Multiport fluid pump with reserve capacity impeller

Abstract

An apparatus and method for distributing coolant through a first coolant loop and a second coolant loop includes a pump having a first outlet port connected to the first coolant loop and a second outlet port connected to the second coolant loop, and a valve positioned on the pump housing switchable to direct coolant to either the first outlet port or the second outlet port individually, or to the first outlet port and the second outlet port simultaneously. The coolant is pumped by the pump at an unrestricted flow rate and circulated through the first coolant loop at a flow rate less than the unrestricted flow rate when the valve connects the first outlet port to the first coolant loop, and circulated through the second coolant loop at a flow rate less than the unrestricted flow rate when the valve connects the second outlet port to the second coolant loop. Coolant is circulated through the first and second coolant loops at a flow rate less than the unrestricted flow rate when the valve simultaneously connects the first and second outlet ports to the first and second coolant loops, and the combined flow rates through the first and second coolant loops are equal to the unrestricted flow rate.

Description

[Technical Field]

[0001]

[0001] The present disclosure relates generally to multi-port fluid pumps for switching flow to heat-generating or heat-absorbing components, and more particularly to multi-port fluid pumps with integrated valves having reserve capacity impellers. [Background technology]

[0002] Pumps are known and commonly used to move fluids, such as coolants, in vehicles. One example is a cooling system involving a water pump, used to cool different electrical or mechanical components of a vehicle. In hybrid or purely electric vehicles, electrical components require cooling. Valves are used to ensure the distribution of coolant throughout the cooling system. Each valve requires an actuator with electrical control and a retainer on the vehicle component, leading to high component costs. Some vehicles may employ two or more cooling loops to cool heat-generating components and moderate the temperature of the cab. In pumps with multiple output ports connecting a single pump to one or more cooling loops, valves may be used to switch and direct fluid flow between one or more cooling loops. A rotating impeller driven by an electric motor or other mechanical means is used by the pump to move coolant from the pump through one or more cooling loops. The pump's impeller, housing, and outlet ports are designed to provide fluid flow rate based on impeller rotation with maximum efficiency and minimal flow restriction. It would be desirable to provide an impeller with reserve capacity that provides the same fluid flow rate through two or more cooling loops as for a single cooling loop. Summary of the Invention

[0003] The present disclosure relates to an apparatus for distributing coolant through a first coolant loop and a second coolant loop, the apparatus comprising a pump having a housing including an inlet port connected to a coolant source, a first outlet port connected to the first coolant loop, and a second outlet port connected to the second coolant loop. A valve positioned on the pump housing is switchable to direct coolant from the inlet port to either the first outlet port or the second outlet port individually, or to the first outlet port and the second outlet port simultaneously. An impeller positioned on the pump housing pumps coolant received from the inlet port at an unrestricted flow rate. When the valve connects the first outlet port to the first coolant loop, the coolant is circulated through the first coolant loop at a flow rate less than the unrestricted flow rate, and when the valve connects the second outlet port to the second coolant loop, the coolant is circulated through the second coolant loop at a flow rate less than the unrestricted flow rate. Coolant is circulated through the first and second coolant loops at a flow rate less than the unrestricted flow rate when the valve simultaneously connects the first and second outlet ports to the first and second coolant loops, and the combined flow rates through the first and second coolant loops are equal to the unrestricted flow rate.

[0004] The present disclosure also relates to a method for distributing coolant through a first coolant loop and a second coolant loop, the method including pumping coolant from a pump at an unrestricted flow rate and positioning a valve in a first position to direct the coolant through a first outlet port of a pump connected to the first coolant loop, thereby circulating the coolant through the first coolant loop at a flow rate less than the unrestricted flow rate. The method further includes positioning the valve in a second position to direct the coolant through a second outlet port of a pump connected to a second coolant loop, thereby circulating the coolant through the second coolant loop at a flow rate less than the unrestricted flow rate. The method further includes positioning the valve in a third position to simultaneously direct the coolant through the first outlet port and the second outlet port, thereby circulating the coolant through each of the first coolant loop and the second coolant loop at flow rates less than the unrestricted flow rate that together equal the unrestricted flow rate.

[0005]

[0005] Other technical features may be readily apparent to those skilled in the art from the following drawings, descriptions, and claims.

[0006] For a more complete understanding of the present disclosure, reference is now made to the following description taken in conjunction with the accompanying drawings. [Brief explanation of the drawings]

[0006] [Figure 1]

[0007] FIG. 1 is a schematic diagram of a system of the present disclosure. [Figure 2]

[0008] FIG. 1 is a schematic diagram of a system of the present disclosure. [Figure 3]

[0009] FIG. 1 is a schematic diagram of a system of the present disclosure. [Figure 4]

[0010] FIG. 1 is an isometric view of a pump of the present disclosure. [Figure 5]

[0011] 6 is an isometric cross-sectional view of the valve member of the pump of FIG. 4 taken at section 6-6. [Figure 6]

[0012] 6 is a cross-sectional view of the pump taken at section 6-6 of FIG. 4, with the valve member in a first position. [Figure 7]

[0013] 6 is a cross-sectional view of the pump taken at section 6-6 of FIG. 4 with the valve member in a second position. [Figure 8]

[0014] 6 is a cross-sectional view of the pump taken at section 6-6 of FIG. 4 with the valve member in a third position. DETAILED DESCRIPTION OF THE INVENTION

[0007]

[0015] The drawings discussed below and the various embodiments used to illustrate the principles of the present invention in this patent document are merely exemplary and should not be construed in any way as limiting the scope of the invention. Those skilled in the art will understand that the principles of the present invention may be implemented in any type of suitably arranged device or system.

[0008]

[0016] 1-3 illustrate a system 10 for regulating the temperature of heat-generating components of a vehicle. The heat-generating components may be those used in the vehicle's drive unit, such as a DC-to-AC inverter 18 and an electric motor 20 for powering a hybrid or electric vehicle. The heat-generating components may also be components used in an electric energy generating unit, such as a high-voltage-to-low-voltage DC converter 14 and a vehicle battery charger 16. The heat-generating components may be organized into separate coolant loops in the system 10. For example, a first coolant loop 30 encompasses the heat-generating components of the drive components 18, 20, and a second coolant loop 40 encompasses the high-voltage-to-low-voltage DC converter 14 and vehicle battery charger 16 of the energy generating unit.

[0009]

[0017] A first coolant loop 30 containing a coolant is fluidly connected to a heat-dissipating device 12, such as a heat exchanger or radiator, and effects the transfer of heat from the coolant by directing ambient temperature air across the heat-dissipating device 12 using an electrically or mechanically driven fan. The heat-dissipating device 12 removes heat absorbed by the coolant from the heat-generating components. A second coolant loop 40 containing the coolant fluid fluidly connects the energy-generating components 14, 16 to the heat-dissipating device 12 through junction 18. Both the first loop 30 and the second loop 40 are connected to an electrically driven pump 50. The pump 50 includes a suction inlet port 51 fluidly connected to the fluid line 16 from the heat-dissipating device 12. The inlet port 51 receives the coolant from the heat-dissipating device 12 and pumps the coolant through the loops 30 and 40. The pump 50 further includes two outlet ports 55 and 58. Outlet port 55 provides a fluid outlet from pump 50 to fluid line 21 of coolant loop 30, and outlet port 58 provides a separate fluid outlet to fluid line 23 of coolant loop 40. Valve 56 is mounted to pump 50 and is movable to switch the flow of coolant from the outlet ports.

[0010]

[0018] 1 , valve 56 is switched to a first position providing a fluid path from inlet port 51 to outlet port 55 fluidly connecting coolant loop 30 and heat-generating components 18, 20 to heat dissipation device 12. In the first position, the valve closes outlet port 58, isolating coolant loop 40 from heat dissipation device 12. Coolant from pump 50 flows from outlet 55 to drive unit heat-generating components 18, 20, through fluid line 25, junction 18, and return line 13 to heat dissipation unit 12.

[0011]

[0019] 2, valve 56 is switched to a second position providing a fluid path from inlet port 51 to outlet port 58 that fluidly connects coolant loop 40 and energy generating unit heat-generating components 14, 16 to heat dissipation equipment 12. In the second position, the valve closes outlet port 55, isolating coolant loop 30 from heat dissipation equipment 12. Coolant from pump 50 flows from outlet port 58 to energy generating unit components 14, 16, through fluid line 27, junction 18, and return line 13 to heat dissipation unit 12.

[0012]

[0020] 3, valve 56 has been switched to a third position providing a fluid path from inlet port 51 to both outlet ports 55 and 58, simultaneously fluidly connecting both coolant loop 30 and coolant loop 40 to heat dissipation device 12. In the third position, the flow rate of coolant produced by pump 50 is shared between outlet ports 55 and 58. Coolant from pump 50 is pumped through both outlet port 55 and outlet port 58 to loops 30 and 40.

[0013]

[0021] Determining the flow rate that a pump can produce at a setpoint RPM, as produced by the motor driving the pump, is an art in pump design. The geometric design of the pump impeller and outlet port housing / volute region work in conjunction with the setpoint RPM to achieve the desired flow rate from the pump without flow restriction. Flow restriction causes inefficient use of energy as the impeller rotates the throttled fluid, preventing it from exiting the pump. When a larger than normal impeller is used in a restricted pump housing or with an outlet port having a small diameter or outlet area, geometric restriction and throttled flow rate result.

[0014]

[0022] For example, if the internal housing volume of the pump housing and the outlet port surrounding the impeller are too small for the setpoint RPM, the flow rate at the setpoint RPM will be restricted and the full flow the impeller is capable of producing will not exit the outlet. A solution to such flow restrictions would be to increase the housing volume or reduce the impeller geometry, e.g., the outer diameter of the impeller, to provide a more efficient flow rate.

[0015]

[0023] However, an impeller design suitable for unrestricted efficient flow for a single outlet pump will not provide sufficient flow for a diverting multiport pump when two or more outlet ports are open in the pump. A pump design with an impeller optimally designed to provide efficient flow for a pump with one outlet port will produce fractional flow for a pump with two or more open outlet ports.

[0016]

[0024] For example, sizing the impeller to have twice the capacity allowed by the outlet volume formed by the housing and opening a single outlet port results in a limited or throttled impeller capacity (φ 制限 = restriction factor). In this example, the inlet flow rate is half the impeller flow capacity (φ 制限 =2, i.e. Q 羽根車 / 2). Similarly, the outlet flow rate follows the inlet flow, minus any small losses, and is also half the impeller volume (Q 羽根車 / 2). The factor of 2 is shown for convenience only. where: Q 羽根車 = Impeller capacity Q 入口 =Q 羽根車 / φ 制限 Q y出口 =Q 羽根車 / φ 制限 is.

[0017]

[0025] For pumps with multiple diverting outlet ports, it is useful to make the impeller larger than normal to provide an equal amount of flow when two or more outlet ports are open for a single outlet port setpoint RPM. For example, using an impeller with twice the capacity allowed by the outlet volume formed by the housing, and a single outlet port, results in a restricted or throttled impeller capacity as shown above. However, when a diverting pump opens two or more outlet ports, the impeller capacity is no longer throttled. This results in a full, unrestricted impeller capacity to be achieved at the same setpoint RPM. The inlet capacity increases to match the outlet capacity (Q 入口 =Q 羽根車 ). The resulting outlet flow rate into both open outlet ports is calculated by multiplying the impeller capacity by the number of outlets (n 出口 ) by the quotient (i.e., Q x出口 =Q 羽根車 / n 出口 and Q y出口 =Q 羽根車 / n 出口 ) for convenience, two exits are shown in this example (n 出口 =2). where: Q 羽根車 = Impeller capacity Q 入口 =Q 羽根車 Q x出口 =Q 羽根車 / n 出口 Q y出口 =Q 羽根車 / n 出口 is.

[0018]

[0026] This results in the full unrestricted impeller volume to be used at the same setpoint RPM, with the inlet volume equal to the impeller volume. Therefore, in a diverter pump, it is useful to design an impeller that is restricted when only one outlet port is open, to provide reserve volume when two or more outlet ports are open.

[0019]

[0027] 4 illustrates an example of a diverter pump 50 for pumping coolant through system 10. As can be appreciated, pump 50 may be used in a vehicle or in non-vehicle applications. Pump 50 is an integration of a pump and a valve for selectively controlling the flow of coolant from the pump. Pump 50 includes a pump motor section 102 and a pump section 104. Pump motor section 102 includes a motor housing 106.

[0020]

[0028] FIG. 5 shows a cross-sectional perspective view of the pump compartment 104 taken at section 6-6 of FIG. 5. The pump motor housing 106 contains a pump motor (not shown) and a motor shaft 112 that is installed through an opening in a pump motor mounting plate 113. The pump motor drives an impeller 116 to move the coolant. The impeller 116 includes a plurality of impeller blades 118 for moving the coolant from an inlet to an outlet. The impeller 116 is driven by the motor shaft 112 and is configured to be rotatable within the pump compartment 104. The pump motor includes an electrical connection (not shown) adapted to receive power from a remotely located power source to energize and operate the pump motor.

[0021]

[0029] In FIG. 4 , the pump housing 131 of the pump compartment 104 is essentially cylindrically shaped and includes a peripheral outer wall 132. The inlet port 51, e.g., a suction inlet for drawing in coolant, is positioned about the axis of rotation of the pump housing 131. The pump housing 131 also includes at least two outlet ports for discharging coolant from the pump compartment 104. In this embodiment, a first outlet port 55 and a second outlet port 58 are shown. The first outlet port 55 and the second outlet port 58 extend from the wall 132 and are axially offset from one another, in this example, such that the centers of the outlet ports 55, 58 are oriented at 90 degrees from one another. It will be understood by those skilled in the art that the outlet ports 55, 58 may be offset from one another at any other convenient angle. A valve actuator may be housed in the actuator housing 105.

[0022]

[0030] Referring to FIG. 5 , outlet ports 55 and 58 are in downstream communication with pump cavity 150. Adjustable valve member 56 is positioned radially outward of impeller 116 and within pump cavity 150. Valve member 56 is positioned to adjustably direct coolant through each of outlet ports 55, 58. Valve member 56 has an annular wall 145 with an outer wall surface 149 and an inner wall surface 146, and an opening 144 extending through wall 145. In this example, wall 145 of valve member 56 is spirally convoluted from a generally thicker wall section at a first end 147 of opening 144 to a generally thinner wall section at a second end 148 of opening 144. Impeller 116 is positioned to rotate at a setpoint RPM within annular wall 145, and specifically within convoluted inner wall surface 146.

[0023]

[0031] During operation, rotation of the valve member 142 selectively switches the opening 144 to divert coolant from the pump cavity 150 to the first outlet port 55, the second outlet port 58, or to both outlet ports 55, 58 simultaneously, thereby controlling the discharge of coolant from the pump compartment 104.

[0024]

[0032] 6-8 illustrate the operation of the valve member 56 to direct flow from the pump cavity 150 to the outlet ports 55, 58. FIGS. 6-8 illustrate the mechanical position of the valve member 56 within the valve 50 as an actuator rotates the valve member 56 to switch the outlet ports 55, 58 on or off. As shown in FIG. 6, the impeller 116 rotates within the pump cavity 150 and inside the valve member 56. The impeller is driven by the pump motor 10 at a designed setpoint RPM. The pump cavity 150 receives coolant from the fluid line 16 via the pump inlet port 51. The impeller 116 and vanes 118 drive the fluid from the pump cavity 150 to one or more outlet ports 55, 58 according to the position of the opening 144. 6 , for example, the actuator rotates valve member 56 to a first position, switching opening 144 into alignment with outlet port 55 and providing a fluid path through pump 50 from inlet port 51 and pump cavity 150 to outlet port 55. In the first position, wall 145 of valve member 56 closes fluid outlet port 58. In the first position, fluid driven by impeller 116 is routed entirely through opening 144 in valve member 56 to outlet port 55. Referring again to FIG. 1 , when rotated to the first position, valve member 56 fluidly connects outlet port 55 to fluid line 21 and coolant loop 30, isolating the coolant from flowing into fluid line 23 and coolant loop 40.

[0025]

[0033] 7 shows valve member 56 positioned in a second position in which the actuator rotates valve member 56 to switch opening 144 into alignment with outlet port 58. This causes coolant driven by impeller 116 to be routed entirely through opening 144 in valve member 56 to fluid outlet port 58. Referring again to FIG. 2, valve member 56 switched to the second position fluidly connects outlet port 58 to fluid line 23 and coolant loop 40, isolating fluid flow to fluid line 21 and coolant loop 30.

[0026]

[0034] As discussed above, the impeller 116 is designed to have twice the capacity than is allowed by the outlet volume formed by each single port opening in the housing and outlets 55, 58. This results in a limited or throttled impeller volume (φ 制限 = restriction factor). In this example discussed previously, the inlet flow rate is half the impeller flow capacity (φ 制限 =2, i.e. Q 羽根車 / 2). Similarly, the outlet flow rate follows the inlet flow, minus any small losses, and is also half the impeller volume (Q 羽根車 / 2). For example, the impeller 116 is designed to provide a flow rate of 100 liters per minute (lpm) at a set point of 5000 RPM. This is the maximum efficient flow rate for the impeller 116. However, as previously discussed, the pump 50 throttles or restricts flow when only one of the two available outlet ports is switched into operation. Switching the valve member 56 to either the first or second position throttles the flow rate to a flow rate of 50 liters per minute (lpm) from either one of the fluid outlets 55, 58, or approximately half of that designed flow rate (Q x出口 or Q y出口 ) to achieve this. where: Wrpm set point = 5000rpm Q impeller = 100 lpm Q inlet=50lpm Qx outlet or Qy outlet = 50 lpm is.

[0027]

[0035] The impeller 116 has a capacity to produce a flow rate of 100 lpm, but when only one of the two fluid outlets is open, a throttled flow rate of 50 lpm is output from either one of the individually open fluid outlets 55, 58, and therefore the impeller 116 has a reserve capacity of 50 lpm.

[0028]

[0036] Switching of valve member 56 to the third position by the actuator is shown in Figure 8 and in the flow schematic diagram of Figure 3. In the third position, opening 144 is simultaneously aligned with both outlet ports 55, 58, allowing coolant fluid to be driven by impeller 116 from pump cavity 150 into both fluid lines 21, 23 and both coolant loops 30 and 40. With a constant impeller rotation of 5000 RPM and application of the equation previously determined, the impeller now provides its designed reserve flow capacity, which is shared between coolant loop 30 and coolant loop 40. where Wrpm set point = 5000rpm Q impeller = 100 lpm Q inlet=100lpm Qx outlet or Qy outlet = 50 lpm This provides equal flow rates through each of loops 30 and 40 using reserve capacity.

[0029]

[0037] Those skilled in the art will appreciate that the impeller 116 can be designed to provide a reserve capacity impeller to maintain equal flow rates from pumps with three or more switched outlet ports at a setpoint RPM. For example, when a pump impeller is sized by a design with a flow rate that is not restricted or throttled by the housing, volute volume, and fluid outlet, for example, in dual-flow mode, with the first and second outlet ports of a three-outlet-port pump open, the simultaneous flow rate is the sum of both flows from the two open outlet ports, which equals the flow rate at the pump inlet port, which equals the impeller flow capacity at the rpm setpoint. When the pump valve is switched to only one open port, for example, with the third outlet port open and the first and second outlet ports closed, the flow rate is equal to the flow rate through either of the two previously open outlet ports, with the inlet being half the impeller capacity.

[0030]

[0038] It may be useful to set forth definitions of certain words and phrases used throughout this patent document. The term "communicate" and its derivatives encompass both direct and indirect communication. The terms "include" and "comprise" and their derivatives mean inclusiveness without limitation. The term "or" is inclusive and / or. The phrase "associated with" and its derivatives can mean including, contained within, interconnected with, containing, contained within, connected to or with, coupled to or with, communicable with, cooperate with, interposed between, juxtaposed with, adjacent to, joined to or with, having, having a characteristic of, or having a relationship with or to, etc. The phrase "at least one of," when used in conjunction with a list of items, means that different combinations of one or more of the listed items may be used, and that only one item of the list may be required. For example, "at least one of: A, B, and C" includes any of the following combinations: A, B, C, A and B, A and C, B and C, and A, B, and C.

[0031]

[0039] Nothing in this patent application should be read to imply that any particular element, step, or function is an essential or critical element required for inclusion in the scope of any claim. The scope of the claimed subject matter is defined solely by the claims as granted. Moreover, nothing in the claims is intended to invoke 35 U.S.C. § 112(f) with respect to any of the appended claims or claim elements unless the precise words "means for" or "step for" are expressly used in a particular claim after the participial phrase identifying the function. The use of terms such as (without limitation) "mechanism," "module," "device," "unit," "component," "element," "member," "apparatus," "machine," "system," or "controller" in the claims is understood and intended to refer to structures known to those skilled in the art, as further modified or augmented by the features of the claims themselves, and is not intended to invoke 35 U.S.C. § 112(f).

[0032]

[0040] While this disclosure has described particular embodiments and generally associated methods, variations and permutations of these embodiments and methods will be apparent to those skilled in the art. Accordingly, the above description of exemplary embodiments does not define or constrain the disclosure. Moreover, other changes, substitutions, and alterations are possible without departing from the spirit and scope of the disclosure, as defined by the following claims.

Claims

1. 1. An apparatus for distributing coolant through a first coolant loop and a second coolant loop, comprising: a pump having a housing including an inlet port connected to a coolant source, a first outlet port connected to the first coolant loop, and a second outlet port connected to the second coolant loop; a valve located on the pump housing switchable to direct coolant from the inlet port to either the first outlet port or the second outlet port individually, or to the first outlet port and the second outlet port simultaneously; an impeller positioned in the pump housing for pumping the coolant received from the inlet port at an unrestricted flow rate; Equipped with when the valve connects the first outlet port to the first coolant loop, the coolant is circulated through the first coolant loop at a flow rate less than the unrestricted flow rate; when the valve connects the second outlet port to the second coolant loop, the coolant is circulated through the second coolant loop at a flow rate less than the unrestricted flow rate; and when the valve connects the first outlet port and the second outlet port simultaneously to the first coolant loop and the second coolant loop, the coolant is circulated through the first coolant loop and the second coolant loop at flow rates less than the unrestricted flow rate that together equal the unrestricted flow rate.

2. 10. The apparatus of claim 1, wherein the pump includes a motor connected to the impeller, the motor configured to rotate the impeller at a setpoint RPM.

3. The apparatus of claim 1 , wherein the impeller is positioned within the pump housing between the inlet port and the valve.

4. The apparatus of claim 2 , wherein the pump inlet port is connected to a heat dissipation device that supplies the source of coolant.

5. The apparatus of claim 4 , wherein the heat dissipation device is fluidly connected to the first coolant loop and the second coolant loop.

6. 6. The apparatus of claim 5, wherein the first coolant loop includes at least one heat-generating component, and the pump circulates coolant through the first outlet port to the at least one heat-generating component in the first coolant loop and to the heat dissipation equipment.

7. 6. The apparatus of claim 5, wherein the second coolant loop includes at least one heat-generating component, and the pump circulates coolant through the second outlet port to the at least one heat-generating component of the second coolant loop and to the heat dissipation device.

8. 3. The apparatus of claim 2, wherein the pump impeller pumps the coolant at an unrestricted flow rate greater than the flow rate provided through the first outlet port and circulated through the first coolant loop, and the flow rate of the coolant returned to the inlet port is less than the unrestricted flow rate produced by the impeller at the setpoint RPM.

9. 3. The apparatus of claim 2, wherein the pump impeller pumps the coolant at an unrestricted flow rate greater than the flow rate provided through the second outlet port and circulated through the second coolant loop, and the flow rate of the coolant returned to the inlet port is less than the unrestricted flow rate produced by the impeller at the setpoint RPM.

10. 3. The apparatus of claim 2, wherein the pump impeller pumps the coolant at an unrestricted flow rate greater than the flow rates simultaneously applied to the first and second outlet ports and circulated through the first and second coolant loops, and the flow rate of the coolant returned to the inlet port is equal to the unrestricted flow rate produced by the impeller at the setpoint RPM.

11. 1. A method for distributing coolant through a first coolant loop and a second coolant loop, comprising: pumping coolant through a pump at an unrestricted flow rate; positioning a valve in a first position to direct the coolant through a first outlet port of the pump connected to the first coolant loop, circulating the coolant through the first coolant loop at a flow rate less than the unrestricted flow rate; A method comprising:

12. positioning a valve in a second position to direct the coolant through a second outlet port of the pump connected to the second coolant loop, circulating the coolant through the second coolant loop at a flow rate less than the unrestricted flow rate. The method of claim 11 further comprising:

13. positioning a valve in a third position to simultaneously direct the coolant through a first outlet port and a second outlet port to circulate the coolant through each of the first and second coolant loops at a flow rate that together equals the unrestricted flow rate but is less than the unrestricted flow rate. The method of claim 11 further comprising:

14. 14. The method of claim 13, wherein a heat dissipation device is fluidly connected to the first coolant loop and the second coolant loop, and the pump further includes an inlet port connected to the heat dissipation device.

15. 15. The method of claim 14, wherein the first coolant loop includes at least one heat-generating component, and the pump circulates coolant through the first outlet port to the at least one heat-generating component in the first coolant loop and to the heat dissipation equipment.

16. 15. The method of claim 14, wherein the second coolant loop includes at least one heat-generating component, and the pump circulates coolant through the second outlet port to the at least one heat-generating component of the second coolant loop and to the heat dissipation equipment.

17. 17. The method of claim 16, wherein the pump includes a motor connected to the impeller, the motor configured to rotate the impeller at a setpoint RPM to pump the coolant from the inlet port at the unrestricted flow rate.

18. 18. The method of claim 17, wherein the pump impeller pumps the coolant at a flow rate greater than the flow rate provided through the first outlet port and circulated through the first coolant loop, and the flow rate of the coolant returned to the inlet port is less than the unrestricted flow rate produced by the impeller at the setpoint RPM.

19. 18. The method of claim 17, wherein the pump impeller pumps the coolant at the unrestricted flow rate greater than the flow rate provided through the second outlet port and circulated through the second coolant loop, and the flow rate of the coolant returned to the inlet port is less than the unrestricted flow rate produced by the impeller at the setpoint RPM.

20. 18. The method of claim 17, wherein the pump impeller pumps the coolant at the unrestricted flow rate greater than the flow rate provided to the first and second coolant loops simultaneously through each of the first and second outlet ports, and the flow rate of the coolant returned to the inlet port is equal to the unrestricted flow rate produced by the impeller at the setpoint RPM.

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