EP4306801A1 - Pumpsystem mit inneren spiralen - Google Patents

Pumpsystem mit inneren spiralen Download PDF

Info

Publication number
EP4306801A1
EP4306801A1 EP22765390.4A EP22765390A EP4306801A1 EP 4306801 A1 EP4306801 A1 EP 4306801A1 EP 22765390 A EP22765390 A EP 22765390A EP 4306801 A1 EP4306801 A1 EP 4306801A1
Authority
EP
European Patent Office
Prior art keywords
pump
gears
internal
pumping system
lobe
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.)
Pending
Application number
EP22765390.4A
Other languages
English (en)
French (fr)
Inventor
Luciano Barros OLIVEIRA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP4306801A1 publication Critical patent/EP4306801A1/de
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/02—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees
    • F04C3/04—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing

Definitions

  • the present patent application refers to a new type of positive displacement rotary pump.
  • the project presents varied properties according to the established configuration.
  • One of the configurations has a higher flow capacity than the other types of positive displacement pumps.
  • One of the models of the invention presents an internal compression between the elements of the chambers, an ideal property for use in compressors.
  • the perfect dynamic balance and robust geometry favor use at high speeds, favorable conditions for use as a high-power hydraulic motor.
  • centrifugal pumps are the lowest cost alternative when pumping requires a high flow and a low discharge pressure is sufficient.
  • a commonly used option is multistage centrifugal pumps. These pumps in series can have more than 40 stages. As the stages increase, the cost increases and the mechanical efficiency drops.
  • turbopumps have a reasonable mechanical performance and a great cost for use in low discharge pressure in onestage models
  • positive displacement pumps are capable of reaching high discharge pressures with excellent mechanical performance, however the flow capacity is low and the cost of acquisition and maintenance is extremely high.
  • the pumped volume is extremely high even when compared to some high-flow centrifugal pumps of the same size driven by standard 2-pole electric motors, rotation close to 3600 rpm.
  • a pump with internal spring of 120 mm in diameter and 50 mm thick (not counting the collectors, in the illustrated case, spikes) can pump more than 50 m 3 /hour at 3600 rpm. It is worth remembering that positive displacement pumps are capable of practically maintaining the flow as the discharge pressure increases, unlike centrifugal pumps, which present a sharp drop in flow in their flow x pressure curve.
  • the “internal spring pumping system” is composed of 3 types of main elements.
  • the description, layout and general function of the components will be shown below.
  • the "lobe gears” (4) present the pumping agents, the lobes (9), just as a gear contains its teeth.
  • a lobe gear is shown separately in figure 3 .
  • the "one-piece rotor” (25) is the central element that holds the lobular gears and features the "drive shaft” (5), the drive shaft of the mechanism.
  • the rotor also admits a bipartite version in its equatorial plane to facilitate assembly or 3D printing. Sometimes in this text, to simplify the understanding of the function of the rotor, regardless of whether it is a bipartite model or not, it will be treated as a rotor.
  • the housing is the external element, the wrapper, the cap that has spiral grooves on its inside.
  • the project is composed of a pair of housings that are joined in their equatorial plane through the "central flange" (16) to enable assembly and closing. It is foreseen the use of models with the two housings with the same format without causing disadvantages, on the contrary, standardization is recommended and reduces costs. Some models have a housing that is slightly or quite different from the other housing depending on the purpose of the design configuration. A good example is that some configurations require one of the housings to be smooth internally, without any grooves. The housing model without grooves is called “smooth housing” (2).
  • the "spiral housings" (1) are the type housings that have the elements individually named “spiral groove” (10).
  • the set of grooves form a type of thread that describes a trajectory in a toroidal shape and admits having more than one entry
  • figures 5, 6 and 7 illustrate the generative trajectory of the grooves in the design of the pumping system with internal spring of 8-entry.
  • the "groove spiral” is a type of thread or toroidal spiral that has a circular section in the cuts orthogonal to its trajectory, see figures 16 and 17 .
  • the two parts of the housing pair are joined through screws installed in holes at the ends of the central flange (16). Housings can be joined in other ways, press fitting, welding or gluing.
  • the "bipartite rotor” consists of 2 parts arranged together in their equatorial plane. In said flat region, in the plane of union between the rotors, there is a bearing support means (11) to accommodate the "lobe gear shaft” (12), the shaft that passes through the center of the lobe gear.
  • One of the pairs that make up the split rotor is the "rotor shaft” (6), characterized by having the “drive shaft” (5), a shaft long enough to reach the external region of the pump to be coupled to the available driving source.
  • the pump works well even at low speeds, with manual operation or any other driving source, such as wind turbines, hydraulic turbines, electric motors, combustion engines, steam.
  • the "solidarity rotor” (7) is the other part of the rotor of the split-type rotor model and admits having a shorter shaft, the “secondary shaft” (26).
  • One of the functions of the secondary shaft is to provide extra support when inserted into the bearing of the spiral housing.
  • the so-called “secondary axis” is not a mandatory structure and can be removed from the project.
  • the "one-piece rotor" is represented in figures 28 and 29 , with figure 29 in section to illustrate the bearings (11), hollow holes to allow the insertion and removal of the lobular gear shafts.
  • the pumping chambers are defined by the action of the lobes when generating a mobile closing area in the section of the pumping ducts.
  • the "pumping ducts” are formed by the internal area of the “spiral grooves” and by the toroidal surface of the rotors that touch the “rotor sweep surface” waxing, sealing the “spiral grooves” by closing the said region of the "groove entry”.
  • the rotation of the rotor causes a translational movement in the "lobular gears” under the action of the lateral force exerted on the "lobular gears” by the “radial slots” of the rotor.
  • Said translation movement causes the rotation of the lobular gears since the gears are assembled with the “lobes” inserted, housed in the internal surface of the "spiral grooves” forcing the lobes to follow the path defined by the trajectory of the spiral grooves generating the rotation of the lobular gears in synchrony with their translation.
  • each of the collectors can act as a suction or discharge collector.
  • One of the collectors offers an internal path for the axis, the so-called “axis collector” (13) and the other a simple collector, (14).
  • lobular gears rotate freely (mounted only on the rotors) through their axis which is supported by bearings present in the rotor.
  • lobe gears can work well, as they are also guided and centered by the fit and constant contact of at least 2 of the 5 lobes of each fitted lobe gear in a spiral groove, the lobe gear being always supported also by its lateral contact surface of its internal disk with said sweeping surface of the rotor.
  • Said internal spirals are composed of a type of thread that presents, in some configurations, a complete single and continuous trajectory, being described on the internal surface of the housing of spirals.
  • the complete trajectory of the drawing that generated the grooves of the 8-entry housing can be seen in figures 5, 6 and 7 , with figure 7 being a central cut, the complete drawings of figures 5 and 6 consist of only one continuous line, because in the drawing that defines the trajectory of the grooves, the groove at the beginning of a "groove spring" must coincide with the end of this same spring or another spring, a possibility in case there is more than one entry.
  • Each of the housings admits to have a bearing (3), but there is the freedom to be defined in the project to support only one of the rotor shafts in a bearing in only one of the housings or to dispense with the adoption of bearings in both housings, especially if the pump is driven directly by a motor shaft, preferably a flanged type motor to ensure perfect alignment with the rotor shaft, dispensing with the use of couplings and/or flexible joints between the motor shaft and the rotor.
  • a surface treatment is indicated and/or the adoption of a surface coating on the surfaces that will act on the bearing to reduce friction between the parts.
  • the adoption of sleeves made of synthetic material or bearings to act as a bearing between the shaft and the housing is foreseen and recommended.
  • the spiral housing can be the fastening element, the static part that can be fixed by means of feet or a fixed flange on the "central flange". None prevents the spools from being set to rotate, the rotor axis being static or rotating in the opposite direction.
  • the radial symmetry of the design is favorable to the external movement of the referred housings.
  • the "internal spiral pumping system” presents several models, configurations in the most varied proportions, being more or less flattened, closer to the shape of a sphere or a disc, according to the adopted configuration.
  • the pump admits a configuration with an internal thread of only one entry, as well as configurations with 10 entries or more.
  • lobe gears have different numbers of lobes, making it possible to define a lobe gear with more than 10 lobes, defined according to the design pressure to which the system will be applied, since the greater the number of lobes present in each spiral groove, the greater the pressure reached by the system.
  • Configurations with more than 5 lobes are normally designed for pumping gases and have a complementary housing without spiral grooves, the so-called “smooth housing” (2).
  • This demonstrate the versatility of number of entries and lobes in lobular gears 2 models will be presented.
  • An example will be a pump configuration ( figs. 9 , 10 , 11 and 12 ) with 3-entry with 3 lobe gears with 12 lobes.
  • Another configuration ( figs. 13, 14 and 15 ) presented will be a pump with 4 entries with 5 lobe gears with 14 lobes.
  • each sulcus or entry presents 9 acting lobes forming 7 chambers of decreasing volume towards the central discharge for each of the entries, totaling 28 chambers, similar to what happens in a scroll type pump. Due to the progressive reduction in the size of the chambers, these configurations are not recommended for pumping incompressible fluids.
  • Configurations such as those exemplified with the smooth housing admit 2 or more lobe gears, whose maximum number of lobe gears is defined according to the design pressure to which the system will be applied, since the greater the number of lobular gears, allows more than one lobe to act in each groove at the same time in the spiral grooves in order to achieve a greater capacity for holding pressure.
  • the number of lobes acting in each spiral groove would increase, providing a better seal and consequently a greater capacity to reach higher pressures.
  • the distance to be defined between the grooves and the spirals can be changed, a greater distance between the grooves provides a better seal between the contact surfaces of the rotor and the housing of the spirals, as the area of adjustment or minimum contact between the "scanning surface of the rotor" (15) and the toroidal side of the rotor becomes larger.
  • the 3-entry pump with 12-lobe gears has the lobes farther apart than the 14-lobe model, so the "impeller sweep surface" region is less prone to leaks.
  • the highest flow capacity configuration to be illustrated features 4 lobe gears of 5 lobes and the 5 "spire housings" with an internal thread with 8 spiral groove entries.
  • a similar configuration with 4-entry salient grooves will also be shown.
  • the 4-entry design will be commented on more superficially, it only shows a view of a housing in this model ( figure 4 ). The objective is only to illustrate the possible variations and some implications of this geometric variation.
  • the configuration of the pump with internal spirals with lobular gears with only 5 lobes and salient type presents spiral grooves (10) of the surrounding type to house the most salient lobes.
  • the objective is to increase the area of the sweep section of the lobes so that the pumping ducts, that is, the inner region of the spiral grooves that define the pumping chambers, present a greater volume.
  • the surrounding groove goes beyond the diameter of the lobe, making the lobes embedded in the groove's spirals in the assembly.
  • a lobe of a lobe gear is at the entry of a groove, the next one is in the middle of the course of another groove, region of the union of the grooves and the third following lobe is at the exit of another subsequent groove.
  • 8-entry pump Comparing "internal spring pumping system" with 8-entry wraparound grooves with 4 entries configuration, 8-entry pump has much higher volumetric capacity than 4 entries inner spring pump. Both with 115mm in diameter, the configuration with 8 ports in figure 30 pumps 260 ml against 150 ml for the configuration with 4-entry.
  • the 4-entry pump must have at least 2 opposing lobe gears of 5 lobes, while the 8-entry pump must have the same external diameter, it must have at least 4 lobe gears with 5 lobes also equidistant to ensure that there is at least one lobe inside each pumping duct.
  • the pump with 4 entries has a smaller angle on the windings and therefore needs a much smaller lobular gear.
  • the 8-entry pump As it has a greater angle in the turns, when turning only 90 degrees, the lobes run completely along the length of the grooves, therefore, it pumps the entire volume of the 8 pumping ducts 4 times for each turn of the impeller drive shaft, this is one of the main factors for the high flow capacity.
  • the 4-entry pump in turn, requires half a turn for each lobe to travel the entire length of the spiral groove, greatly reducing the flow capacity.
  • the lobe gears on the 4-entry pump turn 4/5 of a turn whereas on the 8-entry pump the lobe gears turn 8/5 of a turn for each revolution of the driveshaft.
  • the 4-entry pump Due to the lower rotation of the lobular gears, the 4-entry pump has a smoother movement and less wear because it has fewer lobes passing through a spiral groove at each rotation. On the other hand, due to its smoother operation due to the smaller angle of the turns and the lower rotation of the lobular gears, the 4-entry pump is more capable of turning at a higher maximum rotation, a condition of greater wear that would partly compensate for the lower volumetric capacity. Analogously, the 8-entry model, when rotating at a speed 40% lower than the 4-entry model, still has a slightly higher flow rate.
  • the "internal spiral pumping system” is suitable for being assembled in series in order to reach a higher discharge pressure in relation to the use of only one stage.
  • the multistage configuration can be seen in a radial sectional view of a 3-stage assembly, figure 27 .
  • the so-called "coupling sleeve” logically has 3 keyways where the keys are inserted.
  • the keys are hidden in the drawing, as they are inside the coupling sleeves.
  • the project admits the adoption of a splined shaft compatible with the internal spline to be adopted in the coupling sleeve.
  • the coupling sleeve therefore, is inserted in the union region between the shafts of each stage.
  • the "coupling manifold” (22), a sleeve with a type of coupling at both ends, in the case shown the coupling manifold is a cylinder with a continuous external thread. Therefore, the “coupling collector” performs the function of uniting the stages so that the discharge of the previous stage is coupled to the suction of the next stage.
  • the “internal spring pumping system” admits to having 10 stages or more, as it was said, it will depend on the pumping pressure to be required by the project.
  • Figure 16 shows the position of the orthogonal cut in relation to a spiral groove
  • figure 17 shows a cross-sectional view of the outermost lobe
  • Figure 18 shows the internal spiral housings with transparency. Through this transparency it is possible to observe a zigzag stain (18) formed by the contact line between the lobular gear and the spiral grooves.
  • the thickness of the internal part of the rotor that is, the region between the axis and the beginning of the toroid surface, must be defined so that the length of the path of the path of the lobes in this internal region of the rotor, allow that, during the return of the lobes to the interior of the rotors, at least one of the lobes is present in this path described inside the rotors, this passage channel of the lobes is called "reflux channel" (17).
  • the objective is to always keep this section obstructed by at least 1 lobe to avoid a free return of the fluid in this region.
  • Figures 19 , 20, 21 and 22 are consecutive cuts in the design of the 8-entry pump to demonstrate, from another angle, the perfect fit between the lobes and the spiral grooves.
  • Figure 23 is a representation of the 8-port pump in a radial section outside the lobe gear region to demonstrate the fit between the toroidal lateral surface of the impellers and the impeller sweep area (15).
  • the pumping pressure acts exerting a lateral force on the lobe gears through the line of contact between the lobe and the inner surface of the spiral grooves, this line of contact of the lobe can be seen in detail 18 of figure 18 .
  • This pumping reaction force does little to interfere with the rotational movement of the lobe gears, since the angle between the pumping reaction force exerted on the lobes is close to the perpendicular to the face of the lobe. Therefore, the closer the angle between the face of the lobe and the trajectory of the spiral groove is to the perpendicular, the better it will be for the greater durability of the pump.
  • the "lobes” admit having a rectangular ( figure 24 ), continuing curved on its side, being the piece in this rectangular shape called a “rectangular gear” (19).
  • the shape of the spiral grooves would be changed to adapt to this new shape of the lobes, being called “rectangular spiral groove” (20).
  • This new geometry of the lobes and spiral grooves aims to further increase the volumetric capacity of the "internal spiral pumping system".
  • This type of pump with rectangular lobes will be called “Pump with rectangular internal spring”.
  • the pump with internal turns presents a version in which the lobular gears are arranged obliquely, seeking to be closer to the orthogonal position in relation to the grooves, as can be seen in the geometric study shown in figure 25 .
  • One of the objectives of the lobular gears is to be in a plane as orthogonal as possible to the section of the pumping ducts previously discussed, is related to a reduction in wear due to the decomposition of reaction forces to pumping that act on the lobes, preventing the pressure exerted on the fluid during pumping from generating forces contrary to the rotation movement of the lobe gear.
  • Figure 26 shows an electric motor embedded inside the pump rotor, its housing being fixed to said rotor, with the shaft of said motor being fixed in one of the housings with internal turns.
  • Parts of internal spiral pumps can be manufactured via injection into plastic or resins, printed (with thermoplastics or metals), sintered (powder metallurgy), cast in lost wax using the micro fusion process and/or machined.
  • Surface treatment on parts is an option as a device to increase durability in metals with low machining costs such as aluminum, another option is chemical coatings with low coefficient of friction and self-lubrication.
  • the "internal spiral pumping system” acts as an engine, when coupled to a pressurized fluid in one of its collectors, being suitable for use in hydroelectric power plants due to its reduced size in relation to other positive displacement pumps.
  • the “internal coil pumping system” can act as an engine using pressurized gas flows as energy sources by coupling a source of steam pressure to one of its collectors, pressurized air or pressurized gases from burning fuels. When designed to perform the motor function, it is called an “internal spiral motor”.
  • the "internal spring pumping system” performs the function of a hydraulic pump and, when designed for this function, it is called an “internal spring pump”.
  • the “internal spring pump” can be used in several ways. Use as a water pump for pumping clean or dirty water, with abrasive particles such as sand or less abrasive particles, food pump, sanitary pump, oil pump, fuel pump, hydraulic fluid pump, hemodialysis pump, auxiliary cardiac pump for internal or external use or in the function of an artificial heart. It has good suction capacity due to its long-term expansion in pumping ducts, similar to piston systems.
  • the internal spiral pump is indicated for use as a heart pump for internal use because it is very compact and has a small internal surface area in relation to its flow capacity, favorable factor to generate less rejection in contact with blood, therefore it is also indicated for use as a hemodialysis pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP22765390.4A 2021-03-07 2022-03-02 Pumpsystem mit inneren spiralen Pending EP4306801A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BR102021004295-8A BR102021004295A2 (pt) 2021-03-07 2021-03-07 Sistema de bombeamento de espiras internas
PCT/BR2022/050067 WO2022187920A1 (pt) 2021-03-07 2022-03-02 Sistema de bombeamento de espiras internas

Publications (1)

Publication Number Publication Date
EP4306801A1 true EP4306801A1 (de) 2024-01-17

Family

ID=83226083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22765390.4A Pending EP4306801A1 (de) 2021-03-07 2022-03-02 Pumpsystem mit inneren spiralen

Country Status (4)

Country Link
EP (1) EP4306801A1 (de)
CN (1) CN117083458A (de)
BR (1) BR102021004295A2 (de)
WO (1) WO2022187920A1 (de)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4167933A (en) * 1976-09-08 1979-09-18 Bertram Slanhoff Engine system
NL8400246A (nl) * 1984-01-26 1985-08-16 Jeichienus Adriaan Van Der Wer Torusmotor/pomp.
DE3677221D1 (de) * 1985-05-08 1991-02-28 Hartwig Groeneveld Rotationskolbenmaschine.
CA2450542C (en) * 2003-11-21 2011-01-04 Anatoly Arov Arov engine/pump
ITCT20060019A1 (it) * 2006-09-07 2006-12-07 Emanuele Spada Macchina volumetrica con camera toroidale a sezione circolare, suddivisa in due volumi variabili da due valvole di separazione e da un pistone a settore toroidale.
US7730869B2 (en) * 2007-04-13 2010-06-08 Yan Li Housing wheel engine
US9157323B2 (en) * 2009-12-07 2015-10-13 Mars Sterling Turner Oscillatory rotary engine
WO2016145440A1 (en) * 2015-03-12 2016-09-15 Hicks Edward Alan Motor/engine with rotating pistons

Also Published As

Publication number Publication date
WO2022187920A1 (pt) 2022-09-15
BR102021004295A2 (pt) 2022-09-13
CN117083458A (zh) 2023-11-17

Similar Documents

Publication Publication Date Title
US7014436B2 (en) Gear pump
US6824369B2 (en) Rotary variable expansible chamber-kinetic hybrid pump
US4526518A (en) Fuel pump with magnetic drive
JP2016508558A (ja) 容積型の機械のためのデバイス、当該デバイスのための制御ギヤ機構および制御ギヤ機構の使用法
US4132504A (en) Liquid ring pump
TWI384157B (zh) 冷媒壓縮機供油結構
CN102374164B (zh) 高效率固定排量叶片泵
US6503071B2 (en) High speed UniVane fluid-handling device
EP4306801A1 (de) Pumpsystem mit inneren spiralen
US5144802A (en) Rotary fluid apparatus having pairs of connected vanes
JPS58170875A (ja) スクロ−ル・コンプレツサ
KR100192066B1 (ko) 용적형 유체기계
CN101979867A (zh) 旋转斜盘轴向柱塞油马达及其组合
KR102636718B1 (ko) 이중 구동 베인 펌프
CN210919828U (zh) 一种用于流体泵的轴承
CN115143109A (zh) 柱面密封转子压缩机和泵及马达
CN210218117U (zh) 无油单螺杆空气压缩机
CN100392251C (zh) 电动燃油双槽叶轮泵
CN208236647U (zh) 一种真空泵及其多级真空泵
CN112879283A (zh) 一种三角转子泵
CN210422767U (zh) 基于流体容积变化的能量转换装置
CN210422765U (zh) 基于流体容积变化的能量转换装置
CN219344967U (zh) 柱面密封转子压缩机
EP1458954B1 (de) Koaxialenergiewandler
CN218850469U (zh) 通用流体模组及应用该通用流体模组的通用流体装置

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20231002

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

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)