EP3480460B1 - Volumetric pump - Google Patents
Volumetric pump Download PDFInfo
- Publication number
- EP3480460B1 EP3480460B1 EP17382733.8A EP17382733A EP3480460B1 EP 3480460 B1 EP3480460 B1 EP 3480460B1 EP 17382733 A EP17382733 A EP 17382733A EP 3480460 B1 EP3480460 B1 EP 3480460B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- diaphragm
- volumetric pump
- sub
- linear actuator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000012530 fluid Substances 0.000 claims description 28
- 238000004891 communication Methods 0.000 claims description 9
- 239000002775 capsule Substances 0.000 claims description 4
- 230000008878 coupling Effects 0.000 claims description 4
- 238000010168 coupling process Methods 0.000 claims description 4
- 238000005859 coupling reaction Methods 0.000 claims description 4
- 230000001681 protective effect Effects 0.000 claims description 4
- 239000007787 solid Substances 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 238000000908 micropen lithography Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 239000013590 bulk material Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- -1 dimensions Substances 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0081—Special features systems, control, safety measures
- F04B43/009—Special features systems, control, safety measures leakage control; pump systems with two flexible members; between the actuating element and the pumped fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/04—Pumps having electric drive
- F04B43/043—Micropumps
- F04B43/046—Micropumps with piezoelectric drive
Definitions
- the invention refers to a mechanical pump for application in spacecraft, in particular in active thermal control systems, namely in Mechanically Pumped Driven Loops (MPDL) also known as Mechanically Pumped Loops (MPL).
- MPDL Mechanically Pumped Driven Loops
- MPL Mechanically Pumped Loops
- the thermal control of spacecraft equipment is an important feature of the spacecraft overall functionality, being one of the main thermal loads the heat generated at the electronic components.
- PTC passive thermal control
- ATC active thermal control
- Passive thermal control does not involve moving parts and relies solely on conductive and radiative heat paths to achieve thermal management, using components such as heat pipes, coatings, multi-layer insulation (MLI), sun shields, radiating fins, etc.
- Active thermal control requires input power and is commonly used in applications involving high heat loads.
- a mechanically pumped loop is an active thermal control (ATC) technique that uses a pumping device (a centrifugal or positive displacement pump) to move a fluid within a closed hydraulic circuit (loop).
- the fluid absorbs heat from a source (components that dissipate heat) and transfers it to a sink (an external surface that rejects heat to space by radiation).
- Mechanically pumped loops can be categorized as single-phase loops or two-phase loops.
- MPL Mechanically Pumped Loops
- centrifugal pumps are not suitable for double-phase loops since they are not self-priming, which are the current trends of the developments due to their higher heat transfer capacity and thermal stability.
- a reliable and durable mechanical pump would be desirable, in order to allow the application of MPL technology to high-capacity long-life applications, such as unmanned missions, serving telecommunications platforms, nuclear facilities, or any environment where reliability requirements are particularly high.
- Diaphragm pumps are devices with no tribological issues due to dynamic seals or any other friction elements, so they offer some advantages with respect to the aforementioned documents.
- the linear actuators used in these devices cannot provide the required strokes against the high-pressure forces typical of the applications indicated above and for the long-life demanded, so the person skilled in the art would not be prompt to use any of these devices as a solution for this problem.
- EP2930363 A1 discloses a piezoelectric pump for use in a pressurised circuit, comprising a pump chamber, a pressure chamber and a pump diaphragm closing one end of the pump chamber such that the pressure chamber is defined at the side of the pump diaphragm facing away from the pump chamber.
- the invention provides a solution for this problem by means of a volumetric pump according to claim 1 or 6.
- Preferred embodiments of the invention are defined in dependent claims.
- the invention provides a volumetric pump comprising
- the invention provides a volumetric pump comprising:
- the proposed invention improves the performance with respect to other volumetric pumps because of the absence of friction and dynamic seals, thereby increasing the reliability and extending its lifetime and being specially indicated for spacecraft applications, including unmanned missions.
- the difference between the pressure at both sides of the diaphragm is only the differential pressure caused by the compression, but the diaphragm and, therefore, the actuator, have not to withstand the total fluid pressure. This also improves the lifetime of the pump.
- first diaphragm is clamped to the chamber does not exclude the possibility that both the first diaphragm and the chamber are manufactured together as a single part. This only makes reference to the fact that the diaphragm does not rotate or pivot with respect to the chamber, but the rotation is also restricted.
- the linear actuator is connected to the diaphragm by means of a coupling device.
- the linear actuator is a piezoelectric actuator.
- the linear actuator is a magnetostrictive actuator.
- This kind of actuators provide strokes in similar ranges to the piezoelectric actuators with lower actuation voltages and have potentially higher lifetimes since they are made of bulk material actuated electromagnetically.
- the first diaphragm has a central portion with a central thickness greater than the thickness in any point outside the central portion.
- This central reinforcement of the diaphragm improves the efficiency of the pump, since it maximizes the volume displacement by limiting the diaphragm deformation.
- This arrangement is a way of defining a secondary sub-chamber between two diaphragms, the linear actuator being configured to move the two diaphragms as a single piece, since they are solidly attached.
- the linear actuator is therefore kept outside the contact with the fluid, being a single way of preserving it from an aggressive environment.
- the second diaphragm has a lower surface than the first diaphragm.
- the coupling device comprises a protective capsule around the linear actuator, the linear actuator being located inside the secondary sub-chamber, so that the linear actuator is adapted to move the first diaphragm without being in direct contact with the working fluid of the secondary sub-chamber.
- the inlet and/or the outlet valve comprises
- valves of these embodiments are aimed for simplicity and reliability, since no electronic parts or controlled elements are present; the valves of these embodiments are passive valves, and are therefore less prone to be damaged.
- the inlet valve and/or the outlet valve is operated by a secondary piezoelectric actuator.
- valve of these embodiments are aimed for better performance, since the valve of these embodiments may be synchronized with the movement of the main actuator, not depending on fluid-dynamic effects.
- Figure 1 shows an exploded view of a first embodiment of a volumetric pump 1 according to the invention.
- This volumetric pump 1 comprises
- the chamber 2 comprises a compensation port 26, intended to provide fluid communication between one of the sub-chambers and the inlet port 23.
- Figure 2 provides a side cross section of such a volumetric pump 1. In this figure, the internal arrangement of each element may be seen.
- the chamber 2 is divided into a main sub-chamber 21 and a secondary sub-chamber 22 by means of the first diaphragm 5.
- the first diaphragm 5 has a first face 51 oriented towards the main sub-chamber 21 and a second face 52 opposite to the first face 51, being therefore oriented towards the secondary sub-chamber 22.
- An outer edge 53 of the first diaphragm 5 is clamped to the chamber, thus dividing the chamber 2 into a main sub-chamber 21 and a secondary sub-chamber 22.
- Both the main sub-chamber 21 and the secondary sub-chamber 22 are intended to be full of working fluid, so the difference between the pressure in the first face 51 and the second face 52 of the first diaphragm 5 is only due to the differential pressure provided by the first diaphragm movement.
- the inlet port 23, covered by the inlet valve 31, and the outlet port 24, covered by the outlet valve 32, are located in the main sub-chamber 21.
- the inlet port 23 is in fluid communication with the pump inlet 25, where the working fluid enters the pump system.
- the first diaphragm 5 has a central portion 54 with a thickness which is greater than the thickness in any point outside the central portion 54.
- a compensation port 26 located in the secondary sub-chamber 22 is intended to provide a fluid communication between the secondary sub-chamber 22 and the inlet port 23, so that the pressure at both sides of the first diaphragm 5 (i.e., in the main and secondary sub-chambers) is similar, and, as mentioned above, only differs due to the differential pressure provided by the first diaphragm movement.
- the secondary sub-chamber is limited between the first diaphragm 5 and a second diaphragm 7.
- This second diaphragm 7 is solidly attached to the first diaphragm 5 by means of a rigid shank 91, so that the first diaphragm 5, the shank 91 and the second diaphragm 5 constitute a single element. Both the first diaphragm 5 and the second diaphragm 7 are clamped to the inner wall of the chamber 2 in two different zones, thus limiting their movements.
- the linear actuator 6 does not need to be isolated from the working fluid, since it is located outside the secondary sub-chamber 22. It contacts the second diaphragm 7 and, since this second diaphragm 7 constitutes a single element with the first diaphragm 5 by the solid attachment with the shank 91, the linear actuator 6 is able to move the first diaphragm 5 without a direct contact.
- Figure 3 shows a cross section of a second embodiment, which has some differences with respect to the first embodiment shown in Figure 2 .
- the chamber 2 is a closed cavity, and is divided into two sub-chambers by the first diaphragm.
- the linear actuator 6 is located inside the secondary sub-chamber 22, inside a protective capsule 92 which isolates the linear actuator 6 from the working fluid which fills the secondary sub-chamber 22. This protective capsule 92 does not prevent the linear actuator 6 from acting over the first diaphragm 5, transmitting the linear reciprocating movement thereto.
- Figures 4a and 4b show a cross section of the volumetric pump 1 of Figure 2 , so that its operation may be observed.
- the embodiment shown in Figure 3 works in the same manner.
- the displacement of the first and second diaphragms 5, 7 has been exaggerated for the sake of understanding the working principle.
- the inlet valve 31 and the outlet valve 32 are arranged to control the flow across the inlet port 23 and the outlet port 24 respectively.
- the linear actuator 6 is arranged to cause an alternating displacement in the single element constituted by the first diaphragm 5, the rigid shank 91 and the second diaphragm 7, at an operation frequency, thus causing a variation in the volume comprised within the main sub-chamber 21, as may be observed in the difference between Figures 4a and 4b .
- the variation of the volume comprised in the main sub-chamber 21 is caused by the elastic deformation of the first diaphragm 5, since the outer edge 53 thereof is clamped to the main chamber 2 and does not displace during this volume variation.
- FIG. 5 shows a detail of the inlet valve 31.
- the outlet valve has an analogue structure. In these figure, the following elements may be observed:
- valves 31 and/or 32 are operated by a secondary piezoelectric actuator instead.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Description
- The invention refers to a mechanical pump for application in spacecraft, in particular in active thermal control systems, namely in Mechanically Pumped Driven Loops (MPDL) also known as Mechanically Pumped Loops (MPL).
- The thermal control of spacecraft equipment is an important feature of the spacecraft overall functionality, being one of the main thermal loads the heat generated at the electronic components.
- Spacecraft thermal control techniques can be classified as passive thermal control (PTC) or active thermal control (ATC). Passive thermal control does not involve moving parts and relies solely on conductive and radiative heat paths to achieve thermal management, using components such as heat pipes, coatings, multi-layer insulation (MLI), sun shields, radiating fins, etc. Active thermal control requires input power and is commonly used in applications involving high heat loads.
- A mechanically pumped loop (MPL) is an active thermal control (ATC) technique that uses a pumping device (a centrifugal or positive displacement pump) to move a fluid within a closed hydraulic circuit (loop). The fluid absorbs heat from a source (components that dissipate heat) and transfers it to a sink (an external surface that rejects heat to space by radiation). Mechanically pumped loops can be categorized as single-phase loops or two-phase loops.
- Mechanically Pumped Loops (MPL) are robust and reliable systems that provide efficient heat transfer capacity for relatively higher power dissipation requirements and wider temperature ranges than other techniques, along with other advantages such as the distribution flexibility and ease of integration into the spacecraft, predictable thermal performance and scalability. Moreover, the coolant can be selected to match the required thermal environment. Double-phase MPLs provide a more interesting thermal control mass budget when compared with the single-phase fluid loop as they are more weight-effective, being capable of achieving large heat transfer rates with much less pumping power that single-phase fluid loops.
- Initial developments of MPLs for space use have implemented single-phase loops featuring centrifugal pumps. However, the output of a centrifugal pump fluctuates with the pressure variations; additionally, they have a very limited capability of dealing with high vapor volume fractions in the flow, which can lead to gas-locking of the pump can with the consequent loss of functionality. Therefore, centrifugal pumps are not suitable for double-phase loops since they are not self-priming, which are the current trends of the developments due to their higher heat transfer capacity and thermal stability.
- Some solutions have been already proposed, such as the lobe pump
FR 2824366 EP 2264317 B1 . However, these rotary pumps sustain necessarily friction and wear (at the guiding of the shafts or the contact of the gears), compromising the durability of the pump. Rotary seals are also a critical component which is likely to fail in the long-term operation due to tribological issues. These limitations are common to all the positive displacement pumps of the rotary type, and similar issues preclude screw and piston pumps for long life spacecraft applications. The reciprocating pump proposed inUS 6345963 B1 has potentially limited lifetime due to the intrinsic stress concentration of the metal bellows upon which it is based and the relatively large static pressures required; additionally, the vortex diode valves have shown very low efficiencies in general, which could be allowed, but cannot withstand full-gas flow, which is a stringent limitation on their use on an unmanned spacecraft. - Therefore, a reliable and durable mechanical pump would be desirable, in order to allow the application of MPL technology to high-capacity long-life applications, such as unmanned missions, serving telecommunications platforms, nuclear facilities, or any environment where reliability requirements are particularly high.
- Diaphragm pumps are devices with no tribological issues due to dynamic seals or any other friction elements, so they offer some advantages with respect to the aforementioned documents. However, the linear actuators used in these devices cannot provide the required strokes against the high-pressure forces typical of the applications indicated above and for the long-life demanded, so the person skilled in the art would not be prompt to use any of these devices as a solution for this problem.
-
EP2930363 A1 discloses a piezoelectric pump for use in a pressurised circuit, comprising a pump chamber, a pressure chamber and a pump diaphragm closing one end of the pump chamber such that the pressure chamber is defined at the side of the pump diaphragm facing away from the pump chamber. - The invention provides a solution for this problem by means of a volumetric pump according to
claim 1 or 6. Preferred embodiments of the invention are defined in dependent claims. - In a first inventive aspect, the invention provides a volumetric pump comprising
- a chamber divided into a main sub-chamber and a secondary sub-chamber by a first diaphragm, the first diaphragm comprising a first face oriented towards the main sub-chamber, a second face opposite to the first face and oriented towards the secondary sub-chamber and an outer edge clamped to the chamber;
- at least one inlet port and at least one outlet port being located in the main sub-chamber and being covered by at least one inlet valve and one outlet valve respectively;
- a compensation port being located in the secondary sub-chamber, this compensation port being in fluid communication with the inlet port;
- a linear actuator connected at one end to the first diaphragm and at an opposite end to a surface of the secondary sub-chamber, and the linear actuator being configured to cause a reciprocating movement in the first diaphragm, thus causing a variation in the volume of the main sub-chamber.
- In a second inventive aspect, the invention provides a volumetric pump comprising:
- a chamber divided into a main sub-chamber and a secondary sub-chamber by a first diaphragm, the first diaphragm comprising a first face oriented towards the main sub-chamber and a second face opposite to the first face and oriented towards the secondary sub-chamber and an outer edge being clamped in the chamber;
- at least one inlet port and at least one outlet port being located in the main sub-chamber and being covered by at least one inlet valve and one outlet valve respectively;
- a compensation port being located in the secondary sub-chamber, this compensation port being in fluid communication with the inlet port;
- a linear actuator connected at one end to a second diaphragm, the second diaphragm being connected to the first diaphragm by interposition of a rigid shank, and the linear actuator is configured to cause a reciprocating movement in the first diaphragm, thus causing a variation in the volume of the main sub-chamber.
- The proposed invention improves the performance with respect to other volumetric pumps because of the absence of friction and dynamic seals, thereby increasing the reliability and extending its lifetime and being specially indicated for spacecraft applications, including unmanned missions.
- Further, due to the compensation port located in the secondary sub-chamber, and being in fluid communication with the inlet port of the pump, the difference between the pressure at both sides of the diaphragm is only the differential pressure caused by the compression, but the diaphragm and, therefore, the actuator, have not to withstand the total fluid pressure. This also improves the lifetime of the pump.
- The fact that the first diaphragm is clamped to the chamber does not exclude the possibility that both the first diaphragm and the chamber are manufactured together as a single part. This only makes reference to the fact that the diaphragm does not rotate or pivot with respect to the chamber, but the rotation is also restricted.
- In some particular embodiments, the linear actuator is connected to the diaphragm by means of a coupling device.
- This makes it easier that the linear actuator is protected from the working fluid.
- In some particular embodiments, the linear actuator is a piezoelectric actuator.
- The use of a compact high-force piezoelectric actuator operated at low frequencies allows a much easier control electronics than the typically used for the centrifugal pumps, the gear pump and the rotary lobe rotary brushless motor, thereby increasing the reliability and extending its lifetime.
- In other particular embodiments, the linear actuator is a magnetostrictive actuator. This kind of actuators provide strokes in similar ranges to the piezoelectric actuators with lower actuation voltages and have potentially higher lifetimes since they are made of bulk material actuated electromagnetically.
- In some particular embodiments, the first diaphragm has a central portion with a central thickness greater than the thickness in any point outside the central portion.
- This central reinforcement of the diaphragm improves the efficiency of the pump, since it maximizes the volume displacement by limiting the diaphragm deformation.
- In some particular embodiments,
- the secondary sub-chamber is limited between the first diaphragm and the second diaphragm solidly attached to the first diaphragm by means of the rigid shank arranged coaxially with the linear actuator;
- the linear actuator is located outside the chamber and in contact with the second diaphragm, so that when the linear actuator moves, it moves the second diaphragm and the solid connection between the second diaphragm and the first diaphragm by means of the rigid shank makes that the first diaphragm also moves.
- This arrangement is a way of defining a secondary sub-chamber between two diaphragms, the linear actuator being configured to move the two diaphragms as a single piece, since they are solidly attached. The linear actuator is therefore kept outside the contact with the fluid, being a single way of preserving it from an aggressive environment.
- In some particular embodiments, the second diaphragm has a lower surface than the first diaphragm.
- These embodiments reduce the preload effect of the base pressure over the actuator, extending the working range of the actuators and allowing a higher life of the pump.
- In some particular embodiments, the coupling device comprises a protective capsule around the linear actuator, the linear actuator being located inside the secondary sub-chamber, so that the linear actuator is adapted to move the first diaphragm without being in direct contact with the working fluid of the secondary sub-chamber.
- This is an alternative way of achieving the isolation of the linear actuator. This improves its lifetime, since the working fluid may harm such a delicate part, especially in long term periods.
- In some particular embodiments, the inlet and/or the outlet valve comprises
- one clamped edge which is clamped to the main sub-chamber in the corresponding inlet or outlet port; and
- a free end which allows the work fluid enter/exit the main sub-chamber by being flexed with respect to the clamped edge.
- These embodiments are aimed for simplicity and reliability, since no electronic parts or controlled elements are present; the valves of these embodiments are passive valves, and are therefore less prone to be damaged.
- In some embodiments, the inlet valve and/or the outlet valve is operated by a secondary piezoelectric actuator.
- These embodiments are aimed for better performance, since the valve of these embodiments may be synchronized with the movement of the main actuator, not depending on fluid-dynamic effects.
- To complete the description and in order to provide for a better understanding of the invention, a set of drawings is provided. Said drawings form an integral part of the description and illustrate an embodiment of the invention, which should not be interpreted as restricting the scope of the invention, but just as an example of how the invention can be carried out. The drawings comprise the following figures:
-
Figure 1 shows an exploded view of a first embodiment of a volumetric pump according to the invention. -
Figure 2 shows a cross section of the volumetric pump ofFigure 1 . -
Figure 3 shows a cross section of a second embodiment of a volumetric pump according to the invention. -
Figures 4a and 4b show a cross section of the volumetric pump ofFigure 2 in two different operative positions. -
Figure 5 shows a detail of an inlet valve of a volumetric pump according to the invention. -
Figure 1 shows an exploded view of a first embodiment of a volumetric pump 1 according to the invention. - This volumetric pump 1 comprises
- a
chamber 2; - a
first diaphragm 5 intended to divide thechamber 2 into two sub-chambers; - a
second diaphragm 7 intended to provide a cover for thechamber 2; - an
inlet port 23 and anoutlet port 24; - an
inlet valve 31 and anoutlet valve 32, intended to cover theinlet 23 andoutlet 24 ports; - a
rigid shank 91 intended to be solidly attached to thefirst diaphragm 5 and to thesecond diaphragm 7, so that thefirst diaphragm 5, thesecond diaphragm 7 and therigid shank 91 may constitute a single element; and - a
linear actuator 6 intended to move the single element constituted by thefirst diaphragm 5, thesecond diaphragm 7 and therigid shank 91. - The
chamber 2 comprises acompensation port 26, intended to provide fluid communication between one of the sub-chambers and theinlet port 23. -
Figure 2 provides a side cross section of such a volumetric pump 1. In this figure, the internal arrangement of each element may be seen. - As mentioned above, the
chamber 2 is divided into amain sub-chamber 21 and asecondary sub-chamber 22 by means of thefirst diaphragm 5. Thefirst diaphragm 5 has afirst face 51 oriented towards themain sub-chamber 21 and asecond face 52 opposite to thefirst face 51, being therefore oriented towards thesecondary sub-chamber 22. Anouter edge 53 of thefirst diaphragm 5 is clamped to the chamber, thus dividing thechamber 2 into amain sub-chamber 21 and asecondary sub-chamber 22. - Both the
main sub-chamber 21 and thesecondary sub-chamber 22 are intended to be full of working fluid, so the difference between the pressure in thefirst face 51 and thesecond face 52 of thefirst diaphragm 5 is only due to the differential pressure provided by the first diaphragm movement. - The
inlet port 23, covered by theinlet valve 31, and theoutlet port 24, covered by theoutlet valve 32, are located in themain sub-chamber 21. Theinlet port 23 is in fluid communication with thepump inlet 25, where the working fluid enters the pump system. - The
first diaphragm 5 has acentral portion 54 with a thickness which is greater than the thickness in any point outside thecentral portion 54. - A
compensation port 26 located in thesecondary sub-chamber 22 is intended to provide a fluid communication between thesecondary sub-chamber 22 and theinlet port 23, so that the pressure at both sides of the first diaphragm 5 (i.e., in the main and secondary sub-chambers) is similar, and, as mentioned above, only differs due to the differential pressure provided by the first diaphragm movement. - In the embodiment shown in this figure, the secondary sub-chamber is limited between the
first diaphragm 5 and asecond diaphragm 7. Thissecond diaphragm 7 is solidly attached to thefirst diaphragm 5 by means of arigid shank 91, so that thefirst diaphragm 5, theshank 91 and thesecond diaphragm 5 constitute a single element. Both thefirst diaphragm 5 and thesecond diaphragm 7 are clamped to the inner wall of thechamber 2 in two different zones, thus limiting their movements. - The
linear actuator 6 does not need to be isolated from the working fluid, since it is located outside thesecondary sub-chamber 22. It contacts thesecond diaphragm 7 and, since thissecond diaphragm 7 constitutes a single element with thefirst diaphragm 5 by the solid attachment with theshank 91, thelinear actuator 6 is able to move thefirst diaphragm 5 without a direct contact. -
Figure 3 shows a cross section of a second embodiment, which has some differences with respect to the first embodiment shown inFigure 2 . - In the embodiment shown in this figure, the
chamber 2 is a closed cavity, and is divided into two sub-chambers by the first diaphragm. Thelinear actuator 6 is located inside thesecondary sub-chamber 22, inside aprotective capsule 92 which isolates thelinear actuator 6 from the working fluid which fills thesecondary sub-chamber 22. Thisprotective capsule 92 does not prevent thelinear actuator 6 from acting over thefirst diaphragm 5, transmitting the linear reciprocating movement thereto. - There is also a fluid connection between the
secondary sub-chamber 22 and theinlet port 23 by means of thecompensation port 26. This fluid communication makes thesecondary sub-chamber 22, under thefirst diaphragm 5, have the same pressure as theinlet port 23, which is the base pressure. The pressure in themain sub-chamber 21 will oscillate around this base pressure, by adding or removing a differential pressure which is small compared with the base pressure. Hence, thefirst diaphragm 5 has a small pressure difference between their first and second faces. -
Figures 4a and 4b show a cross section of the volumetric pump 1 ofFigure 2 , so that its operation may be observed. The embodiment shown inFigure 3 works in the same manner. The displacement of the first andsecond diaphragms - The
inlet valve 31 and theoutlet valve 32 are arranged to control the flow across theinlet port 23 and theoutlet port 24 respectively. - The
linear actuator 6 is arranged to cause an alternating displacement in the single element constituted by thefirst diaphragm 5, therigid shank 91 and thesecond diaphragm 7, at an operation frequency, thus causing a variation in the volume comprised within themain sub-chamber 21, as may be observed in the difference betweenFigures 4a and 4b . - The variation of the volume comprised in the
main sub-chamber 21 is caused by the elastic deformation of thefirst diaphragm 5, since theouter edge 53 thereof is clamped to themain chamber 2 and does not displace during this volume variation. -
Figure 5 shows a detail of theinlet valve 31. The outlet valve has an analogue structure. In these figure, the following elements may be observed: - a clamped
edge 311 which is clamped to the main sub-chamber 21 in theinlet port 23; and - a
free end 312 which allows the work fluid enter themain sub-chamber 21 by being flexed with respect to the clampededge 311. - In different embodiments, the
valves 31 and/or 32 are operated by a secondary piezoelectric actuator instead. - In this text, the term "comprises" and its derivations (such as "comprising", etc.) should not be understood in an excluding sense, that is, these terms should not be interpreted as excluding the possibility that what is described and defined may include further elements, steps, etc.
- The invention is obviously not limited to the specific embodiments described herein, but also encompasses any variations that may be considered by any person skilled in the art (for example, as regards the choice of materials, dimensions, components, configuration, etc.), within the general scope of the invention as defined in the claims.
Claims (14)
- Volumetric pump (1) comprisinga chamber (2) divided into a main sub-chamber (21) and a secondary sub-chamber (22) by a first diaphragm (5), the first diaphragm (5) comprising a first face (51) oriented towards the main sub-chamber (21) and a second face (52) opposite to the first face (51) and oriented towards the secondary sub-chamber (22) and an outer edge (53) being clamped in the chamber (2);at least one inlet port (23) and at least one outlet port (24) being located in the main sub-chamber (21) and being covered by at least one inlet valve (31) and one outlet valve (32) respectively;a compensation port (26) being located in the secondary sub-chamber (22), this compensation port (26) being in fluid communication with the inlet port (23);characterized in that the volumetric pump further comprises a linear actuator (6) connected at one end to the first diaphragm (5) and at an opposite end to a surface of the secondary sub-chamber (22) and being configured to cause a reciprocating movement in the first diaphragm (5), thus causing a variation in the volume of the main sub-chamber (21).
- Volumetric pump (1) according to claim 1, wherein the linear actuator (6) is connected to the first diaphragm (5) by means of a coupling device (91, 92).
- Volumetric pump (1) according to any of claims 1 or 2, wherein the linear actuator (6) is a piezoelectric actuator or a magnetostrictive actuator.
- Volumetric pump (1) according to any of the preceding claims, wherein the first diaphragm (5) has a central portion (54) with a thickness greater than the thickness in any point outside the central portion (54).
- Volumetric pump (1) according to any of claims 2 to 4, wherein the coupling device comprises a protective capsule (92) around the linear actuator (6), the linear actuator (6) being located inside the secondary sub-chamber (22), so that the linear actuator (6) is adapted to move the first diaphragm (5) without being in direct contact with the working fluid of the secondary sub-chamber (22).
- Volumetric pump (1) comprisinga chamber (2) divided into a main sub-chamber (21) and a secondary sub-chamber (22) by a first diaphragm (5), the first diaphragm (5) comprising a first face (51) oriented towards the main sub-chamber (21) and a second face (52) opposite to the first face (51) and oriented towards the secondary sub-chamber (22) and an outer edge (53) being clamped in the chamber (2);at least one inlet port (23) and at least one outlet port (24) being located in the main sub-chamber (21) and being covered by at least one inlet valve (31) and one outlet valve (32) respectively;a compensation port (26) being located in the secondary sub-chamber (22), this compensation port (26) being in fluid communication with the inlet port (23);characterized in that the volumetric pump further comprises a linear actuator (6) connected at one end to a second diaphragm (7), the second diaphragm (7) being connected to the first diaphragm (5) by interposition of a rigid shank (91), and the linear actuator (6) is configured to cause a reciprocating movement in the first diaphragm (5), thus causing a variation in the volume of the main sub-chamber (21).
- Volumetric pump (1) according to claim 6, wherein the linear actuator (6) is a piezoelectric actuator or a magnetostrictive actuator.
- Volumetric pump (1) according to claim 6 or 7, wherein the first diaphragm (5) has a central portion (54) with a thickness greater than the thickness in any point outside the central portion (54).
- Volumetric pump (1) according to any of claims 6 to 8, whereinthe secondary sub-chamber (22) is limited between the first diaphragm (5) and the second diaphragm (7), the second diaphragm (7) being solidly attached to the first diaphragm (5) by means of the rigid shank (91) that is arranged coaxially with the linear actuator (6); andthe linear actuator (6) is located outside the chamber (2) and in contact with the second diaphragm (7), so that when the linear actuator (6) moves, it moves the second diaphragm (7) and the solid connection between the second diaphragm (7) and the first diaphragm (5) by means of the rigid shank (91) makes that the first diaphragm (5) also moves.
- Volumetric pump (1) according to claim 9, wherein the second diaphragm (7) has a lower surface than the first diaphragm (5).
- Volumetric pump (1) according to any of preceding claims, wherein the inlet valve (31) comprisesone clamped edge (311) which is clamped to the main sub-chamber (21) in the inlet port (23); anda free end (312) which allows the work fluid enter the main sub-chamber (21) by being flexed with respect to the clamped edge (311).
- Volumetric pump (1) according to any of claims 1 to 10, wherein the inlet valve (31) is operated by a first secondary piezoelectric actuator.
- Volumetric pump (1) according to any of preceding claims, wherein the outlet valve (32) comprisesone clamped edge (321) which is clamped to the main sub-chamber (21) in the outlet port (24); anda free end (322) which allows the work fluid exit the main sub-chamber (21) by being flexed with respect to the clamped edge (321).
- Volumetric pump (1) according to any of claims 1 to 12, wherein the outlet valve (32) is operated by a second secondary piezoelectric actuator.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17382733.8A EP3480460B1 (en) | 2017-11-02 | 2017-11-02 | Volumetric pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17382733.8A EP3480460B1 (en) | 2017-11-02 | 2017-11-02 | Volumetric pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3480460A1 EP3480460A1 (en) | 2019-05-08 |
EP3480460B1 true EP3480460B1 (en) | 2021-06-23 |
Family
ID=60331539
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17382733.8A Active EP3480460B1 (en) | 2017-11-02 | 2017-11-02 | Volumetric pump |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP3480460B1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113137363B (en) * | 2021-04-26 | 2022-03-29 | 长春工业大学 | Valveless double-cavity resonance piezoelectric drive type insulin pump |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2146016A1 (en) * | 1971-09-15 | 1973-03-22 | Erich Becker | DEVICE FOR SECURING AND GGFS. IMPROVING A DIAPHRAGM PUMP |
FR2772436B1 (en) | 1997-12-16 | 2000-01-21 | Centre Nat Etd Spatiales | POSITIVE DISPLACEMENT PUMP |
JP3985023B2 (en) | 2001-03-19 | 2007-10-03 | 彰三 勝倉 | Pump device |
US20050238506A1 (en) * | 2002-06-21 | 2005-10-27 | The Charles Stark Draper Laboratory, Inc. | Electromagnetically-actuated microfluidic flow regulators and related applications |
JP2005016367A (en) * | 2003-06-25 | 2005-01-20 | Sharp Corp | Piezo-electric pump and stirling cooling vessel |
US8267675B2 (en) * | 2008-06-16 | 2012-09-18 | GM Global Technology Operations LLC | High flow piezoelectric pump |
FR2946100B1 (en) | 2009-05-28 | 2011-06-03 | Centre Nat Etd Spatiales | METHOD AND DEVICE FOR DIPHASIC THERMAL HEATING WITH A GEAR PUMP ON BEARINGS |
EP2930363B1 (en) * | 2014-04-10 | 2020-06-10 | Stichting Nationaal Lucht- en Ruimtevaart Laboratorium | Piezoelectric pump assembly and pressurised circuit provided therewith |
-
2017
- 2017-11-02 EP EP17382733.8A patent/EP3480460B1/en active Active
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
EP3480460A1 (en) | 2019-05-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7198250B2 (en) | Piezoelectric actuator and pump using same | |
EP2588759B1 (en) | Pumps and pump heads comprising volume-compensation feature | |
EP3168550B1 (en) | Liquid supply system | |
US20050147506A1 (en) | Multi pumping chamber magnetostrictive pump | |
US9273703B2 (en) | Universal orientation electro-hydraulic actuator | |
EP3199812A1 (en) | Liquid supply system | |
EP3480460B1 (en) | Volumetric pump | |
KR101431263B1 (en) | Improved fluidic actuator for application inside turbomachinery | |
KR20180103270A (en) | Air pump equipped with diaphragm | |
JP2014051950A (en) | Bellows pump | |
KR102428655B1 (en) | Heat engine with dynamically controllable hydraulic exhaust | |
CN112302931B (en) | Vane pump | |
CA2960380A1 (en) | Engine actuated by static pressure and reactionless drive | |
US3806283A (en) | Pump by-pass | |
EP0919724B1 (en) | Hydraulically driven double acting diaphragm pump | |
EP3507492B1 (en) | Diaphragm with edge seal | |
JP2013068114A (en) | Reciprocating compressor | |
US20140260952A1 (en) | Rotary vane actuator seal | |
US20180195614A1 (en) | Face Seal | |
JP2024522771A (en) | Piezoelectric Fluid Pump | |
US10920770B2 (en) | Volumetric pump | |
WO2017078852A1 (en) | Pump displacement control assembly | |
JP4861902B2 (en) | Rotary valve unit and pulse tube refrigerator | |
SU1323753A1 (en) | Hydrostatic off-loading device of rotor | |
CN109236558A (en) | An a kind of tooth difference internal messing planetary hydraulic motor floating side plate device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20191108 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20200528 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20210118 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602017040718 Country of ref document: DE Ref country code: AT Ref legal event code: REF Ref document number: 1404539 Country of ref document: AT Kind code of ref document: T Effective date: 20210715 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210923 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1404539 Country of ref document: AT Kind code of ref document: T Effective date: 20210623 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210924 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210923 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20210623 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20211025 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602017040718 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20220324 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211102 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211130 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20211130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211102 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230331 Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20230331 Year of fee payment: 6 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220630 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20171102 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220630 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230427 Year of fee payment: 6 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 602017040718 Country of ref document: DE Representative=s name: KRAUS & LEDERER PARTGMBB, DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210623 |