WO2013010687A1 - Compresseur à pistons - Google Patents

Compresseur à pistons Download PDF

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Publication number
WO2013010687A1
WO2013010687A1 PCT/EP2012/057357 EP2012057357W WO2013010687A1 WO 2013010687 A1 WO2013010687 A1 WO 2013010687A1 EP 2012057357 W EP2012057357 W EP 2012057357W WO 2013010687 A1 WO2013010687 A1 WO 2013010687A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
compressor according
piston
piston compressor
connection
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.)
Ceased
Application number
PCT/EP2012/057357
Other languages
German (de)
English (en)
Inventor
Georg Flade
Franz-Josef Ritzen
Klaus Hoff
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.)
Neuman & Esser & Co KG GmbH
Original Assignee
Neuman & Esser & Co KG 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
Application filed by Neuman & Esser & Co KG GmbH filed Critical Neuman & Esser & Co KG GmbH
Publication of WO2013010687A1 publication Critical patent/WO2013010687A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • 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
    • F04B49/16—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 adjusting the capacity of dead spaces of working chambers
    • 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
    • F04B49/225—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 with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • 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 reciprocating compressor according to the preamble of claim 1.
  • Such reciprocating compressors are known for example from DE-PS 681 287 or DE-PS 664 566.
  • the actual intake volume V s is smaller than the theoretical intake volume VHUB-
  • the intake volume can be adjusted via the size of the dead space. Since the dead space in the piston cylinder is not changeable, one has proceeded to volume control to switch on another dead space, which is referred to as Zuschaltraum.
  • a device for flow control of reciprocating compressors with unregulated suction and pressure valves and a fixed Zuschaltraum is known. This Zuschaltraum is connected to the cylinder chamber by a standing under load after the cylinder chamber plate valve which shuts off during each Verdichtungshubes the Zuschalt- space when exceeding the set valve load corresponding compression and during the suction stroke falls below the same pressure in the cylinder chamber again.
  • This connecting valve is manually adjustable via a compression spring, which has the disadvantage that the delivery quantity of the reciprocating compressor can only be adjusted inaccurately and switching to a different delivery quantity is accompanied by a loss of time.
  • the Zuschaltraum is connected by a line to the suction channel of the reciprocating compressor, wherein in the line after the Zuschaltraum back opening check valve is installed, so that the pressure in the Zusalt- space can automatically adjust to the pressure in the suction channel.
  • DE-PS 664 566 describes a piston compressor in which the Zuschaltraum is switched off during the compression stroke by a jerk under the winning mitteid piston slide after overcoming the adjustable pressure of a second means and switched on again during the following suction stroke at the same pressure.
  • a two-stage compressor in which the suction valves are used to connect the Zuschalttsammlung and keeping open the valves by gas pressure.
  • the Zuschaltraum is arranged in front of the suction valve, wherein the suction valve is also used as a Zuschaltventil during the compression phase.
  • a control device is provided with a Drossei beautiful comprising a container and throttle valves, which are adjustable by hand.
  • additional non-return valves have to be installed between the suction valves and a gas reservoir.
  • the suction valves must be equipped with stepped pistons and optionally with a spring device and a gripping device for the valve disk.
  • the throttle device must also be adjusted by hand.
  • the Zuschaltraum is always switched on only during the beginning of the compression process, because the gas to be compressed is sucked by the piston via the Zuschaltraum. The Zuschaltraum is therefore not available during the intake process as additional dead space.
  • a pneumatically actuated sequence valve is that the pressures at the suction port and at the pressure port can be used, which define the maximum and minimum pressures. These pressures are applied directly to the connecting valve by means of the pneumatic control device.
  • Embodiment holds in the closed position and according to another embodiment in the open position, is denoted by Pz.
  • the sequence valve is an additional valve to the valves at the pressure connection and at the suction connection. It is at least one Zuschaltventil, preferably at least two Zuschaltven- tile provided.
  • connection valve Pz
  • Pz To set intermediate values for the delivery quantity, Pz must be set to a value between the minimum value and the maximum value, so that the Zuschaltraum can be switched on and off, which is performed by means of the pneumatic control device.
  • the final pressure P D By means of the pneumatic control device, preferably the final pressure P D can also be reduced to a desired value Pz.
  • the pneumatic control device has a switching valve with which the connection valve can be connected to the suction connection or the pressure connection.
  • the switching valve By switching the switching valve back and forth, ie by alternately applying P S and P D , the intermediate pressures, ie P z , required for setting the desired delivery quantity can be applied to the connecting valve.
  • the pneumatic control device has a throttle device. This throttle device is preferably arranged between the switching valve and the Zuschaltventil.
  • An adjustable throttling device is preferred and has the advantage that different intermediate values Pz between Ps and P D can be set.
  • the control device is connected to the pressure port. By means of the throttle device, the applied final pressure P D is reduced to the desired value Pz, so that a switching back and forth of the changeover valve can be omitted.
  • the pneumatic control device is electrically connected to a control device.
  • This control device preferably has means for inputting the desired delivery quantities of the compressor and preferably calculates therefrom the required pressure P z .
  • the control of, for example, the switching valve and / or the throttling device takes place on the basis of the averaged pressure Pz.
  • a first pressure sensor between the pneumatic control device and the Zuschaltventil is arranged.
  • the actual applied to the Zuschaltventil pressure Pz can be measured.
  • this first pressure sensor is also connected to the control device, so that the calculated and the measured pressure P z can be adjusted.
  • a second pressure sensor on the suction flange and a third pressure sensor on the pressure connection are preferably electrically connected to the control device.
  • the values measured at the suction flange and at the pressure port can also be included in the control of the pneumatic control device. By this measure, the accuracy of the adjustment of the delivery quantity is further improved.
  • the pneumatic control device preferably in conjunction with the control device, a quick and easy adjustment of the delivery quantity of the compressor and thus a quick conversion to other delivery quantities is possible. In particular, in applications in connection with natural gas storage, it depends on a rapid delivery adjustment, which is possible with the piston compressor according to the invention in a simple manner.
  • the pneumatic control device has at least one control chamber.
  • This control chamber is preferably arranged between the connecting valve and the switching valve and / or the throttle device.
  • the control chamber preferably directly adjoins the or the Zuschaltventil / e.
  • the control room serves to the pressure surges, z. B. occur when switching the switching valve to mitigate.
  • the control chamber is preferably an additional space to the required pipeline leading from the Zuschaltventil to the switching valve or the throttle device.
  • the control chamber can be formed by a cross-sectional widening in comparison to the cross-section of the pipeline. It is advantageous if the control chamber has a volume which is significantly larger than the volume of the subsequent pipeline, so that the leaks occurring at the connection valve does not lead to a permanent switching of the changeover valve in control mode.
  • the control room also allows the control of several Zuschaltventilen.
  • the control room is a common room for several additional valves.
  • Several connection valves can be combined to form a valve unit.
  • each valve unit has a common control chamber.
  • a plurality of valve units may be provided, the control chambers are connected via their own pipes.
  • the control chamber is integrated in the piston cylinder.
  • the reciprocating compressor thereby has a compact design.
  • control chamber is arranged between the cylinder cover and the compression space.
  • control chamber is integrated in the cylinder cover, which also reduces the manufacturing cost of the reciprocating compressor.
  • the control space is preferably separated from the compression space of the piston cylinder by an intermediate wall arranged in the piston cylinder.
  • the intermediate wall preferably extends perpendicular to the axis of the Koi- cylinder.
  • the intermediate wall is preferably arranged in the frontal region of the piston cylinder.
  • the compression space is preferably bounded by the intermediate wall.
  • the Zuschaltventil is preferably located within the piston cylinder.
  • the Zuschaltraum has at least a first region, which is preferably provided within the piston cylinder. It is thereby created a compact arrangement, which has the further advantage that the existing dead space is not increased.
  • the dead space z. B. by a supply from
  • the Zuschaltraum has a second region, which is provided according to a first embodiment outside of the piston cylinder and is preferably housed in a container.
  • This container takes up the larger volume of the Zuschaltraums. If necessary, to adapt the volume of the Zuschaltraums this container can be easily replaced, the arrangement of the first region thereof is not affected.
  • the second region of the Zuschaltraums is also disposed within the piston cylinder. Particularly preferred is an accommodation of the second region of the Zuschaltraums in the cylinder cover.
  • the second area is preferably bounded by the intermediate wall opposite the compression space. If preferably the one or more control rooms are also in the space between partition and cylinder cover, the control room has its own housing.
  • the first region of the Zuschaltraums is arranged in the intermediate wall connecting channel.
  • the Zuschaltventil is also arranged in the intermediate wall.
  • the sequence valve is preferably arranged in front of the connecting channel.
  • the Zuschaltventil is thus located between the compression space and the connecting channel, so that the dead space is not increased within the compression space.
  • the Zuschaltventil according to a first embodiment on a dumbbell-shaped valve body.
  • the advantage of this embodiment of the valve body is that the valve body can be pressurized from both sides, namely the pressure of the control chamber and the pressure of the compression space.
  • the waisted portion of the valve body in the open position of the Ventii operates the connection between the compression chamber and connecting channel ago.
  • the valve body preferably has a valve disc on each end face, wherein a first valve disc faces the compression space and a second valve disc faces the pneumatic control device.
  • both valve discs and thus the pressure surfaces of the valve body are the same size.
  • the valve disks are preferably circular, wherein the thickness d of the valve disks is preferably smaller than the diameter D of the valve disks.
  • the second valve disc opens or closes the access to the connection space, in particular to the connection channel.
  • the first valve disc has no closing and sealing function, but only a guiding function for the valve body. It is therefore preferred that the connection valve has only a cylindrical valve body with height h and diameter D, wherein preferably h> D.
  • the valve body has an upper and a lower cover surface. The upper Deckfiambae is the control room and the lower Deckfiache faces the compression space.
  • the valve seat is preferably designed such that the lower cover surface is pressed against the valve seat in the closed position with an axial force component.
  • the advantage of this embodiment is that leakage losses between Zuschaltraum and compression space when switching the Zuschaltventils be avoided by open position in the closed position more effective.
  • the cylindrical valve body is preferably a straight circular cylinder.
  • connection valve preferably has sealing means. These are preferably provided on the cylindrical valve body on the two cover surfaces.
  • the cylindrical valve body may preferably have a
  • Figure 1 is a PV diagram of a reciprocating compressor according to the prior
  • FIG. 2 shows a circuit diagram of a piston compressor according to the invention
  • Figure 4 is a PV diagram for explaining the operation of the in the
  • FIG. 7 shows a PV diagram for the valve arrangement according to FIG. 6, wherein the
  • FIG. 2 schematically shows a piston compressor 1 which has a piston cylinder 4 in which a piston 5 (see FIG. 3) is arranged.
  • a suction port 2 and a Druckanschiuss 3 with corresponding suction and pressure valves 8, 9 are arranged. Via the suction port 2, the gas to be compressed is sucked in and via the Druckanschius 3, the compressed gas is discharged. This is symbolized by the arrows.
  • control chamber 20 is arranged, which is explained in more detail in connection with the figure 3.
  • a pipe 36 is connected, which connects the control chamber 20 with a switching valve 32, which is designed as a 3/2-way valve.
  • This switching valve 32 is part of an adjusting device 30, which is designed as a pneumatic control device 31, and is connected to a pipe 37 to the Druckanschius 3 and via a pipe 38 to the suction port 2.
  • the switching valve 32 allows an optional connection of the control chamber 20 with the suction port 2 and the Druckanschiuss 3 or a complete interruption with these two terminals.
  • a second pressure sensor 72 and a third pressure sensor 74 are connected in each case.
  • a first pressure sensor 76 is connected to the pipeline 36. All the pressure sensors 72, 74, 76 are electrically connected via the connecting lines 82, 84, 86 to a regulating device 70, so that the pressure values in this regulating device 70 can be processed.
  • This controller 70 has means for entering delivery quantities. This input can be z. B. via a keyboard.
  • the control unit calculates the connection pressure P z from the values entered and controls it via the
  • an adjustable throttle device 34 may be provided in the pipeline 36, which is controlled via the electrical line 88. This is shown in detail in FIG.
  • the control device 70 controls the working space, ie the compression space control and processes the measured values for suction and discharge pressure. It is therefore provided within the control device, a control unit, which converts the supply quantity specification linearly in the lying between suction and discharge pressure Zuschaltdruck P z .
  • the control device may further include a process control, with which the suction or end or differential pressure is kept constant.
  • a process control with which the suction or end or differential pressure is kept constant.
  • FIG. 3a, b an enlarged view of the piston cylinder 4, the Zuschaltraums 40 and the pneumatic control device 30 is shown.
  • the piston cylinder 4 receives the movable piston 5 with piston rod 6, which sucks the gas to be compressed via the suction port 2 and discharges via the pressure port 3 compressed gas.
  • Adjacent to this dead space 12 is an intermediate wall 24 with connection valves 50, with which the connection space 40 can be switched on or off.
  • the intermediate wall 24 is arranged perpendicular to the longitudinal axis 10 of the piston cylinder 4 in the piston cylinder.
  • intermediate wall 24 is a control chamber 20.
  • the intermediate wall 24 and the control chamber 20 are integrated into the cylinder cover 22.
  • the intermediate wall 24 with the valves 50 can be preassembled in the cylinder cover 22.
  • a connecting channel 44 is provided, which continues in the cover flange 23.
  • a container 42 is arranged to the connecting channel 44.
  • the connecting channel 44 forms a first region 46 of the Zuschaltraums 40, while the container 42 forms the second region 48 of the Zuschaltraums.
  • the container 42 has the larger volume of the Zuschaltraums and can be replaced if necessary.
  • a plurality of Zuschaltventile 50 are arranged, which have displaceable in the vertical direction valve body 52.
  • Each valve body 52 is formed dumbbell-shaped and has a first valve disc 56 and a second valve disc 54, the body portion 58 are connected to each other via a waisted valve.
  • the second valve disk 54 in the intermediate wall 24 is assigned a valve seat 60.
  • FIG. 3 a shows the open position of the connection valves 50, in which the valve disc 56 does not bear against the valve seat 60, so that the compression space is connected to the connection channel 44.
  • FIG. 3b shows the connection valves 50 in the closed position.
  • the inner surface of the first valve disc 56 abuts against the valve seat 60, so that the connection of the compression chamber 7 and the connecting channel 44 is interrupted.
  • the first valve disk 54 bears against a stop 26 in the region of the opening 28.
  • the second valve disc 54 faces the control chamber 20 and is acted upon via the control chamber 20 with the Zuschalttik P z .
  • the control chamber 20 has a defined volume for reducing pressure surges. All Valve body are connected via openings 28 in the intermediate wall 24 with the control chamber 20 in connection. Thus, it is possible that all the additional valves 50 can be acted upon at the same time with the pressure P z .
  • the cylinder cover 22 and thus the control chamber 20 are connected via the pipe 36 and the controllable throttle valve 34 with the switching valve 32, which in turn is connected to the pipes 37 and 38 with the pressure connection 3 and the Sauganschius 2. Via the electrical line 80, the switching valve 32 is controlled by the control device 70.
  • FIG. 4 shows the pV diagram of the piston compressor according to the invention, wherein the connection space 40 is active in the suction pressure range between P s and P z .
  • the theoretical curves A and B from FIG. 1 are indicated by dashed lines.
  • the valve position and flow shown in FIG. 3a are assigned to the region ef in the pV diagram of FIG.
  • the piston 5 is brought to its minimum stroke position in the area fa, wherein the gas to be compressed is sucked.
  • the piston then moves upward and compresses the gas, wherein at point b, the pressure P z is reached in the compression chamber.
  • the pressure P z is the acting on the valves Zuschalttik which prevails in the control chamber 20.
  • the Zuschaltventiie 50 are brought into its closed position, so that the first valve disc 56 rests against the valve seat 60 and the access to the connecting channel 44 is interrupted.
  • the connection space 40 is separated from the compression space 7 at the point b (see FIG. 3b).
  • the delivery quantity is indicated by the solid lines over the distance a, b, c, d, e, f, cd.
  • the delivery quantity is proportional to the distance.
  • the curve is set and adjusted the delivery quantity.
  • FIG. 5 shows the delivery quantity in relation to the full load as a function of the intermediate pressure P z . It can clearly be seen that the theoretical delivery amount represented by the straight line deviates only slightly from the actual delivery quantity represented by the squarated line. Thus, the flow rate can be very well approximate by a linear approach. Of course, the control device 70, the exact application-related history can be made available.
  • FIGS. 3 a, b and 7 the second installation alternative of the Zuschaltventile 50 is shown. While in the embodiment illustrated in FIGS. 3 a, b the first valve disc 56 opens or closes the access to the connecting channel 44, in the illustration shown here, the second valve disc 54 is arranged such that it contacts the valve seat 60 and thus access to the connecting channel 44 opens and closes.
  • This arrangement has the advantage that the connection space is active in the end pressure range (pressure range between P z and P D ) (see FIG.
  • This arrangement has the additional advantage that when 100% promotion the Zuschaltventil is closed during the intake defined and thus no loss of flow caused by late closing of the valve. Furthermore, there is no appreciable leakage from the control chamber 20 into the compression chamber 7.
  • the thickness d and the diameter D of the valve disks 54,56 is located.
  • FIG. 8 shows a further embodiment in which a plurality of connecting valves 50 are combined to form a valve unit 62.
  • the valve units 62 are arranged in the intermediate wall 24 and have a housing 64 which limits the control chamber 20.
  • the three control chambers 20 are connected to the pipeline 36 via pipelines 36a, b, c.
  • each valve unit 62 each one in the intermediate wall 24 befind Anlagen connection channel 44, which forms the first portion 46 of the Zuschaltraums 40, in the second region 48 of the Zuschaltraums 40.
  • the second portion 48 of the Zuschaltraums 40 is located in the cylinder cover 22.
  • An additional container 42 is not required in this embodiment, since the second region 48 of the Zuschaitraums 40 is integrated into the piston cylinder 4.
  • the advantage of this arrangement is that only one or a few standardized venting units are required, which can then be combined independently of the application.
  • the cylinder ceiling! 22 without additional container 42 can be used as Zuschaltraum 40.
  • the control chamber 20 is part of the valve unit 62.
  • the control chambers 20 are connected to the pipes 36a, b, c gas-tight against the Zuschaltraum 40 via the pipe 36 to the switching valve 32.
  • FIG. 9 shows a further embodiment of the connection valve 50.
  • the valve body 52 is a right circular cylinder with height h and diameter D, where h> D.
  • the circular cylinder On the two cover surfaces 53a, b, the circular cylinder has sealing means 59a, b.
  • the sealing means 59a consists of an annular elevation at the edge of the cover surface 53a. In open division (position A), the sealing means 9 a abuts the stop 26 and seals against the control chamber 20.
  • the lower cover surface 53b merges into the cylinder jacket of the valve body 52 via a curve. This rounding forms the sealant 59b. In the closed position (position B), the rounding abuts the valve seat 60.
  • the valve seat 60 is conical in this embodiment.
  • the lower cover surface 53b is formed with the rounding 5 formed as sealing means 59b with an axial, d. H. pressed in the direction of the longitudinal axis of the valve body force component against the valve seat.
  • the valve body 52 on the lower top surface 53b has a smaller diameter than the valve body 52 pin 57, which has the task of minimizing the design-related dead space of the valve to affect the capacity of the compressor at full load as low as possible.
  • the connecting valve is guided in a bore 29 of the intermediate wall 24 and is in the open position A (pressure P in the compression chamber 7> Pz) with the sealing means 59a to the stop 26 at.
  • the compression chamber 7 is in fluid communication with the connecting channel 44.
  • the closed position B pressure p in the compression space 7 ⁇ P z
  • the sealant 59b bears against the valve seat 60, so that the connection between the compression space 7 and the connecting passage 44 is interrupted.
  • the pressure in the connecting channel 44 remains, ie the pressure in the Zuschaltraum 40 at the pressure P z in the control chamber 20.
  • the spaces 20 and 40 can communicate with each other, which is harmless insofar as the Zuschaltraum 40 is effectively sealed against the compression chamber 7 ,
  • third pressure sensor 80 electrical connection line 82 electrical connection line 84 electrical connection line 86 electrical connection line 88 electrical connection line

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur à pistons (1) comprenant au moins un cylindre à piston (4). Le cylindre à piston (4) comporte au moins une chambre de compression (7) ainsi qu'au moins un raccordement d'aspiration (2) et un raccordement de pression (3). Par ailleurs, au moins une chambre de mise en circuit (40) non modifiable comporte au moins une soupape de mise en circuit (50) et un dispositif d'actionnement (30) de la soupape de mise en circuit (50), la chambre de compression (7) et la chambre de mise en circuit (40) étant en connexion fluidique l'une avec l'autre par l'intermédiaire de la soupape de mise en circuit (50). Le dispositif d'actionnement (30) est un dispositif de commande pneumatique (31) et la soupape de mise en circuit (50) est une soupape à actionnement pneumatique. La soupape de mise en circuit (50) peut être connectée au choix au raccordement d'aspiration (2) ou au raccordement de pression (3) du cylindre à piston (4) par l'intermédiaire du dispositif de commande pneumatique (31).
PCT/EP2012/057357 2011-07-20 2012-04-23 Compresseur à pistons Ceased WO2013010687A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011079478A DE102011079478A1 (de) 2011-07-20 2011-07-20 Kolbenverdichter
DE102011079478.6 2011-07-20

Publications (1)

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WO2013010687A1 true WO2013010687A1 (fr) 2013-01-24

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PCT/EP2012/057357 Ceased WO2013010687A1 (fr) 2011-07-20 2012-04-23 Compresseur à pistons

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WO (1) WO2013010687A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE664566C (de) 1935-07-03 1938-09-05 Rheinmetall Borsig Akt Ges Wer Verfahren zur stufenlosen Mengenregelung von ein- oder mehrstufigen Kolbenverdichtern unter Verwendung eines unveraenderlichen Zuschaltraumes
DE681287C (de) 1937-06-05 1939-09-20 Demag Akt Ges Vorrichtung zur Mengenregelung von Kolbenverdichtern
DE857259C (de) 1940-02-13 1952-11-27 Hoerbiger & Co Mehrstufiger Kolbenverdichter mit stufenloser Liefermengenregelung durch synchron zugeschaltete Zuschaltraeume in den einzelnen Verdichterstufen
CH389816A (de) * 1961-06-20 1965-03-31 Veb Zek Vorrichtung zur Fördermengenregelung von Hubkolbenverdichtern, insbesondere für Hochdruckstufen
AT277436B (de) * 1967-02-02 1969-12-29 Hoerbiger Ventilwerke Ag Einrichtung zur stufenlosen Liefermengenregelung für Kolbenverdichter
DE3930814A1 (de) * 1989-09-14 1991-03-28 Knorr Bremse Ag Einrichtung zur leistungseinsparung bei kolbenverdichtern, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
DE4026684A1 (de) * 1990-08-23 1992-02-27 Knorr Bremse Ag Einrichtung zur leistungseinsparung bei kolbenverdichtern, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
EP1400692A1 (fr) * 2002-09-19 2004-03-24 HOERBIGER KOMPRESSORTECHNIK SERVICES GmbH Compresseur volumétrique à piston et procédé de réglage à variation continue de son débit

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