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
• • 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
• the compressor valves used on the pressure side still have a high load, especially when the compressor system according to the method of a continuously variable
• 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 a relatively large wear, which is a correspondingly high
• Flow control of a reciprocating compressor by the movement of a closing member of a self-acting suction valve is influenced by means of a driven by a control Abhebegreifers during at least part of a cycle of the crank circuit
• the method comprises a continuous backflow control, in which the lift-off gripper rests against the closing member during a first part of the cycle of the crank circuit and the latter
• Closure prevents, and in which the lifting gripper is moved back during a second portion of the cycle of the crank circle and the closing member is closed,
• the method comprises a skip control in which the skimmer prevents the closing of the closing member during a whole cycle of the crank circuit
• the flow rate is controlled at least by a combination of continuous backflow control and Aussetzregelung, and wherein the closing member by the control device and the
• Lifting gripper is influenced such that a closing member of a pressure valve of the reciprocating compressor is opened at least during a predetermined total opening angle of a crank circle.
• 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.
• Poppet valve push in an open position, and preferably press 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. This increases the pressure during the compression phase
• the intermittent control can be operated in such a way that certain working cycles are run with normal operation, and during certain working cycles the intermittent control can be operated
• Aussetzregelung is that the unloaded compression chamber, that is, when not opening pressure valve, is not flowed through and can accumulate dirt in the compression chamber, which increases the wear of the valves or the packing rings and piston rings.
• the suction valve with the help of Abhebegreifers during a partial angle range of
• Opening time of the pressure valve is shortened so that the
• 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 through the cylinder wall and due to a
• the erf ⁇ ndungsgemässe method has the advantage that by the combined use of backflow control and intermittent control, the volume delivered by the reciprocating compressor can be varied within a wide range, in particular without additional
• the reduction of the wear of the pressure valve is in particular the fact that the suction valve is kept open at low flow rates during certain cycles according to the Aussetzregelung and thus no gas is compressed, and that at
• control can take place, for example, as follows:
• the suction valve is not affected and thus opens and closes automatically.
• a continuous backflow control is used. Whereby it is also possible that not every cycle of the crank circuit is regulated with the backflow control, but the suction valve is also operated, for example, one or two cycles automatically and thus without interference.
• This method has the advantage that the lift-off gripper is subjected to less stress, resulting in longer service lives, and that the volume control itself consumes less energy.
• Backflow control can be used.
• the suction valve is influenced by the control device and the Abhebegreifer such that the closing member of the pressure valve of the reciprocating compressor at least during a predetermined opening angle range or a
• the opening angle range is at least 10 ° and
• 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 - o -
• 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.
• Drive device a controllable damping device in order to influence the speed of the lift-off gripper and in particular also the location of the reduced speed such that the
• Suction valve impinges so that the closing member thus "gently” touches down on the suction valve and closes the damping device is particularly advantageous electrically controlled, and particularly advantageously comprises an electrorheological or magnetorheological
• the damping device can also be based on another principle and, for example, as
• 1 shows a longitudinal section through a controllable valve
• 2 shows an example of the movement of the lift-off gripper, the closing member of the suction valve and the speed of the lift-off gripper as a function of the crank angle
• FIG. 4 shows the course of the valve lift of the suction valve and of the pressure valve in the operating method shown in FIG. 3;
• Fig. 5 shows a load curve in a PV diagram at different
• Fig. 7 shows schematically a reciprocating compressor.
• FIG. 8 shows schematically a control device for actuating the gripper acting on the suction valve
• 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 configured as a connecting rod connection means 7 from outside the
• Compressor housing 4 arranged control device 2 is actuated.
• the compressor housing 4 comprises a lantern 4a, a gas space 4b, a compression space 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.
• Lifting gripper 6 is, driven by the electromagnet 2 a, in
• the control device 2 comprises a drive device as a
• Electromagnet 2a with a magnet armature 2b, a magnetic core 2c and a magnetic coil 2d.
• the control device 2 further comprises a housing 2m, which via the connecting part 2e with the
• Compressor housing 4 is connected.
• the control device 2 also comprises a drive device 2i or a control device 2i, electrical lines 2k, 21, wherein the electrical line 21 the
• the Drive device 2i connects to the solenoid 2a.
• the control device 2 comprises two guides 2f, 2g around the
• Electromagnet 2a and the connecting rod 7 slidably store 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 lift-off gripper 6 in the stroke direction B detected.
• a cycle is understood to mean a rotation of the crankshaft of the reciprocating compressor through 360 °.
• Figure 2 shows the method of a continuous backflow control, wherein in Figure 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
• Valve plate 5b during suction in the illustrated
• Embodiment in the angular range between about 90 ° and 1 10 ° automatically opens, 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.
• Figure 2 with the curve C nor the speed of the Abhebegreifers 6 is shown.
• the suction valve 5 would automatically close when reversing the direction of movement of the piston, in the example shown at 225 °.
• Closing member 5b is applied and prevents its closure, and that the lifting gripper 6 during a second portion K2 of the Cycle of the crank circuit is returned 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 rests on the Abhebegreifer 6, so that the valve plate 5b at some point, in the illustrated
• Example at about 290 °, rests on the valve seat 5a and the valve 5 closes.
• the lift-off gripper 6 is moved even further, so that this e.g. is 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 lift-off gripper 6 as a function of the crank circle the stroke course A shown in Figure 2 or the speed course C shown in Figure 2 , wherein the electromagnet 2a is advantageously controlled such that the speed of the moving closing organ 5a before placing on the
• Suction valve 5 is reduced, as shown in Figure 2.
• Abhebegreifer 6 is then moved in a further section K3 still in an end position,
• 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. ⁇ . o ⁇
• the valve 1 can also be operated with the method of Aussetzregelung.
• the lifting gripper 6 is moved such that this during a whole cycle of
• Cranking prevents the closing of the closing member 5b, preferably in that the Abhebegreifer 6 rests during the entire cycle on the closing member 5b, so that it remains open throughout the cycle.
• Figure 7 shows schematically a reciprocating compressor comprising a compressor housing 4 with a movably mounted, via a
• 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, the one of a control device 2 comprising a
• the drive device is driven.
• 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 can also a plurality of
• Compression chambers 4c include, wherein each compression chamber 4c comprises a separate piston 4e with piston rod 4f, and wherein each compression chamber 4c comprises a separate, controllable valve 1.
• FIG. 3 now shows the course of the pressure in a compression chamber 4c of a reciprocating compressor as a function of the crank angle for different operating methods.
• Embodiment is the bottom dead center UTP at 90 °, that is, in this position, the compression chamber 4c reaches the maximum Volume.
• the top dead center OTP in this example is 270 °, ie in 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 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 Maximaloffenwinkel Scheme Kw 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 in the compression chamber 4c of the illustrated
• Pressure curve results.
• the pressure in the compression chamber 4c is constantly below 3.2 bar, so that the pressure valve 8 does not open automatically.
• the third section F a continuous backflow control is shown, in which, as described in Figure 2, 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 later, and the pressure curve shown results.
• the pressure valve 8 opens approximately at a ⁇ - -
• 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 - -
• Flow control can be used, 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 operated automatically at high flow rates during certain cycles, and is operated during certain cycles according to the continuous backflow control,
• FIG. 4 shows the lifting movement 8c of the pressure valve 8 as a function of the crankshaft angle.
• the lifting movement is 5e of
• the opening duration of the automatic pressure valve 8 is determined by the angular range during which the pressure in
• Compaction space 4c is above the opening pressure of the pressure valve 8, in the embodiment according to Figure 3 above a pressure of 3.2 bar. From the continuously variable in Fig. 3 and 4 shown with F.
• the reciprocating compressor is operated such that the Aussetzregelung E is used during one or more Kurbeizyklen to promote in the subsequent backflow control F a large enough amount of gas, so that the pressure valve 8 over one
• FIG. 5 shows a load curve in a PV diagram in the case of different operating methods, namely, as already shown in FIG. 3, at full load D with automatic intake valve 5, at intermittent control E and at stepless return flow control F.
• a compressor may be configured such that, as shown in FIG. 7, it has only one compression space 4c per cylinder, such a compression space 4c also being referred to below as an 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 a compression space and sucked in the other compression space.
• Opening time must be determined because the closing time is reasonably well known and an idealized valve in Dead center of upper or lower if available
• the opening time of the pressure valve 8 can be determined for example via a measurement of the pressure in the compression chamber and comparison with the final pressure, or with knowledge of the operating cases of the compressor over a previous, respectively simultaneous
• FIG. 6 shows characteristic magnitudes of the controllable valve 1 as a function of the crank angle or the angle of rotation in order to obtain the course of movement B of the valve plate 5b and the course of movement A of the lift-off gripper 6 shown in FIG.
• the curve C the speed profile of the lift-off gripper 6 is shown.
• Electromagnet 2a caused force G and to control the
• Electromagnet 2a required current H shown.
• the courses shown in FIG. 6 are particularly important in order to bring about the "gentle landing" of the valve plate 5b on the valve catcher 5c shown in FIG.
• FIG. 8 shows schematically another embodiment of a control device 2 for actuating and driving the on the
• the control device 2 comprises a drive device 2n, which is connected via the linearly movably mounted connecting rod 7 with the gripper 6 shown schematically in Figure 7.
• 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 the function has to dampen electrically controlled the movement generated by the linear drive 2w so that the gripper 6 and the valve plate 5b of the suction valve 5 as shown for example in Figure 2 moves.
• the linear drive 2w has a linearly movable connecting rod 2t, which
• the damping device 2o 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.
• Damping device 2o can be configured in a variety of ways to effect a damping of the movement of the linear drive 2w. To the inventive "soft landing" of
• 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 between the two inner spaces 2q, 2s a fluid
• 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 a "gentle landing" of the valve plate 5b is effected as shown by way of example in Figure 2.
• the control device 2 shown in Figure 8 also comprises a device for determining the stroke and / or the speed of the gripper or the valve plate 5b. This device is not shown in FIG.
• 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 a
• Such liquids have the property that their viscosity is electrically controllable, so that with such liquids, an electrically controllable throttle section can be configured.
• a 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.
• the 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
• 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 US Pat
• the linear drive 2w can, for example, as a hydraulic or pneumatic drive, as an electromagnetic drive, as
• Linear motor or be designed as an electric motor with translation.

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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)

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Citations (10)

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• 2010
  • 2010-07-21 US US13/386,374 patent/US20120207623A1/en not_active Abandoned
  • 2010-07-21 WO PCT/EP2010/060550 patent/WO2011009880A1/de active Application Filing
  • 2010-07-21 JP JP2012521026A patent/JP5739420B2/ja active Active
  • 2010-07-21 WO PCT/EP2010/060545 patent/WO2011009879A1/de active Application Filing
  • 2010-07-21 US US13/386,328 patent/US20120189467A1/en not_active Abandoned
  • 2010-07-21 CN CN201080033185.6A patent/CN102472265B/zh active Active

Patent Citations (10)

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