PATENT DOCUMENT

Publication Number: US-11207939-B2
Application Number: US-201716089641-A
Country: US
Kind Code: B2

Title: Vehicle thermal management system and heat exchangers

Abstract:
A vehicle thermal management system includes selective use of a liquid cooled gas cooler (LCGC) and conductive heat exchangers between heating, cooling, battery, and powertrain thermal management loops to increase temperature control and efficiency of the system.

Claims:
What is claimed is: 
     
       1. A method for thermal management of a battery module through use of a battery loop having a battery loop coolant flowing through the battery loop, a heating loop having a heating loop coolant flowing through the heating loop, a cooling loop having a cooling loop coolant flowing through the cooling loop, and a refrigerant loop having a refrigerant flowing through the refrigerant loop, the method comprising:
 measuring a temperature of the battery loop coolant; 
 increasing the temperature of the battery loop coolant flowing to the battery module by directing a flow of the battery loop coolant to one of a heating loop heat exchanger in thermal communication with the heating loop or a liquid cooled gas cooler (LCGC) in thermal communication with the refrigerant loop, wherein the battery loop coolant is not in fluid communication with the heating loop coolant; and 
 decreasing the temperature of the battery loop coolant flowing to the battery module by directing the flow of the battery loop coolant to one of a cooling loop heat exchanger in thermal communication with the cooling loop or a chiller in thermal communication with the refrigerant loop, 
 wherein the battery loop coolant is not in fluid communication with the cooling loop coolant, 
 wherein the step of increasing the temperature of the battery loop coolant with the LCGC includes indirectly transferring heat from the refrigerant to the battery loop coolant by the heating loop coolant, and 
 wherein the step of decreasing the temperature of the battery loop coolant with the chiller includes indirectly transferring heat from the battery loop coolant to the refrigerant by the cooling loop coolant. 
 
     
     
       2. The method of  claim 1 , further comprising:
 maintaining the temperature of the battery loop coolant flowing to the battery module by directing the flow of the battery loop coolant to bypass the one of the heating loop heat exchanger or the LCGC and to bypass the one of the cooling loop heat exchanger or the chiller; 
 comparing the measured battery coolant loop temperature to a predetermined battery coolant temperature target value; and 
 determining whether an increase in, a decrease in, or maintaining the temperature of the battery loop coolant is needed based on the battery coolant temperature target value, 
 wherein one of the steps of increasing the temperature of the battery loop coolant, decreasing the temperature of the battery loop coolant, or maintaining the temperature of the battery loop coolant is performed according to the step of determining whether the increase in, the decrease in, or the maintaining of the temperature of the battery loop coolant is needed. 
 
     
     
       3. The method of  claim 2 , wherein:
 the step of increasing the temperature of the battery loop coolant comprises simultaneously directing a portion of the flow of the battery loop coolant to the one of the heating loop heat exchanger or the LCGC before the battery module and directing another portion of the flow of the battery loop coolant to the battery module without being directed to the one of the heating loop heat exchanger or the LCGC, and 
 the step of decreasing the temperature of the battery loop coolant comprises simultaneously directing a portion of the flow of the battery loop coolant to the one of the cooling loop heat exchanger or the chiller before the battery module and directing another portion of the flow of the battery loop coolant to the battery module without being directed to the one of the cooling loop heat exchanger or the chiller. 
 
     
     
       4. The method of  claim 1 , wherein a thermal management system includes the battery loop, the refrigerant loop, the LCGC, and the chiller, and the refrigerant flows through the LCGC and through the chiller. 
     
     
       5. The method of  claim 4 , wherein the step of increasing the temperature of the battery loop coolant is performed by directing the flow of the battery loop coolant to the LCGC, and the step of decreasing the temperature of the battery loop coolant is performed by directing the flow of the battery loop coolant to the chiller. 
     
     
       6. The method of  claim 5 , wherein the heating loop coolant flows through the LCGC, and the cooling loop coolant flows through the chiller; and
 wherein the method further comprises increasing a temperature of the heating loop coolant with the LCGC and decreasing a temperature of the cooling loop coolant with the chiller. 
 
     
     
       7. The method of  claim 6 , wherein the step of increasing the temperature of the battery loop coolant and the step of increasing the temperature of the heating loop coolant are performed simultaneously by the LCGC, and the step of decreasing the temperature of the battery loop coolant and the step of decreasing the temperature of the cooling loop coolant are performed simultaneously by the chiller. 
     
     
       8. The method of  claim 7 , wherein the step of increasing the temperature of the battery loop coolant and the step of increasing the temperature of the heating loop coolant includes transferring heat from the refrigerant to the battery loop coolant and to the heating loop coolant by the LCGC, and the step of decreasing the temperature of the battery loop coolant and the step of decreasing the temperature of the cooling loop coolant includes transferring heat from the battery loop coolant and from the cooling loop coolant to the refrigerant by the chiller. 
     
     
       9. A thermal management system, comprising:
 a refrigerant loop having a refrigerant flowing therethrough, a liquid cooled gas cooler (LCGC), and a chiller, the LCGC and the chiller being in fluid communication by the refrigerant; 
 a heating loop having a heating loop heat exchanger and a heating loop coolant flowing therethrough, the heating loop being in fluid communication with the LCGC by the heating loop coolant; 
 a cooling loop having a cooling loop heat exchanger and a cooling loop coolant flowing therethrough, the cooling loop being in fluid communication with the chiller by the cooling loop coolant; 
 a battery loop having a battery loop valve, a battery module, and a battery loop coolant flowing therethrough, the battery loop valve configured to direct the battery loop coolant to:
 (a) one of the LCGC or the heating loop heat exchanger that is in fluid communication with the heating loop by the heating loop coolant, the one of the LCGC or the heating loop heat exchanger configured to increase a temperature of the battery loop coolant upstream of the battery module; and 
 (b) one of the chiller or the cooling loop heat exchanger that is in fluid communication with the cooling loop by the cooling loop coolant, the one of the chiller or the cooling loop heat exchanger configured to decrease the temperature of the battery loop coolant upstream of the battery module, 
 
 wherein the heating loop coolant, the cooling loop coolant, and the battery loop coolant are not in fluid communication, and 
 wherein the increase or decrease in temperature of the battery loop coolant is based on indirect heat transfer from the refrigerant to the battery loop coolant by the heating loop coolant or from the battery loop coolant to the refrigerant by the cooling loop coolant, respectively. 
 
     
     
       10. The thermal management system of  claim 9 , wherein:
 the refrigerant loop further comprises a compressor, an accumulator having an internal heat exchanger, an expansion valve, and a sensor in fluid communication with the LCGC and the chiller by the refrigerant, 
 the refrigerant loop is self-contained, closed loop, and pre-pressurized with the refrigerant prior to installation into the thermal management system, and 
 the refrigerant loop further comprises a refrigerant radiator in fluid communication with the LCGC and the chiller by the refrigerant. 
 
     
     
       11. The thermal management system of  claim 9 , wherein the heating loop further comprises a heating loop valve, a heater core, and a heating loop radiator in fluid communication by the heating loop coolant; and
 wherein the heater core is downstream of the heating loop valve, the heating loop radiator is downstream of the heating loop valve, and the heating loop valve includes flow positions for selectively directing the heating loop coolant at an elevated temperature from the LCGC to the heater core to provide heated air to a passenger cabin or to the heating loop radiator to decrease the temperature of the heating loop coolant. 
 
     
     
       12. The thermal management system of  claim 11 , wherein:
 the heating loop further comprises a heater in thermal communication with the heating loop coolant to increase the temperature of the heating loop coolant upstream of the heater core and independently of the LCGC, 
 the battery loop is in fluid communication with the LCGC by the battery loop coolant, and 
 the battery loop is in fluid communication with the heating loop heat exchanger by the battery loop coolant to provide heat from the heating loop coolant to the battery loop coolant. 
 
     
     
       13. The thermal management system of  claim 9 , wherein:
 the cooling loop further comprises a cooling core in fluid communication with the one of the chiller or the cooling loop heat exchanger by the cooling loop coolant to provide cooled air to a passenger cabin, 
 the battery loop is in fluid communication with the chiller by the battery loop coolant, and 
 the battery loop is in fluid communication with the cooling loop heat exchanger by the battery loop coolant to provide heat from the battery loop coolant to the cooling loop coolant. 
 
     
     
       14. The thermal management system of  claim 9 , further comprising a powertrain loop having a powertrain loop coolant and a powertrain heat exchanger, the powertrain heat exchanger being in fluid communication with a wheel drive motor by the powertrain loop coolant and in fluid communication with the cooling loop by the cooling loop coolant to decrease a temperature of the powertrain loop coolant to the wheel drive motor. 
     
     
       15. The thermal management system of  claim 14 , wherein the powertrain loop further comprises a powertrain loop valve and a powertrain radiator, the powertrain loop valve having flow configurations for directing the powertrain loop coolant to the cooling loop heat exchanger or the powertrain radiator to decrease the temperature of the powertrain loop coolant. 
     
     
       16. The thermal management system of  claim 15 , wherein the powertrain loop valve comprises five alternative powertrain loop coolant flow configurations comprising:
 a cooling loop heat exchanger flow configuration in which the powertrain loop coolant flows from the powertrain loop valve to the cooling loop heat exchanger; 
 a radiator flow configuration in which the powertrain loop coolant flow from the powertrain loop valve to the powertrain radiator; 
 a bypass conduit flow configuration in which the powertrain loop coolant flows from the powertrain loop valve to the wheel drive motor without flowing to the cooling loop heat exchanger and without flowing to the powertrain radiator; 
 a cooling loop heat exchanger and bypass blend configuration in which a portion of the powertrain loop coolant flows from the powertrain loop valve to the cooling loop heat exchanger and another portion of the powertrain loop coolant flows from the powertrain loop valve to the wheel drive motor without flowing to the cooling loop heat exchanger and without flowing to the powertrain radiator; and 
 a radiator and bypass blend configuration in which a portion of the powertrain loop coolant flows from the powertrain loop valve to the powertrain radiator and another portion of the powertrain loop coolant flows from the powertrain loop valve to the wheel drive motor without flowing to cooling loop heat exchanger and without flowing to the powertrain radiator. 
 
     
     
       17. A thermal management system, comprising:
 a battery loop having a battery loop coolant flowing therethrough; 
 a heating loop having a heating loop coolant flowing through a heating loop heat exchanger that is configured to supply heat to the battery loop coolant; 
 a cooling loop having a cooling loop coolant flowing through a cooling loop heat exchanger that is configured to absorb heat from the battery loop coolant; 
 a refrigerant loop having a refrigerant flowing therethrough; 
 a liquid cooled gas cooler (LCGC) that is in thermal communication with the refrigerant loop and is configured to supply heat to the battery loop coolant without contact between the heating loop coolant and the battery loop coolant; and 
 a chiller that is in thermal communication with the refrigerant loop and is configured to absorb heat from the battery loop coolant without contact between the cooling loop coolant and the battery loop coolant. 
 
     
     
       18. The thermal management system of  claim 17 , wherein the heating loop further comprises a heating loop valve, a heater core, and a heating loop radiator in fluid communication by the heating loop coolant; and
 wherein the heater core is downstream of the heating loop valve, the heating loop radiator is downstream of the heating loop valve, and the heating loop valve includes flow positions configured to selectively direct the heating loop coolant from the LCGC to the heater core to provide heated air to a passenger cabin or to the heating loop radiator to decrease the temperature of the heating loop coolant. 
 
     
     
       19. The thermal management system of  claim 17 , wherein the refrigerant loop further comprises a compressor, an accumulator having an internal heat exchanger, an expansion valve, and a sensor in fluid communication with the LCGC and the chiller by the refrigerant, wherein the refrigerant loop is self-contained, closed loop, and pre-pressurized with the refrigerant prior to installation into the thermal management system, and wherein the refrigerant loop further comprises a refrigerant radiator in fluid communication with the LCGC and the chiller by the refrigerant.

Description:
CROSS-REFERENCE TO RELATED APPLICATION(S) 
     This application claims priority to and the benefit U.S. Provisional Application No. 62/382,794 (filed Sep. 2, 2016) and U.S. Provisional Application No. 62/533,949 (filed Jul. 18, 2017), the entire disclosures of which are incorporated by reference herein. 
    
    
     TECHNICAL FIELD 
     This application generally relates to thermal management of vehicle systems and heat exchangers. 
     BACKGROUND 
     Battery-powered electric or hybrid vehicles have become an increasingly popular choice by consumers for their fuel efficiency and low impact on the environment. With limits in technology on battery performance and consumer demand for maximum range between vehicle charging, there is an increased need for more efficient power management systems, particularly in the area of vehicle thermal management. The heating and cooling of vehicle operation systems has a significant impact on vehicle efficiency and performance. The heating, cooling and conditioning of the passenger cabin environment is important to passenger comfort and vehicle enjoyment. 
     Traditional electric and hybrid vehicles employed independent heating and cooling systems using dedicated heating and cooling devices to support the specific vehicle system. For example, if the vehicle battery system required heating at start up in cold temperatures, but cooling during extended operation for optimum battery efficiency, traditional vehicle battery systems employed dedicated heating and cooling devices to support the battery system. These independent systems and dedicated components for each thermal management subsystem consume more power, are less efficient, and add complexity, packaging space, weight, and overall cost to the vehicle. 
     SUMMARY 
     One aspect of the disclosure is a vehicle thermal management system. The thermal management system includes a refrigerant subsystem or loop, a heating loop, a cooling loop, a battery loop, and a powertrain loop. In one aspect, each of the heating, cooling, battery, and powertrain loops includes a heat exchanger in communication with another of the subsystem loops to provide selective heating or cooling between the communicating loops. In another aspect, only the cooling loop and powertrain loop share a common, dedicated heat exchanger to assist in cooling the powertrain loop coolant. 
     In another aspect of the disclosure, a modular, self-contained thermal management refrigerant subsystem or loop is disclosed. The modular refrigerant subsystem can be assembled, pre-charged, pre-tested, and delivered as a unit to a vehicle assembly plant or system integrator for efficient hook-up to other vehicle subsystems. In one example, the refrigerant subsystem uses R744 refrigerant. 
     In another aspect of the disclosure, a thermal management heating subsystem or loop using a liquid cooled gas cooler (LCGC) is disclosed. The LCGC draws heat from the refrigerant subsystem to supplement heat energy in the heating subsystem. In one example, a 3-port valve can be used to selectively add heat to the heating loop coolant for use in heating a passenger cabin or to expel excess heat from the refrigerant system via a low temperature radiator based on a flow position of the 3-port valve. In another aspect, the 3-port valve can blend or direct a flow of the heating loop coolant to both heat the passenger cabin and expel heat to the low temperature radiator to further control temperature in the heating and refrigerant loops. In another example, the LCGC can be the sole source of heat energy provided to the heating loop. 
     In another aspect of the disclosure, a thermal management battery subsystem or loop is disclosed. In one aspect, the battery loop selectively uses a heat exchanger in communication with the heating loop and a heat exchanger in thermal communication with a cooling loop to selectively provide heat to, or remove heat from, the battery loop coolant as needed for efficient battery module operation. In another aspect, the battery loop selectively adds heat directly from the LCGC, selectively removes heat directly by a chiller without the need for additional heat exchangers between the battery loop and the heating and cooling loops. In one example, a 4-port valve can be used to selectively provide heat, remove heat, bypass additional heating or cooling, or provide a blend of bypass with heat addition or removal based on a flow position of the 4-port valve to increase the level of temperature control of the battery loop and the battery module. 
     In another aspect of the disclosure, a thermal management powertrain subsystem or loop is disclosed. The powertrain loop uses a heat exchanger in thermal communication with the cooling loop for efficient cooling of the powertrain subsystem. In one example, a 4-port valve can be employed to selectively use one of two cooling devices in thermal communication with the powertrain loop, provide a bypass to one or both cooling devices, or provide a blend of one of the cooling devices and the bypass based on a flow position of the 4-port valve to increase the level of temperature control of the powertrain loop and powertrain drive components. In another aspect of the disclosure, excess cooling capacity of the refrigeration system is transferred to the powertrain subsystem in order to increase the LCGC heat generation for heating loop heating, even when the powertrain loop does not require additional cooling. 
     In another aspect of the disclosure, a process for thermal management of the battery loop is disclosed. The process selectively provides heat or removes heat from the battery loop through selected use of two heat exchangers in respective thermal communication with the heating loop and the cooling loop. In another aspect, the addition or removal of heat is respectively provided directly by the LCGC or the chiller rather than separate heat exchangers. In another aspect, a bypass can be used to maintain a measured temperature of the battery loop coolant. 
     In another aspect, a process for increasing the temperature of a heating loop coolant is disclosed. The process selectively provides heat to the heating loop through use of the LCGC which transfers heat expelled from the refrigerant loop. 
     In another aspect, a method is provided for thermal management of a battery module through use of a battery loop having a battery loop coolant flowing through the battery loop. The method includes measuring a temperature of the battery loop coolant, increasing the temperature of the battery loop coolant, and decreasing the temperature of the battery loop coolant. The step of increasing the temperature of the battery loop coolant flowing to the battery module includes directing a flow of the battery loop coolant to one of a heating loop heat exchanger in thermal communication with a heating loop or a liquid cooled gas cooler (LCGC) in thermal communication with a refrigerant loop. The step of decreasing the temperature of the battery loop coolant flowing to the battery module includes directing the flow of the battery loop coolant to one of a cooling loop heat exchanger in thermal communication with a cooling loop or a chiller in thermal communication with the refrigerant loop. 
     In another aspect, a thermal management system includes a refrigerant loop, a heating loop, a cooling loop, and a battery loop. The refrigerant loop includes a refrigerant flowing therethrough, a liquid cooled gas cooler (LCGC), and a chiller, the LCGC and the chiller being in fluid communication by the refrigerant. The heating loop includes a heating loop coolant flowing therethrough, the heating loop being in fluid communication with the LCGC by the heating loop coolant. The cooling loop includes a cooling loop coolant flowing therethrough, the cooling loop being in fluid communication with the chiller by the cooling loop coolant. The battery loop includes a battery loop coolant flowing therethrough, a battery loop valve, and a battery module, the battery loop valve and the battery module being in fluid communication by the battery loop coolant. The battery loop valve includes flow configurations for directing the battery loop coolant to (a) one of the LCGC, or a heating loop heat exchanger that is in fluid communication with the heating loop by the heating loop coolant, to increase a temperature of the battery loop coolant upstream of the battery module, and (b) one of the chiller, or a cooling loop heat exchanger that is in fluid communication with the cooling loop by the cooling loop coolant, to decrease the temperature of the battery loop coolant upstream of the battery module. 
     In another aspect, a heat exchanger is provided for exchanging heat between at least three fluids that are fluidically separated. The heat exchanger includes refrigerant passes, primary coolant passes, and a secondary coolant pass. The refrigerant passes are configured for a refrigerant to flow serially therethrough. The primary coolant passes are configured for a first coolant to flow serially therethrough. The secondary coolant pass is configured for a second coolant to flow therethrough. The refrigerant passes are configured to exchange heat directly with the primary coolant passes, the primary coolant passes are configured to exchange heat directly with the secondary coolant pass, and the refrigerant passes do not exchange heat directly with the secondary coolant pass. 
     In another aspect, a heat exchanger includes a refrigerant passage, a primary coolant passage, and a secondary coolant passage. The refrigerant passage is for connecting to a refrigerant loop of a thermal management system for receiving from and transferring thereto a refrigerant. The refrigerant passage is cooperatively defined by refrigerant tubes. The primary coolant passage is for connecting to a primary coolant loop of the thermal management system for receiving from and transferring thereto a primary coolant. The primary the primary coolant passage is cooperatively defined by at least two primary coolant cavities of a core structure of the heat exchanger. The secondary coolant passage is for connecting to a secondary coolant loop of the thermal management system for receiving from and transferring thereto a secondary coolant. The secondary coolant passage is formed by a secondary coolant cavity of the core structure. The refrigerant tubes extend in a serpentine manner through the two primary coolant cavities to exchange heat directly between the refrigerant and the primary coolant and do not extend through the secondary coolant cavity. 
     A thermal management system includes a refrigerant loop, a first primary coolant loop, a second primary coolant loop, a secondary coolant loop, a first heat exchanger, and a second heat exchanger. The refrigerant loop carries a refrigerant therethrough. The first primary coolant loop carries a first primary coolant therethrough. The second primary coolant loop carries a second primary coolant therethrough. The secondary coolant loop carries a secondary coolant therethrough. 
     The first heat exchanger is connected to the refrigerant loop, the first primary coolant loop, and the secondary coolant loop for the refrigerant, the first primary coolant, and the secondary coolant, respectively, to flow through the heat exchanger. The first heat exchanger includes a primary coolant passage, a secondary coolant passage, and a refrigerant passage. The first primary coolant flows serially in a first primary coolant pass and a second primary coolant pass of the primary coolant passage. The secondary coolant flows in a secondary coolant pass of the secondary coolant passage. The refrigerant flows serially in at least four refrigerant passes of the refrigerant passage. Heat is exchanged directly between the refrigerant in a first two of the refrigerant passes and the first primary coolant in the first primary coolant pass and directly between the refrigerant in a second two of the refrigerant passes and the first primary coolant in the second primary coolant pass. The second heat exchanger is connected to the refrigerant loop, the second primary coolant loop, and the secondary coolant loop for the refrigerant, the second primary coolant, and the secondary coolant, respectively, to flow through the second heat exchanger. The second heat exchanger includes another primary coolant passage, another secondary coolant passage, and a refrigerant passage. The second primary coolant flows serially in another first primary coolant pass, another a second primary coolant pass, and a third primary coolant pass of the other primary coolant passage. The secondary coolant flows in another secondary coolant pass of the other secondary coolant passage. The refrigerant flows serially in at least another six refrigerant passes of the other refrigerant passage. Heat is exchanged directly between the refrigerant in another first two of the other six refrigerant passes and the second primary coolant in the other first primary coolant pass, directly between the refrigerant in another second two of the six refrigerant passes and the second primary coolant in the other second primary coolant pass, and directly between the refrigerant in a third two of the six refrigerant passes and the second primary coolant in the third primary coolant pass. 
     For example, in the first heat exchanger, heat may be transferred directly from the secondary coolant to the first primary coolant, and directly from the first primary coolant to the refrigerant. In the second heat exchanger, heat may be transferred directly from the refrigerant to the second primary coolant, and directly from the second primary coolant to the secondary coolant. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a schematic of one example of a thermal management system. 
         FIG. 2  is a schematic of an alternate example of a thermal management system similar to the thermal management system of  FIG. 1 . 
         FIG. 3  is a block diagram of an electronic control system. 
         FIG. 4  is a flow chart of one example of a method of thermal management of a vehicle battery module. 
         FIG. 5  is a schematic flow chart of one example of a method of increasing the temperature of a heating loop coolant. 
         FIG. 6A  is a top schematic view of a first embodiment of a heat exchanger. 
         FIG. 6B  is a front schematic view of the heat exchanger of  FIG. 6A . 
         FIG. 6C  is a side schematic view of the heat exchanger of  FIG. 6A . 
         FIG. 6D  is a partial cross-sectional view of the heat exchanger taken along line  6 D- 6 D in  FIG. 6A  and of which a refrigerant passage is omitted for clarity. 
         FIG. 6E  is a cross-sectional view of the heat exchanger taken along line  6 E- 6 E in  FIG. 6A  and of which the refrigerant passage is shown. 
         FIG. 6F  is a cross-sectional view of the heat exchanger taken along line  6 F- 6 F in  FIG. 6A . 
         FIG. 6G  is a cross-sectional view of the heat exchanger taken along line  6 G- 6 G in  FIG. 6A . 
         FIG. 6H  is a cross-sectional view of a refrigerant tube of the refrigerant passage of the heat exchanger of  6 A. 
         FIG. 7  is a cross-sectional view of another embodiment of a heat exchanger, which is taken similar to the cross-sectional view of  FIG. 6F . 
         FIG. 8  is a cross-sectional view of another embodiment of a heat exchanger, which is taken similar to the cross-sectional view of  FIG. 6F . 
         FIG. 9  is a cross-sectional view of another embodiment of a heat exchanger, which is taken similar to the cross-sectional view of  FIG. 6F . 
         FIG. 10  is a cross-sectional view of another embodiment of a heat exchanger, which is taken similar to the cross-sectional view of  FIG. 6F . 
         FIG. 11  is a cross-sectional view of another embodiment of a heat exchanger, which is taken similar to the cross-sectional view of  FIG. 6E . 
     
    
    
     DETAILED DESCRIPTION 
     Thermal management systems are described in the context of use with passenger vehicles. Heat exchange interfaces between individual subsystems or loops can be leveraged to decrease power consumption and increase efficiency of the individual loops and the overall thermal management system. Thermal communication between the respective loops can be conducted without direct communication or mixing of refrigerant or coolant between the respective loops, allowing for closed loop subsystems. Although described in reference to passenger vehicles, these thermal management systems can also be used in other applications. 
     Referring to the example in  FIG. 1 , a thermal management system  100  is schematically shown for use in a passenger vehicle having a front end  104 , commonly referred to as an engine compartment, a passenger compartment or cabin  108 , and a rear end  120  typically housing the drivetrain components to power wheels for motion. 
     In the example shown in  FIG. 1 , the system  100  includes a refrigerant subsystem or loop  124 , a heating subsystem or loop  128 , a cooling subsystem or loop  130 , a battery subsystem or loop  134 , and a powertrain subsystem or loop  140  as generally shown. It is understood that additional components, connecting conduit lines, alternative conduit routing schemes, and additional or alternative system loads can be included (not shown).  FIG. 1  also illustrates a heating, ventilation, and air conditioning (HVAC) unit  146  which provides heating, cooling, and conditioning of air for the passenger cabin  108  as described further below. 
     The refrigerant loop  124  includes an accumulator  150  (e.g., with an internal heat exchanger unit), a compressor  152 , a refrigerant line or conduit  154 , a first pressure and temperature sensor  158 , a liquid cooled gas cooler (LCGC)  160 , an expansion valve  162 , a chiller  166 , and a second temperature and pressure sensor  170  all in fluid communication along the conduit  154  as generally shown. In one example, the refrigerant loop  124  uses R744 refrigerant. Other types of refrigerant, for example R-134a, can also be used. Generally speaking, the term “fluid communication” is used to refer to various components to and/or through which a common fluid flows. For example, the LCGC  160  and the chiller  166  are in fluid communication by the refrigerant, which flows therethrough. 
     In the  FIG. 1  example, the compressor  152  compresses the vapor phase refrigerant to high pressure and temperature and forces the refrigerant toward the LCGC  160 . The LCGC  160  is a high-pressure refrigerant to coolant heat exchanger. As shown in  FIG. 1 , the LCGC  160  is in thermal communication with the heating loop  128 , thereby providing a source of heat/thermal energy to the heating loop  128  from heat expelled from the refrigerant loop  124 . The transfer of expelled heat from the refrigerant loop  124  to the heating loop  128  can be made without direct communication or contact between the refrigerant and the heating loop coolant as discussed further below. Through use of R744 refrigerant, the system  100  can operate as a heat generator in temperatures down to −30° Celsius. In this manner, the refrigerant loop  124  operates as a heat pump to generate heat from a refrigerant cycle. Generally speaking, the term “thermal communication” refers to loops and fluids and/or components thereof that transfer heat to other loops and fluids and/or components thereof. For example, each of the refrigerant loop  124 , the refrigerant, and/or the LCGC  160  may be considered in thermal communication with the heating loop  128  and the heating loop coolant. Thermal communication may include direct heat transfer. 
     On exiting the LCGC  160 , the cooled refrigerant flows through a refrigerant to refrigerant heat exchanger internal to the accumulator  150  to lower the refrigerant temperature further. The high pressure, low temperature vapor phase refrigerant then flows through an expansion valve  162  that reduces the pressure of the refrigerant, causing it to condense into a liquid phase refrigerant. The refrigerant can be forced into the chiller  166  as generally shown. In the  FIG. 1  example, the liquid phase refrigerant absorbs heat from the coolant loop coolant in the chiller  166  as it evaporates back to a vapor phase refrigerant. The refrigerant then flows through the accumulator  150  where any residual liquid refrigerant can be stored and only vapor phase refrigerant can be selectively moved to the compressor  152  to start the cycle again. The remaining liquid phase refrigerant in the accumulator  150  absorbs heat from the refrigerant to refrigerant heat exchanger internal to the accumulator  150 . 
     The refrigerant loop  124  in the  FIG. 1  example can be an independent, closed-loop system which cools or draws heat away from the refrigerant through use of the LCGC  160  instead of using a forced air to refrigerant condenser/gas cooler present in conventional refrigeration systems. The LCGC  160  transfers the heat from the refrigerant, thereby cooling the refrigerant and transferring that heat into the heating loop coolant as further discussed below. Through use of a self-contained refrigerant loop  124  which does not require a traditional air to refrigerant condenser/gas cooler for removing heat, the refrigerant loop  124  can be preassembled, filled with refrigerant, tested, packaged, and shipped directly to the final assembly facility or a systems integrator for rapid installation in the partially assembled vehicle. 
     Still referring to  FIG. 1 , an example of the heating loop  128  is shown. In the example, the heating loop  128  includes a reservoir  180  for the storage of heating loop coolant, a pump  181  to force the heating loop coolant through a line or conduit  182  in a closed loop, an electric heater  184 , and a temperature sensor  186  to monitor the temperature of the heating loop coolant as generally shown. 
     As discussed above for  FIG. 1 , the LCGC  160  can be positioned to be in thermal communication, but not direct refrigerant fluid to coolant fluid communication, with both the heating loop  128  and the refrigerant loop  124 . The LCGC  160  can transfer heat expelled from the refrigerant to the heating loop coolant for use by other vehicle systems requiring heated fluid, for example, a heater core  188  that is part of the HVAC unit  146 , and can be used to selectively heat the passenger cabin  108 . An advantage of the heating loop  128  and use of the LCGC  160  is that the system  100  can operate at a Coefficient of Performance (COP) greater than 1. The COP is the ratio of thermal power to electrical power. 
     In the  FIG. 1  example, the electric heater  184  can be included to selectively supply additional heat or thermal energy to warm the flow of heating loop coolant flowing through the electric heater  184  toward the heater core  188 . The heating loop  128  can also include a heating loop heat exchanger  190  in thermal conductive communication with the battery loop  134  as generally shown. The heat exchanger  190  selectively provides heat energy from the heating loop coolant to the battery loop  134  as further discussed below. 
     In the example of  FIG. 1 , the heating loop  128  includes a valve  194  in alternative fluid communication with a heating conduit  196  and an exhaust conduit  200 , both positioned downstream of the valve  194  as generally shown. The heating conduit  196  provides a path for the heating loop coolant to flow through heater core  188  and heat exchanger  190 . The exhaust conduit  200  provides a path for the heating loop coolant to flow through a low temperature radiator  204  (e.g., a heating loop radiator) to expel or dump heat to the atmosphere as generally shown. The low temperature radiator  204  cools the heating loop coolant through convection or forced air as further described below. Both the heating conduit  196  and the exhaust conduit  200  return the heating loop coolant to the LCGC  160  in a closed loop as described above. 
     In the  FIG. 1  example, the valve  194  can be a 3-port valve which selectively directs the flow of the heating loop coolant through the heating conduit  196  to the heater core  188  and the heat exchanger  190  or through the exhaust conduit  200  to the low temperature radiator  204  to exhaust heat from the heating loop coolant to the atmosphere. In one aspect, the valve  194  includes flow positions allowing it to mix or blend the flow of heating loop coolant to both the heating conduit  196  and the exhaust conduit  200 . For example, the valve  194  can simultaneously direct a portion of the heating loop coolant to flow to the heating conduit  196  and a portion of the heating loop coolant to flow to the exhaust conduit  200  to further control the temperature of the heating loop coolant as well as the refrigerant loop  124 . 
     In the examples discussed herein, the term “coolant” is used to include an automotive grade mixture of about equal parts of ethylene glycol and water. It is understood that different fluids and/or different mixtures of ethylene glycol and water can be used. 
     Still referring to  FIG. 1 , an example of the cooling subsystem or loop  130  is illustrated. In the example, the cooling loop  130  includes a reservoir  210  for the storage of cooling loop coolant and a pump  214  to selectively force the flow of cooling loop coolant through a closed-loop cooling line or conduit  216  as generally shown. 
     In the  FIG. 1  example, the cooling loop conduit  216  is in thermal communication with the refrigerant loop  124  through the chiller  166 . As described above, as the refrigerant of the refrigerant loop  124  flows through the chiller  166 , the refrigerant draws or absorbs heat as it evaporates inside the chiller  166  which in turn removes heat from the cooling loop conduit  216 . In this example, the cooling loop  130  includes a powertrain heat exchanger  220  in thermal communication with the powertrain loop  140  and a battery heat exchanger  226  in thermal communication with the battery loop  134  as generally shown. A temperature sensor  228  in communication (e.g., thermal and/or fluid communication) with cooling loop coolant can also be used to measure and monitor the temperature and other conditions of the cooling loop coolant. The cooling loop  130  can also extend through a cooling core  230  described further below in reference to the HVAC unit  146 . 
     Additional operational and control components  232 , for example, computing and power distribution components, can also be placed in fluid communication with the cooling loop  130 . The  FIG. 1  powertrain heat exchanger  220  and the battery heat exchanger  226  independently operate to respectively and selectively transfer heat from the powertrain loop coolant and the battery loop coolant, for example, through conduction with the cooling loop coolant, to reduce the temperature of the battery loop coolant and the powertrain loop coolant as further described below. 
     Still referring to  FIG. 1 , the HVAC unit  146  can be used to filter air, cool and de-humidify air, and heat air to ventilate and condition the passenger cabin  108 . In the example shown, the HVAC unit  146  includes an air filter  236 , at least one cabin blower  238 , a recirculation air filter  240 , and a distribution manifold  242  for selective distribution of air to and from the passenger cabin  108 . The heating loop  128  and the cooling loop  130  are in fluid communication with the heater core  188  and the cooling core  230  of the HVAC unit  146  respectively. One or more of the cabin blowers  238  can be used to force air over the respective cores  188 ,  230  to selectively heat or cool the passenger cabin  108 . The air filter  236  can be positioned upstream of the cabin blower  238  in communication with environmental air. The recirculation air filter  240  can also be used to filter both environmental air and recirculated cabin air entering the HVAC unit  146 . The heating and cooling controls (not shown) for the passenger cabin  108  can be in electronic communication with the cabin blowers  238  through control units (not shown). 
     An advantage of the system  100  and use of the cooling loop  130  is the elimination of a dedicated air-to-refrigerant evaporator core and refrigerant conduit connections inside the passenger cabin  108  required by prior designs that have the potential to leak refrigerant into the cabin air. Use of the chiller  166  to remove heat from the cooling loop coolant cools the cooling loop coolant without the need for a separate, dedicated cooling/evaporator core along the cooling loop  130 . 
       FIG. 1  further illustrates the battery loop  134 . In the example, the battery loop  134  includes a reservoir  250  for the storage of liquid battery loop coolant and a battery loop pump  252  to selectively force the flow of battery loop coolant through a closed-loop cooling line or conduit  254  in fluid communication with a battery module  260 . The battery module  260  provides the principal or supplemental power to drive motors which power the drive wheels of the vehicle. 
     In the  FIG. 1  example, a 4-port valve  266  can be positioned in fluid communication with a heating conduit  270 , a cooling conduit  274 , and a bypass conduit  280  as generally shown. The valve  266  is operable to selectively direct a flow of battery loop coolant to the heating conduit  270  and through the heat exchanger  190  which will add heat to the battery loop coolant from the heating loop  128 . It can be desirable to temporarily heat the battery module  260 , for example, during start up and early operation in cold environmental temperatures. 
     The valve  266  is also operable to selectively direct the flow of battery loop coolant to the cooling conduit  274  and through the battery heat exchanger  226  in thermal communication with the cooling loop  130  to remove heat from the battery loop coolant to reduce or maintain the temperature of the battery module  260 . Alternatively, the valve  266  is further operable to selectively direct the flow of battery loop coolant to the bypass conduit  280  to avoid additional heating or cooling of the battery loop coolant by the respective heat exchangers  190 ,  226 . In one example, the valve  266  includes additional flow positions in which a portion of the battery loop coolant is directed to blend flow to both the heating conduit  270  and the bypass conduit  280  or blend flow to both the cooling conduit  274  and the bypass conduit  280  for increased control of the temperature of the battery loop coolant and of the battery module  260 . 
     An advantage of the  FIG. 1  system  100  and use of the battery loop  134  is that a dedicated heater and a dedicated chiller/cooling device is not needed along the battery loop  134  due to use of the respective heat exchangers  190 ,  226 . 
       FIG. 1  further shows an example of the powertrain loop  140 . The powertrain loop  140  includes a reservoir  290  for storage of powertrain loop coolant, a pump  292  to selectively force flow of the powertrain loop coolant through a line or conduit  294 , a temperature sensor  296  to measure and monitor the temperature of the powertrain loop coolant, a battery charger  300 , a control circuit and power electronics module  304 , a traction motor  310 , and a traction motor invertor  314  for the vehicle rear wheels as generally shown. 
     In the  FIG. 1  example, a 4-port valve  320  can be in fluid communication with the powertrain loop conduit  294  and a cooling conduit  324  in communication with the heat exchanger  220  on the cooling loop  130  as previously described. Alternatively, the valve  320  can direct the flow of powertrain loop coolant to an exhaust conduit  330  in communication with a high temperature radiator  334  (e.g., a powertrain radiator) positioned at the front end  104  of the vehicle as generally shown. The high temperature radiator  334  can be operable to exhaust heat or remove heat from the powertrain loop coolant to the atmosphere through forced air induced by a fan  336  or by movement of the vehicle. 
     The valve  320  can also be in communication with a bypass conduit  338  which selectively keeps powertrain loop coolant from being directed to the cooling conduit  324 , the exhaust conduit  330 , and thus, the heat exchanger  220  or the high temperature radiator  334 . In the  FIG. 1  example, the valve  320  further includes a flow position in which a portion of the powertrain loop coolant is directed to blend flow to both the cooling conduit  324  and the bypass conduit  338  or to blend flow to both the exhaust conduit  330  and the bypass conduit  338  for increased control of the temperature of the powertrain loop coolant and components in fluid communication with the powertrain loop  140 . Although the traction motor  310  and associated components are shown for the rear wheels of the vehicle, it is understood that the powertrain loop  140  is equally applicable to the front wheels of a vehicle or both the front and rear wheels, for example, in a four-wheel drive vehicle. 
     In one aspect of the powertrain loop  140 , excess cooling capacity of the refrigerant loop  124  is transferred to the powertrain loop  140  in order to increase heat generation or output by the LCGC  160  for heating the heating loop  128 , even when the powertrain loop  140  does not require additional heating. In other words, the powertrain loop  140  and the valve  320  may be used to continuously warm or transfer heat to the cooling loop  130  thereby raising the temperature of the cooling loop coolant. This heat in the cooling loop coolant is then transferred to the chiller  166  to warm the refrigerant in the refrigerant loop  124  as described above. This in turn causes an additional load on the refrigerant loop compressor  152 . Through additional load or running of the compressor  152 , more heat is generated or expelled through the LCGC  160  which may be used for additional heating of the passenger cabin  108  or the battery loop  134  as described above. In this manner, the refrigerant loop  124  is effectively being used as a heat pump, i.e., use of a refrigeration cycle or the refrigerant loop  124  to generate heat. In this manner, the Coefficient of Performance for heating may exceed 2 or 3. 
     Referring to  FIG. 2 , an alternate aspect of the thermal management system  100  of  FIG. 1  is shown. Where identical components disclosed in  FIG. 1  are included, the same reference numbers are used and not further described except where noted. In the  FIG. 2  example, aspects of the refrigerant loop  124 , the heating loop  128 , the cooling loop  130 , the battery loop  134 , the powertrain loop  140 , and the HVAC unit  146  are as generally described above in  FIG. 1 . When the components are slightly modified, the use of an “A” after the reference numeral is employed. 
     An alternate refrigerant loop  124 A, shown in  FIG. 2 , includes an optional gas cooler radiator  161  (e.g., refrigerant radiator) as generally shown in dotted line to further reduce the temperature of the refrigerant flowing from the LCGC  160  to the accumulator  150 . A valve (not shown) or other device may be used to bypass the gas cooler radiator  161  and selectively route refrigerant directly from the LCGC  160  to the accumulator  150  as shown in  FIG. 1 . 
       FIG. 2  also shows an alternate battery loop  134 A. The battery loop  134 A includes a heating conduit  270 A routed directly to, and in thermal communication with, the LCGC  160  as generally shown without the separate heat exchanger  190  as described in  FIG. 1 . When the valve  266  is selectively positioned to direct battery coolant to the heating conduit  270 A, the LCGC  160  provides additional heat directly to the battery coolant in the manner generally described in  FIG. 1 . 
     The battery loop  134 A of  FIG. 2  also includes a cooling conduit  274 A routed directly to, and in thermal communication with, the chiller  166  as generally shown without the separate heat exchanger  226  described in  FIG. 1 . When the valve  266  is selectively positioned to direct battery coolant to the cooling conduit  274 A, the chiller  166  removes heat from or cools the battery coolant in the manner generally described in  FIG. 1 . The bypass conduit  280  is used with the heating conduit  270 A and the cooling conduit  274 A, as well as with various positions of the valve  266 , to blend the battery coolant flow to both the heating conduit  270 A or the cooling conduit  274 A with the bypass conduit  280  as described for  FIG. 1 . The  FIG. 2  example is advantageous in that the heat exchangers  190  and  226  of  FIG. 1  are eliminated and replaced by expanded use of the LCGC  160  and the chiller  166 . 
     In an example of the structure of the LCGC  160  as configured in  FIG. 2 , the battery loop heating conduit  270 A carrying the battery coolant is placed in thermal communication with the refrigerant conduit  154  carrying the high pressure and high temperature refrigerant. In addition, the heating loop conduit  182  is placed in thermal communication with the refrigerant conduit  154 . The position of the battery loop valve  266 , the position of the heating loop valve  194 , and operation of the compressor  152  determine which, if any, of the fluids are actively flowing through the LCGC  160  depending on the demands or loads on the system  100 A. Examples of heat exchangers that may be used as the LCGC  160  of the thermal management system  100 A are discussed further below with reference to  FIGS. 6A-10 . 
     The construction of the chiller  166  as configured in  FIG. 2  would be the same as for the LCGC  160  described above. Further, the construction of the LCGC  160  and the chiller  166  in the  FIG. 1  example would be similar in the  FIG. 2  example except that the battery loop heating conduit  270 A and the battery loop cooling conduit  274 A would not be included in either the LCGC  160  or the chiller  166  in the  FIG. 1  configuration. Examples of heat exchangers that may be used as the chiller  166  of the thermal management system  100 A are discussed further below with reference to  FIGS. 6A-10 . 
     It should be understood that the various valves disclosed herein may be different types of valves and/or be formed of multiple valves. Furthermore, the flow positions of such valves may also be referred to as configurations accounting for the different types of valves and/or combinations of valves that may provide similar flow paths. 
     Referring to  FIG. 3 , an electronic control system  350  is shown which includes, or is in electronic and digital communication with, a processor  352 , a programmable controller  354 , and a temporary and/or permanent memory device  356  for storing algorithms, computer code instructions and data. These components are all in communication with each other through a bus  358  or other similar device. A human machine interface (HMI) and other components (not shown) can also be included and connected through a bus interface  360 . The electronic control system  350  can be part of a vehicle electronic control unit (ECU) (not shown) or can be separate and in communication with the vehicle ECU. Although described in use with  FIG. 1  system  100  below, it is understood system  350  is equally applicable to the system  100 A example shown in  FIG. 2 . 
     The previously described temperature and/or pressure sensors (collectively shown as  362 ) for each of the thermal management subsystem loops  124 ,  128 ,  130 ,  134 ,  140  are also in electronic and/or digital communication with the electronic control system  350 . In one example of the system  100 , the electronic control system  350  monitors the temperature and/pressure sensor signals and data generated by the sensors  362  and adjusts the respective valves  194 ,  266 ,  320  (collectively shown as  364 ) to the appropriate flow position according to pre-programmed and stored software or coded instructions in the electronic control system  350 . In a similar manner, the various pumps  214 ,  252 ,  292 , the compressor  152 , and other components which are selectively operable as previously described can be in electronic and/or digital communication with the electronic control system  350  through the bus interface  624  for operation, coordination, sequencing, and control of the functions and operations described herein. 
     For example, if the temperature sensor  284  on the battery loop  134  measures the temperature of the battery loop coolant to be above a preprogrammed temperature target or range, the electronic control system  350  can automatically and electronically adjust the valve  266  to a flow position that directs the battery loop coolant to the cooling conduit  274  through the battery heat exchanger  226  to cool or remove thermal heat from the battery loop  134 , reducing the temperature of the battery loop coolant and the battery module  260  to within the predetermined temperature target or range. A similar process can be executed if the temperature sensor  284  measures the temperature of the battery loop coolant to be below a preprogrammed temperature target or range. The electronic control system  350  can adjust the flow position of the valve  266  to direct the flow of battery loop coolant toward the heating conduit  270  and the heat exchanger  190  to add thermal heat to the battery loop coolant. Alternatively, the bypass conduit  280  or various combinations of the cooling conduit  274 , the heating conduit  270 , and the bypass conduit  280  described above can receive the battery loop coolant based on the flow position of the valve  266  and depending on the preprogrammed ranges and measured operating conditions of the battery loop  134 . 
     A similar loop sensor measurement and valve control operation or process can be used for the heating loop  128  to add heat through the LCGC  160  or expel heat through the low temperature radiator  204 . A similar loop sensor measurement and valve control operation or process can be used for the powertrain loop  140  to cool or bypass the cooling and exhaust conduits  324 ,  330 . Other devices and methods of monitoring and controlling the flow position of the valves  364  and the flow of refrigerant or coolant can be used. In another example, the electronic control system  350  can further monitor and control the operation of the refrigerant loop  124  through adjusting and controlling operation of the compressor  152  speed and expansion valve  162  position to control the temperature and pressure of the refrigerant for the refrigerant loop  124  and the coolant for the loops  128 ,  130 ,  134 ,  140  in communication with refrigerant loop  124 . 
     In other examples, different valve or fluid control devices (not shown) for controlling the flow of coolant through the heating, cooling, battery, and powertrain loops  128 ,  130 ,  134 ,  140  can be used. Further, different conduit numbers, configurations and routing for each loop can be made to suit the particular application. Different heat transfer devices than the disclosed heat exchangers  190 ,  220 ,  226 , the chiller  166 , and the LCGC  160  can also be used to obtain the disclosed features and functions. 
     Referring to  FIG. 4 , a process  400  for monitoring and altering the temperature of the thermal management battery subsystem or loops  134 ,  134 A is illustrated. In the example, process step  410  monitors the temperature of the battery loop coolant in the battery loops  134 ,  134 A. In the example shown in  FIGS. 1 and 2 , the temperature sensor  284  measures the temperature of the battery loop coolant and transfers temperature management data to the electronic control system  350  of  FIG. 3 . 
     In step  420 , the measured received battery loop coolant temperature data can be compared to a preprogrammed temperature target or temperature range that can be pre-stored in the memory device  356  connected to the electronic control system  350 . In one example, the stored temperature target is an acceptable value or range for optimal performance of the battery module  260 . It is understood that this comparison step  420  can be eliminated and replaced with a less sophisticated temperature measurement device and/or system. 
     In step  430 , the electronic control system  350  automatically adjusts the flow position of the battery loop coolant flow valve  266  to add heat, remove heat, or maintain the measured temperature of the battery loop coolant. The valve  266  can be adjusted to a variety of positions as described in the alternative sub-steps below. 
     In sub-step  440 , on determination that the measured battery loop coolant temperature is below the preprogrammed temperature target or range, the flow position of the valve  266  can be automatically adjusted to add heat to the battery coolant as described above and generally illustrated. For example, the valve  266  can direct the flow of the battery loop coolant to the heating conduit  270  and through the heat exchanger  190  as shown in  FIG. 1  or to the heating conduit  270 A and through the LCGC  160  as shown in  FIG. 2  to add thermal heat to the battery coolant. 
     In alternative sub-step  450 , on determination that the measured battery loop coolant temperature is above a preprogrammed target value or range, the flow position of the valve  266  can be automatically adjusted to remove heat or cool the battery coolant as described above and generally illustrated. For example, the valve  266  can direct the battery loop coolant to the cooling conduit  274  and through the heat exchanger  226  in communication with the cooling loop  130  as shown in  FIG. 1  or to the cooling conduit  274 A and the chiller  166  as shown in  FIG. 2  to remove thermal heat from the battery loop coolant. 
     In alternative sub-step  460 , on determination that the measured battery loop coolant temperature is at the target value or within the target/acceptable range, the flow position of the valve  266  can be automatically adjusted to direct the flow of battery loop coolant to the bypass conduit  280  to avoid the flow of battery loop coolant to either of the heat exchangers  190 ,  226  in  FIG. 1 , or the LCGC  160  or the chiller  166  in  FIG. 2 , to avoid adding or removing thermal heat from the battery loop coolant. In another alternative sub-step (not shown), the speed of the battery loop pump  252  can be reduced, increased, or stopped, temporarily idling the flow of battery loop coolant through the battery loop  134 . The activation, change in speed, or idling of the other pumps discussed and illustrated in the other system loops may also be controlled by electronic control system  350 . 
     In another alternative sub-step  470 , the flow position of the valve  266  can be automatically adjusted to a position so as to direct the battery loop coolant to partially flow to both the heating conduits  270 ,  270 A and the bypass conduit  280  or to both the cooling conduits  274 ,  274 A and the bypass conduit  280  for increased control of the temperature of the battery loop coolant. 
     Referring to  FIG. 5 , a process  500  for heating the heating loop  128  and/or the battery loops  134 ,  134 A using the refrigerant loops  124 ,  124 A is illustrated. In step  510 , refrigerant is compressed in the refrigerant loops  124 ,  124 A. In one example, the compressor  152  is used to compress the refrigerant to a high pressure and high temperature. 
     In step  520 , the compressed refrigerant flows through the LCGC  160 . In the  FIG. 1  and  FIG. 2  examples, the heating loop coolant from the heating loop  128  draws heat from the refrigerant conduit  154  in the LCGC  160 . In the  FIG. 2  example, the battery loop coolant from the battery loop  134 A may also draw heat from the refrigerant conduit  154  in the LCGC  160 . 
     In step  530 , in the  FIG. 1  and  FIG. 2  examples, the LCGC  160  transfers thermal energy in the form of heat to the heating loop  128 , that is, to the heating loop coolant which draws or absorbs the expelled heat, thereby increasing the temperature of the heating loop coolant. In the  FIG. 2  example, the LCGC  160  may also transfer thermal energy in the form of heat to the battery loop coolant from the battery loop  134 A. The steps  520  and  530  can occur simultaneously. 
     In optional step  535 , applicable to the example in  FIGS. 1 and 2 , increasing the temperature of the heating loop coolant is possible through use of the electric heater  184  in thermal communication with the heating loop coolant. 
     In optional step  540 , applicable to the example in  FIGS. 1 and 2 , the increased temperature heating loop coolant can be used to selectively heat the passenger cabin  108 . As disclosed above, the HVAC unit  146  includes the heater core  188  in fluid communication with the heating loop  128 , and the cabin blower  238  can be used to selectively provide heated air to the passenger cabin  108  by forcing the air across the heater core  188 . 
     In optional, alternative step  550 , applicable to the example in  FIG. 1 , selectively heating the battery loop coolant is possible by sending the increased-temperature heating loop coolant through the heat exchanger  190  in thermal communication with the battery loop coolant. It is understood that additional steps and a different ordering of the disclosed steps in the process  500  is also possible. 
     Referring to  FIGS. 6A-6G , a heat exchanger  600  is configured to exchange or transfer heat between at least three fluids of various loops flowing therethrough. The heat exchanger  600  may, for example, be configured and used as the chiller  166  and/or the LCGC  160  of the thermal management system  100 A. For example, the thermal management system  100 A may include two of the heat exchangers  600 , which are used as the chiller  166  and the LCGC  160  and which may have different configurations. 
     Referring to  FIGS. 6A-6C , the heat exchanger  600  includes a core  602  (e.g., structure or core structure) that defines passages through which the fluids flow and various manifold structures  604  that connect the heat exchanger  600  to a thermal management system, such as the thermal management system  100 A. Referring to  FIGS. 6D-6G , more particularly, the heat exchanger  600  includes a refrigerant passage  620  through which refrigerant  620   a  flows, a primary coolant passage  640  through which a primary coolant  640 ′ flows, and a secondary coolant passage  660  through which a secondary coolant  660 ′ flows. Fluidic separation is maintained between the refrigerant  620   a , the primary coolant  640 ′, and the secondary coolant  660 ′, while heat is transferred therebetween. The core  602 , including the refrigerant passage  620 , the primary coolant passage  640 , and the secondary coolant passage  660  thereof, are discussed in further detail below. The manifolds are also discussed in further detail below. In the figures, the passages, the passes thereof, the fluid flowing therethrough, and the direction of the fluid flow may generally be indicated by arrows and/or cross-hatching of which down-right angled cross-hatching indicates flow into the page and up-right angled cross-hatching indicates flow out of the page. 
     The heat exchanger  600  may be configured, among other considerations, according to a number of passes the refrigerant passage  620 , the primary coolant passage  640 , and the secondary coolant passage  660  each make through the heat exchanger  600 , as well as which passes of the refrigerant passage  620 , the primary coolant passage  640 , and the secondary coolant passage  660  transfer heat directly between each other. The term “pass” generally refers a portion of a respective passage, or the fluid flowing therethrough, which extends across the width or the length, or substantial majorities thereof of the heat exchanger  600  or the core  602  thereof. A single pass may be cooperatively formed by parallel flows of a fluid (e.g., in different tube structures or cavities, as discussed below). Direct heat transfer is generally considered heat transfer between two fluids without heat transfer through an intermediate fluid but may occur through an intermediate structure (e.g., a wall structure or a tube structure). Direct heat transfer may be referred to as occurring between passes of fluids or between the fluids of the passes. Indirect heat transfer is generally considered heat transfer between two fluids via one or more intermediate fluids. 
     For example, in the heat exchanger  600 , the refrigerant passage  620  includes six refrigerant passes  620   a ,  620   b ,  620   c ,  620   d ,  620   e ,  620   f , the primary coolant passage  640  includes two primary coolant passes  640   a ,  640   b , and the secondary coolant passage  660  includes one secondary coolant pass  660   a . Three of the refrigerant passes  620   a ,  620   b , and  620   c  extend through and transfer heat directly with a first of the coolant passes  640   a , the three other refrigerant passes  620   d ,  620   e , and  620   f  extend through are transfer heat directly with a second of the primary coolant pass  640   b , and the secondary coolant pass  660   a  transfers heat directly with both the primary coolant passes  640   a ,  640   b . Variations of the heat exchanger  600  are discussed with reference to  FIGS. 7-10  below, which include a heat exchanger  700  having three primary coolant passes, and a heat exchanger  800  having seven refrigerant passes, but which may include more or fewer primary coolant passes (e.g., one, four, or five), and more or fewer refrigerant passes (e.g., fewer than six or more than seven). 
     The core  602  includes wall structures that define various cavities that form the primary coolant passage  640  and the secondary coolant passage  660 . The core  602  additionally includes refrigerant tubes  622  that cooperatively form the refrigerant passage  620  and which extend through the cavities. Referring to  FIG. 6D , more particularly, the core  602  includes a first primary coolant cavity  642   a  and a second primary coolant cavity  642   b , which cooperatively form the primary coolant passage  640  and which individually form the first primary coolant pass  640   a  and the second primary coolant pass  640   b , respectively. The first primary coolant cavity  642   a  and the second primary coolant cavity  642   b  are fluidically connected, such that the primary coolant  640 ′ flows serially therethrough in opposite directions. The wall structures are formed of a metal material (e.g., aluminum) or other suitable material, which facilitates heat transfer between the primary coolant passage  640  and the secondary coolant passage  660  (e.g., via conduction therethrough). The refrigerant tubes  622  are discussed in further detail below. 
     The primary coolant cavities  642   a ,  642   b  are generally rectangular in cross-section. The first primary coolant cavity  642   a  is formed by (e.g., defined between) by a top wall  602   a  and a first intermediate wall  602   b  opposite and parallel thereto, a first side wall  602   c  and a second side wall  602   d  opposite and parallel thereto, and a first end wall  602   e  and a second end wall  602   f . The second primary coolant cavity  642   b  is also formed by various wall structures of the core  602 , which may be common with those wall structures forming the first primary coolant cavity  642   a . More particularly, the second primary coolant cavity  642   b  is formed by a bottom wall  602   g  and a second intermediate wall  602   h  opposite and parallel thereto, the first side wall  602   c  and the second side wall  602   d , and the first end wall  602   e  and the second end wall  602   f  The first end wall  602   e  and/or the second end wall  602   f , or portions thereof, may be omitted in some embodiments as discussed in further detail below. The intermediate walls  602   b ,  602   h  may, for example, be referred to as a coolant plate, as they facilitate heat transfer between fluids (e.g., the primary coolant  640 ′ and the secondary coolant  660 ′) flowing on either side thereof as discussed in further detail below. The intermediate walls  602   b ,  602   h , as well as the top wall  602   a  and the bottom wall  602   g , each have a width and a length that generally corresponds to the width and the length, respectively of the core  602  (e.g., between 250 and 290 mm, such as approximately 270 mm). Furthermore, the length of the core  602  and the intermediate walls  602   b ,  602   h , as well as the top wall  602   a  and the bottom wall  602   g , account for the number, width, and spacing of the refrigerant tubes  622  discussed below. 
     The core  602  may, for example, have a height measured between the top wall  602   a  and the bottom wall  602   g  of between approximately 40 and 50 mm (e.g., approximately 46 mm), a width measured between the first side wall  602   c  and the second side wall  602   d  of between approximately 250 and 290 mm (e.g., approximately 270 mm), and a length measured between the first end wall  602   e  and the second end wall  602   f  of between approximately 250 and 290 mm (e.g., approximately 270 mm). The manifold structures  604  may, for example, be arranged on each side and one end of the core  602  and have widths of between approximately 10 and 40 mm (e.g., approximately 30 mm and 20 mm, respectively). As a result, the heat exchanger  600  may have an overall length measured between the manifold structures  604  on each end (e.g., adjacent the end walls  602   e ,  6020  of between approximately 290 and 370 mm (e.g., approximately 330 mm), and an overall width measured between the manifold structure  604  at one side and the second side wall  602   d  of between approximately 260 and 310 mm (e.g., approximately 290 mm). The heat exchanger  600  may, however, have different dimensions overall, of the core  602 , and/or of the manifold structures  604  (e.g., taller or shorter, wider or narrower, longer or shorter). Furthermore, while the various wall structures are referred to with directional terms for reference purposes, it should be understood that the heat exchanger  600  may, in use, be arranged in different orientations. For example, in one preferred orientation, the heat exchanger  600  may be arranged such that gravity is in the direction of the width (e.g., such that second side wall  602   d  may be an upper, horizontal surface while, while the top wall  602   a  and the bottom wall  602   g  are side, vertical surfaces). 
     As referenced above, the primary coolant  640 ′ flows serially through the first primary coolant cavity  642   a , forming the first primary coolant pass  640   a , and then through the second primary coolant cavity  642   b , forming the second primary coolant pass  640   b . Referring additionally to  FIG. 6G , the first primary coolant cavity  642   a  receives the primary coolant  640 ′ at a first end thereof from an inlet structure (e.g., a primary inlet manifold  644   a , as discussed in further detail below), for example, through the first end wall  602   e . The primary coolant  640 ′ flows through the first primary coolant cavity  642   a  in a first direction from the first end to a second end thereof. The primary coolant  640 ′ then flows from the second end of the first primary coolant cavity  642   a , for example, through the second end wall  602   f , to a first end of the second primary coolant cavity  642   b . The first primary coolant cavity  642  and the second primary coolant cavity  642   b  may, for example, be fluidically connected by one or more primary coolant tubes  646  extending therebetween (e.g., between the second end and the first end, respectively, thereof), which may be arranged in or formed by one of the manifold structures  604 . The primary coolant  640 ′ then flows through the second primary coolant cavity  642   b  in a second direction from the first end to the second end thereof, which is substantially opposite the first direction. The primary coolant  640 ′ is expelled from the second end of the second primary coolant cavity  642   b , for example, through the first end wall  602   e , to an outlet structure (e.g., a primary outlet manifold  644   b , as discussed in further detail below). The first primary coolant cavity  642   a  and the second primary coolant cavity  642   b  may be fluidically connected in other suitable manners, for example, by a chamber (e.g., formed by one of the manifold structures  604 ). 
     The secondary coolant cavity  662  is arranged between the primary coolant cavities  642   a ,  642   b  to facilitate heat transfer between the secondary coolant  660 ′ and the primary coolant  640 ′, respectively, flowing therethrough. More particularly, the secondary coolant cavity  662  is defined between the first intermediate wall  602   b , which also defines the first primary coolant cavity  642   a , and the second intermediate wall  602   h , which also defines the second primary coolant cavity  642   b . Heat is, thereby, transferred between the secondary coolant  660 ′ and the primary coolant  640 ′ in the first primary coolant cavity  642   a  and the second primary coolant cavity  642   b  via the first intermediate wall  602   b  and the second intermediate wall  602   h . In this arrangement, the secondary coolant passage  660 , in effect, insulates the first primary coolant pass  640   a  from the second primary coolant pass  664   b  to prevent direct heat transfer therebetween through a wall structure. 
     The secondary coolant cavity  662  is generally rectangular in cross-section. The secondary coolant cavity  662  may, for example, have similar (e.g., substantially equal) cross-sectional dimensions in one plane (e.g., width and length) as the primary coolant cavities  642   a ,  642   b , while having a different dimension in a perpendicular plane (e.g., having a lesser height). The secondary coolant cavity  662 , as described above, is formed by the first intermediate wall  602   b  and the second intermediate wall  602   h , and additionally by the first side wall  602   c  and the second side wall  602   d , and the first end wall  602   e  and the second end wall  602   f.    
     The secondary coolant  660 ′ flows through the secondary coolant cavity  662  in a single pass. The secondary coolant cavity  662  receives the secondary coolant  660 ′ at a first end thereof from an inlet structure (e.g., a secondary inlet manifold  664   a , as discussed in further detail below), for example, through the first end wall  602   e . The secondary coolant  660 ′ then flows through the secondary coolant cavity  662  from the first end to a second end thereof in the same direction (i.e., the first direction) as the primary coolant  640 ′ flows through the first primary coolant cavity  642   a . The secondary coolant  660 ′ is expelled from the second end of the primary coolant cavity  642   a , for example, through the second end wall  602   f , to an outlet structure (e.g., a secondary outlet manifold  664   b , as discussed in further detail below). Alternatively, the secondary coolant  660 ′ may flow through the secondary coolant cavity  662  in the same direction as the primary coolant  640 ′ flows through the second primary coolant cavity  642   b  (i.e., in the second direction), or may flow perpendicular thereto (e.g., between the first side wall  602   c  and the second side wall  602   d ). 
     Referring to  FIGS. 6E-6F , the refrigerant passage  620  is cooperatively formed by the refrigerant tubes  622  (e.g., n number of refrigerant tubes  622   1  to  622   n ) that are spaced apart laterally (e.g., along the first side wall  602   c ) and extend substantially parallel with each other. The heat exchanger  600  may, for example, include between 20 and 60 refrigerant tubes  622  (e.g., between 25 and 35 refrigerant tubes  622 , such as 28 refrigerant tubes  622 ). It should be noted that in  FIG. 6E  only 13 refrigerant tubes  622  are illustrated for clarity purposes, while the vertical jagged line indicates that additional refrigerant tubes  622  may be included and that the core  602  may have different dimensions to accommodate additional refrigerant tubes  622 . The refrigerant tubes  622  may also be referred to as refrigerant lines. 
     The refrigerant tubes  622  extend through the core  602  in a serpentine manner to form the multiple refrigerant passes. More specifically, each of the refrigerant tubes  622  includes six tube segments  622   a ,  622   b ,  622   c ,  622   d ,  622   e , and  622   f  (e.g., straight segments) through which the refrigerant  620 ′ flows serially. The tube segments  622   a - 622   f  extend through the first primary coolant cavity  642   a  and the second primary coolant cavity  642   b  from the first side wall  602   c  to the second side wall  602   d , for example, parallel with the top wall  602   a  and the first end wall  602   e . For example, in the heat exchanger  600 , three of the tube segments  622   a ,  622   b , and  622   c  extend through the first primary coolant cavity  642   a , while the other three of the tube segments  622   d ,  622   e , and  622   f  extend through the second primary coolant cavity  642   b . The refrigerant tubes  622  additionally include connecting segments (e.g., curved segments; not labeled), which extend outside the primary coolant cavities  642   a ,  642   b  (e.g., through the first side wall  602   c  and the second side wall  602   d ) and interconnect the tube segments  622   a - 622   f  for the refrigerant  620 ′ to flow serially therethrough. The refrigerant tubes  622  may protrude through the first side wall  602   c  and the second side wall  602   d  and, for example, be supported thereby and/or be sealingly connected thereto (e.g., to prevent the primary coolant  640 ′ and the secondary coolant  660 ′ from leaking between the side walls  602   c ,  602   d  and the refrigerant tubes  622 ). Alternatively, the refrigerant tubes  622 , including the curved segments, may be contained within the primary coolant cavities  642   a ,  642   b  (i.e., between the first side wall  602   c  and the second side wall  602   d ) with, for example, only the first and the second end thereof (i.e., formed by the first and the sixth of the tube segments  622   a ,  622   f  extending through the first side wall  602   c ). The tube segments  622   a - 622   f  have a length that generally corresponds to a width of the core  602  (e.g., between 250 and 290 mm, such as approximately 270 mm). 
     The refrigerant  620 ′ flows through the refrigerant passage  620  in six passes (i.e., formed by the tube segments  622   a - 622   f ) back and forth in opposing directions, which are perpendicular to the first direction and the second direction that the primary coolant  640 ′ flows through the primary coolant cavities  642   a ,  642   b . The refrigerant tubes  622  each receive the refrigerant  620 ′ at a first end thereof (e.g., formed by a first of the tube segments  622   a ) from an inlet structure (e.g., a refrigerant inlet manifold  664   a , a discussed in further detail below), for example, through the first side wall  602   c . The refrigerant  620 ′ then flows serially through the tube segments  622   a - 622   f  and the connecting segments therebetween in a serpentine manner (i.e., back and forth directions) to a second end thereof (e.g., formed by a sixth or last of the tube segments  6220 . The refrigerant  620 ′ is expelled from the second ends of the refrigerant tubes  622 , for example, through the second side wall  602   d , to an outlet structure (e.g., a refrigerant outlet manifold  624   b ). 
     The refrigerant tubes  622  are, for example, configured to carry the refrigerant  620 ′ (e.g., CO 2 , such as R744), under high pressure. The refrigerant tubes  622  may, for example, each be continuously formed of a metal material (e.g., aluminum), for example, being extruded and bent to form the tube segments  622   a - 622   f  and the connection segments therebetween. Referring to  FIG. 6H , in one example, each of the refrigerant tubes  622  includes therein a series of channels  622 ′ (e.g., channels, for example, three) that are spaced apart laterally and extend therethrough from the first end to the second end thereof. In cross-section, the refrigerant tube  622  may be substantially rectangular in cross-section, for example, having a width of approximately 6.3 mm and a height of approximately 1.4 mm, or be larger or smaller in width or height. As is shown, the larger dimension of the refrigerant tube  622  (e.g., the width as shown) may be arranged in the primary coolant cavities  642   a ,  642   b  substantially parallel with the direction of flow of the primary coolant  640 ′. The channels  622 ′ may, for example, be circular and have a diameter of between 0.5 and 1.3 mm (e.g., 1.3 mm), or may have another shape (e.g., triangular, rectangular, oval, etc.) and/or have another size. The refrigerant tube  622  may be still configured in other manners, for example, having a few or more channels  622 ′ (e.g., one, two, four, or more), have a different cross-sectional shape (e.g., circular), and/or be configured for other fluids (e.g., a low pressure refrigerant or coolant). As a result, the refrigerant tubes  622  may collectively include, for example, between approximately 60 and 180 the channels  622 ′ (e.g.,  84  of the channels  622 ′), which cooperatively form the refrigerant passage  620 . 
     With the refrigerant tubes  622  extending through the primary coolant cavities  642   a ,  642   b , the primary coolant  640 ′ flows in contact therewith, such that heat may be transferred between the refrigerant  620 ′ and the primary coolant  640 ′ via the material forming the refrigerant tubes  622 . Moreover, heat may be transferred indirectly between the refrigerant  620 ′ and the secondary coolant  660 ′ via the primary coolant  640 ′, which exchanges heat directly with the refrigerant  620 ′ and the secondary coolant  660 ′. 
     Additionally, with the primary coolant cavities  642   a ,  642   b  having the refrigerant tubes  622  (i.e., the tube segments  622   a - 622   f  thereof) extend therethrough and the secondary coolant cavity  662  being arranged therebetween, the heat exchanger  600  may be considered to have fluid layers. The heat exchanger  600  includes 15 fluid layers, which include six refrigerant layers (i.e., formed by the six tube segments  622   a - 622   f ), eight primary coolant layers (i.e., defined above, below, and between the six tube segments  622   a - 622   f  within the primary coolant cavities  642   a ,  642   b , and which may have the same or different height as each other), and one secondary coolant layer (i.e., defined by the secondary coolant cavity  662 , which may have the same or different height as the primary coolant layers). 
     The refrigerant inlet manifold  624   a  is configured to connect to a refrigerant input, for example at a refrigerant inlet  624   a ′, and is connected to the refrigerant passage  620 . The refrigerant inlet manifold  624   a  may be formed by and/or contained in one of the manifold structures  604 . The refrigerant inlet manifold  624   a  is, for example, configured as a tubular structure that is connected to the first ends (e.g., the first tube segments  622   a ) each of the refrigerant tubes  622  that cooperatively form the refrigerant passage  620 . The refrigerant inlet manifold  624   a  receives the refrigerant  620 ′ from the refrigerant input and passes the refrigerant  620 ′ to the refrigerant passage  620  and, in particular, distribute the refrigerant  620 ′ to each of the refrigerant tubes  622 . 
     The refrigerant outlet manifold  624   b  is configured to connect to a refrigerant output, for example at a refrigerant outlet  624   b ′. The refrigerant outlet manifold  624   b  is a tubular structure that is connected to the second ends (e.g., the sixth tube segments  622   f ) of each of the refrigerant tubes  622 . The refrigerant outlet manifold  624   b  may be formed by one of the manifold structures  604 . The refrigerant outlet manifold  624   b  receives the refrigerant  620 ′ from the refrigerant tubes  622  and passes the refrigerant  620 ′ to the refrigerant output. The refrigerant input and the refrigerant output may be a common refrigerant loop. For example, when the heat exchanger  600  is configured and used as either the chiller  166  or the LCGC  160  in the thermal management system  100 A, the refrigerant passage  620  is connected to the refrigerant loop  124 A via the refrigerant inlet manifold  624   a  and the refrigerant outlet manifold  624   b.    
     As shown, the refrigerant inlet manifold  624   a  and the refrigerant outlet manifold  624   b  are arranged on a common side of the heat exchanger  600 , which corresponds to an even number refrigerant passes (i.e., six as shown) of the refrigerant passage  620 . The refrigerant inlet manifold  624   a  and the refrigerant outlet manifold  624   b  each extend substantially parallel with and adjacent to the first side wall  602   c  of the core  602 . The refrigerant inlet manifold  624   a  and the refrigerant outlet manifold  624   b  are each made of a compatible material (e.g., aluminum) for being connected to the refrigerant tubes  622  and reliably handle the pressure associated with refrigerant  620 ′. The refrigerant inlet manifold  624   a  and the refrigerant outlet manifold  624   b  are additionally configured to connect to the refrigerant input and refrigerant output, respectively, in a suitable manner, such as with releasable connections (e.g., fittings) or with permanent connections (e.g., brazed). 
     The primary inlet manifold  644   a  is configured to connect to a primary coolant input, for example at a primary inlet  644   a ′, and is connected to the primary coolant passage  640 . The primary inlet manifold  644   a  is, for example, configured as a chamber in fluid communication with the first end of the first primary coolant cavity  642   a , for example, through one or more apertures (not labeled) in the first end wall  602   e  of the core  602 . Alternatively, the first end wall  602   e  may be omitted. The primary inlet manifold  644   a  receives the primary coolant  640 ′ from the primary coolant input and passes the primary coolant  640 ′ to the primary coolant passage  640  and, may additionally, distribute the primary coolant  640 ′ across the first end of the first primary coolant cavity  642   a.    
     The primary outlet manifold  644   b  is configured to connect to a primary coolant output, for example at a primary outlet  644   b ′. The primary outlet manifold  644   b  is, for example, configured as another chamber in fluid communication with the second end of the second primary coolant cavity  642   b . The primary outlet manifold  644   b  receives the primary coolant  640 ′ from the second primary coolant cavity  642   b  and passes the primary coolant  640 ′ to the primary coolant output. The primary coolant input and the primary coolant output may be a common coolant loop. For example, when the heat exchanger  600  is configured and used as the chiller  166 , the primary coolant passage  640  is connected to the cooling loop  130  via the primary inlet manifold  644   a  and the primary outlet manifold  644   b . When instead configured and used as the LCGC  160  of the thermal management system  100 A, the primary coolant passage  640  is connected to the heating loop  128  via the primary inlet manifold  644   a  and the primary outlet manifold  644   b.    
     As shown, the primary inlet  644   a ′ and the primary outlet  644   b ′ are arranged on a common side of the heat exchanger  600 , which corresponds to an even number of primary coolant passes (i.e., two as shown) of the primary coolant passage  640 . It may also be preferred to orient the primary inlet  644   a ′ to be lower than the primary outlet  644   b ′ (e.g., when installed in the thermal management system  100 A). The primary inlet manifold  644   a  and the primary outlet manifold  644   b  each extend substantially parallel with and adjacent to the first end wall  602   e  of the core  602 . The primary inlet manifold  644   a  and the primary outlet manifold  644   b  are each made of a compatible material (e.g., aluminum) for being connected to the core  602  and for carrying the primary coolant  640 ′ therein (e.g., 50/50 mixture of water and ethylene glycol), and may be formed separately or continuously with other portions of the core  602 . The primary inlet manifold  644   a  and the primary outlet manifold  644   b  are additionally configured to connect to the primary coolant input and primary coolant output, respectively, in a suitable manner, such as with releasable connections (e.g., fittings) or with permanent connections (e.g., brazed). 
     The secondary inlet manifold  664   a  is configured to connect to a secondary coolant input, for example at a secondary inlet  664   a ′, and is connected to the secondary coolant passage  660 . The secondary inlet manifold  664   a  is, for example, configured as a chamber in fluid communication with the first end of the secondary coolant cavity  662   a , for example, through one or more apertures (not labeled) in the first end wall  602   e  of the core  602 . Alternatively, the first end wall  602   e  may be omitted. The secondary inlet manifold  664   a  receives the secondary coolant  660 ′ from the secondary coolant input and transfers the secondary coolant  660 ′ to the secondary coolant passage  660  and, may additionally, distribute the secondary coolant  660 ′ across the first end of the secondary coolant cavity  662 . 
     The secondary outlet manifold  664   b  is configured to connect to a secondary coolant output, for example at a secondary outlet  664   b ′, and is connected to the secondary coolant passage  660 . The secondary outlet manifold  664   b  is, for example, configured as another chamber in fluid communication with the second end of the secondary coolant cavity  662 . The secondary outlet manifold  664   b  receives the secondary coolant  660 ′ from the secondary coolant cavity  662  and transfers the secondary coolant  660 ′ to the secondary coolant output. The secondary coolant input and the secondary coolant output may be a common coolant loop. For example, when the heat exchanger  600  is configured and used as either the chiller  166  or the LCGC  160 , the secondary coolant passage  660  is connected to the battery loop  134 A via the secondary inlet manifold  664   a  and the secondary outlet manifold  664   b . It may be preferred to locate the secondary inlet  664   a ′ below the secondary outlet  664   b ′, for example, in the thermal management system  100 A. 
     As shown, the secondary inlet manifold  664   a  and the secondary outlet manifold  664   b  are arranged on different sides of the heat exchanger  600 , which corresponds to an odd number of secondary coolant passes  660   a  (i.e., one as shown) of the secondary coolant passage  660 . The secondary inlet manifold  664   a  and the secondary outlet manifold  664   b  extend substantially parallel with and adjacent to the first end wall  602   e  and the second end wall  602   f , respectively, of the core  602 . The secondary inlet manifold  664   a  and the secondary outlet manifold  664   b  are each made of a compatible material (e.g., aluminum) for being connected to the core  602  and for carrying the secondary coolant  660 ′ therein (e.g., a 50/50 mixture of water and ethylene glycol), and may be formed separately or continuously with other portions of the core  602  and/or the primary inlet manifold  644   a  and/or the primary outlet manifold  644   b . The secondary inlet manifold  664   a  and the secondary outlet manifold  664   b  are additionally configured to connect to the secondary coolant input and secondary coolant output, respectively, in a suitable manner, such as with releasable connections (e.g., fittings) or with permanent connections (e.g., brazed). 
     Additionally, the various manifolds and passages may be configured for the primary refrigerant  620 ′ and the primary coolant  640 ′ to transfer heat therebetween either as both enter the heat exchanger  600  or as one fluid enters and the other fluid exits the heat exchanger  600 . For example, when configured and used as a the LCGC  160 , heat is transferred from the refrigerant  620 ′ to the primary coolant  640 ′ and in turn to the secondary coolant  660 ′. The refrigerant  620 ′ decreases in temperature flowing therethrough and, thereby, has a maximum refrigerant temperature at the refrigerant inlet  624   a ′ and a minimum temperature at the refrigerant outlet  624   b ′. The primary coolant  640 ′ and the secondary coolant  660 ′ each increase in temperature flowing through the heat exchanger  600  to have minimum temperatures at the respective inlets  644   a ′,  664   a ′ and maximum temperatures at the respective outlets  644   b ′,  664   b ′. The manifolds and passages may be arranged such that the highest temperature refrigerant  620 ′ (i.e., in those tube segments  622   a - 622   c  after entering through the inlet  624   a ′) transfers heat to that primary coolant  640 ′ with the lowest temperature (i.e., in the first primary coolant cavity  642   a  after entering through the inlet  644   a ′) or that primary coolant  640 ′ with the highest temperature (i.e., in the second primary coolant cavity  642   b  prior to exiting through the outlet  644   b ′). Conversely, when configured and used as the chiller  166 , heat is transferred from the primary coolant  640 ′ to the refrigerant  620 ′. The heat exchanger  600  may be configured for the highest temperature primary coolant  640 ′ (i.e., in the first primary coolant cavity  642   a  after entering through the inlet  644   a ′) to transfer heat to the lowest temperature refrigerant  620 ′ (i.e., in those tube segments  622   a - 622   c  after entering through the inlet  624   a ′) or the highest temperature refrigerant  620 ′ (i.e., in those tube segments  622   d - 622   f  before exiting through the outlet  624   b ′). 
     Referring to  FIG. 7 , a heat exchanger  700  is a variation of the heat exchanger  600 . The heat exchanger  700  may, for example, be used as the chiller  166  in the thermal management system  100 A and/or use as the LCGC  160  in the thermal management system  100 A. For example, in one preferred embodiment, the thermal management system  100 A may include the heat exchanger  600  as the chiller  166  (e.g., transfer heat from the battery loop coolant to the refrigerant, for example, indirectly via the cooling loop coolant, thereby decreasing the temperature of the battery loop coolant) and may include the heat exchanger  700  as the LCGC  160  (e.g., to transfer heat to the battery loop coolant from the refrigerant, for example, indirectly via the heating loop coolant, thereby increasing the temperature of the battery loop coolant). 
     For brevity, differences between the heat exchanger  600  and the heat exchanger  700  are described below. For further understanding of the heat exchanger  700 , refer to the discussion of the heat exchanger  600  above. The heat exchanger  700  includes six refrigerant passes  720   a - 720   f , three primary coolant passes  740   a - 740   c , and one secondary coolant pass  760   a . Two of the refrigerant passes  720   a - 720   f  extend through and transfer heat directly with one of the three primary coolant passes  740   a - 740   c . The three primary coolant passes  740   a - 740   c  additionally transfer heat directly with the secondary coolant pass  760   a.    
     For example, the heat exchanger  700  includes a core  702 , along with a refrigerant passage  720 , a primary coolant passage  740 , and a secondary coolant passage  760 . The refrigerant passage  720  is formed by a series of refrigerant tubes  722 . The refrigerant passage  720  includes six passes  720   a - 720   f , which are each formed by tube segments  722   a - 722   f  of the refrigerant tubes  722 . 
     The primary coolant passage  740  includes three passes  740   a ,  740   b ,  740   c , which are, respectively, formed by a first cavity  742   a  (defined between first and second intermediate walls  704   h ,  704   i  of the core  702 ), a second cavity  742   b  (defined between third and fourth intermediate walls  704   j ,  704   k ), and a third cavity  742   c  (defined between the fifth and sixth intermediate walls  704   l ,  704   m ). The second cavity  742   b  is connected to the first cavity  742   a  and the third cavity  742   c  for serial flow therethrough (e.g., with connecting tubes or another suitable manner, as described above with respect to the primary coolant passage  640 ). The first and third passes  740   a ,  740   c  flow in a first direction (i.e., into the page as indicated by down-right angled cross-hatching), while the second pass  740   b  flows opposite the first direction (i.e., out of the page as indicated by up-right angled cross-hatching). A primary inlet manifold may be configured substantially similar to the primary inlet manifold  644   a  described previously, while a primary outlet manifold may be configured substantially similar to the second primary outlet manifold  644   b  but is arranged on an opposite side of the heat exchanger  700  relative to the primary inlet manifold. 
     The secondary coolant passage  760  forms a single pass  760   a , which is cooperatively formed by four secondary coolant cavities  762   a - 762   d  (i.e., parallel flow occurs through the four secondary coolant cavities  762   a - 762   d ). The four secondary coolant cavities  762   a - 762   d  are, respectively, defined between a top wall  704   a  and the first intermediate wall  704   h , between the second and third intermediate walls  704   i ,  704   j , between the fourth and fifth intermediate walls  704   k ,  704   lk , and between the sixth intermediate wall  704   m  and a bottom wall  704   b  of the core  702 . A secondary inlet manifold and a secondary outlet manifold (not shown) are, respectively, configured to, respectively, distribute and collect the secondary coolant (not labeled) to and from the four secondary coolant cavities  762   a - 762   d.    
     Heat transfer occurs directly between two of the refrigerant passes  720   a - 720   f  and each of the three primary coolant passes  740   a - 740   c  (i.e., through the material forming the refrigerant tubes  722 ). More particularly, two of the tube segments  722   a - 722   f  extend through each of the primary coolant cavities  742   a - 742   c.    
     Heat transfer additionally occurs directly between the secondary coolant pass  760   a  in two of the secondary coolant cavities  762   a - 762   d  and each of the primary coolant passes  740   a - 740   c . More particularly, two of the secondary coolant cavities  762   a - 762   d  surround each of the primary coolant cavities  742   a - 742   c  and share a common one of the intermediate walls  704   h - 704   m  therewith. For example, the secondary coolant pass  760   a  flows through the first primary coolant cavity  742   a , which is surrounded by the first and second secondary coolant cavities  762   a ,  762   b  and shares the first and second intermediate walls  704   h ,  704   i , respectively, therewith. 
     Furthermore, the first and fourth secondary coolant cavities  762   a ,  762   d  are defined, in part, by the top wall  704   a  and the bottom wall  704   b , which may be exposed to ambient air. Thus, heat may additionally be transferred between the secondary coolant pass  760   a  flowing through the first and fourth secondary coolant cavities  762   a ,  762   d  and ambient air. Moreover, the secondary coolant cavities  762   a ,  762   d  may insulate the primary coolant passage  740  from ambient air, which may prevent condensation that might otherwise form on outer surfaces of the heat exchanger  700  from humidity of the ambient air condensing as heat is transferred from the ambient air to the primary coolant  740 ′. 
     As a result of the configuration described above and shown in  FIG. 7 , the heat exchanger  700  includes 19 fluid layers, which include six refrigerant layers (i.e., formed by the six tube segments  722   a - 722   g ), nine primary coolant layers (i.e., formed in the primary coolant cavities  742   a - 742   c  between and outside of the six tube segments  722   a - 722   g  extending therethrough), and four secondary coolant layers (i.e., formed by the secondary coolant cavities  762   a - 762   d , which extend outside of and between the three primary coolant cavities  742   a - 742   c ). 
     The core  702  may, for example, have a height of between approximately 55 and 65 mm (e.g., approximately 60 mm), a width of between approximately 250 and 290 mm (e.g., approximately 270 mm), and/or a length of between approximately 190 and 230 mm (e.g., approximately 210 mm). The heat exchanger  700 , accounting for manifold structures configured as described previously, may have an overall height of between 55 and 65 mm (e.g., approximately 60 mm), an overall width of between 290 and 370 mm (e.g., approximately 330 mm), and an overall length of between approximately 200 and 270 mm (e.g., approximately 230 mm). The heat exchanger  700  and the core  702  may, however, be configured with other dimensions. Furthermore, in preferred usage scenarios, gravity may extend in the direction of the width (e.g., in either direction in which the refrigerant  720 ′ flows through the refrigerant passage  720 ) or in the direction of the length (e.g., in either direction in which the primary coolant  740 ′ flows through the primary coolant passage  740 ). 
     Referring to  FIG. 8 , a heat exchanger  800  is a variation of the heat exchanger  600 . For brevity, differences between the heat exchanger  600  and the heat exchanger  800  are described below. For further understanding of the heat exchanger  800 , refer to the discussion of the heat exchanger  600  above. The heat exchanger  800  includes a refrigerant passage  820  having seven refrigerant passes  820   a - 820   g , a primary coolant passage  840  having two primary coolant passes  840   a - 840   b , and one secondary coolant passage  860  having one secondary coolant pass  860   a . By having an odd number of refrigerant passes (i.e., seven), the refrigerant  820 ′ enters and exits the heat exchanger  800 , respectively, through a refrigerant inlet manifold  824   a  and a refrigerant outlet manifold  824   b  that are positioned on opposites sides of the heat exchanger  800 . 
     Three of the refrigerant passes  820   a - 820   f  extend through and exchange heat directly with one of the two primary coolant passes  840   a - 840   b . Another of the refrigerant passes  820   g  extends through and transfer heat directly with the secondary coolant pass  860   a . The first primary coolant pass  840   a  and the second primary coolant pass  840   b  may exchange heat directly with each other (e.g., by sharing a intermediate wall  840   m  common therebetween). The second primary coolant pass  840   b  and the secondary coolant pass  860   a  may additionally exchange heat directly with each other (e.g., by sharing another intermediate wall  804   n  common therebetween). The first primary coolant pass  840   a  may additionally exchange heat directly with ambient air (e.g., through a top wall  804   a ). The secondary coolant pass  860   a  may additionally exchange heat directly with ambient air via a bottom wall  804   b ). 
     As a result, the heat exchanger  800  may include 17 fluid layers, which include seven refrigerant layers (i.e., formed by the seven refrigerant passes  820   a - 820   g ), eight primary coolant layers (i.e., formed by the two primary coolant passes  840   a - 840   b  above, below, and between six of the refrigerant passes  820   a - 820   f ), and two secondary coolant layers (i.e., formed by the secondary coolant pass  860   a  above and below the seventh refrigerant pass  820   g ). 
     Referring to  FIG. 9 , a heat exchanger  900  is a variation of the heat exchanger  600 . For brevity, differences between the heat exchanger  600  and the heat exchanger  900  are described below. For further understanding of the heat exchanger  900 , refer to the discussion of the heat exchanger  600  above. The heat exchanger  900  includes six refrigerant passes  920   a - 920   f , two primary coolant passes  940   a - 940   b , and one secondary coolant pass  960   a  that is divided into three parallel cavities. Three of the refrigerant passes  920   a - 920   f  extend through and exchange heat directly with one of the two primary coolant passes  940   a - 940   b . The first primary coolant pass  940   a  exchanges heat directly with two of the three secondary coolant passes  960   a - 960   b  (e.g., by sharing intermediate walls therewith). The second primary coolant pass  940   b  exchanges heat directly with two of the three secondary coolant passes  960   b - 960   c  (e.g., by sharing two intermediate walls therewith). The first primary coolant pass  940   a  and the second primary coolant pass  940   b  do not exchange heat directly with each other or with ambient air. The secondary coolant pass  960   a  may additionally exchange heat directly with ambient air via a top wall  904   a  and a bottom wall  904   b . Variations of the heat exchangers  600 ,  700 , and  800  may similarly include a refrigerant pass configured to exchange heat directly with a secondary coolant pass. 
     As a result, the heat exchanger  900  may include 17 fluid layers, which include six refrigerant layers (i.e., formed by the six refrigerant passes  920   a - 920   f ), eight primary coolant layers (i.e., formed by the two primary coolant passes  940   a - 940   b  above, below, and between the six refrigerant passes  920   a - 920   f ), and three secondary coolant layers (i.e., formed by the secondary coolant pass  960   a , below, and between the first primary coolant pass  940   a  and the second primary coolant pass  940   b.    
     Referring to  FIG. 10 , a heat exchanger  1000  is a variation of the heat exchanger  600  and the heat exchanger  800 . For brevity, differences between the heat exchangers  600 ,  800  and the heat exchanger  1000  are described below. For further understanding of the heat exchanger  1000 , refer to the discussion of the heat exchangers  600 ,  800  above. The heat exchanger  1000  includes a refrigerant passage  1020  having seven refrigerant passes  1020   a - 1020   g , a primary coolant passage  1040  having two primary coolant passes  1040   a - 1040   b , one secondary coolant pass  1060   a , and an insulating chamber  1080 . Three of the refrigerant passes  1020   a - 1020   f  extend through and exchange heat directly with one of the two primary coolant passes  1040   a - 1040   b . The first primary coolant pass  1040   a  and the second primary coolant pass  1040   b  may exchange heat directly with each other (e.g., by sharing an intermediate wall  1040   m  therewith). The seventh refrigerant pass  1020   g  may exchange heat directly with the secondary coolant pass  1060   a  (e.g., by sharing another intermediate wall  1040   n  therewith). The insulating chamber  1080  has no fluid flow therethrough and insulates the second primary coolant pass  1040   b  from the secondary coolant pass  1060   a , for example, by sharing different intermediate walls  1040   o ,  1040   p  therewith and forming an air gap therebetween. The insulating chamber  1080  may be incorporated into variations of the heat exchangers  600 ,  700 ,  800 , and  900  described above. 
     As a result, the heat exchanger  1000  may include 17 fluid layers, which include seven refrigerant layers (i.e., formed by the seven refrigerant passes  1020   a - 1020   g ), eight primary coolant layers (i.e., formed by the two primary coolant passes  1040   a - 1040   b  above, below, and between the six of the refrigerant passes  1020   a - 1020   f ), one secondary coolant layer (i.e., formed by the secondary coolant pass  1060   a ), and one insulating layer (i.e., formed by the insulating chamber  1080  and having a static fluid, such as air, contained therein). 
     Referring to  FIG. 11 , which is a cross-sectional view taken similar to  FIG. 6E , a heat exchanger  1100  is a variation of the heat exchanger  600 . The heat exchanger includes a passage  1120 , a primary coolant passage  1140 , and a secondary coolant passage  1160 . The passage  1120 , rather than being formed by tubes, is instead formed by cavities  1122   a - f  (e.g., six as shown), which form two passes  1120   a ,  1120   b  for a refrigerant, which may be the high pressure coolant described previously or another refrigerant (e.g., R134a), or another coolant. That is flow through a first set of three of the cavities  1122   a - c  and another set of three of the cavities  1122   d - f  is in parallel, and flow is serial from the first set to the second set. Alternatively, the passage  1120  may be provided with fewer or more cavities  1122   a - f  and fewer or more passes (e.g., the six cavities being connected serially to form six passes). The primary coolant passage  1140  is formed by eight cavities  1142   a - h , which form two passes  1140   a ,  1140   b . The secondary coolant passage  1160  is formed by a single cavity  1162 , which forms a single pass  1160   a . The first pass  1120   a  of the passage  1120  exchanges heat directly with the first pass  1140   a  of the primary coolant passage  1140 , the first cavity  1142   a  of which insulates the first pass  1120   a  of the passage  1120  from ambient air and the fourth cavity  1142   d  of which insulates the first pass  1120   a  of the passage  1120  from the secondary coolant passage  1160 . The second pass  1120   b  of the passage  1120  exchanges heat directly with the second pass  1140   b  of the primary coolant passage  1140 , the last cavity  1142   h  of which insulates the second pass  1120   a  of the passage  1120  from ambient air and the fifth cavity  1142   e  of which insulates the first pass  1120   a  of the passage  1120  from the secondary coolant passage  1160 . The pass  1160   a  of the secondary coolant passage  1160  exchanges heat directly with the first pass  1140   a  and the second pass  1140   b  of the primary coolant passage  1140 . 
     As a result, the heat exchanger  1100  includes 15 fluid layers, which include eight primary coolant layers, one secondary coolant layers, and six layers of the refrigerant or additional coolant. 
     Furthermore, the construction of the heat exchanger  1100  with cavities instead of refrigerant tubes may be applied to the other heat exchangers described previously. Each refrigerant pass would instead be formed by one or more cavities, and each primary coolant layer would be formed by a distinct cavity (i.e., rather than multiple layers being formed by one cavity).

Metadata:
Filing Date: 20170830
Publication Date: 20211228
Grant Date: 20211228
Priority Date: 20160902
Inventors: JOHNSTON, VINCENT G.
Yuhasz, Donald P.
HOEHNE, MARK R.
Assignee: APPLE INC
CPC Classifications: [{"code": "H01M10/663", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/625", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/615", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/27", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/26", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00307", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H1/3227", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00385", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00278", "inventive": true, "first": true, "tree": "[]"}, {"code": "H01M10/613", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00342", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/27", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L2240/545", "inventive": false, "first": false, "tree": "[]"}, {"code": "H01M10/66", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00899", "inventive": true, "first": false, "tree": "[]"}, {"code": "F25B25/005", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00321", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00885", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/26", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00928", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H1/32284", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00307", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H2001/00935", "inventive": false, "first": false, "tree": "[]"}, {"code": "F25B25/005", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00307", "inventive": false, "first": false, "tree": "[]"}, {"code": "Y02E60/10", "inventive": false, "first": false, "tree": "[]"}, {"code": "F25B40/00", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00278", "inventive": true, "first": true, "tree": "[]"}, {"code": "Y02T10/70", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H1/00899", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00885", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/143", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00278", "inventive": true, "first": true, "tree": "[]"}, {"code": "H01M10/66", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/625", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/26", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/625", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L2240/545", "inventive": false, "first": false, "tree": "[]"}, {"code": "F25B40/00", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/32284", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/27", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/143", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00307", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H1/00278", "inventive": true, "first": true, "tree": "[]"}, {"code": "F25B25/005", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/66", "inventive": true, "first": false, "tree": "[]"}, {"code": "F25B40/00", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00321", "inventive": true, "first": false, "tree": "[]"}, {"code": "H01M10/625", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00935", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60L2240/545", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60H1/00899", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/32284", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60L58/27", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H2001/00928", "inventive": false, "first": false, "tree": "[]"}, {"code": "B60L58/26", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/143", "inventive": true, "first": false, "tree": "[]"}, {"code": "B60H1/00885", "inventive": true, "first": false, "tree": "[]"}]
Family ID: 59901574