Cooling system for a work vehicle

A cooling system includes a charge air cooler system that includes a first stage that receives charge air via a charge air flow path and receives coolant fluid via a first coolant fluid flow path. A second stage receives charge air from the first stage via the charge air flow path, outputs the charge air, and receives the coolant fluid via a second coolant fluid flow path. A third stage receives and outputs the charge air from the second stage via the charge air flow path and receives the coolant fluid via a third coolant fluid flow path. The cooling system includes a low temperature radiator system that includes a low temperature radiator that directs the coolant fluid toward the third stage via the third coolant fluid flow path and includes a high temperature radiator system that directs the coolant fluid toward the first stage and second stage.

BACKGROUND

The present disclosure relates generally to a cooling system for a work vehicle.

Certain work vehicles (e.g., tractors, harvesters, skid steers, etc.) may be used to tow or support tools to plow a field, till land, excavate soil, harvest crops, or accomplish other ground-working operations. The operations performed by the work vehicle may cause internal components of the work vehicle to generate heat. Typical work vehicles employ a cooling system to cool certain internal components. Generally, as the power of the work vehicle increases, more cooling is used, but the overall size of the work vehicle may not increase. As a result, there may not be enough room (e.g., inside the work vehicle under the hood) to accommodate typical cooling systems capable of providing suitable cooling for high-power work vehicles.

BRIEF DESCRIPTION

In one embodiment, a cooling system is provided. The cooling system includes a charge air cooler system that includes a first stage that receive charge air at a first temperature via a charge air flow path and receives coolant fluid via a first coolant fluid flow path. In addition, the charge air cooler system includes a second stage that receives the charge air at a second temperature from the first stage of the charge air cooler system via the charge air flow path, outputs the charge air at a third temperature, and receives the coolant fluid via a second coolant fluid flow path. Additionally, the charge air cooler system includes a third stage that receives the charge air at the third temperature from the second stage of the charge air cooler system via the charge air flow path, outputs the charge air at a fourth temperature, receives the coolant fluid via a third coolant fluid flow path, such that the second temperature is lower than the first temperature, the third temperature is lower than the second temperature, and the fourth temperature is lower than the third temperature. Moreover, the cooling system includes a low temperature radiator system that includes a low temperature radiator that directs the coolant fluid toward the third stage of the charge air cooler system via the third coolant fluid flow path, and the cooling system also includes a high temperature radiator system that directs the coolant fluid toward the first stage of the charge air cooler system via the first coolant fluid flow path and toward the second stage of the charge air cooler system via the second coolant fluid flow path.

In another embodiment, a cooling system is provided. The cooling system includes a high temperature radiator system that outputs coolant fluid via a first coolant fluid flow path and a second coolant fluid flow path, and the cooling system includes a water hydraulic oil cooler system that receives hydraulic oil via a hydraulic oil flow path. The water hydraulic oil cooler includes a first stage that receives the coolant fluid via the second coolant fluid flow path and receives the hydraulic oil via the hydraulic oil flow path, and the water hydraulic oil cooler also includes a second stage that receives the coolant fluid via a third coolant fluid flow path, directs the coolant fluid toward the second coolant fluid flow path, and receives the hydraulic oil from the first stage of the water hydraulic oil cooler system via the hydraulic oil flow path. Moreover, the cooling system includes a low temperature radiator system that includes a low temperature radiator that receives the coolant fluid via the third coolant fluid flow path and to directs the coolant fluid toward the second stage of the water hydraulic oil cooler system via the third coolant fluid flow path.

In an additional embodiment, a cooling system is provided. The cooling system includes a charge air cooler system that includes a first stage that receives charge air at a first temperature via a charge air flow path and receive coolant fluid via a first coolant fluid flow path. The charge air cooler system also includes a second stage that receives the charge air at a second temperature from the first stage of the charge air cooler system via the charge air flow path, outputs the charge air at a third temperature, receives the coolant fluid via a second coolant fluid flow path. In addition, the charge air cooler system includes a third stage that receives the charge air at the third temperature from the second stage of the charge air cooler system via the charge air flow path, outputs the charge air at a fourth temperature, and receives the coolant fluid via a third coolant fluid flow path, such that the second temperature is lower than the first temperature, the third temperature is lower than the second temperature, and the fourth temperature is lower than the third temperature. Moreover, the cooling system includes a low temperature radiator system that includes a low temperature radiator that directs the coolant fluid toward the third stage of the charge air cooler system via the third coolant fluid flow path, and the cooling system also includes a high temperature radiator system that direct the coolant fluid toward the first stage of the charge air cooler system via the first coolant fluid flow path and toward the second stage of the charge air cooler system via the second coolant fluid flow path. The cooling system also includes a water hydraulic oil cooler system that includes a first stage and a second stage, such that the first stage of the water hydraulic oil cooler system is receives hydraulic oil via a hydraulic oil flow path and directs the hydraulic oil toward the second stage of the water hydraulic oil cooler system via the hydraulic oil flow path.

DETAILED DESCRIPTION

Turning to the drawings,FIG. 1is a perspective view of an embodiment of a work vehicle10that may include a cooling system. In the illustrated embodiment, the work vehicle10is a tractor. However, it should be appreciated that the cooling system disclosed herein may be utilized on other work vehicles, such as but not limited to buses, cars, on-road trucks, skid steers, harvesters, and construction equipment. In the illustrated embodiment, the work vehicle10includes a cab12and a chassis14. In certain embodiments, the chassis14may house a motor (e.g., diesel engine, etc.), a hydraulic system (e.g., including a pump, valves, reservoir, etc.), and other components (e.g., an electrical system, a suspension system, etc.) that facilitate operation of the work vehicle. In addition, the chassis14may support the cooling system described herein. In some embodiments, the work vehicle10includes a hood15configured to be lifted or pivotally rotated to facilitate access to the cooling system and/or other components of the work vehicle10.

In addition, the chassis14supports the cab12and wheels16. The wheels16may rotate in a circumferential direction to cause the forward linear movement of the work vehicle10along a direction of travel22. In the illustrated embodiment, a coordinate system includes a longitudinal axis24(e.g., parallel to the direction of travel22), a lateral axis26, and a vertical axis28. While the illustrated work vehicle10includes wheels16, in alternative embodiments, the work vehicle may include tracks or a combination of wheels and tracks that cause the work vehicle to advance along the direction of travel22.

The cab12may house an operator of the work vehicle10. Accordingly, various controls, such as the illustrated hand controller30, are positioned within the cab12to facilitate operator control of the work vehicle10. For example, the controls may enable the operator to control rotational speed of the wheels16, thereby facilitating adjustment of the speed and/or the direction of the work vehicle10. In the illustrated embodiment, the cab12also includes a door32to facilitate ingress and egress of the operator from the cab12.

FIG. 2is a perspective view of an embodiment of a radiator assembly40of a cooling system that may be employed within the work vehicle10ofFIG. 1. In the illustrated embodiment, the cooling system includes two radiator systems. As illustrated, the cooling system includes a low temperature radiator system42and a high temperature radiator system44. The cooling system also includes a fan46(e.g., a solid fan, a clutch fan, a flex fan, an electric fan, etc.) configured to drive air48(e.g., external airflow) through the low temperature radiator system42and the high temperature radiator system44. Furthermore, the fan46may be configured to operate at any suitable speed (e.g., about 2180 revolutions per minute (RPM), etc.). Although in the illustrated embodiment the cooling system includes one fan46and two radiator systems, it should be noted that in alternative embodiments, the cooling system may include any other suitable number of fans and/or radiator systems. In some embodiments, the fan46may be omitted.

Furthermore, the radiator assembly40may have any suitable dimensions that enable the cooling system to be supported by the chassis of the work vehicle. For example, the cooling system may have any suitable length (e.g., extended along the longitudinal axis24), any suitable width (e.g., extended along the lateral axis26), and any suitable height (e.g., extended along the vertical axis28). In addition, the cooling system has dimensions that enable the cooling system to be housed inside the work vehicle. For example, the cooling system may be positioned at the front of the work vehicle and housed inside the hood. It should be noted that the dimensions of the cooling system may be modified to be incorporated into other vehicles of varying sizes. For example, a smaller fan (e.g., operated at a higher speed) may be substituted for the illustrated fan46to facilitate incorporating the cooling system into a vehicle. The cooling system described herein provides more efficient cooling to the various components of the work vehicle, as compared to previous cooling systems, thereby enabling the cooling system to effectively cool higher power engines while being able to fit inside the work vehicle (e.g., under the hood). That is, the cooling system is configured to fit inside (e.g., the space constraints under the hood of) previous/current work vehicles, while providing suitable cooling to component that utilize more cooling capacity (e.g., due to higher power requirements).

In the illustrated embodiment, the low temperature radiator system42is positioned forward of the high temperature radiator system44and the fan46along the longitudinal axis24. Accordingly, the high temperature radiator system44is positioned between the fan46and the low temperature radiator system42along the longitudinal axis24, such that the low temperature radiator system42is positioned forward of the high temperature radiator system44relative to the direction of travel22, and the fan is positioned rearward of the high temperature radiator system44relative the direction of travel22. The fan46is configured to direct the flow of air48along the longitudinal axis24, such that the air48flows through the high temperature radiator system44after the air48flows through the low temperature radiator system42. As such, the low temperature radiator system42may receive the cooler air (e.g., to enable the coolant to be cooled to a lower temperature). It should be noted that in additional embodiments, the fan and the two radiator systems may be arranged in another suitable order along the longitudinal axis. For example, the low temperature radiator system may be positioned behind the fan or the high temperature radiator system relative to the direction of travel. In further embodiments, the low temperature radiator system, the high temperature radiator system, and the fan may be oriented in another suitable direction. For example, the low temperature radiator system, the high temperature radiator system, and the fan may each be oriented substantially along the lateral axis, the vertical axis, or any other suitable direction.

The two radiator systems42,44are configured to circulate coolant fluid used to cool various components of the work vehicle as discussed in detail below. For example, the coolant fluid may include only water, a mixture of about 50 percent water and about 50 percent ethylene glycol, only ethylene glycol, or any other suitable coolant fluid. In some embodiments, the coolant fluid may flow into the high temperature radiator system44via a first opening50. In addition, the coolant fluid may flow out of the low temperature radiator system42via a second opening52. In further embodiments, the coolant fluid may enter the low temperature radiator system42via the second opening, and the coolant fluid may exit the high temperature radiator system44via the first opening50.

FIG. 3is a block diagram of an embodiment of a cooling system60that may be employed within the work vehicle ofFIG. 1. To facilitate discussion, the embodiments discussed herein include specific values for dimensions, heat dissipation, inlet temperature, outlet temperature, and the like, but it should be appreciated that these specific values are meant to be exemplary and in no way limiting. Furthermore, the embodiments discussed herein include a discussion of various coolant fluid flow path (e.g., fluid connections). The coolant fluid flow paths (e.g., fluid connections) may include multiple segments fluidly coupling two components of the cooling system. Furthermore, the segments are each configured to direct coolant fluid. In some embodiments, the segments are configured to direct coolant fluid with no intervening components between the illustrated components. For example, each illustrated segment of each illustrated coolant fluid flow path may include a first end and a second end configured to form a direct fluid connection (e.g., via an annular conduit) between two components. However, in alternative embodiments, intervening components may be present between the two illustrated components.

In the illustrated embodiment, the cooling system60includes the high temperature radiator system44, which includes three separate heat exchangers (e.g., radiators). In the illustrated embodiment, the high temperature radiator system44includes an engine radiator62, a charge air cooler high temperature radiator (CAC HT radiator)64, and a hydraulic oil cooler high temperature radiator (HOC HT radiator)66. However, in other embodiments, the high temperature radiator system44may include any suitable number of heat exchangers, such as one, two, four, six, etc.

In some embodiments, the engine radiator62is configured to dissipate about 149 kilowatts (kW) of heat (e.g., to the environment). However, it should be appreciated that in further embodiments, the engine radiator may be configured to dissipate any suitable amount of heat (e.g., between 100 kW and 200 kW). In some embodiments, the engine radiator62may have dimensions (e.g., width and height) of about 532 millimeters (mm) by about 825 mm, but it should be appreciated that in further embodiments, the engine radiator may be sized to have any suitable dimensions. In addition, the engine radiator outputs coolant fluid at a target temperature, such as about 93 degrees Celsius (° C.), and receives coolant fluid via an engine radiator coolant fluid flow path70at another temperature from an associated engine72(e.g., about 101° C.).

In the illustrated embodiment, the engine radiator coolant fluid flow path70is a single closed-loop coolant fluid flow path, such that the coolant fluid output from the engine radiator62is provided to the engine72, and the coolant fluid output by the engine72is provided to the engine radiator62. The flow of the coolant fluid via the engine radiator coolant fluid flow path70may be driven by an engine pump74configured to drive the flow of the coolant fluid at a volumetric flow rate of about 300 liters per minute (LMP), for example. In some embodiments, while the coolant fluid is flowing through the engine radiator coolant fluid flow path70, the temperature of the air leaving the engine radiator62may be between 40° C. and 60° C. (e.g., about 49° C.).

With regard to the discussion above of segments of the flow paths, in the illustrated embodiment, the engine radiator coolant fluid flow path70includes two segments. In particular, in the illustrated embodiment, a first segment is included between the outlet of the engine radiator62and the inlet of the engine72, and a second segment is included between the outlet of the engine72and the inlet of the engine radiator62. As mentioned above, each illustrated segment of each illustrated flow path may include a first end and a second end configured to form a direct fluid connection (e.g., via an annular conduit) between two components. However, in alternative embodiments, intervening components may be present between the two illustrated components. For example, in alternative embodiments, an intervening component may be present between the outlet of the engine72and the inlet of the engine radiator62along the second segment.

In some embodiments, the engine72may be any suitable engine for converting fuel into mechanical energy to drive the motion of the work vehicle (e.g., and/or perform other operations). For example, the engine72may be an internal combustion engine, such as a spark ignition engine (e.g., gasoline engine, etc.) or a compression ignition engine (e.g., a diesel engine, a partially premixed combustion (PPC) engine, a homogeneous charge compression ignition (HCCI) engine, etc.). Furthermore, the engine pump74may be any suitable pump for delivering coolant fluid at a target flow rate (e.g., about 300 LPM). In some embodiments, the engine pump74may be electrically driven or driven directly by the engine72. For example, the engine pump74may be a centrifugal pump, an axial pump, a mixed-flow pump, a positive displacement pump, or the like.

Turning to the CAC HT radiator64, in some embodiments, the CAC HT radiator64is configured to dissipate about 52 kW of heat (e.g., to the environment). However, it should be appreciated that in further embodiments, the CAC HT radiator may be configured to dissipate any suitable amount of heat (e.g., between 25 kW and 100 kW). In some embodiments, the CAC HT radiator64may have dimensions (e.g., width and height) of about 120 mm by about 825 mm, but it should be appreciated that in further embodiments, the CAC HT radiator may have any suitable dimensions. Furthermore, in the illustrated embodiment, the CAC HT radiator64is configured to output coolant fluid toward a first stage water charge air cooler (WCAC)78of a charge air cooler system79via a CAC HT coolant fluid flow path80(e.g., first coolant fluid flow path). The coolant fluid that exits the CAC HT radiator64via the CAC HT coolant fluid flow path80is at a lower temperature than the temperature of the coolant entering the CAC HT radiator64(e.g., because the CAC HT64radiator facilitates heat transfer from the coolant fluid to the environment). For example, the temperature of the coolant fluid output by the CAC HT radiator64may be about 107° C., and the temperature of the coolant fluid input to the CAC HT radiator64may be about 112° C.

In the illustrated embodiment, the CAC HT coolant fluid flow path80is a single closed-loop coolant fluid flow path, such that the coolant fluid output from the CAC HT radiator64flows to the first stage WCAC78, and the coolant fluid output from the first stage WCAC78flows to the CAC HT radiator64. The flow of the coolant fluid via the CAC HT coolant fluid flow path80may be driven by a CAC pump82configured to drive the flow of the coolant fluid in the CAC HT coolant fluid flow path80at a volumetric flow rate of about 160 LPM. In some embodiments, while the coolant fluid is flowing to the first stage WCAC78, the temperature of the charge air84output from the first stage WCAC78may be about 108° C.

In the certain embodiments, the charge air84entering the first stage WCAC78via a charge air flow path85may have a mass flow rate of about 1415 kilograms per hour (kg/h) and a temperature of about 234° C. In some embodiments, the charge air84may be received from a turbocharger of the work vehicle. It should be understood that the temperature and mass flow rate of the charge air84depends on the type of turbocharger, the type of engine, and boost pressure, among other factors. In some embodiments, the first stage WCAC78may dissipate about 52 kW of heat. For example, the coolant fluid flowing through the first stage WCAC may facilitate the heat dissipation of about 52 kW, however it should be understood that the first stage WCAC may dissipate any suitable amount of heat (e.g., between 25 kW and 100 kW). In some embodiments, after the first stage WCAC78dissipates about 52 kW of heat, the charge air84may exit the first stage WCAC78via the charge air flow path85at a lower temperature than when it entered the first stage WCAC78. For example, the charge air84may be output from the first stage WCAC at about 108° C.

In the illustrated embodiment, the charge air84then flows from the first stage WCAC78into a second stage WCAC86of the charge air cooler system79via the charge air flow path85for additional cooling. The second stage WCAC86may dissipate about 10 kW of heat, as described in detail below, such that the charge air84output by the second stage WCAC86is lower in temperature than when it entered the second stage WCAC86. After flowing through the second stage WCAC86, the charge air84flows into a third stage WCAC87. The third stage WCAC87may dissipate about 7 kW of heat, as described in detail below, such that the charge air84output by the third stage WCAC87is lower in temperature than when it entered the third stage WCAC87. In the illustrated embodiment, the charge air84expelled from the third stage WCAC87may have a temperature of about 67° C., but it should be appreciated that in additional embodiments, the charge air may be expelled from the third stage WCAC87at any suitable temperature below about 70° C., for example, such as 69.5° C., 68° C., 65° C., and the like. In some embodiments, the second stage WCAC86and the third stage WCAC87may be combined into a single unit.

Turning to the HOC HT radiator66, in some embodiments, the HOC HT radiator66is configured to dissipate about 21 kW of heat (e.g., to the environment). However, it should be appreciated that in further embodiments, the HOC HT radiator may be configured to dissipate any suitable amount of heat (e.g., between 15 kW and 40 kW). In some embodiments, the HOC HT radiator66may have dimensions (e.g., width and height) of about 80 mm by about 825 mm, but it should be appreciated that in further embodiments, the HOC HT radiator may have any suitable dimensions. Furthermore, in some embodiments, the HOC HT radiator66is configured to output coolant fluid toward the low temperature radiator system42via the HOC HT coolant fluid flow path90. In some embodiments, the coolant fluid output by the HOC HT radiator66has a lower temperature than the coolant fluid input into the HOC HT radiator66. For example, the coolant fluid expelled by the HOC HT66radiator may be at a temperature of about 76° C., while the coolant fluid entering the HOC HT radiator66may be at a temperature of about 83° C. However, it should be appreciated that in alternative embodiments, the temperatures of the coolant fluid at the inlet and outlet of the HOC HT radiator may be any suitable temperatures. In the illustrated embodiment, the flow of the coolant fluid via the HOC HT coolant fluid flow path90(e.g., the fourth coolant fluid flow path) is driven by the HOC pump92, which may include any suitable pump configured to drive the flow of the coolant fluid into the low temperature radiator system42at a target volumetric flow rate. In particular, the HOC pump92may pump the coolant fluid into the low temperature radiator system42at a volumetric flow rate of about 160 LMP and at a temperature of about 73° C.

In the illustrated embodiment, the low temperature radiator system42includes a low temperature (LT) radiator94and an ultra-low temperature (ULT) radiator96. In some embodiments, the low temperature radiator94is configured to dissipate about 46 kW of heat (e.g., to the environment). However, it should be appreciated that in further embodiments, the low temperature radiator may be configured to dissipate any suitable amount of heat (e.g., between 30 kW and 60 kW). In some embodiments, the low temperature radiator94may have dimensions (e.g., width and height) of about 800 mm by about 406 mm, but it should be appreciated that in further embodiments, the low temperature radiator have any suitable dimensions. In addition, the low temperature radiator94is configured to output coolant fluid at a target temperature, such as about 66° C.

In the illustrated embodiment, the coolant fluid may be pumped by the HOC pump92into two coolant fluid flow paths. Specifically, the coolant fluid may flow from the HOC HT coolant fluid flow path90into a low temperature radiator coolant fluid flow path100(e.g., third coolant fluid flow path) and a water hydraulic oil cooler (WHOC) coolant fluid flow path102(e.g., second coolant fluid coolant fluid flow path). In the illustrated embodiment, the coolant fluid flowing through the HOC HT coolant fluid flow path90flows at a volumetric flow rate and temperature of about 160LPM and about 73° C., respectively, before splitting into the low temperature radiator coolant fluid flow path100and the WHOC coolant fluid flow path102. Indeed, the low temperature radiator coolant fluid flow path100may receive the coolant fluid at a volumetric flow rate and a temperature of about 110LMP and about 73° C., respectively. In addition, the WHOC coolant fluid flow path102may receive the coolant fluid at a volumetric flow rate and a temperature of about 110LMP and about 73° C., respectively.

The low temperature radiator coolant fluid flow path100may direct the coolant fluid into the low temperature radiator94and the ultra-low temperature radiator96, whereby the coolant fluid is then directed toward an ultra-low temperature radiator coolant fluid flow path104(e.g., fourth coolant fluid flow path), which directs the coolant fluid into the ultra-low temperature radiator96at a target volumetric flow rate and temperature (e.g., about 15LPM and about 59° C., respectively). In addition, after the low temperature radiator coolant fluid flow path100directs the coolant fluid into the low temperature radiator94, the coolant fluid is directed toward a WCAC coolant fluid flow path103(e.g., third coolant fluid flow path), which directs the coolant fluid into the third stage WCAC87at another target volumetric flow rate and temperature (e.g., about 95LPM and about 66° C., respectively). The WHOC coolant fluid flow path102may direct the flow of the coolant fluid into a WHOC system110at a target volumetric flow rate (e.g., about 50LPM), as discussed in detail below. Accordingly, in the illustrated embodiment, the fluid flowing along the HOC HT coolant fluid flow path90at about 160LPM, for example, may split and flow to the low temperature radiator coolant fluid flow path100and to the WHOC coolant fluid flow path102(e.g., via a three-way valve, a T-junction, etc.). The coolant fluid flowing through the low temperature radiator flow path100may then split into the WCAC coolant fluid flow path103and the ultra-low radiator coolant fluid flow path104.

The coolant fluid may flow through the low temperature radiator coolant fluid flow path100, the WHOC coolant fluid flow path102, the WCAC coolant fluid flow path103, and the ultra-low temperature radiator coolant fluid flow path104at any suitable respective volumetric flow rates. For example, the coolant fluid may flow through the low temperature radiator coolant fluid flow path100at about 110LPM, the coolant fluid may flow through the WHOC coolant fluid flow path102at about 50LPM, the coolant fluid may flow through the WCAC coolant fluid flow path103at about 95LPM, and the coolant fluid may flow through the ultra-low temperature radiator coolant fluid flow path104at about 15LPM.

With regard to the coolant fluid directed to the ultra-low temperature radiator coolant fluid flow path104, the coolant fluid is directed to the ultra-low temperature radiator96(e.g., at about 15 LPM) after flowing through the low temperature radiator94. In some embodiments, the low temperature radiator coolant fluid flow path100may fluidly couple the low temperature radiator94and the ultra-low temperature radiator96, such that the coolant fluid may flow from the low temperature radiator94toward the ultra-low temperature radiator96before flowing toward the ultra-low temperature radiator coolant fluid flow path104. In some embodiments, the ultra-low temperature radiator96is configured to dissipate about 7 kW of heat (e.g., to the environment). However, it should be appreciated that in further embodiments, the ultra-low temperature radiator may be configured to dissipate any suitable amount of heat (e.g., between 2 kW and 15 kW). In some embodiments, the ultra-low temperature radiator96has dimensions (e.g., width and height) of about 101 mm by about 800 mm, but it should be appreciated that in further embodiments, the ultra-low temperature radiator may have any suitable dimensions. In addition, in the illustrated embodiment, the ultra-low temperature radiator96outputs coolant fluid at a target temperature, such as about 59° C. While in the illustrated embodiment the WCAC coolant fluid flow path103and the ultra-low temperature radiator coolant fluid flow path104split from the low temperature radiator coolant fluid flow path100, in further embodiments, the WCAC coolant fluid flow path and the ultra-low temperature radiator coolant fluid flow path may be connected to different outlets of the radiator to receive coolant fluid at different temperatures, different volumetric flow rates, or any combination thereof.

In some embodiments, the coolant fluid output by the ultra-low temperature radiator96may be directed via the ultra-low temperature radiator flow path104toward other components associated with the work vehicle10. For example, in the illustrated embodiment, the coolant fluid output by the ultra-low temperature radiator96is directed toward a condenser106and then toward a fuel cooler108before flowing into the HOC HT coolant fluid flow path90(e.g., to be directed into the low temperature radiator94by the HOC pump92and to the WHOC systems). The coolant fluid flowing through the ultra-low temperature radiator coolant fluid flow path104is used to cool the condenser106and the fuel cooler108, such that the temperature of the coolant is higher (e.g., about 70° C.) after flowing through the condenser106and the fuel cooler108than the temperature (e.g., 59° C.) of the coolant fluid before flowing into the condenser106and the fuel cooler108. In the illustrated embodiment, the condenser106and the fuel cooler108dissipate about 9 kW and about 1.5 kW of heat, respectively. The condenser may be any suitable device used to condense a substance from a gaseous state to a liquid state (e.g., by cooling it), and the fuel cooler may be any suitable device used to decrease the temperature of fuel flowing through the work vehicle (e.g., to the engine72). Furthermore, in some embodiments, the condenser106may be part of the heating, ventilation, and air conditioning (HVAC) system of the work vehicle. Furthermore, in certain embodiments, the condenser106and/or the fuel cooler108may be omitted, and/or another component may be fluidly coupled to the ultra-low temperature radiator coolant fluid flow path104to receive the coolant fluid.

With regard to the coolant fluid directed to the WHOC coolant fluid flow path102, the coolant fluid is received from the HOC HT coolant fluid flow path90at a target temperature and volumetric flow rate (e.g., about 73° C. and about 50LPM, respectively), and the coolant fluid is directed toward the WHOC system110. In the illustrated embodiment, the coolant fluid flowing through the WHOC coolant fluid flow path102is directed toward a first stage WHOC111of the WHOC system110. In some embodiments, the first stage WHOC111dissipates about 23 kW of heat. However, the first stage WHOC may dissipate any other suitable amount of heat (e.g., between 15 kW and 30 kW) based on the properties of the first stage WHOC (e.g., the number of fins, the size of the fins, the number of coolant fluid flow path passes, the material, etc.). After the coolant fluid flows through the first stage WHOC111, the coolant fluid is directed toward the second stage WCAC86at a target temperature and a target volumetric flow rate via the WHOC coolant fluid flow path102. For example, the coolant fluid expelled from the first stage WHOC111may have a temperature of about 81° C. and a volumetric flow rate of about 50LPM. As mentioned above, the second stage WCAC86may be configured to dissipate any suitable amount of heat (e.g., 10 kW). After the coolant fluid flow through the second stage WCAC86, the coolant fluid flows through the second state WCAC86, the coolant fluid is directed toward the HOC HT radiator66, and the coolant fluid is then directed toward the HOC HT coolant fluid flow path90.

As mentioned above, the coolant fluid expelled from the low temperature Radiator94splits into the WCAC coolant fluid flow path103and the ultra-low temperature radiator coolant fluid flow path104. With regard to the coolant fluid directed to the WCAC coolant fluid flow path103, the coolant fluid flows toward the third stage WCAC87at a target volumetric flow rate and temperature. For example, the coolant fluid may be directed toward the third stage WCAC87through the WCAC coolant fluid flow path103at about 95LPM and about 66° C. The coolant fluid may cool the charge air84flowing through the third stage WCAC87to a temperature below 70° C., thereby dissipating about 7 kW of heat. After the coolant fluid passes through the third stage WCAC87, the coolant fluid is directed along the WCAC coolant fluid flow path103at a higher temperature (e.g., about 68° C.) than the temperature (e.g., about 66° C.) of the coolant before entering the third stage WCAC87.

Furthermore, in the illustrated embodiment, the coolant fluid is directed from the third stage WCAC87toward a second stage WHOC114of the WHOC system110via the WCAC coolant fluid flow path103. The second stage WHOC114may receive coolant fluid at a lower temperature (e.g., 68° C.) than the temperature (e.g., 72° C.) at which the coolant fluid is output by the second stage WHOC114. In some embodiments, the second stage WHOC114may be configured to dissipate a suitable amount of heat, such as about 25 kW (e.g., to cool hydraulic oil112to a suitable temperature). The coolant fluid from the second stage WHOC114may be directed through the WCAC coolant fluid flow path103toward the HOC HT coolant fluid flow path90. Accordingly, in some embodiments, coolant fluid from the WCAC coolant fluid flow path103and from the ultra-low temperature radiator coolant fluid flow path104may flow into the HOC HT coolant fluid flow path90.

In the illustrated embodiment, the hydraulic oil112(e.g., hydraulic fluid) is directed into the first stage WHOC111of the WHOC system110via a hydraulic oil flow path115. The hydraulic oil112is then directed from the first stage WHOC111into the second stage WHOC114of the WHOC system110via the hydraulic oil flow path115. Indeed, the hydraulic oil112is directed through the two stages of the WHOC system110via the hydraulic oil flow path115, whereby the hydraulic oil112is cooled by each stage WHOC. For example, the first stage WHOC111and the second stage WHOC114may be configured to dissipate about 23 kW and about 25 kW of heat, respectively, to facilitate cooling the hydraulic oil112. However, it should be appreciated that the WHOC system110may include any suitable number of stages (e.g., one stage, two stages, three stages, four stages, etc.) to cool the hydraulic oil112. In the illustrated embodiment, the first stage WHOC111is cooled by coolant fluid directed along the WHOC coolant fluid flow path102, and the second stage WHOC114is cooled by coolant fluid received from the third stage WCAC87along the WCAC coolant fluid flow path103. The hydraulic oil112may enter the first stage WHOC111at a volumetric flow rate of about 92 LPM and a temperature of about 90° C., but it should be appreciated that the hydraulic oil112may enter the first stage WHOC111at any other suitable volumetric flow rate and temperature. In addition, the second stage WHOC110receives the hydraulic oil112from the first stage WHOC111before outputting the hydraulic oil112(e.g., toward the hydraulic system of the work vehicle). In some embodiments, the second stage WHOC114may output the hydraulic oil112at a temperature lower than the temperature at which the hydraulic oil112enters the first stage WHOC111. For example, the first stage WHOC111may receive the hydraulic oil112at a temperature of about 90° C., and the second stage WHOC114may output the hydraulic oil112at a target temperature, such as about 73° C., 75° C., or any suitable temperature (e.g., below 80° C.).

In the illustrated embodiment, the first stage WHOC111directs the coolant fluid via the WHOC coolant fluid flow path102toward the second stage WCAC86and then toward the HOC HT radiator66. The temperature of the coolant fluid output by the first stage WHOC111may be at a higher temperature (e.g., about 81° C.) than the temperature of the coolant fluid received by the first stage WHOC111(e.g., about 73° C.). The coolant fluid flowing through the WHOC coolant fluid flow path102is directed toward the HOC HT radiator66, such that the HOC HT radiator66cools the coolant fluid. Furthermore, coolant fluid then flows from the HOC HT radiator66toward the low temperature radiator system42via the HOC HT coolant fluid flow path90, which also receives coolant fluid from (e.g., the condenser106and the fuel cooler108via) the ultra-low temperature radiator coolant fluid flow path104and from (e.g., the second stage WHOC114via) the WHOC coolant fluid flow path103.

Accordingly, the cooling system60includes a high temperature radiator system44that is configured to output coolant to the engine72, the first stage WCAC78, and the low temperature radiator system42via three different heat exchangers (e.g., the engine radiator62, the CAC HT radiator64, and the HOC HT radiator66) of the high temperature radiator system44. In some embodiments, the coolant fluid directed toward the low temperature radiator system42from the high temperature radiator system44splits into a coolant fluid flow path directed toward the low temperature radiator96(e.g., via the low temperature radiator coolant fluid flow path100) and another coolant fluid flow path directed toward the first stage WHOC111(e.g., via the WHOC coolant fluid flow path102). As such, in some embodiments, the high temperature radiator system44may cool (e.g., with output coolant fluid) the engine72, the charge air84, and the coolant fluid provided to the low temperature radiator system42and the first stage WHOC111. In some embodiments, the high temperature radiator system44may also cool the second stage WCAC86. It should be appreciated that the high temperature radiator system may include any other suitable number of heat exchangers (e.g., one, two, four, etc.). In addition, the cooling system60includes a low temperature radiator system42that is configured to output coolant fluid toward the third stage WCAC87along the WCAC coolant fluid flow path103. In some embodiments, the low temperature radiator system42may be configured to expel coolant fluid toward the second stage WCAC86. Furthermore, the low temperature radiator system42is configured to output coolant fluid toward the condenser106and the fuel cooler108(e.g., via the ultra-low temperature coolant fluid flow path104). As such, in some embodiments, the low temperature radiator system42may cool (e.g., with output coolant fluid) the condenser106and the fuel cooler108via the ultra-low temperature radiator coolant fluid flow path104. In addition, the low temperature radiator system42may cool the charge air84and the hydraulic oil112via the WHOC coolant fluid flow path103.

FIG. 4is a block diagram of another embodiment of a cooling system118that may employed within the work vehicle ofFIG. 1. As illustrated, the cooling system118has a similar configuration to that of the cooling system60disclosed above with reference toFIG. 3. Indeed, the cooling system118includes the high temperature radiator system44, the low temperature radiator system42, the WHOC system110, and the WCAC system79. In the illustrated embodiment, the cooling system118includes a two-stage WCAC120(e.g., as compared to the three-stage WHOC disclosed above with reference toFIG. 3).

In the illustrated embodiment, the two-stage WCAC120includes the first stage WCAC78configured to dissipate about 52 kW of heat and a second stage WCAC122configured to dissipate about 16 kW of heat. The second stage WCAC122of the cooling system118ofFIG. 4may be larger and/or dissipate more heat than each of the second stage WCAC and the third stage WCAC of the cooling system60ofFIG. 3. The two-stage WCAC120may receive charge air84via the charge air flow path85and output the charge air84at a lower temperature. In particular, in the illustrated embodiment, the charge air84enters the first stage WCAC78of the two-stage WCAC120via the charge air flow path85with a mass flow rate of about 1415 kilograms per hour (kg/h) and a temperature of about 234° C. However, it should be understood that the temperature and mass flow rate of the charge air entering the two-stage WCAC120depends on the type of turbocharger, the type of engine, and boost pressure, among other factors. In some embodiments, the first stage WCAC78may dissipate about 52 kW of heat. For example, the coolant fluid flowing through the first stage WCAC78may facilitate the heat dissipation of about 52 kW, thereby cooling the charge air84. However, it should be understood that the first stage WCAC78may dissipate any suitable amount of heat (e.g., between 25 kW and 100 kW). In some embodiments, after the first stage WCAC78dissipates about 52 kW of heat, the charge air84may exit the first stage WCAC78via the charge air flow path85at a lower temperature than when it entered the first stage WCAC78. For example, the charge air84may be output from the first stage WCAC at about 108° C.

In the illustrated embodiment, the charge air84then flows from the first stage WCAC78into the second stage WCAC122of the two-stage charge air cooler system120via the charge air flow path85for additional cooling. The second stage WCAC122may dissipate about 16 kW of heat, such that the charge air84output by the second stage WCAC122is lower in temperature than when it entered the second stage WCAC122. After flowing through the second stage WCAC122, the charge air84is expelled from the second stage WCAC122. The temperature of the charge air84output by the second stage WCAC122may be lower than the temperature of the charge air84entering the second stage WCAC122. For example, the charge air84expelled from the second stage WCAC122may have a temperature of about 67° C. However, it should be appreciated that in additional embodiments, the charge air may be expelled from the second stage WCAC122at any suitable temperature below about 70° C., for example, such as 69.5° C., 68° C., 65° C., and the like. In the illustrated embodiment, the cooling system118includes a two-stage WCAC system120(e.g., the first stage WCAC78and the second stage WCAC122. However, it should be appreciated that in further embodiments the cooling system may include a WCAC system with any suitable number of stages (e.g., one stage, two stages, three stages, four stages, etc.) to cool the charge air.

As mentioned above, in the illustrated embodiment, the CAC HT radiator64is configured to output coolant toward the first stage WCAC78of the two-stage WCAC system120via the CAC HT coolant fluid flow path80to cool the charge air84. In the illustrated embodiment, the charge air84is cooled by the second stage WCAC122with the coolant fluid received from the low temperature radiator94via the WCAC coolant fluid flow path103and with coolant fluid received from the HOC HT radiator66via the HOC HT coolant fluid flow path90and the WHOC coolant fluid flow path102. As such, in some embodiments, the coolant fluid may be directed into the second stage WCAC122via the WHOC coolant fluid flow path102and the WCAC coolant fluid flow path103. Indeed, the coolant fluid flowing through the WHOC coolant fluid flow path102may be directed toward the first stage WHOC111before flowing into the second stage WCAC122at a volumetric flow rate of about 50LPM and a temperature of about 81° C.

In some embodiments, the coolant fluid enters the second stage WCAC122via the WCAC coolant fluid flow path103at a volumetric flow rate of about 95LPM and a temperature of about 66° C. and is output by the second stage WCAC122at a volumetric flow rate of about 95LPM and a temperature of about 68° C. via the WCAC coolant fluid flow path103. As such, the coolant fluid may be output by the second stage WCAC122via the WCAC coolant fluid flow path103at a higher temperature than when it entered the second stage WCAC122. In the illustrated embodiment, the coolant fluid is output from the second stage WCAC122toward the second stage WHOC114. The coolant fluid then flows into the HOC HT coolant fluid flow path90via the WCAC coolant fluid flow path103. The WHOC coolant fluid flow path102and the WCAC coolant fluid flow path103both flow into and out of the second stage WCAC122. Accordingly, in some embodiments, the coolant fluid flowing through the second stage WCAC122may be restricted to flowing along respective coolant fluid flow paths (e.g., the WHOC coolant fluid flow path102and the WCAC coolant fluid flow path103), such that the coolant fluid flowing through the WHOC coolant fluid flow path102does not come in contact (e.g., mix) with the coolant fluid flowing through the WCAC coolant fluid flow path103. In some embodiments, the coolant fluid may be output from the second stage WCAC122via the WHOC coolant fluid flow path102at a volumetric flow rate of about 50LPM and a temperature of about 83° C., while the coolant fluid may be output from the second stage WCAC122along the WCAC coolant fluid flow path103at a volumetric flow rate of about 95LPM and a temperature of about 68° C. In particular, the WHOC coolant fluid flow path102may fluidly couple the second stage WCAC122to the HOC HT radiator66, such that coolant fluid flows from the second stage WCAC122toward the HOC HT radiator66. Furthermore, in some embodiments, the heat dissipated by the second stage WCAC122of the cooling system118ofFIG. 4may dissipate the same amount of heat as the second stage WCAC86and the third stage WCAC87of the cooling system60ofFIG. 3.