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WO2015110284A1 - Compressor for a refrigeration circuit of a domestic refrigerator, domestic refrigerator with a compressor and a method for operating a compressor of a domestic refrigerator - Google Patents

Compressor for a refrigeration circuit of a domestic refrigerator, domestic refrigerator with a compressor and a method for operating a compressor of a domestic refrigerator Download PDF

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Publication number
WO2015110284A1
WO2015110284A1 PCT/EP2015/050150 EP2015050150W WO2015110284A1 WO 2015110284 A1 WO2015110284 A1 WO 2015110284A1 EP 2015050150 W EP2015050150 W EP 2015050150W WO 2015110284 A1 WO2015110284 A1 WO 2015110284A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
refrigerant
valve
pressure
shut
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.)
Ceased
Application number
PCT/EP2015/050150
Other languages
German (de)
French (fr)
Inventor
Christian Mayershofer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Priority to US15/113,058 priority Critical patent/US20170010025A1/en
Publication of WO2015110284A1 publication Critical patent/WO2015110284A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F04B35/04—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 electric
    • F04B35/045—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 electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/108—Valves characterised by the material
    • F04B53/1082—Valves characterised by the material magnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/073—Linear compressors
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • F25B2600/2519—On-off valves

Definitions

  • a compressor for a refrigeration cycle of a household refrigerator a household refrigerator with a compressor, and a method of operating a compressor of a household refrigerator
  • the invention relates to a compressor for a refrigeration cycle of a household refrigerating appliance and a method for operating a compressor of a domestic refrigerating appliance of the type specified in the preambles of the independent claims. Furthermore, the invention relates to a household refrigerating appliance with such a compressor.
  • WO 2008 055810 A1 shows a linear compressor for a household appliance, with a movable in the longitudinal direction of a cylinder between an upper and lower dead center piston, the piston outer surface is to form a gas pressure bearing in the radial direction of the cylinder without contact against a corresponding cylinder inner surface storable.
  • the linear compressor shown there can be used in a refrigeration cycle of a household refrigerator.
  • This object is achieved by a compressor for a refrigeration cycle of a household refrigerator and by a method for operating a compressor of a refrigeration cycle of a household refrigerating appliance with the features of the independent claims and, moreover, by a household refrigerating appliance with such a compressor.
  • the compressor according to the invention for a refrigeration cycle of a household refrigerating appliance comprises a piston which is movable within a compressor chamber of a cylinder for compressing a refrigerant, wherein the piston can be stored without contact in the radial direction of the cylinder by means of a gas pressure bearing which can be formed from the refrigerant. Furthermore, the compressor comprises an inlet valve for regulating a volume flow of the uncompressed refrigerant from a low-pressure inlet of the compressor into the compressor chamber. Furthermore, the compressor comprises an outlet valve for regulating a volume flow of the compressed refrigerant from the compressor space to a high-pressure outlet of the compressor.
  • the compressor comprises a shut-off valve arranged between the low-pressure inlet and the high-pressure inlet, which is designed for this purpose to prevent backflow of the refrigerant from the high-pressure outlet to the low-pressure inlet when the compressor is deactivated.
  • shut-off valve By the inventively provided shut-off valve, it is now possible, this undesirable pressure equalization between the low pressure input and the To stop the high-pressure outlet of the compressor by closing the shut-off valve as soon as the compressor is deactivated.
  • the solution according to the invention makes it possible to maintain a previously established pressure difference between the low-pressure inlet and the high-pressure outlet of the compressor during the downtime of the compressor, whereby a considerable increase in the efficiency of a refrigeration cycle of a household refrigerating appliance can be achieved, in which the compressor according to the invention is used.
  • the shut-off valve is arranged in a gas storage supply line of the compressor, through which the refrigerant for forming the gas pressure bearing can be fed.
  • the shut-off valve can be arranged directly in the gas bearing supply line of the compressor serving as a pressure line, whereby a pressure compensation can be suppressed when the compressor is switched off by a return flow of the refrigerant through the gas storage supply line.
  • the shut-off valve is arranged in a refrigerant line of the compressor through which the compressed refrigerant flows in the direction of the high-pressure outlet when the compressor is activated.
  • the accessibility of such a refrigerant line may be better than in the gas storage supply line, so that an optionally defective shut-off valve can be exchanged particularly easily.
  • the shut-off valve is designed as a check valve.
  • that can Shut-off valve may be formed as a louvered valve, spring valve or the like, which can be actuated solely by the pressure difference between the low-pressure inlet and the high-pressure outlet of the compressor.
  • Such a shut-off valve is usually relatively simple and can therefore be manufactured and provided particularly cost.
  • the shut-off valve is electromotive or electromagnetically actuated.
  • the shut-off valve is an active element, in which the valve position can be influenced, for example, by applying an electric current.
  • the compressor is designed as a linear compressor.
  • Linear compressors are usually piston compressors, in which the pistons are driven by linear drives, for example roller screw drives, independently of a crankshaft.
  • linear compressors Compared with conventional reciprocating compressors with a rotary drive, for example via a connecting rod driven by a rotary motor, linear compressors have the advantage that the piston stroke can be changed. This makes it possible to adjust the compression ratio within the compressor in a particularly simple manner as needed.
  • the cylinder comprises a socket, within which the piston is arranged. For example, if due to a defect, the gas pressure bearing can not be formed, the piston only comes into contact with the socket, within which it is guided, so that in such a case, only the socket is damaged and it must be replaced.
  • a further advantageous embodiment of the invention provides that the socket comprises a plurality of openings through which the refrigerant for forming the Gas pressure bearing can be fed in the direction of the piston.
  • these openings are provided evenly distributed on the socket, so that the gas pressure bearing can be constructed very quickly and evenly.
  • the domestic refrigerator according to the invention comprises the compressor according to the invention or an advantageous embodiment of the compressor according to the invention.
  • the compressor is arranged in the flow direction of a refrigeration cycle of the household refrigerating appliance after an evaporator and a condenser, wherein a further shut-off valve is arranged in the flow direction after the condenser and in front of the evaporator.
  • the flow direction of the refrigerant within the refrigeration cycle is designated by the flow direction, in which the refrigerant flows through the refrigeration cycle when the compressor is activated.
  • a refrigerant is compressed by means of a piston which is movable within a compressor chamber of a cylinder and which is mounted without contact in the radial direction of the cylinder by means of a gas pressure bearing formed from the refrigerant.
  • an inlet valve of the compressor for regulating a volume flow of the uncompressed refrigerant from a low pressure input of the compressor is actuated in the compressor chamber.
  • an exhaust valve of the compressor for regulating a volume flow of the compressed refrigerant from the compressor space to a high-pressure outlet of the compressor is actuated.
  • the inventive method is characterized in that a shutoff valve arranged between the low pressure inlet and the high pressure outlet is closed as soon as the compressor is deactivated, whereby a Return flow of the refrigerant is prevented from the high-pressure outlet to the low-pressure inlet when the compressor is deactivated.
  • Advantageous embodiments of the compressor according to the invention are to be regarded as advantageous embodiments of the method according to the invention for operating such a compressor.
  • the shut-off valve is opened with a predetermined time course, before the deactivated compressor for compressing the refrigerant is activated again.
  • the time advance before the activation of the compressor is chosen to be so large that the gas pressure bearing between the piston and the cylinder is completely formed by means of the refrigerant flowing from the high-pressure outlet into the compressor.
  • the shut-off valve is opened against a prevailing pressure gradient when the compressor is deactivated, so that due to the prevailing pressure gradient between the high-pressure outlet and the low-pressure inlet of the compressor, the refrigerant flows into the compressor and the gas pressure bearing between the piston and the cylinder is formed, even before the Compressor is reactivated.
  • the piston can already be mounted without contact relative to the cylinder before the compressor is activated.
  • the wear on the piston-cylinder mating can be significantly reduced.
  • the drawing shows in: a schematic longitudinal sectional view of a household refrigerator with a compressor;
  • Fig. 2. is a schematic representation of a refrigeration cycle of the household refrigerator, within which the compressor is arranged;
  • Fig. 3 is a schematic side sectional view of a first embodiment of the compressor.
  • Fig. 4 is a schematic side sectional view of a second
  • Embodiment of the compressor Embodiment of the compressor.
  • a domestic refrigerator 10 is shown in Fig. 1 in a schematic longitudinal section.
  • the household refrigerating appliance 10 may be, for example, a refrigerator, a freezer or a refrigerated combined freezer.
  • the household refrigeration appliance 10 comprises an interior space 12 which is designed to receive food.
  • This interior space 12 may be a refrigerated compartment, a freezer compartment or a no-frost compartment or at least two of these compartments.
  • the domestic refrigeration appliance 10 comprises a refrigeration cycle 14, which comprises a compressor 16 designed as a linear compressor.
  • the compressor 16 is preferably arranged in a machine room 18, which is located in the lower and rear area of the domestic refrigerator 10.
  • the refrigeration cycle 14 is shown in a schematic representation.
  • the refrigeration cycle 14 includes a condenser 20, a throttle 22, which may also be an expansion valve or the like, and an evaporator 24.
  • the compressor 16 includes a shut-off valve 50, to which in the following even closer will be received.
  • the refrigeration cycle 14 includes a further shut-off valve 28.
  • the arrow 30 indicates a flow direction of the refrigeration cycle 14, in which a non-designated refrigerant flows, as long as the compressor 16 is activated.
  • FIG. 3 is a schematic side sectional view of a first embodiment of the compressor 16 is shown.
  • the compressor 16 comprises a piston 36, which can be moved within a compressor chamber 32 of a cylinder 34, for compressing a refrigerant which is not described in more detail, wherein the piston 36 can be mounted in the radial direction in relation to the cylinder 34 without contact by means of a gas pressure bearing which can be formed from the refrigerant.
  • the cylinder 34 in this case comprises a bushing 38, within which the piston 36 is arranged.
  • the bushing 38 has a plurality of openings 40 through which the refrigerant for forming the gas pressure bearing in the direction of the piston 36 can be fed.
  • the compressor 16 has an inlet valve 42, which serves for regulating a volume flow of the uncompressed refrigerant from a low-pressure inlet 44 of the compressor 16 into the compressor chamber 32.
  • the low-pressure inlet 44 is arranged on a housing 35 of the compressor 16 and connected within the refrigeration cycle 14 to the evaporator 24, so that the refrigerant is supplied to the compressor 16 with the compressor 16 activated by the evaporator 24 via the low-pressure inlet 44.
  • the compressor 16 further includes an outlet valve 46 for regulating a volume flow of the compressed refrigerant from the compressor room 32 to a high pressure outlet 48 of the compressor 16, which is also disposed on the housing 35.
  • the high-pressure outlet 48 is connected to the condenser 20 within the refrigeration cycle 14. The compressed refrigerant is thus supplied via the high-pressure outlet 48 to the condenser 20.
  • the compressor 16 comprises a shut-off valve 50, which is arranged between the low-pressure inlet 44 and the high-pressure outlet 48 and which is designed to prevent a backflow of the refrigerant from the high-pressure outlet 48 to the low-pressure inlet 44 when the compressor 16 is deactivated.
  • the shut-off valve 50 may be closed when the compressor 16 is deactivated, so that a pressure difference built up between the high-pressure outlet 48 and the low-pressure inlet 44 during operation of the compressor 16 can be maintained.
  • the shut-off valve 50 is arranged in a gas bearing supply line 52 of the compressor 16, through which the refrigerant for forming the gas pressure bearing can be fed.
  • the gas bearing supply line 52 leads from a high-pressure side of the compressor 16 into a reservoir 41, from where the refrigerant can be supplied through the openings 40 of the bush 38 in the direction of the piston 36 to form the gas pressure bearing between the piston 36 and the bushing 38.
  • the shut-off valve 50 may be formed as a simple check valve, for example as a multi-plate valve, spring valve or the like. In this case, the shut-off valve 50 is automatically closed by a pressure difference between the high-pressure outlet 48 and the low-pressure inlet 44 of the compressor 16. Alternatively, it is also possible that the shut-off valve 50 is formed as an active element and, for example, electromotive or electromagnetically actuated.
  • a further embodiment of the compressor 16 is shown in a schematic side sectional view.
  • the shut-off valve 50 is arranged in a high-pressure-side refrigerant line 54 of the compressor 16, through which the compressed refrigerant flows in the direction of the high-pressure outlet 48 when the compressor 16 is activated.
  • the compressor 16 When the compressor 16 is activated, the refrigerant is compressed by means of the piston 36 moved within the compressor chamber 32 within the cylinder 34, wherein the piston 36 is mounted in the radial direction relative to the cylinder 34 without contact by means of the gas pressure bearing formed from the refrigerant.
  • the gas bearing supply line 52 Through the gas bearing supply line 52 while refrigerant is continuously conveyed into the gas reservoir 41 and fed through the openings 40 in the direction of the piston 36, whereby the gas pressure bearing, which is formed from the refrigerant is supplied with a sufficient pressure.
  • the inlet valve 42 and the outlet valve 46 are cyclically and alternately operated to regulate the flow of refrigerant from the low pressure inlet 44 through the compressor chamber 32 via the high pressure outlet 48.
  • the shut-off valve 50 arranged between the low-pressure inlet 44 and the high-pressure outlet 48 is closed, whereby a return flow of the refrigerant from the high-pressure outlet 48 to the low-pressure inlet 44 when the compressor 16 is deactivated.
  • the further shut-off valve 28 which, as shown in FIG. 2, is arranged within the refrigeration cycle 14 between the condenser 20 and the throttle 22, is closed as soon as the compressor 16 is deactivated.
  • the shut-off valve 50 disposed within the compressor 16 is opened with a predetermined time delay before the deactivated compressor 16 is reactivated to compress the refrigerant.
  • the time advance before activating the compressor 16 is selected to be so large that the gas pressure bearing between the piston 36 and the cylinder 34 is completely formed by means of the refrigerant flowing from the high-pressure outlet 48 into the compressor 16, before the compressor 16 is reactivated. This ensures that the gas pressure bearing between the piston 36 and the cylinder 34 is fully formed before the compressor 16 is reactivated and the piston 36 moves within the cylinder 34 to compress the refrigerant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Abstract

The invention relates to a compressor (16) for a refrigeration circuit (14) of a domestic refrigerator (10) comprising: a piston (36) for compressing a refrigerant, which piston is moveable within a compression chamber (32) of a cylinder (34), wherein the piston (36) can be mounted in a contact-free way in the radial direction thereof with respect to the cylinder (34) by means of a gas pressure bearing formed from the refrigerant; an inlet valve (42) for regulating a volume flow of the uncompressed refrigerant from a low-pressure inlet (44) of the compressor (16) into the compression chamber (32); an outlet valve (46) for regulating a volume flow of compressed refrigerant from the compression chamber (32) to a high-pressure outlet (48) of the compressor (16); wherein the compressor (16) comprises a check valve (50) arranged between the low-pressure inlet (44) and the high-pressure outlet (50), said check valve is additionally designed to prevent a backflow of refrigerant from the high-pressure outlet (48) to the low-pressure inlet (44) in the case of a deactivated compressor (16). The invention further relates to a domestic refrigerator (10) comprising a compressor (16) and a method for operating a compressor (16) for a refrigeration circuit (14) of a domestic refrigerator (10).

Description

Verdichter für einen Kältekreislauf eines Haushaltskältegeräts, Haushaltskältegerät mit einem Verdichter und Verfahren zum Betreiben eines Verdichters eines Haushaltskältegeräts  A compressor for a refrigeration cycle of a household refrigerator, a household refrigerator with a compressor, and a method of operating a compressor of a household refrigerator

Die Erfindung betrifft einen Verdichter für einen Kältekreislauf eines Haushaltskältegeräts und ein Verfahren zum Betreiben eines Verdichters eines Haushaltskältegeräts der in den Oberbegriffen der unabhängigen Patentansprüche angegebenen Art. Des Weiteren betrifft die Erfindung ein Haushaltskältegerät mit einem derartigen Verdichter. Die WO 2008 055810 A1 zeigt einen Linearverdichter für ein Haushaltsgerät, mit einem in Längsrichtung eines Zylinders zwischen einer oberen und unteren Totpunktlage bewegbaren Kolben, dessen Kolbenaußenfläche unter Ausbildung eines Gasdrucklagers in radialer Richtung des Zylinders berührungslos gegenüber einer korrespondierenden Zylinderinnenfläche lagerbar ist. Der dort gezeigte Linearverdichter kann in einem Kältekreislauf eines Haushaltskältegeräts eingesetzt werden. The invention relates to a compressor for a refrigeration cycle of a household refrigerating appliance and a method for operating a compressor of a domestic refrigerating appliance of the type specified in the preambles of the independent claims. Furthermore, the invention relates to a household refrigerating appliance with such a compressor. WO 2008 055810 A1 shows a linear compressor for a household appliance, with a movable in the longitudinal direction of a cylinder between an upper and lower dead center piston, the piston outer surface is to form a gas pressure bearing in the radial direction of the cylinder without contact against a corresponding cylinder inner surface storable. The linear compressor shown there can be used in a refrigeration cycle of a household refrigerator.

Während einer Stillstandzeit eines derartigen Verdichters mit einer Gaslagerung kann es bedingt durch die Gaslagerung zu einem unerwünschten Rückströmen eines gasförmigen Kältemittels von einem Hochdruckausgang zu einem Niederdruckeingang des Verdichters kommen. Die Folge ist, dass eine entsprechende Druckdifferenz zwischen dem Hochdruckausgang und dem Niederdruckeingang während der Stillstandszeit eines derartigen Verdichters nicht aufrechterhalten werden kann, was sich negativ auf den Betrieb eines Kältekreislaufs eines Haushaltskältegeräts auswirkt. Denn bei einem erneuten Starten eines derartigen Verdichters muss zunächst die Druckdifferenz zwischen dem Hochdruckausgang und dem Niederdruckeingang des Verdichters wieder aufgebaut werden. During a standstill period of such a compressor with a gas storage, it may be due to the gas storage to an undesirable backflow of a gaseous refrigerant from a high pressure outlet to a low pressure input of the compressor. The result is that a corresponding pressure difference between the high-pressure outlet and the low-pressure inlet during the downtime of such a compressor can not be maintained, which has a negative effect on the operation of a refrigeration cycle of a domestic refrigerator. Because at a restart of such a compressor, first, the pressure difference between the high pressure outlet and the low pressure inlet of the compressor must be rebuilt.

Es ist daher die Aufgabe der vorliegenden Erfindung, eine Druckdifferenz zwischen einem Niederdruckeingang und einem Hochdruckausgang eines Verdichters auch während der Stillstandzeit des Verdichters aufrechterhalten zu können. Diese Aufgabe wird durch einen Verdichter für einen Kältekreislauf eines Haushaltskältegeräts sowie durch ein Verfahren zum Betreiben eines Verdichters eines Kältekreislaufs eines Haushaltskältegeräts mit den Merkmalen der unabhängigen Patentansprüche und darüber hinaus durch ein Haushaltskältegerät mit einem derartigen Verdichter gelöst. It is therefore the object of the present invention to be able to maintain a pressure difference between a low-pressure inlet and a high-pressure outlet of a compressor even during the downtime of the compressor. This object is achieved by a compressor for a refrigeration cycle of a household refrigerator and by a method for operating a compressor of a refrigeration cycle of a household refrigerating appliance with the features of the independent claims and, moreover, by a household refrigerating appliance with such a compressor.

Der erfindungsgemäße Verdichter für einen Kältekreislauf eines Haushaltskältegeräts umfasst einen innerhalb eines Verdichterraums eines Zylinders bewegbaren Kolben zum Komprimieren eines Kältemittels, wobei der Kolben in dessen radialer Richtung gegenüber dem Zylinder berührungslos mittels eines aus dem Kältemittel ausbildbaren Gasdrucklagers lagerbar ist. Des Weiteren umfasst der Verdichter ein Einlassventil zum Regulieren eines Volumenstroms des unkomprimierten Kältemittels von einem Niederdruckeingang des Verdichters in den Verdichterraum. Ferner umfasst der Verdichter ein Auslassventil zum Regulieren eines Volumenstroms des komprimierten Kältemittels von dem Verdichterraum zu einem Hochdruckausgang des Verdichters. Um eine während des Betriebs des Verdichters aufgebaute Druckdifferenz zwischen dem Niederdruckeingang und dem Hochdruckausgang des Verdichters auch während der Stillstandzeit des Verdichters aufrechterhalten zu können, ist es erfindungsgemäß vorgesehen, dass der Verdichter ein zwischen dem Niederdruckeingang und dem Hochdruckeingang angeordnetes Absperrventil umfasst, welches dazu ausgelegt ist, bei deaktiviertem Verdichter ein Rückströmen des Kältemittels von dem Hochdruckausgang zum Niederdruckeingang zu unterbinden. The compressor according to the invention for a refrigeration cycle of a household refrigerating appliance comprises a piston which is movable within a compressor chamber of a cylinder for compressing a refrigerant, wherein the piston can be stored without contact in the radial direction of the cylinder by means of a gas pressure bearing which can be formed from the refrigerant. Furthermore, the compressor comprises an inlet valve for regulating a volume flow of the uncompressed refrigerant from a low-pressure inlet of the compressor into the compressor chamber. Furthermore, the compressor comprises an outlet valve for regulating a volume flow of the compressed refrigerant from the compressor space to a high-pressure outlet of the compressor. In order to be able to maintain a pressure difference between the low-pressure inlet and the high-pressure outlet of the compressor established during operation of the compressor, it is provided according to the invention that the compressor comprises a shut-off valve arranged between the low-pressure inlet and the high-pressure inlet, which is designed for this purpose to prevent backflow of the refrigerant from the high-pressure outlet to the low-pressure inlet when the compressor is deactivated.

Es ist also erfindungsgemäß vorgesehen, neben dem Einlassventil und dem Auslassventil, welche zur Regulierung der Volumenströme des Kältemittels durch den Verdichter dienen, ein weiteres Absperrventil innerhalb des Verdichters zwischen dem Niederdruckeingang und dem Hochdruckausgang vorzusehen, mittels welchem ein Durchströmen des Verdichters mit dem Kältemittel bei deaktiviertem Verdichter unterbunden werden kann. Denn während des Betriebs des Verdichters wird eine Druckdifferenz zwischen dem Niederdruckeingang und dem Hochdruckausgang aufgebaut, welche beim Deaktivieren des Verdichters durch ein Rückströmen des Kältemittels durch den Verdichter hindurch zu einem unerwünschten Druckausgleich führen würde. Durch das erfindungsgemäß vorgesehene Absperrventil ist es nun möglich, diesen unerwünschten Druckausgleich zwischen dem Niederdruckeingang und dem Hochdruckausgang des Verdichters zu unterbinden, indem das Absperrventil geschlossen wird, sobald der Verdichter deaktiviert wird. Durch die erfindungsgemäße Lösung ist es möglich, auch während der Stillstandzeit des Verdichters eine zuvor aufgebaute Druckdifferenz zwischen dem Niederdruckeingang und dem Hochdruckausgang des Verdichters aufrechtzuerhalten, wodurch eine erhebliche Effizienzsteigerung eines Kältekreislaufs eines Haushaltskältegeräts erzielt werden kann, in welchem der erfindungsgemäße Verdichter eingesetzt wird. Beim erneuten Starten des Verdichters ist es nämlich durch die erfindungsgemäße Lösung nicht mehr erforderlich, zunächst eine Druckdifferenz zwischen dem Niederdruckeingang und dem Hochdruckeingang aufzubauen, da die zuvor während des Betriebs des Verdichters aufgebaute Druckdifferenz durch das abschließschließbare Absperrventil auch während des Stillstands des Verdichters zuverlässig aufrechterhalten werden kann. It is therefore provided according to the invention, in addition to the inlet valve and the outlet valve, which serve to regulate the volume flows of the refrigerant through the compressor, to provide a further shut-off valve within the compressor between the low-pressure inlet and the high pressure outlet, by means of which a flow through the compressor with the refrigerant at deactivated Compressor can be prevented. Because during the operation of the compressor, a pressure difference between the low-pressure inlet and the high-pressure outlet is constructed, which would lead to an undesired pressure equalization by deactivation of the compressor by a return flow of the refrigerant through the compressor. By the inventively provided shut-off valve, it is now possible, this undesirable pressure equalization between the low pressure input and the To stop the high-pressure outlet of the compressor by closing the shut-off valve as soon as the compressor is deactivated. The solution according to the invention makes it possible to maintain a previously established pressure difference between the low-pressure inlet and the high-pressure outlet of the compressor during the downtime of the compressor, whereby a considerable increase in the efficiency of a refrigeration cycle of a household refrigerating appliance can be achieved, in which the compressor according to the invention is used. When the compressor is restarted, it is no longer necessary by the solution according to the invention initially to build up a pressure difference between the low-pressure inlet and the high-pressure inlet since the pressure difference previously built up during operation of the compressor is reliably maintained by the lockable shut-off valve even during standstill of the compressor can.

In vorteilhafter Ausgestaltung der Erfindung ist es vorgesehen, dass das Absperrventil in einer Gaslagerversorgungsleitung des Verdichters angeordnet ist, durch welche das Kältemittel zum Ausbilden des Gasdrucklagers zuführbar ist. Mit anderen Worten kann das Absperrventil direkt in der als Druckleitung dienenden Gaslagerversorgungsleitung des Verdichters angeordnet sein, wodurch ein Druckausgleich bei abgeschaltetem Verdichter durch ein Rückströmen des Kältemittels durch die Gaslagerversorgungsleitung unterbunden werden kann. In an advantageous embodiment of the invention, it is provided that the shut-off valve is arranged in a gas storage supply line of the compressor, through which the refrigerant for forming the gas pressure bearing can be fed. In other words, the shut-off valve can be arranged directly in the gas bearing supply line of the compressor serving as a pressure line, whereby a pressure compensation can be suppressed when the compressor is switched off by a return flow of the refrigerant through the gas storage supply line.

In weiterer vorteilhafter Ausgestaltung der Erfindung ist es vorgesehen, dass das Absperrventil in einer Kältemittelleitung des Verdichters angeordnet ist, durch welche das komprimierte Kältemittel bei aktiviertem Verdichter in Richtung des Hochdruckausgangs strömt. Die Zugänglichkeit einer derartigen Kältemittelleitung kann unter Umständen besser sein, als bei der Gaslagerversorgungsleitung, so dass ein gegebenenfalls defektes Absperrventil besonders einfach ausgetauscht werden kann. Bei der Anordnung des Absperrventils in der Kältemittelleitung, die zu dem Hochdruckausgang des Verdichters führt, kann ebenfalls ein unerwünschter Druckausgleich zwischen dem Hochdruckausgang und dem Niederdruckeingang des Verdichters bei deaktiviertem Verdichter effektiv unterbunden werden. In a further advantageous embodiment of the invention, it is provided that the shut-off valve is arranged in a refrigerant line of the compressor through which the compressed refrigerant flows in the direction of the high-pressure outlet when the compressor is activated. The accessibility of such a refrigerant line may be better than in the gas storage supply line, so that an optionally defective shut-off valve can be exchanged particularly easily. With the arrangement of the shut-off valve in the refrigerant line, which leads to the high-pressure outlet of the compressor, also an undesirable pressure equalization between the high-pressure outlet and the low-pressure inlet of the compressor can be effectively prevented when the compressor is deactivated.

Gemäß einer weiteren vorteilhaften Ausführungsform der Erfindung ist es vorgesehen, dass das Absperrventil als Rückschlagventil ausgebildet ist. Beispielsweise kann das Absperrventil als Lamellenventil, Federventil oder dergleichen ausgebildet sein, welches allein durch die Druckdifferenz zwischen dem Niederdruckeingang und dem Hochdruckausgang des Verdichters betätigbar ist. Ein derartiges Absperrventil ist üblicherweise relativ einfach aufgebaut und kann daher besonders kostengünstig hergestellt und bereitgestellt werden. According to a further advantageous embodiment of the invention, it is provided that the shut-off valve is designed as a check valve. For example, that can Shut-off valve may be formed as a louvered valve, spring valve or the like, which can be actuated solely by the pressure difference between the low-pressure inlet and the high-pressure outlet of the compressor. Such a shut-off valve is usually relatively simple and can therefore be manufactured and provided particularly cost.

In weiterer vorteilhafter Ausgestaltung der Erfindung ist es vorgesehen, dass das Absperrventil elektromotorisch oder elektromagnetisch betätigbar ist. Mit anderen Worten kann es vorgesehen sein, dass es sich bei dem Absperrventil um ein aktives Element handelt, bei welchem die Ventilstellung beispielsweise durch Anlegen eines elektrischen Stromes beeinflusst werden kann. Der Vorteil bei einer derartigen Ausgestaltung liegt darin, dass das Absperrventil aktiv angesteuert werden kann, wodurch dessen Betätigung im Wesentlichen unabhängig von den herrschenden Druckverhältnissen innerhalb des Verdichters frei wählbar ist. Eine weitere vorteilhafte Ausführungsform der Erfindung sieht vor, dass der Verdichter als Linearverdichter ausgebildet ist. Linearverdichter sind üblicherweise Kolbenkompressoren, bei denen die Kolben durch Linearantriebe, zum Beispiel Rollengewindegetriebe, unabhängig von einer Kurbelwelle angetrieben werden. Gegenüber konventionellen Kolbenverdichtern mit einem rotatorischen Antrieb, zum Beispiel über eine von einem Drehmotor angetriebene Pleuelstange, haben Linearverdichter den Vorteil, dass der Kolbenhub verändert werden kann. Dadurch ist es möglich, das Kompressionsverhältnis innerhalb des Verdichters auf besonders einfache Weise bedarfsgerecht einstellen zu können. In weiterer vorteilhafter Ausgestaltung der Erfindung ist es vorgesehen, dass der Zylinder eine Buchse umfasst, innerhalb welcher der Kolben angeordnet ist. Sollte beispielsweise aufgrund eines Defekts das Gasdrucklager nicht ausgebildet werden können, gerät der Kolben lediglich in Kontakt mit der Buchse, innerhalb welcher dieser geführt ist, so dass in einem derartigen Fall nur die Buchse beschädigt wird und diese ausgetauscht werden muss. In a further advantageous embodiment of the invention, it is provided that the shut-off valve is electromotive or electromagnetically actuated. In other words, it can be provided that the shut-off valve is an active element, in which the valve position can be influenced, for example, by applying an electric current. The advantage with such a configuration is that the shut-off valve can be activated actively, whereby its operation is essentially independent of the prevailing pressure conditions within the compressor freely selectable. A further advantageous embodiment of the invention provides that the compressor is designed as a linear compressor. Linear compressors are usually piston compressors, in which the pistons are driven by linear drives, for example roller screw drives, independently of a crankshaft. Compared with conventional reciprocating compressors with a rotary drive, for example via a connecting rod driven by a rotary motor, linear compressors have the advantage that the piston stroke can be changed. This makes it possible to adjust the compression ratio within the compressor in a particularly simple manner as needed. In a further advantageous embodiment of the invention, it is provided that the cylinder comprises a socket, within which the piston is arranged. For example, if due to a defect, the gas pressure bearing can not be formed, the piston only comes into contact with the socket, within which it is guided, so that in such a case, only the socket is damaged and it must be replaced.

Eine weitere vorteilhafte Ausführungsform der Erfindung sieht vor, dass die Buchse mehrere Öffnungen umfasst, durch welche das Kältemittel zur Ausbildung des Gasdrucklagers in Richtung des Kolbens zuführbar ist. Vorzugsweise sind diese Öffnungen gleichmäßig verteilt an der Buchse vorgesehen, so dass das Gasdrucklager besonders schnell und gleichmäßig aufgebaut werden kann. A further advantageous embodiment of the invention provides that the socket comprises a plurality of openings through which the refrigerant for forming the Gas pressure bearing can be fed in the direction of the piston. Preferably, these openings are provided evenly distributed on the socket, so that the gas pressure bearing can be constructed very quickly and evenly.

Das erfindungsgemäße Haushaltskältegerät umfasst den erfindungsgemäßen Verdichter oder eine vorteilhafte Ausführungsform des erfindungsgemäßen Verdichters. The domestic refrigerator according to the invention comprises the compressor according to the invention or an advantageous embodiment of the compressor according to the invention.

Gemäß einer vorteilhaften Ausführungsform des Haushaltskältegeräts ist es vorgesehen, dass der Verdichter in Strömungsrichtung eines Kältekreislaufs des Haushaltskältegeräts nach einem Verdampfer und vor einem Verflüssiger angeordnet ist, wobei ein weiteres Absperrventil in der Strömungsrichtung nach dem Verflüssiger und vor dem Verdampfer angeordnet ist. Mit der Strömungsrichtung ist dabei diejenige Strömungsrichtung des Kältemittels innerhalb des Kältekreislaufs bezeichnet, in welcher das Kältemittel den Kältekreislauf bei aktiviertem Verdichter durchströmt. Dadurch, dass ein weiteres Absperrventil nach dem Verflüssiger und vor dem Verdampfer angeordnet ist, kann ein unerwünschter Druckausgleich bei deaktiviertem Verdichter zwischen dem Verflüssiger und dem Verdampfer unterbunden werden, da der Verflüssiger eine Hochdruckseite und der Verdampfer eine Niederdruckseite des Kältekreislaufs darstellt. Dies trägt ebenfalls zur Effizienzsteigerung des Kältekreislaufs des Haushaltskältegeräts bei, weil ein Druckausgleich zwischen Verflüssiger und Verdampfer durch Schließen der weiteren Absperrventils verhindert werden kann. According to an advantageous embodiment of the domestic refrigerator, it is provided that the compressor is arranged in the flow direction of a refrigeration cycle of the household refrigerating appliance after an evaporator and a condenser, wherein a further shut-off valve is arranged in the flow direction after the condenser and in front of the evaporator. In this case, the flow direction of the refrigerant within the refrigeration cycle is designated by the flow direction, in which the refrigerant flows through the refrigeration cycle when the compressor is activated. The fact that a further shut-off valve is arranged after the condenser and before the evaporator, an undesirable pressure equalization with deactivated compressor between the condenser and the evaporator can be prevented because the condenser is a high pressure side and the evaporator is a low pressure side of the refrigeration cycle. This also contributes to increasing the efficiency of the refrigeration cycle of the household refrigeration appliance, because a pressure equalization between the condenser and evaporator can be prevented by closing the other shut-off valve.

Bei dem erfindungsgemäßen Verfahren zum Betreiben eines Verdichters eines Kältekreislaufs eines Haushaltskältegeräts wird ein Kältemittel mittels eines innerhalb eines Verdichterraums eines Zylinders bewegbaren Kolbens komprimiert, welcher in dessen radialer Richtung gegenüber dem Zylinder berührungslos mittels eines aus dem Kältemittel ausgebildeten Gasdrucklagers gelagert wird. Dabei wird ein Einlassventil des Verdichters zum Regulieren eines Volumenstroms des unkomprimierten Kältemittels von einem Niederdruckeingang des Verdichters in den Verdichterraum betätigt. Des Weiteren wird ein Auslassventil des Verdichters zum Regulieren eines Volumenstroms des komprimierten Kältemittels von dem Verdichterraum zu einem Hochdruckausgang des Verdichters betätigt. Das erfindungsgemäße Verfahren zeichnet sich dabei dadurch aus, dass ein zwischen dem Niederdruckeingang und dem Hochdruckausgang angeordnetes Absperrventil geschlossen wird, sobald der Verdichter deaktiviert wird, wodurch ein Rückströmen des Kältemittels von dem Hochdruckausgang zum Niederdruckeingang bei deaktiviertem Verdichter unterbunden wird. Vorteilhafte Ausgestaltungen des erfindungsgemäßen Verdichters sind dabei als vorteilhafte Ausgestaltungen des erfindungsgemäßen Verfahrens zum Betreiben eines derartigen Verdichters anzusehen. In weiterer vorteilhafter Ausgestaltung des Verfahrens ist es vorgesehen, dass das Absperrventil mit einem vorgegebenen zeitlichen Verlauf geöffnet wird, bevor der deaktivierte Verdichter zum Komprimieren des Kältemittels wieder aktiviert wird. Vorzugsweise wird der zeitliche Vorlauf vor dem Aktivieren des Verdichters so groß gewählt, dass mittels des vom Hochdruckausgang in den Verdichter einströmenden Kältemittels das Gasdrucklager zwischen dem Kolben und dem Zylinder vollständig ausgebildet wird. Mit anderen Worten wird das Absperrventil gegen ein vorherrschendes Druckgefälle bei deaktiviertem Verdichter geöffnet, so dass aufgrund des vorherrschenden Druckgefälles zwischen dem Hochdruckausgang und dem Niederdruckeingang des Verdichters das Kältemittel in den Verdichter einströmt und das Gasdrucklager zwischen dem Kolben und dem Zylinder ausbildet wird, noch bevor der Verdichter wieder aktiviert wird. Dadurch kann der Kolben gegenüber dem Zylinder bereits berührungslos gelagert sein, bevor der Verdichter aktiviert wird. Infolgedessen kann der Verschleiß an der Kolben-Zylinder-Paarung erheblich reduziert werden. Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung. Die vorstehend in der Beschreibung genannten Merkmale und Merkmalskombinationen sowie die nachfolgend in der Figurenbeschreibung genannten und/oder in den Figuren alleine gezeigten Merkmale und Merkmalskombinationen sind nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar, ohne den Rahmen der Erfindung zu verlassen. In the method according to the invention for operating a compressor of a refrigeration cycle of a household refrigerating appliance, a refrigerant is compressed by means of a piston which is movable within a compressor chamber of a cylinder and which is mounted without contact in the radial direction of the cylinder by means of a gas pressure bearing formed from the refrigerant. In this case, an inlet valve of the compressor for regulating a volume flow of the uncompressed refrigerant from a low pressure input of the compressor is actuated in the compressor chamber. Furthermore, an exhaust valve of the compressor for regulating a volume flow of the compressed refrigerant from the compressor space to a high-pressure outlet of the compressor is actuated. The inventive method is characterized in that a shutoff valve arranged between the low pressure inlet and the high pressure outlet is closed as soon as the compressor is deactivated, whereby a Return flow of the refrigerant is prevented from the high-pressure outlet to the low-pressure inlet when the compressor is deactivated. Advantageous embodiments of the compressor according to the invention are to be regarded as advantageous embodiments of the method according to the invention for operating such a compressor. In a further advantageous embodiment of the method, it is provided that the shut-off valve is opened with a predetermined time course, before the deactivated compressor for compressing the refrigerant is activated again. Preferably, the time advance before the activation of the compressor is chosen to be so large that the gas pressure bearing between the piston and the cylinder is completely formed by means of the refrigerant flowing from the high-pressure outlet into the compressor. In other words, the shut-off valve is opened against a prevailing pressure gradient when the compressor is deactivated, so that due to the prevailing pressure gradient between the high-pressure outlet and the low-pressure inlet of the compressor, the refrigerant flows into the compressor and the gas pressure bearing between the piston and the cylinder is formed, even before the Compressor is reactivated. As a result, the piston can already be mounted without contact relative to the cylinder before the compressor is activated. As a result, the wear on the piston-cylinder mating can be significantly reduced. Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the description of the figures and / or in the figures alone can be used not only in the respectively specified combination but also in other combinations or in isolation, without the scope of To leave invention.

Die Zeichnung zeigt in: eine schematische Längsschnittdarstellung eines Haushaltskältegeräts mit einem Verdichter; Fig. 2. eine schematische Darstellung eines Kältekreislaufs des Haushaltskältegeräts, innerhalb welchem der Verdichter angeordnet ist;The drawing shows in: a schematic longitudinal sectional view of a household refrigerator with a compressor; Fig. 2. is a schematic representation of a refrigeration cycle of the household refrigerator, within which the compressor is arranged;

Fig. 3 eine schematische Seitenschnittansicht eines ersten Ausführungsbeispiels des Verdichters; und Fig. 3 is a schematic side sectional view of a first embodiment of the compressor; and

Fig. 4 eine schematische Seitenschnittansicht eines zweiten  Fig. 4 is a schematic side sectional view of a second

Ausführungsbeispiels des Verdichters.  Embodiment of the compressor.

In den Figuren werden gleiche oder funktionsgleiche Elemente mit gleichen Bezugszeichen versehen. Ein Haushaltskältegerät 10 ist in Fig. 1 in einer schematischen Längsschnittdarstellung gezeigt. Bei dem Haushaltskältegerät 10 kann es sich beispielsweise um ein Kühlgerät, ein Gefriergerät oder ein Kühl-Gefrier-Kombigerät handeln. Das Haushaltskältegerät 10 umfasst einen Innenraum 12, der zur Aufnahme von Lebensmitteln ausgebildet ist. Dieser Innenraum 12 kann ein Kühlfach, ein Gefrierfach oder ein No-Frost-Fach sein oder zumindest zwei dieser Fächer aufweisen. In the figures, identical or functionally identical elements are provided with the same reference numerals. A domestic refrigerator 10 is shown in Fig. 1 in a schematic longitudinal section. The household refrigerating appliance 10 may be, for example, a refrigerator, a freezer or a refrigerated combined freezer. The household refrigeration appliance 10 comprises an interior space 12 which is designed to receive food. This interior space 12 may be a refrigerated compartment, a freezer compartment or a no-frost compartment or at least two of these compartments.

Das Haushaltskältegerät 10 umfasst einen Kältekreislauf 14, welcher einen als Linearverdichter ausgebildeten Verdichter 16 umfasst. Der Verdichter 16 ist vorzugsweise in einem Maschinenraum 18, der sich im unteren und hinteren Bereich des Haushaltskältegeräts 10 befindet, angeordnet. The domestic refrigeration appliance 10 comprises a refrigeration cycle 14, which comprises a compressor 16 designed as a linear compressor. The compressor 16 is preferably arranged in a machine room 18, which is located in the lower and rear area of the domestic refrigerator 10.

In Fig. 2 ist der Kältekreislauf 14 in einer schematischen Darstellung gezeigt. Neben dem Verdichter 16 umfasst der Kältekreislauf 14 einen Verflüssiger 20, eine Drossel 22, bei welcher es sich auch um ein Expansionsventil oder dergleichen handeln kann, und einen Verdampfer 24. Darüber hinaus umfasst der Verdichter 16 ein Absperrventil 50, auf welches im Nachfolgenden noch näher eingegangen wird. Ferner umfasst der Kältekreislauf 14 ein weiteres Absperrventil 28. Mit dem Pfeil 30 ist eine Strömungsrichtung des Kältekreislaufs 14 angedeutet, in welcher ein nicht bezeichnetes Kältemittel fließt, solange der Verdichter 16 aktiviert ist. In Fig. 2, the refrigeration cycle 14 is shown in a schematic representation. In addition to the compressor 16, the refrigeration cycle 14 includes a condenser 20, a throttle 22, which may also be an expansion valve or the like, and an evaporator 24. In addition, the compressor 16 includes a shut-off valve 50, to which in the following even closer will be received. Further, the refrigeration cycle 14 includes a further shut-off valve 28. The arrow 30 indicates a flow direction of the refrigeration cycle 14, in which a non-designated refrigerant flows, as long as the compressor 16 is activated.

Der Verdichter 16 ist also in Strömungsrichtung 30 des Kältekreislaufs 14 nach dem Verdampfer 24 und vor dem Verflüssiger 20 angeordnet, wobei das weitere Absperrventil 28 in der Strömungsrichtung 30 nach dem Verflüssiger und vor dem Verdampfer 24, im vorliegenden Fall noch vor der Drossel 22, angeordnet ist. In Fig. 3 ist in einer schematischen Seitenschnittansicht ein erstes Ausführungsbeispiel des Verdichters 16 dargestellt. Der Verdichter 16 umfasst einen innerhalb eines Verdichterraums 32 eines Zylinders 34 bewegbaren Kolben 36 zum Komprimieren eines nicht näher bezeichneten Kältemittels, wobei der Kolben 36 in dessen radialer Richtung gegenüber dem Zylinder 34 berührungslos mittels eines aus dem Kältemittel ausbildbaren Gasdrucklagers lagerbar ist. Der Zylinder 34 umfasst vorliegend eine Buchse 38, innerhalb welcher der Kolben 36 angeordnet ist. Die Buchse 38 weist dabei mehrere Öffnungen 40 auf, durch welche das Kältemittel zur Ausbildung des Gasdrucklagers in Richtung des Kolbens 36 zuführbar ist. The compressor 16 is thus arranged in the flow direction 30 of the refrigeration cycle 14 after the evaporator 24 and before the condenser 20, the further shut-off valve 28 in the flow direction 30 after the condenser and before the evaporator 24, in the present case, before the throttle 22, respectively is. In Fig. 3 is a schematic side sectional view of a first embodiment of the compressor 16 is shown. The compressor 16 comprises a piston 36, which can be moved within a compressor chamber 32 of a cylinder 34, for compressing a refrigerant which is not described in more detail, wherein the piston 36 can be mounted in the radial direction in relation to the cylinder 34 without contact by means of a gas pressure bearing which can be formed from the refrigerant. The cylinder 34 in this case comprises a bushing 38, within which the piston 36 is arranged. The bushing 38 has a plurality of openings 40 through which the refrigerant for forming the gas pressure bearing in the direction of the piston 36 can be fed.

Des Weiteren weist der Verdichter 16 ein Einlassventil 42 auf, welches zum Regulieren eines Volumenstroms des unkomprimierten Kältemittels von einem Niederdruckeingang 44 des Verdichters 16 in den Verdichterraum 32 dient. Der Niederdruckeingang 44 ist an einem Gehäuse 35 des Verdichters 16 angeordnet und innerhalb des Kältekreislaufs 14 an den Verdampfer 24 angeschlossen, so dass das Kältemittel bei aktiviertem Verdichter 16 von dem Verdampfer 24 über den Niederdruckeingang 44 dem Verdichter 16 zugeführt wird. Furthermore, the compressor 16 has an inlet valve 42, which serves for regulating a volume flow of the uncompressed refrigerant from a low-pressure inlet 44 of the compressor 16 into the compressor chamber 32. The low-pressure inlet 44 is arranged on a housing 35 of the compressor 16 and connected within the refrigeration cycle 14 to the evaporator 24, so that the refrigerant is supplied to the compressor 16 with the compressor 16 activated by the evaporator 24 via the low-pressure inlet 44.

Der Verdichter 16 umfasst des Weiteren ein Auslassventil 46 zum Regulieren eines Volumenstroms des komprimierten Kältemittels von dem Verdichterraum 32 zu einem Hochdruckausgang 48 des Verdichters 16, welcher ebenfalls am Gehäuse 35 angeordnet ist. Der Hochdruckausgang 48 ist innerhalb des Kältekreislaufs 14 mit dem Verflüssiger 20 verbunden. Das komprimierte Kältemittel wird also über den Hochdruckausgang 48 dem Verflüssiger 20 zugeleitet. The compressor 16 further includes an outlet valve 46 for regulating a volume flow of the compressed refrigerant from the compressor room 32 to a high pressure outlet 48 of the compressor 16, which is also disposed on the housing 35. The high-pressure outlet 48 is connected to the condenser 20 within the refrigeration cycle 14. The compressed refrigerant is thus supplied via the high-pressure outlet 48 to the condenser 20.

Der Verdichter 16 umfasst ein zwischen dem Niederdruckeingang 44 und dem Hochdruckausgang 48 angeordnetes Absperrventil 50, welches dazu ausgelegt ist, bei deaktiviertem Verdichter 16 ein Rückströmen des Kältemittels von dem Hochdruckausgang 48 zum Niederdruckeingang 44 zu unterbinden. Mit anderen Worten kann das Absperrventil 50 bei deaktiviertem Verdichter 16 geschlossen werden, so dass eine während des Betriebs des Verdichters 16 aufgebaute Druckdifferenz zwischen dem Hochdruckausgang 48 und dem Niederdruckeingang 44 aufrechterhalten werden kann. Vorliegend ist das Absperrventil 50 in einer Gaslagerversorgungsleitung 52 des Verdichters 16 angeordnet, durch welche das Kältemittel zum Ausbilden des Gasdrucklagers zuführbar ist. Die Gaslagerversorgungsleitung 52 führt von einer Hochdruckseite des Verdichters 16 in ein Reservoir 41 , von wo aus das Kältemittel durch die Öffnungen 40 der Buchse 38 in Richtung des Kolbens 36 zuführbar ist, um das Gasdrucklager zwischen dem Kolben 36 und der Buchse 38 auszubilden. The compressor 16 comprises a shut-off valve 50, which is arranged between the low-pressure inlet 44 and the high-pressure outlet 48 and which is designed to prevent a backflow of the refrigerant from the high-pressure outlet 48 to the low-pressure inlet 44 when the compressor 16 is deactivated. In other words, the shut-off valve 50 may be closed when the compressor 16 is deactivated, so that a pressure difference built up between the high-pressure outlet 48 and the low-pressure inlet 44 during operation of the compressor 16 can be maintained. In the present case, the shut-off valve 50 is arranged in a gas bearing supply line 52 of the compressor 16, through which the refrigerant for forming the gas pressure bearing can be fed. The gas bearing supply line 52 leads from a high-pressure side of the compressor 16 into a reservoir 41, from where the refrigerant can be supplied through the openings 40 of the bush 38 in the direction of the piston 36 to form the gas pressure bearing between the piston 36 and the bushing 38.

Das Absperrventil 50 kann als einfaches Rückschlagventil, beispielsweise als Lamellenventil, Federventil oder dergleichen, ausgebildet sein. In diesem Fall wird das Absperrventil 50 selbständig durch eine Druckdifferenz zwischen dem Hochdruckausgang 48 und dem Niederdruckeingang 44 des Verdichters 16 geschlossen. Alternativ ist es auch möglich, dass das Absperrventil 50 als aktives Element ausgebildet ist und beispielsweise elektromotorisch oder elektromagnetisch betätigbar ist. The shut-off valve 50 may be formed as a simple check valve, for example as a multi-plate valve, spring valve or the like. In this case, the shut-off valve 50 is automatically closed by a pressure difference between the high-pressure outlet 48 and the low-pressure inlet 44 of the compressor 16. Alternatively, it is also possible that the shut-off valve 50 is formed as an active element and, for example, electromotive or electromagnetically actuated.

In Fig. 4 ist in einer schematischen Seitenschnittansicht ein weiteres Ausführungsbeispiel des Verdichters 16 gezeigt. Im Gegensatz zum in Fig. 3 gezeigten Ausführungsbeispiel des Verdichters 16 ist im vorliegend gezeigten Fall das Absperrventil 50 in einer hochdruckseitigen Kältemittelleitung 54 des Verdichters 16 angeordnet, durch welche das komprimierte Kältemittel bei aktiviertem Verdichter 16 in Richtung des Hochdruckausgangs 48 strömt. 4, a further embodiment of the compressor 16 is shown in a schematic side sectional view. In contrast to the embodiment of the compressor 16 shown in FIG. 3, in the case shown here, the shut-off valve 50 is arranged in a high-pressure-side refrigerant line 54 of the compressor 16, through which the compressed refrigerant flows in the direction of the high-pressure outlet 48 when the compressor 16 is activated.

Nachfolgend wird ein Verfahren zum Betreiben des Verdichters 16 erläutert. Bei aktiviertem Verdichter 16 wird das Kältemittel mittels des innerhalb des Verdichterraums 32 innerhalb des Zylinders 34 bewegten Kolbens 36 komprimiert, wobei der Kolben 36 in dessen radialer Richtung gegenüber dem Zylinder 34 berührungslos mittels des aus dem Kältemittel ausgebildeten Gasdrucklagers gelagert wird. Über die Gaslagerversorgungsleitung 52 wird dabei kontinuierlich Kältemittel in das Gasreservoir 41 befördert und durch die Öffnungen 40 in Richtung des Kolbens 36 zugeführt, wodurch das Gasdrucklager, welches aus dem Kältemittel ausgebildet wird, mit einem ausreichenden Druck versorgt wird. Hereinafter, a method of operating the compressor 16 will be explained. When the compressor 16 is activated, the refrigerant is compressed by means of the piston 36 moved within the compressor chamber 32 within the cylinder 34, wherein the piston 36 is mounted in the radial direction relative to the cylinder 34 without contact by means of the gas pressure bearing formed from the refrigerant. Through the gas bearing supply line 52 while refrigerant is continuously conveyed into the gas reservoir 41 and fed through the openings 40 in the direction of the piston 36, whereby the gas pressure bearing, which is formed from the refrigerant is supplied with a sufficient pressure.

Solange der Verdichter 16 in Betrieb ist, werden das Einlassventil 42 und das Auslassventil 46 zyklisch und abwechselnd betätigt, um den Volumenstrom des Kältemittels von dem Niederdruckeingang 44 durch den Verdichterraum 32 über den Hochdruckausgang 48 zu regulieren. Sobald der Verdichter 16 deaktiviert wird, wird das zwischen dem Niederdruckeingang 44 und dem Hochdruckausgang 48 angeordnete Absperrventil 50 geschlossen, wodurch ein Rückströmen des Kältemittels von dem Hochdruckausgang 48 zum Niederdruckeingang 44 bei deaktiviertem Verdichter 16 unterbunden wird. Gleichzeitig wird noch das weitere Absperrventil 28, welches wie in Fig. 2 gezeigt, innerhalb des Kältekreislaufs 14 zwischen dem Verflüssiger 20 und der Drossel 22 angeordnet ist, geschlossen, sobald der Verdichter 16 deaktiviert wird. Dadurch wird ein Druckausgleich zwischen dem Verflüssiger 20 und dem Verdampfer 24 bei deaktiviertem Verdichter 16 verhindert, da das Kältemittel stromabwärts vom Verflüssiger 20 nicht mehr in Richtung des Verdampfers 24 strömen kann. As long as the compressor 16 is in operation, the inlet valve 42 and the outlet valve 46 are cyclically and alternately operated to regulate the flow of refrigerant from the low pressure inlet 44 through the compressor chamber 32 via the high pressure outlet 48. As soon as the compressor 16 is deactivated, the shut-off valve 50 arranged between the low-pressure inlet 44 and the high-pressure outlet 48 is closed, whereby a return flow of the refrigerant from the high-pressure outlet 48 to the low-pressure inlet 44 when the compressor 16 is deactivated. At the same time, the further shut-off valve 28, which, as shown in FIG. 2, is arranged within the refrigeration cycle 14 between the condenser 20 and the throttle 22, is closed as soon as the compressor 16 is deactivated. As a result, a pressure equalization between the condenser 20 and the evaporator 24 is prevented when the compressor 16 is deactivated, since the refrigerant downstream of the condenser 20 can no longer flow in the direction of the evaporator 24.

Das innerhalb des Verdichters 16 angeordnete Absperrventil 50 wird mit einem vorgegebenen zeitlichen Vorlauf geöffnet, bevor der deaktivierte Verdichter 16 zum Komprimieren des Kältemittels wieder aktiviert wird. Dabei wird der zeitliche Vorlauf vor dem Aktivieren des Verdichters 16 so groß gewählt, dass mittels des vom Hochdruckausgang 48 in den Verdichter 16 einströmenden Kältemittels das Gasdrucklager zwischen dem Kolben 36 und dem Zylinder 34 vollständig ausgebildet wird, bevor der Verdichter 16 wieder aktiviert wird. Dadurch wird gewährleistet, dass das Gasdrucklager zwischen dem Kolben 36 und dem Zylinder 34 voll ausgebildet ist, bevor der Verdichter 16 wieder aktiviert wird und der Kolben 36 sich innerhalb des Zylinders 34 bewegt, um das Kältemittel zu komprimieren. The shut-off valve 50 disposed within the compressor 16 is opened with a predetermined time delay before the deactivated compressor 16 is reactivated to compress the refrigerant. In this case, the time advance before activating the compressor 16 is selected to be so large that the gas pressure bearing between the piston 36 and the cylinder 34 is completely formed by means of the refrigerant flowing from the high-pressure outlet 48 into the compressor 16, before the compressor 16 is reactivated. This ensures that the gas pressure bearing between the piston 36 and the cylinder 34 is fully formed before the compressor 16 is reactivated and the piston 36 moves within the cylinder 34 to compress the refrigerant.

Bezugszeichenliste LIST OF REFERENCE NUMBERS

10 Haushaltskältegerät10 household refrigerators

12 Innenraum 12 interior

14 Kältekreislauf  14 refrigeration cycle

16 Verdichter  16 compressors

18 Maschinenraum  18 engine room

20 Verflüssiger  20 liquefier

22 Drossel  22 throttle

24 Verdampfer  24 evaporator

28 Absperrventil  28 shut-off valve

30 Strömungsrichtung  30 flow direction

32 Verdichterraum  32 compressor room

34 Zylinder  34 cylinders

35 Gehäuse  35 housing

36 Kolben  36 pistons

38 Buchse 38 socket

40 Öffnung  40 opening

41 Reservoir  41 reservoir

42 Einlassventil  42 inlet valve

44 Niederdruckeingang 44 low pressure input

46 Auslassventil 46 exhaust valve

48 Hochdruckausgang 48 high pressure outlet

50 Absperrventil 50 shut-off valve

52 Gaslagerversorgungsleitung 52 gas storage supply line

54 Kältemitteleitung 54 refrigerant line

Claims

Patentansprüche claims 1. Verdichter (16) für einen Kältekreislauf (14) eines Haushaltskältegeräts (10), mit einem innerhalb eines Verdichterraums (32) eines Zylinders (34) bewegbaren Kolben (36) zum Komprimieren eines Kältemittels, wobei der Kolben (36) in dessen radialer Richtung gegenüber dem Zylinder (34) berührungslos mittels eines aus dem Kältemittel ausbildbaren Gasdrucklagers lagerbar ist; einem Einlassventil (42) zum Regulieren eines Volumenstroms des unkomprimierten Kältemittels von einem Niederdruckeingang (44) des Verdichters (16) in den Verdichterraum (32); Compressor (16) for a refrigeration circuit (14) of a household refrigerator (10), with a within a compressor chamber (32) of a cylinder (34) movable piston (36) for compressing a refrigerant, wherein the piston (36) in the radial Direction opposite the cylinder (34) can be stored without contact by means of a formable from the refrigerant gas pressure bearing; an inlet valve (42) for regulating a volume flow of the uncompressed refrigerant from a low pressure inlet (44) of the compressor (16) into the compressor chamber (32); einem Auslassventil (46) zum Regulieren eines Volumenstroms des komprimierten Kältemittels von dem Verdichterraum (32) zu einem Hochdruckausgang (48) des Verdichters (16);  an outlet valve (46) for regulating a volume flow of the compressed refrigerant from the compressor room (32) to a high pressure outlet (48) of the compressor (16); dadurch gekennzeichnet, dass  characterized in that der Verdichter (16) ein zwischen dem Niederdruckeingang (44) und dem  the compressor (16) between the low pressure input (44) and the Hochdruckausgang (48) angeordnetes Absperrventil (50) umfasst, welches dazu ausgelegt ist, bei deaktiviertem Verdichter (16) ein Rückströmen des Kältemittels von dem Hochdruckausgang (48) zum Niederdruckeingang (44) zu unterbinden.  High-pressure outlet (48) arranged shut-off valve (50), which is designed to prevent backflow of the refrigerant from the high-pressure outlet (48) to the low-pressure inlet (44) when the compressor (16) is deactivated. 2. Verdichter (16) nach Anspruch 1 , 2. Compressor (16) according to claim 1, dadurch gekennzeichnet, dass  characterized in that das Absperrventil (50) in einer Gaslagerversorgungsleitung (52) des Verdichters (16) angeordnet ist, durch welche das Kältemittel zum Ausbilden des  the check valve (50) is arranged in a gas bearing supply line (52) of the compressor (16), through which the refrigerant for forming the Gasdrucklagers zuführbar ist.  Gas pressure bearing can be fed. 3. Verdichter (16) nach Anspruch 1 , 3. compressor (16) according to claim 1, dadurch gekennzeichnet, dass  characterized in that das Absperrventil (50) in einer Kältemittelleitung (54) des Verdichters (16) angeordnet ist, durch welche das komprimierte Kältemittel bei aktiviertem Verdichter (16) in Richtung des Hochdruckausgangs (48) strömt.  the shut-off valve (50) is arranged in a refrigerant line (54) of the compressor (16), through which the compressed refrigerant flows in the direction of the high-pressure outlet (48) when the compressor (16) is activated. 4. Verdichter (16) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass 4. compressor (16) according to any one of the preceding claims, characterized in that das Absperrventil (50) als Rückschlagventil ausgebildet ist.  the shut-off valve (50) is designed as a check valve. 5. Verdichter (16) nach einem der Ansprüche 1 bis 3, 5. Compressor (16) according to one of claims 1 to 3, dadurch gekennzeichnet, dass  characterized in that das Absperrventil (50) elektromotorisch oder elektromagnetisch betätigbar ist.  the shut-off valve (50) can be actuated by an electric motor or electromagnetically. 6. Verdichter (16) nach einem der vorhergehenden Ansprüche, 6. compressor (16) according to any one of the preceding claims, dadurch gekennzeichnet, dass  characterized in that der Verdichter (16) als Linearverdichter ausgebildet ist.  the compressor (16) is designed as a linear compressor. 7. Verdichter (16) nach einem der vorhergehenden Ansprüche, 7. compressor (16) according to any one of the preceding claims, dadurch gekennzeichnet, dass  characterized in that der Zylinder (34) eine Buchse (38) umfasst, innerhalb welcher der Kolben (36) angeordnet ist.  the cylinder (34) comprises a bushing (38) within which the piston (36) is arranged. 8. Verdichter (16) nach Anspruch 7, 8. compressor (16) according to claim 7, dadurch gekennzeichnet, dass  characterized in that die Buchse (38) mehrere Öffnungen (40) umfasst, durch welche das Kältemittel zur Ausbildung des Gasdrucklagers in Richtung des Kolbens (36) zuführbar ist.  the bush (38) comprises a plurality of openings (40) through which the refrigerant for forming the gas pressure bearing in the direction of the piston (36) can be fed. 9. Haushaltskältegerät (10) mit einem Verdichter (16) nach einem der 9. domestic refrigeration appliance (10) with a compressor (16) according to one of vorhergehenden Ansprüche.  previous claims. 10. Haushaltskältegerät (10) nach Anspruch 9, 10. Domestic refrigerating appliance (10) according to claim 9, dadurch gekennzeichnet, dass  characterized in that der Verdichter (16) in Strömungsrichtung (30) eines Kältekreislaufs (14) des Haushaltskältegeräts (10) nach einem Verdampfer (24) und vor einem Verflüssiger (20) angeordnet ist, wobei ein weiteres Absperrventil (28) in der  the compressor (16) in the flow direction (30) of a refrigeration circuit (14) of the household refrigerating appliance (10) after an evaporator (24) and in front of a condenser (20) is arranged, wherein a further shut-off valve (28) in the Strömungsrichtung (30) nach dem Verflüssiger (20) und vor dem Verdampfer (24) angeordnet ist.  Flow direction (30) after the condenser (20) and upstream of the evaporator (24) is arranged. 1 1. Verfahren zum Betreiben eines Verdichters (16) eines Kältekreislaufs (14) eines Haushaltskältegeräts (10), mit den Schritten: Komprimieren eines Kältemittels mittels eines innerhalb eines Verdichterraums (32) eines Zylinders (34) bewegten Kolbens (36), welcher in dessen radialer Richtung gegenüber dem Zylinder (34) berührungslos mittels eines aus dem Kältemittel ausgebildeten Gasdrucklagers gelagert wird; 1 1. A method for operating a compressor (16) of a refrigeration cycle (14) of a household refrigerating appliance (10), comprising the steps: Compressing a refrigerant by means of a piston (36) moved within a compressor chamber (32) of a cylinder (34), which is mounted without contact in the radial direction thereof with respect to the cylinder (34) by means of a gas pressure bearing formed from the refrigerant; Betätigen eines Einlassventils (42) des Verdichters (16) zum Regulieren eines Volumenstroms des unkomprimierten Kältemittels von einem  Actuating an inlet valve (42) of the compressor (16) to regulate a volume flow of the uncompressed refrigerant from one Niederdruckeingang (44) des Verdichters (16) in den Verdichterraum (32); Betätigen eines Auslassventils (46) des Verdichters (16) zum Regulieren eines Volumenstroms des komprimierten Kältemittels von dem Verdichterraum (32) zu einem Hochdruckausgang (48) des Verdichters (16);  Low pressure input (44) of the compressor (16) in the compressor chamber (32); Actuating an exhaust valve (46) of the compressor (16) to regulate a volume flow of the compressed refrigerant from the compressor chamber (32) to a high pressure outlet (48) of the compressor (16); dadurch gekennzeichnet, dass characterized in that ein zwischen dem Niederdruckeingang (44) und dem Hochdruckausgang (48) angeordnetes Absperrventil (50) geschlossen wird, sobald der Verdichter (16) deaktiviert wird, wodurch ein Rückströmen des Kältemittels von dem a shut-off valve (50) disposed between the low-pressure inlet (44) and the high-pressure outlet (48) is closed as soon as the compressor (16) is deactivated, whereby a return flow of the refrigerant from the Hochdruckausgang (48) zum Niederdruckeingang (44) bei deaktiviertem High pressure outlet (48) to low pressure inlet (44) with deactivated Verdichter (16) unterbunden wird. Compressor (16) is prevented. Verfahren nach Anspruch 1 1 , Method according to claim 1 1, dadurch gekennzeichnet, dass characterized in that das Absperrventil (50) mit einem vorgegebenen zeitlichen Vorlauf geöffnet wird, bevor der deaktivierte Verdichter (16) zum Komprimieren des Kältemittels wieder aktiviert wird. the shut-off valve (50) is opened with a predetermined time delay before the deactivated compressor (16) is reactivated to compress the refrigerant. Verfahren nach Anspruch 12, Method according to claim 12, dadurch gekennzeichnet, dass characterized in that der zeitliche Vorlauf vor dem Aktivieren des Verdichters (16) so groß gewählt wird, dass mittels des vom Hochdruckausgang (48) in den Verdichter einströmenden Kältemittels das Gasdrucklager zwischen dem Kolben (36) und dem Zylinder (34) ausgebildet wird. the time advance before activation of the compressor (16) is chosen to be so large that the gas pressure bearing between the piston (36) and the cylinder (34) is formed by means of the refrigerant flowing from the high-pressure outlet (48) into the compressor.
PCT/EP2015/050150 2014-01-21 2015-01-07 Compressor for a refrigeration circuit of a domestic refrigerator, domestic refrigerator with a compressor and a method for operating a compressor of a domestic refrigerator Ceased WO2015110284A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801671A (en) * 2015-11-10 2017-06-06 罗伯特·博世有限公司 Piston pump with outlet valve in the piston

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013213380A1 (en) * 2013-07-09 2015-01-15 BSH Bosch und Siemens Hausgeräte GmbH Linear compressor for a household appliance and household refrigeration appliance
JP2016208708A (en) * 2015-04-24 2016-12-08 パナソニックＩｐマネジメント株式会社 Motor drive device and refrigerator using the same
US11806250B2 (en) 2018-02-22 2023-11-07 Warsaw Orthopedic, Inc. Expandable spinal implant system and method of using same
AU2019226102A1 (en) 2018-02-22 2020-08-13 Warsaw Orthopedic, Inc. Expandable spinal implant system and method of using same
US10774873B2 (en) 2018-06-11 2020-09-15 Trane International Inc. Porous gas bearing
US10753392B2 (en) 2018-06-11 2020-08-25 Trane International Inc. Porous gas bearing
US10815831B2 (en) * 2018-12-18 2020-10-27 General Electric Company Bearing support including hermetic squeeze film damper and accumulator volume
US11395743B1 (en) 2021-05-04 2022-07-26 Warsaw Orthopedic, Inc. Externally driven expandable interbody and related methods
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US11291554B1 (en) 2021-05-03 2022-04-05 Medtronic, Inc. Unibody dual expanding interbody implant
US12318308B2 (en) 2020-11-05 2025-06-03 Warsaw Orthopedic, Inc. Dual expandable inter-body device
US11376134B1 (en) 2020-11-05 2022-07-05 Warsaw Orthopedic, Inc. Dual expanding spinal implant, system, and method of use
US12171439B2 (en) 2020-11-05 2024-12-24 Warsaw Orthopedic, Inc. Protected drill
US11638653B2 (en) 2020-11-05 2023-05-02 Warsaw Orthopedic, Inc. Surgery instruments with a movable handle
US11517443B2 (en) 2020-11-05 2022-12-06 Warsaw Orthopedic, Inc. Dual wedge expandable implant, system and method of use
US12121453B2 (en) 2020-11-05 2024-10-22 Warsaw Orthopedic, Inc. Dual wedge expandable implant with eyelets, system, and method of use
US12239544B2 (en) 2020-11-05 2025-03-04 Warsaw Orthopedic, Inc. Rhomboid shaped implants
US11963881B2 (en) 2020-11-05 2024-04-23 Warsaw Orthopedic, Inc. Expandable inter-body device, system, and method
KR102430411B1 (en) * 2020-12-07 2022-08-09 엘지전자 주식회사 Linear compressor
US12268614B2 (en) 2021-06-24 2025-04-08 Warsaw Orthopedic, Inc. Interbody implant with adjusting shims
US12440349B2 (en) 2021-11-01 2025-10-14 Warsaw Orthopedic, Inc. Expandable interbody implant and breakoff screw
US12414863B2 (en) 2021-06-24 2025-09-16 Warsaw Orthopedic, Inc. Expandable interbody implant and corresponding surgical tool
US11612499B2 (en) 2021-06-24 2023-03-28 Warsaw Orthopedic, Inc. Expandable interbody implant
US12485019B2 (en) 2021-06-24 2025-12-02 Warsaw Orthopedic, Inc. Parallel jaw inserter
US12295865B2 (en) 2021-06-24 2025-05-13 Warsaw Orthopedic, Inc. Expandable interbody implant and corresponding inserter
US11730608B2 (en) 2021-07-13 2023-08-22 Warsaw Orthopedic, Inc. Monoblock expandable interbody implant
US11850163B2 (en) 2022-02-01 2023-12-26 Warsaw Orthopedic, Inc. Interbody implant with adjusting shims
CN115247905B (en) * 2022-08-31 2024-06-28 珠海格力电器股份有限公司 Refrigerant circulation system, air conditioning equipment and control method of refrigerant circulation system
CN115717583A (en) * 2022-12-06 2023-02-28 武汉高芯科技有限公司 Gas bearing linear compressor and linear refrigerator

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006009274A1 (en) * 2006-02-28 2007-08-30 BSH Bosch und Siemens Hausgeräte GmbH Linear compressor for cooling device has compressor piston mounted in piston housing with aid of housing with openings, gaseous fluid flowing through openings, outflow device for fluid condensate
WO2008055810A1 (en) * 2006-11-07 2008-05-15 BSH Bosch und Siemens Hausgeräte GmbH Gas thrust bearing and bearing bush therefor
WO2013071385A1 (en) * 2011-11-16 2013-05-23 Whirpool S.A. Restrictor and production process of a fluid leakage restrictor for aerostatic bearings

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005023879A (en) * 2003-07-04 2005-01-27 Matsushita Electric Ind Co Ltd Oilless linear compressor
JP2006022719A (en) * 2004-07-08 2006-01-26 Matsushita Electric Ind Co Ltd Oilless linear compressor
DE102006052430A1 (en) * 2006-11-07 2008-05-08 BSH Bosch und Siemens Hausgeräte GmbH Compressor with gas-bearing piston
US7980093B2 (en) * 2009-09-25 2011-07-19 Whirlpool Corporation Combined refrigerant compressor and secondary liquid coolant pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006009274A1 (en) * 2006-02-28 2007-08-30 BSH Bosch und Siemens Hausgeräte GmbH Linear compressor for cooling device has compressor piston mounted in piston housing with aid of housing with openings, gaseous fluid flowing through openings, outflow device for fluid condensate
WO2008055810A1 (en) * 2006-11-07 2008-05-15 BSH Bosch und Siemens Hausgeräte GmbH Gas thrust bearing and bearing bush therefor
WO2013071385A1 (en) * 2011-11-16 2013-05-23 Whirpool S.A. Restrictor and production process of a fluid leakage restrictor for aerostatic bearings

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801671A (en) * 2015-11-10 2017-06-06 罗伯特·博世有限公司 Piston pump with outlet valve in the piston
CN106801671B (en) * 2015-11-10 2020-09-08 罗伯特·博世有限公司 Piston pump with outlet valve in piston

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