EP2984347B1 - Device for conserving power in a piston compressor - Google Patents
Device for conserving power in a piston compressor Download PDFInfo
- Publication number
- EP2984347B1 EP2984347B1 EP14715843.0A EP14715843A EP2984347B1 EP 2984347 B1 EP2984347 B1 EP 2984347B1 EP 14715843 A EP14715843 A EP 14715843A EP 2984347 B1 EP2984347 B1 EP 2984347B1
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- EP
- European Patent Office
- Prior art keywords
- suction
- valve
- pressure
- cylinder head
- lamella
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0003—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber
- F04B7/0007—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber and having a rotating movement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0042—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member
- F04B7/0046—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member for rotating distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/08—Actuation of distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0057—Mechanical driving means therefor, e.g. cams
- F04B7/0061—Mechanical driving means therefor, e.g. cams for a rotating member
Definitions
- the invention relates to a device for power saving in a reciprocating compressor, in particular for compressed air generation in a motor vehicle, with a piston arranged axially movable in a cylinder for generating compressed air, which passes through at least one intake valve for compressing into a compression chamber of the cylinder, wherein the intake valve with pressure-controlled means for power saving cooperates.
- the field of application of the invention extends primarily to reciprocating compressors for motor vehicle construction, in particular commercial vehicle construction, which are primarily used for generating compressed air for compressed air systems in the motor vehicle.
- the pressure valve opens at the top of the valve plate as before at a certain pressure level. Compressed air enters the pressure regulator from the pressure chamber where it is blown off to the atmosphere via a relief valve.
- the lubricating oil present in the crankcase has an increased tendency to creep upwardly along the piston rings due to the reduced pressure level in the compression space, so that the lubricating oil can eventually enter the compression space and contribute to an increased accumulation in the air with lubricating oil , With prolonged operation at high temperatures, consequently, increased carbon accumulation is to be accepted.
- the suction valve has a serving to hold open the same actuating mechanism.
- This is a plunger which acts on the suction valve and carries a piston which can be acted upon by the pressure of the pressure vessel connected to the compressor, such that the plunger is displaced through the piston when a pressure threshold is exceeded and the suction valve is accordingly opened.
- a check valve is provided in the suction line thereof, which opens when a negative pressure in the suction line, to suck air into the reciprocating compressor.
- the pressure valve of the reciprocating compressor is unaffected by the operation of the suction valve, which is constantly in the ready state, so that even in idle position of the suction valve always a certain compression work is done.
- the pressure valve opens at a certain pressure level, thereby performing compressor work.
- pressure levels in the compression chamber is also in constructions of this kind the Problem that the lubricating oil along the piston rings can go up, ie in the compression space and thus enriching the air with lubricating oil is given.
- due to the non-return valve throttle losses which adversely affect the efficiency of the compressor.
- the object of the present invention is to provide a device for power saving in a reciprocating compressor with which as complete as possible power savings is achieved in the shutdown or idling phase, and that unnecessarily reach lubricating oil from the crankcase in the compression chamber and there An oil enrichment of the air in the suction line can contribute.
- the invention includes the technical teaching that the actuating means the suction plate of the valve plate so coordinated actuated that it at least partially closes the at least one pressure valve opening in the valve plate or a comparable component in the idle position and simultaneously releases adjacent Saugventilquer4.000e and the suction port on the cylinder head cover or a shut off comparable component by means of a slider or the like to form an increased harmful space in the region of the cylinder head.
- the suction blade can be moved as a sliding or rotary blade by means of the actuating means under control of a pressure regulator or otherwise provided control signal from its working position to the idle position, in which the at least one suction port is either partially or completely exposed, such that the in the air sucked in the compression chamber can flow back into the suction chamber.
- the achievable power savings is on the order of about 60%.
- the solution according to the invention ensures that no unnecessary volume of air is displaced on the pressure side of the compressor. It is also prevented in particular in parallel to the suction line of the reciprocating compressor turbochargers or compressors that occur in these by sucking air laden with lubricating oil under the action of high temperatures coking. Furthermore, the efficiency of the compressor in the delivery phase is not adversely affected by the inventive solution, so it throttle losses are avoided.
- the suction lamella is designed so that it works without friction. As a result, no wear between the suction plate and the valve plate occurs even with very little lubricating oil in the compression chamber. This design is therefore particularly suitable for oil-reduced compressors as well as for oil-free compressor types.
- the suction plate is formed so that in the idle phase, the pressure openings are completely or partially closed as needed. An unnecessary displacement of a volume fraction of air in the pressure chamber therefore does not take place. Only if a certain amount of residual air to avoid icing or contamination is desired, a partial opening of the pressure openings in the valve plate is set. In addition, by closing the suction port creates a certain back pressure in the compression chamber, which helps that the lubricating oil is retained from the crankcase. The partial or complete covering of the suction openings thus contributes to a further optimization in the achievable power saving.
- the actuating means which are preferably pneumatically actuated for adjusting the suction lamella and the slide, act in a preferred embodiment of the invention substantially parallel to the plane of the valve plate and have an actuating piston which can be acted upon by a control pressure.
- the actuating piston can be guided in a bore of the cylinder head cover, which can be formed by casting in the cylinder head cover.
- the actuating piston acts by means of a driving pin extending through the bore, both on an actuating member rotating the suction lamella between the working and idle position and on the slide closing the suction connection.
- the closing the suction port in the cylinder head cover slide is designed according to a preferred embodiment as a hinged thereto pivoting slide and lies within the cylinder head cover.
- the slider is furthermore preferably provided with a minimum air valve in the region closing off the suction connection.
- the minimum air valve acting as a check valve is a lamellar valve which consists of a minimum air valve catcher with a valve lamella cooperating therewith as a breakthrough on one end side of the pusher.
- the plurality of suction openings formed in the valve plate are arranged in a circular ring and can be closed with a disk-shaped as a rotary blade with openings and recesses formed suction lamella.
- a plurality formed in the valve plate pressure valve cross-sections can be arranged in an annular shape, which open inside the cylinder cover in a pressure chamber with connection to the pressure line, which are alternately closed with the disc-shaped suction plate.
- These pressure valve cross-sections interact with a pressure-valve unit arranged inside the cylinder head, preferably consisting of pressure-valve catch, pressure-valve spring and pressure-valve lamella.
- a piston compressor for producing compressed air essentially consists of a piston 100, which is articulated to a driven crankshaft 300 via a connecting rod 200.
- the crankshaft 300 is rotatably mounted in a crankcase 400.
- the crankcase 400 includes a cylinder which together with the piston 100 forms a compression space 500, which is provided on the front side with a cylinder head 600, which is shown here only schematically, with a power saving device integrated therein.
- the cylinder head 600 comprises a slide 7 which functions as a 2/2-way valve and activates a suction connection 1 of the reciprocating compressor with integrated minimum air valve 8.
- the ambient air sucked in via the suction connection 1 passes via the slide 7 within the cylinder head 600 into a dead space formed therein and switchable Serving suction chamber 18.
- Direction of compression chamber 500, the suction chamber 18 opens in the cylinder head 600 via a - not shown - valve plate in trained suction openings. 3
- the suction openings 3 are controlled via a 2/2-Wegeventilbesclien designed as a suction plate 4 to prevent in the valve position shown, which corresponds to the working position of the compressor via a check valve function, a return flow of compressed air into the suction chamber 18 and the generated compressed air over at least a likewise formed in the valve plate pressure bore 5 with downstream pressure valve unit 9 eject.
- a voltage applied to the actuating means for the device for power saving control pressure S - as shown here - the mechanism is pressed by the spring force of a return spring 12 in the working position.
- the control pressure S is applied, the pressure bores 5 are at least partially closed and the suction openings 3 are opened - in the other switching position of the suction lamella 4, not shown here.
- the piston 100 then only compresses into the now closed suction chamber 18.
- the minimum air valve 8 of the slide 7 also serves to ensure a reduced flow rate in the case of a blocked in the closed position mechanism and thus constitutes a safety function.
- the cylinder head 600 in the outer view essentially consists of a valve plate 2, on which an intermediate plate 20 is placed for extended placement of the device for power saving, which is followed by a cylinder head cover 21.
- a valve plate 2 on which an intermediate plate 20 is placed for extended placement of the device for power saving, which is followed by a cylinder head cover 21.
- the cylinder head cover 21 there is disposed an opening for supplying the control pressure S for the power saving device to be accommodated inside the cylinder head 600.
- the disc-shaped designed as a rotary blade suction plate 4 is arranged at the bottom of the valve plate 2.
- the Sauglamelle 4 is here in the working position, wherein - in accordance with FIG. 1 - Which are arranged annularly arranged in the valve plate 2 introduced pressure holes 5, while here - not recognizable - covered by the suction plate 4 and also annularly arranged in the valve plate 2 suction ports 3 are covered.
- FIG. 3 11 illustrates, in contrast to the external view described above, a partial sectional bottom view of the power saving device with omission of the intermediate plate 20 and cylinder head cover 21, showing in detail the actuating means for the power saving device in the working position.
- the pneumatically actuated actuating means comprise a parallel to the plane of the valve plate 2 guided and acted upon by the control pressure S actuating piston 11.
- the actuating means are in the control pressure-less Starting position.
- a coupled to the actuating piston 11 driving pin 17 acts via a rotary lever 10 with a rotary lever axis 14 for actuation on the suction plate 4, to switch them between working and idle position.
- the driving pin 17 of the actuating piston 11 actuates the slide 7 serving to actuate the suction port 1 (not shown), which is articulated via a pivot bearing 13 and designed as a pivoting slide.
- the slide 7 is provided in the region closing off the suction connection 1 with a minimum air valve 8a, 8b.
- the suction lamella 4 closes the suction openings 3 formed in the valve plate, while at the same time adjacent pressure valve cross sections 5 are released via openings 6 in the suction lamella 4.
- the pressure valve cross sections 5 cooperate with a pressure valve unit 9a-9c, which form a check valve to the delivery side.
- FIG. 4 is a top view of the in the FIG. 3 shown mechanism, the above in connection with the FIG. 3 used reference numerals apply using the above detailed description. Illustrated by way of illustration here is the functional position of the actuating means of the device for power saving. In addition, it can be seen that the slide 7 is provided at the end, which is not shown here - the suction connection 1, with a minimum air intake opening 15 of the minimum air valve 8 (not shown here).
- the device for power saving using the component designation according to the preceding detailed description is shown in the working position.
- the attached to the valve plate 2 suction plate 4 covers the introduced into the valve plate 2 suction ports 3 and the adjacent pressure valve cross sections 5 of the valve plate 2 are opened via the openings 6 in the suction plate 4.
- the suction port 1 is not in - further illustrated - cylinder head because of the pivoted away therefrom slide 7 in the open position.
- This working position is achieved in the control-pressure-free state of the actuating piston 11, which is pressed by a return spring 12 in the starting position.
- the actuating piston 11 is tax-pressurized, so that the device for power saving is in the neutral position.
- the suction openings 3 of the valve plate 2 are opened by recesses 16 of the suction plate 4, whereas the pressure valve cross-sections 5 are closed, since they are not in accordance with the corresponding openings 6 in the suction plate 4.
- the suction port 1 in the cylinder head (not shown here) is closed by the end of the slide 7, so that air can only flow via the minimum air valve 8 through the minimum air intake 15 into the suction chamber 18 (not shown here).
- FIG. 7 is a sectional view of line VV FIG. 6 and illustrates the device for power saving in neutral position.
- the actuating piston 11 of the actuating means for the power-saving device in a corresponding bore 22 in the cylinder head cover 21 is guided to form a piston-cylinder unit, which is acted upon by the control pressure.
- the driving pin 17 arranged on the outer circumference of the actuating piston 11 extends through an oblong hole-shaped recess in the cylinder head cover 21 into the slide 7 designed as a pivoting lever.
- the pressure valve unit cooperating with the pressure valve cross sections 5 in the valve plate 2 consists of a pressure valve catch 9a, a pressure valve spring 9b and a pressure valve cam 9c, which is arranged here in the region of the intermediate plate 20 of the cylinder head.
- FIG. 8 is a sectional view of line IV-IV in FIG. 4 and illustrates the device for power saving in the working position. Incidentally, the above detailed description also applies here with regard to the reference numbers used.
- FIG. 9 shows a two-cylinder construction of a reciprocating compressor, in which the same suction space is used by both cylinders.
- the slider 7 ' is present only once, since there is only one suction port 1 in this embodiment.
- Each compression chamber 500 and 500a is associated with its own rotatable suction plate 4 and 4a.
- the idle phase then pushes a piston 100, the air via the suction chamber 18 in the other compression chamber 500a at 180 ° stroke displacement at this moment just a downwardly moving piston 100a has, so sucks.
- the cylinder pressure on the size of the approved Saugkanalqueritese interpret so that enough back pressure to avoid oil leakage remains.
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Description
Die Erfindung betrifft eine Einrichtung zur Leistungseinsparung bei einem Kolbenverdichter, insbesondere zur Drucklufterzeugung bei einem Kraftfahrzeug, mit einem in einem Zylinder axial bewegbar angeordneten Kolben zur Erzeugung von Druckluft, die über mindestens ein Ansaugventil zum Komprimieren in einen Verdichtungsraum des Zylinders gelangt, wobei das Ansaugventil mit druckgesteuerten Mitteln zur Leistungseinsparung zusammenwirkt.The invention relates to a device for power saving in a reciprocating compressor, in particular for compressed air generation in a motor vehicle, with a piston arranged axially movable in a cylinder for generating compressed air, which passes through at least one intake valve for compressing into a compression chamber of the cylinder, wherein the intake valve with pressure-controlled means for power saving cooperates.
Das Einsatzgebiet der Erfindung erstreckt sich vornehmlich auf Hubkolbenkompressoren für den Kraftfahrzeugbau, insbesondere Nutzfahrzeugbau, welche vornehmlich zur Erzeugung von Druckluft für Druckluftanlagen im Kraftfahrzeug verwendet werden.The field of application of the invention extends primarily to reciprocating compressors for motor vehicle construction, in particular commercial vehicle construction, which are primarily used for generating compressed air for compressed air systems in the motor vehicle.
Zur Regelung der Fördermenge derartiger Kolbenverdichter sowie zur Regelung des Drucks in nachgeschalteten Verbrauchern, beispielsweise einer Bremsanlage, sind Einrichtungen zur Leistungseinsparung allgemein bekannt. Diese stoßen das Ansaugventil des Kolbenverdichters auf, wenn ein vorbestimmter Druck erreicht ist und dieser als Steuerdruck auf ein mechanisches Betätigungselement für das Aufstoßen des Ansaugventils einwirkt. Derartige Einrichtungen sind als sogenannte "Governor" Einrichtungen allgemein bekannt.To control the flow rate of such reciprocating compressors and to regulate the pressure in downstream consumers, such as a brake system, devices for power saving are well known. These encounter the intake valve of the reciprocating compressor when a predetermined pressure is reached and this acts as a control pressure on a mechanical actuator for the regurgitation of the intake valve. Such devices are well known as so-called "governor" devices.
Aus der
Dies bedeutet also, dass ein Anteil der während des Saugtaktes angesaugten Luft den Zylinderraum durch die Saugöffnungen verlässt, während ein nach wie vor bestehender Anteil der Luft durch die Drucköffnungen ausgeschoben wird.This means that a portion of the air sucked in during the suction cycle leaves the cylinder space through the suction openings, while a still existing proportion of the air is pushed out through the pressure openings.
Während dieses Betriebszustandes besitzt das sich im Kurbelgehäuse befindliche Schmieröl die verstärkte Neigung, in Folge des reduzierten Druckniveaus im Verdichtungsraum entlang der Kolbenringe nach oben zu kriechen, so dass das Schmieröl schließlich in den Verdichtungsraum gelangen kann und zu einer erhöhten Anreicherung in der Luft mit Schmieröl beiträgt. Bei längerem Betrieb mit hohen Temperaturen ist folglich erhöhter Kohleanfall in Kauf zu nehmen.During this operating condition, the lubricating oil present in the crankcase has an increased tendency to creep upwardly along the piston rings due to the reduced pressure level in the compression space, so that the lubricating oil can eventually enter the compression space and contribute to an increased accumulation in the air with lubricating oil , With prolonged operation at high temperatures, consequently, increased carbon accumulation is to be accepted.
Bei geöffnetem Saugventil, also bei sich im Leerlaufstellung befindlicher Sauglamelle, wird bei weiterlaufendem Betrieb für den Kolbenverdichter nach wie vor Saugarbeit verrichtet, es wird also Luft über die Saugleitung, den geöffneten Sauganschluss und das in Leerlaufstellung befindliche Saugventil in den Verdichtungsraum des Verdichters angesaugt und wird wenigstens teilweise in die Saugleitung wieder zurückgeschoben, wenn der Kolben des Verdichters Verdichtungsarbeit leistet. Die in den Verdichtungsraum angesaugte Luft ist mit Ölpartikeln befrachtet, welche in Folge des reduzierten Druckniveaus im Zylinderraum entlang der Kolbenringe in Richtung des Verdichtersraums kriechen. Diese mit Ölpartikeln befrachtete Luft wird durch die Saugleitung wenigsten teilweise wieder ausgeschoben, das Schmieröl wird kumuliert und tritt dann später schwallartig beim Umschalten auf den Förderbetrieb in die Druckleitung über.When the intake valve is open, that is, in the idling position located Sauglamelle, continues to perform Saugarbeit during ongoing operation for the reciprocating compressor, so it is sucked air via the suction line, the open suction port and the suction valve located in neutral position in the compression chamber of the compressor and is at least partially in the Suction line pushed back again when the piston of the compressor performs compression work. The air drawn into the compression chamber is laden with oil particles which creep in the direction of the compressor chamber as a result of the reduced pressure level in the cylinder chamber along the piston rings. This fraught with oil particles air is at least partially pushed out again by the suction line, the lubricating oil is cumulative and then occurs later like a surge when switching to the conveying operation in the pressure line over.
Sollte an die Saugleitung parallel zum Kolbenverdichter ein Turbolader angeschlossen sein, welcher durch seine Saugwirkung einen gewissen Unterdruck innerhalb der Saugleitung erzeugt, dann besteht außerdem die Gefahr, dass die Ölpartikel der in der Saugleitung befindlichen Luft in den Turbolader gelangen und dort zu starken Verkokungen beitragen. Derartige Verkokungen sind natürlich in hohem Maße unerwünscht.If a turbocharger connected to the suction line parallel to the reciprocating compressor, which generates a certain negative pressure within the suction line by its suction, then there is also the danger that the oil particles of the air located in the suction line enter the turbocharger and contribute there to strong coking. Of course, such coking is highly undesirable.
In der
Die Aufgabe wird ausgehend von einer Einrichtung gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of a device according to the preamble of
Die Erfindung schließt die technische Lehre ein, dass die Betätigungsmittel die Sauglamelle der Ventilplatte derart koordiniert betätigten, dass diese in der Leerlaufstellung die mindestens eine Druckventilöffnung in der Ventilplatte oder einem vergleichbaren Bauteil zumindest teilweise verschließt und gleichzeitig benachbarte Saugventilquerschnitte freigibt sowie den Sauganschluss am Zylinderkopfdeckel oder einem vergleichbaren Bauteil mittels eines Schiebers oder dergleichen absperrt, um einen erhöhten schädlichen Raum im Bereich des Zylinderkopfes zu bilden.The invention includes the technical teaching that the actuating means the suction plate of the valve plate so coordinated actuated that it at least partially closes the at least one pressure valve opening in the valve plate or a comparable component in the idle position and simultaneously releases adjacent Saugventilquerschnitte and the suction port on the cylinder head cover or a shut off comparable component by means of a slider or the like to form an increased harmful space in the region of the cylinder head.
Durch die in Leerlaufstellung sich vollziehende Verstellung der Sauglamelle in die geöffnete Lage und durch die sich gleichzeitig vollziehende, wenigstens teilweise Schließung des Sauganschlusses am Zylinderkopfdeckel mittels des Schiebers innerhalb des Zylinderkopfes wird eine Optimierung der Leistungseinsparung erreicht. In der Leerlaufphase wird durch die verstellbare Sauglamelle in Verbindung mit dem Schieber sichergestellt, dass die Saugleitung und ggf. an die Saugleitung angeschlossene Filter und Kompressoranlagen unbeeinflusst bleiben vom weiteren Leerlauf des Kolbens. Durch die gleichzeitige, wenigstens teilweise vollzogene Schließung des mindestens einen Druckventilquerschnittes des Kolbenverdichters wird außerdem erreicht, dass kein unnötiges Abblasen von Luft stattfindet. Als Folge davon ist es nur erforderlich, ein den Leckageverlusten entsprechendes geringes Volumen über ein vorzugsweise am Schieber befindliches Rückschlagventil anzusaugen, wenn der Kolben des Verdichters in Leerlaufstellung der Sauglamelle eine Saugbewegung vollzieht. Bei vollständig geschlossenen Drucköffnungen des Verdichters reduziert sich die zusätzlich anzusaugende Luftmenge aus der Saugleitung auf das tatsächlich existierende Leckagevolumen auch blow-by genannt, im Verdichtungsraum des Zylinders.By performing in idle position adjustment of the suction lamella in the open position and by the simultaneously executing, at least partially closing the suction port on the cylinder head cover by means of the slide within the cylinder head optimization of the power saving is achieved. In the idling phase is through the adjustable suction plate in combination ensured with the slide that the suction line and possibly connected to the suction line filter and compressor systems are unaffected by the further idling of the piston. Due to the simultaneous, at least partially completed closure of the at least one pressure valve cross-section of the reciprocating compressor is also achieved that no unnecessary blowing off of air takes place. As a result, it is only necessary to suck a small volume corresponding to the leakage losses via a check valve, which is preferably located on the slide, when the piston of the compressor performs a suction movement in the idling position of the suction lamella. When the pressure openings of the compressor are completely closed, the additional amount of air to be sucked in from the suction line is reduced to the actually existing leakage volume, also called blow-by, in the compression chamber of the cylinder.
Die Sauglamelle kann als eine Schiebe- oder Drehlamelle mit Hilfe der Betätigungsmittel unter Steuerung durch einen Druckregler oder ein anderweitig bereitgestelltes Steuersignal aus ihrer Arbeitsstellung in die Leerlaufstellung verschoben werden, in welcher die mindestens eine Saugöffnung entweder teilweise oder vollständig freigelegt wird, derart, dass die in den Verdichtungsraum angesaugte Luft wieder in den Saugraum zurückströmen kann. Die hierdurch erzielbare Leistungseinsparung liegt in der Größenordnung von etwa 60%.The suction blade can be moved as a sliding or rotary blade by means of the actuating means under control of a pressure regulator or otherwise provided control signal from its working position to the idle position, in which the at least one suction port is either partially or completely exposed, such that the in the air sucked in the compression chamber can flow back into the suction chamber. The achievable power savings is on the order of about 60%.
Die erfindungsgemäße Lösung stellt sicher, dass auf der Druckseite des Verdichters kein unnötiges Luftvolumen verschoben wird. Es wird auch insbesondere bei an der Saugleitung des Kolbenverdichters parallel angeschlossenen Turboladern oder Kompressoren verhindert, dass bei diesen durch Ansaugen von mit Schmieröl befrachteter Luft unter Einwirkung hoher Temperaturen Verkokungen auftreten. Des Weiteren wird durch die erfindungsgemäße Lösung die Effizienz des Verdichters in der Förderphase nicht nachteilig beeinflusst, es werden also Drosselverluste vermieden.The solution according to the invention ensures that no unnecessary volume of air is displaced on the pressure side of the compressor. It is also prevented in particular in parallel to the suction line of the reciprocating compressor turbochargers or compressors that occur in these by sucking air laden with lubricating oil under the action of high temperatures coking. Furthermore, the efficiency of the compressor in the delivery phase is not adversely affected by the inventive solution, so it throttle losses are avoided.
Die Sauglamelle ist so konstruiert, dass diese reibungsfrei arbeitet. Dadurch tritt auch bei sehr wenig Schmieröl im Verdichtungsraum kein Verschleiß zwischen Sauglamelle und Ventilplatte auf. Dieses Design eignet sich damit besonders für im Ölauswurf reduzierte Verdichter als auch für ölfreie Verdichtertypen.The suction lamella is designed so that it works without friction. As a result, no wear between the suction plate and the valve plate occurs even with very little lubricating oil in the compression chamber. This design is therefore particularly suitable for oil-reduced compressors as well as for oil-free compressor types.
In vorteilhafter Weise ist die Sauglamelle so ausgebildet, dass in der Leerlaufphase die Drucköffnungen je nach Bedarf ganz oder teilweise verschlossen werden. Ein unnötiges Verschieben eines Volumenanteils von Luft in den Druckraum findet folglich nicht statt. Nur wenn eine gewisse Restluftförderung zur Vermeidung von Vereisung oder Verschmutzung erwünscht ist, wird eine Teilöffnung der Drucköffnungen in der Ventilplatte eingestellt. Außerdem entsteht durch das Verschließen des Sauganschlusses ein gewisser Staudruck im Verdichtungsraum, welcher dazu beiträgt, dass das Schmieröl aus dem Kurbelgehäuse zurückgehalten wird. Das teilweise oder vollständige Abdecken der Saugöffnungen trägt somit zu einer weiteren Optimierung in der erzielbaren Leistungseinsparung bei.Advantageously, the suction plate is formed so that in the idle phase, the pressure openings are completely or partially closed as needed. An unnecessary displacement of a volume fraction of air in the pressure chamber therefore does not take place. Only if a certain amount of residual air to avoid icing or contamination is desired, a partial opening of the pressure openings in the valve plate is set. In addition, by closing the suction port creates a certain back pressure in the compression chamber, which helps that the lubricating oil is retained from the crankcase. The partial or complete covering of the suction openings thus contributes to a further optimization in the achievable power saving.
Die zur Verstellung der Sauglamelle sowie des Schiebers vorzugsweise pneumatisch angesteuerten Betätigungsmittel wirken bei einer bevorzugten Ausführungsform der Erfindung im Wesentlichen parallel zur Ebene der Ventilplatte und weisen einen mit einem Steuerdruck beaufschlagbaren Betätigungskolben auf. Der Betätigungskolben kann dabei in einer Bohrung des Zylinderkopfdeckels geführt sein, welche gießtechnisch im Zylinderkopfdeckel ausgebildet werden kann.The actuating means, which are preferably pneumatically actuated for adjusting the suction lamella and the slide, act in a preferred embodiment of the invention substantially parallel to the plane of the valve plate and have an actuating piston which can be acted upon by a control pressure. The actuating piston can be guided in a bore of the cylinder head cover, which can be formed by casting in the cylinder head cover.
Vorzugsweise wirkt der Betätigungskolben mittels eines durch die Bohrung sich erstreckenden Mitnahmestiftes sowohl auf ein die Sauglamelle zwischen Arbeits- und Leerlaufstellung verdrehendes Betätigungsorgan als auch auf den Sauganschluss verschließenden Schieber ein.Preferably, the actuating piston acts by means of a driving pin extending through the bore, both on an actuating member rotating the suction lamella between the working and idle position and on the slide closing the suction connection.
Der den Sauganschluss im Zylinderkopfdeckel verschließende Schieber ist gemäß einer bevorzugten Ausführungsform als ein hieran angelenkter Schwenkschieber ausgebildet und liegt innerhalb des Zylinderkopfdeckels.The closing the suction port in the cylinder head cover slide is designed according to a preferred embodiment as a hinged thereto pivoting slide and lies within the cylinder head cover.
Der Schieber ist weiterhin vorzugsweise in dem den Sauganschluss verschließenden Bereich mit einem Mindestluftventil versehen. Gemäß einer bevorzugten Ausführungsform ist das als Rückschlagventil wirkende Mindestluftventil ein Lamellenventil, welches aus einem endseits des Schiebers als Durchbruch ausgebildeten Mindestluftventilfänger mit hiermit zusammenwirkender Ventillamelle besteht.The slider is furthermore preferably provided with a minimum air valve in the region closing off the suction connection. According to a preferred embodiment, the minimum air valve acting as a check valve is a lamellar valve which consists of a minimum air valve catcher with a valve lamella cooperating therewith as a breakthrough on one end side of the pusher.
Gemäß einer bevorzugten Ausführungsform der Erfindung sind die mehreren in der Ventilplatte ausgebildeten Saugöffnungen kreisringförmig angeordnet und mit einer scheibenförmig als Drehlamelle mit Durchbrüchen und Ausnehmungen ausgebildeten Sauglamelle verschließbar. Außerdem können mehrere in der Ventilplatte ausgebildete Druckventilquerschnitte kreisringförmig angeordnet werden, die innerhalb des Zylinderdeckels in einen Druckraum mit Verbindung zur Druckleitung münden, welche abwechselnd mit der scheibenförmigen Sauglamelle verschließbar sind. Diese Druckventilquerschnitte wirken mit einer innerhalb des Zylinderkopfes förderleitungsseitig angeordneten Druckventileinheit, vorzugsweise bestehend aus Druckventilfänger, Druckventilfeder und Druckventillamelle zusammen.According to a preferred embodiment of the invention, the plurality of suction openings formed in the valve plate are arranged in a circular ring and can be closed with a disk-shaped as a rotary blade with openings and recesses formed suction lamella. In addition, a plurality formed in the valve plate pressure valve cross-sections can be arranged in an annular shape, which open inside the cylinder cover in a pressure chamber with connection to the pressure line, which are alternately closed with the disc-shaped suction plate. These pressure valve cross-sections interact with a pressure-valve unit arranged inside the cylinder head, preferably consisting of pressure-valve catch, pressure-valve spring and pressure-valve lamella.
Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:
Figur 1- eine schematische Darstellung eines Kolbenverdichters mit hiermit zusammenwirkender Einrichtung zur Leistungseinsparung,
Figur 2- eine perspektivische Ansicht eines aus Ventilplatte und Zylinderkopfdeckel bestehenden Zylinderkopfes des Kolbenverdichters mit integrierter Einrichtung zur Leistungseinsparung,
Figur 3- eine perspektivische Ansicht von mit der Ventilplatte (geschnitten dargestellt) zusammenwirkenden Betätigungsmitteln der Einrichtung zur Leistungseinsparung (von unten),
Figur 4- eine perspektivische Ansicht von mit der Ventilplatte (geschnitten dargestellt) zusammenwirkenden Betätigungsmitteln der Einrichtung zur Leistungseinsparung (von oben),
Figur 5- eine Draufsicht auf die Ventilplatte mit Betätigungsmitteln für die Einrichtung zur Leistungseinsparung in Arbeitsstellung,
Figur 6- eine Draufsicht auf die Ventilplatte mit Betätigungsmitteln für die Einrichtung zur Leistungseinsparung in Leerlaufstellung,
Figur 7- eine Schnittdarstellung von Linie
V-V gemäß Figur 6 mit Darstellung von sich innerhalb des Zylinderkopfes befindlichen Betätigungsmitteln in der Leerlaufstellung, Figur 8- eine Schnittdarstellung von Linie IV-
IV gemäß Figur 5 mit Darstellung von sich innerhalb des Zylinderkopfes befindlichen Betätigungsmitteln in der Arbeitsstellung, und Figur 9- eine schematische Darstellung einer Zweizylinderbauweise eines Kolbenverdichters mit hiermit zusammenwirkender Einrichtung zur Leistungseinsparung.
- FIG. 1
- a schematic representation of a reciprocating compressor with hereby cooperating device for power saving,
- FIG. 2
- a perspective view of a valve plate and cylinder head cover existing cylinder head of the reciprocating compressor with integrated device for power saving,
- FIG. 3
- a perspective view of with the valve plate (shown in section) cooperating actuating means of the device for power saving (from below),
- FIG. 4
- a perspective view of with the valve plate (shown in section) cooperating actuating means of the device for power saving (from above),
- FIG. 5
- a top view of the valve plate with actuating means for the device for saving power in working position,
- FIG. 6
- a top view of the valve plate with actuating means for the device for power saving in neutral position,
- FIG. 7
- a sectional view of line VV according to
FIG. 6 with representation of actuating means located inside the cylinder head in the neutral position, - FIG. 8
- a sectional view of line IV-IV according to
FIG. 5 with representation of itself located within the cylinder head actuating means in the working position, and - FIG. 9
- a schematic representation of a two-cylinder design of a reciprocating compressor with hereby cooperating device for power saving.
Gemäß
Der Zylinderkopf 600 umfasst einen als 2/2-Wegeventil fungierenden und einen Sauganschluss 1 des Kolbenverdichters ansteuernden Schieber 7 mit integriertem Mindestluftventil 8. Die über den Sauganschluss 1 angesaugte Umgebungsluft gelangt über den Schieber 7 innerhalb des Zylinderkopfes 600 in eine hierin ausgebildete und als zuschaltbarer Schadraum dienende Ansaugkammer 18. Richtung Verdichtungsraum 500 mündet die Ansaugkammer 18 im Zylinderkopf 600 über eine - nicht weiter dargestellte - Ventilplatte in ausgebildete Saugöffnungen 3.The
Die Saugöffnungen 3 werden über eine als Sauglamelle 4 ausgebildete 2/2-Wegeventilbeschaltung angesteuert, um in der gezeigten Ventilstellung, welche der Arbeitsstellung des Verdichters entspricht, über eine Rückschlagventilfunktion ein Rückströmen von komprimierter Druckluft in die Ansaugkammer 18 zu verhindern und die erzeugte Druckluft über mindestens eine ebenfalls in der Ventilplatte ausgebildeten Druckbohrung 5 mit nachgeschalteter Druckventileinheit 9 auszustoßen. Konkret wird ohne einen an die Betätigungsmittel für die Einrichtung zur Leistungseinsparung anliegenden Steuerdruck S - wie hier dargestellt - der Mechanismus durch die Federkraft einer Rückstellfeder 12 in die Arbeitsstellung gedrückt. Bei anliegendem Steuerdruck S werden - in der hier nicht dargestellten anderen Schaltstellung der Sauglamelle 4 - die Druckbohrungen 5 zumindest teilweise verschlossen und die Saugöffnungen 3 geöffnet. Der Kolben 100 verdichtet dann nur noch in die jetzt abgeschlossene Ansaugkammer 18.The
Etwaige, beispielsweise am Kolben 100 vorbeilaufende Leckverluste werden durch die Rückschlagventilfunktion des Mindestluftventils 8 ausgeglichen. Das Mindestluftventil 8 des Schiebers 7 dient auch dazu, im Falle eines in Schließstellung blockierten Mechanismus eine reduzierte Fördermenge sicherzustellen und bildet insoweit eine Sicherheitsfunktion.Any, for example, the
Gemäß
An der Unterseite der Ventilplatte 2 ist die scheibenförmig als Drehlamelle ausgebildete Sauglamelle 4 angeordnet. Die Sauglamelle 4 befindet sich hier in der Arbeitsstellung, wobei - in Übereinstimmung mit
Die
Die pneumatisch angesteuerten Betätigungsmittel umfassen einen parallel zur Ebene der Ventilplatte 2 geführten und mit dem Steuerdruck S beaufschlagbaren Betätigungskolben 11. Die Betätigungsmittel befinden sich in der steuerdrucklosen Ausgangsposition. Hierbei wirkt ein mit dem Betätigungskolben 11 gekoppelter Mitnahmestift 17 über einen Drehhebel 10 mit einer Drehhebelachse 14 zur Betätigung auf die Sauglamelle 4, um diese zwischen Arbeits- und Leerlaufstellung zu schalten. Gleichzeitig betätigt der Mitnahmestift 17 des Betätigungskolbens 11 den zur Ansteuerung des - nicht weiter dargestellten - Sauganschlusses 1 dienenden Schieber 7, welcher über ein Drehlager 13 angelenkt als Schwenkschieber ausgebildet ist. Der Schieber 7 ist in dem den Sauganschluss 1 verschließenden Bereich mit einem Mindestluftventil 8a, 8b versehen.The pneumatically actuated actuating means comprise a parallel to the plane of the
In der dargestellten Arbeitsstellung verschließt die Sauglamelle 4 die in der Ventilplatte ausgebildeten Saugöffnungen 3, wogegen gleichzeitig benachbarte Druckventilquerschnitte 5 über Durchbrüche 6 in der Sauglamelle 4 freigegeben werden. Die Druckventilquerschnitte 5 wirken mit einer Druckventileinheit 9a-9c zusammen, welche ein Rückschlagventil zur Förderseite hin bilden.In the illustrated working position, the
Die
Gemäß
In der
Die
Über den Mitnahmestift 17 wird ferner der Drehhebel 10 betätigt, welcher über die Drehhebelachse 14 die Sauglamelle 4 betätigt. Die mit den Druckventilquerschnitten 5 in der Ventilplatte 2 zusammenwirkende Druckventileinheit besteht aus einem Druckventilfänger 9a, einer Druckventilfeder 9b sowie einer Druckventillamelle 9c, welche hier im Bereich der Zwischenplatte 20 des Zylinderkopfes angeordnet ist. Im Übrigen gilt hinsichtlich der restlichen Bezugszeichen die vorstehende Detailbeschreibung.About the driving
Die
Die
- 11
- Sauganschlusssuction
- 22
- Ventilplattevalve plate
- 33
- Saugöffnungsuction opening
- 44
- Sauglamellesuction plate
- 55
- DruckventilquerschnittPressure valve area
- 66
- Durchbruchbreakthrough
- 77
- Schieberpusher
- 88th
- MindestluftventilMinimum air valve
- 99
- DruckventileinheitPressure valve unit
- 1010
- Drehhebellever
- 1111
- Betätigungskolbenactuating piston
- 1212
- RückstellfederReturn spring
- 1313
- Drehlagerpivot bearing
- 1414
- DrehhebelachsePivot lever axis
- 1515
- MindestluftansaugöffnungMindestluftansaugöffnung
- 1616
- Ausnehmungrecess
- 1717
- Mitnahmestiftdriving pin
- 1818
- Ansaugkammersuction
- 1919
- Druckraum (Förderseite)Pressure chamber (delivery side)
- 2020
- Zwischenplatteintermediate plate
- 2121
- ZylinderkopfdeckelCylinder head cover
- 2222
- Bohrungdrilling
- 100100
- Kolbenpiston
- 200200
- Pleuelpleuel
- 300300
- Kurbelwellecrankshaft
- 400400
- Kurbelgehäusecrankcase
- 500500
- Verdichtungsraumcompression chamber
- 600600
- Zylinderkopfcylinder head
- SS
- Steuerdruckcontrol pressure
Claims (10)
- Device for conserving power in a piston compressor, in particular for generating compressed air in a motor vehicle, having a piston (100), which delimits a compression chamber (500), for generating compressed air, which, originating from the ambient environment, enters the compression chamber (500) for compression via at least one suction port (1) formed on a cylinder head cover (21) and via an intake valve array arranged on a valve plate (2), wherein, for the purpose of conserving power, a pressure-dependently acting idling device is provided for the intake valve array, which is provided with an associated suction lamella (4), wherein the suction lamella (4) can be rotated by actuating means between a working position overlapping at least one suction opening (3) and an idling position exposing, at least in part, the at least one suction opening (3), characterised in that the actuating means actuate the suction lamella (4) in a coordinated manner in such a way that, in the idling position, said lamella (4) exposes the at least one suction opening (3) in the valve plate (2) while simultaneously closing adjacent pressure valve cross-sections (5), at least partially, and blocks the suction port (1) on the cylinder head cover (21) by means of a slider (7) in order to form an increased dead space in the region of the cylinder head (600).
- Device according to claim 1,
characterised in that the pneumatically controlled actuating means have an actuating piston (11), which is guided substantially parallel to the plane of the valve plate (2) in the region of the cylinder head cover (21) and can be subjected to a control pressure. - Device according to claim 2,
characterised in that the actuating piston (11) is guided in a bore (22) in the cylinder head cover (21). - Device according to claim 2,
characterised in that the pneumatic actuating piston (11) that can be subjected to control pressure can be moved into an initial position free from control pressure, corresponding to the working position, by a return spring (12). - Device according to claims 2 and 3,
characterised in that the actuating piston (11) acts by means of a driver pin (17) coupled thereto on a rotary lever spindle (14), which rotates the suction lamella (4) between the working position and the idling position, and also on the slider (7), which closes the suction port (1). - Device according to claim 1,
characterised in that the slider (7), which closes the suction port (1), is designed as a pivoted slider attached to the cylinder head cover (21). - Device according to claim 1,
characterised in that the slider (7) is provided with a minimum air valve (8a, 8b) in the region that closes the suction port (1). - Device according to claim 7,
characterised in that the minimum air valve (8a, 8b), which is designed as a check valve, is a reed valve, which comprises a minimum air valve stop, formed as an aperture (8a) at the end of the slider, with a valve reed (8b) interacting therewith. - Device according to claim 1,
characterised in that a plurality of suction openings (3) formed in the valve plate (2) are arranged in a circular ring shape and interact with a suction lamella (4) designed as a disc-shaped rotary lamella having apertures (6) and openings (16). - Device according to claim 9,
characterised in that a plurality of pressure valve cross-sections (5) formed in the valve plate (2) are furthermore arranged in a circular ring shape and interact alternately with the disc-shaped suction lamella (4) in the manner of a valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102013006138.5A DE102013006138A1 (en) | 2013-04-10 | 2013-04-10 | Device for saving power in a reciprocating compressor |
PCT/EP2014/000908 WO2014166615A1 (en) | 2013-04-10 | 2014-04-04 | Device for conserving power in a piston compressor |
Publications (2)
Publication Number | Publication Date |
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EP2984347A1 EP2984347A1 (en) | 2016-02-17 |
EP2984347B1 true EP2984347B1 (en) | 2017-03-22 |
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ID=50442472
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Application Number | Title | Priority Date | Filing Date |
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EP14715843.0A Active EP2984347B1 (en) | 2013-04-10 | 2014-04-04 | Device for conserving power in a piston compressor |
Country Status (5)
Country | Link |
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US (1) | US10072653B2 (en) |
EP (1) | EP2984347B1 (en) |
CN (1) | CN105102817B (en) |
DE (1) | DE102013006138A1 (en) |
WO (1) | WO2014166615A1 (en) |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2139313A (en) * | 1938-03-14 | 1938-12-06 | York Ice Machinery Corp | Valve for compressors |
FR1098045A (en) | 1953-11-24 | 1955-07-15 | Regulation device for air or gas compressors | |
US3351271A (en) * | 1965-11-02 | 1967-11-07 | Worthington Corp | Unloading device for reciprocating compressors |
DE3329790C2 (en) | 1983-08-18 | 1995-11-30 | Wabco Gmbh | Valve carrier for piston compressors |
DE3642852A1 (en) * | 1986-12-16 | 1988-06-30 | Wabco Westinghouse Fahrzeug | DEVICE FOR TRANSFERRING A DRIVE FORCE BETWEEN TWO COMPONENTS |
DE3904172A1 (en) * | 1989-02-11 | 1990-08-16 | Wabco Westinghouse Fahrzeug | VALVE LAMPS |
DE4138664A1 (en) * | 1991-11-25 | 1993-05-27 | Knorr Bremse Ag | ENERGY-SAVING PISTON COMPRESSOR |
CN2109465U (en) * | 1991-12-20 | 1992-07-08 | 宋振龙 | Power saving device for car air compressor |
DE19529684C2 (en) * | 1995-08-11 | 1998-03-19 | Knorr Bremse Systeme | Piston compressors, in particular for the generation of compressed air in motor vehicles |
DE19739662A1 (en) | 1997-09-10 | 1999-03-11 | Bosch Gmbh Robert | Valve system for reciprocating compressor of braking system in commercial vehicle |
DE19848217B4 (en) | 1998-10-20 | 2013-06-27 | Wabco Gmbh | gas compressor |
CN201096070Y (en) * | 2007-08-07 | 2008-08-06 | 上海扎努西电气机械有限公司 | Cold compressor piston decreasing clearance volume |
CN201225264Y (en) * | 2008-05-06 | 2009-04-22 | 武汉理工大学 | Clearance stepless adjusting device of piston reciprocating compressor |
-
2013
- 2013-04-10 DE DE102013006138.5A patent/DE102013006138A1/en not_active Ceased
-
2014
- 2014-04-04 CN CN201480020383.7A patent/CN105102817B/en not_active Expired - Fee Related
- 2014-04-04 WO PCT/EP2014/000908 patent/WO2014166615A1/en active Application Filing
- 2014-04-04 EP EP14715843.0A patent/EP2984347B1/en active Active
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2015
- 2015-10-09 US US14/879,219 patent/US10072653B2/en active Active
Also Published As
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US10072653B2 (en) | 2018-09-11 |
CN105102817A (en) | 2015-11-25 |
WO2014166615A1 (en) | 2014-10-16 |
DE102013006138A1 (en) | 2014-10-16 |
EP2984347A1 (en) | 2016-02-17 |
CN105102817B (en) | 2017-02-22 |
US20160032917A1 (en) | 2016-02-04 |
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