EP4269796A1 - Hubkolbenverdichter für kältemittel - Google Patents

Hubkolbenverdichter für kältemittel Download PDF

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Publication number
EP4269796A1
EP4269796A1 EP23168978.7A EP23168978A EP4269796A1 EP 4269796 A1 EP4269796 A1 EP 4269796A1 EP 23168978 A EP23168978 A EP 23168978A EP 4269796 A1 EP4269796 A1 EP 4269796A1
Authority
EP
European Patent Office
Prior art keywords
suction
recess
lamella
valve plate
contact surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23168978.7A
Other languages
German (de)
English (en)
French (fr)
Inventor
Andreas Becker
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP4269796A1 publication Critical patent/EP4269796A1/de
Pending legal-status Critical Current

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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • F04B27/0531—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders with cam-actuated 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
    • 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
    • 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
    • F04B53/1037—Flap valves
    • F04B53/1047—Flap valves the valve being formed by one or more flexible elements
    • 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
    • F04B53/1087—Valve seats

Definitions

  • the invention relates to a reciprocating piston compressor for refrigerants, comprising a compressor housing with at least one compressor stage, which has at least one cylinder unit, which in turn comprises at least one cylinder chamber, a piston being movably arranged in the cylinder unit, a cylinder drive arranged in the compressor housing for the at least one piston , a valve plate closing the cylinder chamber, which is provided with at least one suction valve, which in turn has a suction opening arranged in the valve plate and which can be closed with a suction lamella and has at least one outlet valve with an outlet opening, the at least one suction valve and the at least one outlet valve of the respective Cylinder chamber are assigned, and a cylinder head arranged on a side of the valve plate arranged opposite the cylinder chamber.
  • valve plate on its side facing the cylinder chamber has a recess which is arranged within an outer contour of a contact surface of the suction lamella assigned to the suction opening and extends from the suction opening and is open towards this contact surface .
  • the advantage of the solution according to the invention can be seen in the fact that with the recess adjoining the suction opening and open towards the contact surface, it is possible to increase the surface with which the refrigerant to be sucked in acts on the suction lamella immediately before it is opened increase and thereby achieve a safer and faster opening of the suction lamella even at low pressures and consequently a better filling of the cylinder chamber.
  • the recess has a recess base that is set back relative to the contact surface of the suction lamella and thus enables the refrigerant to be sucked in to flow into the recess via the suction opening before opening and also to act on the suction lamella in the area of the recess to open it , so that an increased area of influence on the suction lamella is available.
  • the bottom of the recess expediently extends into the suction opening, so that when the suction lamella closes the suction opening, the recess can fill sufficiently quickly with refrigerant to be sucked in and this refrigerant can act on the suction lamella in addition to the refrigerant present in the suction opening to open the suction lamella.
  • the recess starting from the contact surface of the suction lamella, has a depth that is greater than a thickness of a lubricant film that forms between the suction lamella and the contact surface when the suction opening is sealed.
  • This solution has the advantage that it can prevent the recess from filling with lubricant when the suction lamella closes the suction opening, thus preventing the refrigerant from flowing into the recess before the suction lamella is opened.
  • the recess starting from the contact surface of the suction lamella, has a depth that is at least 0.2 mm, in particular at least 0.3 mm.
  • the depth of the recess is a maximum of 40%, in particular a maximum of 50%, of the thickness of the valve plate.
  • a particularly favorable solution provides that the recess runs at a distance from the outer contour of the contact surface of the suction lamella and thus the suction lamella also seals the recess towards the cylinder chamber when closing the suction opening.
  • the recess and the suction opening are surrounded by a contact surface for the suction lamella that is closed around them, so that when the suction opening is closed, the recess is sealed tightly with the necessary security in order to avoid damaging space, as well as sufficient to provide a large contact surface for the suction lamella.
  • the recess has an area on its side facing the suction lamella that is open towards the contact surface of the suction lamella and which is at least 10%, preferably at least 20%, even better at least 50% of the cross-sectional area of the suction opening.
  • the recess could run around the suction opening, but this would be unfavorable in terms of the space available.
  • the recess extends from the suction opening in the direction of a suction blade base.
  • the recess extends from the suction opening over an area of the valve plate which rests on a foot area of the cylinder head on the cylinder head side. This means that the recess can extend over large areas of the valve plate, although on the opposite side of the recess there is a foot area of the cylinder head, which prevents the suction opening itself from being enlarged.
  • the recess extends from the suction opening over an area of the valve plate which delimits an outlet chamber on the side of the cylinder head.
  • the cylinder head is provided with a connection for refrigerant to be sucked in.
  • a suction channel runs through the cylinder head from the connection for the refrigerant to be compressed to the suction opening, the channel cross-section of which corresponds to a maximum of twice, or better a maximum of 1.5 times, a cross-sectional area of the suction opening in order to get the refrigerant to be sucked in as quickly as possible through the cylinder head with little turbulence and thus achieve a quick and safe opening of the suction lamella, especially at low pressures.
  • a suction channel leading to a plurality of suction openings has a cross-sectional area which corresponds to a maximum of twice, even better a maximum of 1.5 times, the sum of the cross-sectional areas of the several suction openings.
  • the suction channel running in the cylinder head is formed into the cylinder head.
  • a further embodiment provides that the suction channel is formed in an insert inserted into the cylinder head.
  • the invention relates to a valve plate for a reciprocating compressor, which comprises a compressor housing with at least one compressor stage, which has at least one cylinder unit, which in turn comprises at least one cylinder chamber, the valve plate closing the cylinder chamber and carrying a cylinder head and being provided with at least one suction valve , which in turn has a suction opening arranged in the valve plate and which can be closed with a suction lamella and is provided with at least one outlet valve with an outlet opening, the at least one suction valve and the at least one outlet valve being assigned to the respective cylinder chamber.
  • valve plate is designed such that it has one or more of the features described above.
  • a cooling unit designated as a whole by 10 comprises a thermally insulated housing 12 which encloses an interior 14 in which temperature-sensitive goods 16 or temperature-sensitive cargo 16 can be stored, the temperature-sensitive goods 16 or the temperature-sensitive cargo 16 being supplied by a gaseous medium 18, in particular Air is surrounded, which is kept at a defined temperature level in order to keep the temperature-sensitive cargo 16 or the temperature-sensitive goods 16 within a certain temperature range.
  • the cooling unit 10 is preferably designed as a transportable cooling unit, for example as a body for a truck or a freight car or as a conventional transport container for transporting temperature-sensitive freight 16 either by a truck or by train or a ship.
  • a circulation stream 22 of the gaseous medium 18 runs in the interior 14, with an inlet stream 26 entering the interior 14 starting from a temperature control unit 24, flowing through it and in turn as an outlet stream 28 the temperature control unit 24 occurs.
  • the circulation flow 22 is generated by a blower unit 32, which is arranged in the temperature control unit 24 and is kept at the desired temperature by an internal heat exchanger 34, which is arranged in the temperature control unit 24.
  • the inlet stream 26 preferably exits the temperature control unit 24 in an area near a top wall 36 of the insulated housing 12 and preferably the circulation stream 22 is returned to the temperature control unit 24 near a bottom wall 38 of the insulated housing 12 and thereby forms the outlet stream 28 flowing back to the temperature control unit 24 .
  • the temperature control unit 24 is arranged near the top wall 36 of the insulated housing 12 and, for example, near a front wall 48 or near a rear wall 48 of the same.
  • a unit unit 52 comprising a refrigerant compressor unit 54 with a refrigerant compressor 56 and an electric drive motor 58 is preferably arranged near the temperature control unit 24 on the thermally insulated housing 12, wherein the unit unit 52 preferably additionally comprises a first external heat exchanger 62 and an external blower unit 64, which For example, an air flow 66 is generated from ambient air, which passes through the first external heat exchanger 62.
  • the refrigerant compressor unit 54, the internal heat exchanger 34 and the first external heat exchanger 62 are arranged in a refrigerant circuit, designated as a whole by 70, of a refrigeration system 60 integrated into the cooling unit.
  • the refrigerant circuit 70 is connected to a high-pressure connection 72 of the refrigerant compressor unit 54, in particular designed as a reciprocating piston compressor, from which a supply line 74 leads to the first external heat exchanger 62, which has a total mass flow G of refrigerant compressed to high pressure PH by the refrigerant compressor 54, in the present case in particular CO 2 , cools, the refrigerant being in a transcritical state in the case of CO 2 .
  • the cooling of the refrigerant in the first external high-pressure side heat exchanger unit 62 can take place either by ambient air or by contact with a heat-absorbing medium of any kind, for example cooling water.
  • the main mass flow H of liquid refrigerant is fed from the intermediate pressure collector 82 to a cooling stage 92, which has a cooling expansion element 94, which increases the main mass flow H by expansion cools to low pressure PN and from which the main mass flow H enters the internal low-pressure side heat exchanger 34, in which it is able to extract heat from the circulation flow 22 in the interior 18 of the cooling unit 10 by providing cooling power.
  • the main mass flow H warmed up in the heat exchanger 34 then enters the refrigerant compressor unit 54 at low pressure PN via a low pressure connection 102.
  • the refrigerant compressor 56 of the refrigerant compressor unit 54 is as in Fig. 2 shown, designed as a reciprocating piston compressor and preferably comprises a first compressor stage 112, formed by two cylinder units 114a and 114b, each driven by a cylinder drive 115a, 115b, in particular an eccentric drive, each of which sucks in the refrigerant of the main mass flow H from a suction chamber 116a, 116b and, for example into a common outlet chamber 118.
  • the first compressor stage 112 compresses the refrigerant supplied to it at low pressure, for example at values of 0.1 bar to 60 bar, from the main mass flow H to a medium pressure PM, which is, for example, at values in the range of 20 bar to 120 bar.
  • the main mass flow H compressed to medium-pressure PM is then fed to a second external medium-pressure-side heat exchanger 124, which, for example, is also arranged in the aggregate unit 52 and, for example, is also flowed through by the external air stream 66.
  • the second external heat exchanger 124 on the medium pressure side makes it possible to cool the refrigerant of the main mass flow H compressed to medium pressure PM to a temperature close to the ambient temperature and to remove a significant part of the heat supplied during compression.
  • the cooled and compressed to medium-pressure PM refrigerant of the main mass flow H is fed via a medium-pressure supply line 126 to a medium-pressure inlet 128 of an overall housing 130 of the refrigerant compressor unit 54, the medium-pressure inlet 128 being arranged in particular on a motor housing 132 of the overall housing 130 of the refrigerant compressor unit 54 is.
  • the medium pressure supply line 126 is also connected to the gas bladder 86 of the intermediate pressure collector 82, so that the additional mass flow Z from the intermediate pressure collector 82 is also supplied to the medium pressure connection 128 of the refrigerant compressor unit 54 via the medium pressure supply line 126 and the medium pressure PM is adjusted, for example, so that it corresponds to the Intermediate pressure PZ corresponds.
  • the medium pressure inlet 128 is preferably arranged on the motor housing 132 in such a way that the incoming coolant enters an engine compartment 134, passes through the engine compartment 134 while cooling the electric drive motor 58, in particular while cooling a rotor 136 and a stator 138 of the same, and then through the entire housing 130, enters a second compressor stage 142 of the refrigerant compressor unit 54.
  • the second compressor stage 142 also includes two cylinder units 144a and 144b, each driven by a cylinder drive 145a, 145b, in particular an eccentric drive, the refrigerant compressed to medium pressure PM and supplied to the second compressor stage 142 being fed into the cylinder units 144a and 144b, for example via inlet chambers 146a and 146b enters, is compressed into this and then exits into an outlet chamber 148, which is connected to the high-pressure connection 72.
  • a cylinder drive 145a, 145b in particular an eccentric drive
  • the cylinder units 114a and 114b of the first compressor stage 112 and the cylinder units 144a and 144b of the second Compressor stage 142 is driven via a common drive shaft 152, in particular an eccentric shaft, acting on the respective cylinder drives 115a, 115b or 145a, 145b, which is preferably connected coaxially and in particular in one piece to a rotor shaft 154 of the rotor 136 and forms an overall drive shaft 188 with it.
  • the cylinder drive chamber 156 which accommodates the drive shaft 152 and the cylinder drives 115a, 115b, 145a, 145b and is adjacent to the cylinder units 114a and 114b or 144a and 144b, is connected or goes to the engine compartment 134 within the overall housing 130 into this, so that the cylinder drive chamber 156 is at medium pressure.
  • the load on the cylinder units 144a and 144b themselves, in particular on the pistons thereof, is lower than in the case of low pressure in the cylinder drive chamber 156.
  • this is designed as a semi-hermetic compressor, in which the refrigerant compressor 56 and the electric drive motor 58 are arranged in the overall housing 130, which has a housing sleeve 162, bearing caps 164 and 166 arranged on both sides of the housing sleeve 162 and on the bearing caps 164 and 166 include molded bearing receptacles 174 and 176, for example made of aluminum are formed, with rolling bearings 184 and 186 being arranged in the bearing receptacles 174 and 176, which in this case support an overall drive shaft 188, comprising the drive shaft 152 and the rotor shaft 154.
  • cylinder heads 192 and 194 are arranged on the housing sleeve 162, which are also made of aluminum, for example, the cylinder head 192 being assigned to the cylinder units 114a and 114b and having the low-pressure connection 102, which is connected to the inlet chambers 116a and 116b, as well as the Has outlet chamber 118, which is connected to the medium pressure outlet 122.
  • the cylinder head 194 is associated with the cylinder units 144a and 144b, with the inlet chambers 146a and 146b being connected to the engine compartment 134 and/or the cylinder drive compartment 156 and the outlet chamber 148 being connected to the high pressure port 72.
  • a converter 212 is provided in particular, which is preferably also arranged in the aggregate unit 52.
  • the electric drive motor 58 can be operated in a speed-controlled manner and thus the cooling capacity of the refrigerant compressor unit 54 can also be continuously controlled within a intended performance range.
  • each of the cylinder units 114 has a cylinder 224 provided in a cylinder block 222, for example formed by the overall housing 130, in which a piston 226 is movable, the piston delimiting a cylinder chamber 228 which is between the piston 226 and one of the respective Cylinder 224 final valve plate 232 lies, the valve plate being sealed relative to the cylinder block 222, for example via a seal 234.
  • the valve plate 232 is provided with a suction valve 240 for sucking in the refrigerant, which has a suction opening 242a with a suction lamella 246a assigned to it and also an outlet valve 243 with an outlet opening 244 and an outlet lamella (not shown).
  • the suction opening 242 can be sealed by the suction lamella 246, which is arranged on the valve plate 232 on a side facing the cylinder chamber 228 and is firmly connected to the valve plate 232 in the area of a suction lamella base 252 and then extends from the suction lamella base 252 via the suction opening 242 extends to a suction lamella end 254a and thereby closes the suction opening 242, in Fig. 3 position shown extends over the suction opening 242 and rests on a contact surface 256a of the valve plate 232 to seal the suction opening 242.
  • the contact surface 256 is formed by a partial area of the side 258 of the valve plate facing the cylinder chamber 228, which extends over the cylinder chamber 228.
  • the contact surface 256 on the side 258 of the valve plate 232 is limited by an outer contour of the respective suction lamella 246 and by the suction opening 242.
  • two suction blades 246a and 246b are provided, which serve to close two suction openings 242a and 242b leading into the cylinder chamber 228, for example the two suction blade feet 252a and 252b are additionally connected to one another, while the suction blade ends 254a and 254b are movable relative to one another .
  • the suction blade end 254a, b as shown in, for example Fig. 3 shown in connection with the suction blade end 254a, in a recess 264 arranged, which forms a stop surface 266 in order to limit the movement of the respective suction lamella, in this case the suction lamella 246a, when releasing the respective suction opening, for example the suction opening 242a.
  • two suction openings 242a and 242b are provided for the respective cylinder 224 in order to provide the largest possible inflow cross section.
  • three outlet openings 244 are provided in order to also provide an optimal outlet cross section for the pressurized refrigerant.
  • the spatial conditions for creating a sufficient cross section for the suction openings 242 and the outlet openings 244, which must all lie within the outer contour of the respective cylinder chamber 228, are also limited.
  • a partition 272 is provided for separating, for example, the suction chamber 116a from the outlet chamber 118, which inevitably extends to the valve plate 232 and is sealed relative to the valve plate 232 by means of a seal 274 for sealing the entire cylinder head 192.
  • a recess 282 adjoining the respective suction opening 242 is provided, for example the Depression 282a, or depression 282b in Fig.
  • the recess 282a, b in the contact surface 256a, b of the respective suction lamella 246a, b preferably has an outer contour 286 which encloses at least 20% of a cross-sectional area of the suction opening 242a, b, so that the force on the respective suction lamella 246a, b is significantly enlarged when lifting from the respective contact surface 256a, b and thus the suction lamella 246a, b can be opened more quickly during the suction process.
  • the respective suction opening 242a, 242b and the associated recess 282a, 282b are surrounded together by a closed, circumferential contact surface 288a or 288b , which is part of the contact surface 256a, 256b and thus ensures a reliable and good seal between the respective suction lamella 246a or 246b and the corresponding contact surface 256a or 256b when the suction opening 242a or 242b is closed by the respective suction lamella 246a or 246b and also also ensures that the respective suction lamella 246a or 246b has a sufficiently large flat contact surface 256a or 256b in order to avoid damage to the respective suction lamella 246a or 246b.
  • the respective recess 282a or 282b extends in the direction of the respective suction plate base 252a, b and in particular - as described - over the area of the side 258 of the valve plate 232 facing the cylinder chamber 228, on the opposite side of which the partition 272 is located of the cylinder head 192 is supported.
  • the recesses 292a and 294a As an alternative to the formation of the recesses 282a, 282b in the first exemplary embodiment, there is a second, in Fig. 6 illustrated embodiment, the possibility of providing recesses 292a and 294a as well as 292b and 294b, the recesses 292a and 292b extending in the same way as the recesses 282a and 282b in the direction of the respective suction blade base 252a and 252b, while the recesses 294a and 294b extend outward extend from the respective suction opening 242a or 242b in the direction of the respective suction lamella end 254a or 254b.
  • recesses 296a and 296b are provided, which extend from the respective suction opening 242a and 242b over a distance in the direction of the respective suction lamella base 252a and 252b, which is larger than a diameter of the respective Suction opening 242a and 242b, for example, even has an extension in the direction of the respective suction lamella base 252a and 252b, which is larger is as a double diameter of the suction opening, the recesses 296a and 296b each lying within the contact surface 256 and also being surrounded by a contact surface 288a or 288b that runs around it in order to provide a sufficiently large sealing surface for sealing the suction opening 242a or 242b and the recess 296a or 296b relative to the cylinder chamber 228.
  • the recesses 296a and 296b extend into an area of the side 258 of the valve plate 232 facing the cylinder chamber 228, on the opposite side of which the outlet chamber 118 lies in the cylinder head 192.
  • the cylinder head 192 ' is modified in that instead of the inlet chambers 116a and 116b, a suction channel 302 is provided, which extends as directly as possible from an external suction port 304 provided on the cylinder head 192 to the suction opening 242, so that a low-turbulence, if non-turbulence-free flow guidance for the refrigerant to be sucked in from the outer suction connection 304 to the respective suction opening 242 is given, which promotes an advantageous low-turbulence, preferably turbulence-free flow of the refrigerant from the outer connection 304 to the suction opening 242, and a warming up of the same in the cylinder head 192 reduced.
  • the suction channel 302 is formed, for example, in the cylinder head 192 '.
  • the inlet channel 302 preferably has a flow cross-sectional area that corresponds to at least one flow cross-sectional area of the respective suction opening 242 and is at most twice, even better 1.5 times, the flow cross-sectional area of the suction opening 242.
  • an external connection 306 is provided on the cylinder head 192", from which two suction channels 312 and 314 branch off, each of which leads to a suction opening 242 for different cylinders 224.
  • the suction channels 312 and 314 are, for example, at least substantially formed in an insert 316 which is inserted into the cylinder head 192".
  • a flow cross-sectional area of the outer connection 306 corresponds at least to the flow cross-sectional area in the suction channels 312 and 314 in order to achieve the lowest possible turbulence, preferably turbulence-free flow through the cylinder head 192" with as little heating of the sucked-in refrigerant as possible.
  • the flow cross-sectional area of the outer connection 306 is preferably a maximum of twice, even better a maximum of 1.5 times, the sum of the flow cross-sectional areas of the suction channels 312, 314.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP23168978.7A 2022-04-25 2023-04-20 Hubkolbenverdichter für kältemittel Pending EP4269796A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102022109938.5A DE102022109938A1 (de) 2022-04-25 2022-04-25 Hubkolbenverdichter für Kältemittel

Publications (1)

Publication Number Publication Date
EP4269796A1 true EP4269796A1 (de) 2023-11-01

Family

ID=86095832

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23168978.7A Pending EP4269796A1 (de) 2022-04-25 2023-04-20 Hubkolbenverdichter für kältemittel

Country Status (4)

Country Link
US (1) US20230341156A1 (zh)
EP (1) EP4269796A1 (zh)
CN (1) CN116950877A (zh)
DE (1) DE102022109938A1 (zh)

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JPH0589876U (ja) * 1992-05-06 1993-12-07 株式会社豊田自動織機製作所 ピストン式圧縮機の吸入リード弁機構
DE19644431A1 (de) * 1995-10-26 1997-04-30 Toyoda Automatic Loom Works Verstellkompressor
US5722818A (en) * 1995-09-05 1998-03-03 Sanyo Electric Co., Ltd. Suction valve arrangement for a hermetic compressor
US6565336B1 (en) * 1998-05-06 2003-05-20 Carrier Corporation Normally unseated suction valve
US20080277008A1 (en) * 2001-10-05 2008-11-13 Carrier Corporation Multi-port suction reed vavle with optimized tips
WO2017056809A1 (ja) * 2015-09-28 2017-04-06 日立工機株式会社 空気圧縮機

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Publication number Priority date Publication date Assignee Title
US3241748A (en) 1964-07-27 1966-03-22 Carrier Corp Hermetic motor compressor unit
JP5756737B2 (ja) 2011-11-17 2015-07-29 株式会社豊田自動織機 圧縮機

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DE19644431A1 (de) * 1995-10-26 1997-04-30 Toyoda Automatic Loom Works Verstellkompressor
US6565336B1 (en) * 1998-05-06 2003-05-20 Carrier Corporation Normally unseated suction valve
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WO2017056809A1 (ja) * 2015-09-28 2017-04-06 日立工機株式会社 空気圧縮機

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