EP3126672B1 - Compresseur à piston alternatif et procédé de régulation dudit compresseur - Google Patents

Compresseur à piston alternatif et procédé de régulation dudit compresseur Download PDF

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Publication number
EP3126672B1
EP3126672B1 EP15722044.3A EP15722044A EP3126672B1 EP 3126672 B1 EP3126672 B1 EP 3126672B1 EP 15722044 A EP15722044 A EP 15722044A EP 3126672 B1 EP3126672 B1 EP 3126672B1
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EP
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Prior art keywords
volume
reciprocating
compressor
piston compressor
connection
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German (de)
English (en)
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EP3126672A1 (fr
Inventor
Martin Schaich
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Bock GmbH
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GEA Bock GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • F04B49/10—Other safety measures
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type

Definitions

  • the present invention relates to a reciprocating compressor according to the preamble of patent claim 1, as well as a reciprocating compressor having refrigeration or air conditioning or a Hubkolbenverêtr having heat pump according to claims 6 and 7. Furthermore, in the thought of the present invention, a corresponding control method is included.
  • Refrigeration systems are often operated with reciprocating compressors. Examples of this can be found inter alia in the field of bus air conditioning, where in a corresponding refrigeration system (air conditioning) a reciprocating compressor is arranged, which is driven by the crankshaft of the drive motor via a belt drive and a magnetic coupling. The compressor can be switched on and off via the magnetic coupling. However, the shut-off and shut-off affects the entire compressor and thus the entire power output of the compressor (100% on-off).
  • Other examples can be found in the field of mobile and stationary air conditioning, mobile and stationary refrigeration, so for example in the field of transport refrigeration and supermarket refrigeration, and in the field of heat pumps.
  • connection and disconnection causes a transient operation of the compressor and leads also to high peak loads in its drive.
  • the switching frequency is basically limited by the masses to be moved and the switching work of the clutch.
  • compressors for example, four-cylinder reciprocating compressors are predominantly used in the field of bus air conditioning, in which two individual cylinder banks are arranged in V-construction.
  • other reciprocating compressors with any number of cylinders are used, wherein the cylinders may be arranged in cylinder banks or may be divided into such or not.
  • compressors are constantly operated at a rotational speed corresponding to the driving operation, which does not coincide with a rotational speed at which the compressor would produce the desired cooling capacity. For this reason, there is a continuous need for correction of the cooling or cooling capacity.
  • a reciprocating compressor of the prior art is in US3119550 disclosed. It shows a reciprocating compressor with a control device having an input for supplying input information, in particular suction or high pressure of a corresponding compressor, and at least one output for controlling a control element, the reciprocating compressor a shut-off device, in particular a valve, further in particular a check valve which, viewed in a flow direction of the refrigerant during normal operation of the reciprocating compressor, is arranged downstream of the high-pressure volume.
  • the reciprocating compressor has at least one suction gas volume and at least one high-pressure volume, wherein a connection between the at least one suction gas volume and the at least one high-pressure volume of the reciprocating compressor is formed.
  • the at least one suction gas volume and the at least one high-pressure volume are integrated in the Hubkobenverêtr. Accordingly, it is an object of the present invention to provide a reciprocating compressor for a variety of applications, such as refrigeration, air conditioning, or heat pump applications, which has over the prior art, an increased control quality. It is another object of the present invention to provide corresponding systems, as well as a corresponding control method. This object is achieved by a reciprocating compressor according to claim 1.
  • the second aspect of the problem is solved by systems according to claims 6 and 7.
  • the procedural aspect of the problem is solved by a method according to claim 8.
  • a corresponding reciprocating compressor has a control device which is provided for particular stepless control of a capacity of the reciprocating compressor and which has an input for supplying input information, in particular a suction pressure or a high pressure of the compressor, and at least one output for controlling a control element.
  • the control device is designed to generate a digital output signal, wherein the control element has a digitally controllable control valve.
  • the reciprocating compressor has at least one suction gas volume and at least one high-pressure volume, wherein a connection between the at least one suction gas volume and the at least one high-pressure volume of the refrigeration system is formed, and wherein the digitally controllable control valve is arranged in the connection.
  • the reciprocating compressor further comprises a shut-off device, in particular a valve, further in particular a check valve, which, viewed in a flow direction of the refrigerant during normal operation of the compressor, downstream of the one / each associated high-pressure volume is arranged.
  • the at least one suction gas volume and the at least one high-pressure volume and the control valve are integrated in the reciprocating compressor.
  • the connection between the high-pressure volume and the suction volume of the compressor can be at simultaneously closing one of the high pressure side associated and downstream in the operating flow direction of the refrigerant the high pressure volume shut-off, resulting in the two aforementioned volumes associated piston or cylinder banks or possibly all cylinders or cylinder banks of the compressor in a state of zero promotion of refrigerant spend.
  • the object is achieved by devices according to claim 6 or 7, which have a corresponding reciprocating compressor.
  • the compressor can be controlled virtually continuously from 100% to preferably about 10% of its nominal delivery volume or its maximum delivery volume.
  • a digitally controllable valve is included as a control valve for the flow rate of a reciprocating compressor in a control device for a refrigeration system.
  • a refrigeration system or air conditioning system 1 in the form of a bus climate system 1 comprises, as essential components, a compressor 10 for compressing refrigerant, which is designed as a reciprocating compressor, and a control device 12, which controls a control 14 and a control device in the form of a shut-off device a valve 16.
  • a compressor 10 for compressing refrigerant which is designed as a reciprocating compressor
  • a control device 12 which controls a control 14 and a control device in the form of a shut-off device a valve 16.
  • the areas stationary and mobile refrigeration as well as the area of heat pumps are mentioned by way of example.
  • the control device 12 further comprises an input 18 for supplying input information, which in the presently described embodiment is represented by a suction pressure of the compressor 10, and an output 20 for controlling the control element (valve 16), as well as a delivery volume determining device for determining a desired Delivery volume in response to an input signal applied to the input 18 and for generating a corresponding output 20 to be supplied to the output signal on.
  • the input is preferably the suction pressure of the compressor 10
  • the input is in the case of heat pumps, for example, preferably the high pressure, ie the pressure which rests against the high-pressure side of the compressor 10.
  • the control device 12 is configured to generate a digital output signal.
  • the valve 16 which regulates the delivery volume of the compressor 10, designed as a digitally controllable electromagnetic valve.
  • other types of valve in particular electromechanical or else mechanically, pneumatically or hydraulically operable valves or other shut-off devices (slides and the like.) are conceivable.
  • the refrigeration system 1 has a suction gas volume 22 and a high pressure volume 24, wherein the suction gas volume 22 is arranged upstream of the cylinders of the compressor 10, and the high pressure volume 24 is arranged downstream of the cylinders of the compressor 10, the direction determinations upstream and downstream in a normal operation of the Refrigeration system 1 are defined by the flow direction of the refrigerant.
  • a connection 26 in the form of a bore or recess, for example in the housing of the compressor 10 or as a pipe, wherein the digitally controllable valve 16 is arranged in the connection 26 and open and interrupt or can close.
  • the refrigeration system 1 further has a second shut-off device in the form of a check valve 28 (second valve), which is arranged downstream of the high-pressure volume 24. It is instead of a check valve 26, any other shut-off device (slide, valve, for example, electromechanically actuated or solenoid-operated or pneumatically actuated valve, or a diaphragm or the like.) Possible.
  • a check valve 28 second valve
  • any other shut-off device (slide, valve, for example, electromechanically actuated or solenoid-operated or pneumatically actuated valve, or a diaphragm or the like.) Possible.
  • the suction gas volume 22 and the high-pressure volume 24 are connected to each other through the above-mentioned connection 26, for example piping (bypass line), which can be opened and closed by the digitally controllable valve 16 such that the suction gas volume 22 and the high-pressure volume 24 directly into each other (Fluid) connection stand when the valve 16 is in an open position.
  • connection 26 for example piping (bypass line)
  • piping bypass line
  • valve 16 If the valve 16 is in a closed position, there is no direct connection between suction gas volume 22 and high-pressure volume 24.
  • the compressor 10 is in normal operation (cf. Fig. 3 ), in which refrigerant is conducted from the suction gas volume 22 into the cylinders, is compressed therein, and then discharged into the high pressure volume 24 and provided to the bus air conditioning system 1 (the path of the refrigerant is indicated by arrows, respectively).
  • valve 16 when the valve 16 is in its open position (see also Fig. 4 In an open position of the valve 16, the check valve 28 closes by the high pressure and thus keeps the high pressure away from the working spaces of the compressor. Thus, the absorbed power of the compressor drops to the unavoidable value, which arises from the internal losses of the compressor, for example at the working valves.
  • another shut-off device is closed, for example, by the control device 12.
  • the compressor 10 is "turned off” because the conveyed through the cylinder refrigerant flows from the high-pressure volume 24 back into the suction gas volume 22 and from there in turn into the cylinder and then turn enters the high-pressure volume 24.
  • the opening duration of the valve 16 can be carried out by the control device 12 in an arbitrary, continuously variable clocking, so that a delivery rate of the compressor 10 of basically 0% to 100% is infinitely variable or nearly infinitely variable.
  • the control device 12 is configured to provide a minimum displacement of 5% to 10% to cool the compressor 10. For air-cooled compressors only, this can be dispensed with.
  • the described refrigeration system 1 has a condenser 30, an expansion element in the form of an expansion valve 32 and an evaporator 34 for air conditioning the vehicle (bus) 36 / for cooling the volume to be cooled.
  • the described embodiment of a refrigeration system 1 has the suction gas volume 22 and the high-pressure volume 24 integrated in the compressor 10.
  • the connection 26 between the suction gas side and the high-pressure side is preferably formed between the suction gas volume 22 and the high-pressure volume 24 in the form of a channel (alternatively as a bore or as a recess formed in the casting of the corresponding components, alternatively also as a pipeline).
  • the valve 16 is arranged in the connection 26 (channel) as in the above-described embodiment, and thus also integrated in the compressor 10.
  • a compressor 10 of a second embodiment of a refrigeration system according to the invention which is also designed as a reciprocating cylinder, two cylinder groups in the form of two cylinder banks 40 (the cylinders need not necessarily be grouped as cylinder banks 40, other criteria for grouping are conceivable).
  • the refrigeration system 1, more precisely the reciprocating compressor 10 of the refrigeration system 1 has per cylinder bank 40 (in alternative embodiments per cylinder group or per cylinder) a suction gas volume 22 for feeding the respective cylinder bank 40 with refrigerant and a high-pressure volume 24 for discharging the refrigerant.
  • the respective volumes of suction gas 22 are disposed upstream of the respective cylinder banks 40 associated therewith, while the respective high pressure volumes 24 are located downstream of the respective associated cylinder banks 40.
  • the suction gas volumes 22 and the high-pressure volumes 24 are disposed within the compressor 10, ie, integrated therein.
  • a compound 26 is formed, which connects the two volumes together.
  • a digitally controllable valve 16 is arranged.
  • An analogous construction is realized for the second cylinder bank 40 associated volumes.
  • a further (second) connection 26 is formed, which connects the two volumes together.
  • a digitally controllable valve (third valve) 16 is arranged.
  • the connections 26 are formed as pipelines.
  • valves 16 are formed analogously to the valve 16 already described in the first and second embodiments and may also be substituted by any other shut-off device, wherein at least one of the shut-off devices must be digitally controllable in order to obtain the desired control precision. It would alternatively also be conceivable that only one cylinder bank 40 assigned volumes a connection 26 (for example, pipe or channel) is provided. The valves 16 are controlled by the control device 12. Also in this embodiment, both the compound (s) 26 and the high-pressure volumes and volumes of suction gas are integrated in the compressor 10.
  • a shutdown and connection of individual cylinder groups take place. It is therefore proposed to actuate cylinder banks 40 or cylinder groups, possibly also individual cylinders, with a quickly switchable controllability.
  • the compressor 10 can be controlled steplessly or virtually continuously or in any increments from 100% to approximately 10%, the lower limit being determined thermally and by the oil balance of the compressor 10.
  • the shift of the Zylinderbänke40 or cylinder groups, possibly also individual cylinders can be carried out asynchronously, so that the time of total zero promotion can be limited.
  • the compound (s) 26 and / or the valve (s) 16 and / or the volumes of suction gas (or volumes) and / or the high pressure volume (s) are located outside the compressor. This is a simple construction, but may be energetically somewhat less effective than the embodiments described above, since in particular the Hoch horrv and the high-pressure volumes are greater than those described above Embodiments.
  • the components in the compressor uncomplicated installation and also an uncomplicated design by the manufacturer of the respective air conditioning or refrigeration system or heat pump, etc. possible.
  • a possible control is: with a desired refrigerant delivery corresponding to 50-100% of the rated power clocked a cylinder bank 40 up to the complete shutdown (at 50%); with a desired refrigerant delivery corresponding to 50-10% of the nominal capacity both banks clock with increasing overlap. At 10%, e.g. each bank in turn 6s per minute.
  • the starting torque of the compressor 10 can be limited by, for example, all cylinders are switched off at start. This makes it possible to limit the size of couplings and also drives, are driven by the corresponding compressor 10 in the rule. Also, the torque can generally be controlled and limited in order to protect the clutch in operation against a possible overload.
  • Another possibility is to switch off one or more cylinder banks 40 or cylinder groups or cylinders each time the clutch is switched on. This reduces the switching work of the clutch. This possibility exists even when switching off the compressor 10, so that even when the compressor 10 is separated from the drive, the torque is reduced.
  • the inventive method is used to control a reciprocating compressor 10, for example, a refrigeration or air conditioning 1 or a heat pump, the control of the refrigeration system 1 is accomplished by controlling the flow rate of the compressor 10.
  • the control of the flow rate is performed by at least one digital signal .
  • the digital signal or digital signals can be supplied to one or more digitally controllable control valve (s) 16.
  • the refrigeration system 1 has at least one suction gas volume 22 and at least one high-pressure volume 24, wherein a connection 26 is formed between the at least one suction gas volume 22 and the at least one high-pressure volume 24 of the reciprocating compressor 10, wherein the regulation of the delivery rate of the compressor 10 by a Open and close the connection 26 controlled by the digital signal, in particular by means of the digitally controllable control valve 16 takes place.
  • the refrigeration system can have a plurality of cylinder groups, in particular cylinder banks 40, and more than one suction gas volume 22, in particular a suction gas volume 22 for each cylinder group, and more than one high pressure volume 24, in particular a high pressure volume 24 for each cylinder group, wherein at least one connection 26 between one of the suction gas volumes 22 and a corresponding high pressure volume 24 of the refrigeration system 1 is formed.
  • the control of the delivery rate of the compressor 10 is effected by opening and closing the connection 26 controlled by the digital signal, in particular by means of the digitally controllable control valve 16.
  • connection 26 is formed between each of the suction gas volumes 22 and each corresponding high-pressure volume 24 of the refrigeration system 1, wherein the control of the delivery rate of the compressor 10 is controlled by opening and closing the connections 26 controlled by the digital signal, in particular by means of digitally controllable control valves 16.
  • the opening and closing of connections 26 assigned to different cylinder groups preferably takes place asynchronously during operation of the refrigeration system 1.
  • a method for controlling a reciprocating compressor 10 which, as already explained, has a control device 12 and is provided for compressing refrigerant.
  • the regulation of the reciprocating compressor 10 is accomplished by controlling the capacity of the compressor 10, wherein the control of the flow rate is performed by at least one digital signal, wherein the digital signal or digital signals one or more digitally controllable control valve (s) 16 is fed.
  • Der reciprocating compressor 10 has at least one suction gas volume 22 and at least one high pressure volume 24, wherein a connection between the at least one suction gas volume 22 and the at least one high pressure volume 24 of the refrigeration system is formed, wherein the control of the capacity of the compressor controlled by opening and closing the connection by the digital signal is carried out in particular by means of the digitally controllable control valve 16.
  • the reciprocating compressor 10 has a shut-off device 28, which, viewed in a flow direction of the refrigerant during normal operation of the reciprocating compressor 10, downstream of the high-pressure volume 24 is arranged, wherein the shut-off device 28 is closed when the connection 26 is opened, and wherein the shut-off device 28 is open when the connection 26 is closed.
  • the control device controls one or more control valves such that a delivery volume of 5% to 10% of the nominal delivery volume or maximum delivery volume of the compressor 10 is provided as a minimum delivery volume and / or that 100% of the nominal delivery or nominal delivery volume or the maximum Delivery volume or the maximum capacity is provided as a maximum delivery volume. Between the minimum delivery volume and the maximum delivery volume is preferably varied or regulated continuously.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (9)

  1. Compresseur à piston alternatif (10) comprenant un dispositif de réglage (12) qui présente une entrée (18) pour l'apport d'une information d'entrée, en particulier une pression d'aspiration ou une haute pression d'un compresseur correspondant (10), ainsi qu'au moins une sortie (20) pour la commande d'un organe de réglage (16),
    le dispositif de réglage (12) étant réalisé de manière à générer un signal de sortie numérique, l'organe de réglage présentant une soupape de réglage (16) pouvant être commandée numériquement, le compresseur à piston alternatif (10) présentant au moins un volume de gaz d'aspiration (22) et au moins un volume haute pression (24), une connexion (26) étant réalisée entre l'au moins un volume de gaz d'aspiration (22) et l'au moins un volume haute pression (24) du compresseur à piston alternatif (10), la soupape de réglage (16) pouvant être commandée numériquement étant disposée dans la connexion (26),
    le compresseur à piston alternatif (10) présentant un dispositif d'arrêt, en particulier une soupape, notamment un clapet antiretour (28) qui, considéré dans une direction d'écoulement du fluide frigorigène dans le cas d'un fonctionnement normal du compresseur à piston alternatif (10), est disposé en aval du volume haute pression (24), l'au moins un volume de gaz d'aspiration et l'au moins un volume haute pression et la soupape de réglage (16) étant intégrés dans le compresseur à piston alternatif (10),
    le dispositif de réglage (12) étant prévu pour effectuer un réglage en continu, sans paliers, d'une puissance de refoulement du compresseur à piston alternatif (10).
  2. Compresseur à piston alternatif (10) selon la revendication 1,
    dans lequel le compresseur (10) présente plusieurs groupes de cylindres, en particulier des bancs de cylindres (40).
  3. Compresseur à piston alternatif (10) selon la revendication 1 ou 2,
    dans lequel le compresseur à piston alternatif (10) présente plus d'un volume de gaz d'aspiration (22), en particulier un volume de gaz d'aspiration (22) pour chaque groupe de cylindres et plus d'un volume haute pression (24), en particulier un volume haute pression (24) pour chaque groupe de cylindres, au moins une connexion (26) étant réalisée entre l'un des volumes de gaz d'aspiration (22) et un volume haute pression correspondant (24) du compresseur à piston alternatif (10), la/une soupape de régulation (16) pouvant être commandée numériquement étant disposée dans la connexion (26).
  4. Compresseur à piston alternatif (10) selon la revendication 3,
    caractérisé en ce que
    entre chaque volume de gaz d'aspiration (22) et entre chaque volume haute pression (24) correspondant à celui-ci est réalisée une connexion (26), une soupape de régulation (16) pouvant être commandée numériquement étant disposée dans la connexion respective (26).
  5. Compresseur à piston alternatif (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le compresseur à piston alternatif (10), en particulier le dispositif de réglage (12), est réalisé de manière à régler le volume de refoulement du compresseur (10) de 5 %, en particulier de 10 % d'une puissance de refoulement nominale ou d'une puissance de refoulement maximale jusqu'à 100 % de celle-ci.
  6. Installation frigorifique ou installation de climatisation, présentant un compresseur à piston alternatif (10) selon l'une quelconque des revendications précédentes.
  7. Pompe à chaleur présentant un compresseur à piston alternatif (10) selon l'une quelconque des revendications précédentes.
  8. Procédé de réglage d'un compresseur à piston alternatif (10), qui présente un dispositif de réglage (12) et qui est prévu pour comprimer un fluide frigorigène, le réglage du compresseur à piston alternatif étant réalisé par une régulation de la puissance de refoulement du compresseur (10), la régulation de la puissance de refoulement étant effectuée par au moins un signal numérique, le signal numérique ou des signaux numériques étant acheminés à une ou plusieurs soupapes de régulation (16) pouvant être commandées numériquement,
    le compresseur à piston alternatif (10) présentant au moins un volume de gaz d'aspiration (22) et au moins un volume haute pression (24), la connexion étant réalisée entre l'au moins un volume de gaz d'aspiration (22) et l'au moins un volume haute pression (24) du compresseur à piston alternatif (10), la régulation de la puissance de refoulement du compresseur étant effectuée de manière commandée par une ouverture et une fermeture de la connexion par le signal numérique, en particulier au moyen de la soupape de régulation (16) pouvant être commandée numériquement, le compresseur à piston alternatif (10) présentant un dispositif d'arrêt (28), qui, considéré dans une direction d'écoulement du fluide frigorigène, dans le cas d'un fonctionnement normal du compresseur à piston alternatif (10), est disposé en aval du volume haute pression (24), le dispositif d'arrêt (28) étant fermé lorsque la connexion (26) est ouverte, et le dispositif d'arrêt étant ouvert lorsque la connexion (26) est fermée,
    la variation ou la régulation s'effectuant en continu, sans paliers, entre le volume de refoulement minimal et le volume de refoulement maximal.
  9. Procédé selon la revendication 8, dans lequel le dispositif de réglage commande une ou plusieurs soupapes de régulation de telle sorte qu'un volume de refoulement de 5 % à 10 % du volume de refoulement nominal ou du volume de refoulement maximal du compresseur soit prévu en tant que volume de refoulement minimal et/ou en ce que 100 % de la puissance de refoulement nominale ou du volume de refoulement nominal ou du volume de refoulement maximal ou de la puissance de refoulement maximale soient prévus en tant que volume de refoulement maximal.
EP15722044.3A 2014-03-29 2015-03-29 Compresseur à piston alternatif et procédé de régulation dudit compresseur Active EP3126672B1 (fr)

Applications Claiming Priority (2)

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DE102014004619.2A DE102014004619A1 (de) 2014-03-29 2014-03-29 Regelung für Kälteanlage, sowie Kälteanlage und entsprechendes Regelverfahren
PCT/EP2015/000671 WO2015149926A1 (fr) 2014-03-29 2015-03-29 Compresseur à piston alternatif et procédé de régulation dudit compresseur

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EP3456563A1 (fr) 2017-09-15 2019-03-20 Schmitz Cargobull AG Unité de réfrigération de transport et son procédé de fonctionnement
CN109387000B (zh) * 2018-10-19 2019-12-10 珠海格力电器股份有限公司 一种压缩机的无级能量调节装置、调节方法以及制冷系统
US11302590B2 (en) 2019-02-15 2022-04-12 Kla Corporation Delivery of light into a vacuum chamber using an optical fiber
DE102021117724A1 (de) * 2021-07-08 2023-01-12 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichterverbund

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WO2011005367A2 (fr) 2009-07-06 2011-01-13 Carrier Corporation Soupape de décompression de dérivation pour régulation de la capacité d’un compresseur

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US20170130713A1 (en) 2017-05-11
DE102014004619A1 (de) 2015-10-01
EP3126672A1 (fr) 2017-02-08
CN106460830B (zh) 2019-10-29
CN106460830A (zh) 2017-02-22

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