CN1914421A - Refrigerant compressor - Google Patents
Refrigerant compressor Download PDFInfo
- Publication number
- CN1914421A CN1914421A CNA2005800034990A CN200580003499A CN1914421A CN 1914421 A CN1914421 A CN 1914421A CN A2005800034990 A CNA2005800034990 A CN A2005800034990A CN 200580003499 A CN200580003499 A CN 200580003499A CN 1914421 A CN1914421 A CN 1914421A
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- Prior art keywords
- suction
- piston
- volume
- silencing apparatus
- compressor
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- 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.)
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Classifications
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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
- F04B39/0027—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
Disclosed is a hermetically enclosed refrigerant compressor comprising a hermetically tight compressor housing (1) inside which a piston-cylinder unit compressing refrigerant operates with an intake valve that is provided with an intake port (2) located in a valve plate (11) of the piston-cylinder unit. A suction muffler (16) which encompasses a certain filling volume (20) and via which refrigerant flows to the intake valve of the piston-cylinder unit is provided on the cylinder head (15) of the piston-cylinder unit. The inlet of said suction muffler (16) has a cross section (18) via which refrigerant flows into the suction muffler (16) while a compensating volume (21) is provided inside which refrigerant oscillates and which is connected to the suction muffler (16) and the interior of the compressor housing (1). The cross section (18) of the inlet also acts as the connecting port (26) between the compensating volume (21) and the filling volume (20). The compensating volume (21) is formed by an outer tube (22) which tightly surrounds the intake port (24) or cross section (18) of the inlet while surrounding at least one section of the refrigerant suction pipe (17) that is connected to the evaporator of the refrigerant compressor and extends into the interior of the compressor housing (1).
Description
Technical field
The present invention relates to a kind of refrigeration compressor as claim 1 leaktight encapsulation as described in the preamble, this refrigeration compressor has the compressor housing of gas tight seal, the piston-cylinder unit of a compressed refrigerant is worked in described compressor housing, the suction silencing apparatus is set on the cylinder cap of above-mentioned piston-cylinder unit, and refrigeration agent passes above-mentioned suction silencing apparatus and flows in the suction valve of piston-cylinder unit.
Background technique
This refrigeration compressor is known for a long time, and mainly is to be used for refrigerator and refrigeration frame.Therefore annual yielding capacity is very high.
Although the power consumption of single refrigeration compressor only greatly between 50 and 150 watts, is considering under all employed refrigeration compressor situations in the whole world that just produce very high power consumption, because less developed country is also fast-developing, power consumption increases constantly.
Therefore, to refrigeration compressor with increase any technological improvement that efficient does when being generalized to the employed refrigeration compressor in the whole world, all provide great potentiality to energy-conservation.
Such a process of refrigerastion is known for a long time.In vaporizer, refrigeration agent is heated by the energy that absorbs in the space to be cooled, make refrigerant superheat at last, and utilize refrigeration compressor to be pumped into higher pressure level, refrigeration agent is by the condenser discharges heat there, and carry by throttle valve and to get back to vaporizer, refrigerant pressure reduces and cooling in throttle valve.
The maximum that may improve and most important potentiality for efficient are to reduce the temperature of refrigeration agent when the compression process of refrigeration agent begins.Each reduction of inlet temperature that refrigeration agent enters the cylinder of piston-cylinder unit all causes the required technical work of compression process to reduce, just as reduce temperature and relevant therewith discharge temperature during compression process.
In the refrigeration compressor of known leaktight encapsulation, carry out a strong heating at its route from compressor (cooling space) to the piston-cylinder unit suction valve according to the structural type refrigeration agent.
During the induction stroke of piston-cylinder unit, the suction of refrigeration agent realizes by the suction pipe that directly comes out from compressor.In the refrigeration compressor of known leaktight encapsulation, suction pipe is passed in the compressor housing of leaktight encapsulation usually, great majority are passed near the entrance cross-section that sucks silencing apparatus, refrigeration agent flows into from described entrance cross-section and sucks silencing apparatus, and flows directly into the suction valve of piston-cylinder unit from described suction silencing apparatus.Sucking silencing apparatus mainly is to be used for keeping in suction process the noise level of refrigeration compressor low as far as possible.Known suction silencing apparatus generally includes some volumes, and sucks cross section and an opening, above-mentioned some volumes are interconnected, and refrigeration agent passes above-mentioned suction cross section and is drawn into the inside that sucks silencing apparatus from the compression case body bulk of leaktight encapsulation, and described opening is close near the suction valve of piston-cylinder unit hermetically.
In refrigeration agent enters process between the suction valve of the inlet of compressor housing and piston-cylinder unit, as mentioned above, carry out the heating of undesirable refrigeration agent.Measurement shows, 32 ℃ refrigerant temperature in suction pipe (pre-determining) by standardized ASHRAE condition, and refrigeration agent is very short time before entering compressor housing, has sucked in the silencing apparatus volume first and has been heated to about 54 ℃.The main cause of this undesirable heating of refrigeration agent is actually from suction pipe and newly flows into the refrigeration agent of compressor housing and the refrigerant mixed of heat that is arranged in compressor housing.Mixture is to produce in this way in principle, so that the suction valve of piston-cylinder unit only is about 180 ° in crank angle range and opens, and therefore refrigeration agent only just is drawn in this time window in the cylinder of refrigeration compressor.After this during compression cycle with suction valve closure.Even when suction valve closure, cold refrigeration agent also has almost constant mass flow, and refrigeration agent flows into compressor housing from behind and rests on there thus, and cools off piston-cylinder unit and the parts thereof that are in motion, causes the heating of refrigeration agent so once more.Because pressure surge during compression process has other flow process from compressor housing to the suction silencing apparatus or opposite process, therefore realizes extra mixing.
For warm refrigerant that prevents compressor and the fresh refrigerant mixed of coming out, in known refrigeration compressor, refrigeration agent is placed the outlet of suction pipe near the entrance cross-section that sucks silencing apparatus from vaporizer.This has guaranteed that more a spot of cold refrigeration agent can go to the inside of compressor housing from vaporizer.Therefore, the suction pipe end is shaped like this, so that an intervalve can be inserted the suction pipe end.Simultaneously intervalve is surrounded with a helical spring, described helical spring is bearing in suction pipe on the one hand and enters on the inlet of housing, and is bearing on the other hand on the intervalve, so that realize suction pipe is connected on the suction silencing apparatus.Effort through the refrigerant mixed of heating in cold refrigeration agent in the device that avoids evaporating that all these are known and the compressor housing only causes this minimizing that mixes, but can not prevent from fully to mix.
Therefore known from WO 03/038280, the entrance cross-section that directly will suck silencing apparatus is connected with the outlet of suction pipe, will directly import the suction silencing apparatus from the refrigeration agent that vaporizer comes out, and does not arrive compressor and do not heat at this place.Based on the above-mentioned fact, even also having almost constant mass flow and flow into when suction valve closure, cold refrigeration agent sucks in the silencing apparatus (being now) by direct connection, must in sucking silencing apparatus, compensation volume be set, so that compensation in sucking silencing apparatus owing to flow into the pressure that refrigeration agent causes continuously from the suction pipe back and rise, and be arranged in the refrigeration agent that sucks silencing apparatus via this suction pipe can be from the suction silencing apparatus compressor housing that comes out to flow into once more.During next induction stroke, be arranged in suck silencing apparatus or from suction pipe flow into suck silencing apparatus refrigeration agent on the one hand by suction valve sucker-piston-cylinder unit, and flow out owing to sewing from piston-cylinder unit and passing through from sucking silencing apparatus on the other hand, the refrigeration agent that will be arranged in compressor sucks compensation volume and is used for pressure compensation, but does not suck in the silencing apparatus.
Thereby the flow characteristic that is produced caused increasing the danger of flow losses, can not produce with sucking under the direct-connected situation of silencing apparatus at suction pipe during above-mentioned flow characteristic especially overflows in the compensation volume.
In addition, as mentioned above, require suction pipe and suck between the silencing apparatus to be tightly connected as disclosed refrigeration compressor among the WO 03/038280, this means in order to guarantee tightness has increased the assembling work amount, and wherein bellows shape connecting element must be connected with the suction silencing apparatus with compressor housing hermetically.Lose under its tightness situation at bellows shape connecting element, desirable refrigerant temperature reduces in the time of may no longer being implemented in compression process and beginning, and refrigeration compressor is also used lower efficient work.Wherein problematic especially situation is that compressor housing is not by for example weld joint air-tight ground encapsulation, so that the possible inefficacy that connects hermetically between suction pipe and the suction silencing apparatus is not remarkable concerning the operator.
Summary of the invention
Therefore, the objective of the invention is to avoid this shortcoming and the refrigeration compressor that starts the type of mentioning is provided, wherein when compression process begins, and in the cylinder of sucker-piston-cylinder unit, make refrigerant temperature keep low as far as possible thus, because avoided flowing into the inside of compressor housing from the refrigeration agent that vaporizer comes out, and the flow loss when having avoided as far as possible simultaneously sucking has wherein improved operating security.
This purpose can reach by the feature of claim 1 according to the present invention.
Therefore need and not suck Packed connection between the silencing apparatus at suction pipe.Can reach same result by structure of the present invention, because the entrance cross-section of suction silencing apparatus is the connection mouth between compensation volume and the injection volume simultaneously, and compensation volume is formed by sleeve pipe, described sleeve pipe surrounds suction port or entrance cross-section on the one hand hermetically, and surround refrigerant suction pipe and point to compressor housing along one section at least on the other hand, above-mentioned refrigerant suction pipe is connected with the vaporizer of refrigeration compressor, and extend into the inside of compressor housing.
Feature by claim 2 guarantees have enough compensation volume to use.
The feature of claim 3, that is the unitary construction of suction silencing apparatus and compensation volume is realized low especially cost and quick manufacturing feasibility.
By feature according to claim 4, form compensation volume with the pistons work volume 0.5-1.2 that is equivalent to piston-cylinder unit volume doubly, when suction valve closure, also can not arrive compressor housing and mix with already heated refrigerated medium even guarantee the refrigeration agent that comes out from suction pipe.Guarantee in suction process, not have refrigeration agent to suck silencing apparatus or the cylinder by compensation volume simultaneously from compressor housing.
Feature by claim 5, the compensation volume that forms is half of pistons work volume of piston-cylinder unit at least, preferably its 0.5-3 doubly, can make in addition by the volume that affords redress and reduce to minimum with the noise that the inflow compressor housing produces because refrigeration agent flows into compensation volume, therefore do not produce the noise of upsetting the operator, this is even more important concerning household refrigerator.In addition, on production technology, the easier production of big slightly compensation volume.
According to the characteristics specify of claim 6, minimum flow cross section has the cross sectional area of the 1/4-3/4 that is equivalent to the suction port cross-section area in the compensation volume.Guarantee that like this pressure reduction is little, it is big with outside noise attentuation to reduce flow loss simultaneously thus.
According to the feature of claim 7, the cross section of compensation volume is equivalent to 1.5 times of piston head surface area at the most.Guarantee that the required space of compensation volume is not too big so on the one hand, and guarantee that on the other hand suction gas cold and heat does not mix, perhaps do not form boundary layer as described below.
The feature description of claim 8 cause the preferred implementation of low especially flow loss, wherein compensation volume has a circular cross section, and the ratio of the length of compensation volume and its diameter is greater than 10.
Description of drawings
Next, illustrate in greater detail the present invention with reference to accompanying drawing, wherein:
Fig. 1 illustrates the sectional view according to the refrigeration compressor of leaktight encapsulation of the present invention;
Fig. 2 illustrates the sectional view according to the suction silencing apparatus of prior art;
Fig. 3 illustrates a kind of alternative mode of execution according to suction silencing apparatus of the present invention;
Fig. 4 illustrates the another kind of alternative mode of execution according to suction silencing apparatus of the present invention.
Embodiment
Fig. 1 illustrates the sectional view of the refrigeration compressor of leaktight encapsulation.Piston-cylinder-motor unit is by the inside of spring 2 yielding supports at the compressor housing 1 of gas tight seal.
Piston-cylinder-motor unit basically by cylinder housing 3, in cylinder housing 3, implement pistons reciprocating 4 and form perpendicular to the crankshaft bearing 5 that cylinder axis 6 is installed.These crankshaft bearing 5 supporting crankshafts 7 also stretch in the center hole 8 of rotor 9 of electric motor 10.Link supporting 12 is positioned at the upper end of bent axle 7, via this link supporting drive link and driven plunger 4 thus.Bent axle 7 has oilhole 13, and at regional 14 internal fixation on rotor 9.Suck silencing apparatus 16 and be arranged on the cylinder cap 15, above-mentioned suction silencing apparatus 16 makes noise produce during the refrigeration agent suction process and reduces to minimum.
Fig. 2 illustrates the sectional view according to the suction silencing apparatus 16 of prior art.As shown in Figure 1, sucking silencing apparatus 16 is arranged on the cylinder cap 15 in compressor housing 1 inside of gas tight seal.When using this known suction silencing apparatus, that come out from vaporizer and to compare with the warm refrigerant that is arranged in compressor housing 1 be cold refrigeration agent, near the entrance cross-section 18 that sucks silencing apparatus 16, flow into the inside of compressor housing 1 by suction pipe 17, mix with the warm refrigerant that is arranged in compressor housing 1 there and heat, and be drawn in the piston-cylinder unit by sucking silencing apparatus 16.
According to the suction silencing apparatus 16 of prior art generally include several be connected in series and/or be connected in parallel pass through the interconnective volume V of pipeline
1, V
2, V
n, and in the oil separator hole 31 at minimum point place.Cold refrigeration agent is by the inside of suction pipe 17 inflow compressor housings 1, and there according to structural type, cold refrigeration agent mixes first with the warm refrigerant that is arranged in compressor housing 1.The refrigeration agent that has mixed then and heated flows into first volume V that sucks silencing apparatus by entrance cross-section 18
1, flow into second volume V then
2, and at V
1And V
2In be positioned at the there warm refrigerant mix heating and cooling agent again thus again.In these known suction silencing apparatuss, according to the power of refrigeration compressor, the heating in outlet in suction pipe 17 and the suction silencing apparatus 16 between the very short segment distance in suction port 24 fronts is between 30K and 40K.
In order to prevent undesirable heating, be provided with according to the suction silencing apparatus 16 of the present invention shown in sectional view among Fig. 3.One compensation volume 21 is connected to and sucks on the silencing apparatus 16, and described suction silencing apparatus 16 has one and injects volume 20 (configuration of a plurality of injection volumes is admissible and is common), and above-mentioned compensation volume 21 has a cross section contraction flow region 32.Compensation volume 21 and suction silencing apparatus 16 form by sleeve pipe 22 according to the present invention, and described sleeve pipe 22 surrounds on the one hand and is arranged on the suction port 24 in the valve plate 11 or feeds described suction port 24, and passes through the inside that compensation opening 23 feeds compressor housings 1 on the other hand.Sleeve pipe 22 surrounds suction pipe 17 along an end segment at least.
That flow out from suction pipe 17 and suck the section of the injection volume 20 of silencing apparatus 16 from the cold refrigeration agent that vaporizer comes out all flow into sleeve pipe 22 whole imbibition cycle formation.In press cycles subsequently, the injection volume 20 that sucks silencing apparatus no longer receives other the refrigeration agent from suction pipe 7 owing to suction valve is closed, refrigeration agent retreats in the compensation volume 21 that is formed by one section sleeve pipe 22 reason that Here it is, and will be positioned at the inside that warm refrigerant is wherein clamp-oned compressor housing 1 by compensation opening 23.
This causes forming one according to the mobilizable boundary layer 25 of imbibition cycle between warm refrigerant and cold refrigeration agent.In next imbibition cycle, cold refrigeration agent can reach from the compensation volume 21 of sleeve pipe 22 from suction pipe 17 and be drawn into the cylinder.Importantly, boundary layer 25 is no more than the line that the mark 33 of marking on a map is marked on the direction of suction port 24, in this embodiment, described line forms simultaneously and enters the entrance cross-section 18 that sucks silencing apparatus 16 or inject the transition opening 26 between volume 20 and the compensation volume 21, so that prevent the mixing of warm refrigerant and cold refrigeration agent before suction process.
Simultaneously, do not allow the suction pipe 17 of cold refrigeration agent from compensation volume 21 to enter compressor housing 1, so boundary layer 25 is not moved to the line back that marks with reference character 23 (compensation opening) among Fig. 3.Therefore irrelevant with described mode of execution, the volume of compensation volume 21 accurately is adjusted to refrigerating capacity, and the swept volume that therefore is adjusted to piston-cylinder unit is necessary.
Fig. 4 illustrates and sucks another alternative mode of execution that silencing apparatus 16 adds compensation volume 21, wherein sucks silencing apparatus 16 and is made of two volumes 20 and 20a.Aspect all the other, this deformation program is identical with shown in Fig. 3 all.At this, boundary layer 25 also must be according to imbibition cycle fluctuation between line that reference character 23 is marked and entrance cross-section 18 or transition opening 26 always.
How different compensation volume 21 and suction silencing apparatus 16 constitute is less important, can fluctuate in compensation volume as long as realize feature of the present invention and gas column or boundary layer 25.Therefore, as shown in Figure 3, extra injection volume 27 can be arranged on and suck silencing apparatus 16.
Especially as shown in Figure 3, suction pipe shifts near to suction port 24 more, and then compensation volume will become big more (length at sleeve pipe 22 keeps under the same case).In contrast, the injection volume 20 that sucks silencing apparatus 16 reduces this sonorific problem.Therefore, Fig. 4 illustrates a kind of alternative embodiment, wherein as mentioned above, sucks silencing apparatus 16 and comprises two volumes 20 and 20a.By moving suction pipe 17 towards injecting volume 20 directions, can enlarge compensation volume 21, and the shortcoming that need not to stand noise simultaneously.
(Fig. 3 and Fig. 4) in both cases sucks silencing apparatus 16 and sleeve pipe 22 and preferably constitutes with integral way, produces so that simplify.Under embodiment's situation of Fig. 3, suck silencing apparatus 16 and form by sleeve pipe 22 extraly.
In addition, importantly compensation volume is adjusted on the refrigerating capacity of refrigeration compressor, in other words, is adjusted to the size of piston-cylinder unit.Only the ratio at compensation volume 21 and the pistons work volume of piston-cylinder unit is under the 0.5-1.2, the desirable decline that when suction process begins, guarantees best-of-breed functionality and guarantee refrigerant temperature only because can prevent surely that at this boundary layer 25 that fluctuates is no more than any above-mentioned border of mentioning.
In addition, if the noise level that is produced by refrigeration compressor operation reduces, then the ratio of compensation volume 21 and the pistons work volume of piston-cylinder unit must be set to 0.5-3.
Preferably, compensation volume also has a circular cross section, and the ratio of length and diameter is greater than 10 simultaneously.
Claims (8)
1. the refrigeration compressor of a leaktight encapsulation, this refrigeration compressor has the compressor housing (1) of gas tight seal, the piston-cylinder unit of a compressed refrigerant is at described compressor housing (1) internal work, and comprise the band suction port (24) suction valve, described suction port (24) is arranged in the valve plate (11) of piston-cylinder unit, wherein go up the suction silencing apparatus (16) with injection volume (20) is set at the cylinder cap (15) of piston-cylinder unit, refrigeration agent passes the suction valve that described suction silencing apparatus flows to piston-cylinder unit, wherein suck silencing apparatus (16) and have an entrance cross-section (18), refrigeration agent flows into via described entrance cross-section (18) and sucks in the silencing apparatus (16), and be provided with and suck the compensation volume (21) of the internal communication of silencing apparatus (16) and compressor housing (1), refrigeration agent fluctuates in described compensation volume, it is characterized in that, entrance cross-section (18) is the connection mouth (26) between compensation volume (21) and the injection volume (20) simultaneously, and compensation volume (21) is formed by sleeve pipe (22), described sleeve pipe (22) surrounds suction port (24) or entrance cross-section (18) on the one hand hermetically, and surround refrigerant suction pipe (17) and point to compressor housing (1) along one section at least on the other hand, described suction pipe is connected with the vaporizer of refrigeration compressor, and extend into the inside of compressor housing (1).
2. according to the refrigeration compressor of the described leaktight encapsulation of claim 1, it is characterized in that suction pipe (17) is guided until near suction port (24) in sleeve pipe (22).
3. according to the refrigeration compressor of one of claim 1 and 2 described leaktight encapsulation, it is characterized in that sleeve pipe (22) and suction silencing apparatus (16) integrally constitute.
4. according to the refrigeration compressor of one of claim 1-3 described leaktight encapsulation, it is characterized in that, compensation volume (21) be piston-cylinder unit the pistons work volume 0.5-1.2 doubly.
5. according to the refrigeration compressor of one of claim 1-3 described leaktight encapsulation, it is characterized in that, compensation volume (21) be piston-cylinder unit the pistons work volume at least half, preferably 0.5-3 is doubly.
6. according to the refrigeration compressor of one of claim 1-5 described leaktight encapsulation, it is characterized in that minimum flow cross section (32) has 1/4th to 3/4ths cross sectional area of the cross sectional area that is equivalent to suction port (24) in compensation volume (21).
7. according to the refrigeration compressor of one of claim 1-6 described leaktight encapsulation, it is characterized in that the cross sectional area of compensation volume (21) is 1.5 times of piston head surface area of piston-cylinder unit piston at the most.
8. according to the refrigeration compressor of one of claim 1-7 described leaktight encapsulation, it is characterized in that compensation volume (21) has circular cross section, and the length of compensation volume (21) and its diameter ratio value are greater than 10.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ATGM59/2004 | 2004-01-29 | ||
| AT0005904U AT7576U1 (en) | 2004-01-29 | 2004-01-29 | REFRIGERANT COMPRESSOR WITH COMPENSATING VOLUME |
| ATGM933/2004 | 2004-12-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1914421A true CN1914421A (en) | 2007-02-14 |
| CN100434698C CN100434698C (en) | 2008-11-19 |
Family
ID=34222782
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800034990A Active CN100434698C (en) | 2004-01-29 | 2005-01-31 | Refrigerant compressor |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN100434698C (en) |
| AT (1) | AT7576U1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734129A (en) * | 2011-04-11 | 2012-10-17 | 松下电器产业株式会社 | Sealed compressor |
| CN104093982A (en) * | 2011-12-26 | 2014-10-08 | 阿塞里克股份有限公司 | A compressor comprising a connection member |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5496156A (en) * | 1994-09-22 | 1996-03-05 | Tecumseh Products Company | Suction muffler |
| JP4020986B2 (en) * | 1996-01-23 | 2007-12-12 | 松下冷機株式会社 | Hermetic electric compressor |
| JPH1162827A (en) * | 1997-08-21 | 1999-03-05 | Matsushita Electric Ind Co Ltd | Muffler for hermetic compressor |
| BR9900463A (en) * | 1999-02-26 | 2000-08-29 | Brasil Compressores Sa | Suction damper for hermetic compressor |
| DE19983936B4 (en) * | 1999-02-26 | 2008-03-20 | Embraco Europe S.R.L. | Inlet silencer for a sealed coolant compressor |
| BR0105694B1 (en) * | 2001-10-29 | 2009-05-05 | suction filter for reciprocating airtight compressor. |
-
2004
- 2004-01-29 AT AT0005904U patent/AT7576U1/en not_active IP Right Cessation
-
2005
- 2005-01-31 CN CNB2005800034990A patent/CN100434698C/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734129A (en) * | 2011-04-11 | 2012-10-17 | 松下电器产业株式会社 | Sealed compressor |
| CN102734129B (en) * | 2011-04-11 | 2016-03-30 | 松下电器产业株式会社 | Hermetic type compressor |
| US9541079B2 (en) | 2011-04-11 | 2017-01-10 | Panasonic Intellectual Property Management Co., Ltd. | Sealed compressor |
| CN104093982A (en) * | 2011-12-26 | 2014-10-08 | 阿塞里克股份有限公司 | A compressor comprising a connection member |
| CN104093982B (en) * | 2011-12-26 | 2016-08-31 | 阿塞里克股份有限公司 | Compressor including connecting elements |
Also Published As
| Publication number | Publication date |
|---|---|
| AT7576U1 (en) | 2005-05-25 |
| CN100434698C (en) | 2008-11-19 |
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Owner name: SAIKEPU AUSTRIA GMBH Free format text: FORMER OWNER: ACC AUSTRIA GMBH Effective date: 20140808 |
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