cross Flow inside an engine by the opposite operation between the outlet ports of the engine head and the engine block according to an example of the present disclosure. 
         FIGS. 5A   5 B and  6  are operational flowcharts of a cooling circuit control method of a vehicle thermal management system according to an example of the present disclosure. 
         FIGS. 7A and 7B  are a diagram illustrating a mutual associated control state of an ITM and an SSV of a valve controller according to STATES  1 - 7  of an engine coolant control mode according to an example of the present disclosure. 
     
    
    
     DESCRIPTION OF SPECIFIC EMBODIMENTS 
     Hereinafter, various embodiments of the present disclosure are described in detail with reference to the accompanying drawings, and since these embodiments may be implemented by those of ordinary skill in the art to which the present disclosure pertains in various different forms, they are not limited to the embodiment described herein. 
     Referring to  FIG. 1 , a Vehicle Thermal Management System (hereinafter referred to as VTMS)  100  includes: an Integrated Thermal Management Valve (hereinafter referred to as ITM)  1  through which engine coolant of an engine  110  flows in and out; a coolant circulation system  100 - 1  for adjusting the temperature of the engine coolant, a plurality of coolant distribution systems  100 - 2 ,  100 - 3 ,  100 - 4  for optionally distributing the coolant of the ITM  1  to a plurality of heat exchange systems according to an engine operating condition; a Smart Single Valve (SSV)  400  for adjusting a coolant flow distributed from the ITM  1 ; a turbocharger  900 - 3  for supercharging the intake air, a coolant reservoir  900 - 2  for storing the engine coolant, and a valve controller  1000 . 
     In particular, the vehicle thermal management system  100  connects the SSV  400 , which associates the turbocharger  900 - 3  installed at the front end of the engine with the coolant circulation system  100 - 1  by a coolant branch flow path  107 , with an electronic water pump  120 B, and associates the coolant reservoir  900 - 2  with the coolant circulation system  100 - 1  and some of the plurality of coolant distribution systems  100 - 2 ,  100 - 3 ,  100 - 4  by first, second, and third reservoir degassing lines  900 - 2 A,  900 - 2 B,  900 - 2 C. 
     Therefore, the vehicle thermal management system  100  may drive the electronic water pump  120 B during a certain time to prevent turbo boiling that may occur due to stopping the engine coolant supply to the turbocharger  900 - 3  at the engine stop (for example, IG Key Off) to supply it to the turbocharger  900 - 3 , and performs the Degassing for gas, and the like flowing out together with the engine coolant while replenishing the flow rate of the engine coolant circulating the coolant circulation system  100 - 1  and the plurality of coolant distribution systems  100 - 2 ,  100 - 3 ,  100 - 4 . 
     The coolant described below refers to an engine coolant. 
     Specifically, the ITM  1  is a four-port configuration of first, second, and third layer balls  10 A,  10 B,  10 C constituting a layer ball  10 , and associates a coolant control mode (for example, STATES  1 - 7  in  FIGS. 5A, 5B and 6 ) of the vehicle thermal management system  100  with the unique operating modes (for example, B, C, D, E in  FIGS. 7A and 7B ) of the SSV  400  in the same opening condition of the ITM  1  even while performing all functions implemented by the existing four-port ITM. Thereby, heat exchange efficiency together with a fast mode switching may be enhanced. 
     Specifically, the engine  110  is a gasoline engine. The engine  110  forms an engine coolant inlet  111  into which coolant flows and an engine head coolant outlet  112 - 1  and an engine block coolant outlet  112 - 2  out which the coolant flows. The engine coolant inlet  111  is connected to a water pump  120  by a first coolant line  101  of the engine cooling system  100 - 1 . The engine head coolant outlet  112 - 1  is formed at an engine head that includes a cam shaft, a valve system, and the like to be connected with an engine head coolant inlet  3 A- 1  of the ITM  1 . The engine block coolant outlet  112 - 2  is formed at an engine block that includes a cylinder, a piston, a crankshaft, and the like to be connected with the engine block coolant inlet  3 A- 2  of the ITM  1 . 
     Further, the engine  110  includes a first Water Temperature Sensor (WTS)  130 - 1  and a second Water Temperature Sensor (WTS)  130 - 2 . The first WTS  130 - 1  detects the temperature of the engine coolant inlet  111  side of the engine  110 . The second WTS  130 - 2  detects the temperature of the engine coolant outlet  112  side of the engine  110 , respectively to transmit them to the valve controller  1000 . 
     Specifically, the coolant circulation system  100 - 1  is composed of a mechanic water pump  120 A and a High Temperature (HT) radiator  300 A and forms a coolant circulation flow of the engine  110  by the first coolant line  101 . Further, the coolant circulation system  100 - 1  is associated with the turbocharger  900 - 3  by connecting the coolant branch flow path  107  to the water pump outlet end of the mechanic water pump  120 A. 
     For example, the mechanic water pump  120 A pumps the engine coolant to form the coolant circulation flow. To this end, the mechanic water pump  120 A is connected with the crankshaft of the block by a belt or a chain to pump the engine coolant to the block side of the engine  110 . The HT radiator  300 A cools high temperature coolant flowing out from the engine  110  by exchanging heat with the air. 
     For example, the first coolant line  101  is connected to the radiator outlet flow path  3 B- 1  of the coolant outlet flow path  3 B of the ITM  1  (see  FIG. 2 ) so that the coolant flowing out from the ITM  1  is distributed, and is connected with the first reservoir degassing line  900 - 2 A connecting the ITM  1  and the coolant reservoir  900 - 2  by the second reservoir degassing line  900 - 2 B. 
     Specifically, the plurality of coolant distribution systems  100 - 2 ,  100 - 3 ,  100 - 4  include the first coolant distribution system  100 - 2 , the second coolant distribution system  100 - 3 , and the third coolant distribution system  100 - 4 . The heat exchange system is composed of: a heater core  200  for raising the outside air temperature by exchanging heat with the engine coolant, a Low Temperature (LT) radiator  300 B for cooling the engine coolant by exchanging heat with the air; an EGR cooler  500  for lowering the EGR gas temperature transmitted to the engine of the exhaust gas by exchanging heat with the engine coolant; an oil warmer  600  for raising the engine oil temperature by exchanging heat with the engine coolant; an ATF warmer  700  for raising the ATF temperature (transmission fluid temperature) by exchanging heat with the engine coolant; and an intercooler  900 - 2  for controlling the supercharged air temperature by the turbocharger  900 - 3 . 
     For example, the first coolant distribution system  100 - 2  forms the coolant circulation flow by the second coolant flow path  102  that associates the heater core  200  and the EGR cooler  500  with the ITM  1 . In this case, the heater core  200  and the EGR cooler  500  are arranged in series, and the second coolant line  102  is arranged in parallel with the first coolant line  101 . Further, the second coolant flow path  102  is formed in one line by being joined as one with the first coolant line  100 - 1  via a junction at the front end of the mechanic water pump  120 A. 
     In particular, the second coolant flow path  102  is connected with the first distribution flow path  3 B- 2  of the coolant outlet flow path  3 B of the ITM  1  to form the coolant circulation flow by the coolant distribution using a different path from the radiator outlet flow path  3 B- 1  (see  FIG. 2 ). Therefore, the first coolant distribution system  100 - 2  receives the coolant by the first distribution flow path  3 B- 2  of the ITM  1  to circulate it in the second coolant flow path  102 . 
     For example, the second coolant distribution system  100 - 3  forms the coolant circulation flow by the third coolant flow path  103  that associates the oil warmer  600  and the ATF warmer  700  with the ITM  1 . In this case, the oil warmer  600  and the ATF warmer  700  are arranged in series. Further, the third coolant flow path  103  is formed in one line by being joined as one with the first coolant line  100 - 1  via the junction at the front end of the mechanic water pump  120 A. 
     In particular, the third coolant flow path  103  is connected with the second distribution flow path  3 B- 3  of the coolant outlet flow path  3 B of the ITM  1  to form the coolant circulation flow by the coolant distribution using a different path from the radiator outlet flow path  3 B- 1  and the first distribution flow path  3 B- 2 . Therefore, the second coolant distribution system  100 - 3  receives the coolant by the second distribution flow path  3 B- 3  of the ITM  1  to circulate it in a fourth coolant flow path  104 . Hereinafter, the fourth coolant flow path  104  means a bypass coolant flow path. 
     For example, the third coolant distribution system  100 - 4  forms the coolant circulation flow by the fourth coolant flow path  104  connecting the electronic water pump  120 B, the LT radiator  300 B, and the intercooler  900 - 1  by an auxiliary coolant flow path  104 - 1 . In this case, the LT radiator  300 B and the intercooler  900 - 1  are arranged in series. 
     Furthermore, the fourth coolant flow path  104  is connected with the coolant branch flow path  107  connecting from the turbocharger  900 - 3  to the SSV  400  by the auxiliary coolant flow path  104 - 1  to return the coolant having passed through the turbocharger  900 - 3  by an operation of the electronic water pump  120 B at the engine operation to the first coolant line  101  through the SSV  400  by the coolant branch flow path  107  while it circulates the coolant having passed through the turbocharger  900 - 3  by the operation of the electronic water pump  120 B at the engine stop to the LT radiator  300 B and the intercooler  900 - 1 . 
     In particular, the fourth coolant line  104  is connected with the coolant reservoir  900 - 2  by the third reservoir degassing line  900 - 2 C. 
     Specifically, the SSV  400  switches the opening direction of the coolant branch line  107  to the first coolant flow path  101  by the valve opening by the rotation of an SSV valve body embedded in an SSV housing to return the coolant having passed through the turbocharger  900 - 3  to the engine side by the operation of the electronic water pump  120 B or switches it to the auxiliary coolant flow path  104 - 1  connected to the fourth coolant flow path  104  to transmit the coolant having passed through the turbocharger  900 - 3  to the LT radiator  300 B or the intercooler  900 - 1  side by the operation of the electronic water pump  120 B. 
     For example, the SSV  400  forms an inner space in which the engine coolant bypassed to the SSV housing flows in and out, and the SSV valve body accommodated in the inner space of the SSV housing is controlled by the valve controller  1000  to form the SSV valve opening. To this end, the SSV  400  is composed of a 2-way variable flow rate control valve. 
     Specifically, the coolant reservoir  900 - 2  stores the engine coolant to replenish an insufficient flow rate, and perform the degassing for the gas and foreign matters in the coolant by the first reservoir degassing line  900 - 2 A connected with the ITM  1 , the second reservoir degassing line  900 - 2 B connected with the first coolant flow path  101 , and the third reservoir degassing line  900 - 2 C connected with the fourth coolant flow path  104 . 
     Specifically, the valve controller  1000  optionally forms: the coolant flow of the first coolant flow path  101  circulating the radiator  300  of the coolant circulation system  100 - 1 ; the coolant flow of the second coolant flow path  102  circulating the heater core  200  and the EGR cooler  500  of the first coolant distribution system  100 - 2 ; and the coolant flow of the third coolant flow path  103  circulating the oil warmer  600  and the ATF warmer  700  of the second coolant distribution system  100 - 3  under the valve opening control of the ITM  1 , and the joining flow of the first coolant flow path  101  of the coolant flowing out from the turbocharger  900 - 3  or the coolant flow of the fourth coolant flow path  104  having passed through the auxiliary coolant flow path  104 - 1  under the valve opening control of the SSV  400 . 
     To this end, the valve controller  1000  shares the information of the engine controller (for example, the information inputter  1000 - 1 ) for controlling the engine system via CAN, and receives temperature detection values of first and second WTSs  130 - 1 ,  130 - 2  to control the valve opening of the ITM  1  and the SSV  400 , respectively. In particular, the valve controller  1000  has a memory in which logic or a program matching the coolant control mode (for example, STATES  1 - 8 ) (see  FIGS. 5A and 5B to 7A and 7B ) has been stored, and outputs the valve opening signals of the ITM  1  and the SSV  400 . 
     Further, the valve controller  1000  has the information inputter  1000 - 1 , and a variable separation cooling map  1000 - 2  provided with an ITM map that matches the valve opening of the ITM  1  to the engine coolant temperature condition and the operating condition according to the vehicle information and a SSV map that matches the valve opening of the SSV  400  to the engine coolant temperature condition and the operating condition according to the vehicle information. 
     In particular, the information inputter  1000 - 1  detects an IG on/off signal, a vehicle speed, an engine load, an engine temperature, a coolant temperature, a transmission fluid temperature, an outside air temperature, an ITM operating signal, accelerator/brake pedal signals, and the like to provide them as input data of the valve controller  1000 . In this case, the vehicle speed, the engine load, the engine temperature, the coolant temperature, the transmission fluid temperature, the outside air temperature, and the like are applied as the operating conditions. Therefore, the information inputter  1000 - 1  may be an engine controller for controlling the entire engine system. 
       FIGS. 2 and 3  illustrate a detailed configuration of the ITM  1 . 
     Referring to  FIG. 2 , the ITM  1  performs an engine coolant distribution control and an engine coolant flow stop control according to a variable separation cooling operation by a combination of the first layer ball  10 A, the second layer ball  10 B, and the third layer ball  10 C constituting the layer ball  10 . 
     In this case, in the four-port layout, the first layer ball  10 A is arranged in the rear direction of the vehicle, the third layer ball  10 C is arranged in the front direction of the vehicle, and the second layer ball  10 B is arranged between the first layer ball  10 A and the third layer ball  10 C. Therefore, the first layer ball  10 A is classified as a first layer, the second layer ball  10 B is classified as a second layer, and the third layer ball  10 C is classified as a third layer. 
     Furthermore, the ITM  1  includes a valve housing  3  accommodating the layer ball  10  and forming four ports; and an actuator  5  for operating the layer ball  10  under the control of the valve controller  1000 . 
     Specifically, the valve housing  3  forms an inner space in which the layer ball  10  is accommodated and forms four ports through which the engine coolant flows in and out in the inner and outer spaces. The four ports are formed of the coolant inlet  3 A forming one port and the coolant outlet flow path  3 B forming three ports. 
     For example, the coolant inlet  3 A includes an engine head coolant inlet  3 A- 1  connected to the engine head coolant outlet  112 - 1  of the engine  110  and an engine block coolant inlet  3 A- 2  connected to the engine block coolant outlet  112 - 2  of the engine  110 . Further, the coolant outlet flow path  3 B includes: a radiator outlet flow path  3 B- 1  connected with the first coolant line  101  connected to the radiator  300 ; a first distribution flow path  3 B- 2  connected with the second coolant flow path  102  connected to the heater core  200  and the EGR cooler  500 ; and a second distribution flow path  3 B- 3  connected with the third coolant flow path  103  connected to the oil warmer  600  and the ATF warmer  700 . 
     In particular, the radiator outlet flow path  3 B- 1  may be formed in a general symmetrical structure for applying a 0-100% variable control unit so that the 100% opening condition of the radiator is partially maintained to set the switching range of the mode for the variable flow pattern control. 
     Further, the valve housing  3  has a leak hole  3 C. The leak hole  3 C may flow a small amount of coolant from the first distribution flow path  3 B- 2  to the second coolant flow path  102  to supply the coolant required in the EGR cooler  500  according to the initial operation of the engine  110 , thereby improving the temperature sensitivity. In this case, the leak hole  3 C applies an existing setting value to the hole diameter. The existing setting value applies the diameter of the leak hole of about D 1.0 to 3.0 mm that may flow about 1 to 5 LPM (Liter Per Minutes) at a partial flow rate, thereby preventing condensate of the EGR cooler  500  from occurring at the engine coolant outlet side of the EGR cooler  500 . 
     Specifically, the actuator  5  is connected with a speed reducer  7  by applying a motor. In this case, the motor may be a Direct Current (DC) motor or a Step motor controlled by the valve controller  1000 . The speed reducer  7  is composed of a motor gear that is rotated by a motor and a valve gear having a gear shaft  7 - 1  for rotating the layer ball  10 . 
     Therefore, the actuator  5 , the speed reducer  7 , and the gear shaft  7 - 1  have the same configuration and operating structure as those of the general ITM  1 . However, there is a difference in that the gear shaft  7 - 1  is configured to rotate the first layer ball  10 A, the second layer ball  10 B, and the third layer ball  10 C of the layer ball  10  together at operation of the motor  6  to change a valve opening angle. 
     Referring to  FIG. 3 , the third layer ball  10 C of the first, second, and third layer balls  10 A,  10 B,  10 C has a channel flow path  13 , which oppositely forms the opening of the engine head coolant inlet  3 A- 1  and the engine block coolant inlet  3 A- 2 , formed by cutting a certain section of the ball body  11  of the hollow sphere, and has the radiator outlet flow path  3 B- 1  perforated in the ball body  11  in a circular hole. In this case, the channel flow path  13  is formed at about 180° relative to 360° of the ball body  11 . 
     In particular, if the channel flow path  13  is completely opened in a head direction section (fa) of the engine head coolant inlet  3 A- 1  according to the rotational direction of the ball body  11 , the channel flow path  13  is completely blocked in a block direction section (fb) of the engine block coolant inlet  3 A- 2  or is partially opened in the head direction section (fa) and the block direction section (fb) at the same time, and is opened or partially opened or blocked in a radiator section (fc) of the radiator outlet flow path  3 B- 1  together with the opening of one side of the heat direction section (fa) or the block direction section (fb) so that the coolant flowing into the engine head coolant inlet  3 A- 1  or the engine block coolant inlet  3 A- 2  flows out from the third layer ball  10 C to flow into the first and second layer balls  10 A,  10 B sides. 
     As a result, the coolant flowing into the first, second, and third layer balls  10 A,  10 B,  10 C flows out from the third layer ball  10 C to the first coolant flow path  101 , flows out from the second layer ball  10 B to the second coolant flow path  102 , and flows out from the first layer ball  10 A to the third coolant flow path  103 . 
     Meanwhile,  FIG. 4  illustrates an example of a coolant formation pattern of the ITM  1  using the mutual opposite opening or blocking of the engine head coolant inlet  3 A- 1  and the engine block coolant inlet  3 A- 2  of the third layer ball  10 C. In this case, the coolant formation pattern is classified into a Parallel Flow (Pt) formed in STATES  1 - 4  of the engine coolant control mode in  FIG. 7 , and a Cross Flow (Cf) formed in STATES  5 - 7  of the engine coolant control mode in  FIG. 7 . 
     For example, the Parallel Flow of coolant opens the engine head coolant inlet  3 A- 1  to communicate with the engine head coolant outlet  112 - 1  by 100% while it closes the engine block coolant inlet  3 A- 2  to be blocked from the engine block coolant outlet  112 - 2  by 100%, thereby being formed so that the coolant flows out only to the head side inside the engine  110 . In this case, the Parallel Flow raises the block temperature of the engine  110 , thereby improving fuel economy. 
     For example, the Cross Flow of the coolant opens the engine block coolant inlet  3 A- 2  to communicate with the engine block coolant outlet  112 - 2  by 100% while it closes the engine head coolant inlet  3 A- 1  to be blocked from the engine head coolant outlet  112 - 1  by 100%, thereby being formed so that the coolant flows out only to the block side inside the engine  110 . In this case, the Cross Flow lowers the block temperature of the engine  110 , thereby improving knocking and durability. 
     In particular, the valve opening of the ITM  1  may form a switching range between the Parallel Flow (Pt) and the Cross Flow (Cf). In this case, the switching range maintains the opening of the radiator flow path having the 0 to 100% symmetry setting of the variable control by 100% in a state where the flow path of the first distribution flow path  3 B- 2  of the second layer ball  10 B has continuously maintained the complete opening, thereby being implemented by a coupling control that forms the simultaneous opening section of the head direction section (fa) and the block direction section (fb) of the third layer ball  10 C. 
       FIGS. 5A, 5B and 6  illustrate a variable separation cooling control method of a coolant control mode (for example, STATES  1 - 8 ) of the vehicle thermal management system  100 . In this case, the control subject is the valve controller  1000  and the control target includes the operation of the junction and the heat exchange system in which the direction of the valve is controlled with respect to the ITM  1  and the SSV  400  in which the valve opening is controlled, respectively. 
     As illustrated, the cooling circuit control method of the vehicle thermal management system applying the ITM  1  performs determining an engine coolant control mode (S 20 ) by detecting the ITM variable control information of the heat exchange system by the valve controller  1000  (S 10 ) and then performs a variable separation cooling valve control (S 30 -S 202 ). As a result, the vehicle thermal management system control method may simultaneously implement the fast warm-up of the engine and the fast warm-up of the engine oil/transmission fluid (ATF). In particular, the vehicle thermal management system control method may improve fuel efficiency and simultaneously improve heating performance by shortening the EGR usage time point. 
     Specifically, the valve controller  1000  performs the detecting of the ITM variable control information of the heat exchange system (S 10 ) by using, as input data, an IG on/off signal, a vehicle speed, an engine load, an engine temperature, a coolant temperature, a transmission fluid temperature, an outside air temperature, an ITM operating signal, and accelerator/brake pedal signals provided by the information inputter  1000 - 1 . In other words, the operating information of the vehicle thermal management system  100  having the coolant circulation/distribution systems  100 - 1 ,  100 - 2 ,  100 - 3 ,  100 - 4 , in which the heater core, the HT/LT radiators, the EGR cooler, the oil warmer, the ATF warmer, the intercooler, and the mechanic/electronic water pumps are optionally combined by the valve controller  1000 , is detected. 
     Subsequently, the valve controller  1000  matches the valve opening of the ITM  1  with the engine coolant temperature condition by using the ITM map of the variable separation cooling map  1000 - 2  and at the same time, matches the valve opening (i.e., B, C, D, E operating modes in  FIGS. 7A and 7B ) of the SSV  400  with the engine coolant temperature condition by using the SSV map with respect to the input data of the information inputter  1000 - 1 . The valve controller  1000  performs the determining of the engine coolant control mode (S 20 ) therefrom. In this case, the determining of the engine coolant control mode (S 20 ) applies an operating condition, and the operating condition is determined by a vehicle speed, an engine load, an engine temperature, a coolant temperature, a transmission fluid temperature, an outside air temperature, and the like to be determined as a state of the different operating condition, respectively, according to its value. 
     As a result, the valve controller  1000  enters the variable separation cooling valve control (S 30 -S 202 ). For example, the variable separation cooling valve control (S 30 -S 202 ) is classified into a warm-up condition control (S 30 -S 50 ) and a requirement control (S 60  and S 70 ) in which the mode is switched by the arrival of a transition condition according to the operating condition (S 100 ), and an engine stop control (S 200 ) according to the engine stop (for example, IG OFF). 
     Specifically, the valve controller  1000  determines the necessity of the warm-up by applying the warm-up mode (S 30 ) and then enters the engine quick warm-up mode (S 40 ) or the air-conditioning quick warm-up mode (S 50 ) with respect to the warm-up condition control (S 30 -S 50 ). 
     For example, the engine quick warm-up mode (S 40 ) is performed by a flow stop control (S 43 ) according to the entry of STATE  1  (S 42 ) in the case of an engine temperature priority condition (S 41 ) while the engine quick warm-up mode (S 40 ) is performed by a heat exchange system control (S 43 - 1 ) according to the entry of STATE  2  (S 42 - 1 ) in the case of a coolant temperature sudden change prevention condition (S 41 - 1 ) rather than the engine temperature priority condition (S 41 ). For example, the air-conditioning quick warm-up mode (S 50 ) is performed by a heater control (S 53 ) according to the entry of STATE  3  (S 52 ) in the case of a fuel economy consideration condition (S 51 ) while it is performed by a maximum heating control (S 53 - 1 ) according to the entry of STATE  7  (S 52 - 1 ) in the case of an indoor heating priority condition (S 51 - 1 ) rather than the fuel economy consideration condition (S 51 ). 
     Specifically, the valve controller  1000  is classified into the temperature adjustment mode (S 60 ) and the forced cooling mode (S 70 ) with respect to the requirement control (S 60  and S 70 ). For example, the temperature adjustment mode (S 60 ) is performed by a water temperature control (S 63 ) according to the entry of STATE  4  (S 62 ) in the case of a coolant temperature adjustment condition (S 61 ) while it is performed by the high speed/high load control (S 63 - 1 ) according to the entry of STATE  6  (S 62 - 1 ) in the case of an engine load consideration condition (S 61 - 1 ) rather than a coolant temperature adjustment condition (S 61 ). For example, the forced cooling mode (S 70 ) is performed by a maximum cooling control (S 72 ) according to the entry of STATE  5  (S 71 ) in the case of the forced cooling mode condition (S 70 ). 
     Specifically, the valve controller  1000  is performed by the engine stop control (S 202 ) according to the entry of STATE  8  (S 201 ) with respect to the engine stop control (S 200 ). 
     Hereinafter, the operation of the vehicle thermal management system  100  in each of the STATES  1 - 8  is described. 
     For example, the STATE  1  (S 42 ) stops the flow of the engine coolant flowing through the engine  110  until arriving to the flow stop release temperature, thereby raising the engine temperature as quickly as possible. In this case, the arrival of the engine temperature condition when the flow stop release temperature is beyond the cold start due to the rise in the coolant temperature, or the high speed/high load condition of the rapid acceleration according to the depression of the accelerator pedal with respect to the stop of the STATE  1  (S 41 ) is set to the transition condition  100 . 
     For example, the STATE  2  (S 42 - 1 ) converges the smoothed temperature up to a target coolant temperature (for example, a warm-up temperature), thereby reducing the temperature fluctuation of the engine coolant after the flow stop release according to the switching of the STATE  1  (S 42 ). In this case, the arrival of the micro flow rate control condition of the engine coolant flow rate with respect to the stop of the STATE  2  (S 42 - 1 ) is set to the transition condition  100 . 
     For example, the STATE  3  (S 51 ) performs the flow rate control of the heater core  200  side in a flow rate maximum condition of the oil warmer  600  side in a temperature adjustment section (for example, a fuel economy section) after the warm-up of the engine  110  (however, the heater control section is used at the warm-up before the heater is turned on). In this case, an initial coolant temperature/outside air temperature of a constant temperature or more (i.e., a fuel economy priority mode switchable temperature), a coolant temperature threshold or more, and a heater operation (heater on) with respect to the stop of the STATE  3  (S 51 ) are set to the transition condition  100 . In this example, the coolant temperature threshold is set to a value that exceeds the warm-up temperature. 
     For example, the STATE  4  (S 62 ) adjusts the engine coolant temperature of the engine  110  according to the target coolant temperature. In this case, the arrival of the condition of the coolant temperature threshold or more calculated by being matched with the outlet temperature of the HT radiator  300 A with respect to the STATE  4  (S 62 ) is set to the transition condition  100 . 
     For example, the STATE  5  (S 71 ) reduces the engine coolant flow rate of the heater core  200  required for a cooling/heating control to a minimum flow rate while maintaining the engine coolant flow rates of the oil warmer  600  and the ATF warmer  700  at an appropriate amount, thereby maximally securing cooling capability under the high load condition and the uphill condition. In this case, the arrival of the condition of setting the engine coolant temperature of about 110° C. to 115° C. or more to the coolant temperature threshold with respect to the STATE  5  (S 71 ) is set to the transition condition  100 . 
     For example, the STATE  6  (S 62 - 1 ) performs the coolant temperature adjustment of the engine  110  in the variable separation cooling release condition. In this case, the arrival of the conditions of the high speed/high load operating data of the engine  110  (for example, the result value matched with the variable separation cooling map  1000 - 2 ) and the coolant temperature threshold or more with respect to the STATE  6  (S 62 - 1 ) is set to the transition condition  100 . However, it is more limited to frequently change from the STATE  6  state to other STATES by actually applying the hysteresis and/or the response delay time of the ITM  1 . In this example, the coolant temperature threshold is set to a value that exceeds the warm-up temperature. 
     For example, the STATE  7  (S 52 - 1 ) flows the engine coolant only to the heater core  200  considering low outside air temperature and initial coolant temperature in the heating operating mode of the heater during the warm-up of the engine  110  and reflects the rise in the temperature of the engine coolant to gradually flow the engine coolant to the oil warmer  600 , thereby maximally securing the heating capability. In this case, the arrival of the engine coolant temperature condition of the coolant temperature threshold or more after exceeding the warm-up temperature with respect to the STATE  7  (S 52 - 1 ) is set to the transition condition  100  moving to the STATE  3  (S 52 ). 
     For example, since the engine  110  is in the engine stop (IG off) state, the STATE  8  (S 201 ) is switched to a state where the ITM  1  has been opened by the valve controller  1000  at the maximum cooling position, and further, opens the coolant branch flow path  107  to the electronic water pump  120 B under the valve opening control of the SSV  400  to drive the electronic water pump  120 B during a certain time so that the turbocharger  900 - 3  receives the coolant even after the engine stop. Thereby, turbo boiling is prevented, which may be caused by the engine coolant supply stop. 
     Referring to  FIGS. 7A and 7B , the valve opening control of the ITM  1  and the SSV  400  of the valve controller  1000  for the STATES  1 - 7  of the engine coolant control mode is illustrated. 
     In the STATE  1 , the valve opening of the ITM  1  closes the radiator outlet flow path  3 B- 1 , the first distribution flow path  3 B- 2 , and the second distribution flow path  3 B- 3  while opening the engine head coolant inlet  3 A- 1  and closing the engine block coolant inlet  3 A- 2 . Further, the valve opening of the SSV  400  is switched to a C mode that opens the coolant branch flow path  107  to the mechanic water pump  120 A side. 
     As a result, the ITM  1  flows a small amount of coolant to the EGR cooler  500  side through the leak hole  3 C while raising the engine temperature as quickly as possible until arriving to the coolant flow stop release temperature in the Parallel Flow. Thereby, the temperature sensitivity of the EGR cooler  500  is improved. Further, the SSV  400  flows the coolant flowing out from the turbocharger  900 - 3 , which is in the exhaust flow state, to the engine  110  side, thereby quickly performing the warm-up at the initial start before the warm-up. 
     In the STATE  2 , the valve opening of the ITM  1  closes the radiator outlet flow path  3 B- 1  while opening the engine head coolant inlet  3 A- 1  and closing the engine block coolant inlet  3 A- 2  while it partially opens the first distribution flow path  3 B- 2  and the second distribution flow path  3 B- 3 . Further, the valve opening of the SSV  400  is switched to the C mode that opens the coolant branch flow path  107  to the mechanic water pump  120 A side, and if necessary, performs a D mode, which partially opens it to the electronic water pump  120 B side, at the same time. 
     As a result, the ITM  1  converges the smoothed temperature up to the target coolant temperature (for example, the warm-up temperature) in the Parallel Flow, thereby reducing the temperature fluctuation of the engine coolant after the flow stop release according to the switching of the STATE  1  (S 42 ). Further, the SSV  400  flows the coolant flowing out from the turbocharger  900 - 3 , which is in the exhaust flow state, to the engine  110  side to assist the rise in the coolant temperature after the initial start, and allows a minimum flow rate of coolant to flow through the LT radiator  300 B and the intercooler  900 - 1  according to whether the electronic water pump  120 B operates. 
     In the STATE  3 , the valve opening of the ITM  1  closes the radiator outlet flow path  3 B- 1  while opening the engine head coolant inlet  3 A- 1  and closing the engine block coolant inlet  3 A- 2  while it opens the first distribution flow path  3 B- 2  and partially opens the second distribution flow path  3 B- 3 . Further, the valve opening of the SSV  400  is switched to the C mode, which opens the coolant branch flow path  107  to the mechanic water pump  120 A side, and if necessary, performs the D mode, which partially opens it to the electronic water pump  120 B side at the same time. 
     As a result, the ITM  1  performs the flow rate control of the heater core  200  side in the maximum flow rate condition of the oil warmer  600  side in a temperature adjustment section (for example, a fuel economy section) after the warm-up in the Parallel Flow (however, the heater control section is used at the warm-up before the heater is turned on). Further, the SSV  400  flows the coolant flowing out from the turbocharger  900 - 3 , which is in the exhaust flow state, to the engine  110  side to assist the rise in the coolant temperature after the initial start, and allows a minimum flow rate of coolant to flow through the LT radiator  300 B and the intercooler  900 - 1  according to whether the electronic water pump  120 B operates. 
     In the STATE  4 , the valve opening of the ITM  1  opens the first distribution flow path  3 B- 2  and the second distribution flow path  3 B- 3  together with partially opening the radiator outlet flow path  3 B- 1  while opening the engine head coolant inlet  3 A- 1  and closing the engine block coolant inlet  3 A- 2 . Further, the valve opening of the SSV  400  is switched to the C mode, which opens the coolant branch flow path  107  to the mechanic water pump  120 A side, and if necessary, performs the D mode, which partially opens it to the electronic water pump  120 B side at the same time. 
     As a result, the ITM  1  adjusts the engine coolant temperature according to the target coolant temperature in the Parallel Flow. Further, the SSV  400  flows the coolant flowing out from the turbocharger  900 - 3 , which is in the exhaust flow state, to the engine  110  side to maintain the performance of the turbocharger  900 - 3  after the initial start, and supplies a minimum flow rate of coolant to the LT radiator  300 B and the intercooler  900 - 1  according to whether the electronic water pump  120 B operates. 
     In the STATE  5 , the valve opening of the ITM  1  partially opens the first distribution flow path  3 B- 2  and the second distribution flow path  3 B- 3  together with partially opening the radiator outlet flow path  3 B- 1  while closing the engine head coolant inlet  3 A- 1  and opening the engine block coolant inlet  3 A- 2 . Further, the valve opening of the SSV  400  is switched to the C mode, which opens the coolant branch flow path  107  to the mechanic water pump  120 A side. In this case, it performs the D mode, which partially opens it to the electronic water pump  120 B side at the same time, if necessary. 
     As a result, the ITM  1  reduces the engine coolant flow rate of the heater core  200  required for the cooling/heating control to a minimum flow rate while maintaining the engine coolant flow rates of the oil warmer  600  and the ATF warmer  700  at an appropriate amount in the Cross Flow, thereby maximally securing the cooling capability in the high load condition and the uphill condition. Further, the SSV  400  circulates it to the engine  110  side while maintaining the coolant supply to the turbocharger  900 - 3 , which is in the exhaust flow state, to maintain the performance of the turbocharger  900 - 3  after the initial start. If necessary, the SSV  400  forms the flow rate of the coolant flowing to the LT radiator  300 B and the intercooler  900 - 1  at a minimum amount according to whether the electronic water pump  120 B operates. 
     In the STATE  6 , the valve opening of the ITM  1  opens the radiator outlet flow path  3 B- 1 , the first distribution flow path  3 B- 2 , and the second distribution flow path  3 B- 3  while closing the engine head coolant inlet  3 A- 1  and opening the engine block coolant inlet  3 A- 2 . Further, the valve opening of the SSV  400  is switched to the C mode, which opens it to the mechanic water pump  120 A side. In this case, it performs the D mode, which partially opens it to the electronic water pump  120 B side at the same time, if necessary. 
     As a result, the ITM  1  performs a block temperature downward control with respect to the engine block in the Cross Flow. Further, the SSV  400  circulates it to the engine  110  side while maintaining the coolant supply to the turbocharger  900 - 3 , which is in the exhaust flow state, to maintain the performance of the turbocharger  900 - 3  after the initial start. If necessary, the SSV  400  forms the flow rate of the coolant flowing to the LT radiator  300 B and the intercooler  900 - 1  at a minimum amount according to whether the electronic water pump  120 B operates. 
     In the STATE  7 , the valve opening of the ITM  1  opens the first distribution flow path  3 B- 2  and closes the second distribution flow path  3 B- 3  together with closing the radiator outlet flow path  3 B- 1  while closing the engine head coolant inlet  3 A- 1  and opening the engine block coolant inlet  3 A- 2 . Further, the valve opening of the SSV  400  is switched to the C mode, which opens it to the mechanic water pump  120 A side. In this case, it performs the D mode, which partially opens it to the electronic water pump  120 B side at the same time, if necessary. 
     As a result, the ITM  1  flows the engine coolant only to the heater core  200  considering the low outside air temperature and the initial coolant temperature in the heating operating mode of the heater during the warm-up of the engine  110  in the Cross Flow, and reflects the rise in the temperature of the engine coolant to gradually flow the engine coolant to the oil warmer  600 , thereby maximally securing the heating capability. Further, the SSV  400  circulates it to the engine  110  side while maintaining the coolant supply to the turbocharger  900 - 3 , which is in the exhaust flow state, to maintain the performance of the turbocharger  900 - 3  after the initial start, and if necessary, forms the flow rate of the coolant flowing to the LT radiator  300 B and the intercooler  900 - 1  at a minimum amount according to whether the electronic water pump  120 B operates. 
     In the STATE  8 , the ITM closes the engine head coolant inlet  3 A- 1 , the first distribution flow path  3 B- 2 , and the second distribution flow path  3 B- 3  while it opens the engine block coolant inlet  3 A- 2  and the radiator outlet flow path  3 B- 1 . Further, the SSV  400  closes the coolant branch flow path  107  to the mechanic water pump  120 A side while it is switched to a B mode, which opens it to the electronic water pump  120 B side. 
     As a result, the ITM  1  opens the valve opening to the maximum cooling position according to the engine stop. The SSV  400  performs the valve opening to the electronic water pump side so that the coolant flows to the turbocharger during an operating time of the electronic water pump through the coolant branch flow path to receive the coolant even after the engine stop, thereby preventing turbo boiling, which may be caused by stopping the engine coolant supply. 
     As described above, the vehicle thermal management system  100  according to the present embodiment includes the plurality of coolant circulation/distribution systems  100 - 1 ,  100 - 2 ,  100 - 3 ,  100 - 4  forming the engine coolant flow, which circulates the engine  110  optionally via the mechanic/electronic water pumps  120 A,  120 B, the heater core  200 , the HT/LT radiators  300 A,  300 B, the EGR cooler  500 , the oil warmer  600 , the ATF warmer  700 , and the intercooler  900 - 1 , in association with the ITM  1  and the SSV  400 . Thereby, turbo boiling of the turbocharger  900 - 3  at the Ignition Key Off is prevented in association with the SSV and the Electric Water Pump (EWP) of the water-cooled intercooler while quickly implementing the warm-up of the engine and the engine oil/ATF oil by the four-port layout of the ITM  1  at the same time.