EP1448895A1 - Pompe a piston rotatif - Google Patents

Pompe a piston rotatif

Info

Publication number
EP1448895A1
EP1448895A1 EP02787733A EP02787733A EP1448895A1 EP 1448895 A1 EP1448895 A1 EP 1448895A1 EP 02787733 A EP02787733 A EP 02787733A EP 02787733 A EP02787733 A EP 02787733A EP 1448895 A1 EP1448895 A1 EP 1448895A1
Authority
EP
European Patent Office
Prior art keywords
piston
annular
control
annular space
contour
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.)
Withdrawn
Application number
EP02787733A
Other languages
German (de)
English (en)
Inventor
Peter Schnabl
Paul Schnabl
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 EP1448895A1 publication Critical patent/EP1448895A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • 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
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • 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
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/007—Oscillating-piston machines or pumps the points of the moving element describing approximately an alternating movement in axial direction with respect to the other element
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise

Definitions

  • the invention relates to a rotary lobe pump with a housing, an annular piston in the form of a tubular section which is connected in a rotationally fixed manner to a shaft which can be rotated in the housing and is rotatably and axially displaceably guided in an annular space of the housing which is coaxial to the shaft, the axially facing one another End surfaces of the annular space and the annular piston are designed as shaft surfaces with axially parallel amplitude and with at least one wave crest and a wave trough, and each with at least one inlet and one outlet channel, which are formed in the housing such that the inlet and outlet openings on the annulus side are within an axial area of an annular space surface, which is determined by the maximum axial distance of the mutually facing end faces.
  • Such a rotary lobe pump is known from DE 199 53 168 A.
  • the inlet and outlet openings are controlled by the contour of the shaft surface of the annular piston. It has been shown that the opening cross-sections have to be made relatively small in order to be able to control the inlet and outlet of the medium to be pumped without additional control elements such as check valves. Furthermore, it has been shown that the changes in the opening cross section take place only relatively slowly due to the combined lifting and rotating movement of the piston, viewed over the angle of rotation of the piston. This prevents an optimal filling of the annular space at higher speeds due to the increasing throttle effect on the inlet side. Another disadvantage is that the inlet and outlet channels cannot be separated from one another at bottom dead center.
  • the medium to be pumped therefore flows back through the bottom dead center from the outlet-side high-pressure region into the inlet region, which is approximately at atmospheric pressure, during the passage of the annular piston.
  • the invention has for its object to design a rotary lobe pump of the type mentioned while maintaining the simplest possible structure so that the delivery rate of the pump can be increased significantly.
  • the annular piston to the axial end face of the annular space has open control pockets for controlling the inlet and outlet openings and that the position, shape and size of the control pockets and the inlet and outlet openings are chosen so that the inlet opening with a piston movement between the top and bottom dead center and the outlet opening with a piston movement between the bottom dead center and the top dead center allow a maximum volume flow of the medium to be conveyed.
  • control pockets can ensure that, during the passage of the annular piston through bottom dead center, ie when the end face of the annular piston has its maximum axial distance from the end face of the annular space facing it, a sealing of inlet openings and outlet openings is ensured against each other so that no medium can overflow.
  • additional valves for this is not necessary.
  • control pockets preferably have at least approximately axially parallel control edges, the pocket bottom following at least approximately the contour of the shaft surface section lying between the control edges when viewed in the circumferential direction of the annular piston.
  • the inlet opening has an axially parallel front and rear edge (based on the direction of rotation) and that the upper edge of the inlet opening close to the wave surface of the annular space is shaped such that it is approximately congruent with the contour of the shaft surface of the annular piston when the rear control edge of a control pocket reaches the front edge of the inlet opening, ie the inlet opening is closed.
  • This shape of the inlet opening also takes into account that the annular piston not only performs a rotary movement but also an axial movement.
  • the lower edge of the inlet opening which is remote from the wave surface of the annular space, preferably follows at least approximately the path of movement of the front lower corner of a control pocket during the movement of the annular piston from top dead center to bottom dead center.
  • a wave surface shape with two wave peaks and two wave troughs if the width of the inlet opening measured in the circumferential direction of the piston and the width of the control pockets are so coordinated with one another that the inlet opening over the complete Hu of the ring piston between the top dead center and bottom dead center is open.
  • Controlling the cross section of the outlet opening is less critical to the overall volume flow rate than controlling the cross section of the inlet opening.
  • the outlet opening is also designed so that its rear edge is directed at least approximately axially parallel, that a first portion of the upper edge of the outlet opening adjoining the rear edge of the outlet opening is directed parallel to the shaft surface of the annular piston when the front control edge of a control pocket faces the rear edge reached the outlet opening, and that a second section of the upper edge adjoining the first section of the outlet opening follows the contour of the edge of the control pocket when the annular piston has reached top dead center.
  • two annular space / annular piston arrangements are arranged coaxially to one another so that the pistons arranged on the same shaft move together between the end faces of the two annular spaces so that the two annular spaces have one fluid connection lying radially inside the annular piston are in communication with each other and that the radially inner wall of each annular space is formed by the outer surface of a control sleeve, which are arranged in the housing in a rotationally fixed but axially displaceable manner so that by means of a control drive they move between an axially inner position in which they block the fluid connection, and an axially outer position that at least partially releases the fluid connection is adjustable.
  • This solution makes it possible to control the delivery volume of the pump by pumping a more or less large portion of the volume back and forth between the two annular spaces, i.e. is not released to the outside of the pump. If the fluid connection is blocked by the control sleeves, the pump delivers its maximum delivery volume. If, on the other hand, the cross section of the fluid connection is opened more or less, less or more fluid is released from the pump to the outside. The opening cross section of the fluid connection can be selected so that no medium is released to the outside when the fluid connection is opened to the maximum, i.e. the pump does not deliver anything.
  • the axial displacement of the control sleeves can react very quickly and sensitively to such a change in speed and in this way the delivery volume of the pump can be kept constant despite the changing speed become.
  • control sleeves are expediently continuously adjustable between their axially inner and outer end positions.
  • the axially inner end of the control sleeves can serve as the control edge on the control sleeves.
  • the control sleeves have at least one control slot directed parallel to the axis, which enables the opening or control of the fluid connection independently of the axial movement of the annular piston.
  • the outlet and inlet openings are expediently formed in the respective radially outer wall of the annular spaces in order to ensure that the pump is as simple as possible. You can in the two ring pistons are known to be combined to form a one-piece double piston.
  • the annular piston should perform a harmonic oscillating movement in the axial direction. This means that the vertex of the piston contour, i.e. the summit of a wave mountain - viewed in one development - the function
  • the contours of the two sliding shaft surfaces are selected so that the shaft surfaces are continuous at least in the area in which they are brought together or touch each other when the piston rotates. While it seems obvious at first glance to design both mutually facing wave surfaces as pure sine surfaces, practice shows that with such a solution the piston can never rotate smoothly and uniformly. When the top dead center was reached, the two wave surfaces would be in full contact with one another. In order to move the piston further from this position, a special force and therefore a sudden change in the acceleration is required. Which in turn means that the piston not only runs extremely rough, but is also exposed to high wear. In the solution described above, this is minimized in that the contours of the shaft surfaces touch each other only at one point, which also moves back and forth when the ring piston rotates around the respective apex of the piston contour.
  • A can of course have a larger or smaller value.
  • the piston contour is determined so that the harmonic movement of the piston results.
  • the contours of the two sliding shaft surfaces are expediently coordinated with one another in such a way that in the most wear-critical area, when the vertex of the piston contour sweeps over the vertex of the contour of the shaft surface of the annular space, the sum of the wear of the surfaces brought together is as small as possible, as will be described later is explained in more detail.
  • a rolling element for example a roller, a ball or a cone with a rotary axis directed radially to the piston axis
  • annular piston is not slidably guided on the shaft surface of the annular space or stator, but rather rolls with the roller on the shaft surface of the annular space or stator while it rotates about its axis.
  • This solution can be particularly advantageous if the rotary lobe pump is used to pump non-lubricatable liquid media or gaseous substances shall be.
  • This results in an improved wear behavior since the relative movement between the ring piston and the stator is essentially absorbed by the bearing of the rolling element.
  • the respective rolling element can also be mounted in the stator shaft surface.
  • FIG. 1 is a schematic section containing the axis through a rotary lobe pump according to the invention
  • Fig. 2 is a perspective view of the between the end faces of the
  • Fig. 4 is a schematic representation of the between the end faces of the
  • Annularly lying rotary pistons with the schematically illustrated inlet openings in 10 different rotary angle positions of the piston between 0 ° and 90 °, each by 10 °
  • 5 shows a representation of the rotary pistons corresponding to FIG. 4 with the schematically represented outlet openings in 10 rotary angle positions of the piston between 90 ° and 180 °, each different by 10 °
  • Rotary or ring pistons in various angular positions to explain the regulation of the delivery volume, the control sleeves being shown in an axially outer position,
  • FIG. 7 shows a representation corresponding to FIG. 6 with the control sleeves in an axially central position
  • Fig. 8 is a graph showing the shape of the contour of the
  • Fig. 9 is a graph showing the shape of the contour of the
  • Fig. 1 shows in a section containing the axis in schematic form a rotary lobe pump according to the invention with a cylindrical housing 10, the cylindrical bore 12 is closed by an end piece 14 and 16, respectively.
  • a tubular annular piston 18 is mounted, which is connected via a linear bearing 20 in a rotationally fixed but axially displaceable manner to a shaft 22 which passes through the end piece 16 coaxially to the cylindrical housing 10.
  • the ring piston 20 has at its axial ends a shaft surface 24 with which it is guided on a shaft surface 26 formed on the end piece 14 and 16, respectively.
  • annular space 28 lying between the shaft surface 26 of the first end piece 14 and the shaft surface 24 of the annular piston 18 facing it and the annular space lying between the shaft surface 26 of the lower end piece 16 and the shaft surface 24 of the ring piston 18 facing it Annulus 30 connected to one another by one or more axially parallel channels 32, which are indicated by dashed lines in FIG. 1. These channels form a fluid connection between the two annular spaces 28 and 30.
  • a first control sleeve 34 is arranged in a rotationally fixed but axially displaceable manner, which forms the radially inner boundary wall of the annular space 28.
  • a second control sleeve 36 is arranged in the end piece 16 in a rotationally fixed but axially displaceable manner, which forms the radially inner boundary wall of the annular space 30.
  • Both control sleeves 34 and 36 can be adjusted axially by an actuator (not shown) in the direction of the double arrows shown in order to block the channels 32, ie the fluid connection between the annular spaces 28 and 30 or to open them more or less.
  • the function of these control sleeves 34 and 36 will be explained in more detail later with reference to FIGS. 6 and 7.
  • open control pockets 38 are formed in the annular piston to the respective shaft surface, which serve to control the inflow of the medium to be conveyed, and the outflow of the medium from the annular spaces 28 and 30 and their shape and interaction with the inlet and outlet openings will now be explained in more detail with reference to FIGS. 4 and 5.
  • the inlet openings 40 are shown, which represent the mouth of an inlet channel in the bore 12 of the housing 10.
  • the respective inlet opening 40 has - with respect to the direction of rotation of the annular piston 18 - a front edge 42 and a rear edge 44, which are each parallel to the axis of the annular piston 18.
  • the lower edge 46 and the upper edge 48 of an inlet opening are approximately parallel to the contour of the shaft surface 24 of the annular piston 18 when it is in its 90 ° position, as will be explained later.
  • the control pockets 38 also each have a front edge 50 and a rear edge 52, which run parallel to the axis of the annular piston.
  • the pocket 38 is open to the wave surface 24.
  • the pocket bottom 54 runs approximately parallel to the contour of the wave surface 24 between the edges 50 and 52.
  • the entire cross section of the inlet opening 40 is available between 30 ° and 60 ° for the inflow of the medium. From 70 °, the rear edge 52 of the control pocket 38 slides over the inlet opening 40. At the transition from 80 ° to bottom dead center to 90 °, the entire height of the inlet opening is crossed again by the final piston edge. Due to the axially approximately the same length of the opening edges, approximately the same values of the change in cross section result during the opening and closing process. At 90 °, i.e. at the bottom dead center, the inlet opening 40 is closed.
  • the upper oblique edge of the inlet opening is approximately congruent with the contour of the shaft surface of the piston, which specifies the maximum upper position of the edge 48 of the inlet opening.
  • the width of the inlet opening and the arc length of the control pocket are coordinated with one another such that the opening duration of the inlet opening extends over the total stroke of the annular piston 18 between the top dead center and the bottom dead center, i.e. extends over the angle of rotation of 90 °.
  • This part of the piston movement thus corresponds to the suction stroke in the upper annular space 28, which is thereby filled with the medium to be conveyed.
  • FIG. 5 shows the contour of the outlet opening 56.
  • the contour of the outlet opening results from the structural specifications that were made on the inlet side.
  • the outlet opening 56 is still closed.
  • the rear edge 58 of the outlet opening 56 runs parallel to the axis of the rotary piston 18 and is congruent with the front edge 50 of the control pocket 38.
  • a first section 60 of the upper edge of the outlet opening 56 runs approximately parallel to the shaft surface 24 in this area. If the piston is moved from the bottom dead center in the direction of the 100 ° position, this results in a maximum change in the opening cross section.
  • the axially parallel extension of the opening to the center is determined by the depth of the control pocket or by the minimum size of the resulting opening cross-section required in accordance with the performance requirements of the pump.
  • the outlet opening 56 has its maximum opening cross-section between approximately 120 ° and 140 °. Then the outlet opening begins to close again. In the 180 ° position, ie top dead center, the outlet opening is completely closed. It can be seen that the second section 62 of the upper opening edge of the outlet opening 56 is adapted to the course of the lower edge 54 of the control pocket 38.
  • FIG. 1 shows the ring piston in different rotational positions, the control sleeves always being maximally axially extended. In this position the effective volume flow rate is practically zero.
  • the pump does not deliver any fluid.
  • Fig. 7 shows the pump with the control sleeves in a middle position. In Fig. 7 two superimposed representations of the pump belong together.
  • the upper illustration shows the relevant function of the upper annulus or the upper chamber and the lower illustration shows the relevant function of the lower chamber.
  • the axially parallel front edge 50 of the control pocket 38 is congruent with the rear edge of an axially parallel slot 64, which is formed in the control sleeve 34.
  • the upper chamber 28 is still closed inwards, ie towards the connecting channels 32.
  • the lower chamber 30, is connected to the channels 32 by a cross-hatched cross section.
  • the annular piston 18 releases an opening cross section to the inside. In this phase, fluid flows into the upper chamber 28, the fluid volume displaced from the lower chamber escapes into the interior of the pump and flows through the connecting channels 32 into the upper chamber 28 without pressure.
  • control sleeves 34 and 36 are arranged in a rotationally fixed manner and can only be moved axially. This can be ensured, for example, via a vertical guide groove, which is not shown. Under certain circumstances, however, it can prove to be advantageous to superimpose a rotary movement on the pure axial movement in order to achieve a correspondingly desired operating behavior.
  • This combined rotary-stroke movement can be achieved, for example, by a helical groove in the respective control sleeve, in which a pin connected to the respective part 14 or 16 engages.
  • the cross section of the connecting channels 32 is to be selected so that a practically throttle-free change of the fluid volume between the two chambers is ensured at the maximum speed of the pump.
  • a servomotor can be used on both sides, which converts the input signal (speed or volume flow or system pressure or combinations of these three variables) into a corresponding stroke position of the control sleeves. This allows the pump delivery volume to be regulated continuously, for example, to keep it constant at a variable speed.
  • control sleeves 34, 36 are adjusted without back pressure. This means that the adjustment can be carried out with relatively little energy and in a relatively short time, since the masses to be moved are very small.
  • the shape of the wave surfaces 24 and 26 will now be explained in more detail with reference to FIG. 8.
  • the aim is to ensure a harmonious kinematic movement of the ring piston 18 when pumping.
  • a harmonic kinematic sequence of motion of the piston exists if the translatory speed component of the piston is the basic equation of the speed of the harmonic oscillation
  • stator curve B in FIG. 8 An actual realistic stator curve is shown in FIG. 8 in the area enclosed by curves B and C and labeled D. It represents the envelope for the movement of the actual rotor curve E.
  • the movement of a piston with the contour E is represented by a family of curves 1 to 9.
  • the apex passes through the various layers 1 to 9.
  • the respective contact points of the rotor contour are at the apex the stator contour shown, characterized by the points V to 9 'on the envelope D.
  • the choice of the two associated curves E and D is preferably such that in the most wear-critical area, when the vertex of the piston contour passes the vertex of the contour of the wave surface of the annular space, the sum of the wear of the surfaces brought together is as small as possible.
  • the opposite curvature behavior has a negative impact on the surface pressure.
  • a shift of curve D from the position shown in FIG. 8 towards curve C means less wear on the piston at the expense of the stator
  • a shift of curve D towards curve B means less wear on the stator at the expense of the piston.
  • FIG. 9 relates to the modified embodiment described above, in which the annular piston represented by the contour line F of its shaft surface does not slide on the stator shaft surface represented by curve G, but on - -
  • roller 66 is mounted in a slot, not shown, formed in the shaft surface of the annular piston, so as to be freely rotatable about an axis of rotation directed radially with respect to the piston axis, which is designated by the bearing center 68.
  • the exact course of the piston contour F is not critical as long as it is ensured that the contour is withdrawn to such an extent that it cannot touch the stator contour G during a piston revolution.

Abstract

L'invention concerne une pompe à piston rotatif comprenant un corps (10), un piston annulaire (18) se présentant sous la forme d'une section tubulaire, ce piston étant relié de façon solidaire en rotation à un arbre (22) et guidé de façon rotative et déplaçable axialement dans un espace annulaire (28, 30) du corps, cet espace étant coaxial à l'arbre. Au moins un canal d'entrée et au moins un canal de sortie sont ménagés dans le corps de telle sorte que l'ouverture d'entrée ou l'ouverture de sortie côté espace annulaire soit située dans une zone axiale d'une surface extérieure de l'espace annulaire, cette zone étant déterminée par la distance axiale maximale entre les creux d'onde des surfaces terminales se faisant face. Cette pompe se caractérise en ce que le piston annulaire comporte des poches de commande ouvertes sur la surface terminale axiale, ces poches servant à commander les ouvertures d'entrée et de sortie. Les caractéristiques des poches de commande (38) et des ouvertures d'entrée et de sortie sont choisies de telle sorte qu'un débit volumétrique maximal du fluide à acheminer soit rendu possible par l'ouverture d'entrée (40) en cas de déplacement du piston entre le point mort supérieur et le point mort inférieur et par l'ouverture de sortie (56) en cas de déplacement du piston entre le point mort inférieur et le point mort supérieur.
EP02787733A 2001-11-20 2002-11-19 Pompe a piston rotatif Withdrawn EP1448895A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10156835A DE10156835C1 (de) 2001-11-20 2001-11-20 Drehkolbenpumpe
DE10156835 2001-11-20
PCT/EP2002/012960 WO2003044372A1 (fr) 2001-11-20 2002-11-19 Pompe a piston rotatif

Publications (1)

Publication Number Publication Date
EP1448895A1 true EP1448895A1 (fr) 2004-08-25

Family

ID=7706286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02787733A Withdrawn EP1448895A1 (fr) 2001-11-20 2002-11-19 Pompe a piston rotatif

Country Status (6)

Country Link
US (1) US20050019195A1 (fr)
EP (1) EP1448895A1 (fr)
JP (1) JP2005509801A (fr)
AU (1) AU2002352059A1 (fr)
DE (2) DE10164813B4 (fr)
WO (1) WO2003044372A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102004019373B4 (de) * 2004-04-21 2013-04-18 Peter Schnabl Drehkolbenmaschine
FR2882795B1 (fr) * 2005-03-01 2007-05-11 Baxi S A Sa Pompe et installation d'alimentation d'un dispositif consommateur de liquide au moyen d'une telle pompe
US20070287775A1 (en) * 2006-06-09 2007-12-13 Wheelock Brian C Low viscosity curable compositions
CN103470466B (zh) 2007-12-10 2016-08-17 拜耳医疗保健公司 连续的流体输送系统和方法
US8539931B1 (en) 2009-06-29 2013-09-24 Yousry Kamel Hanna Rotary internal combustion diesel engine
CN107427411B (zh) 2015-01-09 2021-04-02 拜耳医药保健有限公司 具有多次使用可丢弃套件的多流体递送系统及其特征
CN106315593A (zh) * 2016-07-25 2017-01-11 汪承源 一种超微孔纳米SiO2的制法

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US205868A (en) * 1878-07-09 Improvement in rotary steam-engines
US686809A (en) * 1900-06-28 1901-11-19 Frederick W Jaeger Combined steam and gas engine.
FR693534A (fr) * 1930-04-08 1930-11-21 Pompe à haute pression
US2896590A (en) * 1957-04-05 1959-07-28 Garrett Corp Fluid motor
AT281605B (de) * 1967-12-28 1970-05-25 Albert Hoeffleur Schubkolbenpumpe oder -motor
DE2733574A1 (de) * 1977-07-26 1979-02-08 Hans Frank Drehkolbenmaschine
CH623631A5 (en) * 1978-07-18 1981-06-15 Paul Ernest Rey Rotary piston machine
GB2075122A (en) * 1980-04-14 1981-11-11 Jayasooriya L Rotary positive-displacement fluid-machines
US4854837A (en) * 1987-09-15 1989-08-08 Cordray International Corporation Rotary actuated pump or motor
DE19953168A1 (de) * 1999-11-04 2001-05-10 Peter Schnabl Drehkolbenmaschine

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Title
See references of WO03044372A1 *

Also Published As

Publication number Publication date
US20050019195A1 (en) 2005-01-27
DE10164813B4 (de) 2004-11-18
JP2005509801A (ja) 2005-04-14
AU2002352059A1 (en) 2003-06-10
WO2003044372A1 (fr) 2003-05-30
DE10156835C1 (de) 2003-04-30
DE10164813A1 (de) 2003-10-23

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