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EP4089280A1 - Compresseur à piston à réglage de capacité variable - Google Patents

Compresseur à piston à réglage de capacité variable Download PDF

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Publication number
EP4089280A1
EP4089280A1 EP22172088.1A EP22172088A EP4089280A1 EP 4089280 A1 EP4089280 A1 EP 4089280A1 EP 22172088 A EP22172088 A EP 22172088A EP 4089280 A1 EP4089280 A1 EP 4089280A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
actuator
sequence
opening
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.)
Pending
Application number
EP22172088.1A
Other languages
German (de)
English (en)
Inventor
Matthias Kornfeld
Klaus Stachel
Lili Wang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hoerbiger Wien GmbH
Original Assignee
Hoerbiger Wien 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 Hoerbiger Wien GmbH filed Critical Hoerbiger Wien GmbH
Publication of EP4089280A1 publication Critical patent/EP4089280A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • 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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc 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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1053—Adaptations or arrangements of distribution members the members being Hoerbigen 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1208—Angular position of the shaft
    • 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
    • F04B2205/16—Opening or closing of a valve in a circuit

Definitions

  • the invention relates to a piston compressor with a piston which can be moved back and forth in a cylinder in order to form a compression space in the cylinder, at least one suction valve and at least one pressure valve being provided on the compression space, at least one connection space being provided with a fixed connection space volume, which is connected to the compression chamber via an overflow opening, a sequence valve being provided for opening and closing the overflow opening and a sequence valve control unit for actuating the sequence valve. Furthermore, the invention relates to a method for operating such a piston compressor and a valve assembly for a piston compressor.
  • the regulation of the capacity or the flow rate of a piston compressor by means of an additional chamber is a well-established principle that is mainly used in piston compressors with a constant speed.
  • the dead space can be increased by the switch-on space, so that the pressure increase and decrease rate of the compressor flattens out and the quantity of the conveyed medium can be reduced.
  • This form of control is hardly lossy and is often used, especially in medium-sized and large compressors, to adjust the operating point of the compressor to its drive.
  • the type of change in the volume of the dead space by means of an additional space can in principle take place in two ways. On the one hand, one or more switch-on spaces with a fixed volume can be provided, which can be switched on in series or in parallel via one or more valves. On the other hand, an additional space with a variable volume can be provided, the volume being variable by moving a piston.
  • connection rooms with different volumes are off, for example CN 111188759A or US 5,735,675A known.
  • individual partial volumes of the connection chamber are connected to the compression chamber via hydraulic or pneumatic actuators by opening a valve.
  • switching on is relatively slow compared to the compressor speed.
  • the sequence valve remains open over a longer period of time, so that the associated connection space remains connected to the compression volume.
  • sequence valve is designed as an automatic ring valve which automatically opens and closes the overflow opening depending on a pressure ratio between a pressure in the supply space and a pressure in the compression space, with the supply valve opening automatically when the pressure in the supply space is greater than the pressure in the compression chamber, that an unloader is provided, which can be actuated by an electrically controllable actuator in order to keep the sequence valve in an open state, regardless of the pressure ratio, and that the electromagnetic actuator can be controlled by the sequence valve control unit for actuation.
  • a flow cross-sectional area of the overflow opening in the open state of the sequence valve is preferably at least 5% of a bore cross-sectional area of a bore of the cylinder, preferably at least 10%, particularly preferably at least 15%.
  • the bore diameter of the bore of the cylinder is preferably at least 100 mm, preferably at least 500 mm, particularly preferably at least 800 mm.
  • the throttling losses can be reduced by large flow cross-sections and the force required to keep the valve open can be reduced.
  • the advantage of the ring valve increases in particular with the size of the compressor, in particular the bore diameter.
  • the actuator preferably has a switching frequency of at least 5 Hz, preferably at least 10 Hz, particularly preferably at least 20 Hz.
  • An electromagnetic actuator or an electrohydraulic actuator is advantageously provided as the actuator. As a result, very precise closing times of the valve can be achieved. Electromagnetic actuators and electrohydraulic actuators are particularly well suited for this.
  • the suction valve and/or the pressure valve is also designed as an automatic valve, preferably as an automatic ring valve, because this means that no actuators are required for actuation.
  • the suction valve and/or the pressure valve are preferably arranged on a peripheral surface of the cylinder in the compression space and/or the sequence valve is arranged on an end face of the cylinder of the piston compressor opposite a piston head of the piston. This is advantageous because there is plenty of space for the sequence valve on the front side. In addition, a simple installation and retrofitting of the sequence valve can thereby be made possible.
  • the sequence valve preferably has a plurality of concentrically arranged, at least partially annular overflow openings, each overflow opening being assigned a sealing element and the unloader acting on the sealing elements through the annular overflow openings.
  • each overflow opening being assigned a sealing element and the unloader acting on the sealing elements through the annular overflow openings.
  • connection valve can have a valve housing in which the connection space is provided, with the electromagnetic actuator being arranged outside of the valve housing and being connected to the unloader via a transmission rod which protrudes through a wall of the valve housing into the connection space .
  • the actuator can be protected from the high temperatures and pressures in the switchgear room and a simple connection to the control unit is possible.
  • the sequence valve control unit is preferably designed to control the sequence valve as a function of a load signal and/or as a function of a crank angle signal of the piston compressor.
  • the switch-on chamber can advantageously be switched on and off depending on the operating state of the piston compressor.
  • the object is also achieved with a valve assembly in that the sequence valve is designed as an automatic ring valve that automatically opens and closes the overflow opening depending on a pressure ratio between a pressure in the supply chamber and an ambient pressure, with the sequence valve opening automatically when the pressure in the connection space is greater than the ambient pressure and that a lifting gripper is provided which can be actuated by an electrically controllable actuator in order to keep the connection valve in an open state regardless of the pressure ratio, the actuator being controllable by the connection valve control unit for actuation.
  • the sequence valve is designed as an automatic ring valve that automatically opens and closes the overflow opening depending on a pressure ratio between a pressure in the supply chamber and an ambient pressure, with the sequence valve opening automatically when the pressure in the connection space is greater than the ambient pressure and that a lifting gripper is provided which can be actuated by an electrically controllable actuator in order to keep the connection valve in an open state regardless of the pressure ratio, the actuator being controllable by the connection valve control unit for actuation.
  • connection valve opens automatically at an opening point in the expansion stroke before the suction valve opens, if a pressure in the connection space is greater than a pressure in the compression space, with the unloader being activated in order to open the connection valve independently of the pressure in the switch-on chamber and the pressure in the compression chamber in the open state and the unloader is deactivated after the closing of the suction valve at a certain point in the compression stroke, so that the switch-on valve at a fixed closing point in the compression stroke by the higher pressure in the compression chamber relative to the pressure in the switch-on chamber automatically closes, with the unloader being actuated by the actuator and the actuator being controlled by the sequence valve control unit.
  • a section through a compressor housing 10 of a piston compressor 1 in the region of a cylinder 2 is shown schematically in each case. Since the structure and the mode of operation of a piston compressor 1 are well known, they will not be discussed in more detail at this point, but instead the components relevant to the invention and their mode of operation will be explained below. Even if only one cylinder 2 is shown here as an example, it is of course clear that the piston compressor 1 can also have a plurality of cylinders 2 .
  • a piston 3 is arranged in the cylinder 2 in a known manner and can be moved back and forth in the cylinder 2 .
  • the piston 3 can be driven, for example, via a piston rod 4 that is only indicated, which oscillates in the axial direction.
  • the piston rod 4 can in turn be driven by a connecting rod (not shown) via a crankshaft.
  • the lateral forces are absorbed by a separate joint, the so-called crosshead, which is mounted on plain bearings in cylinder 2 or the crankcase.
  • the piston rod 4 performs a purely axial movement.
  • the lateral forces are absorbed by the piston 3 and supported on the cylinder 2.
  • the type of drive is immaterial for the invention and essentially depends on the design, the size and the application of the piston compressor 1 .
  • the crosshead design is used, for example, in double-acting piston compressors.
  • Fig.1b differs from Fig.1a in that a separate liner 2a is used in the compressor housing 10, which is also known as a cylinder liner, and through the structural design of the valve assembly VG of the sequence valve 13 described below.
  • the liner 2a forms the cylinder 2 and the piston 3 is moved within the liner 2a.
  • a compression chamber 5 is formed in the cylinder 2 above a piston crown 3a of the piston 3, in which a compression medium such as air or a specific gas is compressed by the movement of the piston 3.
  • the compression medium can be drawn in from one or more suction lines 7 via one or more suction valves 6 and fed to one or more pressure lines 9 via one or more pressure valves 8 .
  • one or more suction valves 6 and/or one or more pressure valves 8 can be arranged on the circumference of the cylinder 2, for example as shown. If a separate cylinder head (not shown) is provided on the piston compressor 1, then an arrangement of the suction valve 6 and/or pressure valve 8 on the cylinder head of the piston compressor 1 would also be possible. In this case, the compression chamber 5 would be formed between the piston crown 3a of the piston 3 and the cylinder head.
  • the suction valve 6 and the pressure valve 8 are only indicated as schematic check valves by corresponding symbols.
  • controllable valves could also be used, which can be (forcedly) actuated by an actuator, for example hydraulic, pneumatic or electromagnetically actuated valves.
  • the specific structural design plays no significant role for the invention and is the responsibility of the person skilled in the art.
  • the suction valve 6 and/or the pressure valve 8 can be designed as known automatic ring valves.
  • the designed as a ring valve suction valve 6 opens during an expansion stroke of the piston 3 automatically depending on the pressure ratio between a pressure in the suction line 7 and a relatively lower pressure in the compression chamber 5 in the direction of the compression chamber 5.
  • a prestressing device e.g. in the form of spring elements, can be provided on the suction valve 6 in order to generate a prestressing force by which the suction valve 6 is prestressed in the direction of the closed state . This can influence the opening and closing behavior.
  • the pressure valve 8 which is designed as a ring valve, opens automatically during a compression stroke of the piston 3 depending on the pressure ratio between a pressure in the pressure line 9 and the relatively higher pressure in the compression chamber 5 in the direction of the pressure line 9.
  • a pretensioning device can also be used , e.g. in the form of spring elements, can be provided on the pressure valve 8 in order to generate a biasing force by which the pressure valve 8 is biased in the direction of the closed state.
  • a certain constant delivery rate is obtained for each speed of the piston compressor 1. In the case of large compressors, which are usually operated at a constant speed, the flow rate is therefore essentially constant.
  • one or more additional chambers with a constant or variable additional chamber volume can be provided for this purpose, which can be selectively connected to the compression chamber 5 .
  • the dead space in the cylinder 2 is increased, as a result of which the pressure rise or fall in the compression chamber 5 can be flattened out, as will be seen below with reference to FIG Fig.2 will be explained in more detail.
  • a single switch-on chamber 11 is provided with a constant volume of the switch-on chamber.
  • the connection chamber 11 is connected to the compression chamber 5 via at least one overflow opening 12 .
  • sequence valve 13 for opening and closing the overflow opening 12 and a sequence valve control unit 14 for controlling the sequence valve.
  • sequence valve 13 for opening and closing the overflow opening 12
  • sequence valve control unit 14 for controlling the sequence valve.
  • this is only to be understood as an example and not as a restriction.
  • several parallel connection chambers 11, each with a connection valve 13 according to the invention could also be provided, or several connection chambers 11 connected to one another in series via valves, with a common connection valve 13 according to the invention, to the compression chamber 5.
  • connection space volume is variable, for example by means of a piston.
  • the example shown is sufficient for understanding the invention.
  • sequence valve control unit 14 can, for example, be controlled by a higher-level compressor control unit 16 of the piston compressor 1 are controlled, but could of course also be integrated into this.
  • the compressor control unit 16 can, for example, transmit a load signal L about the current load state of the piston compressor 1 to the sequence valve control unit 14 .
  • the sequence valve control unit 14 can set a specific operating mode for the capacity control and set and change the closing point SP and the opening point OP of the sequence valve 13 accordingly depending on the load signal L.
  • the compressor control unit 16 can, for example, also transmit a crank angle signal ⁇ to the sequence valve control unit 14 .
  • the crank angle signal ⁇ can be detected by a crank angle sensor of the piston compressor 1, for example.
  • the sequence valve 13 is embodied as an automatic ring valve which automatically opens and closes the overflow opening(s) 12 depending on a pressure ratio between a pressure in the connection chamber 11 and a pressure in the compression chamber 5, with the sequence valve opening in the direction of the compression chamber 5 when the pressure in the connection space is greater than the pressure in the compression space 5.
  • an unloader 15 is provided, which can be actuated by a suitable actuator 17.
  • the unloader 15 is intended to keep the connecting valve 13 in an open state after it has opened automatically, as shown below with reference to FIG Fig.2 will be explained in detail later.
  • the actuator 17 can be controlled by the sequence valve control unit 14 (or the compressor control unit) in order to actuate the unloader 15 .
  • a suitable actuator 17 is an actuator with a sufficiently short actuation time (or sufficiently high switching frequency) that can generate a sufficiently large actuation force to keep the sequence valve 13 open.
  • An electrohydraulic actuator or an electromagnetic actuator is preferably provided as the actuator 17 .
  • Electromagnetic actuators have the advantage that they enable relatively short actuation times or high switching frequencies and that no hydraulic fluid is required.
  • Electrohydraulic actuators have the advantage that relatively large actuation forces can be generated.
  • the actuator 17 is designed, for example, as an electromagnetic actuator.
  • a separate valve assembly VG can be provided with an optionally multi-part valve housing 18 in which the switch-on chamber 11 is arranged.
  • the valve assembly VG can be arranged in the area of the cylinder 2 on the compressor housing 10 of the piston compressor 1 . If the reciprocating compressor has a separate cylinder head (not shown), then the valve assembly VG can be installed, for example, at an opening provided for this purpose on the cylinder head of the reciprocating compressor. In the following, however, reference is made to the variant shown without a cylinder head.
  • the valve assembly VG can be fastened to the compressor housing 10 with suitable fastening means 19, for example with a number of screws distributed around the circumference, as in FIG Fig.1a and Fig.1b is indicated schematically.
  • the valve housing 18 preferably has a cylindrical valve housing section 26 with a valve housing diameter Dv.
  • the valve housing section 26 is at least partially arranged inside the cylinder 2 .
  • the cylindrical valve housing section 26 is not arranged directly in the cylinder 2, in which the piston 3 moves, but in a cylindrical receiving opening provided for receiving the liner 2a.
  • valve housing diameter Dv essentially corresponds to the bore diameter B of cylinder 2.
  • valve housing diameter Dv is slightly larger than the bore diameter B due to the liner 2a and essentially corresponds to the diameter of the cylindrical receiving opening.
  • the actuator 17 is preferably arranged outside the valve housing 18 and is connected to the unloader 15 via a transmission rod 20 which protrudes through a wall of the valve housing 18 into the connection space 11 .
  • this is advantageous for thermal reasons because the actuator 17 is not exposed to the temperatures and pressures in the connection space 11 .
  • a simpler electrical connection to the sequence valve control unit 14 is thus possible.
  • the switch-on space 11 can be made smaller with the same switch-on space volume, because the volume of the actuator 17 does not reduce the switch-on space volume of the switch-on space 11 .
  • the valve housing 18 is advantageously designed in several parts.
  • valve housing 18 has a first housing part 18a, on which the cylindrical valve housing section 26 is provided and on which the sequence valve 13 is arranged, and a second housing part 18b, which is here in the form a housing cover is formed.
  • the connection space 11 is hereby formed by the first and second housing part 18a, 18b or delimited thereby. Due to the multi-part design, easier assembly and maintenance of the sequence valve 13 are possible, among other things.
  • the actuator 17 is arranged outside on the second housing part 18b or housing cover and the transmission rod 20 protrudes through the housing cover into the connection space 11.
  • an automatic ring valve with unloader 15 and a suitable, in particular electromagnetic, actuator 17 now makes it possible to react very precisely to load changes of the compressor 1 within a very short time, in particular within a compression cycle or one revolution of the crankshaft. For example, it is possible to close the sequence valve 13 in the compression stroke within a maximum of 5°, preferably a maximum of 3° crank angle after the unloader 15 has been actuated. In the prior art, such rapid control of the sequence valves was previously not possible due to the valve geometries used and in particular due to the relatively slow pneumatic or exclusively hydraulic actuation.
  • the capacity control can be used in a particularly advantageous manner in larger piston compressors 1 that have a bore diameter B of the cylinder 2 of at least 100 mm, preferably at least 500 mm, particularly preferably at least 800 mm.
  • the bore diameter B is in Fig.1b formed by the inner diameter of the liner 2a.
  • Conventional seat valves used hitherto quickly reach their limits here because the overflow cross section of the overflow opening is relatively small for a comparable valve lift in relation to the valve surface facing the compression chamber due to the design.
  • there would be a relatively strong throttling in the area of the overflow opening which would lead to an undesired heating of the compressed compression medium due to the throttling losses.
  • the ring valve is preferably dimensioned such that a flow cross-sectional area of the overflow opening(s) 12 when the sequence valve 13 is open is at least 5% of a bore cross-sectional area of the bore of the cylinder 2 or a cross-sectional area of the cylindrical valve housing section 26 with the housing diameter Dv, preferably at least 10%. more preferably at least 15%.
  • a sufficiently large area can be made available so that the compression medium does not heat up to an unacceptably high level as a result of throttling in the area of the overflow opening(s) 12 .
  • the actuator 17 has a switching frequency of at least 5 Hz, preferably at least 10 Hz, particularly preferably at least 20 Hz.
  • the unloader 15 can be actuated very quickly, so that closing times of the sequence valve 13 of less than 5° CA, preferably less than 3° CA, can be implemented.
  • the suction valve 6 and the pressure valve 8 are arranged on a peripheral surface of the cylinder 2 in the compression chamber 5 and the sequence valve 13 is arranged on an end face of the cylinder 2 in the compression chamber 5 opposite the piston head 3a of the piston 3 .
  • This arrangement is advantageous because it means that a relatively large area is available for the sequence valve 13 .
  • a different arrangement would also be conceivable in principle.
  • a bevel 26a is provided at the free end of the cylindrical housing section 26 of the first housing part 18a, which faces the compression chamber 5 in the assembled state, at least in the region of the pressure and suction valves 6, 8.
  • the bevel 26a is preferably in the form of a chamfer running around the entire circumference of the housing section 26 .
  • the sequence valve 13 preferably has a plurality of concentrically arranged overflow openings 12, which are annular at least in sections, such as in Fig.1b is shown.
  • Each overflow opening 12 is assigned a corresponding sealing element 21 which seals the respective overflow opening 12 when the sequence valve 13 is in the closed state.
  • the unloader 15 acts on the sealing elements 21 through the at least partially ring-shaped overflow openings 12 by means of unloader fingers 15a.
  • several ring-shaped sealing elements 21 can also be connected via radial webs to form a common sealing plate, as in Fig.1b is indicated.
  • Such ring valves are basically known from the prior art for suction valves, for example out EP 2 876 303 B1 , which is why only the basic structure is discussed here.
  • the sequence valve 13 can have a valve carrier 22 which is arranged in an opening provided for this purpose in the valve housing 18 and can be fastened to the valve housing 18 by means of suitable fastening means 27 such as screws.
  • valve carrier 22 forms Fig.1a thus a part of the valve housing 18, which faces the compression chamber 5 in the installed state on the piston compressor 1.
  • a suitable seal (not shown) can also be arranged between the valve carrier 22 and the housing 18 .
  • a recess in which a valve seat plate 23 is arranged is provided in the valve carrier 22 .
  • the valve seat plate 23 can in turn be fastened to the valve carrier 22 with suitable fastening means 28 such as screws.
  • valve seat plate 23 On the valve seat plate 23 are a ( Fig.1a ) or preferably several ( Fig.1b ) Preferably concentric ring-shaped overflow openings 12 are arranged. A suitable seal (not shown) can in turn be provided between the valve seat plate 23 and the valve carrier 22 .
  • the sequence valve 13 preferably also has a so-called valve catcher 24, which, for example, according to the example Fig.1a can be fastened in a suitable manner on the side of the valve seat plate 23 which faces the outside of the valve housing 18 and which faces the compression chamber 5 in the mounted state on the piston compressor 1 .
  • the valve catcher 24 may be formed as a substantially circular plate.
  • the valve catcher 24 can, for example, be attached to the valve seat plate 23 via a central attachment element 25, for example in the form of a threaded rod.
  • the sealing element or elements 21 are arranged so as to be movable in the axial direction between the valve seat plate 23 and the valve catcher.
  • the sealing element or elements 21 are preferably made of a material with sufficiently high strength and the best possible sealing effect, for example a suitable plastic.
  • a pretensioning device can also be provided in order to pretension the or the sealing elements 21 in the direction of the valve seat plate 23 in the closed position.
  • a number of spring elements (not shown) distributed in the circumferential direction, for example helical springs, can be provided as a prestressing device between the sealing element or elements 21 and the valve catcher 24 .
  • the sealing element or elements 21 are in contact with the valve seat plate 23 and close the overflow openings 12 of the valve seat plate 23. If the pressure in the switching chamber 11 exceeds the pressure in the compression chamber and any pretensioning force of the pretensioning device during the expansion stroke of the piston 3 exceeds, the sealing element or elements 21 are automatically displaced in the direction of the valve catcher 24 . In the maximum open state of the sequence valve 13 or the Sealing elements 21 also rest against the valve catcher 24. The valve lift can thus be limited by the valve catcher 24. Suitable openings 24a are advantageously also provided in the valve catcher 24 in order to keep the throttling effect of the open sequence valve 13 as small as possible.
  • the unloader 15 is arranged here within the connecting space 11 and the unloader fingers 15a of the unloader 15 protrude through the overflow openings 12 in order to act on the sealing element(s) 21.
  • the unloader 15 is connected to the actuator 17 by means of the transmission rod 20 .
  • the actuator 17 can be controlled by the sequence valve control unit 14 in order to actuate the unloader 15 .
  • the working stroke of the unloader 15 can be fixed, but could also be adjustable, for example by means of a suitable adjusting device that can be provided in the valve assembly VG.
  • the adjusting device could, for example, be designed in such a way that the length of the transmission rod 20 can be changed or that a common position of the actuator 17 including the transmission rod 20 and the unloader 15 can be adjusted.
  • Fig.1b the valve assembly VG is designed differently than in Fig.1a , with only the essential differences being discussed below.
  • the basic function remains unchanged.
  • the sequence valve 13 in Fig.1b has a valve seat plate 23 in which three concentric annular overflow openings 12 are provided.
  • the sequence valve 13 has three annular sealing elements 21 that interact with it.
  • the sealing elements 21 are connected to one another here and form a common sealing plate.
  • individual ring-shaped sealing elements 21 that can be moved independently of one another would also be possible. Consequently, the unloader 15 has at least one unloader finger 15a per overflow opening 12 .
  • the sequence valve 13 in Fig.1b no separate valve support 22, which is fixed in the valve housing by means of fasteners 27, such as screws.
  • the valve catcher 24 is designed in such a way that it forms a part of the valve housing 18 which faces the compression chamber 5 in the assembled state.
  • a first step is provided on an outer peripheral surface of the valve catcher 24 and a second step corresponding to the first step is provided on an inner peripheral surface of the opening of the valve housing 18 facing the compression chamber 5 .
  • the first step of the valve catcher 24 rests against the second step of the valve housing 18 in the assembled state.
  • the valve catcher 24 is centered in the valve housing 18 and closes the opening in the valve housing 18 from the side of the connection space 11, ie from the inside.
  • a contact surface is provided on the side of the valve catcher 24 facing the switch-on chamber 11, on which the valve seat plate 23 rests.
  • the valve catcher 24 can, for example, in turn be connected to the valve seat plate 23 by a central fastening element 25, for example in the form of a threaded rod.
  • Fig.1a In contrast to Fig.1a is on the valve housing 18 in accordance with the example Fig.1b additionally provided a holding portion 18c.
  • the holding section 18a is arranged on the side of the second housing part 18b, in this case the housing cover, which faces the switch-on space 11 .
  • the holding section 18c protrudes into the switch-on chamber 11 and contacts the valve seat plate 23.
  • a holding shoulder for example, can be provided for this purpose on the side of the valve seat plate 23 facing the switch-on chamber 11, as in FIG Fig.1b shown, which can also be used for centering.
  • the holding section 18c can, for example, have holding fingers distributed over the circumference and spaced apart from one another in the circumferential direction.
  • the holding section 18c can preferably also be designed in the form of an at least partially cylindrical holding sleeve, so that a holding force that is as uniform as possible can be exerted on the valve seat plate 23 in the circumferential direction.
  • the holding section 18c presses on the valve seat plate 23 and thereby fixes the valve seat plate 23 incl intended.
  • the space outside the sleeve is therefore not part of the switch-on volume and therefore does not contribute to increasing the dead space. If necessary, however, suitable connection openings could also be provided on the circumference of the holding sleeve in order to increase the volume that can be switched on.
  • holding means such as screws are no longer necessary in an advantageous manner in order to fasten the valve seat plate 23 and/or the valve catcher 24 to the valve housing 18 .
  • the holding force is generated here via the fastening means or, in particular, screws 19, with which the entire valve housing 18 (ie the first, lower housing part 18a and the second, upper housing part 18b together) is fastened to the compressor housing 10.
  • the holding section 18c is designed as an integral part of the second housing part 18b or housing cover.
  • the holding section 18c could, for example, also be designed in the form of one or more separate components which could, for example, be attached in a suitable manner to the second housing part 18b, here the housing cover. With a suitable design, a fixed attachment to the second housing part 18b could also be dispensed with under certain circumstances.
  • Fig.2 shows in pV diagram of the piston compressor 1, with the ordinate of the pressure p im Compression chamber 5 is plotted and the volume V in the compression chamber 5 is plotted on the abscissa.
  • the pressure p and the volume V change depending on the piston stroke of the piston 3 between a bottom dead center UT and a top dead center OT and depending on the switching points of the Suction and pressure valve 6, 8.
  • the solid line between the points ABCDA represents a work cycle with a deactivated connection chamber 11 or a piston compressor 1 without connection chamber 11.
  • the piston 3 is at bottom dead center UT at the beginning of the compression stroke, with the suction valve 6 and the pressure valve 8 closed.
  • the movement of the piston 3 compresses the compression medium in the compression space 5 until the opening pressure pD of the pressure valve is reached and the pressure valve 8 opens at point B.
  • the compressed compression medium is displaced from the compression space 5 into the pressure line 9 by the open pressure valve 8 .
  • the piston 3 reaches top dead center OT and the pressure valve 8 closes.
  • the expansion stroke of the piston 3 now begins, with the piston 3 being moved again in the opposite direction towards bottom dead center UT.
  • the volume in the compression space 5 increases again and the pressure p decreases.
  • the suction valve 6 opens and fresh compression medium is sucked in through the suction valve 6 from the suction line 7 at an essentially constant pressure until the piston 3 again reaches the bottom dead center UT and the work cycle is completed.
  • the area F0 enclosed by the solid line between the points ABCDA corresponds to the maximum work of the compressor 1 with the switch-on chamber 11 deactivated or of a piston compressor 1 without the switch-on chamber 11, as in Figure 3a is shown.
  • the work is essentially proportional to the flow rate, so the area F can generally be viewed as a measure of the flow rate or the capacity of the piston compressor 1.
  • this area F can now be specifically influenced by connecting the compression chamber 5 to the connection chamber 11 by opening the connection valve 13 or separating it again by closing the connection valve 13, as explained below.
  • the flow rate can be adjusted essentially steplessly between the maximum flow rate (area F0) and a minimum flow rate (area F3 - Fig.3d ) can be set.
  • the switching valve 13 can be kept permanently in the open state by means of the unloader 15 .
  • the compression space 5 is thus permanently connected to the connection space 11 via the overflow opening(s) 12, so that the dead space is substantially permanently enlarged as a result.
  • the compression line A-B3 (dotted) is much flatter than the compression line AB (solid) for operation without the switch-on chamber 11.
  • the opening pressure pD is therefore reached significantly later in the compression stroke, so that that of the pressure valve 8 is correspondingly later opens at point B3.
  • Minimum flow operation is in Fig.3d shown. It can be seen that the area F3 enclosed by the dotted lines between A-B3-C-D3-A is significantly smaller than that in Figure 3a shown area F0 between ABCD, which corresponds to the maximum flow rate.
  • the delivery rate of the compressor 1 can now vary between the maximum delivery rate (area F0 - Figure 3a ) and the minimum flow rate (area F3 - Fig.3d ) can be continuously adjusted, as exemplified by a first operating mode in the pV diagram in Fig.3b and based on a second operating mode in the pV diagram in Fig.3c is shown.
  • the first area F1 enclosed by the dashed line in Fig.3b is larger than the second area F2 enclosed by the dot-dash line in Fig.3c .
  • the flow rate of the first operating mode is proportional to the first area F1 and is therefore greater than the flow rate of the second operating mode, which is proportional to the second area F2.
  • Fig.2 the control of the switching valve 13 is explained in more detail below.
  • the switching valve 13 is designed according to the invention as an automatic ring valve, the sealing element(s) 21 are moved away from the valve seat plate 23 in the direction of of the compression chamber 5 lifted, whereby the overflow opening / s 12 are released. As a result, no additional opening force is required, which would have to be applied by the actuator 17 via the unloader 15 .
  • the sequence valve 13 opens, for example, at a first opening point OP1 in the expansion stroke at a first sequence valve opening pressure pOP1 in the compression chamber 5 lying between the opening pressure pD of the pressure valve 8 and the opening pressure pS of the suction valve 6 and at a first sequence valve opening volume VOP1.
  • the sequence valve 13 opens, for example, at a second opening point OP2 in the expansion stroke at a second sequence valve opening pressure pOP2 in the compression chamber 5 lying between the opening pressure pD of the pressure valve 8 and the opening pressure pS of the suction valve 6 and at a second sequence valve opening volume VOP2.
  • the volume V im Compression chamber 5 in a piston compressor 1 generally dependent on the crank angle ⁇ of the crankshaft, i.e. V( ⁇ ), as on the abscissa in Fig.2 shown.
  • the opening point OP of the sequence valve 13 can thus be assigned to the crank angle ⁇ .
  • the crank angle ⁇ can be detected, for example, by a crank angle sensor and transmitted to the sequence valve control unit 14 in the form of a crank angle signal ⁇ .
  • the dashed expansion curve in the first operating mode from the first opening point OP1 runs much flatter than the solid expansion curve in the operating mode without or with deactivated switch-on chamber 11 due to the now enlarged dead space in cylinder 2.
  • the unloader 15 is activated by the actuator 17 in order to follow the opening movement of the connection valve 13 or of the sealing element(s) 21.
  • This movement can take place, for example, within a period of up to 20° crank angle and requires little or no effort from the actuator 17.
  • the mechanical and thermal stress on the valve assembly VG can advantageously be kept low.
  • the sealing element(s) 21 of the connection valve 13 are held in the open position by the unloader fingers 15a of the unloader 15 until the following compression stroke, after the suction valve 6 has already been closed again at point A.
  • the actuator 17 generates a holding force that counteracts a closing force that is exerted on the sealing element or elements by the pressure ratio between the pressure in the compression space 5 and the (relatively lower) pressure in the connection space 11 and the resulting flow of the compression medium into the connection space 11 21 is exercised.
  • the unloader 15 is deactivated, that is to say it is moved in the opposite direction away from the sealing elements 21, in that the actuator 17 is activated by the sequence valve control unit 14 at a specified point in time.
  • the sequence valve 13 is preferably designed in such a way that the flow forces acting during the closing process result in a deformation, in particular a deflection, of the sealing element(s) 21 .
  • a sufficiently high restoring force can be generated so that the closing process is made possible in a crank angle range of at most 5°, preferably at most 3° crank angle after deactivation of the unloader 15 .
  • the first closing point SP1 of the connecting valve 13 can be defined as a function of the crank angle ⁇ by assigning the first closing volume of the connecting valve VSP1( ⁇ ) to the crank angle ⁇ .
  • the sequence valve control unit 14 can therefore control the actuator 17 as a function of the crank angle ⁇ in such a way that the sequence valve 13 is closed at the specified first closing point SP1.
  • Fig.3c is the second operating mode with a compared to the first operating mode in Fig.3b lower flow rate (proportional to area F2) shown. It can be seen that the second closing point SP2 of the sequence valve 13 is later in the compression stroke than the first closing point SP1. The dot-dash compression line of the second operating mode therefore runs flatter up to the second closing point SP2 and only then rises again due to the smaller clearance volume. Due to the later second closing point SP2, the second opening point OP2 is consequently again fixed in the subsequent expansion stroke, because the sequence valve closing pressure pSP2 and the sequence valve opening pressure pOP2 are essentially at the same pressure level pSP2 ⁇ pOP2.
  • the sequence valve control unit 14 receives a load signal L of the piston compressor 1, for example from the compressor control unit 16 ( Fig.1 ).
  • the sequence valve control unit 14 can select a desired operating mode of the sequence valve 13 depending on the load of the piston compressor 1 set to.
  • the inventive design of the sequence valve 13 with unloader 15 and suitable actuator 17 also makes it possible for the operating mode of the sequence valve 13 to be changed within a very short time depending on the load of the compressor 1 .
  • the closing point SP can be changed within a compression cycle (which corresponds to one revolution of the crankshaft in the case of a piston compressor), eg from a first closing point SP1 to a second closing point SP2, as in FIG Fig.2 is shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP22172088.1A 2021-05-10 2022-05-06 Compresseur à piston à réglage de capacité variable Pending EP4089280A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA50359/2021A AT525119B1 (de) 2021-05-10 2021-05-10 Kolbenkompressor mit variabler Kapazitätsregelung

Publications (1)

Publication Number Publication Date
EP4089280A1 true EP4089280A1 (fr) 2022-11-16

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EP22172088.1A Pending EP4089280A1 (fr) 2021-05-10 2022-05-06 Compresseur à piston à réglage de capacité variable

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US (1) US12140137B2 (fr)
EP (1) EP4089280A1 (fr)
JP (1) JP2022174018A (fr)
CN (1) CN115324881A (fr)
AT (1) AT525119B1 (fr)

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Publication number Priority date Publication date Assignee Title
IT202100029873A1 (it) * 2021-11-25 2023-05-25 Nuovo Pignone Tecnologie Srl Sistema valvolare con sensore integrato per compressore alternativo

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GB487916A (en) 1936-06-19 1938-06-28 Johann Robert Hoerbiger Method and apparatus for the infinitely variable regulation of the output of air compressors
DE688429C (de) * 1938-04-26 1940-02-20 Hoerbiger & Co Gleichstromverdichter
US5735675A (en) 1995-07-25 1998-04-07 Peoples; Richard Claude Combination compressor unloader
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
EP2876303B1 (fr) 2013-11-21 2017-12-06 Hoerbiger Kompressortechnik Holding GmbH Griffe de levage pour un élément de soupape d'un clapet de compresseur
WO2017174717A1 (fr) * 2016-04-07 2017-10-12 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Compresseur muni d'un dispositif d'économie d'énergie et procédé de décharge du compresseur
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Publication number Publication date
AT525119A1 (de) 2022-12-15
US20220356874A1 (en) 2022-11-10
AT525119B1 (de) 2023-04-15
JP2022174018A (ja) 2022-11-22
US12140137B2 (en) 2024-11-12
CN115324881A (zh) 2022-11-11

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