EP4004370A1 - Dispositif de soupape pour un compresseur à piston - Google Patents

Dispositif de soupape pour un compresseur à piston

Info

Publication number
EP4004370A1
EP4004370A1 EP20743992.8A EP20743992A EP4004370A1 EP 4004370 A1 EP4004370 A1 EP 4004370A1 EP 20743992 A EP20743992 A EP 20743992A EP 4004370 A1 EP4004370 A1 EP 4004370A1
Authority
EP
European Patent Office
Prior art keywords
lamella
relief
stage
cylinder head
compressor
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
EP20743992.8A
Other languages
German (de)
English (en)
Inventor
Marius BURKAUSKAS
Sven Hensel
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.)
Voith Patent GmbH
Original Assignee
Voith Patent 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 Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP4004370A1 publication Critical patent/EP4004370A1/fr
Pending 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
    • 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
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed 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
    • F04B39/08—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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • 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

Definitions

  • the invention relates to a reciprocating piston compressor for a compressed air supply system in a motor vehicle, such as a truck, bus or rail vehicle.
  • a reciprocating piston compressor essentially comprises two areas, the cylinder head area in which the valves are arranged and the crankshaft housing with at least one cylinder that can be moved in a working space, so that a suction stroke movement and a compression stroke movement arise.
  • the reciprocating compressor can be single-stage or multi-stage, in particular two-stage.
  • the valve device for controlling the air flow is usually assigned to the cylinder head and comprises automatically effective suction valves and pressure valves which are opened and closed by the pressures prevailing in the working space due to the stroke movement of the piston.
  • the suction stroke of the piston causes a negative pressure in the working space of the respective cylinder, so that the associated suction valve opens and the associated pressure valve is closed. Air enters the working chamber of the cylinder or is sucked into the working chamber via the inlet chamber and the inlet channels in the valve carrier plate.
  • the compression stroke of the piston causes an overpressure in the working space of the respective cylinder, so that the associated suction valve closes and the associated pressure valve is opened, whereby compressed air is fed from the working space of the cylinder via the pressure channel into the downstream compressed air system.
  • the suction valve is usually designed as a valve lamella, the valve tongue of which is clamped on one side between the cylinder housing and the cylinder head of the reciprocating piston compressor and on its free end is guided with at least one tab in a recess of the cylinder housing.
  • the valve tongue By means of the valve tongue, the inlet openings in the valve support plate, which connect a suction chamber with the working space of the cylinder, can be closed.
  • the valve lamella is designed in such a way that at least one outlet opening is recessed in the valve support plate, which is arranged between the working space of the cylinder and the pressure channel.
  • the pressure valve via which the outlet opening can be closed, is usually located within the cylinder head area.
  • Another idle valve is known from DE 10 2013 001 147 A1, for example.
  • an idle valve for a relief system is proposed that is held in the closed position by means of a spring and can optionally be switched into an open position by applying a pressure.
  • Such systems are also called “externally controlled systems”.
  • an idle valve device is known. This is arranged in such a way that it does not protrude into the area over which the piston of the compressor moves. All idle systems have in common that in idle operation the working area is connected to another room via a relief duct, so that no compression or only reduced compression occurs.
  • the object of the invention is to propose a relief system by means of which the energy consumption of a reciprocating compressor can be further reduced.
  • the embodiment according to the invention is a Hubkolbenkom compressor for a compressed air supply system in a motor vehicle, with a Zylin derkopf in which a relief system is integrated, by means of which a relief channel in a valve support plate of the cylinder head, the a working space of the reciprocating compressor with a space in Cylinder head connects, is switchable.
  • the relief system comprises a switching device and a lamella, the lamella being attached to the valve carrier plate on the working space side and being designed in such a way that it can be lifted off the valve carrier plate to open the relief channel, the lamella being lifted off can take place automatically and / or controlled by means of the relief system.
  • the automatic lifting of the lamella results in an enlarged effective duct cross-section, which reduces the inflow resistance of the air into the working space during the suction stroke of the cylinder.
  • the controlled lifting of the lamella ensures that the compressor is switched to idle mode in which there is no compression.
  • a preferred embodiment can provide that the cylinder head has an inlet chamber which has several inlet channels in the valve support plate and an inlet valve lamella, designed automatically as a tongue valve, can be connected to the working chamber, the at least one relief channel being arranged within the inlet channels. In other words, that the at least one relief channel is surrounded by inlet channels.
  • the lamella can preferably be designed as a tongue valve, a tongue valve being understood to be a lamella that is clamped on one side and closes a channel in the non-actuated position and opens the passage through the channel in the actuated position.
  • the inlet chamber can preferably be connected to the working space via the inlet channels and the relief channel.
  • the inlet chamber is connected to an air inlet through which, in particular, ambient air enters the inlet chamber.
  • the air is distributed over the inlet ducts and the at least one relief duct and is sucked into the working space via these.
  • the enlarged cross section facilitates the suction stroke movement of the piston, which reduces energy consumption.
  • the relief system for supporting the lamella can comprise a means for limiting the stroke of the lamella. Particularly with large air volumes that are sucked into the working space during the suction stroke due to the resulting negative pressure, it may be necessary to limit the movement of the lamellae, as is also necessary for the valve lamella in accordance with the StdT.
  • a limiter lamella protruding into the working space can be used. So that the dead space remains relatively small, the cylinder can have a corresponding recess for the delimitation lamella. Alternatively, this recess can also be used directly as a means of limiting, so that the lamella hits the recess at least when the lifting movement starts.
  • the relief system can comprise a relief piston which can be reset by means of a spring element and which can be actuated by means of a control pressure.
  • the reciprocating compressor can be designed as a two-stage compressor, with a preliminary stage and a high-pressure stage, with a relief system and a connecting duct that connects the relief duct of the high-pressure stage with the inlet chamber being provided in the cylinder head for each stage.
  • the compression stroke of all stages is relieved via a connection that connects the respective working space to the inlet chamber via the relief channel. In this way, when the lamella is in the relief position, ambient air can enter the working area directly even during the suction stroke of the high pressure stage
  • the lamella of the relief system of the high pressure stage is designed in such a way that it remains in the closed position during operation during the suction stroke.
  • the lamella of the high pressure stage or subsequent high pressure stages is thus designed so that the lamella can only be actively moved into the open position by means of the piston of the relief system.
  • the reciprocating compressor has a cylinder head in which a relief system is integrated, by means of which a relief channel in a valve support plate of the cylinder head, which connects a working space of the reciprocating compressor with a space in the cylinder head, is switchable.
  • the method is characterized in that during a suction stroke in which a negative pressure is generated in the working space, a lamella of the relief system is automatically or, when the relief system is actuated, forcibly moved into an open position, so that additional air via the inlet chamber and the Relief channel is sucked into the work area, or when the relief system is actuated, air can be forced out of the work area via the relief channel.
  • This process is used in a single-stage reciprocating compressor or in the preliminary stage or the first stage of a multi-stage reciprocating compressor.
  • the reciprocating piston compressor as a two-stage compressor, a preliminary stage and a high-pressure stage are connected in series, a relief system being provided in the cylinder head for each stage.
  • a connecting duct for connecting the relief systems can be provided in the cylinder head of the two-stage compressor, the relief duct of the high-pressure stage being connected to the inlet chamber of the preliminary stage via the connecting duct, with the relief pistons of both relief systems being switched in this way for relief or switching to idle mode of the reciprocating compressor that the slats of both stages are moved into an open position.
  • Fig. 1 Piston-side view of the valve plate of a two-stage
  • Fig. 2 Cylinder head side view of the valve plate of a two-stage
  • FIG. 1 shows a piston-side view of the valve carrier plate 4 of a two-stage reciprocating compressor with the relief system which is assigned to the cylinder head 12.
  • the two compressor stages, the preliminary stage 2 and the high pressure stage 3 have a similar structure but differ somewhat in terms of size and function.
  • the basic structure is the same.
  • Both compressor stages have an inlet valve 5a, b, which is fixed on one side and has stop surfaces on the opposite side. For the stop surfaces are in the crankcase 11 not shown here recesses provided through which the opening movement of the inlet valves 5a, b is limited.
  • the outlet channels 23 are arranged within the outer contour of the inlet valves 5a, b and partially run through recesses in the inlet valves 5a, b.
  • the lamellae 9a, b belonging to the relief system 7a, b are arranged roughly in the middle of the inlet valves 5a, b, i.e. roughly in the middle of the working space of the cylinders 20a, b, where the inlet valves 5a, b have a recess.
  • the lamellae 9a, b are also clamped on one side.
  • the valves of preliminary stage 2 and high pressure stage 3 differ somewhat. Due to the larger volume of air that must be sucked in during the suction stroke of the cylinder 20a of the preliminary stage 2, the lamella 9a is designed in such a way that the valve opens automatically with each suction stroke of the cylinder 20a of the preliminary stage 2. To limit the opening movement, a limiting lamella 22 is provided, which represents a stop for the lamella 9a.
  • FIG. 2 shows a cylinder head side view of the valve support plate 4 of a two-stage reciprocating compressor with a relief system.
  • Both stages 2, 3 each have an inlet chamber 14a, b and an outlet chamber 15a, b.
  • the automatically effective outlet valves 6a, b are arranged, which in the closed position close the outlet channels 23 in the valve support plate and are moved into an open position when a definable pressure in the working space is exceeded.
  • the inlet channels 21a are assigned to the inlet valve 5a with the inlet valve plate 18a.
  • the inlet valve lamella 18a is moved into an open position.
  • the inlet valve lamella 18a closes the inlet channels 21a.
  • the discharge processing channels 19a are arranged within the semicircle of the inlet channels 21 a. Their passage is switched by means of the lamella 9a of the relief system 7a.
  • the high-pressure stage is designed somewhat differently, here the relief channel 19b of the relief system 7b is arranged in a separate chamber which is connected to the inlet chamber 14a of the preliminary stage 2 via the connecting channel 13.
  • the separate channel connection between outlet chamber 15a of preliminary stage 2 and inlet chamber 14b of high pressure stage 3 is not shown.
  • Figures 3 and 4 show the relief systems 7a, b of preliminary stage 2 and high pressure stage 3 in section.
  • the general layered structure of the cylinder head 12 is known from the prior art, so that only the channels and chambers that are essential to the invention are considered further here.
  • the relief system 7a according to the invention for the preliminary stage is shown in FIG. 3 and the relief system 7b for the high-pressure stage 3 is shown in FIG.
  • the relief system 7a of the preliminary stage can be used as described above and shown in FIG.
  • all stages following the preliminary stage receive the relief system 7b of the high-pressure stage 2, whereby in a preferred embodiment a connection channel can be provided through which all stages can be connected to the inlet chamber of the preliminary stage.
  • each stage can also include a separate channel that is connected to the environment.
  • the special feature of the relief valve of preliminary stage 2 is the limiting lamella 22, which is designed as a solid component and supports the lamella 9a so that the lamella 9a does not extend too far in bends the working space and this leads to excessive bending stress.
  • the cylinder 20a has a recess at the end face into which the delimiting lamella 22 plunges when the cylinder is at top dead center, so that the dead space is as small as possible.
  • the recess is just large enough to accommodate the delimiting lamella 22 and the lamella 9a lying on it in the open state.
  • the relief piston 10a which is guided in the cylinder head 12, can also be seen. In the position shown, it is in the rest position and is held in this position by a spring.
  • the relief piston 10a can be pressurized via the illustrated control pressure channel 16, so that it is moved into the relief position and the lamella 9a into the open position.
  • the special feature of the relief system 8b of the high pressure stage 3 shown in Figure 4 is the design of the lamella 9b, which is designed to be spring-stiff so that it can only be moved into the open position with the help of the relief piston 10b
  • a suction stroke of the piston 20b of the high pressure stage 2 does not have an automatic effect Movement of the lamella 9b in the open position.
  • Both relief pistons 10a, b are simultaneously acted upon with compressed air via the control pressure channel 16 shown.
  • the piston 20b also has a recess in which the lamella 9b has space in the open position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un compresseur à piston pour un système d'alimentation en air comprimé dans un véhicule automobile, comprenant une culasse dans laquelle est intégré un système de détente au moyen duquel un conduit de détente, dans une plaque de support de soupape de la culasse qui relie une chambre de travail du compresseur à piston à une chambre de la culasse, peut être commuté. Pour améliorer l'efficacité du compresseur à piston, selon l'invention, le système de détente comprend un dispositif de commutation et une lamelle, la lamelle étant fixée du côté de la chambre de travail à la plaque de support de soupape et étant conçue de telle sorte que celle-ci puisse être soulevée de la plaque de support de soupape pour ouvrir le conduit de détente, le soulèvement de la lamelle pouvant s'effectuer automatiquement et/ou de manière commandée au moyen du système de détente.
EP20743992.8A 2019-07-24 2020-07-16 Dispositif de soupape pour un compresseur à piston Pending EP4004370A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019119944.1A DE102019119944A1 (de) 2019-07-24 2019-07-24 Ventilvorrichtung für einen Hubkolbenverdichter
PCT/EP2020/070084 WO2021013670A1 (fr) 2019-07-24 2020-07-16 Dispositif de soupape pour un compresseur à piston

Publications (1)

Publication Number Publication Date
EP4004370A1 true EP4004370A1 (fr) 2022-06-01

Family

ID=71741774

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20743992.8A Pending EP4004370A1 (fr) 2019-07-24 2020-07-16 Dispositif de soupape pour un compresseur à piston

Country Status (5)

Country Link
EP (1) EP4004370A1 (fr)
JP (1) JP2022542871A (fr)
CN (1) CN114270037A (fr)
DE (1) DE102019119944A1 (fr)
WO (1) WO2021013670A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115977930A (zh) * 2023-02-28 2023-04-18 采埃孚商用车系统(青岛)有限公司 卸荷装置和空气压缩机

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246932A (en) * 1939-09-21 1941-06-24 Chicago Pneumatic Tool Co Combination single and two stage vacuum pump
US4382749A (en) * 1980-11-14 1983-05-10 The Trane Company Reciprocating compressor with integral unloader valve
DE3214713A1 (de) * 1982-04-21 1983-10-27 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Einrichtung zur erzeugung von druckgas
JP2509785Y2 (ja) * 1989-12-22 1996-09-04 三輪精機株式会社 エアコンプレッサ
JPH0557380U (ja) * 1991-12-27 1993-07-30 マックス株式会社 多段圧縮機の負荷軽減装置
JPH062667A (ja) * 1992-06-19 1994-01-11 Tokico Ltd 空気圧縮機のアンロード装置
BR9304028A (pt) * 1993-10-18 1995-06-06 Freios Varga Sa Dispositivo descarregador para compressor governado de sistema de freios a ar para veículos automotores
JPH1030565A (ja) * 1996-07-11 1998-02-03 Tokico Ltd 往復動型圧縮機
DE19850269A1 (de) * 1998-10-31 2000-05-04 Wabco Gmbh & Co Ohg Gasverdichter
WO2003083304A1 (fr) * 2002-03-29 2003-10-09 Devilbiss Air Power Company Assemblage limiteur de pression de tete
US7270145B2 (en) * 2002-08-30 2007-09-18 Haldex Brake Corporation unloading/venting valve having integrated therewith a high-pressure protection valve
DE502005002636D1 (de) * 2004-10-19 2008-03-13 Voith Patent Gmbh Mehrstufiger Kolbenverdichter mit reduzierter Leistungsaufnahme im Leerlauf
DE102013001147A1 (de) * 2013-01-24 2014-07-24 Voith Patent Gmbh Mehrstufiger Kolbenverdichter
CN103267004B (zh) * 2013-05-17 2015-08-19 台州中际汽车零部件有限公司 安保型汽车空压机
DE102016006358A1 (de) * 2016-05-21 2017-11-23 Wabco Gmbh Hubkolbenkompressor einer Druckluftversorgungsanlage

Also Published As

Publication number Publication date
CN114270037A (zh) 2022-04-01
WO2021013670A1 (fr) 2021-01-28
DE102019119944A1 (de) 2021-01-28
JP2022542871A (ja) 2022-10-07

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