Starting stage of a self-limiting regenerative pumping element for a high-speed centrifugal motor fu

专利摘要:
A motor or pump fuel system includes a centrifugal pump having an impeller for transmitting energy to an associated fluid for an associated downstream engine fuel system. A regenerative start stage is in selective fluid communication with the pump. An ejector includes an input that communicates with the pump output and an output that communicates with the pump input. In addition, a control valve is interposed between the pump output and the regenerative start stage which selectively regulates the associated flow from the regenerative start stage. The associated method includes transmitting the flow from the centrifugal pump to a regenerative start stage to power an associated downstream flow circuit. During low speed start, a portion of the flow of the regenerative start stage is supplied to an ejector which recirculates it to an inlet of the centrifugal pump. Once the centrifugal pump provides a predetermined level of at least one of the flow and pressure requirements of the associated flow circuit, the method includes stopping flow from the regenerative start stage. Figure to be published with the abstract: Fig. 1
公开号:FR3078769A1
申请号:FR1902354
申请日:2019-03-07
公开日:2019-09-13
发明作者:Martin A. Clements
申请人:Eaton Intelligent Power Ltd；
IPC主号:

专利说明:

Description
Title of the invention: Start stage of a self-limiting regenerative pumping element for high speed centrifugal motor fuel pump and associated method
BACKGROUND The present invention relates to a fluid pump system, and in particular a pumping system requiring different ignition requirements. More particularly, the present invention relates to an aircraft engine fuel system which uses a high speed centrifugal pump, and one which responds to the need to effect an engine start, i.e., to provide a appropriate flow and pressure at low drive speed.
[0002] High speed centrifugal pumps have distinct advantages for minimizing the weight and the manufacturing cost of the fuel pump of an aircraft engine. For these reasons, fuel system designers have sought to incorporate the high-speed centrifugal pump into the fuel systems of aircraft engines. These attempts have most often proven to be inadequate due to the inability of the high speed centrifugal pump to start the engine. Indeed, starting the engine requires sufficient flow and sufficient pressure at a low drive speed. The assistance of a second engine or a starter pump is generally used to start the engine. In most cases, the second pump increases both the weight and the cost of the system, thereby questioning the reasons for using the centrifugal pump at high speed. Other problems arise from the need to disengage the starter pump so as not to create an excessive amount of pumping energy which must be absorbed as heat in the fuel system.
The systems previously proposed have undesirable modes which allow the regenerative stage to remain engaged in the pumping of fluid to the fuel system. In this case, prior systems which incorporate regenerative stages could undesirably produce system pressures far in excess of the needs of the system, and it would therefore be desirable to have an arrangement which automatically limits the production of pressure and protects against this makes the fuel system of a potential overpressurization.
There is a need for an improved arrangement which addresses at least one or more of the problems described above. Indeed, it would be desirable to provide a secondary pumping function for ignition purposes which would not jeopardize the advantages in terms of weight and cost of the high speed centrifugal pump, while profitably retaining the advantages and the beneficial effects of using the high speed centrifugal pump in an engine fuel system, which protects a fuel system from potential overpressurization. Summary [0005] A fuel system is provided, meeting the need for a secondary pumping function for ignition purposes, and not calling into question the advantages in terms of weight and cost of a large centrifugal pump. speed.
The engine fuel system uses a regenerative type pump element, an ejector pump and a series of valves to control the starting process in conjunction with the high speed centrifugal pump.
The pump or engine fuel system includes a pump having an inlet and an outlet which communicate with a rotary kinetic pumping element for transmitting energy to an associated fluid for an associated downstream flow circuit. A regenerative start stage is in selective fluid communication with the pump. An ejector includes an inlet which communicates with the pump outlet and an outlet which communicates with the pump inlet. In addition, a control valve is interposed between the pump outlet and the regenerative start stage which selectively controls the associated flow from the regenerative start stage.
The control valve communicates with the pump outlet and selectively directs the fluid therefrom to an inlet of the regenerative start stage.
The control valve responds to pressure signals from the pump outlet and upstream from the pump inlet.
The control valve is configured to monitor the flow rate of the pump output and supply the flow rate of the input to the regenerative start stage until the pump provides flow and / or pressure requirements. of the associated flow circuit.
The pump and the regenerative start stage can be driven in common by a first shaft.
The ejector receives the flow from the pump outlet.
The ejector communicates with the regenerative start stage to recover the fluid thereof once the pump provides the predetermined flow and / or pressure requirements for the associated flow circuit.
The ejector recirculates the flow from the pump outlet to the pump inlet.
The regenerative start stage is in fluid communication with both the ejector and the associated downstream flow circuit so that during ignition, the regenerative start stage transmits the flow both to the and the associated downstream engine fuel system.
The ejector receives the flow from the regenerative start stage during ignition and is configured to recirculate the flow from the regenerative start stage to the pump inlet.
The system provides a flow from the regenerative start stage until the pump provides at least one of the predetermined flow and pressure requirements of the associated downstream flow circuit, and thereafter the ejector discharges the fluid from the regenerative start stage and thereby decouples the regenerative start stage from the pump system.
The system further includes a first check valve downstream of the centrifugal pump outlet which is biased towards a closed position so that when it is in a closed position, the flow rate of the outlet of the centrifugal pump is directed to the regulating valve of the regenerative start stage.
The first non-return valve opens when the pump reaches at least one of the predetermined flow and pressure requirements of the associated downstream engine fuel system.
The system further includes a second check valve downstream of the regenerative start stage which allows the flow from the regenerative start stage during ignition.
A method of supplying a flow rate to an associated downstream flow circuit during ignition and transitioning the flow rate from a centrifugal pump is provided.
The method includes supplying fuel from a fuel source to the centrifugal pump. During a low speed start approximately less than 10% of the motor shaft speed, the method includes transmitting the flow from the centrifugal pump to a regenerative start stage in order to supply an associated engine fuel system ( flow circuit). During low speed starting, part of the flow from the regenerative starting stage is supplied to an ejector which recirculates it to an inlet of the centrifugal pump. Once the centrifugal pump provides a predetermined level of at least one of the flow and pressure requirements of the associated flow circuit, the method includes stopping the flow from the regenerative start stage to the flow circuit associated.
Once the centrifugal pump provides the predetermined level of at least one of the flow and pressure requirements of the flow circuit / associated engine fuel system, the ejector empties the fluid from the stage of regenerative start to isolate the regenerative start stage from the flow system / associated engine fuel system.
The method further includes transitioning the flow requirements for the associated engine fuel system from the initial delivery of flow from the regenerative start stage to the subsequent supply of the flow circuit / fuel system. associated motor from the centrifugal pump, wherein the transition occurs when an outlet pressure of the centrifugal pump exceeds a pressure outlet of the regenerative start stage.
Once the centrifugal pump provides the predetermined level of at least one of the flow and pressure requirements of the flow circuit / associated engine fuel system, the ejector empties the fluid from the stage of regenerative start to isolate the regenerative start stage from the flow system / associated engine fuel system.
The method further includes regulating the flow rate from the centrifugal pump through the regenerative start stage as a function of monitoring the outlet pressure of the pump and the inlet pressure to the centrifugal pump.
The method further includes driving the centrifugal pump and the regenerative start stage from a common shaft, and selectively reducing the power consumed by the regenerative start stage after ignition.
A main advantage relates to the reduction in the weight and the manufacturing cost of the aircraft engine fuel pump by using a high speed centrifugal pump with the help of a second arrangement of ignition pump which does not does not call into question the advantages of the centrifugal pump.
Another advantage lies in the ability to discharge the ignition pump stage from the system once at least one of an appropriate flow and pressure is supplied by the high speed centrifugal pump. .
Another advantage is associated with the ability to recover or evacuate the cavity of the ignition pump stage in order to effectively decouple the starter pump stage from the system.
Another advantage is the ability to protect the system by automatically limiting / limiting the potential for overpressurization.
Other beneficial effects and advantages of the present invention will become more evident by reading and understanding the detailed description which follows.
Brief description of the drawings [fig.l] [Eig. 1]
Ligure 1 is a schematic representation of the present invention.
[Fig.2] [Eig. 2]
Ligure 2 is a modified self-limiting regenerative pumping element for a high speed centrifugal motor fuel pump.
Detailed Description The following description referring to the accompanying drawing is provided to assist in the overall understanding of one or more embodiments of the present invention as defined by the claims and their equivalents. It includes various specific details to facilitate this understanding, but these details should be considered as merely exemplary. Thus, those skilled in the art recognize that various changes and modifications to the various embodiments described herein can be made without departing from the scope and spirit of the present invention. Various exemplary embodiments of the present invention are not limited to the specific details of the various embodiments and should be interpreted to include all changes and / or equivalents or substitutes included in the ideas and technological scope of the appended claims. In the description of the drawings, where possible, like reference numerals are used for like elements.
The terms "include" or "may include" used in the present invention indicate the presence of functions, operations, elements, etc. correspondents described and do not limit one or more of the functions, operations, elements, etc. additional. In addition, it should be understood that the terms "include", "including", "have" or "having" used in the present invention indicate the presence of components, characteristics, numbers, steps, operations, elements, parts, or a combination of these described in the specification, and do not exclude the presence or addition of one or more other characteristics, numbers, steps, operations, elements, parts, or a combination of these.
The terms "or" or "at least one of A and / or B" used in the present invention include any and all combinations of words listed with them. For example, "A or B" or "at least one of A and / or B" means including A only, including B only, or including both A and B.
Although terms such as "first" and "second" used in the present invention may modify various elements of the different exemplary embodiments, these terms do not limit the corresponding elements. For example, these terms do not limit an order and / or importance of the corresponding elements, and these terms do not exclude additional elements (eg, second, third, fourth, etc.). Terms can be used to distinguish one item from another. For example, a first mechanical device and a second mechanical device both indicate mechanical devices and can indicate different types of mechanical devices or the same type of mechanical device. For example, a first element can be named a second element without departing from the scope of the various exemplary embodiments of the present invention, and similarly, a second element can be named a first element.
It will be understood that, when an element is mentioned as being "connected" to or "coupled" to or "in communication" with another element in a functional manner, the element can be directly connected to, coupled to or in communication with another element, and it may be an intermediate element between the element and another element. On the contrary, it will be understood that, when an element is mentioned as being "directly connected", "directly coupled", or "in direct communication" with another element, there is no intermediate element between the element and another element.
The terms used in the various exemplary embodiments of the present invention are intended to describe specific exemplary embodiments and are not intended to limit different or various exemplary embodiments of the present invention. As used herein, singular forms are intended to also include plural forms, unless the context clearly indicates otherwise.
All the terms used here (including the technical and scientific terms) have the same meanings as those generally understood by a person skilled in the ordinary art in the associated technique, unless otherwise indicated. Terms defined in a generally used dictionary should be interpreted as having the same meanings as the contextual meanings of the relevant technology and should not be interpreted as having inconsistent or exaggerated meanings unless they are clearly defined in the various embodiments copies.
Figure 1 initially shows a fluid system 100, in particular a pumping system 110 requiring different ignition requirements. More specifically, a preferred embodiment of this system 100 is a flow circuit or an aircraft engine fuel system comprising the pump system 110. The pump system 110 preferably uses a high speed pump 112, for example example a centrifugal pump, having a pump inlet 114 and a pump outlet 116. A rotary kinetic pump element such as an impeller 118 is shown schematically in Figure 1. Those skilled in the art will appreciate that the impeller 118 is received for rotational movement relative to the centrifugal pump housing (not shown), and that the inlet 114 and outlet 116 are provided at desired locations in the housing and communicate with a pump cavity which receives the impeller. The centrifugal impeller is driven by a shaft 130 supported by appropriate bearings 132 in a manner well known in the art. Fluid, such as engine fuel, is supplied from an appropriate fluid source 134. Rotation of the impeller 118 through shaft 130 transmits energy to the fluid where pressurized fluid is supplied to a main flow system or an associated engine fuel system 136 through a fluid passage 138. The details of the main flow system / associated engine fuel system 136 are standard and are not part of this invention so further description is unnecessary here to fully understand the present invention. The impeller 118 is driven by a drive shaft 130 at high speed and can range, for example, from 0 rpm to about 35,000 rpm, although the rotational speed of the impeller should not be considered to limit the present invention.
As noted in the Context, fuel from a source 134 is supplied to a centrifugal pump to supply the main flow circuit / engine fuel system 136 downstream. There is, however, a need to respond to engine start-up or ignition problems, i.e. to provide adequate flow and pressure at a low drive speed, particularly when a rotary pump is used. light high speed such as the centrifugal pump 112 is used in the pumping system 100 and is not capable of providing sufficient flow and / or sufficient pressure at ignition speeds. The system 100 is modified as shown in Ligure 1 so that the centrifugal pump 112 provides flow under pressure through a first non-return valve 140 (where the non-return valve includes a biasing member or a conventional biasing spring 142 which imposes a predetermined closing force on a conventional spherical member 144) to the main flow circuit 136 through a fluid passage 138 and also provides a regenerative start stage or a regenerative pump 150 through a fluid passage 152 which receives a flow from the centrifugal pump upstream of the first non-return valve.
The regenerative pump 150 (sometimes called a regenerative turbine pump or peripheral pump) preferably has a rotary impeller 154 with vanes 156 on either side of a peripheral part thereof to generate a high pressure between an inlet / suction 158 and an outlet / exhaust 160. The regenerative start stage 150 is driven by the shaft 130 in the preferred embodiment, although it will be understood that a separate drive shaft could also be used. More particularly, the pressurized fluid coming from the centrifugal pump outlet 116 flows through the passage 152 towards the control valve 170 which is interposed between the centrifugal feed passage pump outlet 116 and the inlet 158 of the 'regenerative start stage. The regulating valve 170 controls, regulates, or limits the pressure output from the regenerative start stage 150 until the centrifugal pump 112 catches up, that is to say until the centrifugal pump provides at least one of sufficient flow and / or pressure required for the downstream flow system or the associated downstream engine fuel system 136. The regulating valve 170 receives pressure signals from upstream of the centrifugal pump 112 through a fluid passage 172 and also from the pump outlet 138 through a fluid passage 174. when the regulating valve 170 closes, the regenerative start stage 150 provides a flow under pressure during the ignition at the passage 138 through the second check valve 180 through a fluid passage 162. The second check valve 180 includes a biasing member or a biasing spring 182 which imposes a preselected closing force on a spherical member 184. In this way, the ignition rate of the regenerative start stage 150 feeds the main flow circuit 136 associated, until the centrifugal pump 112 has developed a sufficient flow and / or pressure to overcome the stressing force of the first non-return valve 140 and to feed from this makes the main flow circuit. At this time, the second non-return valve 180 closes to prevent the flow of fluid from the regenerative start stage 150 from supplying pressurized fluid to the associated downstream system 136.
In addition, once the centrifugal pump 112 supplies the main flow circuit, it is desirable to discharge the regenerative start stage since the fluid passing through it would otherwise add unwanted heat to the system. At the transition point where the outlet pressure of the centrifugal stage begins to be supplied to the main flow circuit, in addition to the opening of the first non-return valve, the flow of the regenerative start stage is reduced to zero by the closing the regulating valve 170. Thus, the additional flow rate of the centrifugal stage 112 does not reach the inlet 158 of the regenerative start-up stage 150. As also illustrated in FIG. 1, during the ignition part of the discharge flow from the pump 138 is directed as a source of motive flow to an ejector pump 200, namely a first port or an inlet port 202 thereof. A second orifice or outlet / evacuation orifice 204 recirculates the flow rate of the ejector 200 through a fluid passage 206 to supply the passage 208 which communicates with the inlet 114 of the centrifugal pump 112. As indicated above, a fluid passage 172 communicates with the supply passage 208 towards the regulating valve 170 so that once the regulating valve closes, all the flow from the ejector 200 recirculates towards the inlet 114 of the centrifugal pump 112. As the flow to the inlet orifice 202 of the ejector 200 is now provided by the centrifugal pump 112 after the opening of the non-return valve 140, the recovery orifice 210 of the ejector 200 now has the capacity to evacuate the pumping cavity from the regenerative stage. The withdrawal of the fluid from the pumping cavity of the regenerative stage pushes the pumping power consumed by the regenerative starting stage to be brought close to zero, thus effectively decoupling the regenerative starting stage 150 from the system 100. From this In this way, the pumping capacity for the flow circuit 136 passes efficiently from the regenerative start stage 150 to the centrifugal pump 112.
The system illustrated schematically in Figure 1 provides the secondary function or ignition pumping through the regenerative start stage 150 in a manner which does not question the advantages in terms of weight and cost of the high speed centrifugal pump 112. The combination of the regenerative start stage 150, the ejector pump 200, the control valve 170 and the check valves 140, 180 effectively controls the start process.
The associated method of supplying a flow to the main flow circuit during ignition and transition to the centrifugal pump is as follows. The fuel enters the high speed centrifugal pumping stage 112 at pressure levels created by the supply, i.e., the cell fuel system. The fuel is pressurized by the action of the centrifugal pump. In the case of starting at low speed, typically less than 10% of the speed of the shaft, the centrifugal stage 112 provides very little fuel pressurization. The fuel leaving the centrifugal stage 112 feeds both the regenerative starting stage 150 through the regulating valve of the starting stage 170, and the main flow circuit 136 by means of the first non-return valve 140.
The flow entering the regenerative start stage 150 is significantly pressurized by the regenerative pump element 154. This flow leaves the regenerative start stage through a second non-return valve 180 and enters the main flow circuit 136. The regulating valve 170 at the inlet of the regenerative stage 150 acts to slow down the flow supplied to the regenerative stage and thereby regulates the total pressure pumping system 100 during the Beginning phase. As the drive speed increases, the pressure output of the centrifugal stage approaches and ultimately exceeds the regulated output of the regenerative start stage 150. At the point where the output pressure of the centrifugal stage exceeds the pressure level of the main circuit (maintained by the regulated regenerative stage 150), the first non-return valve 140 opens and the flow is supplied by the centrifugal pump stage 112 to the main circuit 136. The flow of the stage regenerative start point is reduced to zero by completely closing the pressure regulator of the input of the regenerative stage 170.
When the flow of the regenerative ignition stage stops, the regenerative evacuation non-return valve 180 closes and isolates the regenerative start stage 150 from the system 100. At this point, the ejector pump 200 , which has always recovered the fluid from the evacuation of the regenerative start stage, now has the capacity to completely evacuate the pumping cavity from the regenerative stage. During the evacuation of the pumping cavity from the regenerative stage, the pumping power consumed by the regenerative starting stage 150 is brought close to zero, thus effectively decoupling the starting stage element.
The regenerative start stage 150 successfully produces a pressure at low speed, unlike the centrifugal stage 112. The outlet pressure of the regenerative start stage 150 is regulated during the acceleration of the speed of training. The centrifugal stage 112 is then fluidly connected without disturbing the pressure and the flow rate of the system. In addition, the regenerative start stage is freed from the rest of the system by evacuating the pump cavity and therefore does not subsequently add pump energy and excessive heat to the system.
Ligure 2 presents and describes a second embodiment. Similar reference numbers with a prime symbol as a suffix (’) refer to similar components, and new items will be referenced by new reference numbers. A fluid system 100 ’, in particular a pumping system 110’ requiring different ignition requirements is shown. More specifically, a preferred embodiment of this system 100 ’is a flow circuit or an aircraft engine fuel system comprising the pump system 110’. The pump system 110 ’preferably uses a high speed pump 112’, for example a centrifugal pump, having a pump inlet 114 ’and a pump outlet 116’. A rotary kinetic pump element such as an impeller 118 'is shown schematically in Figure 2. Those skilled in the art will appreciate that the impeller 118' is received for rotational movement relative to the centrifugal pump housing (not shown) , and that inlet 114 'and outlet 116' are provided at desired locations in the housing and communicate with a pump cavity which receives the impeller. The centrifugal impeller 118 'is driven by a shaft 130' supported by appropriate bearings 132 'in a manner well known in the art. Fluid, such as engine fuel, is supplied from a suitable 134 ’fluid source. The rotation of the impeller 118 'by the shaft 130' transmits energy to the fluid where the pressurized fluid is supplied for a main flow circuit or an associated engine fuel system 136 'through a fluid passage 138 '. The details of the main flow circuit / associated engine fuel system 136 ’are conventional and are not part of the present invention, so further description is unnecessary here to fully understand the present invention. The impeller 118 'is driven by a high-speed drive shaft 130' and can range, for example, from 0 rpm to about 35,000 rpm, although the rotational speed of the impeller should not not be considered to limit the present invention.
As noted in the Background, fuel from a source 134 ’is supplied to a centrifugal pump to supply the main flow circuit / engine fuel system 136’ downstream. There is, however, a need to respond to engine start-up or ignition problems, i.e. to provide adequate flow and pressure at a low drive speed, particularly when a rotary pump is used. light high speed such as the centrifugal pump 112 'is used in the pumping system 100' and is not capable of providing sufficient flow and / or sufficient pressure at ignition speeds. The system 100 'is modified as shown in Ligure 2 so that the centrifugal pump 112' provides a flow under pressure through a first non-return valve 140 '(where the non-return valve includes a biasing member or a conventional biasing spring 142 'which imposes a predetermined closing force on a valve or a conventional spherical member 144') to the main flow circuit 136 'through a fluid passage 138'. Upstream of the first check valve 140 ’is a pressure signal line 152’ which connects to a control valve 170 ’as described in more detail below.
A regenerative start stage or a 150 'regenerative pump (sometimes called a regenerative turbine pump or peripheral pump) is provided. The regenerative pump 150 'preferably has a rotary impeller 154' with vanes 156 'on either side of a peripheral part thereof to generate a high pressure between an inlet / suction 158' and an outlet / evacuation 160 '. The regenerative start stage 150 'is driven by the shaft 130' in the preferred embodiment, although it will be understood that a separate drive shaft could also be used. More particularly, the fluid from the source 134 ′ flows through the passage 174 ′ towards the regulating valve 170 ′ which communicates with the inlet 158 ′ of the regenerative start stage. The regulating valve 170 'controls, regulates, or limits the pressure output from the regenerative start stage 150' until the centrifugal pump 112 'catches up, that is to say until the centrifugal pump provides at least one of sufficient flow and / or pressure required for the downstream flow system or the associated downstream engine fuel system 136 '. Specifically, the regulating valve 170 'receives pressure signals from upstream of the centrifugal pump 112' through a fluid passage 172 'and also from the pump outlet 116' through a passage of fluid 152 '. Until the regulating valve 170 'closes (when sufficient pressure is supplied by the signal passage 152' to push the valve member or the valve spool 176 'to a closed position which overcomes the force spring biasing 178 'in the control valve), the regenerative start stage 150' supplies a pressurized flow during ignition to the passage 138 'through the second non-return valve 180' through a passage fluid 162 '. The second non-return valve 180 ’includes a biasing member or a biasing spring 182’ which imposes a preselected closing force on a spherical member 184 ’. In this way, the ignition flow from the regenerative start stage 150 'feeds the associated main flow circuit 136', until the centrifugal pump 112 'has developed sufficient flow and / or pressure to overcome the biasing force of the first non-return valve 140 'and thereby supply the main flow circuit. At this time, the second check valve 180 'closes to prevent the flow of fluid from the regenerative start stage 150' from supplying pressurized fluid to the associated downstream system 136 '.
In addition, once the centrifugal pump 112 ’supplies the main flow circuit, it is desirable to discharge the regenerative start stage 150’ since the fluid passing through it would otherwise add undesirable heat to the system. At the transition point where the outlet pressure of the centrifugal stage begins to be supplied to the main flow circuit, in addition to the opening of the first non-return valve 140 ', the flow of the regenerative start stage is reduced to zero by closing the regulating valve 170 '. Thus, the additional flow rate of the fluid source 134 "does not reach the inlet 158" of the regenerative start stage 150 ". As also illustrated in FIG. 2 ', during ignition, part of the flow in the fluid line 138' is transmitted as a source of motive flow to an ejector pump 200 ', namely a first orifice or a entry 202 'from it. A second outlet or outlet / outlet orifice 204 'recirculates the flow rate of the ejector 200' through a fluid passage 206 'to supply the passage 208' which communicates with the inlet 114 'of the 112 'centrifugal pump. As indicated above, once the regulating valve 170 'closes, all the flow from the ejector 200' recirculates towards the inlet 114 'of the centrifugal pump 112'. As the flow to the inlet port 202 'of the ejector 200' is now supplied by the centrifugal pump 112 'after the opening of the non-return valve 140', the recovery port 210 'of the ejector 200' now has the capacity to evacuate the pumping cavity from the regenerative stage. The withdrawal of the fluid from the pumping cavity of the regenerative stage pump 150 'pushes the pumping power consumed by the regenerative starting stage to be brought close to zero, thus effectively decoupling the regenerative starting stage 150' from the 100 'system. In this way, the pumping capacity for the flow circuit 136 ’passes efficiently from the regenerative start stage 150’ to the centrifugal pump 112 ’.
Thus, in this second embodiment of Figure 2, the fluid is supplied to the inlet of the regenerative stage from the pressure of the pump inlet rather than from the discharge of the centrifugal stage ( Figure 1). In doing so, the complete filling of the regenerative stage 150 'takes place only up to a certain shaft speed based mainly on, for example, the diameter of the regenerative wheel and the inlet pressure of the pump, which does not change with the speed of the pump. Therefore, a wheel diameter can be adapted or matched with the desired stopping speed of the regenerative start stage, thereby automatically limiting the pressure generation process and protecting the fuel system from overpressurization.
The system illustrated schematically in Figure 2 provides the pumping or secondary ignition function through the regenerative start stage 150 'in a way that does not affect the advantages in terms of weight and cost of the high speed centrifugal pump 112 '. The combination of the regenerative start stage 150 ', the ejector pump 200', the regulating valve 170 'and the non-return valves 140', 180 'effectively controls the start process, and advantageously does so by a way that limits the pressure generation process and thereby protects the fuel system from overpressurization.
The associated method of providing a flow rate to the main flow circuit during ignition and transition to the centrifugal pump in relation to the embodiment of Ligure 2 is as follows. Fuel enters the 112 ’high-speed centrifugal pumping stage at feed pressure levels, the cell fuel system. The fuel is pressurized by the action of the centrifugal pump. In the case of starting at low speed, typically less than 10% of the shaft speed, the centrifugal stage 112 ’provides very little fuel pressurization. The fuel leaving the centrifugal stage 112 'feeds the main flow circuit 136' through the first non-return valve 140 ', and also provides a pressure signal to the regulating valve 170'.
The flow entering the regenerative start stage 150 'through a passage 174' of the supply of the cell fuel system 134 'is pressurized significantly by the regenerative pump element 154 '. This flow leaves the regenerative start stage via a second non-return valve 180 ’and enters the main flow circuit 136’. The regulating valve 170 ’at the inlet to the regenerative stage 150’ acts to slow the flow rate supplied to the regenerative stage and thereby regulates the pumping system under total pressure 100 ’during the start-up phase. As the drive speed increases, the pressure output of the centrifugal stage 112 'approaches and ultimately exceeds the regulated output of the regenerative start stage 150'. At the point where the outlet pressure of the centrifugal stage exceeds the pressure level of the main circuit (maintained by the regulated regenerative stage 150 '), the first non-return valve 140' opens and the flow is supplied by l 'centrifugal pump stage 112' to the main circuit 136 '. The flow rate from the regenerative start stage 150 'is reduced to zero by completely closing the inlet pressure regulator of the regenerative stage 170' as a result of the increased pressure of the outlet 116 'of the centrifugal stage 112 'via a signal line 152' acting on the valve slide 176 'to overcome the force of the spring 178'.
When the flow of the regenerative ignition stage 150 'stops, the regenerative evacuation check valve 180' closes and isolates the regenerative start stage 150 'from the system 100'. At this point, the 200 ’ejector pump, which has always recovered the fluid from the regenerative start stage discharge, now has the capacity to completely evacuate the pump cavity from the regenerative stage. During the evacuation of the pumping cavity from the regenerative stage, the pumping power consumed by the regenerative starting stage 150 ’is brought close to zero, thus effectively decoupling the starting stage element.
The regenerative start stage 150 ’successfully produces pressure at low speed, unlike the centrifugal stage 112’. The output pressure of the regenerative start stage 150 ’is regulated during the acceleration of the drive speed. The centrifugal stage 112 ’is then connected in a fluid manner without disturbing the pressure and the flow rate of the system. In addition, the regenerative start stage 150 'is released from the rest of the system by evacuating the pump cavity and therefore does not subsequently add excessive pump energy and heat to the system.
This written description uses examples to describe the invention, including the best mode, as well as to allow the person skilled in the art to make and use the invention. Other examples which appear to a person skilled in the art are intended to enter the field of application of the invention if they have structural elements which do not differ from the same concept, or if they include structural elements equivalent with negligible differences.

权利要求:
Claims (1)
[1" id="c-fr-0001]
[Claim 1] [Claim 2] [Claim 3] [Claim 4] [Claim 5] [Claim 6] [Claim 7] [Claim 8]
claims
Pump system comprising:
a pump including an inlet and an outlet which communicate with a rotary kinetic pumping element to transmit energy to an associated pump fluid directed to an associated downstream flow circuit; a regenerative start stage in selective fluid communication with the pump;
a valve which prevents fluid communication between the pump outlet and the associated downstream flow circuit until the pump reaches one of a predetermined pressure or flow threshold;
an ejector having an inlet which communicates with the pump outlet and an outlet which communicates with the pump inlet; and a control valve which selectively regulates the fluid associated with the regenerative start stage, wherein the valve responds to a signal taken between the pump output and the valve.
The pump system of claim 1 wherein the control valve also responds to a second pressure signal from upstream of the pump inlet.
The pump system of claim 1 wherein the control valve is configured to provide an input flow to the regenerative start stage until the pump provides at least one of the predetermined flow and pressure requirements the associated downstream flow circuit.
The pump system of claim 1 wherein the control valve receives flow directly from a source of system fluid.
The pump system of claim 1 wherein the ejector receives flow from the stage from the regenerative start stage during ignition.
The pump system of claim 1 wherein the ejector recirculates a flow from the pump outlet to the pump inlet.
The pump system of claim 1 wherein the regenerative start stage transmits flow to both the ejector and the associated downstream flow circuit during ignition.
The pump system of claim 7 wherein the ejector receives a flow from the regenerative start stage during ignition and is configured to recirculate the flow to the pump inlet.
[Claim 9] [Claim 10] [Claim 11] [Claim 12] [Claim 13] [Claim 14]
The pump system of claim 8 wherein the ejector receives flow from the regenerative start stage until the pump provides at least one of the predetermined flow and pressure requirements of the associated downstream flow circuit , and thereafter the ejector discharges fluid from the regenerative start stage and thereby decouples the regenerative start stage from the pump system.
The pump system of claim 1 wherein the regenerative start stage receives system fluid through the control valve in an open position of the valve.
Method for supplying a flow to a flow circuit during ignition and for transitioning the flow from a centrifugal pump, the method comprising:
supplying fuel from a fuel source to the centrifugal pump;
during low-speed starting approximately less than 10% of the motor shaft speed, transmitting the flow from the fuel source to a regenerative start stage to supply an associated downstream flow circuit;
during low-speed starting, part of the flow coming from the regenerative starting stage is supplied to an ejector which recirculates it towards an inlet of the centrifugal pump; and once the centrifugal pump provides a predetermined level of at least one of the predetermined flow and pressure requirements of the associated flow circuit, stopping the flow from the regenerative start stage to the main flow circuit associated.
The method of claim 11 wherein when the centrifugal pump provides the predetermined level of at least one of the flow and pressure requirements of the associated downstream flow circuit, the ejector removes fluid from the regenerative start stage to isolate the regenerative starting stage from the system.
The method of claim 12 wherein a transition of flow requirements for the flow circuit initially includes providing pressure flow from the regenerative start stage and subsequently providing pressure flow from the centrifugal pump , and the transition occurs when a pressure output from the centrifugal pump exceeds a pressure output from the regenerative start stage.
The method of claim 13 wherein when the centrifugal [claim 15] [claim 16] pump provides the predetermined level of at least one of the flow and pressure requirements of the associated downstream flow circuit, the ejector empties the fluid from the regenerative start stage to isolate the regenerative start stage from the associated flow circuit.
The method of claim 11 further comprising regulating a flow rate from the fuel source through the regenerative start stage as a function of monitoring a pressure difference between an inlet and outlet pressure of the pump centrifugal.
The method of claim 11 further comprising driving the centrifugal pump and the regenerative start stage from a common shaft, and selectively reducing the power consumed by the regenerative start stage after ignition.

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同族专利:

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公开号 | 公开日

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US20190277233A1|2019-09-12|

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US10907598B2|2021-02-02|

引用文献:

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GB1392783A|1973-02-06|1975-04-30|Texaco Development Corp|Reaction propulsion engine and method of operation|

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WO2007095047A2|2006-02-09|2007-08-23|Argo-Tech Corporation|Regenerative pumping element start stage for high-speed centrifugal pump|GB2597563A|2020-03-04|2022-02-02|Eaton Intelligent Power Ltd|Regenerative pump start and actuation stage for high-speed centrifugal fuel pump|

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GB2594145A|2020-03-04|2021-10-20|Eaton Intelligent Power Ltd|Single wheel multi-stage radially-layered regenerative pump|

法律状态:
2020-02-20| PLFP| Fee payment|Year of fee payment: 2 |

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2021-02-18| PLFP| Fee payment|Year of fee payment: 3 |

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2021-12-03| PLSC| Publication of the preliminary search report|Effective date: 20211203 |

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2022-02-21| PLFP| Fee payment|Year of fee payment: 4 |

优先权:

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申请号 | 申请日 | 专利标题

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US201862639745P| true| 2018-03-07|2018-03-07|

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US62/639745|2018-03-07|

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US201862666905P| true| 2018-05-04|2018-05-04|

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US62/666905|2018-05-04|

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