EP1400692B1 - Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben - Google Patents

Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben Download PDF

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Publication number
EP1400692B1
EP1400692B1 EP03450186A EP03450186A EP1400692B1 EP 1400692 B1 EP1400692 B1 EP 1400692B1 EP 03450186 A EP03450186 A EP 03450186A EP 03450186 A EP03450186 A EP 03450186A EP 1400692 B1 EP1400692 B1 EP 1400692B1
Authority
EP
European Patent Office
Prior art keywords
lift
compressor
control valve
piston
valve
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.)
Expired - Fee Related
Application number
EP03450186A
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German (de)
English (en)
French (fr)
Other versions
EP1400692A1 (de
Inventor
Bernhard Dr. Spiegl
Peter Dr. Steinrück
Gunther Dr. Machu
Michael Miks
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.)
Hoerbiger Kompressortechnik Holding GmbH
Original Assignee
Hoerbiger Kompressortechnik Holding GmbH
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
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Publication of EP1400692A1 publication Critical patent/EP1400692A1/de
Application granted granted Critical
Publication of EP1400692B1 publication Critical patent/EP1400692B1/de
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • 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 continuous flow control of a Reciprocating compressor, wherein an at least one automatic suction valve of the compressor arranged Abhebegreifer means of a switchable via a control valve with Gas pressure can be acted upon lifting piston at least one sealing element of the suction valve over a so controllable part of the working stroke of the compressor holds open, as well as a corresponding reciprocating compressor with continuous flow control, with a arranged on at least one automatic suction valve of the compressor Abhebegreifer, the by means of a switchable via a controllable control valve with gas pressure acted lift-off piston at least one sealing element of the suction valve via a controllable part of the Operating stroke of the compressor keeps open.
  • Compressors with also known as sudströmregelungen stepless Flow rate regulations of the type described are known. See for example US 2,296,304 A, AT 403835 B, US 2,626,100 A or US 5,378,117 A.
  • the delivery force of the sealing element of the suction valve influencing Abhebegreifers a pressurized with gas lift-off cylinder or the pressure acting on the lift-off piston provided or adjusted. This pressure is essentially always constant and is either over a Pressure regulator or via pulsating switching control valves set.
  • This type of flow regulation makes use of the fact that the held open by the lift-off gripper sealing element of the suction valve during the compression stroke attacking flow force - which in the sequence as remindströmkraft is referred to - with the progressive crank angle during the compression stroke initially rises, passes through a maximum corresponding to the piston speed, and at the end of the compression stroke when reaching the top dead center of the piston against Zero goes.
  • the crank angle are set at which the lifting force of the remindströmkraft (together with Any feathering of the sealing element) is overcome, bringing the held from the open Sealing element and the Abhebegreifer existing arrangement in the closing direction of the Suction valve is accelerated.
  • the crank angle of closing can be of the suction valve continuously between the bottom dead center and the maximum of Return flow corresponding crank angle (and thus the corresponding flow rate of the compressor).
  • Another disadvantage is that for setting a certain flow rate necessary, and this directly influencing gas pressure in the lifting cylinder of many parameters, how gas density, operating pressure, speed of the compressor and the like depends, which requires complicated and error-prone additional control methods or mechanisms.
  • this form of regulation is also for Damage to valves responsible.
  • the delivery and retraction of the gripper over Conventional diaphragm cylinder or cylinder is due to the large volumes, the high Dead volume, the small supply cross-sections, high line lengths, small switching cross sections and large switching times of the control valves only within several compression cycles possible.
  • the sealing element of the suction valve usually a Valve plate, during delivery or retraction several times against the gripper jaws beaten. This can accelerate or trigger the breakage of valve plates.
  • Constant pressures in the pressure vessel of compressors with conventional ON / OFF Control are dependent on the storage volume and can only be achieved by frequent switching between idle and full load (several times per minute).
  • Components of the piston and diaphragm cylinders are i.a. not suitable for frequent switching and subject to increased Wear.
  • Object of the present invention is operated by gas pressure simple vomströmregelitch to improve the type mentioned so that the mentioned disadvantages not occur and in particular the mentioned limitations of the control range as well the negative effects of fluctuations in the necessary lift-off gas pressure on simple Way can be avoided.
  • This object is according to the present invention in a method of the preamble mentioned type solved in that the lifting piston acting on the gas pressure during the time in which the control valve is closed, always above that to overcome the maximum possible Ruströmkraft gas pressure is required and that on the quick-acting control valve in each period of the power stroke, a controllable Partial bleeding of the lift-off cylinder is carried out until the suction valve is closed, the depending on the to be vented, from displacement of Abhebezylinders and Dead space between control valve and lift-off piston existing, volume, depending From the opening cross section of the control valve, and in dependence on the operation of the Reciprocator used gas resulting in total theoretical venting time venting volume at most approximately equal to or less than twice the duration of a Working stroke of the compressor is.
  • the fast-switching control valve pipes in each Period of the power stroke to a certain crank angle a partial ventilation of the Lifting cylinder, whereby the gas pressure drops in the lifting cylinder.
  • this gas pressure or the resulting lifting force falls below a threshold, in the balance with the remindströmkraft and a possible feathering of the sealing element prevails, closes the previously held open suction valve, whereby the normal compression or Promotion of the compressor with correspondingly reduced flow rate begins.
  • that previously closed open suction valve closes in this way, it is characterized by the in the Working space of the compressor cylinder constructive pressure locked and opens only on Beginning of the next suction cycle again.
  • the lifting cylinder is closed by closing the described partial bleeding inducing control valve before the next working cycle of the Compressor again with that to overcome the maximum possible montströmkraft required gas pressure applied, so that a secure holding open the sealing element of the suction valve is guaranteed until the next vent by the control valve.
  • the leadership of the lift-off gripper and / or the control valve with the Lifting cylinder and / or piston form a constructive unit, which is very simple and Compact manner allows for executions, the minimum dead space of the above Have type.
  • the control valve is in a further embodiment of the invention as electromagnetic actuated 3/2-way valve designed and preferably switched so that it is in the de-energized Condition applied to the lifting cylinder with gas pressure.
  • the compressor with open suction valve which by lowering the pressure acting on the lifting cylinder gas pressure of the lifting gripper retracted and so that the compressor can be brought to full load.
  • an emergency operation without stepless control possible.
  • the lifting cylinder directly in the Combination control valve and lift gripper integrated or molded together.
  • the Control valve is in the immediate vicinity of the lifting cylinder within the suction valve or the gripper guide positioned and forms a 3/2-way valve.
  • the valve switches Optionally, the gas supply or the discharge line to the lift-off cylinder.
  • the middle Switch position is overrun very quickly and can not be controlled directly. Due to the design with very low dead volumes, partly due to short Cable lengths between lifting cylinder and control valve, combined with a fast-switching Solenoid valve, can be a very rapid response and delivery of the lift-off gripper be realized in every work cycle.
  • control valve is subjected to process gas under appropriate pressure, preferably in that it is connected to a storage volume with the Working space of the compressor via a check valve is in communication.
  • process gas under appropriate pressure, preferably in that it is connected to a storage volume with the Working space of the compressor via a check valve is in communication.
  • This can be on a supply of separate gas for loading the Abhebezylinders from the outside be waived, but what an additional connection from the working space of the compressor about the storage volume with the control valve requires.
  • the lifting piston can in a further embodiment of the invention in the field of his End positions the inflow and / or discharge of the pressurizing gas to the lifting cylinder partially shut off, bringing in a simple way a pneumatic cushioning for the lifting piston is realized.
  • FIG. 1 shows an axially cut suction valve of an inventively designed reciprocating compressor
  • Fig. 2 the arrangement of FIG. 1 opened in a means of Abhebegreifers held position of the sealing element of the suction valve
  • Fig. 3 shows another embodiment according to the invention in a substantially corresponding to FIG. 1 representation, Fig. 4, the detail IV of Fig. 3 but in another switching position of the control valve
  • Fig. 5 a Another embodiment of the invention in a turn substantially Fig. 1 corresponding Representation
  • Fig. 5 and Fig. 6 show embodiments of the invention in a substantially in turn Fig. 1 corresponding representation, Fig.
  • FIG. 7 and 8 show the relationship between the gas pressure in the lifting cylinder and the movement of the lift-off piston or gripper for different control angles [° CA (crank angle)] of Control valve in each case different sized clean rooms or theoretical venting times and
  • FIG. 9 shows a partially schematic cross section through an invention trained reciprocating compressor.
  • FIGS. 1 to 6 is on the suction valve 1 of the compressor arranged a Abhebegreifer 2, by means of a switchable via a control valve 3 with Gas pressure can be acted upon lifting piston 4 at least one sealing element 5 of the suction valve 1 holds open over a controllable part of the working stroke of the compressor.
  • the lift-off piston 4 is stationary here and centrally fixed to the suction valve 1 and forms with its outer periphery thus directly in the axial direction, the guide for the Abhebegreifer 2 and the sleeve-like upper part of the thus axially movable lifting cylinder 6 Lifting gripper 2. This is in the position shown in Fig.
  • control valve 3 In the area of the lift-off 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 other leads or the associated control electrics is not shown here.
  • the screwed on top of the stationary lift-off piston 4 and at the same time also for fixing the electromagnet 14 or the entire control valve 3rd in the lifting piston 4 serving housing 16 has outside the housing wall 17 a connection opening 18 for the lifting cylinder 6 to be supplied via the control valve 3, under Compressive 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 to the control valve 3 passes.
  • Compressive gas preferably directly the process gas
  • the power supply to the electromagnet 14th interrupted, whereby the switching element 13 is pressed under the action of the spring 20 downward is and thus (as shown in FIG. 2) in the representation upper seat in the seat body 12th releases and closes the lower one.
  • This can be done via the holes 22 in the seat body 12th and the subsequent bores 21 in the lifting piston 4 pressure in the lifting cylinder 6 constructed be, which subsequently in the Abhebezylinder 6 together with Abhebegreifer 2 against the effect of the coil spring 7 presses down and thus the sealing element 5 of the Suction valve 1 in contact with the valve catcher 26 holds open.
  • the control valve 3 is due to its design, operation and Control quickly switching and thus allows in each period of the power stroke one controllable partial venting of Abhebezylinders 6 to the desired closing of the suction valve to a certain crank angle.
  • the to be vented Volume consists of the actual working volume in the lifting cylinder 6 and the essentially defined by the volumes of the holes 21 and 22 dead spaces, which are to be kept as small as possible.
  • FIG. 3 While in the embodiment of FIGS. 1 and 2, the control valve 3 in the de-energized Condition (as shown in FIG. 1) is applied to the interior of the Abhebezylinders 6 with gas pressure and thus the suction valve 1 holds open, is in the otherwise comparable or largely identical embodiment of FIG. 3 and 4 provided that the control valve. 3
  • the seat body 12 and switching element 13 in FIG. 3 illustrated current-applied state of the electromagnet 14, the lifting cylinder. 6 supplied with lift-off 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 Lifting cylinder 6 is open - the lower valve seat (in the direction of the vent) is closed.
  • FIG. 5th a connecting line 27 in the center screw of the suction valve 1 and the integral central part here, which in the upper area in the turn fixed Lifting piston 4 passes, provided.
  • a check valve 28 On the work space, not shown here the compressor facing the lower side of the connecting hole 27 is a check valve 28 provided, which on the above lying side of the connecting line 27 always sufficient pressure ensured - in addition, could also be here not shown, separate storage volume may be provided to the supply increase under appropriate pressure actuating gas.
  • actuating gas corresponds to the execution of Fig. 5 substantially apparent from FIGS. 1 and 2. Same parts are with the same reference numerals - with respect to the description of the function is on the referenced above.
  • the lifting cylinder 6 together with the lifting piston 4 is now no longer combined with the lifting gripper 2 or its central guide dome 29 but only with the control valve 3 together with its electromagnetic actuation.
  • the whole formed actuation unit is separately on the housing wall 17 of the compressor fitted and is operatively on the piston rod 30 of the lifting piston 4 with a pressure plate 31 on the Abhebegreifer 2 in conjunction, which from the other side ago with one of the coil spring 7 according to FIGS. 1 to 5 corresponding spring 32 loaded is.
  • Other identical or at least functionally equivalent components are components again provided with the same reference numerals as in Figs. 1 to 5 - with respect to the description the function of the arrangement of FIG. 6 is based on the above statements refer to the effective substantially identical embodiment of FIGS. 1 and 2.
  • 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, 42nd and 44 of the control valve 12 for a small selected according to the invention venting time (T ⁇ 0.4 x cycle time) during a working cycle of the compressor.
  • the magnet 4 of the control valve 3 of FIG. 1 is initially until the time or Crank angle 33 energized.
  • the lifting cylinder 6 is vented, the Abhebgreifer is held by the closing spring 7 in the retreat position.
  • the connection between the Pressure supply (port 18) and the lifting cylinder 6 releases the pressure increases in the lifting cylinder 6 at. If (at 34) the compressive force caused by the spring 7 restoring force exceeds the movement of the lift-off gripper 2.
  • the lift-off gripper 2 expands the gas contained in the lift-off cylinder 6, whereby the pressure in the lifting cylinder 6 initially falls 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 (item 35)
  • the pressure in the lifting cylinder 6 increases again on the Value of the inlet pressure.
  • the movement of the Lifting gripper 2 is thereby braked.
  • the gripper 2 reaches its illustrated in Fig. 1 End position at 40 with greatly reduced speed.
  • the switching time 37 was selected so that the lift-off gripper 2 at a crank angle of 180 ° is already withdrawn so far that the sealing element 5 in this moment the valve seat 10 is reached, which during the crank angle with this Compression phase no gas is pushed back into the suction chamber. Of the Compressor therefore compresses the full delivery quantity.
  • the switching time of the control valve 3 is selected later, for example at point 46, retarded the retraction movement 41 of the Abhebegreifers 2.
  • the valve plate is a closed later and part of the cylinder by the compressor sucked gas is pushed back into the suction chamber and thus the delivery quantity reduced.
  • the control valve 3 is actuated later, for example at 42, then the delivery quantity is further reduced because the one represented by the line 43 is also reduced Retraction of the lifting gripper 2 is delayed.
  • the retraction movement (line 45) is delayed so far that no compaction necessary for pushing out on the pressure side at the closing time of the Suction valve 1 can still be achieved in the working space of the compressor enclosed gas can (delivery quantity zero).
  • FIG. 8 shows the course of the lifting gripper movement and of the control pressure as in FIG. 7 for a significantly extended compared to FIG. 7 venting time T (T ⁇ 2x cycle time).
  • the suction valve 1 operates unaffected by the gripper movement and the compressor delivers the full flow rate. If the switching time of the control valve 3 is successive chosen later, the stroke of the lift-off gripper 2 becomes larger, closing the valve plate is delayed and thus reduces the delivery volume of the compressor.
  • the point 44 results in a retraction movement represented by the line 45, which ends at 360 ° crank angle and corresponds to a zero promotion of the compressor. Further delay of the switching point z.B .: in the point 47 (line 48) prevented a timely return of the gripper to the starting position.
  • Fig. 9 is a schematic reciprocating compressor according to the invention with stepless Flow control according to the present invention shown.
  • the one in the cylinder 50 reciprocating piston 51 is via an extended piston rod 52 and a Universal joint 53 actuated by a connecting rod 54, which from the crankshaft 55 by means of a not shown here, mostly electric drive motor is driven.
  • At 56 is a on the crankshaft co-rotating fixed flywheel referred to.
  • suction valves 1 are arranged in two working volumes, which are formed, for example, according to FIGS. 1 to 4 and in the manner described a allow continuous flow control.
  • the associated pressure valves 57 are only indicated. These are usually similar to the suction valves, but without any possibility of regulation.
  • the intake manifold is denoted by 58 and the pressure manifold by 59.
  • connection openings 18 see also Fig. 1 and 3) pressure lines 60 connected, the operating pressure for the lifting piston 4 or Lifting cylinder 6 (see FIGS. 1 to 3) from a pressure source 61 forth ago.
  • the electric Actuation of the electromagnets 14 of the control valves 3 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)
EP03450186A 2002-09-19 2003-08-13 Hubkolbenkompressor und Verfahren zur stufenlosen Fördermengenregelung desselben Expired - Fee Related EP1400692B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0141702A AT413234B (de) 2002-09-19 2002-09-19 Hubkolbenkompressor und verfahren zur stufenlosen fördermengenregelung desselben
AT14172002 2002-09-19

Publications (2)

Publication Number Publication Date
EP1400692A1 EP1400692A1 (de) 2004-03-24
EP1400692B1 true EP1400692B1 (de) 2005-07-13

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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 (zh)
EP (1) EP1400692B1 (zh)
JP (1) JP2004108371A (zh)
CN (1) CN100373052C (zh)
AT (1) AT413234B (zh)
DE (1) DE50300753D1 (zh)

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DE10005388A1 (de) 2000-02-07 2001-09-20 Compart Compressor Technology Vorrichtung und Verfahren zur Regelung eines Ventils
GB0007918D0 (en) 2000-03-31 2000-05-17 Npower Passive valve assembly
AT413234B (de) 2002-09-19 2005-12-15 Hoerbiger Kompressortech Hold Hubkolbenkompressor und verfahren zur stufenlosen fördermengenregelung desselben

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DE102007007301B4 (de) 2006-02-07 2018-10-25 General Electric Co. Systeme und Verfahren zur Erfassung des Schließens eines Ansaugventils

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EP1400692A1 (de) 2004-03-24
JP2004108371A (ja) 2004-04-08
US7331767B2 (en) 2008-02-19
CN100373052C (zh) 2008-03-05
DE50300753D1 (de) 2005-08-18
AT413234B (de) 2005-12-15
CN1493787A (zh) 2004-05-05
ATA14172002A (de) 2005-05-15
US20040091365A1 (en) 2004-05-13

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