EP2828528A1 - Compresseur frigorifique - Google Patents

Compresseur frigorifique

Info

Publication number
EP2828528A1
EP2828528A1 EP13711632.3A EP13711632A EP2828528A1 EP 2828528 A1 EP2828528 A1 EP 2828528A1 EP 13711632 A EP13711632 A EP 13711632A EP 2828528 A1 EP2828528 A1 EP 2828528A1
Authority
EP
European Patent Office
Prior art keywords
housing
compressor according
refrigerant compressor
muffler
unit
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.)
Granted
Application number
EP13711632.3A
Other languages
German (de)
English (en)
Other versions
EP2828528B1 (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
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 EP2828528A1 publication Critical patent/EP2828528A1/fr
Application granted granted Critical
Publication of EP2828528B1 publication Critical patent/EP2828528B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 driver bore is arranged, with at least one screw rotor rotating in the screw driver 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.
  • 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 first muffler unit is arranged in the pressure housing following the housing window, and that the muffler unit has at least one lying between an inlet opening and an outlet opening, transverse to a flow direction relative to the inlet opening and the outlet opening widening chamber.
  • 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.
  • 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.
  • the silencer housing itself receives the compressed and pressure pulsations having refrigerant directly on the housing window and tightly rests around the housing window around. It is particularly expedient if 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.
  • 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.
  • Such a course of the parting plane makes it possible to form and mount the base housing and the cover housing in a particularly simple manner.
  • 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 cover for example, 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 prefferably 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 formed as a passage damper, which at least one through hole and at least one on this passage opening having the following expansion chamber and wherein the inlet opening and the outlet opening also each form a passage opening for the at least one expansion chamber.
  • Damping is dependent on the area ratio of the cross-sectional jumps.
  • a silencer unit it is provided in such a silencer unit that it has a plurality of passage openings on which one each soft
  • the muffler unit is designed so that immediately following each expansion opening an expansion chamber, and preferably also 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 has a plurality of expansion chambers with different volumes, so that it is thus possible in a simple manner to tune the damping properties to different frequencies.
  • 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 to the pipe section
  • 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 adjacent to the pipe section
  • the damping chambers are at several Dämpfungs slaughter
  • 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
  • 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.
  • Fig. 1 is a perspective view of a refrigerant compressor according to the invention
  • FIG. 2 is a side view in the direction of the arrow A in FIG. 1;
  • FIG. Fig. 3 is a view in the direction of arrow B in Fig. 1;
  • Fig. 6 is a perspective view of an end-side cover with
  • FIG. 7 is a perspective view of the lid of FIG. 6 with a view of a suction gas connection on the lid;
  • Fig. 8 shows an enlarged section through the frontal cover with the
  • 11 is a section along line 11-11 in FIG. 4;
  • Fig. 12 is an enlarged section similar to FIG. 11 in the region of a pressure housing
  • FIG. 13 is a view similar to FIG. 12 of a second embodiment of a refrigerant compressor according to the invention.
  • FIG. 14 shows an illustration similar to FIG. 12 of a third exemplary embodiment of a refrigerant compressor according to the invention.
  • FIG. 15 is a view similar to FIG. 12 of a fourth embodiment of a refrigerant compressor according to the invention.
  • FIG. 16 is a view similar to FIG. 12 of a fifth embodiment of a refrigerant compressor according to the invention.
  • FIG. 17 is a view similar to FIG. 12 of a sixth embodiment of a refrigerant compressor according to the invention.
  • FIG. 18 is a view similar to FIG. 12 of a seventh embodiment of a refrigerant compressor according to the invention.
  • An in Fig. 1 to 3 illustrated embodiment of a refrigerant compressor according to the invention has an overall housing 10, which is a Ver ⁇ denser housing 12, a on one side of the compressor housing 12 ange ⁇ arranged motor housing 14 and on a motor housing 14 against ⁇ opposite side of the compressor housing 12 arranged pressure housing 16th includes.
  • 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 contributes in the region of a partial circumference
  • Control housing 18 in which a controller 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 an end wall of the motor housing 14 forming frontal cover 22, which in turn is provided with a suction gas connection 24 via which can be supplied to the refrigerant compressor to be sucked refrigerant.
  • 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.
  • shut-off valve 26 as shown in FIG. 3, about an axis 28 in different rotational positions, for example, in four mutually rotated by 90 ° rotational positions, mountable to allow optimal adaptation to a leading to the refrigerant compressor, not graphically illustrated suction gas line.
  • 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 area of its end wall 48 opposite the compressor housing 12 with an access cover 46 accessible (FIGS. 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 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. Further, the drive shaft 58 between the screw rotor 62 and the rotor 56 in a to a suction side of the screw rotor 62nd
  • suction side bearing set 74 is then arranged suction side bearing set 74 stored.
  • 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 Lageraufname 86 as shown in FIG. 5, Fig. 6 and Fig. 7, held on the cover 22, wherein the bearing receptacle 86 is held by a plurality of webs, for example, the equiangularly spaced webs 88a, 88b or 88c, at a distance from a lid bottom 92.
  • 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 successive webs 88 extending inflow openings 96a, 96b and 96c is surrounded, through which the suction gas with respect to the motor axis 54 axial and radial component, as shown in FIG. 8 shown 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 shown in FIG. 5 and 8 shown in dashed lines, from the shut-off valve 26 in the direction parallel to the motor shaft 54 through the suction gas connection 24 and the suction port 94 into the inflow space 90, which is arranged 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.
  • a first flow path S1 flows through the bearing receptacle 86 in the region of the outer annular body 87, which surrounds the guide bearing 84 radially outwardly and preferably flows around the annular body 87, so that the bearing receptacle is cooled.
  • this flow path S1 also flows to the rotor 56 at its end face 104 facing away from the compressor housing.
  • 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, for example, 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 to form the flow paths S takes place on the one hand by the receiving base 85 and the annular body 87 of the bearing receptacle 86, which form the Sauggasstrom Strömungs Adjustsfikieen 89, as well as by Strömungs Adjustsfikieen 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.
  • FIG. 10 and Fig. 11 in addition to the first screw rotor 62 is still a second, cooperating with this and in one
  • Screw rotor bore 120 arranged screw rotor 122 is provided, wherein the second screw rotor 122 is mounted about a parallel to the motor axis 54 and the rotation axis 63 axis of rotation 123 by means of a end over the screw rotor 122 projecting bearing shaft 124 in a pressure-side bearing set 126 and a suction-side bearing set 128 is stored.
  • 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 furthermore provided for this purpose, the design and function of which is described, for example, in German Patent Application 10 2011 051 730.8.
  • 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 widen transversely to the flow direction 146, are provided and each of the chambers 148 and 150 is, as shown in FIG. 12, separated by a dividing wall 152 from the closest chamber 148, 150, each dividing wall 152 having a flow restricting passage 154 through which the compressed gas or refrigerant may pass from one of the chambers
  • passage openings 154 are each designed so that their extension in the
  • Flow direction 146 of the thickness of the partition wall 152 corresponds, so that the passage openings pass without walls in wall surfaces of the partition wall 152.
  • inlet opening 142 and the outlet opening 144 also pass over into the wall surface of the adjoining chamber 148 or 150 without any projections.
  • 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 central axis 156, and likewise the chambers 148 and 150 are coaxial with the central axis 156, such that the first muffler unit 140 to the central axis 156 is rotationally symmetrical.
  • the 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 have 148 and 150 is an inner diameter D ik of more than 1.3 times, more preferably more than 1.4 times an inner ⁇ diameter Did of the through holes 154 and the inlet port 142 and outlet port 144th
  • an extension A K i 4 8 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 k i 50 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 provide for 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 compressed gas connection 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 70 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 again configured differently, such that the base housing 212" has a minimal extent starting from the compressor housing 12 and thus comprises only the receiving chamber 138 with respect to the first muffler unit 140, while already the inlet opening 142 and thus Also, the chambers 148 and 150 in the cover housing 214 "are arranged, and also the cover housing 214" also the entire second muffler unit 160, in particular with the cross-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 multiple flow constriction and subsequent expansion as it flows through the muffler units 140 and 160.
  • 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 in the muffler housing 200, and the muffler housing 200 is also part of the combined housing 210 formed by the base housing 212 and the cover housing 214 in the same manner as in FIGS above embodiments is formed.
  • the muffler unit 240 also works as a Helmholtz damper, in the same manner as in the fourth embodiment, 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.
  • Damping space 248 which is approximately identical to that of the sixth embodiment, still damping materials 260 are provided.
  • 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.

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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)

Abstract

L'invention concerne un compresseur frigorifique, comprenant un carter intégral, un compresseur hélicoïdal logé dans le carter intégral et doté d'un carter de compresseur formant une partie du carter intégral, au moins un alésage de rotor hélicoïdal étant ménagé dans ce carter de compresseur, d'au moins un rotor hélicoïdal monté rotatif autour d'un axe de rotation dans l'alésage de rotor hélicoïdal, d'une unité palier pour le rotor hélicoïdal disposée sur le carter de compresseur côté aspiration, d'au moins une unité palier pour le rotor hélicoïdal disposée sur le carter de compresseur côté pression et d'un hublot de carter pour le gaz frigorigène comprimé, disposé sur le carter de compresseur, ainsi qu'une première unité de silencieux montée dans le carter intégral. L'invention vise à améliorer encore l'insonorisation de ce compresseur. A cet effet, la première unité de silencieux est disposée dans le prolongement du hublot de carter et elle comporte au moins une chambre qui se trouve entre une ouverture d'entrée et une ouverture de sortie et qui s'étend transversalement à une direction d'écoulement relativement à l'ouverture d'entrée et à l'ouverture de sortie.
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

Publications (2)

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

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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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US9644630B2 (en) * 2015-07-23 2017-05-09 Fca Us Llc Supercharger with integrated contraction chamber for noise attenuation
US10830239B2 (en) * 2015-08-11 2020-11-10 Carrier Corporation Refrigeration compressor fittings
CN107850071B (zh) 2015-08-11 2021-01-22 开利公司 用于脉动降低的螺杆式压缩机节能器增压室
WO2017058369A1 (fr) * 2015-10-02 2017-04-06 Carrier Corporation Réseaux de résonateurs à compresseur à vis
WO2017174131A1 (fr) 2016-04-06 2017-10-12 Bitzer Kühlmaschinenbau Gmbh Unité compresseur et son procédé de fonctionnement
US10309398B1 (en) * 2016-09-02 2019-06-04 Mainstream Engineering Corporation Passage arrangement for cooling, lubricating and reducing the size of rotary machines
ES2806275T3 (es) 2016-11-15 2021-02-17 Carrier Corp Separador de lubricante con silenciador
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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Also Published As

Publication number Publication date
WO2013139772A1 (fr) 2013-09-26
RU2589978C2 (ru) 2016-07-10
US20150004015A1 (en) 2015-01-01
CN104204532A (zh) 2014-12-10
RU2014141936A (ru) 2016-05-10
US10648472B2 (en) 2020-05-12
CN104204532B (zh) 2017-03-08
EP2828528B1 (fr) 2018-12-19
DE102012102349A1 (de) 2013-09-26

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