EP2828528B1 - Compresseur frigorifique - Google Patents

Compresseur frigorifique Download PDF

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Publication number
EP2828528B1
EP2828528B1 EP13711632.3A EP13711632A EP2828528B1 EP 2828528 B1 EP2828528 B1 EP 2828528B1 EP 13711632 A EP13711632 A EP 13711632A EP 2828528 B1 EP2828528 B1 EP 2828528B1
Authority
EP
European Patent Office
Prior art keywords
housing
compressor
sound absorber
unit
accordance
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP13711632.3A
Other languages
German (de)
English (en)
Other versions
EP2828528A1 (fr
Inventor
Dominic Kienzle
Ashraf AGHA
Stephan Rölke
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
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Publication date
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Publication of EP2828528A1 publication Critical patent/EP2828528A1/fr
Application granted granted Critical
Publication of EP2828528B1 publication Critical patent/EP2828528B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/083—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using transversal baffles defining a tortuous path for the gases or successively throttling gas flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/089—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling using two or more expansion chambers in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/002—Apparatus adapted for particular uses, e.g. for portable devices driven by machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/007—Apparatus used as intake or exhaust silencer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/02—Two or more expansion chambers in series connected by means of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/08—Two or more expansion chambers in series separated by apertured walls only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2490/00—Structure, disposition or shape of gas-chambers
    • F01N2490/20—Chambers being formed inside the exhaust pipe without enlargement of the cross section of the pipe, e.g. resonance chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/804—Accumulators for refrigerant circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses

Definitions

  • the invention relates to a refrigerant compressor, comprising an overall housing, a screw compressor provided in the overall housing with a compressor housing formed as part of the overall housing, in which at least one screw rotor bore is arranged, with at least one screw rotor rotating in the screw rotor bore about an axis of rotation, with one on the Compressor housing arranged on the suction side bearing unit for the screw rotor, with at least one arranged on the compressor housing pressure side bearing unit for the screw rotor and with a provided on the compressor housing housing window for compressed refrigerant and arranged in the overall housing first muffler unit.
  • Such refrigerant compressors are known from the prior art, for example DE 103 59 032 A1 known.
  • the documents JP08028479A J and GB2186031A show a refrigerant compressor with the features described in the preamble of claim 1.
  • the invention is therefore based on the object to further improve a refrigerant compressor of the generic type with respect to the sound attenuation.
  • the muffler unit is designed as a passage damper, which has a plurality of through-holes, each followed by an expansion chamber that more of the expansion chambers of the muffler unit have different volumes and that the inlet opening and the outlet opening each form a passage opening.
  • the advantage of the solution according to the invention is that the muffler unit achieves its damping function by virtue of cross-sectional jumps occurring between the passage openings and the expansion chambers and between the expansion chambers and the passage openings, the degree of damping being dependent on the area ratio of the cross-sectional jumps.
  • a further advantage of the invention is that the silencer unit has a plurality of expansion chambers with different volumes, so that the damping characteristics can thus be tuned to different frequencies in a simple manner.
  • the different volume of the plurality of expansion chambers can be achieved in particular advantageously in that the expansion chambers with different volumes have a different extent in the flow direction.
  • this opens up the possibility that the pressure pulsations do not propagate over a significant part of the refrigerant compressor, but are attenuated substantially immediately after their formation in the region of the outlet window and the passage through the housing window, so that the spread in the overall housing of the refrigerant compressor of sound is largely reduced.
  • the silencer unit With regard to the specific arrangement of the silencer unit so far no further details have been made.
  • an advantageous solution provides that the first silencer unit is arranged in a silencer housing adjoining the compressor housing in the region of the housing window.
  • Such a silencer housing can be formed and held in various ways. So could be a gap between the housing window and the muffler housing.
  • An advantageous solution provides that the muffler housing tightly engages over the housing window and consequently the muffler housing itself receives the compressed and pressure pulsations having refrigerant directly on the housing window and tightly abuts around the housing window around.
  • the muffler housing itself forms the inlet opening, the outlet opening and the at least one chamber, that is to say that no additional insert parts are required in the muffler housing, but the muffler housing forms the inlet opening, the outlet opening and the at least one chamber as a unitary component ,
  • the silencer housing is arranged next to a bearing housing accommodating at least one pressure-side bearing unit, that is, that the bearing housing for the at least one pressure-side bearing unit seen in the direction of the axes of rotation of the screw rotor, and the silencer housing not consecutive, but lying side by side and thus are arranged side by side in a direction transverse to the axes of rotation.
  • the muffler housing could be fixed to the pressure housing.
  • both the muffler housing and the bearing housing are preferably held adjacent to the compressor housing.
  • the muffler housing and the bearing housing in a simple manner next to each other, provides a particularly favorable solution that the muffler housing and the bearing housing as parts of a Combined housing are formed, that is, both the bearing housing for the bearing units and the muffler housing for the at least one muffler unit is realized by the combined housing.
  • this enables a cost-effective production of the combined housing and, on the other hand, also simplifies the assembly of the bearing housing and the muffler housing, in particular if both of these are held on the compressor housing.
  • the combined housing is designed in several parts.
  • the combined housing comprises a base housing and a cover, so that thereby simplify the manufacture and assembly of the combined housing.
  • base housing and the cover housing are separable by a transverse to the axis of rotation of the at least one screw rotor separating plane.
  • At least part of the chambers of the silencer unit is formed in the base housing.
  • the silencer unit according to the invention can be realized very simply and inexpensively.
  • the base housing is an integral part.
  • the base part can be formed as a casting, in which the chambers and the partitions and the respective part of the bearing housing are formed, so that so that the base housing together with the respective part of the muffler unit and the cover is very easy to produce.
  • the cover housing is an integral part.
  • the second silencer unit is formed.
  • the cover housing is made as a casting, in which, for example, the corresponding part of the bearing housing and also the corresponding part of the silencer unit is formed.
  • the first silencer unit has a receiving chamber adjoining the outlet window, to which the inlet opening follows, so that the first silencer unit can be adapted to the outlet window in a simple manner, the receiving chamber compacting the same Receives gas or refrigerant from the outlet window and the inlet opening of the first silencer unit supplies, so that the receiving chamber provides in particular for an adaptation of the cross sections of the outlet window to the cross section of the inlet opening.
  • a particularly advantageous arrangement of the first muffler unit according to the invention provides that it is arranged so that the compressed refrigerant can flow in a flow direction which is transverse to a pressure side wall of the compressor housing and away, in particular approximately parallel to a rotation axis of the at least a screw rotor, that is in a direction which forms an angle of at most 30 ° with the axis of rotation runs.
  • the first muffler unit according to the invention can be arranged in a particularly space-saving manner.
  • the first muffler unit extends in the direction parallel to the rotational axes of the screw rotor over approximately the same distance as the bearing housing in order to achieve a space-saving solution.
  • the muffler unit is designed so that immediately after each expansion chamber, a through hole follows.
  • the silencer unit in particular in the realization of the silencer unit in the combined housing, can be designed such that each through opening opening into an expansion chamber passes without supernatant into a chamber wall of the respective expansion chamber, so that the expansion chamber and the through openings can be easily, that is in particular without undercuts as a one-piece part, in particular as a casting, produce.
  • the silencer unit according to the invention is particularly easy to produce if several of the through-openings of the silencer unit have identical cross-sections.
  • the silencer unit comprises a pipe section which extends from the inlet opening to the outlet opening and forms a throughflow channel which has shell-side openings which are arranged in at least one in the at least one chamber and lead to the pipe section adjacent damping chamber.
  • the muffler unit no longer works as a passage damper but as a branch resonator or Helmholtz resonator, in which the damping chamber across the openings to the flow channel across the Coupled flow direction and thus dampens the pressure pulsations in the flow channel in the case of a defined by the apertures and the damping chamber resonance condition.
  • the pipe section passes through a plurality of chambers, each of which forms an adjacent to the pipe section damping chamber.
  • the damping chambers are separated from each other in several damping chambers.
  • the muffler unit has at least two damping chambers, which have a different volume.
  • the different volume of the damping chambers can be realized in that they have a different extent in the longitudinal direction of the pipe section.
  • the overall housing in such a way that it forms the muffler housing with one part.
  • the muffler housing and the bearing housing are combined to form a combined housing
  • a further advantageous solution provides that the muffler housing is disposed within a pressure housing of the overall housing, that is, that within the pressure housing still the muffler housing is formed as a separate housing.
  • the muffler housing is surrounded by a pressure chamber located in the pressure chamber, wherein the pressure chamber ensures that a sound attenuation occurs between the muffler housing and the pressure housing.
  • the pressure chamber is a space in which the compressed gas or refrigerant enters only after passing through the muffler unit and thus the muffler housing, so that in the pressure chamber, the pressure pulsations of the compressed gas or refrigerant are already damped by the muffler unit.
  • a further advantageous solution provides that in the pressure housing, a Schmierstoffabscheideiki is arranged.
  • a lubricant separation can be combined with a sound attenuation in a simple manner.
  • the Schmierstoffabscheidetician is arranged so that it is arranged downstream of the at least one silencer unit, so that the compressed gas or refrigerant on reaching the Schmierstoffabscheideech no longer has pressure pulsations, which is advantageous for a lubricant separation, since pressure pulsations in the Schmierstoffabscheideischen cause already deposited lubricant is again entrained by the compressed gas or refrigerant due to the pressure surges.
  • An in Fig. 1 to 3 illustrated embodiment of a refrigerant compressor according to the invention comprises an overall housing 10 which comprises a compressor housing 12, a motor housing 14 arranged on one side of the compressor housing 12 and a pressure housing 16 arranged on a side of the compressor housing 12 opposite the motor housing 14.
  • the compressor housing 12, the motor housing 14 and the pressure housing 16 separate parts of the overall housing 10 and the Forming the same be composed of it or the compressor housing 12 and the motor housing 14 and / or the compressor housing 12 and the pressure housing 16 may be formed as a continuous parts.
  • the motor housing 14 carries in the region of a partial circumference a control housing 18, in which a control for the refrigerant compressor is arranged.
  • the motor housing 14 encloses an engine compartment 20 and is closed at its end facing away from the compressor housing 12 by a front wall of the motor housing 14 forming frontal cover 22, which in turn is provided with a suction gas connection 24, via which the refrigerant compressor to be sucked refrigerant can be supplied.
  • the suction gas connection 24 is preferably provided with a shut-off valve 26, which is connected to a suction gas line leading to the refrigerant compressor, not shown in the drawings.
  • the possible in different rotational positions mountability of the shut-off valve 26 can be realized that at equal angular intervals about the axis 28 arranged retaining screws 32a, 32b, 32c and 32d are arranged, with which the shut-off valve 26 in the four rotated by 90 ° rotational positions relative to the lid 22 is mountable.
  • the pressure housing 16 is detachably connected to the compressor housing 12, via a pressure housing flange 34 which is connectable to a mounting flange 36 of the compressor housing 12, starting from the pressure housing flange 34, the pressure housing 16 in the form of a cylindrical, end closed by an end wall 48 Capsule 38 extends.
  • the pressure housing 16 carries a compressed gas connection 42, to which a pressure-gas-side shut-off valve 44 can be mounted.
  • the capsule 38 is also still accessible in the region of its end wall 48 opposite the compressor housing 12 with an access cover 46 accessible ( Fig. 1 and 4 ).
  • the drive shaft 58 passes through the rotor 56 in the direction of the motor shaft 54 and on the other hand extends into the compressor housing 12 of a screw compressor designated as a whole by 60.
  • the drive shaft 58 In its extending in the compressor housing 12 area, the drive shaft 58 carries a screw rotor 62 which is disposed in the compressor housing 12 in a helical bore 64 and in this about a coincident with the motor shaft 54 axis of rotation 63 is rotatable.
  • the drive shaft 58 extends on its opposite side of the electric motor 50 on the screw rotor 62 and forms an end portion 66 which is rotatably mounted in a disposed within the pressure housing 16 bearing housing 68, for this purpose in the bearing housing 68, a pressure-side bearing set 72nd is provided.
  • the drive shaft 58 is mounted between the screw rotor 62 and the rotor 56 in a suction-side bearing set 74 which is subsequently arranged on a suction side of the screw rotor 62.
  • suction side bearing set 74 is held on a suction side wall 76 of the compressor housing 12, while the pressure side bearing set 72 is held on a pressure side wall 78, for which purpose the bearing housing 68 is supported by the pressure side wall 78.
  • the drive shaft 58 still has a beyond the rotor 56 also extending end portion 82, which in turn is mounted in a guide bearing 84 which sits in a coaxial with the motor shaft 54 arranged bearing receptacle 86, the fixed is arranged on the motor housing 14, close to the lid 22nd
  • bearing receiver 86 could be supported directly independent of the cover 22 on the motor housing 14.
  • the bearing stock name 86 is as in FIG Fig. 5 .
  • the bearing receptacle 86 comprises a receiving bottom 85, which is supported by the webs 88a, 88b and 88c, and an annular body 87, which encloses the guide bearing 84 radially outboard.
  • a suction opening 94 is also provided, to which the suction gas connection 24 connects and thereby aligned with this.
  • the bearing receptacle 86 is held at such a distance from the lid bottom 92 that forms between lid bottom 92 and bearing receptacle 86 in the direction of the motor shaft 54 and the motor axis 54 extending inflow space of itself between the in Surrounding direction of successive webs 88 extending inflow openings 96 a, 96 b and 96 c is surrounded, through which the suction gas with respect to the motor axis 54 axial and radial component, as in Fig. 8 represented by dashed lines, can enter into an end-side interior 100 of the engine compartment 20.
  • a suction gas filter 98 is arranged around the bearing receptacle 86 in the interior 100, through which the suction gas has to flow.
  • the suction gas flows as in Fig. 5 and 8th shown in dashed lines, from the shut-off valve 26 in the direction parallel to the motor shaft 54 through the suction gas port 24 and the suction port 94 into the inflow space 90 which is disposed between the suction port 94 and the bearing receptacle 86.
  • the suction gas then flows with a component running obliquely to the motor axis 54 through the inflow openings 96 into the interior 100, forming a plurality of flow paths S.
  • This flow path S1 also flows to the rotor 56 at its end facing away from the compressor housing 104.
  • a flow path S2 flows to the stator 52 in the region of its winding heads 102 facing away from the compressor housing 12 in order to cool them.
  • a further flow path S3 opens up the possibility of flowing through a gap 108 between the rotor 56 and the stator 52 in the direction of the compressor housing 12, thereby also providing both cooling of the stator 52 and cooling of the rotor 56.
  • stator 52 flows around in the region of radially outwardly extending recesses 106 in the direction of the compressor housing 12 and thereby cooled radially outboard.
  • the intake opening 94 in the cover 22 is preferably arranged such that the motor shaft 54 passes through it, in particular the intake opening 94 is arranged coaxially to the motor shaft 54, so that approximately rotationally symmetrical flow conditions arise in the region of the inner space 100 and the bearing receptacle 86 relative to the motor axis 54.
  • the guide of the suction gas for the formation of the flow paths S takes place on the one hand by the receiving bottom 85 and the annular body 87 of the bearing receptacle 86, which form the Sauggasstrom facing flow guide surfaces 89, as well as through flow guide surfaces 99, which are formed after the suction port 94 in the lid bottom 90 and expand progressively from the intake opening 94 with increasing extent in the direction of the compressor housing 12.
  • the suction gas collects in the region of the compressor housing 12 facing winding heads 112 of the stator 52 in a compressor housing side interior 116 of the motor housing 14 and is able to cool these winding heads 112, before the sucked gas - or refrigerant, as in Fig. 10 represented by through holes provided in the suction side wall 76 of the compressor housing 12 114a, 114b and 114c passes, thereby entering a suction chamber 118 of the compressor housing 12.
  • a second, cooperating with this and arranged in a screw rotor bore 120 screw rotor 122 is provided, wherein the second screw rotor 122 about a motor axis 54 and the rotation axis 63 parallel axis of rotation 123 by means of an end over the screw rotor 122nd protruding bearing shaft 124 is mounted in a pressure-side bearing set 126 and a suction-side bearing set 128 is mounted.
  • the two screw rotors 62 and 122 now work together in such a way that refrigerant or gas is sucked in from the suction space 118, compressed by the intermeshing screw rotors 62 and 122 and defined as compressed gas or refrigerant in the region of a pressure-side outlet window 132, by the peripheral regions and end side regions free on the pressure side the screw rotor 62, 122 exits into the compressor housing 12, and from the compressor housing 12 passes through a housing window 133 in the pressure housing 16.
  • a slider 134 is further provided for this purpose, the training and function, for example, in the German patent application 10 2011 051 730.8 is described.
  • a first silencer unit 140 is provided immediately after the housing window 133 in the pressure housing 16, which housing chamber 138 adjoins the housing window 133, one on the housing window 133 opposite side of the receiving chamber 138 arranged inlet port 142 and an outlet port 144, which in a transverse to the pressure side wall 78 and directed away therefrom, in particular to the motor axis 54 parallel flow direction 146 are flowed through, between the inlet port 142 and the outlet port 144, for example a plurality of chambers 148a and 148b, 150a, 150b and 150c, which flare transversely to the flow direction 146, are provided, and each of the chambers 148 and 150 is, as in FIG Fig. 12 shown separated by a partition 152 from the nearest chamber 148, 150, wherein each partition wall 152 has a flow-restricting passage opening 154 through which the compressed gas or refrigerant can pass from one
  • the passage openings 154 are each designed so that their extent in the flow direction 146 corresponds to the thickness of the partition wall 152, so that the passage openings transition into wall surfaces of the partition wall 152 free of protrusions.
  • inlet opening 142 and the outlet opening 144 pass over into the wall surface of the respectively adjacent chamber 148 or 150 without any protrusion.
  • the chambers 148, 150 have different chamber volumes.
  • Such different chamber volumes can be achieved, for example, in that the chambers 148, 150 have the same dimensions transversely to the flow direction 146 or radially to the latter, but have different dimensions in the direction of the flow direction 146.
  • the inlet port 142, the through holes 154, and the outlet port 144 are coaxial with a center axis 156, and similarly, the chambers 148 and 150 are coaxial with the center axis 156, so that the first muffler unit 140 is rotationally symmetric to the central axis 156.
  • central axis 156 extends parallel to the axes of rotation 63 and 123 of the screw rotors 62 and 122 and thus parallel to the motor axis 54.
  • the chambers 148 and 150 have an inside diameter D ik that is more than 1.3 times, more preferably more than 1.4 times an inside diameter D id of the through holes 154, and the inlet port 142 and the outlet port 144.
  • an extension A K148 of the individual chambers 148 is more than about 0.2 times, more preferably more than about 0.23 times the inside diameter D ik of the chambers 148, 150.
  • the extent of the chambers 148, 150 in the direction of the central axis 156 corresponds to the inner diameter D ik of the chambers 148, 150, even better is a maximum value of D ik of the half of the inner diameter D ik of the chambers 148.
  • the extension A k150 of the chambers 150 is more than about 0.1 times the inner diameter D ik of the chambers 150.
  • a second muffler unit 160 which has a transverse flow chamber 162 adjoining the outlet opening 144, through which the compressed gas or refrigerant exiting the first muffler unit 140 moves in a direction of flow 164 transverse to the flow direction 146 in the direction of an outlet 166 of the second silencer unit 160, from which then the compressed gas or refrigerant in a channel 168, for example, formed by a tube 172 to the end wall 48 of the capsule 38 is guided and there radially through openings 174 in the tube 172nd exits and enters a tube 172 enclosing the pressure chamber 176 of the pressure housing 16.
  • a Schmierstoffabscheideiki 180 is disposed in the pressure chamber 176 of the pressure housing, which, for example, two sets of porous gas-permeable structures 182 and 184, for example of metal, which results in a deposition of lubricant mist from the pressurized gas or refrigerant.
  • the pressurized gas or refrigerant After flowing through the Schmierstoffabscheideiki 180 then the pressurized gas or refrigerant has the ability to exit via the pressure gas port 42 from the pressure housing 16.
  • the lubricant that collects in the lubricant separation unit 180 forms a downstream portion of the pressure housing 16 and the compressor housing 12 a lubricant bath 190 from which lubricant is received, filtered by a filter 192, and used for lubrication.
  • both the first muffler unit 140 and the second muffler unit 160 are arranged in a muffler housing 200, which is integrated, for example, in the bearing housing 68 or molded onto it, so that the bearing housing 68 and the muffler housing 200 together form a combined housing 210 which within the pressure housing 16 is arranged and in turn is supported by the pressure-side wall 78 of the compressor housing 12.
  • the combined housing 210 can be constructed on the one hand to form the bearing housing 68 and on the other hand to form the muffler housing 200 in a variety of ways.
  • the combined housing 210 is constructed in two parts and includes a base housing 212 which is connected to the pressure side wall 78 of the compressor housing 12 and which receives the pressure side bearing sets 72 and 126 and also a portion of the chambers 148 and 150, for example the chambers 148 and a Part of the chambers 150.
  • a cover housing 214 which receives the transverse flow chamber 162 and a part of the chambers 150 and forms a cover for the pressure-side bearing sets 72 and 126, is then seated on the base housing 212 fixedly connected thereto.
  • the tube 172 then extends in the direction of the end wall 48.
  • the base housing 212 and the cover housing 214 are separable by a geometric separation plane 216 which extends transversely, preferably perpendicular to the axes of rotation 63, 123 of the screw rotor 62, 122.
  • the combined housing 210 can be advantageously produced as a casting, in which the muffler units 140, 160 and the bearing housing 68 are formed near the final contour near the mold.
  • the combined housing 210 ' is formed so that the parting plane 216' between the base housing 212 'and the Cover housing 214 'runs at such a distance from the compressor housing 12, that all chambers 148 and 150 of the first muffler unit 140 are located in the base housing 212 and also the outlet opening 144 in the base housing 212' is located, so that in the cover housing 214 'nor the Querströmhunt 162 of the muffler unit 160 is disposed and the outlet 166 of the second muffler unit 160th
  • the part of the bearing housing 68 which is arranged in the base housing 212 ', such an extent that the bearing sets 72 and 126 are arranged in this and the Abdeckgekoruseteil 214' only one cover of the bearing housing 68 includes, which the rest, in the Base housing 212 'arranged part of the bearing housing 68 covers.
  • the second embodiment is formed in the same manner as the first embodiment, so that the contents of the statements relating to this in connection with the first embodiment can be made and identical reference numerals are used for identical parts.
  • the combined housing 210 is differently shaped, in such a way that the base housing 212" from the compressor housing 12 has a minimal extent and thus with respect to the first muffler unit 140 includes only the receiving chamber 138, while already the inlet port 142 and thus the chambers 148 and 150 are arranged in the cover housing 214 ", and also the cover housing 214" also still the entire second muffler unit 160, in particular with the transverse flow chamber 162 and the outlet 166, receives.
  • the muffler units 140 and 160 are formed as so-called passage damper, that is, between the inlet port 142 and the outlet port 144 at least one chamber, for example, the chambers 148 and 150 are located, which in turn are separated by passage openings 154 from each other such that the compressed gas or compressed refrigerant undergoes a flow constriction with subsequent expansion several times as it flows through the muffler units 140 and 160, with subsequent expansion.
  • a first muffler unit 240 is provided, which although also in a direction parallel to the axes of rotation 63 and 123 of the screw rotor 62 and 122 flow direction 146 can flow, but operates on a different principle ,
  • a pipe section 242 which forms a throughflow channel 244 which extends between the inlet opening 142 and the outlet opening 144 extends between the inlet opening 142 and the outlet opening 144 and through the through openings 154 and the chambers 148 and 150 extends.
  • the pipe section 242 is in turn provided with a plurality of apertures 246 which connect to one or more damping chambers 248 and 250 annularly surrounding the pipe section 242 and lying in the chambers 148 and 150 and around the pipe section 242, the chambers 148 and 150 are formed in the muffler housing 200 in the same manner as in the above embodiments.
  • annular volume of the damping chambers 248 and 250 via the each of the damping chambers 248 and 250 associated number of openings 246 is coupled to the flow channel 244, wherein the natural resonance of the Helmholtz resonator of the respective annular volume of the damping chamber 248 and 250, of the cross-sectional area with which the respective chamber is coupled to the flow channel 244, that is on the sum of each of the damping chambers 248 and 250 associated apertures 246 and the radial extent of the apertures 246 in the pipe section 242 depends.
  • the damping of the first silencer unit 240 can thus be determined by a suitable choice of the damping chambers 248 and 250 as well as the number of openings 246 in the pipe section 242.
  • the second muffler unit 160 is still provided, and the muffler housing 200 is further part of the combined housing 210 formed by the base housing 212 and the cover housing 214 in the same manner as in the above embodiments.
  • the muffler unit 240 also works as a Helmholtz damper, wherein in the same manner as in the fourth embodiment of the pipe section 242 is provided which has openings 246 and the flow channel 244 forms.
  • the apertures 246 couple to three annular attenuation spaces 248, 250, and 252 of different sizes, thus providing the ability to adjust the attenuation to different frequencies of the compressed gas or refrigerant.
  • the number and the volume of the damping chambers 248, 250 and 252 vary depending on the frequencies to be damped.
  • a damping chamber 248 is provided, which is coupled via the openings 246 of the tube section 242 to the flow channel 244, wherein in this solution primarily the damping is tuned to a frequency.
  • the seventh embodiment is formed in the same manner as the sixth embodiment, so that full content can be made to the comments on the sixth embodiment reference.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (15)

  1. Compresseur frigorifique comprenant un carter général (10), un compresseur à vis (60), prévu dans le carter général (10), doté d'un carter de compresseur (12), aménagé comme une partie du carter général (10) et dans lequel est disposé au moins un alésage de rotor à vis (64, 120), d'au moins un rotor à vis (62, 122) disposé en rotation autour d'un axe de rotation (63, 113) dans l'alésage de rotor à vis (64, 120), d'une unité de palier (74, 128) côté aspiration, disposée contre le carter de compresseur (12) et destinée au rotor à vis (12), et destinée au rotor à vis (62, 122), d'au moins une unité de palier (72, 126) côté compression, disposée contre le carter de compresseur (12) et destinée au rotor à vis (62, 122) et d'une fenêtre de carter (133), prévue contre le carter de compresseur (12) et destinée au réfrigérant compressé,
    et une première unité de silencieux (140, 240) disposée dans le carter général (10) et à la suite de la fenêtre de carter (133) et présentant au moins une chambre (148, 150, 248, 250) se trouvant entre un orifice d'entrée (142) et un orifice de sortie (144) et s'élargissant transversalement à un sens de passage par rapport à l'orifice d'entrée (142) et à l'orifice de sortie (144),
    caractérisé en ce que l'unité de silencieux (140) est configurée en forme d'atténuateur de passage présentant plusieurs orifices de passage (154) chacun suivi d'une chambre d'expansion (148, 150), en ce que plusieurs des chambres d'expansion (148, 150) de l'unité de silencieux (140) présentent différents volumes et en ce que l'orifice d'entrée (142) et l'orifice de sortie (144) forment chacun un orifice de passage.
  2. Compresseur frigorifique selon la revendication 1, caractérisé en ce que la première unité de silencieux (140, 240) est disposée dans un carter de silencieux (200) adjacent au carter de compresseur (12) au niveau de la fenêtre de carter (133) .
  3. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le carter de silencieux (200) est disposé à côté d'un logement de palier (68) accueillant au moins une unité de palier (72, 126) côté compression, et en ce que, en particulier, le carter de silencieux (200) est maintenu contre le carter de compresseur (12).
  4. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le carter de silencieux (200) et le logement de palier (68) sont configurés comme des parties d'un carter combiné (210).
  5. Compresseur selon la revendication 4, caractérisé en ce que le carter combiné (210) comporte un carter de base (212) et un carter de recouvrement (214) et en ce que, en particulier, le carter de base (212) et le carter de recouvrement (214) peuvent être séparés par un plan de séparation (216) transversal à l'axe de rotation (63, 123) de l'au moins un rotor à vis (62, 122).
  6. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que la première unité de silencieux (140, 240) présente une chambre d'accueil (138) adjacente à la fenêtre de sortie (132) et suivie de l'orifice d'entrée (142).
  7. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que la première unité de silencieux (140) est disposée de manière à pouvoir être traversée par le réfrigérant de compression dans un sens d'écoulement (146) transversal à une paroi côté compression (78) du carter de compresseur (12) et s'éloignant de celle-ci.
  8. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que plusieurs des orifices de passage (142, 144, 154) de l'unité de silencieux (140) présentent des sections identiques.
  9. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que les chambres d'expansion (148, 150) de différents volumes présentent une extension différente dans le sens d'écoulement (146).
  10. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de silencieux (240) comporte un tronçon de tube (242) s'étendant depuis l'orifice d'entrée (142) jusqu'à l'orifice de sortie (144), formant un canal de passage (244) et présentant des traversées (246) côté chemise qui débouchent dans au moins un espace d'amortissement (248, 250) disposé dans l'au moins une chambre (148, 150) et jouxtant le tronçon de tube.
  11. Compresseur frigorifique selon la revendication 10, caractérisé en ce que le tronçon de tube (242) traverse plusieurs chambres (148, 150) dont chacune forme un espace d'amortissement (248, 250) jouxtant le tronçon de tube (242).
  12. Compresseur frigorifique selon la revendication 11, caractérisé en ce que l'unité de silencieux (240) présente au moins deux espaces d'amortissement (248, 250) dont le volume est différent.
  13. Compresseur frigorifique selon la revendication 12, caractérisé en ce que les espaces d'amortissement (248, 250) de volumes différents présentent une extension différente dans le sens longitudinal du tronçon de tube (242).
  14. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que le carter de silencieux (200) est disposé à l'intérieur d'un corps de compression (16) du carter général (10), en ce que, en particulier, le corps de compression (16) recouvre le carter de silencieux (200) et en ce que, en particulier, le carter de silencieux (200) est entouré par une chambre de pression située dans le corps de compression (16).
  15. Compresseur frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une unité de séparation de lubrifiant (180) est disposée dans le corps de compression (16) et en ce que, en particulier, l'unité de séparation de lubrifiant (180) est disposée en aval de l'au moins une unité de silencieux (140, 160, 240).
EP13711632.3A 2012-03-20 2013-03-19 Compresseur frigorifique Active EP2828528B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012102349A DE102012102349A1 (de) 2012-03-20 2012-03-20 Kältemittelverdichter
PCT/EP2013/055653 WO2013139772A1 (fr) 2012-03-20 2013-03-19 Compresseur frigorifique

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EP2828528A1 EP2828528A1 (fr) 2015-01-28
EP2828528B1 true EP2828528B1 (fr) 2018-12-19

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EP13711632.3A Active EP2828528B1 (fr) 2012-03-20 2013-03-19 Compresseur frigorifique

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US (1) US10648472B2 (fr)
EP (1) EP2828528B1 (fr)
CN (1) CN104204532B (fr)
DE (1) DE102012102349A1 (fr)
RU (1) RU2589978C2 (fr)
WO (1) WO2013139772A1 (fr)

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RU2737072C2 (ru) 2015-08-11 2020-11-24 Кэрриер Корпорейшн Компрессор, способ его использования и система паровой компрессии
EP3356677B1 (fr) * 2015-10-02 2024-01-24 Carrier Corporation Compresseur à vis avec groupes de résonateurs
EP3440357B1 (fr) * 2016-04-06 2023-09-06 BITZER Kühlmaschinenbau GmbH Unité compresseur et son procédé de fonctionnement
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EP3542109B1 (fr) 2016-11-15 2020-07-08 Carrier Corporation Muffler for lubricant separator
CN115324892A (zh) * 2022-08-16 2022-11-11 江森自控空调冷冻设备(无锡)有限公司 螺杆压缩机

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Publication number Publication date
US10648472B2 (en) 2020-05-12
EP2828528A1 (fr) 2015-01-28
US20150004015A1 (en) 2015-01-01
WO2013139772A1 (fr) 2013-09-26
RU2589978C2 (ru) 2016-07-10
CN104204532B (zh) 2017-03-08
CN104204532A (zh) 2014-12-10
DE102012102349A1 (de) 2013-09-26
RU2014141936A (ru) 2016-05-10

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