EP2456979B1 - Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement - Google Patents

Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement Download PDF

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Publication number
EP2456979B1
EP2456979B1 EP10751818.5A EP10751818A EP2456979B1 EP 2456979 B1 EP2456979 B1 EP 2456979B1 EP 10751818 A EP10751818 A EP 10751818A EP 2456979 B1 EP2456979 B1 EP 2456979B1
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EP
European Patent Office
Prior art keywords
during
unloader
closing body
valve
regulation
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EP10751818.5A
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German (de)
English (en)
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EP2456979A1 (fr
Inventor
Andreas Allenspach
Roland Aigner
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Burckhardt Compression AG
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Burckhardt Compression AG
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Application filed by Burckhardt Compression AG filed Critical Burckhardt Compression AG
Priority to EP10751818.5A priority Critical patent/EP2456979B1/fr
Priority claimed from PCT/EP2010/060545 external-priority patent/WO2011009879A1/fr
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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
    • 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
    • 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
    • F04B49/246—Bypassing by keeping open the outlet valve
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet

Definitions

  • the invention relates to a method for flow control of a reciprocating compressor according to the preamble of claim 1.
  • the invention further relates to a reciprocating compressor with flow control according to the preamble of claim 13.
  • the pamphlets EP 0801227 A2 and EP 1400692 A1 disclose a method for influencing the pressure-dependent automatic, periodic opening movement of a closing member of a suction valve of a reciprocating compressor by means of a, if necessary, at least over part of the crank circuit acting on the closing member control device. Since the life of mostly suction and pressure side used, automatic compressor valves is primarily influenced by the impact stress at the alternate impact of the actual closing organ on seat or catcher, said document discloses a method in which the suction valve by means of a so-called lift-off gripper before reaching Pressure equilibrium is forcibly opened, in order to avoid a strong instantaneous acceleration of the closing member towards the catcher, which would occur during automatic opening. This allows to reduce the impact load of the compressor valve.
  • This method has the disadvantage that the suction and in particular the compressor valves used on the pressure side still have a high load, in particular when the compressor system is operated according to the method of a continuous backflow control.
  • the suction valve is kept open by means of Abhebegreifers during a partial angle range of the compression stroke and then closed, thereby affecting the flow rate.
  • a disadvantage of this known method is the fact that the closing member of the suction valve and the pressure valve is subject to relatively high wear, which requires a correspondingly high maintenance.
  • the publication WO2008 / 000698 A2 discloses another device for flow control of a reciprocating compressor. From this device has the disadvantage that the compressor side used compressor valve has a high stress.
  • the object of the invention is to form a more advantageous method for controlling the flow rate of a reciprocating compressor.
  • This object is achieved by a method comprising the features of claim 1.
  • Dependent claims 2 to 12 relate to further advantageous method steps.
  • the object is further achieved with a reciprocating compressor having the features of claim 13.
  • the dependent claims 14 and 15 relate to further advantageous embodiments.
  • the object is achieved in particular with a method for regulating the flow rate of a reciprocating compressor by influencing the movement of a closing organ of an automatic suction valve by means of a screed driven by a control device during at least part of a cycle of the crank circuit, wherein the method comprises a stepless backflow control, wherein the Abhebegreifer during a first portion of the cycle of the crank circuit against the closing member and prevents its closure, and wherein the Abhebegreifer is retracted during a second portion of the cycle of the crank circle and the closing member is closed, and wherein the method further comprises an intermittent control in which the interceptor prevents the closing of the closing member during a whole cycle of the crank circuit, wherein the flow rate is controlled at least by a combination of continuous backflow control and intermittent control, and wherein the closing member is influenced by the control device and the Abhebegreifer such that a closing member of an automatic pressure valve of the reciprocating compressor, at least during a predetermined minimum total opening angle when using the continuous backflow control a
  • the flow rate is controlled by the forced keeping open the suction valve.
  • two different methods are used for control, namely a suspension control and the continuous backflow control. Both methods use a so-called lift-off gripper, which presses the closing member of the valve, for example a plate, ring or Poppetventil, in an open position, and preferably on the valve seat.
  • the reciprocating compressor has a compression chamber, which is supplied via a suction valve gas, and from which via an outlet valve, also referred to as a pressure valve, compressed gas is discharged.
  • a suction valve gas supplied via a suction valve gas
  • an outlet valve also referred to as a pressure valve
  • compressed gas is discharged.
  • the closing member of the suction valve is kept open during an entire working cycle or a whole working cycle.
  • the pressure in the compression chamber does not rise above the pressure which is required to open the pressure valve, so that the aspirated gas is forced back into the suction line during the compression phase, thereby preventing compression and further transport into the pressure line Available.
  • the pressure valve thus remains closed and this compression chamber thus promotes no gas via the pressure valve in the pressure line.
  • the compression chamber again conveys the entire gas flow via the pressure valve into the pressure line. If, for example, the reciprocating compressor has only one compression space, then the intermittent control can be operated in such a way that certain working cycles are operated with normal operation, and during certain operating cycles the intermittent control is activated.
  • a disadvantage of the Aussetzregelung is thus that the amount of gas pumped by the reciprocating compressor can be regulated only gradually.
  • Another disadvantage of the Aussetzregelung is that the unloaded compression chamber, that is, when not opening pressure valve, is not flowed through and thereby accumulate dirt in the compression chamber, which increases the wear of the valves and the packing rings and piston rings.
  • the suction valve is kept open by means of the lift-off gripper during a partial angle range of a complete compression stroke or a complete crank circuit and then closed, thereby affecting the flow rate.
  • the suction valve is pressed only at the beginning of the compression phase by the Abhebegreifer. As a result, a part of the gas located in the compression chamber is pushed back into the suction line. As soon as the closing member of the suction valve closes completely, the remaining gas in the compression chamber is compressed and pressed via the pressure valve in the pressure line.
  • the backflow control only a portion of the maximum possible gas flow from the compression chamber is thus conveyed via the pressure valve in the pressure line.
  • a disadvantage of the method of backflow control is the fact that the opening time of the automatic pressure valve is reduced accordingly for smaller flow rates, and that at flow rates less than 40% of the nominal flow, the opening time of the pressure valve is shortened such that the opening and closing speeds of the pressure valve can multiply. On the one hand, this leads to increased wear of the automatic pressure valve, and on the other hand, this reduces the range within which partial delivery quantities can be reliably conveyed.
  • Another disadvantage of the backflow control is that the gas is heated more strongly before compression due to the longer residence time in the compression chamber and due to the heat transfer via the cylinder wall and due to a leakage flow through the piston. This has the consequence that the gas has an elevated temperature on the pressure side.
  • the suction valve is influenced by the control device and the lift-off gripper such that the closing member of the pressure valve of the reciprocating compressor is opened at least during a minimum predetermined opening angle range or a predetermined total opening angle of a crank circle.
  • the opening angle range is at least 10 ° and preferably at least 20 ° to 30 °.
  • a drive device preferably an electromagnet
  • the speed of the closing closing member can be reduced prior to placement on the suction valve, so that the closing member at low speed on the suction valve hits and comes to rest, so that the closing organ thus "gentle" on the Suction valve touches down.
  • the speed of the closing member during placement on the suction valve is less than 0.1 m / s. This advantageous method reduces the wear of the closing organ in addition.
  • the drive device comprises a controllable damping device in order to influence the speed of the Abhebegreifers and in particular the location of the reduced speed such that the closing member impinges when closing at low speed on the suction valve, so that the closing member thus "gently" on the Suction valve touches down and this closes.
  • the damping device is particularly advantageously electrically controllable, and particularly advantageously comprises an electrorheological or magnetorheological fluid whose viscosity can be changed electrostatically or electromagnetically, so that the damping via electrical signals can be changed very quickly.
  • the damping device can also be based on another principle and be configured for example as an electromagnet.
  • Fig. 1 shows a longitudinal section through a controllable valve 1 comprising a compressor housing 4 with a suction valve 5 disposed therein, the position of which is influenced by a Abhebegreifer 6, wherein the Abhebegreifer 6 is actuated via a connecting rod designed as a connecting means 7 of a arranged outside the compressor housing 4 control device 2 ,
  • the compressor housing 4 comprises a lantern 4a, a gas space 4b, a compression chamber 4c and a lid 4d, wherein the compressor housing 4 also includes a not shown or not visible pressure valve 8, via which the compressed fluid can escape from the compression chamber 4c.
  • the automatic intake valve 5 comprises a valve seat 5a, a closing member 5b movably mounted in a stroke direction B, also referred to below as a valve plate 5b, a valve catcher 5c and a return spring 5d.
  • the lift-off gripper 6 comprises a plurality of gripper extensions 6a or fingers 6a, a guide 6b and a compression spring 6c.
  • the lifting gripper 6, driven by the electromagnets 2a, slidably mounted in the stroke direction B, wherein the tip of the gripper extensions 6a can abut depending on the stroke in direction B on the valve plate 5b, and in particular can press the valve plate 5b against the valve catcher 5c, so that the Valve plate 5b is no longer movable, and the valve 5 thereby forcibly remains open.
  • the control device 2 comprises as drive device an electromagnet 2 a with a magnet armature 2 b, a magnetic core 2 c and a magnetic coil 2 d.
  • the control device 2 further comprises a housing 2m which is connected to the compressor housing 4 via the connecting part 2e.
  • the control device 2 also comprises a drive device 2i or a control device 2i, electrical lines 2k, 21, wherein the electrical line 21 connects the drive device 2i with the solenoid 2a.
  • the control device 2 comprises two guides 2f, 2g for slidably supporting the electromagnet 2a and the connecting rod 7 in the stroke direction B.
  • a filter 3 may be provided.
  • the control device 2 also includes a sensor such as a displacement sensor 2h, which the hub or the position of the electromagnet 2a or the position of the lifting gripper 6 in the stroke direction B detected.
  • controllable valve 1 can now be controlled in different ways over the cycles of the crank circuit.
  • a cycle is understood to mean a rotation of the crankshaft of the reciprocating compressor through 360 °.
  • FIG. 2 shows the method of a continuous backflow control, wherein in FIG. 2 the lifting movement A of the Abhebegreifers 6, the stroke B of the valve plate 5b and the speed C of the Abhebegreifers 6 are shown in function of the crank angle, wherein a single revolution of the crankshaft is shown, that is FIG. 2 shows the course over an angle between 0 ° and 360 °. From the lifting movement B of the valve plate 5b it can be seen that the valve plate 5b automatically opens in the illustrated embodiment in the angular range between about 90 ° and 110 ° during suction, so that the valve plate 5b rests against the valve catch 5c.
  • the lifting gripper 6 is moved or moved until it bears against the valve plate 5b. Moreover, in FIG. 2 with the curve C nor the speed of the Abhebegreifers 6 shown. During automatic operation of the suction valve 5, the suction valve 5 would automatically close when reversing the direction of movement of the piston, in the example shown at 225 °.
  • stepless backflow control now causes the Abhebegreifer 6 rests during a first portion K1 of the cycle of the crank circle on the closing member 5b and prevents its closure, and that the Abhebegreifer 6 during a second portion K2 of the Cycle of the crank circle is moved back according to the course of the curve A2, wherein the closing member 5b, namely the valve plate 5b, due to the applied pressure conditions of the movement of the Abhebegreifers 6 follows or abhebegreifer 6 is applied, so that the valve plate 5b at some point, in the example shown approximately at 290 °, rests on the valve seat 5a and the valve 5 closes. In the further section K3, the lifting gripper 6 is moved even further, so that it is, for example, spaced from the valve plate 5b.
  • the movement of the closing member 5b is influenced via the drive device, in the illustrated embodiment via the solenoid 2a and the connecting rod 7 in the section K2 such that the Abhebegreifer 6 in function of the crank circle in FIG. 2 illustrated Hubverlauf A or the in FIG. 2 shown speed profile C, wherein the solenoid 2a is advantageously controlled such that the speed of the moving closing member 5a is reduced before placing on the suction valve 5, as in FIG. 2 is shown.
  • the Abhebegreifer 6 is then moved in a further section K3 still in an end position, advantageously as shown in the curve C with the "second hump" by again accelerated and then decelerated again, so that the Abhebegreifer 6, as in Stroke course A shown in the section K3, spaced, that is without direct contact with the closing member 5a, comes to a standstill.
  • the electromagnet 2a is controlled in an advantageous method step such that the closing member 5b has a speed of less than 0.1 m / s during placement on the suction valve.
  • the valve 1 can also be operated with the method of Aussetzregelung. In the intermittent control of the Abhebegreifer 6 is moved such that it prevents the closing of the closing member 5b during a whole cycle of the crank circuit, preferably in that the Abhebegreifer 6 rests during the entire cycle on the closing member 5b, so that it remains open over the entire cycle.
  • FIG. 7 schematically shows a reciprocating compressor comprising a compressor housing 4 with a movably mounted, via a piston rod 4f driven piston 4e, which partially defines a compression chamber 4c.
  • a suction valve 5 is also arranged, via which the fluid or gas to be conveyed is sucked.
  • the reciprocating compressor also includes a gripper 6, which is driven by a control device 2 comprising a drive device.
  • the control device 2 the suction valve 5 and the gripper 6 form a controllable valve 1.
  • a pressure valve 8 is also arranged, via which the compressed gas leaves the compression chamber 4c.
  • the reciprocating compressor may also comprise a plurality of compression spaces 4c, each compression space 4c comprising a separate piston 4e with piston rod 4f, and each compression space 4c comprising a separate, controllable valve 1.
  • FIG. 3 shows now the course of the pressure in a compression chamber 4c of a reciprocating compressor in function of the crank angle for different operating methods.
  • the bottom dead center U TP is at 90 °, that is, in this position, the compression chamber 4c reaches the maximum Volume.
  • the top dead center O TP is in this example at 270 °, that is, at this position, the compression chamber 4c reaches the minimum volume.
  • the movement of the closing member 5b of the suction valve 5 is carried out automatically, so that over a crank angle of 360 ° the pressure curve shown results.
  • the movement of the closing member of the pressure valve 8 takes place in FIG. 3 always automatically.
  • the pressure-side pressure for example, about 3.1 bar
  • the pressure valve 8 opens in the illustrated embodiment, including bias by the valve springs at a pressure of about 3.2 bar.
  • the pressure valve 8 opens approximately at a crank angle of 190 °.
  • the automatic pressure valve 8 is fully opened in the illustrated embodiment during an angular range Kw of about 50 °, because the pressure valve 8 in this maximum open angle range K W has the maximum valve lift before the pressure valve 8 closes again.
  • the total opening angle Kv, during which the valve is open, that is, the closing member is lifted from the valve seat, or the entire opening time of the pressure valve 8 is about 80 °.
  • a skip control is shown, in which, as described above, the closing member 5b is kept open over the entire crank angle of 360 ° from Abhebegreifer 6, so that results in the compression chamber 4c of the pressure profile shown.
  • the pressure in the compression chamber 4c is constantly below 3.2 bar, so that the pressure valve 8 does not open automatically.
  • a continuous backflow control is shown, in which, as in FIG. 2 described, the closing member 5b is kept open during part of the crank angle of 360 ° from Abhebegreifer 6, so that the pressure build-up in the compression chamber 4c based on the crank angle takes place later, and the pressure curve shown results.
  • the pressure valve 8 opens approximately at a Crank angle of 210 °.
  • the automatic pressure valve 8 remains fully open in the illustrated embodiment during a Maximaloffenwinkel Scheme Kw of about 30 ° before the valve lift, as in FIG. 4 shown reduced, and the valve 8 completely closes again after the total opening angle Kv.
  • the total opening angle Kv, during which the valve 8 is open, or the total opening time of the valve is about 60 °.
  • the closing element 5b of the suction valve 5 is pressed on only at the beginning of the compression phase. As a result, a portion of the gas is forced back into the suction line. Closes the suction valve 5, the remaining gas can be compressed in the compression chamber and pressed by the pressure valve in the pressure line.
  • the compression chamber promotes only part of the maximum possible gas flow.
  • Both methods use the lift-off gripper 6 to push the sealing element 5b of the valve 5, for example a plate, ring or poppet valve, against the valve catcher 5c and thus into the open position. Since in the continuous backflow control of the lift gripper 6 in a work cycle of the closed in the open position and must be moved back again, and there in the suspension control for the same sequence of movements a longer time available stands, the power consumption, the required forces, the travel speeds and the stress of the components used in the continuous backflow control are higher.
  • the flow rate of a reciprocating compressor can now, as in FIG. 3 indicated, are controlled by a combination of continuous backflow control F and Aussetzregelung E in a wide range, in addition also the section D can be used for flow control, during which the closing member 5b moves automatically.
  • These three types of operation D, E, F of operating the valve 5 can now be combined with each other, so that, for example, during successive cycles initially only the type of operation D, E or F takes place, and later, for example, a combination of at least two of the three types of operation D, E and F.
  • the valve could for example be controlled such that different flow rates are controlled so that the suction valve 5 is automatically operated at high flow rates during certain cycles, and is operated during certain cycles according to the continuous backflow control, that the suction valve 5 is operated at medium flow rates during each cycle according to the continuous backflow control, and that the suction valve 5 is constantly kept open at low flow rates during certain cycles, and is operated during certain cycles according to the stepless backflow control.
  • FIG. 4 shows the lifting movement 8c of the pressure valve 8 in function of the crankshaft angle.
  • the lifting movement 5e of the closing member 5b of the suction valve 5 is shown as a function of the crankshaft angle.
  • the movement of the pressure valve 8 takes place automatically, whereas the movement of the closing member 5b of the suction valve 5 as described above in the Aussetzregelung E and the backflow control F is determined by the gripper 6.
  • the maximum open angle range Kw within which the valve 8 has a maximum valve lift, that is, is open to the maximum.
  • the total opening angle Kv can be seen, during which the valve 8 is opened.
  • the opening duration of the automatic pressure valve 8 is determined by the angular range during which the pressure in the compression chamber 4c is above the opening pressure of the pressure valve 8, according to the exemplary embodiment FIG. 3 above a pressure of 3.2 bar. From the in FIGS. 3 and 4 shown with F continuous backflow control can be seen that the angular range of the open pressure valve 8 is reduced, the later the closing member 5b is closed. This has the consequence, in particular for small flow rates, that the pressure valve 8 would only be opened during a very short total opening angle Kv if the backflow control were used continuously.
  • FIG. 5 shows a load curve in a PV diagram in different operating methods, namely as already in FIG. 3 shown, at full load D with automatic suction valve 5, in the Aussetzregelung E and in the continuous flow control F.
  • a compressor may be configured such that it as in FIG. 7 represented per cylinder only one compression space 4c, wherein such a compression space 4c is also referred to below as the upper compression space.
  • the compressor may also be designed such that it has a second compression chamber in the same cylinder, which is separated from the first compression chamber by the piston 4e, so that during the movement of the piston 4e the fluid is compressed in one compression chamber and drawn in the other compression chamber.
  • the second compression space is also referred to below as the lower compression space.
  • the flow rate control takes place as in FIG.
  • the opening time of the pressure valve 8 can be determined, for example, by measuring the pressure in the compression chamber and comparing it with the final pressure, or by knowing the operating cases of the compressor via a previous, respectively simultaneous calculation of the maximum opening time of the suction valve over the reversal point of the movement of the piston. so that the minimum opening time or the minimum opening angle of the pressure valve is not exceeded.
  • the FIG. 6 shows characteristic variables of the controllable valve 1 as a function of the crank angle or the angle of rotation to the in FIG. 6 in the path diagram shown movement curve B of the valve plate 5b and the course of motion A of the lift-off gripper 6 to obtain.
  • the curve C the speed profile of the lift-off gripper 6 is shown.
  • the curve G the force caused by the electromagnet 2a and shown in the curve H, the current required to drive the solenoid 2a current.
  • Processes shown are particularly important to the in FIG. 2 shown, "gentle landing" of the valve plate 5b on the valve catch 5c to effect.
  • FIG. 8 schematically shows a further embodiment of a control device 2 for actuating and driving the force acting on the suction valve 5 gripper 6.
  • the control device 2 comprises a drive device 2n, which via the linearly movably mounted connecting rod 7 with the in FIG. 7 schematically illustrated gripper 6 is connected.
  • the drive device 2n shown in this embodiment comprises a linear drive 2w and a electrically controllable damping device 2o, wherein the damping device 2o has the function of the electrically driven to dampen the movement generated by the linear drive 2w so that the gripper 6 and the valve plate 5b of the suction valve 5 such as in FIG. 2 shown moves.
  • the linear drive 2w has a linearly movable connecting rod 2t, which is operatively connected to the connecting rod 7.
  • the damping device 2o is disposed between the linear drive 2w and the gripper 6.
  • the damping device 2o could also be arranged at a different location, in the illustrated view of the control device 2, for example, above the linear drive 2w.
  • the damping device 2o can be configured in a variety of ways to effect a damping of the movement of the linear drive 2w.
  • "soft landing" of the valve plate 5b on the valve catcher 5c is the in FIG. 8 schematically illustrated damping device 2o particularly advantageous.
  • the damping device 2o comprises a cylinder 2p and in its interior a linearly displaceable piston 2r which divides the interior of the cylinder 2p into a first inner space 2q and a second inner space 2s.
  • the two inner spaces 2q, 2s are connected to each other via a fluid-conducting connection 2u, so that a fluid is exchangeable between the two inner spaces 2q, 2s.
  • the two inner spaces 2q, 2s are conductively connected to each other via an electrically controllable damping or throttle 2v fluid.
  • a drive and control device 2i is electrically connected via electrical lines 2k, 21 signal to the linear drive 2w and the controllable damping 2v, so that both the linear drive 2w and the damping properties of the damping device 2o are controllable in order to control the position or the speed of the valve plate 5b such that as in FIG. 2 exemplified a "gentle landing" of the valve plate 5b is effected.
  • Control device 2 shown also includes a device for determining the stroke and / or the speed of the gripper or the valve plate 5b. This device is in FIG. 8 not shown.
  • the fluid-conducting connection 2u and the electrically controllable damping 2v could also be arranged on the damping device 2o or within the damping device 2o, in particular also on the piston 2r in that the piston 2r has, for example, a fluid-conducting connection between the first and second internal spaces 2q, 2s ,
  • the fluid of the damping device 2o at least partially consists of an electrorheological or magnetorheological fluid.
  • Such liquids have the property that their viscosity is electrically controllable, so that with such liquids, an electrically controllable throttle section can be configured.
  • an electrically controllable throttle section has the advantage that the viscosity can be varied within a wide range, and that the viscosity can be changed very quickly with the aid of the electrical signal.
  • damping properties of such a damping device 2o are characterized very quickly changed, so that the movement of the piston 2r and thus the movement of the connecting rod 7, the gripper 6 and ultimately the valve plate 5b can be so damped or is controlled and controlled, the valve plate 5b with respect to the path traveled and speed a "gentle landing" is carried out.
  • Damping devices comprising an electrorheological or magnetorheological fluid are known, for example, from the document WO2008 / 141787A1 or from the publication EP 1034383B1 known.
  • the linear drive 2w can be designed, for example, as a hydraulic or pneumatic drive, as an electromagnetic drive, as a linear motor or as an electric motor with a translation.
  • control device 2 comprises an adaptive pilot control, with which the stroke A and the speed C of the lift-off gripper 6 are regulated.
  • control device 2i comprises an adaptive pilot control device in order to generate control signals for the electromagnet 2a from the control variables of the stroke A and the speed C of the lift-off gripper 6.

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  • General Engineering & Computer Science (AREA)
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Claims (15)

  1. Procédé de régulation du débit de refoulement d'un compresseur à piston, en ce que le mouvement d'un organe de fermeture (5b) d'une soupape d'aspiration (5) automatique est influencé à l'aide d'un grappin de levage (6) entraîné par un dispositif de commande (2) pendant au moins une partie d'un cycle du cercle de vilebrequin, le procédé comprenant une régulation continue du reflux pendant laquelle le grappin de levage (6) repose, pendant une première section partielle (K1) du cycle du cercle de vilebrequin, contre l'organe de fermeture (5b) et entravant sa fermeture et pendant laquelle le grappin de levage (6) est ramené en arrière, pendant une deuxième section partielle (K2) du cycle du cercle de vilebrequin et pendant laquelle l'organe de fermeture (5b) est fermé ; caractérisé en ce que le procédé comprend en outre une régulation intermittente pendant laquelle le grappin de levage (6) entrave, pendant un cycle complet du cercle de vilebrequin, la fermeture de l'organe de fermeture (5b) ;
    que le débit de refoulement est au moins réglé par une combinaison de régulation continue du reflux et de régulation intermittente et qu'en cas d'utilisation de la régulation continue du reflux, l'organe de fermeture (5b) est influencé de telle sorte par le dispositif de commande (2) et le grappin de levage (6) qu'un organe de fermeture d'une soupape de pression (8) automatique du compresseur à piston soit ouvert au moins pendant un angle d'ouverture totale (Kv) minimal prédéfini d'un cercle de vilebrequin.
  2. Procédé selon la revendication 1, caractérisé en ce que la soupape d'aspiration (5) est maintenue ouverte en régulation intermittente pendant un certain nombre de cycles en cas de moindre quantité refoulée, afin que l'organe de fermeture de la soupape de pression (8) ne passe pas en dessous d'un angle d'ouverture minimal.
  3. Procédé selon la revendication 2, caractérisé en ce que l'angle d'ouverture totale (Kv) prédéfini est au moins de 10° et de préférence au moins dans la plage comprise entre 20° et 30°.
  4. Procédé selon la revendication 1, caractérisé en ce que la soupape d'aspiration (5) est influencée de telle sorte par le dispositif de commande (2) et le grappin de levage (6) que l'organe de fermeture de la soupape de pression (8) du compresseur à piston soit ouvert au moins sur une plage angulaire (Δ) prédéfinie d'un cercle de vilebrequin avant le point mort haut ou bas (OTP, UTP) respectif.
  5. Procédé selon la revendication 4, caractérisé en ce que la plage angulaire prédéfinie (Δ) est au moins de 10° et de préférence au moins dans la plage comprise entre 20° et 30°.
  6. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la courbe de pression (P) est mesurée et/ou calculée dans la chambre de compression du compresseur à piston et que le dispositif de commande (2) commande le grappin de levage (6) en fonction de la courbe de pression (P) pendant respectivement au moins un cycle du cercle de vilebrequin de telle sorte qu'en cas de régulation continue du reflux ou de régulation intermittente, la courbe de pression (P) comporte, au moins pendant un angle d'ouverture totale (Kv) prédéfini d'un cercle de vilebrequin, une pression (P) située au-dessus de la pression d'ouverture de la soupape de pression (8), de sorte que la soupape de pression (8) s'ouvre automatiquement pendant l'angle d'ouverture totale (Kv).
  7. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le débit de refoulement est réglé pendant une pluralité de cycles du cercle de vilebrequin seulement par la régulation continue du reflux ou seulement par la régulation intermittente et/ou que la soupape d'aspiration (5) est entraînée automatiquement pendant une pluralité de cycles successifs en cas de grand débit de refoulement.
  8. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que différents débits de refoulement sont réglés de telle sorte que la soupape d'aspiration (5) soit entraînée automatiquement pendant un certain nombre de cycles en cas de grand débit de refoulement, et pendant un certain nombre de cycles en cas de régulation continue du reflux, que la soupape d'aspiration (5) est entraînée à un débit de refoulement moyen pendant chaque cycle en cas de régulation continue du reflux et que la soupape d'aspiration (5) est entraînée pendant un certain nombre de cycles en régulation intermittente en cas de moindre quantité refoulée et est entraînée pendant un certain nombre de cycles en régulation continue du reflux.
  9. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la régulation du reflux se produit de telle sorte que le dispositif de commande (2) comprend un électroaimant (2a) entraînant le grappin de levage (6) et que l'électroaimant (2a) est commandé de telle sorte que le grappin de levage (6) repose, pendant une première section partielle (K1) du cercle de vilebrequin, contre l'organe de fermeture (5b) et entrave sa fermeture et que le grappin de levage (6) influence, pendant une deuxième section partielle (K2) du cercle de vilebrequin, le mouvement de l'organe de fermeture (5b) pendant la fermeture, de façon à réduire la vitesse de l'organe de fermeture (5b) se déplaçant avant le placement de l'organe sur la soupape d'aspiration (5).
  10. Procédé selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la régulation du reflux se produit de telle sorte que le dispositif de commande (2) comprenne un dispositif d'entraînement (2n) entraînant le grappin de levage (6) et que le dispositif d'entraînement (2n) comprenne un dispositif d'amortissement (2o) commandable amortissant le mouvement du grappin de levage (6), le dispositif d'entraînement (2n) étant commandé de telle sorte que le grappin de levage (6) repose, pendant une première section partielle (K1) du cercle de vilebrequin, contre l'organe de fermeture (5b) et entrave sa fermeture et que le grappin de levage (6) influence de telle sorte, pendant une deuxième section partielle (K2) du cercle de vilebrequin, le mouvement de l'organe de fermeture (5b) pendant la fermeture, que la vitesse de l'organe de fermeture (5b) se déplaçant soit réduite avant le placement de l'organe sur la soupape d'aspiration (5).
  11. Procédé selon la revendication 9 ou 10, caractérisé en ce que la vitesse de l'organe de fermeture (5b) est inférieure à 0,1 m/s avant le placement de l'organe sur la soupape d'aspiration (5).
  12. Procédé selon l'une quelconque des revendications 9 à 11, caractérisé en ce que le dispositif de commande (2) accélère encore le grappin de levage (6) après le placement de l'organe de fermeture (5b), pendant une troisième section partielle (K3) du cercle de vilebrequin, puis l'amène à l'arrêt, pour placer le grappin de levage (6) à une certaine distance de l'organe de fermeture (5b) et l'amener dans une position terminale.
  13. Compresseur à piston avec régulation continue du débit de refoulement, avec un grappin de levage (6) disposé au niveau d'au moins une soupape d'aspiration (5) automatique du compresseur, avec un dispositif de commande (2) pour entraîner le grappin de levage (6), ainsi qu'avec un organe de fermeture (5b) de la soupape d'aspiration (5) et avec une soupape de pression (8) automatique, le grappin de levage (6) agissant de telle sorte sur l'organe de fermeture (5b) en situation de fonctionnement que la soupape d'aspiration (5) est ouverte sur une partie commandable de la cadence de travail du compresseur, le dispositif de commande (2) comprenant un dispositif d'entraînement (2n) agissant, via un moyen de liaison (7), sur le grappin de levage (6) et le dispositif de commande (2) comprenant une régulation continue du reflux pendant laquelle, en situation de fonctionnement, le grappin de levage (6) repose, pendant une première section partielle (K1) du cycle du cercle de vilebrequin, contre l'organe de fermeture (5b) et entrave sa fermeture et pendant laquelle le grappin de levage (6) revient en arrière pendant une deuxième section partielle (K2) du cycle du cercle de vilebrequin de sorte que l'organe de fermeture (5b) se ferme,
    caractérisé en ce que :
    le dispositif de commande (2) est configuré de telle sorte que celui-ci comprenne en outre une régulation intermittente dans laquelle, en situation de fonctionnement, le grappin de levage (6) entrave, pendant un cycle complet du cercle de vilebrequin, la fermeture de l'organe de fermeture (5b) et que le dispositif de commande (2) est configuré de telle sorte que le grappin de levage puisse être entraîné avec deux procédés différents, la régulation continue du reflux ainsi que la régulation intermittente, et qu'en cas d'utilisation de la régulation continue du reflux, l'organe de fermeture (5b) soit influencé de telle sorte par le dispositif de commande (2) et le grappin de levage (6) qu'un organe de fermeture de la soupape de pression (8) soit ouvert au moins pendant un angle d'ouverture totale (Kv) minimal prédéfini d'un cercle de vilebrequin.
  14. Compresseur selon la revendication 13, caractérisé en ce que le dispositif d'entraînement (2n) est configuré sous la forme d'un électroaimant (2a) et/ou que le dispositif d'entraînement (2n) comprend un entraînement (2w) et un dispositif d'amortissement (2o) commandable, le dispositif d'amortissement (2o) étant configuré et disposé de telle sorte que celui-ci amortisse de façon commandable le mouvement de l'entraînement (2w).
  15. Compresseur selon l'une quelconque des revendications 13 à 14, caractérisé en ce que le dispositif de commande (2) comprend un dispositif pour mesurer et/ou calculer la courbe de pression (P) dans la chambre de compression du compresseur à piston et que le dispositif de commande (2) est configuré de telle sorte que celui-ci entraîne en roue libre l'organe de fermeture (5b) via le grappin de levage (6) ou avec la régulation du reflux ou avec la régulation intermittente, pour ouvrir automatiquement la soupape de pression (8) pendant un angle d'ouverture totale (Kv).
EP10751818.5A 2009-07-23 2010-07-21 Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement Active EP2456979B1 (fr)

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PCT/EP2010/060545 WO2011009879A1 (fr) 2009-07-23 2010-07-21 Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011009879A1 (fr) 2009-07-23 2011-01-27 Burckhardt Compression Ag Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement
USD791842S1 (en) 2016-02-02 2017-07-11 Ge Oil & Gas Compression Systems, Llc Dual compressor nozzle
US10215190B2 (en) 2016-05-31 2019-02-26 GE Oil & Gas, Inc. Refrigerant compressing process with cooled motor

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US5988985A (en) 1996-04-12 1999-11-23 Hoerbiger Ventilwerke Aktiengesellschaft Method and apparatus for controlling compressor valves in a piston compressor
WO2008000698A2 (fr) 2006-06-28 2008-01-03 Dott. Ing. Mario Cozzani S.R.L. Équipement pour la régulation continue du débit de compresseurs alternatifs
EP2281119A1 (fr) 2008-04-30 2011-02-09 Dott. Ing. Mario Cozzani S.r.l. Procédé de commande de la position d'un actionneur électromécanique pour vannes de compresseur à mouvement alternatif

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US4930463A (en) 1989-04-18 1990-06-05 Hare Sr Nicholas S Electro-rheological valve control mechanism
US5988985A (en) 1996-04-12 1999-11-23 Hoerbiger Ventilwerke Aktiengesellschaft Method and apparatus for controlling compressor valves in a piston compressor
WO2008000698A2 (fr) 2006-06-28 2008-01-03 Dott. Ing. Mario Cozzani S.R.L. Équipement pour la régulation continue du débit de compresseurs alternatifs
EP2281119A1 (fr) 2008-04-30 2011-02-09 Dott. Ing. Mario Cozzani S.r.l. Procédé de commande de la position d'un actionneur électromécanique pour vannes de compresseur à mouvement alternatif

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011009879A1 (fr) 2009-07-23 2011-01-27 Burckhardt Compression Ag Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement
USD791842S1 (en) 2016-02-02 2017-07-11 Ge Oil & Gas Compression Systems, Llc Dual compressor nozzle
USD792474S1 (en) 2016-02-02 2017-07-18 Ge Oil & Gas Compression Systems, Llc Dual compressor nozzle
USD792475S1 (en) 2016-02-02 2017-07-18 Ge Oil & Gas Compression Systems, Llc Dual compressor nozzle
USD792912S1 (en) 2016-02-02 2017-07-25 Ge Oil & Gas Compression Systems, Llc Dual compressor nozzle
US10215190B2 (en) 2016-05-31 2019-02-26 GE Oil & Gas, Inc. Refrigerant compressing process with cooled motor

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