EP1710435B1 - Refrigerant compressor - Google Patents
Refrigerant compressor Download PDFInfo
- Publication number
- EP1710435B1 EP1710435B1 EP06005929A EP06005929A EP1710435B1 EP 1710435 B1 EP1710435 B1 EP 1710435B1 EP 06005929 A EP06005929 A EP 06005929A EP 06005929 A EP06005929 A EP 06005929A EP 1710435 B1 EP1710435 B1 EP 1710435B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- switching
- refrigerant compressor
- compressor according
- valve
- cylinder
- 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.)
- Active
Links
- 239000003507 refrigerant Substances 0.000 title claims description 62
- 230000000694 effects Effects 0.000 claims description 2
- 230000003213 activating effect Effects 0.000 claims 2
- 239000000463 material Substances 0.000 claims 1
- 238000005057 refrigeration Methods 0.000 description 12
- 230000002349 favourable effect Effects 0.000 description 5
- 238000004146 energy storage Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000004035 construction material Substances 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000004033 plastic Substances 0.000 description 2
- 229920003023 plastic Polymers 0.000 description 2
- 229920002430 Fibre-reinforced plastic Polymers 0.000 description 1
- 206010037660 Pyrexia Diseases 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000011151 fibre-reinforced plastic Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000003562 lightweight material Substances 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/067—Control
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/24—Control not provided for in a single group of groups F04B27/02 - F04B27/22
-
- 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
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
-
- 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
- F04B2201/06—Valve parameters
- F04B2201/0601—Opening times
- F04B2201/06011—Opening times of the inlet valve only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2515—Flow valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2521—On-off valves controlled by pulse signals
Definitions
- the invention relates to a refrigerant compressor for refrigeration systems comprising at least one cylinder unit, which has a cylinder housing and a piston oscillatingly movable in the cylinder housing, a cylinder head, with an inlet chamber through which an inlet flow of the at least one cylinder unit passes and with one of an outlet flow of the at least one cylinder unit Outlet chamber, and a switching valve for interrupting the inlet flow.
- Such refrigerant compressors are from the US 2001/0011463 A1 known, with these there is the possibility with the switching valve to permanently switch off one or more cylinder units or permanently switch on.
- the invention is therefore based on the object to improve a refrigerant compressor of the generic type such that it can be operated in any part load ranges.
- a control is provided for driving the switching valve, which operates the switching valve in consecutive, each an opening interval and a closing interval of the switching valve comprehensive switching intervals for operation of the refrigerant compressor in a lower part load range, which are shorter than a shortest period of time after which a temperature of an evaporator in the working refrigeration system has increased by about 10% at an interruption of the intake flow.
- the advantage of the solution according to the invention is the fact that this opens up the possibility to operate a refrigerant compressor, in particular a reciprocating compressor in a lower part load range at any part load, as by the ratio of the opening intervals and the closing intervals within each switching interval of the mass flow to be compressed continuously and is arbitrarily adjustable.
- time periods are selected for the switching intervals, which are sufficiently short, so that due to the inertia of the reaction of the refrigeration system according to the invention to the switching intervals only insignificant temperature fluctuations in the evaporator of the refrigerators arise that do not affect a precise control of the temperature.
- a control for driving the switching valve is provided, which for the operation of the refrigerant compressor in a lower part-load range Operating the switching valve in successive, one opening interval and a closing interval of the switching valve comprehensive switching intervals that are shorter than about 10 seconds.
- the switching intervals are longer than approximately 0.02 seconds.
- the switching intervals are longer than 0.05 seconds, and it is particularly favorable if the switching intervals are longer than 0.1 seconds.
- the switching intervals correspond to a switching frequency which is smaller by more than a factor of 5 than a natural frequency of the switching valve.
- a particularly expedient solution provides that the controller operates in the lower part-load range all cylinder units of the refrigerant compressor in the switching intervals.
- duration of the switching intervals a wide variety of possible solutions are conceivable.
- a variant which is particularly favorable for reasons of simplicity provides that the control operates with time-constant switching intervals.
- controller varies the switching intervals according to a drive speed of the refrigerant compressor.
- the switching valve so that it acts directly, for example magnetically controlled, on the inlet flow.
- the switching valve is a servo valve.
- the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
- valve body In order to ensure that the valve body does not automatically assume the end position brought about by the pressure in the outlet chamber, it is preferably provided that the valve body is acted upon by an elastic force store acting in the opposite direction to the action of the pressure on the valve body.
- valve body is coupled to a pressure which is acted upon by the pressure in the outlet chamber and is guided in a switching cylinder housing, which then actuates the valve body.
- the switching piston and the switching cylinder housing enclose a switching cylinder chamber and when the pressure in the switching cylinder chamber is controllable.
- valve body and the switching piston form a unit which is guided in the switching cylinder housing.
- Such a control valve is formed, for example, as a fast-reacting, electrically actuated solenoid valve or similarly constructed valve.
- control valve opens or closes a connection channel between the control cylinder chamber and the outlet, so that in a simple way there is the possibility to pressurize the control piston with under pressure in the outlet chamber medium.
- the natural frequency of the unit consisting of switching piston, valve body and elastic energy storage at least equal to the natural frequency of the switching valve.
- Such a high natural frequency of the switching valve can be achieved in particular when the switching piston is made of a lightweight construction material.
- Such a lightweight material may for example be a light metal or a plastic, for example, a fiber-reinforced plastic.
- control piston provides that this is designed as a hollow body, so that also by a high natural frequency of the unit of control piston, valve body and elastic energy storage device can be achieved.
- An exemplary embodiment of a refrigeration system according to the invention designated as a whole by 10, comprises a refrigerant compressor 12, from whose high-pressure connection 14 a line 16 leads to a condenser designated as a whole by 18, in which the compressed refrigerant condenses due to heat dissipation.
- liquid refrigerant flows in a line 20 to a collector 22, in which the liquid refrigerant collects and from which this then flows via a line 28 to an expansion valve 30 for an evaporator 32.
- the vaporized refrigerant flows via a line 34 to a low pressure port 36 of the refrigerant compressor 12th
- the refrigerant compressor 12 is designed as a reciprocating compressor and comprises a compressor housing 40, in which two cylinder banks 42a and 42b arranged in a V-shape are provided, each of which comprises at least one, in particular two or more cylinder units 44.
- Each of these cylinder units 44 is formed from a cylinder housing 46, in which a piston 48 is oscillated by the fact that the piston 48 is driven by a connecting rod 50, which in turn sits on an eccentric 52 of an eccentric shaft 54 which is driven for example by an electric motor 55 is.
- the cylinder housing 46 of each of the cylinder units 44 is closed by a valve plate 56 on which a cylinder head 58 is disposed.
- valve plate 56 covers not only a cylinder housing 46 of a cylinder bank 42, but all the cylinder housing 46 of the respective cylinder bank 42 and in the same way, the cylinder head 58 also overlaps all the cylinder housing 46 of the respective cylinder bank 42nd
- the compressor housing 40 further comprises an inlet channel 60 communicating with the low-pressure connection 36, which is integrated, for example, in the compressor housing 40.
- each cylinder bank 42 is associated with a switching valve 70, designated as a whole, which serves to convey an inlet flow 74 that passes from the inlet channel 60 into the respective cylinder head 58 and into an inlet chamber 72 thereof through the valve plate 56 of refrigerant to break.
- a switching valve 70 designated as a whole, which serves to convey an inlet flow 74 that passes from the inlet channel 60 into the respective cylinder head 58 and into an inlet chamber 72 thereof through the valve plate 56 of refrigerant to break.
- the inlet flow 74 has the possibility, via an inlet opening 76 provided in the valve plate 56 and an inlet valve 78 provided on the valve plate 56, into a cylinder chamber bounded by the respective piston 48 and the respective cylinder housing 46 and the valve plate 56 80 to be compressed therein by the oscillating movement of the piston 48, so that via an outlet opening 82 and an outlet valve 84, an outlet stream 86 exits the cylinder chamber 80 and enters an outlet chamber 88 of the cylinder head 58.
- the switching valve 70 is formed as a servo valve, which is integrated in the cylinder head 58 and has a valve body 90, with which an opening provided in the valve plate 56 Eihströmö réelle 92 of the inlet chamber 72 is closed.
- the valve body 90 is further arranged on a switching piston 94, which is guided in a switching cylinder housing 96, so that the switching piston 94 is movable by pressure present in a switching cylinder chamber 98 in the direction of the valve plate 56 to close the inflow opening 92 in the same.
- the force acting on the switching piston 94 by the high pressure in the switching cylinder chamber 98 counteracts the force of an elastic force accumulator 120 which is supported on the switching cylinder housing 96 on the one hand and on the other hand acts on the switching piston 94 such that it moves away from the valve plate 56 and thus moves the valve body 90 into a position releasing the inlet opening 92.
- the switching piston 94 is provided with a pressure relief passage 122 which leads from an opening facing the switching cylinder chamber 98 to an outlet opening 124 shown in FIG. 4, which closes in the position of the valve body 90 closing the inlet opening 92
- Switching piston 94 opens into the inlet chamber 72.
- the pressure relief passage 124 thereby causes the pressure in the switching cylinder chamber 98 to rapidly collapse when the connection between the high-pressure passage 116 and the pressure feed passage 118 is interrupted, thus releasing the switching piston 94, together with the valve body 90, into the inlet opening 92 under the action of the elastic force accumulator 120 , move in Fig. 3 shown position.
- the switching valve 70 can be controlled by a controller 130 shown in FIG. 1 such that it closes and opens the switching valve 70 in continuously successive switching intervals SI, wherein each of the switching intervals SI has an opening interval O, in which the valve body 90 is in its releasing position Passage of the inlet stream 74 through the inlet opening 92 allows, and a closing interval S, in which the valve body 90, as shown in Fig. 4, in its closing position, the flow of the inlet stream 74 through the inlet opening 92 blocked.
- the duration of the opening interval O and the closing interval S relative to each other can now be set variably in all partial load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
- the opening interval O may substantially extend over the entire duration of the switching interval SI, while the closing interval S is arbitrarily small, or vice versa, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O becomes arbitrarily small.
- the system is provided with a reaction inertia, so that when the extraction of refrigerant from the evaporator 32 is interrupted, the temperature T of the evaporator 32 does not rise immediately but, as shown in FIG. 6, requires a time Z to increase by one value D to rise.
- the switching interval SI is set to be shorter than the time Z that elapses until the temperature T of the evaporator 32 rises from a temperature T A of the evaporator 32 by a value D of about 10% better about 5%, when there is a sudden interruption in the extraction of refrigerant from the evaporator 32 and the supply of high pressure medium at the high pressure port 14.
- the durations of the switching intervals SI are shorter than about 10 seconds, more preferably less than about 2 seconds.
- the switching intervals are longer than about 0.02 second, more preferably longer than 0.05 second, and preferably longer than 0.1 second.
- a preferred operating range provides switching intervals SI whose duration is between 0.1 and 10 seconds.
- the switching pistons 94 together with the valve body 90 and the elastic force accumulators 120 have a natural frequency higher than the frequency corresponding to the maximum switching intervals SI, so that the switching pistons 94 are able to realize the opening intervals O and the closing intervals S substantially instantaneously within the switching intervals SI.
- the natural frequencies of the systems of switching piston 94, valve body 90 and elastic energy storage device 120 by a factor of at least 5 or even better at least 10 higher than the switching intervals SI corresponding frequencies.
- the switching pistons 94 are made of a lightweight construction material, for example light metal or plastic, in order to move small masses.
- the switching pistons 94 ' are designed as hollow bodies in order to achieve the lowest possible mass and thus the highest possible natural frequency.
- the solution according to the invention provides, for example, such a switching valve 70 per cylinder bank, so that there is the possibility of correspondingly switching off the inlet flow for all cylinder units 44 of a cylinder bank 42.
- the controller 130 controls all cylinder units 44 at the same switching intervals, at least in a lower part-load range, that is, in a range between about 1% and about 30% of the maximum mass flow.
- the controller 130 is now able to control the switching valve 70 in an operation of the refrigerant compressor 12 in the full load range such that the valve body 90 is constantly in the inlet opening 92 releasing position, so that the inlet flow 74 to all cylinder units 44 of the respective cylinder bank 42nd can flow.
- valve body 90 is constantly in its occluding the inflow opening 92 position. In this case, essentially no mass flow of refrigerant is compressed. Only the mass flow flowing through the pressure channel 116 and the pressure supply channel 118 and the pressure relief channel 122 is compressed.
- the controller 130 is capable of continuously adjusting any partial load by variably setting the duration of the opening interval O and the duration of the closing interval S which add to the period of the switching interval SI in the desired ratio.
- the switching interval SI can be the same in all partial load ranges.
- the variation of the switching interval SI occurs so that at low speed of the electric motor, the switching intervals SI are long and at high speed of the electric motor, the switching intervals are shorter.
- the advantage of the solution according to the invention is the fact that in the reciprocating compressor, the power consumption is proportional to the mass flow and thus with a reduction of the mass flow through successive opening intervals O and closing intervals S in the partial load range, the possibility to reduce the power consumption of the reciprocating compressor.
- the solution according to the invention makes it possible to configure the start-up process of the refrigerant compressor 12 by controlling the mass flow rate in such a way that the risks from boiling-out refrigerant are minimized.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft einen Kältemittelverdichter für Kälteanlagen umfassend mindestens eine Zylindereinheit, die ein Zylindergehäuse und einen in dem Zylindergehäuse oszillierend bewegbaren Kolben aufweist, einen Zylinderkopf, mit einer von einem Einlassstrom der mindestens einen Zylindereinheit durchströmten Einlasskammer und mit einer von einem Auslassstrom der mindestens einen Zylindereinheit durchsetzten Auslasskammer, sowie ein Schaltventil zum Unterbrechen des Einlassstroms.The invention relates to a refrigerant compressor for refrigeration systems comprising at least one cylinder unit, which has a cylinder housing and a piston oscillatingly movable in the cylinder housing, a cylinder head, with an inlet chamber through which an inlet flow of the at least one cylinder unit passes and with one of an outlet flow of the at least one cylinder unit Outlet chamber, and a switching valve for interrupting the inlet flow.
Derartige Kältemittelverdichter sind aus der
Mit dieser Lösung ist eine Steuerung des Massendurchsatzes lediglich entsprechend dem Verhältnis des Hubvolumens der abgeschalteten Zylindereinheiten und des Hubvolumens der arbeitenden Zylindereinheiten möglich.With this solution, a control of the mass flow rate is only possible in accordance with the ratio of the stroke volume of the deactivated cylinder units and the stroke volume of the working cylinder units.
Der Erfindung liegt daher die Aufgabe zugrunde, einen Kältemittelverdichter der gattungsgemäßen Art derart zu verbessern, dass dieser in beliebigen Teillastbereichen betreibbar ist.The invention is therefore based on the object to improve a refrigerant compressor of the generic type such that it can be operated in any part load ranges.
Diese Aufgabe wird bei einem Kältemittelverdichter der eingangs beschriebenen Art erfindungsgemäß dadurch gelöst, dass eine Steuerung zum Ansteuern des Schaltventils vorgesehen ist, welche zum Betrieb des Kältemittelverdichters in einem unteren Teillastbereich das Schaltventil in aufeinanderfolgenden, jeweils ein Öffnungsintervall und ein Schließintervall des Schaltventils umfassenden Schaltintervallen betreibt, die kürzer sind als eine kürzeste Zeitdauer, nach welcher eine Temperatur eines Verdampfers in der arbeitenden Kälteanlage bei einer Unterbrechung des Einlassstroms um ungefähr 10% angestiegen ist.This object is achieved in a refrigerant compressor of the type described above according to the invention that a control is provided for driving the switching valve, which operates the switching valve in consecutive, each an opening interval and a closing interval of the switching valve comprehensive switching intervals for operation of the refrigerant compressor in a lower part load range, which are shorter than a shortest period of time after which a temperature of an evaporator in the working refrigeration system has increased by about 10% at an interruption of the intake flow.
Der Vorteil der erfindungsgemäßen Lösung ist darin zu sehen, dass diese die Möglichkeit eröffnet, einen Kältemittelverdichter, insbesondere einen Hubkolbenverdichter in einem unteren Teillastbereich bei beliebiger Teillast zu betreiben, da durch das Verhältnis der Öffnungsintervalle und der Schließintervalle innerhalb jedes Schaltintervalls der zu verdichtende Massenstrom stufenlos und beliebig einstellbar ist.The advantage of the solution according to the invention is the fact that this opens up the possibility to operate a refrigerant compressor, in particular a reciprocating compressor in a lower part load range at any part load, as by the ratio of the opening intervals and the closing intervals within each switching interval of the mass flow to be compressed continuously and is arbitrarily adjustable.
Dabei werden für die Schaltintervalle Zeitdauern gewählt, die ausreichend kurz sind, so dass aufgrund der Trägheit der Reaktion der erfindungsgemäßen Kälteanlage auf die Schaltintervalle nur unwesentliche Temperaturschwankungen im Verdampfer der Kälteanlagen entstehen, die eine präzise Regelung der Temperatur nicht beeinträchtigen.In this case, time periods are selected for the switching intervals, which are sufficiently short, so that due to the inertia of the reaction of the refrigeration system according to the invention to the switching intervals only insignificant temperature fluctuations in the evaporator of the refrigerators arise that do not affect a precise control of the temperature.
Alternativ zur vorstehend beschriebenen Lösung ist bei einem weiteren Ausführungsbeispiel eines Kältemittelverdichters der eingangs beschriebenen Art eine Steuerung zum Ansteuern des Schaltventils vorgesehen, welche zum Betrieb des Kältemittelverdichters in einem unteren Teillastbereich das Schaltventil in aufeinanderfolgenden, jeweils ein Öffnungsintervall und ein Schließintervall des Schaltventils umfassenden Schaltintervallen betreibt, die kürzer sind als ungefähr 10 Sekunden.Alternatively to the solution described above, in a further embodiment of a refrigerant compressor of the type described above, a control for driving the switching valve is provided, which for the operation of the refrigerant compressor in a lower part-load range Operating the switching valve in successive, one opening interval and a closing interval of the switching valve comprehensive switching intervals that are shorter than about 10 seconds.
Durch eine derartige Limitierung der Dauer der Schaltintervalle ist ebenfalls in erfindungsgemäßer Weise die Möglichkeit geschaffen, den Kältemittelverdichter in dem unteren Teillastbereich bei beliebig einstellbarer Teillast zu betreiben, ohne das Druckschwankungen in der Kälteanlage auftreten, die die Qualität der Regelung derselben beeinträchtigen.By such a limitation of the duration of the switching intervals, the possibility is created in accordance with the invention to operate the refrigerant compressor in the lower part load range at any adjustable partial load, without the pressure fluctuations in the refrigeration system occur, affecting the quality of the control of the same.
Noch vorteilhafter ist es dabei, wenn die Schaltintervalle kürzer als ungefähr 2 Sekunden sind.It is even more advantageous if the switching intervals are shorter than about 2 seconds.
Um die Schaltventile wirksam betreiben zu können, ist vorzugsweise vorgesehen, dass die Schaltintervalle länger als ungefähr 0,02 Sekunden sind.In order to be able to operate the switching valves effectively, it is preferably provided that the switching intervals are longer than approximately 0.02 seconds.
Noch vorteilhafter ist es, wenn die Schaltintervalle länger als 0,05 Sekunden sind und besonders günstig ist es, wenn die Schaltintervalle länger als 0,1 Sekunden sind.It is even more advantageous if the switching intervals are longer than 0.05 seconds, and it is particularly favorable if the switching intervals are longer than 0.1 seconds.
Besonders vorteilhaft ist es für ein Schalten des Schaltventils, wenn die Schaltintervalle einer Schaltfrequenz entsprechen, die kleiner als eine Eigenfrequenz des Schaltventils ist.It is particularly advantageous for a switching of the switching valve, when the switching intervals correspond to a switching frequency which is smaller than a natural frequency of the switching valve.
Noch besser ist es, wenn die Schaltintervalle einer Schaltfrequenz entsprechen, die um mehr als einen Faktor 5 kleiner als eine Eigenfrequenz des Schaltventils ist.It is even better if the switching intervals correspond to a switching frequency which is smaller by more than a factor of 5 than a natural frequency of the switching valve.
Grundsätzlich wäre es denkbar, mit der erfindungsgemäßen Steuerung im unteren Teillastbereich beispielsweise einen Teil der Zylindereinheiten abzuschalten und nur einen Teil der Zylindereinheiten in den Schaltintervallen zu betreiben.In principle, it would be conceivable to switch off a part of the cylinder units with the control according to the invention in the lower part-load range and to operate only a part of the cylinder units in the switching intervals.
Eine besonders zweckmäßige Lösung sieht jedoch vor, dass die Steuerung in dem unteren Teillastbereich alle Zylindereinheiten des Kältemittelverdichters in den Schaltintervallen betreibt.However, a particularly expedient solution provides that the controller operates in the lower part-load range all cylinder units of the refrigerant compressor in the switching intervals.
Ferner ist es denkbar, auch im oberen Teillastbereich nur einen Teil der Zylindereinheiten abzuschalten und einen anderen Teil Zylindereinheiten in den Schaltintervallen zu betreiben.It is also conceivable to switch off only a part of the cylinder units in the upper part-load range and to operate another part of cylinder units in the switching intervals.
Besonders günstig ist es jedoch, wenn die Steuerung im gesamten Teillastbereich alle Zylindereinheiten in den Schaltintervallen betreibt.It is particularly favorable, however, if the controller operates all cylinder units in the switching intervals in the entire partial load range.
Hinsichtlich der Zeitdauer der Schaltintervalle sind die unterschiedlichsten Lösungsmöglichkeiten denkbar. So sieht eine aus Gründen der Einfachheit besonders günstige Variante vor, dass die Steuerung mit zeitlich konstanten Schaltintervallen arbeitet.With regard to the duration of the switching intervals, a wide variety of possible solutions are conceivable. For example, a variant which is particularly favorable for reasons of simplicity provides that the control operates with time-constant switching intervals.
Eine andere vorteilhafte Lösung sieht vor, dass die Steuerung die Schaltintervalle entsprechend einer Antriebsdrehzahl des Kältemittelverdichters variiert.Another advantageous solution provides that the controller varies the switching intervals according to a drive speed of the refrigerant compressor.
Hinsichtlich der Ausbildung des Schaltventils wurden bislang keine näheren Angaben gemacht.With regard to the design of the switching valve so far no details have been made.
So wäre es denkbar, das Schaltventil so auszubilden, dass dieses unmittelbar, beispielsweise magnetgesteuert, auf den Einlassstrom einwirkt.Thus, it would be conceivable to design the switching valve so that it acts directly, for example magnetically controlled, on the inlet flow.
Aus Gründen der erforderlichen hohen Ventilkräfte hat es sich jedoch als vorteilhaft erwiesen, wenn das Schaltventil ein Servoventil ist.For reasons of the required high valve forces, it has proved to be advantageous if the switching valve is a servo valve.
Insbesondere ist es dabei günstig, wenn das Servoventil einen durch einen mit dem Druck in der Auslasskammer zusammenhängenden Druck betätigbaren Ventilkörper umfasst.In particular, it is advantageous if the servo valve comprises a valve body which can be actuated by a pressure associated with the pressure in the outlet chamber.
Um sicherzustellen, dass der Ventilkörper nicht die durch den Druck in der Auslasskammer herbeigeführte Endstellung selbsttätig einnimmt, ist vorzugsweise vorgesehen, dass der Ventilkörper durch einen entgegengesetzt zur Wirkung des Drucks auf den Ventilkörper einwirkenden elastischen Kraftspeicher beaufschlagt ist.In order to ensure that the valve body does not automatically assume the end position brought about by the pressure in the outlet chamber, it is preferably provided that the valve body is acted upon by an elastic force store acting in the opposite direction to the action of the pressure on the valve body.
Hinsichtlich der Betätigung des Ventilkörpers durch den Druck in der Auslasskammer sind die unterschiedlichsten konstruktiven Lösungen denkbar. Beispielsweise wären Lösungen mit durch den Druck in der Auslasskammer beaufschlagten Membranen oder ähnliches denkbar.With regard to the actuation of the valve body by the pressure in the outlet chamber a variety of constructive solutions are conceivable. For example, solutions with membranes acted upon by the pressure in the outlet chamber or the like would be conceivable.
Eine besonders zweckmäßige Lösung sieht vor, dass der Ventilkörper mit einem mit den Druck in der Auslasskammer zusammenhängenden Druck beaufschlagbaren und in einem Schaltzylindergehäuse geführten Schaltkolben gekoppelt ist, welcher dann den Ventilkörper betätigt.A particularly expedient solution provides that the valve body is coupled to a pressure which is acted upon by the pressure in the outlet chamber and is guided in a switching cylinder housing, which then actuates the valve body.
Hinsichtlich der Beaufschlagung des Schaltkolbens hat es sich als vorteilhaft erwiesen, wenn der Schaltkolben und das Schaltzylindergehäuse eine Schaltzylinderkammer umschließen und wenn der Druck in der Schaltzylinderkammer steuerbar ist.With regard to the application of the switching piston, it has proven to be advantageous if the switching piston and the switching cylinder housing enclose a switching cylinder chamber and when the pressure in the switching cylinder chamber is controllable.
Ferner ist es aus konstruktiven Gründen günstig, wenn der Ventilkörper und der Schaltkolben eine Einheit bilden, die in dem Schaltzylindergehäuse geführt ist.Furthermore, it is favorable for structural reasons, when the valve body and the switching piston form a unit which is guided in the switching cylinder housing.
Des weiteren ist es bei einem derartigen Servoventil günstig, wenn dieses ein von der Steuerung ansteuerbares Steuerventil umfasst.Furthermore, it is advantageous in such a servo valve, if this comprises a controllable by the control valve control.
Ein derartiges Steuerventil ist beispielsweise als schnellreagierendes, elektrisch anzusteuerndes Magnetventil oder ähnlich aufgebautes Ventil ausgebildet.Such a control valve is formed, for example, as a fast-reacting, electrically actuated solenoid valve or similarly constructed valve.
Zum Betreiben des Servoventils ist dabei bei einem vorteilhaften Ausführungsbeispiel vorgesehen, dass das Steuerventil einen Verbindungskanal zwischen der Steuerzylinderkammer und der Auslasskammer öffnet oder schließt, so dass in einfacher Weise die Möglichkeit besteht, den Schaltkolben mit unter dem Druck in der Auslasskammer stehendem Medium zu beaufschlagen.To operate the servo valve is provided in an advantageous embodiment, that the control valve opens or closes a connection channel between the control cylinder chamber and the outlet, so that in a simple way there is the possibility to pressurize the control piston with under pressure in the outlet chamber medium.
Um bei einem derartigen Servoventil eine möglichst hohe Eigenfrequenz und somit kurze Schaltzeit zu erreichen, ist vorzugsweise vorgesehen, dass die Eigenfrequenz der Einheit aus Schaltkolben, Ventilkörper und elastischem Kraftspeicher mindestens der Eigenfrequenz des Schaltventils entspricht.In order to achieve the highest possible natural frequency and thus short switching time in such a servo valve, it is preferably provided that the natural frequency of the unit consisting of switching piston, valve body and elastic energy storage at least equal to the natural frequency of the switching valve.
Eine derartige hohe Eigenfrequenz des Schaltventils lässt sich insbesondere dann erreichen, wenn der Schaltkolben aus einem Leichtbaumaterial hergestellt ist.Such a high natural frequency of the switching valve can be achieved in particular when the switching piston is made of a lightweight construction material.
Ein derartiges Leichtbaumaterial kann beispielsweise ein Leichtmetall oder auch ein Kunststoff, beispielsweise auch ein faserverstärkter Kunststoff, sein.Such a lightweight material may for example be a light metal or a plastic, for example, a fiber-reinforced plastic.
Eine weitere vorteilhafte Ausbildung des Schaltkolbens sieht vor, dass diese als Hohlkörper ausgebildet ist, so dass auch dadurch eine hohe Eigenfrequenz der Einheit aus Schaltkolben, Ventilkörper und elastischem Kraftspeicher erreichbar ist.A further advantageous embodiment of the control piston provides that this is designed as a hollow body, so that also by a high natural frequency of the unit of control piston, valve body and elastic energy storage device can be achieved.
Weitere Merkmale und Vorteile der Erfindung sind Gegenstand der nachfolgenden Beschreibung sowie der zeichnerischen Darstellung einiger Ausführungsbeispiele.Further features and advantages of the invention are the subject of the following description and the drawings of some embodiments.
In der Zeichnung zeigen:
- Fig. 1
- eine schematische Darstellung einer erfindungsgemäßen Kälteanlage;
- Fig. 2
- einen Querschnitt längs Linie 2-2 durch ein Kältemittelverdichter der erfindungsgemäßen Kälteanlage;
- Fig. 3
- einen Schnitt durch ein Schaltventil integriert in einen Zylinderkopf in der geöffneten Stellung eines Ventilkörpers des Schaltventils;
- Fig. 4
- einen Schnitt ähnlich Fig. 3 in einer geschlossenen Stellung des Ventilkörpers des Schaltventils;
- Fig. 5
- eine schematische Darstellung eines Schaltintervalls umfassend ein Öffnungsintervall und ein Schließintervall;
- Fig. 6
- eine schematische Darstellung eines Verhaltens der Temperatur des Verdampfers in der Kälteanlage bei Unterbrechung der Verdichtung von Kältemittel;
- Fig. 7
- einen Schnitt ähnlich Fig. 3 durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Kältemittelverdichters und
- Fig. 8
- einen Schnitt ähnlich Fig. 4 durch das zweite Ausführungsbeispiel eines erfindungsgemäßen Kältemittelverdichters.
- Fig. 1
- a schematic representation of a refrigeration system according to the invention;
- Fig. 2
- a cross section along line 2-2 through a refrigerant compressor of the refrigeration system according to the invention;
- Fig. 3
- a section through a switching valve integrated in a cylinder head in the open position of a valve body of the switching valve;
- Fig. 4
- a section similar to Figure 3 in a closed position of the valve body of the switching valve.
- Fig. 5
- a schematic representation of a switching interval comprising an opening interval and a closing interval;
- Fig. 6
- a schematic representation of a behavior of the temperature of the evaporator in the refrigeration system in the interruption of the compression of refrigerant;
- Fig. 7
- a section similar to FIG. 3 by a second embodiment of a refrigerant compressor according to the invention and
- Fig. 8
- a section similar to FIG. 4 by the second embodiment of a refrigerant compressor according to the invention.
Ein Ausführungsbeispiel einer als Ganzes mit 10 bezeichneten erfindungsgemäßen Kälteanlage, umfasst einen Kältemittelverdichter 12, von dessen Hochdruckanschluss 14 eine Leitung 16 zu einem als Ganzes mit 18 bezeichneten Kondensator führt, in welchem das verdichtete Kältemittel durch Wärmeabfuhr kondensiert.An exemplary embodiment of a refrigeration system according to the invention, designated as a whole by 10, comprises a
Von dem Kondensator 18 strömt flüssiges Kältemittel in einer Leitung 20 zu einem Sammler 22, in welchem sich das flüssige Kältemittel sammelt und von welchem ausgehend dieses dann über eine Leitung 28 zu einem Expansionsventil 30 für einen Verdampfer 32 strömt.From the
Nach Durchströmen des Verdampfers 32 strömt das verdampfte Kältemittel über eine Leitung 34 zu einem Niederdruckanschluss 36 des Kältemittelverdichters 12.After flowing through the
Wie in Fig. 2 dargestellt, ist der erfindungsgemäße Kältemittelverdichter 12 als Hubkolbenverdichter ausgebildet und umfasst ein Verdichtergehäuse 40, in welchem zwei V-fömig zueinander angeordnete Zylinderbänke 42a und 42b vorgesehen sind, von denen jede mindestens eine, insbesondere zwei oder mehr Zylindereinheiten 44 umfasst.As shown in FIG. 2, the
Jede dieser Zylindereinheiten 44 ist gebildet aus einem Zylindergehäuse 46, in welchem ein Kolben 48 dadurch oszillierend bewegbar ist, dass der Kolben 48 durch ein Pleuel 50 antreibbar ist, das seinerseits auf einem Exzenter 52 einer Exzenterwelle 54 sitzt, die beispielsweise durch einen Elektromotor 55 angetrieben ist.Each of these
Das Zylindergehäuse 46 jeder der Zylindereinheiten 44 wird durch eine Ventilplatte 56 abgeschlossen, auf welcher ein Zylinderkopf 58 angeordnet ist.The
Vorzugsweise überdeckt dabei die Ventilplatte 56 nicht nur ein Zylindergehäuse 46 einer Zylinderbank 42, sondern sämtliche Zylindergehäuse 46 der jeweiligen Zylinderbank 42 und in gleicher Weise übergreift der Zylinderkopf 58 ebenfalls sämtliche Zylindergehäuse 46 der jeweiligen Zylinderbank 42.Preferably, the
Das Verdichtergehäuse 40 umfasst ferner noch einen mit dem Niederdruckanschluss 36 in Verbindung stehenden Einlasskanal 60, welcher beispielsweise in dem Verdichtergehäuse 40 integriert ist.The
Wie in Fig. 3 vergrößert dargestellt, ist jeder Zylinderbank 42 ein als Ganzes mit 70 bezeichnetes Schaltventil zugeordnet, welches dazu dient, einen von dem Einlasskanal 60 in den jeweiligen Zylinderkopf 58, und zwar in eine Einlasskammer 72 desselben durch die Ventilplatte 56 hindurchtretenden Einlassstrom 74 von Kältemittel zu unterbrechen.As shown enlarged in FIG. 3, each cylinder bank 42 is associated with a switching
Ist das Schaltventil 70 geöffnet, so hat der Einlassstrom 74 die Möglichkeit, über eine in der Ventilplatte 56 vorgesehene Einlassöffnung 76 und ein an der Ventilplatte 56 vorgesehenes Einlassventil 78 in eine von dem jeweiligen Kolben 48 und dem jeweiligen Zylindergehäuse 46 sowie der Ventilplatte 56 begrenzte Zylinderkammer 80 einzutreten, um in dieser durch die oszillierende Bewegung des Kolbens 48 verdichtet zu werden, so dass über eine Auslassöffnung 82 und ein Auslassventil 84 ein Auslassstrom 86 aus der Zylinderkammer 80 austritt und in eine Auslasskammer 88 des Zylinderkopfes 58 eintritt.When the switching
Das Schaltventil 70 ist als Servoventil ausgebildet, welches in dem Zylinderkopf 58 integriert ist und einen Ventilkörper 90 aufweist, mit welchem eine in der Ventilplatte 56 vorgesehene Eihströmöffnung 92 der Einlasskammer 72 verschließbar ist.The switching
Der Ventilkörper 90 ist ferner an einem Schaltkolben 94 angeordnet, welcher in einem Schaltzylindergehäuse 96 geführt ist, so dass der Schaltkolben 94 durch in einer Schaltzylinderkammer 98 vorliegenden Druck in Richtung der Ventilplatte 56 bewegbar ist, um die Einströmöffnung 92 in derselben zu verschließen.The
Eine aus dem Schaltzylindergehäuse 96, dem Schaltkolben 94 und der Schaltzylinderkammer 98 gebildete Schaltzylindereinheit 100, die in den Zylinderkopf 58 integriert ist, ist dabei über ein Steuerventil 110 steuerbar, welches einen elektromagnetisch bewegbaren Steuerkolben 112 umfasst, mit welchem ein Steuerventilsitz 114 verschließbar ist, wobei der Steuerkolben 112 und der Steuerventilsitz 114 dazu vorgesehen sind, eine Verbindung zwischen einem zur Auslasskammer 88 führenden Druckkanal 116 und einem zu der Schaltzylinderkammer 98 führenden Druckzufuhrkanal 118 für den Schaltzylinder 100 zu unterbrechen oder freizugeben.A
Wird die Verbindung zwischen dem Hochdruckkanal 116 und dem Druckzufuhrkanal 118 freigegeben, so steht die Schaltzylinderkammer 98 unter dem in der Auslasskammer 88 herrschenden Hochdruck und folglich bewegt sich der Schaltkolben 94 in Richtung der Ventilplatte 56 und presst den Ventilkörper 90 gegen diese, um die Einströmöffnung 92 in der Ventilplatte 56 zu verschließen.When the connection between the high-
Dabei wirkt der auf den Schaltkolben 94 durch den Hochdruck in der Schaltzylinderkammer 98 wirkenden Kraft die Kraft eines elastischen Kraftspeichers 120 entgegen, welcher an dem Schaltzylindergehäuse 96 einerseits abgestützt ist und andererseits auf den Schaltkolben 94 derart wirkt, dass dieser sich von der Ventilplatte 56 weg bewegt und somit den Ventilkörper 90 in eine die Einströmöffnung 92 freigebende Stellung bewegt.In this case, the force acting on the
Insbesondere ist der Schaltkolben 94 mit einem Druckentlastungskanal 122 versehen, welcher von einer der Schaltzylinderkammer 98 zugewandten Öffnung zu einer, in Fig. 4 dargestellten Auslassöffnung 124 führt, die in der die Einströmöffnung 92 verschließenden Stellung des Ventilkörpers 90 und des Schaltkolbens 94 in die Einlasskammer 72 mündet. Der Druckentlastungskanal 124 bewirkt dabei, dass bei einer Unterbrechung der Verbindung zwischen dem Hochdruckkanal 116 und dem Druckzufuhrkanal 118 der Druck in der Schaltzylinderkammer 98 schnell zusammenbricht und sich somit unter Wirkung des elastischen Kraftspeichers 120 der Schaltkolben 94 mitsamt dem Ventilkörper 90 in eine die Einströmöffnung 92 freigebende, in Fig. 3 dargestellte Stellung bewegen.In particular, the
Das Schaltventil 70 ist durch eine in Fig. 1 dargestellte Steuerung 130 derart ansteuerbar, dass dieses in kontinuierlich aufeinanderfolgenden Schaltintervallen SI das Schaltventil 70 schließt und öffnet, wobei jedes der Schaltintervalle SI ein Öffnungsintervall O aufweist, in welchem der Ventilkörper 90 in seiner freigebenden Stellung ein Hindurchtreten des Einlassstroms 74 durch die Einströmöffnung 92 zulässt, sowie ein Schließintervall S, in welchem der Ventilkörper 90, wie in Fig. 4 dargestellt, in seiner verschließenden Stellung das Durchströmen des Einlassstroms 74 durch die Einströmöffnung 92 blockiert.The switching
Innerhalb der Dauer des jeweiligen Schaltintervalls SI kann nun in allen Teillastbereichen die Zeitdauer des Öffnungsintervalls O und des Schließintervalls S relativ zueinander variabel eingestellt werden, so dass entweder das Öffnungsintervall O größer ist als das Schließintervall oder umgekehrt.Within the duration of the respective switching interval SI, the duration of the opening interval O and the closing interval S relative to each other can now be set variably in all partial load ranges, so that either the opening interval O is greater than the closing interval or vice versa.
Im Extremfall kann das Öffnungsintervall O im Wesentlichen sich über die gesamte Dauer des Schaltintervalls SI erstrecken, während das Schließintervall S beliebig klein wird, oder es kann umgekehrt auch sich das Schließintervall S im Wesentlichen über die gesamte Dauer des Schaltintervalls SI erstrecken, so dass das Öffnungsintervall O beliebig klein wird.In the extreme case, the opening interval O may substantially extend over the entire duration of the switching interval SI, while the closing interval S is arbitrarily small, or vice versa, the closing interval S may extend substantially over the entire duration of the switching interval SI, so that the opening interval O becomes arbitrarily small.
Da in der erfindungsgemäßen Kälteanlage 10 über das Expansionsventil 30 in der Regel ständig ein Verdampfen von flüssigem Kältemittel erfolgt, führt eine Unterbrechung der Verdichtung von Kältemittel durch den Kältemittelverdichter 12 zu einem Anstieg der Temperatur T im Verdampfer 32.Since in the
Allerdings ist das System mit einer Reaktionsträgheit versehen, so dass bei einer Unterbrechung der Absaugung von Kältemittel aus dem Verdampfer 32 die Temperatur T des Verdampfers 32 nicht sofort ansteigt, sondern, wie in Fig. 6 dargestellt, eine Zeitdauer Z benötigt, um um einen Wert D anzusteigen.However, the system is provided with a reaction inertia, so that when the extraction of refrigerant from the
So lange der Wert D bei Werten kleiner 10% einer Ausgangstemperatur TA des Verdampfers liegt, sind diese Schwankungen für die Funktion der erfindungsgemäßen Kälteanlage irrelevant.As long as the value D is less than 10% of an outlet temperature T A of the evaporator, these fluctuations are irrelevant to the function of the refrigeration system according to the invention.
Aus diesem Grund ist das Schaltintervall SI so gewählt, dass dieses kürzer ist, als die Zeitdauer Z, die vergeht, bis die Temperatur T des Verdampfers 32 ausgehend von einer Temperatur TA, des Verdampfers 32 um einen Wert D von ungefähr 10%, noch besser ungefähr 5%, gestiegen ist, wenn eine plötzliche Unterbrechung der Absaugung von Kältemittel aus dem Verdampfer 32 und der Zufuhr von unter Hochdruck stehendem Medium am Hochdruckanschluss 14 erfolgt.For this reason, the switching interval SI is set to be shorter than the time Z that elapses until the temperature T of the
Damit ist sichergestellt, dass die Öffnungsintervalle O und die Schließintervalle S innerhalb des jeweiligen Schaltintervalls SI sich unwesentlich auf die Funktion der Kälteanlage auswirken und lediglich zu geringfügigen Temperaturschwankungen des Verdampfers 32 der erfindungsgemäßen Kälteanlage führen.This ensures that the opening intervals O and the closing intervals S within the respective switching interval SI have an insignificant effect on the function of the refrigeration system and only lead to slight temperature fluctuations of the
Üblicherweise liegen die Zeitdauern der Schaltintervalle SI bei Zeitdauern, die kürzer sind als ungefähr 10 Sekunden, noch besser kürzer als ungefähr 2 Sekunden.Usually, the durations of the switching intervals SI are shorter than about 10 seconds, more preferably less than about 2 seconds.
Andererseits sind, um ausreichende Öffnungsintervalle O zu gewährleisten, die Schaltintervalle länger als ungefähr 0,02 Sekunden, noch besser länger als 0,05 Sekunden und vorzugsweise länger als 0,1 Sekunden.On the other hand, to ensure sufficient opening intervals O, the switching intervals are longer than about 0.02 second, more preferably longer than 0.05 second, and preferably longer than 0.1 second.
Ein bevorzugter Betriebsbereich sieht Schaltintervalle SI vor, deren Dauer zwischen 0,1 und 10 Sekunden liegt.A preferred operating range provides switching intervals SI whose duration is between 0.1 and 10 seconds.
Um derart kurze Schaltintervalle SI zu gewährleisten ist vorzugsweise vorgesehen, dass die Schaltkolben 94 mitsamt den Ventilkörper 90 und den elastischen Kraftspeichern 120 insgesamt eine Eigenfrequenz aufweisen, die höher ist als die den maximalen Schaltintervallen SI entsprechende Frequenz, so dass die Schaltkolben 94 in der Lage sind, innerhalb der Schaltintervalle SI die Öffnungsintervalle O und die Schließintervalle S im Wesentlichen verzögerungsfrei zu realisieren.In order to ensure such short switching intervals SI, it is preferably provided that the switching
Vorzugsweise liegen die Eigenfrequenzen der Systeme aus Schaltkolben 94, Ventilkörper 90 und elastischem Kraftspeicher 120 um einen Faktor von mindestens 5 oder noch besser mindestens 10 höher als die den Schaltintervallen SI entsprechenden Frequenzen.Preferably, the natural frequencies of the systems of switching
Um dies zu realisieren ist zweckmäßigerweise vorgesehen, dass die Schaltkolben 94 aus einem Leichtbaumaterial, beispielsweise Leichtmetall oder Kunststoff sind, um geringe Massen bewegen zu müssen.To realize this, it is expediently provided that the switching
Bei einem zweiten Ausführungsbeispiel eines erfindungsgemäßen Kältemittelverdichters, dargestellt in Fig. 7 und 8 sind die Schaltkolben 94' als Hohlkörper ausgebildet, um eine möglichst geringe Masse und somit eine möglichst hohe Eigenfrequenz zu erreichen.In a second embodiment of a refrigerant compressor according to the invention, shown in FIGS. 7 and 8, the switching pistons 94 'are designed as hollow bodies in order to achieve the lowest possible mass and thus the highest possible natural frequency.
Die erfindungsgemäße Lösung sieht beispielsweise ein derartiges Schaltventil 70 pro Zylinderbank vor, so dass die Möglichkeit besteht, den Einlassstrom für sämtliche Zylindereinheiten 44 einer Zylinderbank 42 entsprechend abzuschalten.The solution according to the invention provides, for example, such a
Es ist aber auch denkbar, ein derartiges Schaltventil 70 so anzuordnen, dass es den Einlassstrom 74 zu allen Zylindereinheiten 44 des gesamten Kältemittelverdichters steuert.However, it is also conceivable to arrange such a
Bei einer vorteilhaften Lösung steuert die Steuerung 130 zumindest in einem unteren Teillastbereich, das heißt in einem Bereich zwischen ungefähr 1% und ungefähr 30% des maximalen Massenstroms, alle Zylindereinheiten 44 mit denselben Schaltintervallen.In an advantageous solution, the
Aber auch in höheren Teillastbereichen, beispielsweise in einem oberen Teillastbereich zwischen ungefähr 30% und 100% des maximalen Massenstroms, ist es günstig, alle Zylindereinheiten 44 mit denselben Schaltintervallen zu betreiben um Auswuchtprobleme des Hubkolbenverdichters zu vermeiden, die bei einer Komplettabschaltung von Zylindereinheiten 44 entstehen.But even in higher partial load ranges, for example, in an upper part load range between about 30% and 100% of the maximum mass flow, it is favorable to operate all
Die Steuerung 130 ist nun in der Lage, bei einem Betrieb des Kältemittelverdichters 12 im Volllastbereich das Schaltventil 70 derart anzusteuern, dass der Ventilkörper 90 ständig in der die Einströmöffnung 92 freigebenden Stellung steht, so dass der Einlassstrom 74 zu allen Zylindereinheiten 44 der jeweiligen Zylinderbank 42 strömen kann.The
In diesem Fall wird der maximale Massenstrom von Kältemittel auf Hochdruck H verdichtet.In this case, the maximum mass flow of refrigerant is compressed to high pressure H.
Es besteht auch die Möglichkeit in einem Nulllastbereich das Schaltventil 70 so anzusteuern, dass der Ventilkörper 90 ständig in seiner die Einströmöffnung 92 verschließenden Stellung steht. In diesem Fall wird im Wesentlichen kein Massenstrom von Kältemittel verdichtet. Einzig der durch den Druckkanal 116 und den Druckzufuhrkanal 118 sowie den Druckentlastungskanal 122 strömende Massenstrom wird verdichtet.It is also possible in a zero-load range to control the switching
Im Teillastbereich ist die Steuerung 130 in der Lage kontinuierlich jede beliebige Teillast einzustellen, und zwar dadurch, dass die Zeitdauer des Öffnungsintervalls O und die Zeitdauer des Schließintervalls S, die sich zur Zeitdauer des Schaltintervalls SI addieren, in dem gewünschten Verhältnis variabel eingestellt werden.In the partial load range, the
Dabei kann in allen Teillastbereichen das Schaltintervall SI gleich groß sein.In this case, the switching interval SI can be the same in all partial load ranges.
Es ist aber auch denkbar das Schaltintervall SI entweder proportional oder in einzelnen Schritten abhängig von der Drehzahl der Exzenterwelle 54 und somit des Elektromotors 55 zu variieren.However, it is also conceivable to vary the switching interval SI either proportionally or in individual steps depending on the rotational speed of the
Beispielsweise erfolgt die Variation des Schaltintervalls SI so, dass bei kleiner Drehzahl des Elektromotors die Schaltintervalle SI lang und bei großer Drehzahl des Elektromotors die Schaltintervalle kürzer sind.For example, the variation of the switching interval SI occurs so that at low speed of the electric motor, the switching intervals SI are long and at high speed of the electric motor, the switching intervals are shorter.
Der Vorteil der erfindungsgemäßen Lösung ist darin zu sehen, dass bei den Hubkolbenverdichter die Leistungsaufnahme proportional zum Massendurchsatz ist und somit bei einer Reduzierung des Massendurchsatzes durch aufeinanderfolgende Öffnungsintervalle O und Schließintervalle S im Teillastbereich die Möglichkeit besteht, auch die Leistungsaufnahme des Hubkolbenverdichters zu reduzieren.The advantage of the solution according to the invention is the fact that in the reciprocating compressor, the power consumption is proportional to the mass flow and thus with a reduction of the mass flow through successive opening intervals O and closing intervals S in the partial load range, the possibility to reduce the power consumption of the reciprocating compressor.
Außerdem schafft die erfindungsgemäße Lösung die Möglichkeit, den Anlaufvorgang des Kältemittelverdichters 12 durch Steuerung des Massendurchsatzes so zu gestalten, dass die Risiken aus auskochendem Kältemittel minimiert werden.In addition, the solution according to the invention makes it possible to configure the start-up process of the
Claims (23)
- Refrigerant compressor for refrigerating systems comprising
at least one cylinder unit (44), which has a cylinder housing (46) and a piston (48) which can move in an oscillating manner in the cylinder housing (46), a cylinder head (58), with an inlet chamber (72), flowed through by an inlet flow (74) of the at least one cylinder unit (44), and with an outlet chamber (88), passed through by an outlet flow (86) of the at least one cylinder unit (44), and a switching valve (70) for interrupting the inlet flow (74),
characterized in that a control (130) for activating the switching valve (70) is provided, which control, for operating the refrigerant compressor (12) in a lower part-load range, operates the switching valve (70) in successive switching intervals (SI), respectively comprising an opening interval (O) and a closing interval (S) of the switching valve (70), which are shorter than a shortest time period (Z) after which a temperature (T) of an evaporator (32) in the operating refrigerating system (10) has risen by approximately 10% during an interruption of the inlet flow (74). - Refrigerant compressor according to the precharacterizing clause of Claim 1 or according to Claim 1, characterized in that a control (130) for activating the switching valve (70) is provided, which control, for operating the refrigerant compressor (12) in a lower part-load range, operates the switching valve (70) in successive switching intervals (SI) which are shorter than approximately 10 seconds.
- Refrigerant compressor according to Claim 2, characterized in that the switching intervals (SI) are shorter than approximately 2 seconds.
- Refrigerant compressor according to one of the preceding claims, characterized in that the switching intervals (SI) are longer than approximately 0.02 seconds.
- Refrigerant compressor according to Claim 4, characterized in that the switching intervals (SI) are longer than approximately 0.05 seconds.
- Refrigerant compressor according to Claim 5, characterized in that the switching intervals (SI) are longer than approximately 0.1 seconds.
- Refrigerant compressor according to one of the preceding claims, characterized in that the switching intervals (SI) correspond to a switching frequency which is less than an inherent frequency of the switching valve (70).
- Refrigerant compressor according to Claim 7, characterized in that the switching intervals (SI) correspond to a switching frequency which is less than an inherent frequency of the switching valve (70) by more than a factor of 5.
- Refrigerant compressor according to one of the preceding claims, characterized in that, in the lower part-load range, the control (130) operates all the cylinder units (44) in the switching intervals (SI).
- Refrigerant compressor according to Claim 9, characterized in that the control (130) operates all the cylinder units (44) in the switching intervals (SI) in the entire part-load range.
- Refrigerant compressor according to one of the preceding claims, characterized in that the control (130) operates with switching intervals (SI) that are of a constant time.
- Refrigerant compressor according to one of the preceding claims, characterized in that the control (130) varies the switching intervals (SI) on the basis of a rotational drive speed of the refrigerant compressor (12).
- Refrigerant compressor according to one of the preceding claims, characterized in that the switching valve (70) is a servo valve.
- Refrigerant compressor according to Claim 13, characterized in that the servo valve (70) comprises a valve body (90) which can be actuated by a pressure associated with the pressure in the outlet chamber (88).
- Refrigerant compressor according to Claim 14, characterized in that the valve body (90) is acted upon by an elastic force accumulator (120) acting counter to the effect of the pressure on the valve body (90).
- Refrigerant compressor according to either of Claims 14 and 15, characterized in that the valve body (90) is coupled to a switching piston (94) which can be acted upon by a pressure associated with the pressure in the outlet chamber (88) and is guided in a switching cylinder housing (96).
- Refrigerant compressor according to one of Claims 14 to 16, characterized in that the switching piston (94) and the switching cylinder housing (96) enclose a switching cylinder chamber (98) and in that the pressure in the switching cylinder chamber is controllable.
- Refrigerant compressor according to one of Claims 14 to 17, characterized in that the valve body (90) and the switching piston form a unit which is guided in the switching cylinder housing (96).
- Refrigerant compressor according to one of Claims 13 to 18, characterized in that the servo valve (70) comprises a control valve (110) which can be activated by the control (130).
- Refrigerant compressor according to Claim 19, characterized in that the control valve (110) opens or closes the connecting channel (116, 118) between the switching cylinder chamber (98) and the outlet chamber (88).
- Refrigerant compressor according to one of Claims 15 to 20, characterized in that the inherent frequency of the unit comprising the switching piston (94), valve body (90) and elastic force accumulator (120) corresponds at least to the inherent frequency of the switching valve (70).
- Refrigerant compressor according to one of Claims 14 to 21, characterized in that the switching piston is produced from a lightweight structural material.
- Refrigerant compressor according to one of Claims 14 to 22, characterized in that the switching piston (94') is formed as a hollow body.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SI200630009T SI1710435T1 (en) | 2005-04-05 | 2006-03-23 | Refrigerant compressor |
PL06005929T PL1710435T3 (en) | 2005-04-05 | 2006-03-23 | Refrigerant compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005016433A DE102005016433A1 (en) | 2005-04-05 | 2005-04-05 | Refrigerant compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1710435A1 EP1710435A1 (en) | 2006-10-11 |
EP1710435B1 true EP1710435B1 (en) | 2007-08-22 |
EP1710435B2 EP1710435B2 (en) | 2023-06-07 |
Family
ID=36371025
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06005929.2A Active EP1710435B2 (en) | 2005-04-05 | 2006-03-23 | Refrigerant compressor |
Country Status (10)
Country | Link |
---|---|
US (1) | US20060218959A1 (en) |
EP (1) | EP1710435B2 (en) |
CN (1) | CN100523671C (en) |
AT (1) | ATE371111T1 (en) |
DE (2) | DE102005016433A1 (en) |
DK (1) | DK1710435T3 (en) |
ES (1) | ES2290930T5 (en) |
PL (1) | PL1710435T3 (en) |
PT (1) | PT1710435E (en) |
SI (1) | SI1710435T1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012107183A1 (en) | 2012-08-06 | 2014-05-15 | Kriwan Industrie-Elektronik Gmbh | Method for controlling reciprocating piston compressor of refrigeration system, involves controlling temperature of cooling location, and converting manipulated variable into switching signal for clocked opening and closing of valves |
US9746227B2 (en) | 2012-08-06 | 2017-08-29 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system, and refrigeration system |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6047557A (en) | 1995-06-07 | 2000-04-11 | Copeland Corporation | Adaptive control for a refrigeration system using pulse width modulated duty cycle scroll compressor |
US6206652B1 (en) | 1998-08-25 | 2001-03-27 | Copeland Corporation | Compressor capacity modulation |
US8157538B2 (en) | 2007-07-23 | 2012-04-17 | Emerson Climate Technologies, Inc. | Capacity modulation system for compressor and method |
WO2010019582A2 (en) * | 2008-08-12 | 2010-02-18 | Carrier Corporation | Dedicated pulsing valve for compressor cylinder |
ES2623055T3 (en) | 2009-01-27 | 2017-07-10 | Emerson Climate Technologies, Inc. | System and discharge method for a compressor |
ES2734298T3 (en) | 2009-07-20 | 2019-12-05 | Carrier Corp | Suction disconnect discharge valve for compressor capacity control |
US10378533B2 (en) * | 2011-12-06 | 2019-08-13 | Bitzer Us, Inc. | Control for compressor unloading system |
KR101790545B1 (en) | 2013-02-08 | 2017-10-26 | 가부시키가이샤 히다치 산키시스템 | Fluid compression system and control device therefor |
DE102013101418B4 (en) | 2013-02-13 | 2015-09-10 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor having a motor of a refrigeration system and a compressor of a refrigeration system |
ITMI20130583A1 (en) * | 2013-04-11 | 2014-10-12 | Frascold S P A | COMPRESSOR FOR A REFRIGERATOR SYSTEM AND REFRIGERATING SYSTEM INCLUDING THE COMPRESSOR |
JP5984784B2 (en) * | 2013-11-19 | 2016-09-06 | 三菱電機株式会社 | Hot / cold water air conditioning system |
CN108072201B (en) | 2016-11-11 | 2022-02-01 | 开利公司 | Heat pump system and start control method thereof |
US20230034730A1 (en) * | 2019-12-17 | 2023-02-02 | Officine Mario Dorin S.P.A. | Multi-cylinder reciprocating compressor |
DE102020103975A1 (en) * | 2020-02-14 | 2021-08-19 | Bitzer Kühlmaschinenbau Gmbh | Refrigerant compressor |
DE102020118740A1 (en) * | 2020-07-15 | 2022-01-20 | Bitzer Kühlmaschinenbau Gmbh | refrigerant compressor |
DE102021117724A1 (en) * | 2021-07-08 | 2023-01-12 | Bitzer Kühlmaschinenbau Gmbh | refrigerant compressor group |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2618440A1 (en) * | 1976-04-27 | 1977-11-10 | Sullair Europ Corp | METHOD AND DEVICE FOR CONTROLLING THE OPERATION OF A COMPRESSOR |
US5189886A (en) * | 1987-09-22 | 1993-03-02 | Sanden Corporation | Refrigerating system having a compressor with an internally and externally controlled variable displacement mechanism |
JPH0667686B2 (en) * | 1987-10-26 | 1994-08-31 | 株式会社ゼクセル | Vehicle air conditioning controller |
US4878818A (en) * | 1988-07-05 | 1989-11-07 | Carrier Corporation | Common compression zone access ports for positive displacement compressor |
JP2875087B2 (en) * | 1992-01-09 | 1999-03-24 | 株式会社日立製作所 | refrigerator |
DE4212162C2 (en) * | 1992-04-10 | 1994-02-17 | Ilka Maschinenfabrik Halle Gmb | Device for cooling the electric motor of a semi-hermetic refrigerant compressor |
US5507316A (en) * | 1994-09-15 | 1996-04-16 | Eaton Corporation | Engine hydraulic valve actuator spool valve |
US6047557A (en) * | 1995-06-07 | 2000-04-11 | Copeland Corporation | Adaptive control for a refrigeration system using pulse width modulated duty cycle scroll compressor |
US6206652B1 (en) * | 1998-08-25 | 2001-03-27 | Copeland Corporation | Compressor capacity modulation |
US6047556A (en) * | 1997-12-08 | 2000-04-11 | Carrier Corporation | Pulsed flow for capacity control |
DE19918161A1 (en) * | 1999-04-22 | 2000-11-02 | Bitzer Kuehlmaschinenbau Gmbh | Refrigerant compressor system |
EP1287298B1 (en) * | 2000-06-07 | 2006-11-15 | Samsung Electronics Co., Ltd. | Control system of degree of superheat of air conditioner and control method thereof |
CN1184440C (en) * | 2001-02-16 | 2005-01-12 | 三星电子株式会社 | Air conditioner and method of controlling the same |
US6792975B2 (en) * | 2001-05-24 | 2004-09-21 | Borgwarner Inc. | Pulse-width modulated solenoid valve including axial stop spool valve |
JP3841039B2 (en) * | 2002-10-25 | 2006-11-01 | 株式会社デンソー | Air conditioner for vehicles |
JP3948432B2 (en) * | 2003-05-16 | 2007-07-25 | 株式会社豊田自動織機 | Control device for variable capacity compressor |
DE112004002149D2 (en) * | 2003-09-02 | 2006-07-13 | Luk Fahrzeug Hydraulik | Compressor or air conditioning |
-
2005
- 2005-04-05 DE DE102005016433A patent/DE102005016433A1/en not_active Ceased
-
2006
- 2006-03-23 PT PT06005929T patent/PT1710435E/en unknown
- 2006-03-23 ES ES06005929T patent/ES2290930T5/en active Active
- 2006-03-23 AT AT06005929T patent/ATE371111T1/en not_active IP Right Cessation
- 2006-03-23 EP EP06005929.2A patent/EP1710435B2/en active Active
- 2006-03-23 PL PL06005929T patent/PL1710435T3/en unknown
- 2006-03-23 SI SI200630009T patent/SI1710435T1/en unknown
- 2006-03-23 DK DK06005929T patent/DK1710435T3/en active
- 2006-03-23 DE DE502006000063T patent/DE502006000063D1/en active Active
- 2006-03-30 US US11/393,215 patent/US20060218959A1/en not_active Abandoned
- 2006-04-05 CN CNB2006100732185A patent/CN100523671C/en not_active Ceased
Non-Patent Citations (1)
Title |
---|
None * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012107183A1 (en) | 2012-08-06 | 2014-05-15 | Kriwan Industrie-Elektronik Gmbh | Method for controlling reciprocating piston compressor of refrigeration system, involves controlling temperature of cooling location, and converting manipulated variable into switching signal for clocked opening and closing of valves |
DE102012107183B4 (en) * | 2012-08-06 | 2016-08-04 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system and a refrigeration system |
US9746227B2 (en) | 2012-08-06 | 2017-08-29 | Kriwan Industrie-Elektronik Gmbh | Method for controlling a compressor of a refrigeration system, and refrigeration system |
Also Published As
Publication number | Publication date |
---|---|
ATE371111T1 (en) | 2007-09-15 |
EP1710435B2 (en) | 2023-06-07 |
DK1710435T3 (en) | 2008-01-28 |
DE102005016433A1 (en) | 2006-10-12 |
CN100523671C (en) | 2009-08-05 |
US20060218959A1 (en) | 2006-10-05 |
PL1710435T3 (en) | 2008-01-31 |
DE502006000063D1 (en) | 2007-10-04 |
ES2290930T5 (en) | 2023-11-20 |
SI1710435T1 (en) | 2008-02-29 |
ES2290930T3 (en) | 2008-02-16 |
CN1847757A (en) | 2006-10-18 |
PT1710435E (en) | 2007-09-24 |
EP1710435A1 (en) | 2006-10-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1710435B1 (en) | Refrigerant compressor | |
AT413234B (en) | PISTON COMPRESSOR AND METHOD FOR THE STAGE-FREE DELIVERY RATE CONTROL THEREOF | |
DE69928055T2 (en) | Supply control of a compressor | |
DE10203703B4 (en) | Piston compressor with electromagnetic linear motor | |
EP1886075B1 (en) | Refrigeration plant | |
DE112005003132B4 (en) | Kroygener cooler with reduced input power | |
EP0694693B1 (en) | Method and device for valve control | |
DE1628144C3 (en) | Suction throttle control device | |
DE3022661C2 (en) | ||
DE4218631C2 (en) | Cooling compressor with a profiled piston | |
DE1428008C3 (en) | Device for compressing or relaxing an agent, which is provided with a control device for regulating the size of the harmful volume | |
EP1072796B1 (en) | Process for operating a screw-type compressor | |
DE3446480C2 (en) | Gas chiller | |
DE102008004569A1 (en) | reciprocating | |
DE10222846B4 (en) | Device for fluid compression | |
DE3248086C2 (en) | Fuel injection pumps for internal combustion engines, in particular for diesel engines | |
EP2483559A2 (en) | Multi-stage diaphragm suction pump | |
EP4103840A1 (en) | Coolant compressor | |
EP1967706B1 (en) | Valve gear | |
EP2189645A2 (en) | Stirling machine | |
DE102004048940A1 (en) | Method for controlling the operation of a chiller system has the suction chamber of the piston type compressor periodically isolated by a pulse width modulated control signal | |
DE3210110A1 (en) | Diaphragm pump | |
EP4116586A1 (en) | Refrigerant compressor assembly | |
AT152717B (en) | Method and device for the stepless regulation of compressors. | |
DE1935834C3 (en) | Arrangement for regulating the output of a compression refrigeration machine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
17P | Request for examination filed |
Effective date: 20061124 |
|
17Q | First examination report despatched |
Effective date: 20061222 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
AKX | Designation fees paid |
Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: PT Ref legal event code: SC4A Free format text: AVAILABILITY OF NATIONAL TRANSLATION Effective date: 20070911 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: KIRKER & CIE S.A. |
|
REF | Corresponds to: |
Ref document number: 502006000063 Country of ref document: DE Date of ref document: 20071004 Kind code of ref document: P |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20071017 |
|
REG | Reference to a national code |
Ref country code: RO Ref legal event code: EPE |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
REG | Reference to a national code |
Ref country code: GR Ref legal event code: EP Ref document number: 20070403315 Country of ref document: GR |
|
REG | Reference to a national code |
Ref country code: DK Ref legal event code: T3 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20070822 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20071222 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CZ Payment date: 20071220 Year of fee payment: 3 |
|
REG | Reference to a national code |
Ref country code: PL Ref legal event code: T3 |
|
ET | Fr: translation filed | ||
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2290930 Country of ref document: ES Kind code of ref document: T3 |
|
REG | Reference to a national code |
Ref country code: HU Ref legal event code: AG4A Ref document number: E002340 Country of ref document: HU |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20070822 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BG Payment date: 20080324 Year of fee payment: 3 Ref country code: FI Payment date: 20080307 Year of fee payment: 3 Ref country code: HU Payment date: 20080115 Year of fee payment: 3 Ref country code: LU Payment date: 20080314 Year of fee payment: 3 Ref country code: PT Payment date: 20071217 Year of fee payment: 3 Ref country code: SE Payment date: 20080318 Year of fee payment: 3 Ref country code: SI Payment date: 20080311 Year of fee payment: 3 |
|
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
PLAX | Notice of opposition and request to file observation + time limit sent |
Free format text: ORIGINAL CODE: EPIDOSNOBS2 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: RO Payment date: 20080122 Year of fee payment: 3 Ref country code: AT Payment date: 20080107 Year of fee payment: 3 |
|
26 | Opposition filed |
Opponent name: EMERSON CLIMATE TECHNOLOGIES, INC. Effective date: 20080523 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20080205 Year of fee payment: 3 |
|
NLR1 | Nl: opposition has been filed with the epo |
Opponent name: EMERSON CLIMATE TECHNOLOGIES, INC. |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080331 |
|
PLAF | Information modified related to communication of a notice of opposition and request to file observations + time limit |
Free format text: ORIGINAL CODE: EPIDOSCOBS2 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20070822 |
|
PLBB | Reply of patent proprietor to notice(s) of opposition received |
Free format text: ORIGINAL CODE: EPIDOSNOBS3 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DK Payment date: 20090327 Year of fee payment: 4 Ref country code: IE Payment date: 20090309 Year of fee payment: 4 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: PL Payment date: 20090121 Year of fee payment: 4 Ref country code: SK Payment date: 20090114 Year of fee payment: 4 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20070822 |
|
BERE | Be: lapsed |
Owner name: BITZER KUHLMASCHINENBAU G.M.B.H. Effective date: 20090331 |
|
REG | Reference to a national code |
Ref country code: PT Ref legal event code: MM4A Free format text: LAPSE DUE TO NON-PAYMENT OF FEES Effective date: 20090923 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090323 Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090323 Ref country code: FI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090323 Ref country code: PT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090923 |
|
EUG | Se: european patent has lapsed | ||
NLV4 | Nl: lapsed or anulled due to non-payment of the annual fee |
Effective date: 20091001 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090323 Ref country code: HU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090324 |
|
REG | Reference to a national code |
Ref country code: SI Ref legal event code: KO00 Effective date: 20091215 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090324 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090331 Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20091001 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: DK Ref legal event code: EBP |
|
REG | Reference to a national code |
Ref country code: SK Ref legal event code: MM4A Ref document number: E 2569 Country of ref document: SK Effective date: 20100323 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100323 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100331 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100331 Ref country code: SK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100323 |
|
RDAF | Communication despatched that patent is revoked |
Free format text: ORIGINAL CODE: EPIDOSNREV1 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090331 Ref country code: GR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20101004 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090323 Ref country code: DK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100331 |
|
APBM | Appeal reference recorded |
Free format text: ORIGINAL CODE: EPIDOSNREFNO |
|
APBP | Date of receipt of notice of appeal recorded |
Free format text: ORIGINAL CODE: EPIDOSNNOA2O |
|
APAH | Appeal reference modified |
Free format text: ORIGINAL CODE: EPIDOSCREFNO |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090324 |
|
APBQ | Date of receipt of statement of grounds of appeal recorded |
Free format text: ORIGINAL CODE: EPIDOSNNOA3O |
|
REG | Reference to a national code |
Ref country code: PL Ref legal event code: LAPE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100323 |
|
APBU | Appeal procedure closed |
Free format text: ORIGINAL CODE: EPIDOSNNOA9O |
|
PLAY | Examination report in opposition despatched + time limit |
Free format text: ORIGINAL CODE: EPIDOSNORE2 |
|
PLAH | Information related to despatch of examination report in opposition + time limit modified |
Free format text: ORIGINAL CODE: EPIDOSCORE2 |
|
PLBC | Reply to examination report in opposition received |
Free format text: ORIGINAL CODE: EPIDOSNORE3 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502006000063 Country of ref document: DE Representative=s name: HOEGER, STELLRECHT & PARTNER PATENTANWAELTE MB, DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160323 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 12 |
|
PLAB | Opposition data, opponent's data or that of the opponent's representative modified |
Free format text: ORIGINAL CODE: 0009299OPPO |
|
R26 | Opposition filed (corrected) |
Opponent name: EMERSON CLIMATE TECHNOLOGIES, INC. Effective date: 20080523 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160323 |
|
PGRI | Patent reinstated in contracting state [announced from national office to epo] |
Ref country code: IT Effective date: 20170710 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 13 |
|
RDAD | Information modified related to despatch of communication that patent is revoked |
Free format text: ORIGINAL CODE: EPIDOSCREV1 |
|
RDAE | Information deleted related to despatch of communication that patent is revoked |
Free format text: ORIGINAL CODE: EPIDOSDREV1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
RDAF | Communication despatched that patent is revoked |
Free format text: ORIGINAL CODE: EPIDOSNREV1 |
|
APAH | Appeal reference modified |
Free format text: ORIGINAL CODE: EPIDOSCREFNO |
|
APBM | Appeal reference recorded |
Free format text: ORIGINAL CODE: EPIDOSNREFNO |
|
APBP | Date of receipt of notice of appeal recorded |
Free format text: ORIGINAL CODE: EPIDOSNNOA2O |
|
APBQ | Date of receipt of statement of grounds of appeal recorded |
Free format text: ORIGINAL CODE: EPIDOSNNOA3O |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170808 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502006000063 Country of ref document: DE Representative=s name: HOEGER, STELLRECHT & PARTNER PATENTANWAELTE MB, DE |
|
RAP2 | Party data changed (patent owner data changed or rights of a patent transferred) |
Owner name: BITZER KUEHLMASCHINENBAU GMBH |
|
APBU | Appeal procedure closed |
Free format text: ORIGINAL CODE: EPIDOSNNOA9O |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R081 Ref document number: 502006000063 Country of ref document: DE Owner name: BITZER KUEHLMASCHINENBAU GMBH, DE Free format text: FORMER OWNER: BITZER KUEHLMASCHINENBAU GMBH, 71065 SINDELFINGEN, DE |
|
PUAH | Patent maintained in amended form |
Free format text: ORIGINAL CODE: 0009272 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: PATENT MAINTAINED AS AMENDED |
|
27A | Patent maintained in amended form |
Effective date: 20230607 |
|
AK | Designated contracting states |
Kind code of ref document: B2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R102 Ref document number: 502006000063 Country of ref document: DE |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230517 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: DC2A Ref document number: 2290930 Country of ref document: ES Kind code of ref document: T5 Effective date: 20231120 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230908 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240328 Year of fee payment: 19 Ref country code: GB Payment date: 20240319 Year of fee payment: 19 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: TR Payment date: 20240305 Year of fee payment: 19 Ref country code: IT Payment date: 20240321 Year of fee payment: 19 Ref country code: FR Payment date: 20240326 Year of fee payment: 19 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20240412 Year of fee payment: 19 |