US20080008603A1 - Hermetric Refrigerant Compressor - Google Patents

Hermetric Refrigerant Compressor Download PDF

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Publication number
US20080008603A1
US20080008603A1 US11/793,871 US79387105A US2008008603A1 US 20080008603 A1 US20080008603 A1 US 20080008603A1 US 79387105 A US79387105 A US 79387105A US 2008008603 A1 US2008008603 A1 US 2008008603A1
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United States
Prior art keywords
muffler
refrigerant
piston
refrigerant compressor
volume
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.)
Abandoned
Application number
US11/793,871
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English (en)
Inventor
Hans Schoegler
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.)
Secop Austria GmbH
Original Assignee
ACC Austria GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AT0093304U external-priority patent/AT7831U1/de
Application filed by ACC Austria GmbH filed Critical ACC Austria GmbH
Assigned to ACC AUSTRIA GMBH reassignment ACC AUSTRIA GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHOGLER, HANS PETER
Publication of US20080008603A1 publication Critical patent/US20080008603A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting

Definitions

  • the present invention relates to a hermetically encapsulated refrigerant compressor, comprising a hermetically sealed compressor housing, in the interior of which a piston-cylinder unit works which compresses a refrigerant, on the cylinder head of which a muffler is arranged through which the refrigerant flows to the intake valve of the piston-cylinder unit, according to the preamble of claim 1 .
  • the refrigerant process as such has long been known.
  • the refrigerant is heated in the compressor by taking up energy from the space to be cooled and finally overheats and is pumped by means of the refrigerant compressor to a higher pressure level where it emits heat via a condenser and is conveyed back to the evaporator via a throttle where there is a pressure reduction and a cooling of the refrigerant.
  • the intake of the refrigerant occurs via a suction pipe coming directly from the compressor during an intake stroke of the piston-cylinder unit.
  • the suction pipe usually opens into the hermetically encapsulated compressor housing, mostly close to the inlet cross section into the muffler, from where the refrigerant flows into the muffler and from the same directly into the intake valve of the piston-cylinder unit.
  • the muffler is used primarily to keep the noise level of the refrigerant compressor as low as possible during the intake process.
  • Known mufflers usually consist of several volumes which are in connection with each other and an intake cross section through which the refrigerant is sucked from the hermetically encapsulated compressor housing volume into the interior of the muffler and an opening which lies close to the intake valve of the piston-cylinder unit.
  • the mixture is principally caused in such a way that the intake valve of the piston-cylinder unit is merely open over a crank angle range of approx. 180° per cycle and that refrigerant can be drawn into the cylinder of the refrigerant compressor merely within this time window.
  • the intake valve is closed thereafter, during the compression cycle.
  • the cold refrigerant has a virtually constant mass flow, even when the intake valve is closed, as a result of which it flows in from behind into the compressor housing and dwells there and cools the piston-cylinder unit in motion and its components, which again causes a heating of the refrigerant.
  • the pressure oscillations during the compression phase there are further flow processes from the compressor housing to the muffler and vice-versa, which thus causes an additional mixing.
  • the outlet of the suction pipe for the refrigerant is placed in known refrigerant compressors close to the inlet cross section of the muffler. This ensures that a relatively low amount of cold refrigerant can escape from the evaporator into the interior of the compressor housing. Subsequently, the suction pipe end was configured in such a way that an intermediate pipe could be inserted into the same.
  • the refrigerant situated in the muffler or flowing from the suction pipe into the muffler is drawn into the piston-cylinder unit via the intake valve on the one hand, and refrigerant situated in the interior of the compressor housing is drawn into the compensating volume for pressure compensation (as a result of leakage from the piston-cylinder unit and by the mentioned flow-out from the muffler) on the other hand.
  • the noise development can be minimized which is caused with the creation of the compensating volume by the flow processes into the compensating volume and into the compressor housing, so that there will not be any disturbing noise for the operator, which is an especially important feature for household refrigerators.
  • a slightly larger compensating volume can be produced more easily during manufacturing.
  • the smallest cross section in the compensating volume has a cross-sectional surface area which corresponds to 1 ⁇ 4 to 3 ⁇ 4 of the cross-sectional surface area of the intake opening. This ensures that the pressure difference will become small, the flow losses will decrease and the noise damping increases to the outside.
  • the cross section of the compensating volume can correspond at most to 1.5 times the piston head surface area. This ensures that on the one hand the need for space for the compensating volume will not become too high and it is ensured on the other hand that cold and hot suction gas will not mix or form the boundary layer as described below.
  • the characterizing features of claim 5 are provided, according to which the compensating volume is formed by a compensating pipe which has a substantially U-shaped cross section and wraps around the muffler at least partly.
  • claims 10 and 11 describe two different embodiments of a hermetically encapsulated refrigerant compressor, in which the inlet cross section into the muffler and the transition from muffler to compensating volume is arranged once separately and. once coincidentally. Depending on the need for space in the interior of the compressor housing, the most advantageous embodiment must be chosen. In the case where the inlet cross section into the muffler and the transition from muffler to compensating volume coincide, a further preferred embodiment according to the characterizing features of claims 12 to 14 are provided. This embodiment comes with the advantage that a tight connection between suction pipe and muffler is not necessary.
  • FIG. 1 shows a front view of a hermetically encapsulated refrigerant compressor in accordance with the invention with a compressor housing in a sectional view;
  • FIG. 2 shows a sectional side view of a refrigerant compressor hermetically encapsulated in accordance with the invention
  • FIG. 3 shows a front view of a refrigerant compressor hermetically encapsulated in accordance with the invention
  • FIG. 4 shows a sectional view of a muffler in accordance with the state of the art
  • FIG. 5 shows a further sectional view of a known muffler
  • FIG. 6 shows a sectional view of a muffler in accordance with the invention with a closed intake valve
  • FIG. 7 shows a sectional view of a muffler in accordance with the invention with an opened intake valve
  • FIG. 8 shows an oblique view of the muffler in accordance with the invention in the compressor housing
  • FIG. 9 shows an alternative embodiment of a muffler in accordance with the invention.
  • FIG. 9 a shows a further alternative embodiment of a muffler in accordance with the invention.
  • FIG. 10 shows an additional alternative embodiment of a muffler in accordance with the invention.
  • FIG. 11 shows a detailed view of a hermetically sealed connection between muffler and suction pipe
  • FIG. 12 shows a detailed view of an alternative embodiment of a hermetically sealed connection between muffler and suction pipe
  • FIG. 13 shows a detailed view of a further alternative embodiment of a hermetically sealed connection between muffler and suction pipe;
  • FIG. 14 shows a detailed view of a connection between a plastic hose with a suction pipe
  • FIG. 15 shows a detailed view of a connection of a plastic hose with a suction pipe
  • FIG. 16 shows a detailed view of a connection of a plastic hose with a suction pipe
  • FIG. 17 shows a detailed view of a connection of a plastic hose with a suction pipe
  • FIG. 18 shows a detailed view of a connection of a plastic hose with a suction pipe
  • FIG. 19 shows an oblique view of an alternative muffler in accordance with the invention.
  • FIG. 20 shows a further oblique view of the muffler of FIG. 19 in accordance with the invention.
  • FIG. 21 shows a sectional view of the muffler of FIG. 19 in accordance with the invention.
  • FIG. 22 shows a further sectional view of the muffler of FIG. 19 in accordance with the invention.
  • FIGS. 1, 2 and 3 each show a sectional view through a hermetically encapsulated refrigerant compressor, with FIGS. 1 and 3 each showing a view in the direction of arrow A of FIG. 2 .
  • a piston-cylinder motor unit is elastically held by means of springs 2 in the interior of a hermetically sealing compressor housing 1 .
  • the piston-cylinder-motor unit substantially consists of a cylinder housing 3 and the piston 4 performing a lifting movement therein, and a crankshaft bearing 5 which is arranged perpendicular to the cylinder axis 6 .
  • the crankshaft bearing 5 receives a crankshaft 7 and protrudes into a centric bore 8 of rotor 9 of an electromotor 10 .
  • a connecting rod bearing 12 is situated at the upper end of crankshaft 7 , through which the connecting rod and consequently the piston 4 are driven.
  • the crankshaft 7 comprises a lubricating oil bore 13 and is fixed to rotor 9 in the area 14 .
  • the muffler 16 is arranged on the cylinder head 15 , which muffler is to reduce noise development to a minimum during the intake process of the refrigerant.
  • FIG. 4 shows a sectional view of a muffler 16 according to the state of the art.
  • the muffler 16 is arranged on the cylinder head 15 in the interior of the hermetically sealed compressor housing 1 .
  • the refrigerant coming from the evaporator which refrigerant is cold in comparison with the warm refrigerant situated in the compressor housing 1 , flows via a suction pipe 17 into the interior of the compressor housing 1 close to the inlet cross section 18 of the muffler 16 when such a known muffler 16 is used, where it mixes with the warm refrigerant already situated in the compressor housing 1 and is heated up and is drawn into the piston-cylinder unit via the muffler 16 .
  • Mufflers 16 usually consist of several successively connected and/or parallel connected volumes V 1 , V 2 , V n which are connected via pipes with each other, and of an oil separator opening 31 at the lowest point.
  • the cold refrigerant flows via suction pipe 17 into the interior of the compressor housing 1 where as a result of its configuration a first thorough mixing with the warm refrigerant occurs which is already situated in the compressor housing 1 .
  • the already mixed and heated refrigerant then flows through the inlet cross section 18 into the first volume V 1 and then into the second volume V 2 of the muffler 16 and mixes again with the warm refrigerant already situated both in V 1 as well as V 2 , as a result of which there is a renewed heating of the refrigerant.
  • the heating between the outlet from suction pipe 17 and shortly before the intake opening 24 in the muffler 16 is between 30K and 40K, depending on the output of the refrigerant compressor.
  • FIG. 5 shows a muffler 16 which is also known from the state of the art, namely from WO03/038280, whose inlet cross section 18 is tightly connected with the suction pipe 17 .
  • the cold refrigerant coming from the suction pipe 17 is unable to mix with the warm refrigerant situated in compressor housing 1 before it is drawn into the muffler 16 .
  • a compensating volume 21 is connected to the muffler 16 , through which the pressure compensation can occur which is required as a result of the direct connection of the muffler 16 with the suction pipe 17 , such that a connection exists both to the muffler 16 as well as into the interior of the compressor housing.
  • the required pressure compensation leads to flow states of the refrigerant which can lead to the flow losses which offset the gain in energy which is achieved by the reduction of the refrigerant temperature at the beginning of the compression phase.
  • FIG. 6 An embodiment of a muffler in accordance with the invention is shown in FIG. 6 .
  • Muffler 16 is shown in FIG. 6 in a sectional view.
  • FIGS. 1, 2 and 3 also show refrigerant compressors with such a muffler 16 in accordance with the invention.
  • the inlet cross section 18 of muffler 16 is connected with the suction pipe 17 via a schematically shown, hermetically sealed connection 19 .
  • a tight connection 19 can principally be any preferably elastic connection as known to the person skilled in the art, such as a simple rubber tube which needs to be connected in a tight manner with the muffler 16 and the suction pipe 17 . Examples for such connections are shown in FIG. 11 to FIG. 18 .
  • the muffler 16 in accordance with the invention delimits a filling volume 20 (with the arrangement of several filling volumes being possible and done). Adjacent to the muffler 16 , a compensating volume 21 is arranged which is formed by a U-shaped compensating pipe 34 .
  • the illustrated U-shaped compensating pipe 34 offers the advantage of limiting a sufficient compensating volume 21 and of requiring only little additional space, and of producing the required flow conditions which minimize the mentioned losses.
  • the compensating volume 21 and the compensating pipe 34 are in connection via a compensating opening 23 with the interior of the compressor housing 1 and with the filling volume 20 of the muffler 16 via the transition opening 26 .
  • FIG. 6 shows the flow progress of the refrigerant with closed intake valve by means of arrows, which valve is situated behind the intake opening 24 of the muffler 16 on the side of the valve plate facing the piston.
  • the cold refrigerant flowing from the suction pipe 17 flows via the tight connection 19 to the muffler volume 20 and from there into the compensating volume 21 , as a result of which the warmer refrigerant situated there is pressed from the compensating pipe 34 via the compensating opening 23 into the interior of the compressor housing 1 .
  • the line indicated with reference numeral 25 symbolizes the boundary layer which forms between the cold and warm refrigerant.
  • FIG. 7 shows the same muffler 16 in accordance with the invention, plus flow progress with opened intake valve.
  • the refrigerant is drawn in both from the compensating volume 21 and from the filling volume 20 and the suction pipe 17 . Since the refrigerant in the compensating volume 21 has a lower temperature than the warm refrigerant situated in the interior of the compressor housing 1 , the mixing temperature of the refrigerants from the mentioned intake regions is lower than the mixing temperature of the refrigerants when using mufflers known from the state of the art, as a result of which the aforementioned undesirable temperature increase is prevented.
  • the compensating volume 21 has 0.5 to 3 times the lifting volume of the piston of the piston-cylinder unit, warm refrigerant is unable to flow from the interior of the compressor housing into the muffler, which in this embodiment is volume 20 . Due to the fact that the smallest flow cross section 32 has a cross-sectional surface area in the compensating volume 21 which corresponds to 1 ⁇ 4 to 3 ⁇ 4 of the cross-sectional surface area of the intake opening 24 , it is ensured that the pressure difference between muffler 16 and the interior of the compressor housing 1 is low and at the same time the noise damping in the interior of the compressor housing is high. An enlargement of the compensating volume also contributes to this, with the same being at least half, preferably 0.5 to 3 times the displacement of the piston of the piston-cylinder unit.
  • the flow losses are minimized by the muffler in accordance with the invention and the refrigerant can easily flow into the compensating volume or from the same without negatively influencing the refrigerant process.
  • FIG. 8 shows an oblique view of the muffler 16 in accordance with the invention in the compressor housing 1 without the piston-cylinder motor unit.
  • FIG. 9 shows an alternative embodiment of a muffler 16 in accordance with the invention, plus compensating volume 21 .
  • the compensating volume 21 and the muffler 16 are formed by an encasing pipe 34 which encases the intake opening 24 on the one hand and opens into the same, and encases an end section of the suction pipe 17 along a section on the other hand.
  • the cold refrigerant flowing from the suction pipe 17 flows during the entire intake cycle into the section of the encasing pipe 34 forming the filling volume 20 of the muffler 16 .
  • the filling volume 20 of the muffler 16 can no longer receive any further refrigerant from the suction pipe 17 as a result of the closed intake valve, which is why the refrigerant flows back into the compensating volume 21 which is also formed by a section of the encasing pipe 34 and displaces the warm refrigerant contained therein via the compensating opening 23 into the interior of the compression housing 1 .
  • cold refrigerant can be drawn into the cylinder both from the suction pipe 17 as well as from the compensating volume 21 of the encasing pipe 34 .
  • the relevant aspect is that the boundary layer does not exceed the line designated with reference numeral 33 , which in this embodiment simultaneously forms the inlet cross section 18 into the muffler 16 and the transitional opening 26 , in the direction of intake opening 24 in order to prevent a thorough mixture of warm and cold refrigerant prior to the intake process.
  • FIG. 9 a shows a further alternative embodiment of a muffler 16 plus compensating volume 21 , in which the muffler 16 is provided with an additional volume 20 in comparison with that of FIG. 9 .
  • this variant is identical to the one shown in FIG. 9 .
  • FIG. 10 shows an additional alternative embodiment of a muffler 16 in accordance with the invention.
  • the reference numerals were maintained accordingly.
  • the configuration of the compensating volume can principally be chosen freely as long as the features of compensating volume 21 in accordance with the invention which is situated upstream of the outlet opening of suction pipe 17 are maintained concerning its volume and the smallest flow cross section 32 . Only then will optimal energy savings be achieved and the efficiency of the refrigerant compressor will be improved accordingly.
  • the question as to how the different compensating volumes 21 and the mufflers 16 are arranged is of lower importance as long as the features in accordance with the invention are realized and the gas column and the boundary layer 25 is allowed to oscillate in the compensating volume.
  • the muffler 16 in the embodiment according to FIG. 9 merely consists of a filling volume 20 which extends in a substantially conical manner, and in the embodiment according to FIG. 9 a of a filling volume 20 a extending in a substantially conical manner and of the filling volume 20 , and in the embodiment according to FIG. 10 of the volumes V 2 and V 1 . It is understood that the parallel or serial arrangement of additional volumes of the muffler 16 is possible at any time and leads to improved sound-damping properties of the muffler 16 .
  • the compensating volume 21 consists of a cylindrical volume. In the embodiment according to FIG. 9 a, it also consists of a cylindrical volume and in the embodiment according to FIG. 10 of the volumes 21 a and 21 b .
  • the further arrangement of the compensating volumes, whether parallel or serial, is obviously possible, with the same contributing to sound damping, like 21 b for example.
  • the smallest flow cross section 32 in accordance with the invention can be realized either by a baffle as in FIG. 9, 9 a and 10 , or by a spatial constriction as shown in FIG. 3 .
  • the entire compensating volume 21 can have a constant cross section with the features in accordance with the invention.
  • FIGS. 11 to 18 show different embodiments of the hermetically sealed connection from suction pipe 17 to muffler 16 in accordance with the invention. Only when this connection is actually tight, which means in other words that no warm refrigerant is drawn from the compressor housing 1 into the muffler 16 , the compensating volume 21 will show its optimal effect, if it concerns an embodiment as described in FIG. 6 and FIG. 7 .
  • FIG. 11 The simplest connection is shown in FIG. 11 .
  • the elastic bellows 19 is merely pushed over the suction pipe 17 without any additional fixing, but preferably glued.
  • FIGS. 12 and 13 show a more complex but stable connection.
  • the wall of the compressor housing 1 comprises an inwardly facing nose 28 over which the elastic plastic hose 19 is pushed, which nose simultaneously protrudes into the inlet cross section 18 of the muffler 16 .
  • the plastic hose 19 which can also be arranged as an elastic pipe is enclosed by a spiral spring 27 which ensures required stability and fixing.
  • An 0 -ring 29 is each arranged both in the area of the nose 28 as well as in the area of the inlet cross section 18 , which ring ensures the required tightness.
  • the muffler 16 also comprises a respective nose protruding into the interior of the compressor housing 1 .
  • FIGS. 14 to 18 show different fastening possibilities 30 between elastic connecting means 19 and suction pipe 17 which can be arranged either as a toothing ( FIG. 17 , FIG. 18 ) or as barbs ( FIG. 16 ) arranged on the elastic connecting means, or as simple shoulders ( FIG. 14 , FIG. 15 ).
  • the compensating volume 21 including muffler 1 as described in FIGS. 9, 9 a and 10 lacks the requirement of such a tight connection between muffler 16 and suction pipe 17 for the reasons as described above.
  • FIG. 19 , FIG. 20 , FIG. 21 and FIG. 22 show a further embodiment of a muffler 16 plus compensating volume 21 as already schematically described in FIGS. 9, 9 a and 10 .
  • the suction pipe 17 is guided close to the inlet cross section 18 of the muffler 16 .
  • the inlet cross section 18 is connected by means of a plastic hose 19 tightly with the suction pipe 17 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
US11/793,871 2004-12-22 2005-12-22 Hermetric Refrigerant Compressor Abandoned US20080008603A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0093304U AT7831U1 (de) 2004-01-29 2004-12-22 Kältemittelverdichter
ATGM933/2004 2004-12-22
PCT/EP2005/057110 WO2006067218A1 (de) 2004-12-22 2005-12-22 Hermetischer kältemittelverdichter

Publications (1)

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US20080008603A1 true US20080008603A1 (en) 2008-01-10

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Application Number Title Priority Date Filing Date
US11/793,871 Abandoned US20080008603A1 (en) 2004-12-22 2005-12-22 Hermetric Refrigerant Compressor

Country Status (6)

Country Link
US (1) US20080008603A1 (de)
EP (1) EP1828603B1 (de)
CN (1) CN100587268C (de)
AT (1) ATE393880T1 (de)
DE (1) DE502005003926D1 (de)
WO (1) WO2006067218A1 (de)

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US20060014658A1 (en) * 2002-12-20 2006-01-19 Degussa Ag Sodium percarbonate particles with improved storage stability
JP2013083225A (ja) * 2011-10-12 2013-05-09 Panasonic Corp 密閉型圧縮機
US20150300337A1 (en) * 2011-12-23 2015-10-22 Gea Bock Gmbh Compressor
US20160131125A1 (en) * 2014-11-10 2016-05-12 Lg Electronics Inc. Reciprocating compressor and method for assembling the same
US9541079B2 (en) 2011-04-11 2017-01-10 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor
EP2570670A3 (de) * 2011-09-13 2017-03-22 Black & Decker Inc. Kompressoreinlassdämpfer und -filter
US20170356432A1 (en) * 2014-11-27 2017-12-14 Whirpool S.A. Suction Acoustic Filter and Suction Line Including Suction Acoustic Filter
US9890774B2 (en) 2011-09-13 2018-02-13 Black & Decker Inc. Compressor intake muffler and filter
US11111913B2 (en) 2015-10-07 2021-09-07 Black & Decker Inc. Oil lubricated compressor
US20210381500A1 (en) * 2015-12-21 2021-12-09 Secop Gmbh Encapsulated refrigerant compressor

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BR112014015920A8 (pt) * 2011-12-26 2017-07-04 Arcelik As compressor compreendendo um elemento de conexão
BR102014007254A2 (pt) * 2014-03-26 2015-12-08 Whirlpool Sa dispositivo seletor de fluidos para compressor alternativo e filtro acústico provido de dispositivo seletor de fluidos
CN103925190B (zh) * 2014-03-31 2017-06-06 扎努西电气机械天津压缩机有限公司 提高吸气效率的冰箱压缩机吸气消音器
EP3504436B1 (de) 2016-08-23 2020-03-18 Secop GmbH Saugschalldämpfer
AT17214U1 (de) * 2019-12-19 2021-09-15 Anhui meizhi compressor co ltd Hermetisch gekapselter Kältemittelverdichter

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US5979597A (en) * 1996-03-29 1999-11-09 Tecumseh Europe S.A. Suction silencer system for a refrigeration compressor
US6155800A (en) * 1996-05-10 2000-12-05 Empresa Brasileira De Compressores S/A-Embraco Suction arrangement for a reciprocating hermetic compressor
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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060014658A1 (en) * 2002-12-20 2006-01-19 Degussa Ag Sodium percarbonate particles with improved storage stability
US9541079B2 (en) 2011-04-11 2017-01-10 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor
US10871153B2 (en) 2011-09-13 2020-12-22 Black & Decker Inc. Method of reducing air compressor noise
US12078160B2 (en) 2011-09-13 2024-09-03 Black & Decker Inc. Method of reducing air compressor noise
EP2570670A3 (de) * 2011-09-13 2017-03-22 Black & Decker Inc. Kompressoreinlassdämpfer und -filter
US11788522B2 (en) 2011-09-13 2023-10-17 Black & Decker Inc. Compressor intake muffler and filter
US9890774B2 (en) 2011-09-13 2018-02-13 Black & Decker Inc. Compressor intake muffler and filter
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Also Published As

Publication number Publication date
EP1828603A1 (de) 2007-09-05
WO2006067218A1 (de) 2006-06-29
CN101111677A (zh) 2008-01-23
ATE393880T1 (de) 2008-05-15
EP1828603B1 (de) 2008-04-30
CN100587268C (zh) 2010-02-03
DE502005003926D1 (de) 2008-06-12

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