SPLIT OUTPUT CONNECTION FOR PUMP WITH INTERNAL TEMPERATURE MEASURING DEVICE

Abstract

A pumping system includes: a housing with a pump and an electric motor therein; a pump inlet with a pump inlet port; a pump outlet with a pump outlet port; a drive shaft, rotatably driven by the electric motor, for driving the pump to pressurize fluid received through a main path of the pump from the pump inlet for discharge from an outlet path to the pump outlet; and a controller with a sensor. A portion of the pressurized fluid is directed to an auxiliary circuit for temperature measurement to provide an internal temperature checkpoint of fluid within the system. The sensor is exposed to the auxiliary path, with or without the use of a heat sink. Fluid is directed to a return path for motor cooling and then a secondary path through the housing to return to the outlet path or the pump inlet.

Description

CROSS-REFERENCE TO RELATED APPLICATION(S)

[0001] This disclosure claims priority to U.S. Provisional Patent Application No. 63 / 435,715, filed December 28, 2022, the entire contents of which are hereby incorporated by reference. BACKGROUND area

[0002] The present disclosure generally relates to a pumping system including a pump and a motor and a split output port for directing a portion of fluid / lubricant from an outlet path to a temperature sensor for controlling the same. Description of related technology

[0003] The temperature of oil or fluid in pumps is generally monitored to maintain safe pump operation. U.S. Publications Nos. 2019 / 0003477 and 2021 / 0123436, each incorporated herein in its entirety, illustrate examples of pumps with an auxiliary fluid passage or pathway for directing fluid to a temperature-sensing element. SUMMARY

[0004] One aspect of this disclosure is to provide an internal temperature checkpoint of fluid / lubricant within a pump within a pumping system or assembly to ensure safe and proper control and operation of the pump, as well as relatively higher efficiency of an associated motor.

[0005] Further aspects, features and advantages of the present disclosure will become apparent from the following detailed description, the accompanying drawings and the appended claims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 shows a schematic view of a pump system according to an embodiment of the disclosure. Fig. Figure 2 illustrates a cross-sectional view of an embodiment of parts of a pump system as in Fig. 1 shown. Fig. Figure 3 illustrates a detailed view of an inner rotor and an outer rotor used in the pump system of Fig. 2 to illustrate an inlet port, a new outlet port, and a new outlet groove therein, according to one embodiment. Fig. 4A-4G show a rotation of the parts from Fig. 3 and a displacement volume movement therein, with corresponding diagrams showing the rotation of the external gear (in degrees) versus the cross-sectional area (in mm 2 ), according to one embodiment. Fig. Figure 5 illustrates a cross-sectional view of another embodiment of parts of a pump system as in Fig. 1 illustrated according to another embodiment of this disclosure. Fig. Figure 6 illustrates a detailed view of an inner rotor and an outer rotor used in the pump system of Fig. 2 are provided to illustrate an inlet port, a new outlet port and a new outlet groove therein, according to another embodiment. Fig. 7A-7G show a rotation of the parts from Fig. 6 and a displacement volume movement therein, with corresponding diagrams showing the rotation of the external gear (in degrees) versus the cross-sectional area (in mm 2), according to one embodiment. Fig. Figure 8 shows an exploded view of a pump system and parts according to Fig. 2 and / or Fig. 5, including its housing and covers, according to one embodiment. Fig. 9 shows a cross-sectional view of the pump system from Fig. 8 as assembled, to show positions of journal bearings. Fig. Figure 10 shows a non-limiting embodiment of a sensor and heat sink that may be used in the disclosed pump system(s). DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

[0006] The following description, taken in conjunction with the accompanying drawings, is intended to describe various embodiments of the disclosed subject matter and is not necessarily intended to represent the only embodiment(s). In certain instances, the description includes specific details for the purpose of providing an understanding of the disclosed embodiment(s). However, it will be apparent to one skilled in the art that the disclosed embodiment(s) may be practiced without these specific details. In some instances, well-known structures and components may be shown in block diagram form to avoid obscuring the concepts of the disclosed subject matter.

[0007] References throughout the specification to "an (one) embodiment" mean that a particular feature, structure, or characteristic described in connection with an embodiment is included in at least one embodiment of the disclosed subject matter. Thus, the appearances of the phrase "in an (one) embodiment" in various places throughout the specification do not necessarily refer to the same embodiment. Further, the particular features, structures, or characteristics may be combined in one or more embodiments in any suitable manner. Further, it is intended that embodiments of the disclosed subject matter cover modifications and variations thereof.

[0008] It should be understood that terms such as "above," "below," "top," "bottom," "side," "upper," "lower," "inner," "outer," "inside," "outside," and the like, which may be used herein, merely describe points of reference and do not necessarily limit embodiments of the present disclosure to any particular orientation or configuration. Furthermore, terms such as "first," "second," etc., merely identify one of a number of sections, components, steps, operations, functions, and / or points of reference as disclosed herein and also do not necessarily limit embodiments of the present disclosure to any particular configuration or orientation, or any requirement that each number be included.

[0009] As understood by those skilled in the art, "pump displacement" or "displacement" as used throughout this disclosure refers to a volume of liquid or fluid (e.g., lubricant, oil) that a pump is capable of moving during a specific period of time, i.e., a flow rate. It should be noted that the terms "fluid" and "lubricant" may be used interchangeably throughout this disclosure.

[0010] As can be seen from the drawings and the following description, the disclosed pump system and method of operating the same includes a pump with a split outlet path that enables displacement-driven flow to a temperature measurement circuit (including a temperature sensing element or sensor). Consequently, this disclosure provides greater control over the amount of lubricant (e.g., oil) or fluid sent to an auxiliary circuit (compared to prior art devices such as a pressure relief port). In embodiments, the disclosed system may be designed to be pressure-independent, with a flow rate to the auxiliary circuit / temperature measurement and a cooling path being a percentage of the total displacement of the pump. Therefore, the disclosed system allows for auxiliary flow to be returned to the main path rather than recirculated to the inlet, providing less volumetric efficiency loss.

[0011] In one embodiment, the portion or percentage of auxiliary fluid flow of pressurized fluid through the auxiliary circuit is returned to the main path via the outlet path. In another embodiment, the portion or percentage of the auxiliary circuit may instead include a path that returns a portion of the return flow to the main path via the pump inlet.

[0012] Such configurations enable the management of engines, including knowledge of static and dynamic temperature(s) and a flow rate of oil / lubricant for cooling. Furthermore, the number of sensors used in the larger system (transmission, traction motor, etc.) is relocated from a conventional location (e.g., a position of an oil / fluid temperature sensor is relocated) in such a way that customer or user functionality is incorporated into the disclosed pumping system. Additionally, this disclosure provides a split output port and path in the pump that directs a portion of the output lubricant to the temperature sensor. Accordingly, the disclosed pumping system may be used in some embodiments to provide improved accuracy in the control of output and decisions (via the controller and / or processor) for lubrication.

[0013] Fig. 1 shows a schematic view of a pumping system 10 or pumping assembly according to an embodiment included herein. The pumping system 100 may include an electronic pump 102 or e-pump, also referred to herein simply as "pump 102." According to one non-limiting embodiment, the pumping system 100 may be a system or assembly such as described in U.S. Patent No. 10,808,697 (USSN: 15 / 653,690), which is hereby incorporated by reference in its entirety, i.e., a pumping assembly (or system) having an assembly inlet for inputting fluid, an assembly outlet for outputting fluid, an electric motor contained within a motor enclosure, a pump having a pump housing, a drive shaft connecting the electric motor to the pump, and a controller configured to drive the electric motor.In such an embodiment, the pump of the incorporated '697 application has an inlet for receiving input fluid from the assembly inlet and a transfer outlet for discharging pressurized fluid; the drive shaft is configured to be driven by the electric motor about an axis; and the pump and the electric motor are located on opposite axial sides of the controller. The pump assembly of the incorporated '697 application also includes a heat-conducting plate positioned between the pump and the controller for conducting heat from the controller; a transfer passage provided in the pump assembly for receiving the pressurized fluid discharged from the transfer outlet of the pump.pressurized fluid and for directing the pressurized fluid along and into contact with the heat-conducting plate to conduct heat therefrom into the pressurized fluid, and an outlet passage that puts the transfer path into communication with the assembly outlet to discharge the pressurized fluid. However, such an assembly or system of the incorporated '697 application is not limiting. Other pumping systems and / or features may be employed.

[0014] The pump system 100 includes a housing 28 flanked by covers 60, 62, which contains the pump 102 therein, which has a pump inlet 10 for receiving input fluid to direct the fluid to a pump inlet port 10A, and a pump outlet 14 for discharging pressurized fluid from a pump outlet port 14A or 14B. A drive shaft 18 (see, e.g., Fig. 2 and Fig. 6) is provided for rotation about an axis and for rotatably driving parts of the pump 102 to pressurize the input fluid received through a main path 12 [from the input fluid inlet 10] for discharge from an outlet path 15 to the outlet 14. Fig. Figure 8 shows an exploded view of a pump system 100 and parts according to Fig. 2 and / or Fig. 5, including its housing 28 and its covers (motor-side cover 60 and pump-side cover 62), according to one embodiment. The drive shaft 18 is, for example, Fig. 9 shown journal bearings 64 and 66.

[0015] From the main path 12 or the outlet path 15, a portion (or percentage) of the pressurized fluid or lubricant (of the total pump displacement) is directed to an auxiliary circuit 16, also referred to herein as a temperature sensing and cooling path 16 (or circuit), for temperature measurement. In one embodiment, this path 16 involves directing fluid / lubricant through an internal bore in the drive shaft 18 toward a heat sink 20 (optional) provided in the path for reading by a sensor 22 associated with an electronic control unit (ECU) or controller (described in more detail below). The sensor 22 may optionally be exposed directly to the path 16 instead of using the heat sink 20. However, the heat sink may optionally be used to conduct heat to the sensor 22 without the sensor 22 being directly exposed to the pumped fluid.The fluid / lubricant is then passed to a return path 24. The return path 24, in one embodiment, includes a return flow 26 for motor cooling and then a secondary path 25 through the pump housing 28 for returning fluid flow to the main path 12 via the outlet path 15 and then the outlet 14 (see, e.g., FIG. Fig. 2) of the pump 102. In an optional second embodiment, the return path 24 includes a return flow 26 for motor cooling and then a secondary path 27 through a pump housing for returning the return flow of fluid to the pump inlet 10 (see e.g. Fig. 5) and the main path.

[0016] The type of pump 102 and its parts provided in the pump system / assembly 100 is not limited. In one embodiment, the pump 102 has a gerotor drive, wherein an inner rotor 50, which in embodiments in Fig. 3 and in Fig. 6 in an axial view, is rotatably driven by the drive shaft 18 to in turn rotatably drive an outer rotor 52. The inner rotor 50 is fixedly secured to the shaft 18 for rotation about the axis A with the drive shaft 18. A pump end of the shaft 18 is positioned within the pump cover 62 adjacent to or adjacent the housing 28, which includes the pump inlet 10 and the pump outlet 14 therein. A motor end of the drive shaft 18 is positioned adjacent to or within a motor cover 60, shroud, or section. The outer rotor 52 is rotatably received in the pump housing and in particular the pump chamber 51 thereof (as in Fig. 2). The pumping chamber 51 and the outer surface of the outer rotor 52 are cylindrical. Those skilled in the art will appreciate that rotation of the inner rotor 50 also rotates the outer rotor 52 via their meshing teeth to pressurize the input fluid received in areas between the complementary parts for output from the pump 102, and thus, such details will not be described here. According to one non-limiting embodiment included herein, the inner rotor and outer rotor are part of a gerotor pump and are configured for operation such as that disclosed in the above-referenced and incorporated U.S. '697 patent. In another non-limiting embodiment, the inner rotor and outer rotor are part of a gerotor pump and are configured for operation such as that disclosed in U.S. Patent No. 5,722,815 (USSN: 08 / 515,054), also incorporated herein by reference in its entirety.

[0017] Other types of pump parts for pressurizing input fluid may also be used in the pump according to other embodiments, including gear pumps, and thus the pump 102 should not be limited to gerotor-type pumps.

[0018] As in each case Fig. 3 and Fig. 6, the inlet port 10A is provided, which receives input fluid from the pump inlet 10. For illustrative purposes only, an exemplary known or existing outlet port from the prior art is shown in dashed lines in the figures. Fig. 3 to illustrate the usual position thereof. However, in the disclosed embodiments, depending on the embodiment, a new outlet port and outlet groove are provided in the pump 102 to selectively utilize pressurized fluid within a displacement chamber and to direct a portion of the pressurized fluid to the auxiliary / temperature sensing and cooling path 16. For example, as in Fig. Figure 3 illustrates an outlet groove 40A provided between the inlet port 10A and the outlet port 14A of the pump (e.g., within the housing 28) so that within the displacement area 42 (hereinafter referred to as Fig. 4A-4F) pressurized fluid is directed from the inlet port 10A to and through the groove 40A before being discharged via the outlet port 14A. As described in Fig. 2, according to an embodiment contained herein, the groove 40A may be provided in or near the pump-side cover 62. The outlet groove 40A is provided in a generally linear shape with rounded edges. The inlet port 10A, the outlet port 14A, and the groove 40A are shown in the figure of Fig. 3 relatively below the rotors 50, 52, ie on the same side (eg under or below the gearbox) within the pump 102. In the embodiment of Fig. 6, the outlet groove 40B is provided between the outlet port 14B and the inlet port 10A, so that within the displacement area 42 (hereinafter referred to as Fig. 7A-7F), pressurized fluid is directed to and through the groove 40B after being discharged from the outlet port 14B before moving back to the inlet port 10A. The outlet groove 40B is generally L-shaped with rounded edges. As mentioned, the inlet port 10A, the outlet port 14B, and the groove 40B are shown in the figure of Fig. 6 is provided relatively below the rotors 50, 52, ie, on the same side (e.g., below or under the gearbox) within the pump 102. An additional description is provided below.

[0019] The pump system 100 also includes an electric motor 32 (in Fig. 2 and Fig. 5) and a motor drive shaft provided in the housing 28. In one embodiment, the electric motor 28 may be enclosed by a wall and / or within a motor enclosure that separates the motor parts and parts of the pump 102 within the housing 28. In embodiments, the motor drive shaft and the pump drive shaft 18 are the same drive shaft, i.e., a single shaft extending from the pump and through the motor. In another embodiment, the motor drive shaft and the pump shaft are different parts. The electric motor 32 is connected to the pump 102, the drive shaft of which is configured to be driven about an axis. The electric motor 32 is configured to drive the drive shaft 18 of the pump 102 via the motor drive shaft to rotatably drive parts of the pump 102, i.e., to pressurize the input fluid.

[0020] As in Fig. 2 and Fig. 5, an electronic control unit (ECU) or controller 34 is used to control the pumping system 100. The controller 34 is configured, among other features, to drive the pump drive shaft 18. In the illustrated embodiments, the ECU is shown in the form of a printed circuit board (PCB) 34 with electrical components thereon. As noted below, a temperature sensor 22 is mounted to / on the controller 34 or PCB. In one embodiment, the electric motor 32 is flanked by the controller 34 and the pump 102 in the pumping assembly / system 100.

[0021] Fig. 2 illustrates an embodiment of parts of a pump system 100 as in Fig. 1 and described above. As shown, the auxiliary circuit 16 includes a fluid passage defined in the pump outlet path 15, which diverges from the main path 12, at or near the pump outlet 14, for conveying lubricant to the sensor 22 for temperature measurement and cooling of the heat-generating components in the engine. In particular, the pump outlet path 15 includes the outlet groove 40A therein, which is selectively configured to discharge pressurized fluid during rotation of the pump parts (hereinafter referred to as Fig. 4A-4F). This outlet groove 40A thus assists in creating a split flow of fluid / lubricant that is passed from the outlet region (e.g., outlet passage 15) to a journal bearing end of the drive shaft 18, and thence upwardly within an internal bore of the drive shaft 18 to the heat sink pin 20 (to the sensor 22). Although a heat sink is illustrated, any type of transfer member or mechanism may be used to transfer lubricant to the sensor 22 for reading the temperature of the fluid, or fluid may be passed to the sensor itself. Fig. For example, Figure 10 shows a non-limiting embodiment of a heat sink configuration that may be used in the disclosed pump system(s) with sensor 22, including a (copper) shell filled with thermal paste and a glass bead type NTC.

[0022] The sensor 22 communicates with the electronic control unit (ECU) or controller (or processor) 34 used to control the pump system 100. In the illustrated embodiments, the sensor 22 is mounted on the printed circuit board (PCB) 34 in a specific position (i.e., repositioned to align with a specific path in the pump) adjacent or near the drive shaft 18. The thermal compound 30 may be provided between the sensor 22 and the heat sink 20. A gasket 31 may be used to secure the heat sink within a section or wall (e.g., the motor enclosure) within the housing 28.

[0023] Referring back to the circuit / path 16, lubricant, after flowing to the motor end of the drive shaft 18 and to the sensor 22, is then passed to the return path 24 to the pump outlet 14. As previously noted, in the embodiment of Fig. 2, the return path 24 comprises a return flow path 26 for motor cooling and then the secondary path 25 through the pump housing for returning to the outlet path 15 and then the outlet 14 of the pump 102. That is, the return path 24 is provided through the motor for conducting pressurized fluid in the auxiliary circuit and for cooling the motor, and the secondary path 25 through the housing for returning the fluid to the main path 12. The return path 24 may include multiple paths therein so that the fluid / lubricant is conducted through several locations of the motor parts. For example, the lubricant may be conducted through multiple paths through the rotor and stator components and across the motor, such as generally shown in Fig. 2 and Fig. 5. Such paths of the return path 24 may extend through the engine parts such that the lubricant is collected or directed to the pump housing 28 (positioned relatively below the engine in the illustrated drawings) and thus to the secondary path 25.

[0024] Of course, it should be understood that the auxiliary circuit 16 may also assist in drawing heat, i.e., cooling, of additional components within the pump system 100 or assembly. Such components may include, but are not limited to, cooling of the controller / ECU (via the flow of fluid / lubricant through path 16 and drawing heat therefrom and its components) and / or cooling of the housing components used to secure the motor components therein.

[0025] Fig. 4A-4G show a rotation of the rotors 50, 52 from Fig. 3 and a movement of a displacement volume in the chamber 42 therein relative to the inlet port 10A, the groove 40A and the outlet port 14A, with corresponding diagrams showing the rotation of the external gear 52 (in degrees) versus the cross-sectional area (in mm 2 ) according to one embodiment. As shown by the figures, the displacement volume in chamber 42 is varied via rotation of internal gear / rotor 50 relative to the rotation of external gear / rotor 52. Fig. Figure 4A illustrates a volume in chamber 42 with outer rotor 52 at 0 (zero) degrees (zero being chosen as a convenient reference point for discussing what happens during rotation). This discussion is provided for a single volume between a pair of rotor teeth, assuming this is cyclically repeated for all pairs of rotor teeth during the continued rotation of the rotors. As inner rotor 50 and outer rotor 52 rotate, chamber 42 moves across inlet port 10A as shown in Fig. 4B, communicates with the inlet port 10A and receives input fluid via the pump inlet 10, thereby increasing in volume and moving toward a maximum volume. The leading teeth or projections are engaged such that the chamber 42 is isolated from the groove 40A at this moment (where leading refers to the teeth / projections in front of the chamber 42 in the direction of movement). Fig. 4C, the fluid volume in chamber 42 is isolated from both inlet port 10A and groove 40A because the leading and trailing pairs of inner rotor teeth or projections mesh with each other at circumferential positions between inlet port 10A and groove 40A. The recessed U-shape or other inwardly directed projection 11 of inlet port 10A may optionally be provided to facilitate this isolation. As shown in Fig. As shown in Figures 4C-4D, a pressure spike occurs in the chamber 42 after the volume is isolated from the inlet port 10A (with maximized surface area and volume) and once the volume in the chamber 42 has begun to contract. The rotors 50, 52 continue to rotate and the isolated pressurized fluid / volume within the chamber 42 is then Fig. 4D, for discharge to the temperature sensing and cooling path 16, exposed to the groove 40A. Since the fluid is pressurized and open only to the groove 40A or the slot thereof, particularly before such fluid is exposed to the outlet port 14A, this results in a positive pressure displacement of the pressurized fluid through the path 16 / circuit. This is also noted in the corresponding diagram, which shows an increase in area / volume to the groove. As can be seen, the more the chamber 42 comes into communication with the groove 14, the more the chamber 42 is reduced, thereby applying positive pressure to the fluid therein, forcing it into the path 16 / circuit (and this pressure, in turn, drives it through the path, to the heat sink 22, etc.). Thereafter, the volume of fluid is then exposed to both the groove 40A and the outlet port 14A, as in Fig. 4E. Here, as depicted in the corresponding diagram, the fluid discharge area / volume reaches a maximum in the groove as discharge to the outlet port 14A begins. Since the opening to the outlet 14A is relatively small, the substantial pressure in the chamber 42 is directed to the groove 40A and the path 16 / circuit. Fig. Figure 4F shows further rotation of the rotors 50, 52, with the boundary of the chamber 42 then being restricted from discharging to the groove 40A, and instead discharging to the outlet port 14A. Discharge to the outlet port 14A approaches a maximum, while discharge to the groove (and to the inlet port 10A) is restricted due to the tooth / spike engagement between the rotating teeth. Further rotation results in further narrowing and discharge of the pressurized fluid from the chamber 42 through the outlet port 14A, as in Fig. 4G. As can be seen, each adjacent pair of teeth / processes creates such a chamber, and this is repeated throughout the entire rotation cycle.

[0026] In addition to the advantages and improvements described above, an embodiment such as in Fig. 2-4F, i.e., using an outlet flow to direct a portion of it through the circuit / path 16 and back to the outlet 14, compared, for example, to the usual flow from the outlet back to the inlet, equates to lower or minimal volumetric efficiency losses and provides pressure-independent flow. This is enhanced by the return path 24, as explained above, directing the oil from the path 16 to the outlet such that the oil or other fluid supplied for temperature sensing is also used as part of the outlet volume.

[0027] Fig. Figure 5 illustrates another embodiment of parts of a pump system as in Fig. 1 according to another embodiment of this disclosure. For clarity and brevity, like elements and components are designated by the same designation and numbering throughout the figures as described with reference to Fig. 2-4F. Thus, although this has been fully explained in detail here, it will be understood by those skilled in the art that various aspects of the system / arrangement Fig. 5-7F are analogous to the features previously discussed. Furthermore, it should be understood that the features depicted in each of the individual figures are not intended to be limited solely to the illustrated embodiments. That is, the features described throughout this disclosure may be interchanged and / or used with embodiments other than those depicted and / or described with reference thereto.

[0028] As mentioned, the auxiliary circuit 16 includes a fluid passage defined in the pump outlet path 15, which diverges from the main path 12, at or near the pump outlet 14, for conveying lubricant to the sensor 22 for temperature measurement and cooling. In particular, the pump outlet path 15 includes an outlet groove 40B therein that is selectively configured to discharge pressurized fluid during rotation of the pump parts (hereinafter referred to as Fig. 7A-7F). As described in detail in Fig. 5, for example, according to an embodiment included herein, the groove 40B may be provided in or near the pump-side cover 62. This outlet groove 40B thus assists in creating a split flow of fluid / lubricant that is passed from the outlet region (e.g., the outlet path 15) to a journal bearing end of the drive shaft 18, thence upward through its internal bore, to the heat sink pin (to the sensor 22) (or other transfer member or mechanism used to transfer lubricant to the sensor 22 for temperature reading). In this embodiment, however, the lubricant in the circuit / path 16, after flowing to the motor end of the drive shaft 18 and to the sensor 22, is then passed to the return path 24 to the pump inlet 10. As shown in Fig. As shown in Figure 5, the return path 24 includes a return flow path 26 for motor cooling and then a secondary return to the inlet path 27 through the pump housing to return fluid to the inlet 10 of the pump 102 and the main path. The pressure differential between the inlet path 27 and the groove 40B promotes flow through the auxiliary circuit 16 (i.e., the relative negative pressure of the inlet chamber draws fluid / lubricant through the circuit), but such flow is limited to the fixed percentage of the total pump displacement as defined by the port geometry.

[0029] Fig. 7A-7G show a rotation of the rotors 50, 52 from Fig. 5 and a movement of a displacement volume in the chamber 42 therein relative to the inlet port 10A, the groove 40B and the outlet port 14B, with corresponding diagrams showing the rotation of the external gear 52 (in degrees) versus the cross-sectional area (in mm 2) according to one embodiment. As shown by the figures, the displacement volume in chamber 42 is moved via rotation of internal gear / rotor 50 relative to the rotation of external gear / rotor 52. Fig. Figure 7A illustrates a volume in the chamber 42 with the outer rotor 52 at 0 (zero) degrees. As the inner rotor 50 rotates, the chamber 42 moves over the inlet port 10A as shown in Fig. 7B, and receives input fluid through the pump inlet 10, thereby increasing in volume as it moves towards the outlet port 14B. In Fig. 7C, the fluid volume in the chamber 42 is then exposed to the outlet port 14B for discharge thereto. This is also noted in the corresponding diagram, which shows an increase in surface area / volume to the outlet. As the rotors 50, 52 rotate, fluid continues to be discharged through the outlet port 14B, as shown in Fig. 7D. In Fig. 7E, the fluid volume in the chamber 42 is then isolated due to the engagement between the leading / trailing teeth / extensions of both the outlet port 14B and the groove 40B, the chamber 42 having a corrugated shape, the leading part of which is curved to face concavely outwards and the trailing part of which is curved to face concavely inwards, with a transition at the base of the leading tooth of the outer rotor 52. The rotors 50, 52 continue to rotate and the fluid / volume within the chamber 42 is then exposed to the groove 40B, as in Fig. 7F, for delivery to the temperature sensing and cooling path 16. Since the fluid is here only open to the groove 40B or slot thereof, and such exposure occurs only after delivery to the outlet port 14B, only a portion or percentage of the pump displacement is provided to the path 16 / circuit. This is also noted in the corresponding diagram, which shows an increase in area / volume to the groove. However, since the chamber 42 is now isolated from the outlet port 14B, the reduction in the volume of the chamber 42 creates an overpressure to assist in the delivery of the oil or other fluid therein into the groove 40B for delivery to the path 16 / circuit. Thereafter, the maximum amount of the remaining fluid volume is then determined as in Fig. 7G, the chamber 42 is exposed to the groove 40B, with the chamber 42 having contracted to provide the positive pressure. As depicted in the corresponding diagram, the fluid output area / volume reaches a maximum in the groove while the chamber 42 is isolated from the outlet port 14A and the inlet port 10A. Further rotation results in a further narrowing of the chamber 42 before the cycle begins again. Analogous to the previous embodiment, each adjacent pair of teeth / protrusions creates such a chamber, and this is repeated throughout the rotation cycle.

[0030] In the embodiment as in Fig. 5-7F, i.e., using an exhaust flow to direct a portion of it through the circuit / pathway 16 and to the inlet 10, the groove 40B and the main outlet 10 are completely separated from each other, resulting in less restrictive flow. As noted, there may be a volumetric efficiency loss with this configuration because only a portion or percentage of the pump displacement is sent to the circuit 16. The split outlet maintains flexibility to adapt the flow to the auxiliary circuit, although it is more pressure dependent. When the pressure differential is associated with the inlet (or suction) side of the pump, the amount of fluid or lubricant drawn through the auxiliary circuit 16 is more restricted because the amount or portion of fluid taken over by the exhaust flow depends on such differential.

[0031] The portion or percentage of the pump displacement / pressurized fluid provided to the auxiliary circuit or path 16 is not intended to be limited in amount or volume. In one embodiment, the percentage of fluid provided to the auxiliary circuit may range from about 1% to about 50%. In another embodiment, the percentage of fluid provided to the auxiliary circuit may range from about 1% to about 25%. In yet another embodiment, the percentage of fluid provided to the auxiliary circuit may range from about 1% to about 10%. In yet another embodiment, the percentage of fluid provided to the auxiliary circuit may range from about 1% to about 5%. In one embodiment, the percentage of fluid provided to the auxiliary circuit is about 5%.

[0032] It should be noted that a number of features of the auxiliary circuit have been depicted in a particular location in the drawings. However, it should be noted that elements of the auxiliary circuit may be moved without departing from the features and advantages disclosed herein. For example, according to one embodiment, the position of the sensor 22 and / or heat sink may be on an opposite side (e.g., left side) of the drive shaft and on the circuit board (as opposed to the right side, for example, in Fig.2). In one embodiment, the path 16 through the inner bore of the drive shaft 18 may, for example, include radially extending passage(s) that conduct fluid to the secondary path 25 of the pump housing. In yet another embodiment, instead of using an opening through the pump housing to define the secondary path 25, the secondary path may be a passage provided in the pump housing or cover, the passage being provided in the form of a recess in an underside thereof and facing an axial side of the pump such that fluid is conducted to / from the auxiliary circuit and the pump.

[0033] Furthermore, the illustrations and placement of the pump system 100 as depicted in the figures are not intended to limit the positioning or mounting of the pump system itself. That is, although the pump system 100 is depicted in a vertical position such that the controller is positioned above the motor, both of which are located above the pump, the pump system 100 and thus its housed components may be positioned at any number of angles other than those depicted in the figures. For example, the pump system 100 may be rotated 90 degrees to the right so that the pump inlet 10 and cover 62 are on the left and the controller 34 and cover 60 are on the right.

[0034] Although the principles of the disclosure have been made clear in the illustrative embodiments set forth above, it will be apparent to those skilled in the art that various modifications may be made to the structure, arrangement, proportion, elements, materials, and components used in the practice of the disclosure.

[0035] It will thus be apparent that the features of this disclosure have been fully and effectively attained. However, it should be understood that the foregoing preferred specific embodiments have been shown and described for the purpose of illustrating the functional and structural principles of this disclosure and are subject to change without departing from such principles. Therefore, this disclosure includes all modifications encompassed within the spirit and scope of the following claims. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] US 63 / 435,715

[0001] US 2019 / 0003477

[0003] US 2021 / 0123436

[0003] US 10,808,697

[0013] US 5,722,815

[0016]

Claims

[1] Pump system comprising: a housing with a pump and an electric motor inside; a pump inlet comprising a pump inlet port; a pump outlet comprising a pump outlet port; a drive shaft rotatably driven by the electric motor for driving portions of the pump to pressurize fluid received through a main path of the pump from the pump inlet for discharge from an outlet path to the pump outlet; a controller with a sensor on it, and an auxiliary temperature measurement circuit to provide an internal temperature checkpoint of fluid within the pump system, the auxiliary circuit being deviated from the main path of the pump and configured to direct a portion of the pressurized fluid to the sensor, and wherein the auxiliary circuit comprises a return path through the motor for conducting the pressurized fluid in the auxiliary circuit and for cooling the motor and a secondary path through the housing for returning the pressurized fluid to the main path. [2] The pump of claim 1, wherein the secondary path is configured to return the pressurized fluid to the main path via the outlet path. [3] The pump of claim 1, wherein the secondary path is configured to return the pressurized fluid to the main path via the pump inlet. [4] A pump system according to claim 1, wherein the auxiliary circuit includes a fluid passage defined in the outlet path of the pump. [5] The pump system of claim 1, wherein the auxiliary circuit includes a path through an internal bore in the drive shaft for directing the pressurized fluid to the sensor. [6] The pump system of claim 1, further comprising a heat sink within the auxiliary circuit, wherein the fluid is directed toward the heat sink for reading the temperature measurement by the sensor. [7] A pump system according to claim 1, wherein the pump is a gerotor-type pump comprising an inner rotor fixedly secured to the drive shaft for rotation therewith and an outer rotor rotatably received within the housing. [8] A pump system according to claim 7, wherein a displacement volume of fluid is provided within a chamber formed between teeth of the inner rotor and the outer rotor during rotation thereof. [9] The pump system of claim 8, further comprising an outlet groove positioned relatively below the pump and provided between the pump inlet port and the pump outlet port, configured to selectively receive a portion of the displacement volume of fluid within the chamber prior to discharge via the pump outlet port or the pump inlet port during rotation of the inner rotor and the outer rotor. [10] The pump system of claim 9, wherein the outlet groove comprises a generally linear shape extending radially relative to an axis of rotation of the drive shaft. [11] The pump system of claim 9, wherein the outlet groove comprises a corrugated shape. [12] A pump system according to claim 1, wherein the controller is provided in the form of a printed circuit board, and wherein the sensor is mounted thereon. [13] A method of directing fluid in a pumping system, the pumping system comprising the pumping system of claim 1, the method comprising: Collecting input fluid via the pump inlet port into the pump inlet and into the main path; rotatably driving the drive shaft using the electric motor to drive parts of the pump to pressurize the input fluid received through the main path; Directing the portion of the pressurized fluid to the auxiliary circuit and to the temperature measuring sensor; Directing the pressurized fluid to the return path through the engine for cooling the engine and the secondary path to return the pressurized fluid to the main path. [14] The method of claim 13, wherein the secondary path is configured to return the pressurized fluid to the main path via routing the outlet path. [15] The method of claim 13, wherein the secondary path is configured to return the pressurized fluid to the main path via the pump inlet. [16] The method of claim 13, wherein the auxiliary circuit includes a path through an internal bore in the drive shaft, and wherein the method comprises directing the pressurized fluid through the internal bore and to the sensor.

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