Multi-port fluid pump with reserve capacity impeller

Abstract

An apparatus and method for distributing coolant fluid through first and second coolant circuits includes a pump having a first outlet port connected to the first coolant circuit and a second outlet port connected to the second coolant circuit, and a valve located in a pump housing, the valve is switchable to direct coolant fluid individually to the first or second outlet ports or simultaneously to the first and second outlet ports. When the valve connects the first outlet port to the first coolant circuit, coolant fluid pumped by the pump at an unrestricted flow rate circulates through the first coolant circuit at a flow rate less than the unrestricted flow rate, and when the valve connects the second outlet port to the second coolant circuit, coolant fluid pumped by the pump at a flow rate less than the unrestricted flow rate circulates through the second coolant circuit. The coolant fluid circulates through the second coolant circuit at a flow rate less than the unlimited flow rate. When the valve simultaneously connects the first and second outlet ports to the first and second coolant circuits, coolant fluid circulates through the first and second coolant circuits at a flow rate less than the unrestricted flow rate, and the flow rates through the first and second coolant circuits add up to the unrestricted flow rate.

Description

Technical Field

[0001] The present invention generally relates to a multi-port fluid pump for switching fluid flow to heat generating or heat absorbing components, and more particularly to a multi-port fluid pump with an integrated valve having a reserve capacity impeller. Background Art

[0002] Pumps are known and commonly used to move fluids, such as coolants in vehicles. An example is a cooling system with a water pump for cooling different electrical or mechanical components of the vehicle. In hybrid vehicles or pure electric vehicles, the electrical components need to be cooled. Valves are used to ensure the distribution of coolant throughout the cooling system. Each valve requires an electrically controlled actuator and a bracket mounted on the vehicle component, which leads to high component costs. In some vehicles, more than one cooling circuit can be used to cool the heat-generating components and regulate the temperature of the cabin. In a pump with multiple output ports connecting a single pump to one or more cooling circuits, valves can be used to switch and direct fluid flow between one or more cooling circuits. A rotating impeller driven by an electric motor or by other mechanical means is used by the pump to drive the coolant fluid from the pump through one or more cooling circuits. The impeller, housing and outlet port of the pump are designed to provide fluid flow with maximum efficiency and minimum flow restriction based on the rotation of the impeller. It is desirable to provide an impeller with a reserve capacity so that the fluid flows through two or more cooling circuits at the same flow rate as a single cooling circuit. Summary of the invention

[0003] The present invention relates to an apparatus for distributing a coolant fluid through a first and a second coolant circuit, the apparatus comprising a pump having a housing, the housing comprising an inlet port connected to a coolant fluid source, a first outlet port connected to a first coolant circuit, and a second outlet port connected to a second coolant circuit. A valve located in the pump housing is switchable to direct the coolant fluid from the inlet port to the first outlet port or the second outlet port alone, or to the first outlet port and the second outlet port simultaneously. An impeller located in the pump housing pumps the coolant fluid received from the inlet port at an unrestricted flow rate. When the valve connects the first outlet port to the first coolant circuit, the coolant fluid circulates through the first coolant circuit at a flow rate less than the unrestricted flow rate, and when the valve connects the second outlet port to the second coolant circuit, the coolant fluid circulates through the second coolant circuit at a flow rate less than the unrestricted flow rate. When the valve simultaneously connects the first outlet port to the first coolant circuit and the second outlet port to the second coolant circuit, the coolant fluid circulates through the first coolant circuit and the second coolant circuit at a flow rate that is less than the unrestricted flow rate, and the flow rate through the first coolant circuit and the flow rate of the second coolant circuit add up to equal the unrestricted flow rate.

[0004] The present invention also relates to a method for distributing a coolant fluid through a first coolant circuit and a second coolant circuit, comprising pumping the coolant fluid from a pump at an unrestricted flow rate, and positioning a valve in a first position to direct the coolant fluid through a first outlet port of the pump connected to the first coolant circuit, so that the coolant fluid circulates through the first coolant circuit at a flow rate less than the unrestricted flow rate. The method also includes positioning the valve in a second position to direct the coolant fluid through a second outlet port of the pump connected to the second coolant circuit, so that the coolant fluid circulates through the second coolant circuit at a flow rate less than the unrestricted flow rate. The method also includes positioning the valve in a third position to direct the coolant fluid through both the first outlet port and the second outlet port, so that the coolant fluid circulates through each of the first coolant circuit and the second coolant circuit at a flow rate less than the unrestricted flow rate, and these flow rates add up to equal the unrestricted flow rate.

[0005] Other technical features may be apparent to those skilled in the art from the following drawings, descriptions and claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0006] For a more complete understanding of the present invention, reference is now made to the following description taken in conjunction with the accompanying drawings, in which:

[0007] Figure 1 A schematic diagram of the system of the present invention is shown;

[0008] Figure 2 A schematic diagram of the system of the present invention is shown;

[0009] Figure 3 A schematic diagram of the system of the present invention is shown;

[0010] Figure 4 An isometric view of a pump of the present invention is shown;

[0011] Figure 5 Shown along Figure 4 An isometric cross-sectional view through the valve member of the pump taken along line 6-6 in FIG.

[0012] Figure 6 Shown along Figure 4 A cross-sectional view through the pump taken along line 6-6 in FIG. 1 , wherein the valve member is in a first position;

[0013] Figure 7 Shown along Figure 4 A cross-sectional view through the pump taken along line 6-6 in FIG. 1 , wherein the valve member is in the second position; and

[0014] Figure 8 Shown along Figure 4A cross-sectional view through the pump taken along line 6-6 in FIG. 1 , wherein the valve member is in the third position. DETAILED DESCRIPTION

[0015] In this patent document, the accompanying drawings discussed below and the various embodiments used to describe the principles of the present invention are merely illustrative and should not be interpreted in any way as limiting the scope of the present invention. Those skilled in the art will appreciate that the principles of the present invention can be implemented in any type of appropriately arranged device or system.

[0016] Figure 1-3 A system 10 for regulating the temperature of heat generating components of a vehicle is described. The heat generating components may be those components used in the drive unit of the vehicle, such as a direct current (DC) to alternating current (AC) inverter 18 and an electric motor 20 for powering a hybrid vehicle or an electric vehicle. The heat generating components may also be components used in an electrical 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 arranged in separate coolant loops in the system 10. For example, a first coolant loop 30 contains the heat generating components of the drive components 18, 20, and a second coolant loop 40 contains the high voltage to low voltage DC converter 14, and the vehicle battery charger 16 of the energy generating unit.

[0017] The first coolant loop 30 containing a coolant fluid is fluidly connected to a heat sink 12, such as a heat exchanger or radiator, which uses an electrically driven or mechanically driven fan to provide transfer of heat from the coolant by directing air at ambient temperature through the heat sink 12. The heat sink 12 removes heat absorbed by the coolant fluid from the heat generating components. The second coolant loop 40 containing a coolant fluid fluidly connects the energy generating components 14, 16 to the heat sink 12 through the joint 18, and the first coolant loop 34 and the second coolant loop 40 are both connected to an electrically driven pump 50. The pump 50 includes an inlet port / suction port 51 that is fluidly connected to the fluid line 16 from the heat sink 12. The inlet port 51 receives the coolant fluid from the heat sink 12 and pumps the coolant fluid through the loops 30 and 40. The pump 50 also includes two outlet ports 55 and 58. The outlet port 55 provides a fluid outlet from the pump 50 to the fluid line 21 of the coolant loop 30, and the outlet port 58 provides a separate fluid outlet to the fluid line 23 of the coolant loop 40. A valve 56 mounted in the pump 50 is movable to switch the flow of coolant fluid from the outlet port.

[0018] For example, in Figure 1, the valve 56 is switched to a first position that provides a fluid path from the inlet port 51 to the outlet port 55 that fluidly connects the coolant loop 30 and the heat generating components 18, 20 to the heat sink 12. In the first position, the valve blocks the outlet port 58, isolating the coolant loop 40 from the heat sink 12. The coolant fluid from the pump 50 flows from the outlet port 55 to the drive unit heat generating components 18, 20, through the fluid line 25, the joint 18 and the return line 13 to the heat sink 12.

[0019] exist Figure 2 In the second position, the valve 56 is switched to a second position, which provides a fluid path from the inlet port 51 to the outlet port 58, which fluidly connects the coolant loop 40 and the heat generating components 14, 16 of the energy generating unit to the heat sink 12. In the second position, the valve blocks the outlet port 55, isolating the coolant loop 30 from the heat sink 12. The coolant fluid from the pump 50 flows from the outlet port 58 to the energy generating unit components 14, 16, through the fluid line 27, the joint 18 and the return line 13 to the heat sink 12.

[0020] exist Figure 3 5, the valve 56 is switched to the third position, which provides a fluid path from the inlet port 51 to both the outlet port 55 and the outlet port 58, which fluidly connects both the coolant circuit 30 and the coolant circuit 40 to the heat sink 12. In the third position, the flow of the coolant fluid generated by the pump 50 is distributed between the outlet ports 55 and 58. The coolant fluid from the pump 50 is pumped to both the outlet ports 55 and 58 to reach the coolant circuit 30 and the coolant circuit 40.

[0021] In pump design, a practical technique is to define the flow rate that the pump is capable of producing at a set speed (RPM) produced by the electric motor driving the pump. The geometric design of the pump impeller and the outlet port housing / spiral area work in conjunction with the set speed to achieve the desired flow rate from the pump without flow restriction. Flow restriction results in an inefficient use of energy because there is no impeller rotation throttling the fluid leaving the pump. Using an oversized impeller or an outlet port with a small diameter or outlet area within a restricted pump housing results in geometric restriction and throttling of the flow rate.

[0022] For example, if the internal case volume of the pump casing and the internal case volume surrounding the outlet port of the impeller are too small for the set speed, the flow at the set speed will be restricted and the full flow that the impeller can produce will not leave the outlet. The solution to this flow restriction is to increase the case volume or reduce the impeller geometry, such as the impeller outer diameter, to provide a more efficient flow.

[0023] However, when two or more outlet ports are opened in a pump, the impeller design itself provides unrestricted and efficient flow for a one outlet pump, but may not provide sufficient flow in a switched multi-port pump. A pump design with an impeller optimally designed to provide efficient flow for a pump with one outlet port will produce a fractional flow for a pump with two or more open outlet ports.

[0024] For example, sizing the impeller to have twice the capacity allowed by the outlet volume formed by the casing and the single outlet opening results in a restricted or throttled impeller capacity. In this example, the inlet flow is half the impeller flow capacity ( or Q 叶轮 / 2). Likewise, the outlet flow, minus any small losses, is less than the inlet flow and is also half the impeller capacity (Q 叶轮 / 2). The factor 2 is shown for convenience only.

[0025] in:

[0026] Q 叶轮 = Impeller capacity

[0027]

[0028] For pumps with multiple switched outlet ports, it is advantageous to oversize the impeller for a single outlet port set speed in order to provide an equal amount of flow when two or more outlet ports are open. For example, using an impeller with twice the capacity allowed by the outlet volume formed by the housing and the single outlet port results in a restricted or throttled impeller capacity as shown above. However, when a switched pump opens two or more outlet ports, the impeller capacity is no longer throttled. This results in a full, unrestricted impeller capacity being achieved at the same set speed. The inlet capacity is increased to match the outlet capacity (Q 入口 =Q 叶轮 The final outlet flow to the two open outlet ports is equal to the impeller capacity divided by the number of outlets (n 出口 ) or (Q x-出口 =Q 叶轮 / n 出口 , and Q y-出口 =Q 叶轮 / n 出口 For convenience, two outlets (n 出口 =2).

[0029] in:

[0030] Q 叶轮 = Impeller capacity

[0031] Q 入口 =Q 叶轮

[0032] Q x-出口 =Q 叶轮 / n 出口

[0033] Q y-出口 =Q 叶轮 / n 出口

[0034] This results in the use of completely unrestricted impeller capacity at the same set speed, and where the inlet capacity is equal to the impeller capacity. Therefore, in a switching pump it is advantageous to design the impeller to be restricted when only one outlet port is open, in order to provide reserve capacity when two or more outlet ports are open.

[0035] Figure 4 An example of a switching pump 50 for pumping coolant fluid in the system 10 is shown. As can be appreciated, the pump 50 can be used in a vehicle and can also be used in non-vehicle applications. The pump 50 is an integration of a pump and a valve for selectively controlling the flow of coolant fluid from the pump. The pump 50 includes a pump motor section 102 and a pump section 104. The pump motor section 102 includes a motor housing 106.

[0036] Figure 5 Shown along Figure 4 6, the pump motor housing 106 houses the pump motor (not shown) and the motor shaft 112 is mounted through the opening of the pump motor mounting plate 113. The pump motor drives an impeller 116 to move the coolant fluid. The impeller 116 includes a plurality of impeller blades 118 for moving the coolant fluid from the inlet to the outlet. The impeller 116 is configured to rotate within the pump section 104 driven by the motor shaft 112. The pump motor includes an electrical connection (not shown) that is suitable for receiving electrical energy from a remotely located power source to power and operate the pump motor.

[0037] exist Figure 4 , the pump housing 131 of the pump section 104 is substantially cylindrical and includes a peripheral wall 132. An inlet port 51, such as a suction port for inhaling coolant fluid, is located at the center of the rotational axis of the pump housing 131. The pump housing 131 also includes at least two outlet ports for discharging coolant fluid from the pump section 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 walls 132, 132 and are axially offset from each other so that the centers of the outlet ports 55, 58 are oriented at 90 degrees to each other in this example. Those skilled in the art will appreciate that the outlet ports 55, 58 can be offset from each other at any other convenient angle. The valve actuator can be housed in the actuator housing 105.

[0038] Reference Figure 5 , the outlet ports 55 and 58 are in downstream communication with the pump chamber 150. The adjustable valve member 56 is located radially outside the impeller 116 and inside the pump chamber 150. The valve member 56 is arranged to adjustably guide the coolant fluid through the respective outlet ports 55, 58. The valve member 56 has an annular wall 145 having an outer wall surface 149 and an inner wall surface 146 and an opening 144 extending through the annular wall 145. In this example, the annular wall 145 of the valve member 56 spirally extends from a generally thicker wall section at a first end 147 of the opening 144 to a generally thinner wall section at a second end 148 of the opening 144. The impeller 116 is arranged to be rotatable within the annular wall 145, in particular, within the spirally extending inner wall surface 146 at a set rotational speed.

[0039] In operation, rotation of the valve member 142 selectively switches the opening 144 to divert coolant fluid from the pump chamber 150 to the first outlet port 55 , the second outlet port 58 , or both outlet ports 55 , 58 , thereby controlling discharge of coolant fluid from the pump section 104 .

[0040] Figure 6-8 Operation of the valve member 56 to direct fluid flow from the pump chamber 150 to the outlet ports 55 , 58 is shown. Figure 6-8 2 shows the mechanical position of the valve member 56 within the valve 50 when the actuator rotates the valve member 56 to open or close the outlet ports 55, 58. Figure 6 As shown, the impeller 116 rotates within the pump chamber 150 and the valve member 56. The impeller is driven by the pump motor 10 at a designed set speed. The pump chamber 150 receives the coolant fluid from the fluid line 16 from the pump inlet port 51, and the impeller 116 and the blades 118 drive the fluid from the pump chamber 150 to one or more outlet ports 55, 58 according to the position of the opening 144. For example, in Figure 6 , the actuator rotates the valve member 56 to the first position, switching the opening 144 to align with the outlet port 55, providing a fluid path through the pump 50 from the inlet port 51 and the pump chamber 150 to the outlet port 55. In the first position, the wall 145 of the valve member 56 closes the fluid outlet port 58. In the first position, the fluid driven by the impeller 116 flows completely through the opening 144 of the valve member 56 to the outlet port 55. Referring again to Figure 1 When rotated to the first position, the valve member 56 fluidly connects the outlet port 55 to the fluid line 21 and the coolant circuit 30 , thereby isolating the coolant from flowing into the fluid line 23 and the coolant circuit 40 .

[0041] Figure 7The valve member 56 is shown in a second position, wherein the actuator rotates the valve member 56 to switch the opening 144 into alignment with the outlet port 58. This allows the coolant fluid driven by the impeller 116 to flow completely through the opening 144 of the valve member 56 to the fluid outlet 58. Figure 2 , the valve member 56 switched to the second position fluidly connects the outlet port 58 to the fluid line 23 and the coolant circuit 40 , thereby isolating the fluid flow to the fluid line 21 and the coolant circuit 30 .

[0042] As described above, the impeller 116 is designed to have twice the capacity allowed by the outlet volume formed by each single port opening of the housing and outlets 55, 58, which results in a restricted or throttled impeller capacity. In the example described previously, the inlet flow is half the impeller flow capacity ( or Q 叶轮 / 2). Similarly, the outlet flow (minus any minor losses) is less than the inlet flow and is also half the impeller capacity (Q 叶轮 / 2). For example, the impeller 116 is designed to provide a flow rate of 100 liters per minute (lpm) at a set speed of 5000 RPM. This is the maximum effective flow rate of the impeller 116. However, as previously described, when only one of the two available outlet ports is switched to operation, the pump 50 throttles or restricts the flow rate. Switching the valve member 56 to the first position or the second position, the flow rate is throttled to achieve a flow rate of 50 liters per minute (lpm), or to achieve a flow rate of 100 liters per minute (lpm) from the fluid outlets 55, 58 (Q x -Exit or Q y - outlet) is approximately half of the design flow rate of any of the outlets.

[0043] in:

[0044] W 设定转速 =5000rpm

[0045] Q 叶轮 =100lpm

[0046] Q 入口 =50lpm

[0047] Q x-出口 or Q y-出口 =50lpm

[0048] The impeller 116 has the capability of producing a flow of 100 lpm, however, when only one of the two fluid outlets is open, a throttle flow of 50 lpm is output from either of the individually opened fluid outlets 55 , 58 , and thus the impeller 116 has a reserve capacity of 50 lpm.

[0049] exist Figure 3 In the flow diagram and in Figure 8 1 shows the valve member 56 being switched to the third position by the actuator. In the third position, the opening 144 is aligned with both outlet ports 55, 58 simultaneously, providing coolant fluid from the pump chamber 150 driven by the impeller 116 to both fluid lines 21, 23 and both coolant circuits 30 and 40. With the impeller rotating at a constant speed of 5000 RPM, and applying the previously derived formula, the impeller now provides its designed reserve flow capacity, which is shared by both the coolant circuit 30 and the coolant circuit 40.

[0050] in:

[0051] W 设定转速 =5000rpm

[0052] Q 叶轮 =100lpm

[0053] Q 入口 =100lpm

[0054] Q x-出口 and Q y-出口 =50lpm

[0055] Reserve capacity is thereby utilized to provide equal flow through each of the circuits 30 and 40 .

[0056] Those skilled in the art will appreciate that the impeller 116 can be designed to provide a reserve capacity impeller in order to maintain equal flow from a pump having three or more switched outlet ports at a set speed. For example, when the pump impeller is sized by design to have a flow rate that is not limited or throttled by the casing, the spiral volume, and the fluid outlet in a dual flow mode, such as a first outlet port and a second outlet port of a three-outlet port pump are open, and the flow rate is the sum of the flows from the two open outlet ports, this will be equal to the flow rate at the pump inlet port, which in turn is equal to the impeller flow capacity at the set speed. When the pump valve is switched to only one open port, such as the third outlet port is open and the first outlet port and the second outlet port are closed, the flow rate will be equal to the flow through either of the two previously opened outlet ports, where the inlet flow rate is half of the impeller capacity.

[0057] It may be advantageous to clarify the definitions of certain words and phrases used throughout this patent document. The term "connected" and its derivatives include direct and indirect connections. The terms "include" and "comprises" and their derivatives mean including but not limited to. The term "or" is inclusive and means and / or. The phrase "associated with..." and its derivatives may mean including, included within, interconnected, containing, contained within, connected to or connected with, connected to or connected with, communicable with, coordinated with, interlaced, juxtaposed, close to, combined with or combined with, having, having the attributes of, having a relationship with, etc. When used with a list of items, the phrase "at least one" means that different combinations of one or more of the listed items may be used, and only one item in the list may be required. For example, "at least one of A, B, C" includes any combination of: A, B, C, A and B, A and C, B and C, A and B and C.

[0058] The description in this application should not be construed as implying that any particular element, step, or function is an essential or critical element that must be included within the scope of the claims. The scope of the subject matter for which patent rights are claimed is limited only by the claims that allow. In addition, no claim is intended to invoke 35 U.S.C. §112(f) with respect to any appended claim or claim element unless the exact words "means for..." or "step for..." are expressly used in a particular claim, followed by a participle phrase identifying the function. The use of terms such as (but not limited to) "mechanism", "module", "device", "unit", "component", "element", "member", "device", "machine", "system", or "controller" in the claims shall be understood and intended to refer to structures known to those skilled in the relevant art, further modified or enhanced by the features of the claims themselves, and are not intended to invoke 35 U.S.C. §112(f).

[0059] Although the present invention has described certain embodiments and generally associated methods, the changes and arrangements of these embodiments and methods will be apparent to those skilled in the art. Therefore, the above description of the exemplary embodiments does not define or restrict the present invention. Other changes, substitutions and variations are also possible without departing from the spirit and scope of the present invention as defined by the appended claims.

Claims

1. An apparatus for distributing a coolant fluid through a first coolant circuit and a second coolant circuit, the apparatus comprising: a pump having a housing including an inlet port connected to a coolant fluid source, a first outlet port connected to the first coolant circuit, and a second outlet port connected to the second coolant circuit; a valve in the pump housing, the valve switchable to direct coolant fluid from the inlet port to the first outlet port or the second outlet port alone, or to both the first outlet port and the second outlet port; as well as an impeller located in the pump housing, the impeller pumping the coolant fluid received from the inlet port at an unrestricted flow rate, wherein when the valve connects the first outlet port to the first coolant circuit, the coolant fluid circulates through the first coolant circuit at a flow rate less than the unrestricted flow rate, and when the valve connects the second outlet port to the second coolant circuit, the coolant fluid circulates through the second coolant circuit at a flow rate less than the unrestricted flow rate, and when the valve simultaneously connects the first outlet port to the first coolant circuit and the second outlet port to the second coolant circuit, the coolant fluid circulates through the first coolant circuit and the second coolant circuit at a flow rate less than the unrestricted flow rate and the flow rate of the coolant fluid circulated through the first coolant circuit and the flow rate of the coolant fluid circulated through the second coolant circuit add up to equal the unrestricted flow rate.

2. The device according to claim 1, wherein: The pump comprises an electric motor connected to the impeller, the electric motor being arranged to rotate the impeller at a set rotational speed.

3. The device according to claim 1, wherein: The impeller is disposed within a housing of the pump between the inlet port and the valve.

4. The device according to claim 2, wherein: The inlet port of the pump is connected to a heat sink that provides the source of coolant fluid.

5. The device according to claim 4, wherein: The heat sink is fluidly connected to the first coolant loop and the second coolant loop.

6. The device according to claim 5, wherein: The first coolant loop includes at least one heat generating component, and the pump circulates coolant fluid through the first outlet port to the at least one heat generating component in the first coolant loop and to the heat sink.

7. The device according to claim 5, wherein: The second coolant loop includes at least one heat generating component, and the pump circulates coolant fluid through the second outlet port to the at least one heat generating component of the second coolant loop and to the heat sink.

8. The device according to claim 2, wherein: The impeller of the pump pumps the coolant fluid at the unrestricted flow rate, which is greater than the flow rate applied through the first outlet port and circulated through the first coolant circuit, wherein the flow rate of the coolant fluid returned to the inlet port is less than the unrestricted flow rate generated by the impeller at the set speed.

9. The device according to claim 2, wherein: The impeller of the pump pumps the coolant fluid at the unrestricted flow rate, which is greater than the flow rate applied through the second outlet port and circulated through the second coolant circuit, wherein the flow rate of the coolant fluid returned to the inlet port is less than the unrestricted flow rate generated by the impeller at the set speed.

10. The device according to claim 2, wherein: The impeller of the pump pumps the coolant fluid at the unrestricted flow rate, which is greater than the flow rates simultaneously applied to the first outlet port and the second outlet port and circulated through the first coolant circuit and the second coolant circuit, wherein the flow rate of the coolant fluid returned to the inlet port is equal to the unrestricted flow rate produced by the impeller at the set speed.

11. A method for distributing a coolant fluid through a first coolant circuit and a second coolant circuit, comprising: pumping coolant fluid from the pump at an unrestricted flow rate; Positioning a valve in a first position to direct the coolant fluid through a first outlet port of the pump connected to the first coolant circuit to circulate coolant fluid through the first coolant circuit at a flow rate less than the unrestricted flow rate.

12. The method according to claim 11, wherein: The method further comprises: Positioning the valve in a second position directs the coolant fluid through a second outlet port of the pump connected to the second coolant circuit to circulate the coolant fluid through the second coolant circuit at a flow rate that is less than the unrestricted flow rate.

13. The method according to claim 11, wherein: The method further comprises: The valve is positioned in a third position to direct the coolant fluid through the first outlet port and the second outlet port simultaneously, so that the coolant fluid circulates through each of the first coolant circuit and the second coolant circuit at a flow rate that is less than the unrestricted flow rate, and the flow rate of the coolant fluid circulated through the first coolant circuit and the flow rate of the coolant fluid circulated through the second coolant circuit sum to equal the unrestricted flow rate.

14. The method according to claim 13, wherein: A heat sink 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 sink.

15. The method according to claim 14, wherein: The first coolant loop includes at least one heat generating component, and the pump circulates coolant fluid through the first outlet port to the at least one heat generating component in the first coolant loop and to the heat sink.

16. The method according to claim 14, wherein: The second coolant loop includes at least one heat generating component, and the pump circulates coolant fluid through the second outlet port to the at least one heat generating component of the second coolant loop and to the heat sink.

17. The method according to claim 16, wherein: The pump includes an electric motor connected to an impeller, the electric motor being arranged to rotate the impeller at a set speed so as to pump coolant fluid from the inlet port at the unrestricted flow rate.

18. The method according to claim 17, wherein: The impeller of the pump pumps the coolant fluid at a flow rate greater than the flow rate applied through the first outlet port and circulated through the first coolant circuit, wherein the flow rate of the coolant fluid returning to the inlet port is less than the unrestricted flow rate produced by the impeller at the set speed.

19. The method according to claim 17, wherein: The impeller of the pump pumps the coolant fluid at the unrestricted flow rate, which is greater than the flow rate applied through the second outlet port and circulated through the second coolant circuit, wherein the flow rate of the coolant fluid returned to the inlet port is less than the unrestricted flow rate generated by the impeller at the set speed.

20. The method according to claim 17, wherein: The impeller of the pump pumps the coolant fluid at the unrestricted flow rate, which is greater than the flow rate simultaneously applied to the first coolant circuit and the second coolant circuit through each of the first outlet port and the second outlet port, wherein the flow rate of the coolant fluid returned to the inlet port is equal to the unrestricted flow rate produced by the impeller at the set speed.

Images