EP1400692A1 - Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben - Google Patents
Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben Download PDFInfo
- Publication number
- EP1400692A1 EP1400692A1 EP03450186A EP03450186A EP1400692A1 EP 1400692 A1 EP1400692 A1 EP 1400692A1 EP 03450186 A EP03450186 A EP 03450186A EP 03450186 A EP03450186 A EP 03450186A EP 1400692 A1 EP1400692 A1 EP 1400692A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- lifting
- compressor
- control valve
- valve
- piston
- 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.)
- Granted
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/08—Actuation of distribution members
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- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
- F04B49/243—Bypassing by keeping open the inlet valve
Definitions
- the invention relates to a method for the infinitely variable control of a delivery rate Reciprocating compressor, one on at least one automatic suction valve of the compressor arranged lifting gripper by means of a switchable control valve
- Lifting piston to which gas pressure can be applied via at least one sealing element of the suction valve keeps a controllable part of the compressor's working cycle open, as well as one corresponding reciprocating compressor with stepless flow control, with a on at least one automatic suction valve of the compressor arranged lifting gripper, by means of a lifting piston which can be acted upon by gas pressure via a switchable control valve at least one sealing element of the suction valve via a part of the valve that can be controlled thereby
- the compressor's operating cycle keeps open.
- This type of funding regulation takes advantage of the fact that the sealing element of the suction valve kept open by the lifting gripper during of the compression stroke attacking flow force - which subsequently as the backflow force is designated - with the progressive crank angle during the compression stroke initially rises, passes a maximum corresponding to the piston speed, and at the end of the compression stroke when the top dead center of the piston is reached Zero goes.
- a disadvantage of the described method or the corresponding known ones Facilities is immediate that closing crank angle that occurs after the occurrence of the maximum the backflow force are naturally not realizable, from which one restricted control range, which is between about 40 to 100% of the maximum delivery rate lies, results.
- one restricted control range which is between about 40 to 100% of the maximum delivery rate lies.
- PET bottle production for example, there are one large number of air compressors in use, which have a strongly fluctuating air requirement subject to 10 to 100% while maintaining a very constant final pressure have to.
- Another disadvantage is that for setting a certain flow rate necessary, and this directly influencing gas pressure in the lifting cylinder of many parameters, such as gas density, operating pressure, speed of the compressor and the like, which requires complicated and error-prone additional control procedures or mechanisms.
- this form of regulation is also for Damage to valves responsible. Delivery and withdrawal of the gripper via conventional diaphragm cylinder or cylinder is due to the large volume, the high Dead volume, the small cable cross-sections, long cable lengths, small switching cross-sections and large switching times of the control valves only within several compression cycles possible. This makes the sealing element of the suction valve, usually a Valve plate, against the gripper teeth several times during infeed or retraction beaten. This can accelerate or trigger the breakage of valve plates.
- Constant pressures in the pressure vessel of compressors with conventional ON / OFF Regulation depends on the storage volume and can only be switched by frequent switching realize between idle and full load (several times per minute). Components of the piston and Membrane cylinders are generally not suitable for frequent switching and are subject to increased Wear.
- the object of the present invention is simple backflow controls actuated by gas pressure of the type mentioned to improve so that the disadvantages mentioned not occur and in particular the mentioned restrictions of the control range as well the negative effects of fluctuations in the required lifting gas pressure on simple Way can be avoided.
- the gas pressure acting on the lifting piston is no longer immediate responsible for the closing crank angle - if this pressure only for all operating conditions or addressed parameters above that to overcome the maximum possible backflow force required gas pressure is also fluctuations in the mentioned parameters have no significant influence on the flow rate control.
- the fast switching control valve leads to a specific one in each period of the work cycle Crank angle a partial ventilation of the lifting cylinder, with which the gas pressure in Lift cylinder falls off. As soon as this gas pressure or the resulting lifting force falls below a threshold at which equilibrium with the return flow force and any The sealing element is springed, the suction valve, which was previously open, closes, with which the normal compression or promotion of the compressor with a correspondingly reduced Delivery rate.
- the guidance of the lifting gripper and / or the control valve with the Lift cylinder and / or piston form a structural unit, which is very simple and compact manner enables executions that minimal damage space of those mentioned above Have kind.
- control valve is electromagnetic actuated 3/2-way valve executed and preferably switched so that it is in the de-energized Condition applied to the lifting cylinder with gas pressure.
- the compressor runs in this way with the suction valve held open, with which the lifting gripper by lowering the gas pressure acting on the lifting cylinder withdrawn and the compressor can be brought to full load. In order to emergency operation without stepless regulation is also possible.
- the lifting cylinder can thus directly in the Combination control valve and lifting gripper integrated or formed together.
- the control valve is in the immediate vicinity of the lifting cylinder inside the suction valve or the gripper guide positioned and forms a 3/2-way valve.
- the valve switches either the gas supply or the blow-off line on the lifting cylinder.
- the design corresponds to a 3/3-way valve, the middle one Switch position is passed very quickly and cannot be controlled directly). Due to the design with very low dead volumes, partly due to short Cable lengths between the lifting cylinder and control valve, combined with a quick-switching Solenoid valve, can respond very quickly and deliver the lifting gripper can be realized in every work cycle.
- this is Control valve acted upon on the input side with process gas under appropriate pressure, preferably in which it is connected to a storage volume which is connected to the Working area of the compressor is connected via a check valve. So that can a supply of separate gas to act on the lifting cylinder from the outside be dispensed with, but this is an additional connection from the working area of the compressor required over the storage volume with the control valve.
- the lifting piston can be in the region of its End positions partially the inflow and / or outflow of the pressurized gas to the lifting cylinder shut off, which is a simple way of pneumatic end position damping for the lifting piston is realized.
- FIG. 1 shows an axially cut suction valve of a reciprocating compressor designed according to the invention
- Fig. 2 opens the arrangement of FIG. 1 in a by means of the lifting gripper held position of the sealing element of the suction valve
- Fig. 3 shows another embodiment according to the invention in a representation corresponding essentially to FIG. 1
- FIG. 4 shows detail IV from FIG. 3, however, in a different switching position of the control valve
- FIG. 5 Another embodiment of the invention in a substantially corresponding to Fig. 1 again 5 and 6 show exemplary embodiments according to the invention in a representation essentially corresponding to FIG. 1, FIGS.
- FIG. 7 and 8 show the relationship between the gas pressure in the lifting cylinder and the movement of the lifting piston or gripper for various steering angles [° KW (crank angle)] of the Control valve with different sized damage areas or theoretical ventilation times and
- FIG. 9 shows a partially schematic cross section through a device according to the invention trained reciprocating compressor.
- a lifting gripper 2 is arranged, which by means of a switchable control valve 3 Lifting piston 4 which can be subjected to gas pressure, at least one sealing element 5 of the suction valve 1 keeps open via a part of the compressor's work cycle that can be controlled thereby.
- the lifting piston 4 is stationary here and fixed centrally on the suction valve 1 and forms with its outer circumference thus directly in the axial direction the guide for the lifting gripper 2 or the sleeve-like upper part of the axially movable lifting cylinder 6 Lifting gripper 2. This is in the position shown in Fig.
- control valve 3 In the area of the lifting piston 4, the control valve 3 is in a central bore 11 used, which consists essentially of a seat body 12, a switching element 13 and an electromagnet 14 shown only schematically.
- the electromagnet 14 is provided on its upper side in the illustration with screwed contacts 15, the serve for switchable power supply and protrude from a housing 16 upwards.
- the further connecting lines and the associated control electronics are not shown here.
- the screwed on the top of the fixed lifting piston 4 and at the same time also for fixing the electromagnet 14 or the entire control valve 3 in the lifting piston 4 serving housing 16 has a connection opening outside the housing wall 17 18 for the to be fed to the lifting cylinder 6 via the control valve 3 below Pressurized gas (preferably directly the process gas), which has a central Bore 19 in the electromagnet 14 and the spring 20 at the top of the switching element 13 receiving space reaches the control valve 3.
- Pressurized gas preferably directly the process gas
- the pressure acting on the lift-off piston 4 or lift-off cylinder 6 is greater than that Connection opening 18 supplied actuating gas is always above that to overcome maximum possible backflow force on the sealing element 5 required pressure, so that a safe Keeping the sealing element 5 of the suction valve 1 open over the entire working cycle of the Compressor is possible.
- the control valve 3 is according to its design, operation and Activation quickly switching and thus enables one in every period of the work cycle controllable partial ventilation of the lifting cylinder 6 until the desired closing of the suction valve at a certain crank angle.
- the one to be vented Volume consists of the actual working volume in the lifting cylinder 6 and the damage spaces essentially defined by the volumes of the bores 21 and 22, which are to be kept as small as possible.
- the control valve 3 in the de-energized State (according to FIG. 1) the interior of the lifting cylinder 6 is pressurized with gas pressure and so that the suction valve 1 keeps open, is otherwise comparable or 3 and 4 largely identical embodiment that the control valve 3rd due to a different design of the seat body 12 and the switching element 13 in Fig. 3 illustrated current-charged state of the electromagnet 14, the lifting cylinder 6 supplied with lifting pressure.
- the upper valve seat on the seat body 12 and thus the supply of pressurized actuating gas via the connection opening 18 to the interior of the Lift cylinder 6 is open - the lower valve seat (in the direction of ventilation) is closed.
- the lifting cylinder 6 together with the lifting piston 4 is now no longer combined with the lifting gripper 2 or its central guide mandrel 29 but only with the control valve 3 including its electromagnetic actuation.
- the whole actuating unit formed therefrom is separate on the housing wall 17 of the compressor placed and is effective on the piston rod 30 of the lifting piston 4 with a pressure plate 31 on the lifting gripper 2 in connection, which from the other side forth loaded with a spring 32 corresponding to the coil spring 7 according to FIGS. 1 to 5 is.
- Other identical or at least functionally equivalent components are again provided with the same reference numerals as in FIGS. 1 to 5 - with regard to the description the function of the arrangement according to FIG. 6 is based on the above statements referred to the essentially identical embodiment according to FIGS. 1 and 2.
- control valve 3 and lift-off piston 4 are kept as small as possible in order to be sufficient rapid partial ventilation of the working volume of the lifting cylinder 6 including the clearance until the previously open suction valve 1 closes during each work cycle of the compressor.
- FIGS. 7 and 8 Process for the continuous flow control of a reciprocating compressor explained in more detail.
- Fig. 7 shows the course of gripper movement (dashed lines) and control pressure (solid lines) in the lifting cylinder 6 for different switching times 37, 40, 42 and 44 of the control valve 12 for a venting time selected according to the invention to be small (T ⁇ 0.4 x cycle time) during one cycle of the compressor.
- the magnet 4 of the control valve 3 according to FIG. 1 is initially up to the point in time or Crank angle 33 is energized.
- the lifting cylinder 6 is thus vented, the lifting gripper is held in the retracted position by the closing spring 7.
- the connection between the Pressure supply (connection opening 18) and the lifting cylinder 6 releases, the pressure increases in the lifting cylinder 6.
- the compressive force is the restoring force caused by the spring 7 exceeds, the movement of the lifting gripper 2 begins.
- the gas contained in the lifting cylinder 6 expands, whereby the pressure in the lifting cylinder 6 initially drops because of the limited opening cross section of the control valve 3 can not flow enough gas.
- the gripper 2 has reached its end position (point 35)
- the pressure in the lifting cylinder 6 rises again to Value of the inlet pressure.
- the electromagnet 14 of the control valve 3 is again energized at point 37, escapes the gas enclosed in the lifting cylinder 6 and the control pressure falls.
- the contact pressure acting on the gripper 2 drops and falls below the point 38 which from the closing force acting on the sealing element 5 of the valve springs 9 and Restoring force of the spring 7 composite, acting in the closing direction of the suction valve 1 Total force.
- the speed of the gripper 2 initially increases, which from the steeper course of the movement curve can be seen from point 38.
- the cross section of the bores 21 when approaching the lifting cylinder 6 is reduced in its end position, the control pressure increases after Going through a minimum again and reaching a maximum at 39.
- the movement of the Lifting gripper 2 is braked as a result.
- the gripper 2 reaches the one shown in FIG. 1 End position at 40 with greatly reduced speed.
- the switching time 37 was selected so that the lifting gripper 2 at a crank angle of 180 ° has already been withdrawn so far that the sealing element 5 in reaches the valve seat 10 at this moment, thus during the crank angle commencing the compression phase, no gas is pushed back into the suction space.
- the compressor therefore compresses the full delivery quantity.
- the retraction movement 41 of the lifting gripper 2 is delayed.
- the valve plate becomes one later closed and part of the by the working cylinder of the compressor sucked gas is pushed back into the suction chamber and thus the delivery quantity reduced.
- the control valve 3 is actuated even later, for example at 42, then the delivery quantity is further reduced because the one represented by the line 43 Retraction movement of the gripper 2 is delayed.
- the retraction movement (line 45) is so late that no compression necessary for pushing out on the pressure side at the time of closing the Suction valve 1 can still be reached in the working space of the compressor enclosed gas can (delivery quantity zero).
- FIG. 8 shows the course of the lifting gripper movement and the control pressure as in FIG. 7 for a significantly longer venting time T (T ⁇ 2x cycle time) compared to FIG. 7.
- the suction valve 1 works unaffected by the gripper movement and the compressor delivers the full delivery rate.
- the switching time of the control valve 3 is successive chosen later, the stroke of the lifting gripper 2 is greater, the closing of the valve plate is delayed and thus the delivery quantity of the compressor is reduced.
- the switching point with point 44 there is a withdrawal movement represented by line 45, which ends at 360 ° crank angle and corresponds to zero delivery of the compressor. Further switching point delay e.g. in point 47 (line 48) prevented timely return of the gripper to the starting position.
- the venting time T is selected, for example, about 3 times the working cycle duration the mentioned gradients become so flat that the movement of the lifting gripper 2 no longer follows the switching of the control valve 3.
- the movement of the lifting claw 2 is then essentially only by the balance of those acting on the valve plate Influences flow forces and the average pressure in the cylinder 6. Both sizes depend on a variety of parameters.
- the scheme works then according to the known principle of pneumatic backflow regulation mentioned at the beginning with all the associated disadvantages.
- Fig. 9 is a reciprocating compressor according to the invention with a stepless Flow control according to the present invention shown.
- the one in the cylinder 50 reciprocating piston 51 is a piston rod 52 and an out Universal joint 53 actuated by a connecting rod 54, which is driven by the crankshaft 55 by means of a not shown here, mostly electric drive motor is driven.
- At 56 is one Flywheel attached to the crankshaft.
- suction valves 1 are arranged in both working volumes, which are designed for example according to FIGS. 1 to 4 and in the manner described allow stepless flow control.
- On the lower side of the Cylinder 50, the associated pressure valves 57 are only indicated. These are common Similar to the suction valves, only without any control option.
- the intake manifold is designated 58 and the pressure manifold with 59.
- connection openings 18 are at the connection openings 18 (see also Fig. 1 and 3) Pressure lines 60 connected, the actuating pressure for the lifting piston 4 or Feed lifting cylinder 6 (see FIGS. 1 to 3) from a pressure source 61.
- the electrical Activation of the electromagnets 14 of the control valves 3 takes place via control lines 62 from a control unit 63.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
- K(kappa)
- Konstante abhängig vom Isentropenexponenten des beaufschlagenden Gases
K(kappa) = 0,155 für Luft (kappa = 1,4)
Claims (9)
- Verfahren zur stufenlosen Fördermengenregelung eines Hubkolben-Kompressors, wobei ein an zumindest einem selbsttätigen Saugventil (1) des Kompressors angeordneter Abhebegreifer (2) mittels eines über ein schaltbares Steuerventil (3) mit Gasdruck beaufschlagbaren Abhebekolbens (4) zumindest ein Dichtelement (5) des Saugventils (1) über einen damit steuerbaren Teil des Arbeitstaktes des Kompressors offenhält, dadurch gekennzeichnet, dass der den Abhebekolben (4) beaufschlagende Gasdruck während der Zeit, in der das Steuerventil (3) geschlossen ist, stets über dem zur Überwindung der maximal möglichen Rückströmkraft erforderlichen Gasdruck liegt und dass über das schnellschaltend ausgeführte Steuerventil (3) in jeder Periode des Arbeitstaktes eine steuerbare Teilentlüftung des Abhebezylinders (6) bis zum Schließen des Saugventils (1) durchgeführt wird.
- Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass die sich in Abhängigkeita.) vom zu entlüftenden, aus Hubraum des Abhebezylinders (6) und Schadraum zwischen Steuerventil (3) und Abhebekolben (4) bestehenden, Volumen,b.) vom Öffnungsquerschnitt des Steuerventils (3) , undc.) vom zur Betätigung des Abhebegreifers (2) verwendeten Gas
- Hubkolben-Kompressor mit stufenloser Fördermengenregelung, mit einem an zumindest einem selbsttätigen Saugventil (1) des Kompressors angeordneten Abhebegreifer (2), der mittels eines über ein schaltbares Steuerventil (3) mit Gasdruck beaufschlagbaren Abhebekolbens (4) zumindest ein Dichtelement (5) des Saugventils (1) über einen damit steuerbaren Teil des Arbeitstaktes des Kompressors offenhält, dadurch gekennzeichnet, dass die sich in Abhängigkeita.) vom zu entlüftenden, aus Hubraum des Abhebezylinders (6) und Schadraum zwischen Steuerventil (3) und Abhebekolben (4) bestehenden, Volumen,b.) vom Öffnungsquerschnitt des Steuerventils (3), undc.) vom zur Betätigung des Abhebegreifers (2) verwendeten Gas
- Kompressor nach Anspruch 3, dadurch gekennzeichnet, dass der Schadraum zwischen Steuerventil (3) und Abhebekolben (4) maximal annähernd gleich oder kleiner dem zweifachen Hubraum des Abhebezylinders (6) ist.
- Kompressor nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Führung des Abhebegreifers (2) mit Abhebezylinder (6) und -kolben (4) eine konstruktive Einheit bildet.
- Kompressor nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass das Steuerventil (3) mit dem Abhebezylinder (6) und/oder -kolben (4) eine konstruktive Einheit bildet.
- Kompressor nach einem oder mehreren der Ansprüche 3 bis 6, dadurch gekennzeichnet, dass das Steuerventil (3) als elektromagnetisch betätigtes 3/2-Wegeventil ausgeführt und vorzugsweise so beschaltet ist, dass es im stromlosen Zustand den Abhebezylinder (6) mit Gasdruck beaufschlagt.
- Kompressor nach einem oder mehreren der Ansprüche 3 bis 7, dadurch gekennzeichnet, dass das Steuerventil (3) eingangsseitig mit unter entsprechendem Druck stehendem Prozessgas beaufschlagt ist, vorzugsweise indem es mit einem Speichervolumen verbunden ist, das mit dem Arbeitsraum des Kompressors über ein Rückschlagventil (28) in Verbindung steht.
- Kompressor nach einem oder mehreren der Ansprüche 3 bis 8, dadurch gekennzeichnet, dass der Abhebekolben (4) im Bereich seiner Endlagen den Zu- und/oder Ablauf des beaufschlagenden Gases zum Abhebezylinder (6) teilweise absperrt.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT14172002 | 2002-09-19 | ||
AT0141702A AT413234B (de) | 2002-09-19 | 2002-09-19 | Hubkolbenkompressor und verfahren zur stufenlosen fördermengenregelung desselben |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1400692A1 true EP1400692A1 (de) | 2004-03-24 |
EP1400692B1 EP1400692B1 (de) | 2005-07-13 |
Family
ID=31892568
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP03450186A Expired - Fee Related EP1400692B1 (de) | 2002-09-19 | 2003-08-13 | Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben |
Country Status (6)
Country | Link |
---|---|
US (1) | US7331767B2 (de) |
EP (1) | EP1400692B1 (de) |
JP (1) | JP2004108371A (de) |
CN (1) | CN100373052C (de) |
AT (1) | AT413234B (de) |
DE (1) | DE50300753D1 (de) |
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US7331767B2 (en) | 2002-09-19 | 2008-02-19 | Hoerbiger Kompressortechnik Services Gmbh | Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control |
EP2172651A1 (de) | 2008-10-02 | 2010-04-07 | Hoerbiger Kompressortechnik Holding GmbH | Hubkolben-Kompressor |
WO2011009880A1 (de) | 2009-07-23 | 2011-01-27 | Burckhardt Compression Ag | Verfahren zur fördermengenregelung und hubkolben-kompressor mit fördermengenregelung |
EP2511526A1 (de) | 2011-04-14 | 2012-10-17 | Hoerbiger Kompressortechnik Holding GmbH | Hubkolbenverdichter mit Fördermengenregelung |
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AT525119B1 (de) * | 2021-05-10 | 2023-04-15 | Hoerbiger Wien Gmbh | Kolbenkompressor mit variabler Kapazitätsregelung |
US11732707B2 (en) * | 2021-06-08 | 2023-08-22 | Siemens Energy, Inc. | Inlet valve system |
EP4197428A1 (de) | 2021-12-20 | 2023-06-21 | Ziemer Ophthalmic Systems AG | Opthalmologische behandlungsvorrichtung zur bestimmung eines drehwinkels eines auges |
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- 2003-08-13 EP EP03450186A patent/EP1400692B1/de not_active Expired - Fee Related
- 2003-08-13 DE DE50300753T patent/DE50300753D1/de not_active Expired - Lifetime
- 2003-09-17 US US10/664,042 patent/US7331767B2/en not_active Expired - Fee Related
- 2003-09-18 JP JP2003326753A patent/JP2004108371A/ja active Pending
- 2003-09-18 CN CNB031585612A patent/CN100373052C/zh not_active Expired - Fee Related
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Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7331767B2 (en) | 2002-09-19 | 2008-02-19 | Hoerbiger Kompressortechnik Services Gmbh | Method of stepless capacity control of a reciprocating piston compressor and piston compressor with such control |
EP2172651A1 (de) | 2008-10-02 | 2010-04-07 | Hoerbiger Kompressortechnik Holding GmbH | Hubkolben-Kompressor |
WO2011009880A1 (de) | 2009-07-23 | 2011-01-27 | Burckhardt Compression Ag | Verfahren zur fördermengenregelung und hubkolben-kompressor mit fördermengenregelung |
WO2011009879A1 (de) | 2009-07-23 | 2011-01-27 | Burckhardt Compression Ag | Verfahren zur fördermengenregelung und hubkolben-kompressor mit fördermengenregelung |
EP2511526A1 (de) | 2011-04-14 | 2012-10-17 | Hoerbiger Kompressortechnik Holding GmbH | Hubkolbenverdichter mit Fördermengenregelung |
WO2013010687A1 (de) * | 2011-07-20 | 2013-01-24 | Neuman & Esser Gmbh & Co. Kg | Kolbenverdichter |
CN103244399B (zh) * | 2013-04-17 | 2015-05-20 | 台州环天机械有限公司 | 大型往复式压缩机气量无级调节方法与装置 |
CN103244399A (zh) * | 2013-04-17 | 2013-08-14 | 西安交通大学 | 大型往复式压缩机气量无级调节方法与装置 |
CN103233884A (zh) * | 2013-05-10 | 2013-08-07 | 何峰 | 一种往复压缩机负荷无级调节方法 |
CN103233884B (zh) * | 2013-05-10 | 2016-04-13 | 何峰 | 一种往复压缩机负荷无级调节方法 |
CN104329240A (zh) * | 2014-10-16 | 2015-02-04 | 中国科学院上海技术物理研究所 | 直线压缩机用耐高压且保高真空的充排气阀门及制造方法 |
CN105889050A (zh) * | 2015-04-14 | 2016-08-24 | 康茨(上海)压缩机技术服务有限公司 | 一种用于活塞压缩机气阀智能启闭控制方法 |
WO2023217683A3 (de) * | 2022-05-10 | 2024-02-29 | Hoerbiger Wien Gmbh | Vorrichtung zur bereitstellung von wasserstoff |
Also Published As
Publication number | Publication date |
---|---|
AT413234B (de) | 2005-12-15 |
CN1493787A (zh) | 2004-05-05 |
ATA14172002A (de) | 2005-05-15 |
EP1400692B1 (de) | 2005-07-13 |
DE50300753D1 (de) | 2005-08-18 |
CN100373052C (zh) | 2008-03-05 |
JP2004108371A (ja) | 2004-04-08 |
US20040091365A1 (en) | 2004-05-13 |
US7331767B2 (en) | 2008-02-19 |
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