CN100587268C - Hermetic refrigerant compressor - Google Patents
Hermetic refrigerant compressor Download PDFInfo
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- CN100587268C CN100587268C CN200580047247A CN200580047247A CN100587268C CN 100587268 C CN100587268 C CN 100587268C CN 200580047247 A CN200580047247 A CN 200580047247A CN 200580047247 A CN200580047247 A CN 200580047247A CN 100587268 C CN100587268 C CN 100587268C
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- pumping
- refrigerant
- muffler
- compressor
- compensation volume
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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
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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
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
The invention relates to an electrochemical electrolyte cleaning method using plastic-diamond composite electrodes. The electrolyte is generally liquid waste from chemical or electrochemical methods.The bipolar plastic-diamond composite electrodes (2) are assembled as purpose-made curved structures to form stacks of cells, thus constituting the core of the electrochemical reactor. In an alternative form of embodiment, the bipolar electrodes are used, in the form of balls (12), in a fluidised-bed reactor or a fixed-bed reactor.
Description
Technical field
The present invention relates to a kind of hermetically enclosed coolant compressor, it has a hermetically enclosed compressor housing, the portion's work within it of the pistons work piston-cylinder unit of one compression refrigerant, one pumping muffler (Muffler) is set on its work cylinder head, and refrigerant flows to the suction valve of pistons work piston-cylinder unit by it.
Background technique
This coolant compressor is exactly known for a long time, and is mainly used in refrigerator or refrigerator-freezer.Therefore Annual output is very big.
Although the energy consumption of separate unit refrigerant compression agent is about only between 50 to 150 watts, but in considering world wide, obtain very high energy consumption during used refrigerant compressor, even it is because constantly development is also increasing in impoverished nation's energy consumption rapidly.
Therefore each technological improvement and the efficient that coolant compressor is carried out improves, and calculates by the coolant compressor that the whole world is used, all brings huge energy-saving potential.
The cyclic process of refrigerant early is exactly known, wherein refrigerant heats in vaporizer with overheated at last by absorb energy from cavity to be cooled, and be compressed to a higher pressure rating by means of coolant compressor, it carries back vaporizer again by the condenser quantity of heat given up and by a flow controller there, carries out the cooling of step-down and refrigerant in flow controller.
May improve the maximum of efficient and most important potentiality are to reduce refrigerant when the refrigerant compression process begins temperature, so the reduction of any reduction of temperature and the temperature in compression process and associated extraction temperature all impels reducing for the needed merit of compression process during the clutch release slave cylinder of refrigerant sucker clutch release slave cylinder unit.
In known hermetically enclosed coolant compressor according to mode of structure refrigerant its from vaporizer (cooling chamber) to the road of the suction valve of pistons work piston-cylinder unit heat intensive.
The suction of refrigerant is undertaken by the pumping tube that fetches from evaporator drier always during the suction beat of pistons work piston-cylinder unit.Pumping tube feeds in the hermetically enclosed compressor housing usually in the coolant compressor of known seal sealing, great majority feed the pumping muffler entrance cross-sections near, and directly flow to the suction valve of pistons work piston-cylinder unit therefrom.Pumping muffler at first is used for making the noise level of refrigerant compressor in the suction process to keep low as far as possible, known pumping muffler passes through its entrance cross-section from hermetically enclosed compressor housing suction pumping muffler inside by many interconnective cavitys and a refrigerant usually, and an opening that abuts against on the pistons work piston-cylinder unit suction valve is formed.
Enter at refrigerant on the path between the suction valve of the inlet of compressor housing and pistons work piston-cylinder unit, as mentioned above, undesirable heating of refrigerant takes place.Measure, for example when the refrigerant temperature in nearby the pumping tube before compressor housing inlet is 32 ℃ (by standardized Ashrae-condition regulation), irritate at first dress that refrigerant has been heated to about 54 ℃ temperature in volume.The main cause of this undesirable heating of refrigerant is such fact, and the promptly firm refrigerant that flows into compressor housing from pumping tube mixes with the refrigerant of heat that is positioned at compressor housing.Mixing causes mainly due to such reason, the suction valve that is the pistons work piston-cylinder unit is only just opened in about 180 a ° crank angle range in each circulation, therefore only in this time window refrigerant could suck in the clutch release slave cylinder of coolant compressor, suction valve just cuts out during compression cycle then.But cold refrigerant has the mass flow of constant, even when suction valve closure, therefore it flows into compressor housing and stops there when suction valve closure, and cooling is in pistons work piston-cylinder unit and the member thereof in the motion, but this causes the heating of refrigerant itself again.This external compression stage is because the compressor housing that pressure surge causes to the continuation flow process and reciprocal the flowing of pumping muffler, causes additional mixing thus.
In order to prevent to mix with this of refrigerant that just comes out from vaporizer from the hot refrigerant of compressor, the outlet that is used for the pumping tube of refrigerant in known coolant compressor is arranged near the pumping muffler entrance cross-section.Reach thus, fewer cold refrigerant may flow into compressor from vaporizer.Then design pumping tube like this, make can be bumped into an intervalve in its inside, intervalve is surrounded by a helical spring simultaneously, makes the one end bearing enter the ingress of housing at pumping tube, the other end is bearing on the intervalve, to reach the connection of pumping tube on pumping muffler.All these known tests of attempting to prevent from the cold refrigerant of from evaporator drier to mix with the refrigerant of the heat of compressor only impel the minimizing of this mixing, but end fully.
Known by WO 03/038280, the entrance cross-section of pumping muffler directly is connected with the outlet of pumping tube, makes the refrigerant of from evaporator drier directly to import pumping muffler, and does not arrive compressor and be heated there.Because even the cold refrigerant of having mentioned when suction valve closure also has the fact of the flow of constant, flow into pumping muffler with rising now by directly being connected, in pumping muffler, just need to be provided with a compensation volume, because refrigerant raises from the pressure that pumping tube replenish to flow in the pumping muffler that causes continuously, and make that the refrigerant that is positioned at pumping muffler can be by it again from silencing apparatus inflow compressor housing with compensation.In next imbibition cycle, make on the one hand and be positioned at refrigerant pumping muffler or flow into pumping muffler from pumping tube by suction valve sucker clutch release slave cylinder unit, but make the refrigerant that is positioned at compressor housing flow into compensation volume by the leakage from the pistons work piston-cylinder unit with by the outflow of having mentioned from pumping muffler, so that pressure balance.
But at this moment occurred particularly in overflowing to compensation volume the time the flow characteristic danger that strengthens of flow losses under cover, described compensation volume can not produce when pumping tube directly is not connected with pumping muffler.
Summary of the invention
Therefore the objective of the invention is, avoid these shortcomings and a kind of coolant compressor that starts described type is set, wherein when compression process begins, therefore also must the temperature of refrigerant keep low as far as possible when the clutch release slave cylinder of sucker clutch release slave cylinder unit, wherein the flow losses when sucking are prevented from as far as possible.Another object of the present invention is, makes the pressure surge that occurs in compressor and pumping muffler keep as far as possible little, and the noise level in overflowing to compensation volume the time keeps low as far as possible.
This coolant compressor that can a kind ofly have following technical characteristics is realized according to the present invention, this coolant compressor has the compressor housing of a gas tight seal, the pistons work piston-cylinder unit of one compression refrigerant is at the internal work of compressor housing, this pistons work piston-cylinder unit has and comprises the suction valve that is arranged on the suction port in its valve plate, wherein in the work cylinder head of piston cylinder, be provided with one and have the pumping muffler that a dress is irritated volume, refrigerant flows to the suction valve of pistons work piston-cylinder unit by it, and pumping muffler has an entrance cross-section, refrigerant flows into pumping muffler by it, and a compensation volume that is connected with compressor with pumping muffler is set, refrigerant is in the to-and-fro motion of compensation volume the inside, and compensation volume is 0.5 to 3 times of pistons work volume of pistons work piston-cylinder unit.
By providing a compensation volume of volume with 0.5 to 3 times of swept volume of the piston that is equivalent to the pistons work piston-cylinder unit to guarantee, even when suction valve closure, also can not arrive in the compressor housing and mix with heated refrigerant there from the refrigerant of pumping tube.Guarantee in suction process, do not have refrigerant to suck pumping muffler or clutch release slave cylinder by compensation volume simultaneously from compressor housing.
Can reduce in addition along with the volume that affords redress owing to enter the noise that compensation volume and compression case volume brought and form, thereby do not produce the noise that is harmful to for the operator, this is important for household refrigerator particularly.Bigger slightly in addition compensation volume can be made aspect production technology easily.
Minimum flow cross in compensation volume has the cross-section area that is equivalent to suction port cross-section area 1/4 to 3/4.Guarantee that thus the pressure margin is little, thereby reduce flow losses and strengthen external noise on the other hand and check.
The cross section of compensation volume allows 1.5 times corresponding to the piston basal area at most.Guarantee that thus the locational requirement of compensation volume is unlikely too big on the one hand, guarantees that on the other hand cold and gas heat of suction does not mix the boundary layer that forms the following stated in other words.
Compensation volume has length and its diameter ratio of a circular cross section and compensation volume and has narrated a kind of embodiment preferred greater than 10 feature, and it causes especially little flow losses.
Although in order there to be additional compensation volume still to reach pumping muffler compact structure as far as possible, compensation volume by one in cross section basically the expansion pipe of U-shaped constitute, it surrounds pumping muffler to small part.
The preferred embodiment that connects the entrance cross-section of pumping tube and pumping muffler is: being connected by an elastomeric plastics flexible pipe of being made up of PTEE, acrylonitrile, butadiene or fluorine rubber of the entrance cross-section of pumping muffler and pumping tube made; The elastomeric plastics flexible pipe is a bellows; Pumping tube is provided with barb; Pumping tube is provided with latch elements, corresponding latch elements acting in conjunction on described latch elements and the plastic flexible pipe.
The entrance cross-section of pumping muffler and pumping muffler are done to such an extent that be separated from each other sometimes with the intermediate location of compensation volume and are overlapped sometimes.Here according to selecting best embodiment in the difference of compressor locational requirement, the another kind of embodiment preferred of imagination under the entrance cross-section of pumping muffler and pumping muffler and situation that the intermediate location of compensation volume overlaps wherein, that is: compensation volume is made of a sleeve pipe, this sleeve pipe closely surrounds suction port or entrance cross-section on the one hand, on the other hand at least along the one section encirclement and the vaporizer of coolant compressor refrigerant pumping tube that be connected, that stretch into compressor and towards compressor housing; Pumping tube in sleeve pipe until approaching suction port; Sleeve pipe and pumping muffler are made of one.This embodiment has such advantage, does not promptly require between pumping tube and the pumping muffler to be tightly connected.
Description of drawings
Then carry out of the present invention specifying.Accompanying drawing is represented:
Fig. 1 hermetically enclosed coolant compressor of the present invention and the front view of a compressor housing of cutting open;
The sectional view of Fig. 2 hermetically enclosed coolant compressor of the present invention;
The positive view of Fig. 3 hermetically enclosed coolant compressor of the present invention;
Fig. 4 is by the sectional view of the pumping muffler of prior art;
Another sectional view of Fig. 5 one known pumping muffler;
The sectional view of Fig. 6 pumping muffler of the present invention when suction valve closure;
The sectional view of Fig. 7 pumping muffler of the present invention when suction valve is opened;
The oblique drawing of Fig. 8 pumping muffler in compressor housing of the present invention;
A kind of selection embodiment of Fig. 9 pumping muffler of the present invention;
Another kind of alternative embodiment of Fig. 9 a pumping muffler of the present invention;
A kind of additional alternative embodiment of Figure 10 pumping muffler of the present invention;
The partial view that is tightly connected between Figure 11 pumping muffler and the pumping tube;
The partial view of a kind of alternative embodiment that is tightly connected between Figure 12 pumping muffler and the pumping tube;
The partial view of the another kind of selectable embodiment that is tightly connected between Figure 13 pumping muffler and the pumping tube;
The partial view that Figure 14 one plastic flexible pipe is connected with pumping tube;
The partial view that Figure 15 one plastic flexible pipe is connected with pumping tube;
The partial view that Figure 16 one plastic flexible pipe is connected with pumping tube;
The partial view that Figure 17 one plastic flexible pipe is connected with pumping tube;
The partial view that Figure 18 one plastic flexible pipe is connected with pumping tube;
The oblique drawing of Figure 19 the present invention one selectable pumping muffler;
Another oblique drawing of the pumping muffler of the present invention of Figure 20 Figure 19;
The sectional view of the pumping muffler of the present invention of Figure 21 Figure 19;
Another sectional view of the pumping muffler of the present invention of Figure 22 Figure 19.
Embodiment
Fig. 1,2 and 3 represents the sectional view of a hermetically enclosed coolant compressor respectively, and wherein Fig. 1 and 3 represents respectively along the view of direction of arrow A among Fig. 2.Inner at hermetically enclosed compressor housing 1 by spring 2 yielding supports one piston cylinder electric motor units.
The piston cylinder electric motor units is mainly formed by a cylindrical housings 3 and at its inside piston 4 and crankshaft bearing 5 of moving back and forth, and crankshaft bearing is perpendicular to 6 settings of clutch release slave cylinder axis.Crankshaft bearing 5 supports a bent axle 7, and stretches into the central hole 8 of a motor 10 rotors 9.In bent axle 7 upper ends one connecting rod bearing 12 is arranged, by its drive link and further driven plunger 4.Bent axle 7 has an oilhole 13 and is fixed in the zone 14 on the rotor 9.Pumping muffler 16 is arranged on the work cylinder head 15, and pumping muffler should be reduced to minimum with noise in sucking the refrigerant process.
Fig. 4 represents a sectional view by the pumping muffler 16 of prior art.As having been seen by Fig. 1,2 and 3, pumping muffler 16 is arranged on the hermetically enclosed compressor housing 1 internal work cylinder head 15.Come from evaporator drier, compare cold refrigerant inside by near pumping tube 17 inflow compressor housing 1 pumping muffler 16 entrance cross-sections 18 when adopting this known pumping muffler 16 with the hot refrigerant that is positioned at compressor housing 1, there it and the hot refrigerant compressor housing 1 in mix and heat.
Usually by a plurality of series connection and/or the interconnective cavity V1 of pipe that pass through in parallel, V2, Vn and are positioned at oily separating opening 31 compositions of minimum point by the pumping muffler 16 of prior art.Cold refrigerant flows into compressor housing 1 inside by pumping tube 17, carry out there by mixing the first time with the hot refrigerant that is positioned at compressor housing 1 of structures shape, mixed then with heated refrigerant and flowed in the first cavity V1 by entrance cross-section 18, flow into the second cavity V2 of pumping muffler 16 then, and not only mixed with the hot refrigerant there again, thereby carry out the heating of refrigerant again at V1 but also in V2.Heating between not coexisting before the outlet of pumping tube 17 and pumping muffler 16 suction ports 24 nearby according to the power of coolant compressor in this known pumping muffler is between the 30K to 40K.
Fig. 5 represents one equally by prior art, that is by the pumping muffler known to the WO03/038280 16, but its entrance cross-section 18 closely links to each other with pumping tube 17, therefore from the cold refrigerant of pumping tube 17 before it sucks pumping muffler 16 not be in compressor housing 1 in the refrigerant of heat mix.
On pumping muffler 16, connect a compensation volume 21, can carry out because pumping muffler 16 and pumping tube 17 direct is connected needed pressure compensation, in compensation volume 21, not only be connected with pumping muffler 16 but also with compressor by it.But cause the flowing state of refrigerant by needed pressure compensation, this may cause flow losses, and this makes the energy that the temperature of refrigerant is obtained when reducing compression process and begin come to naught again.
In order to prevent or to reduce this flow losses, need such design compensation volume 21, make and obtain less than sucking the energy that is reached by improvement by the energy loss that flow losses caused of extra appearance.Fig. 6 represents an embodiment of pumping muffler of the present invention.In Fig. 6, represent pumping muffler 16 with sectional view.Fig. 1,2 and 3 has equally illustrated with a this coolant compressor by pumping muffler 16 of the present invention.The entrance cross-section 18 of pumping muffler 16 is connected with the pumping tube 17 that comes from evaporator drier by a hermetically enclosed connection 19 that schematically illustrates.Connect can be as being tightly connected 19 for any especially elasticity of being familiar with of those skilled in the art in principle, for example simple rubber hose, but it must be tightly connected with pumping muffler 16 and pumping tube 17.The example of this connection of Figure 11 to 18 expression.Pumping muffler 16 restriction dresses of the present invention are irritated volume 20 (can consider how dress is irritated volume structure, and this also is common).Connect a compensation volume 21 on pumping muffler 16, it is made of a U-shaped expansion pipe 22.Shown in U-shaped expansion pipe 22 such advantage is provided, be that it surrounds an enough big compensation volume 21, only need little additional positions on the other hand, and foundation reduces the needed flow characteristic of action loss, compensation volume 21 or expansion pipe 22 is connected with the inside of compressor housing 1 by compensating port 23, and passes through ferry 26 and be connected with the dress filling volume 20 of pumping muffler 16.
The flow path of refrigerant when Fig. 6 is illustrated in suction valve closure with arrow, suction valve is in the back that is positioned at pumping muffler 16 suction ports 24 on a side of piston of valve plate.
Fig. 7 represents that same pumping muffler of the present invention 16 is together with the flow path when suction valve is opened.In this case not only from compensation volume 21 but also from dress filling volume 20 and pumping tube 17 suction refrigerant.Because refrigerant has the temperature lower than the hot refrigerant in compressor housing 1 in the compensation volume 21, be lower than the mixing temperature of refrigerant when adopting from the refrigerant mixing temperature of described suction area, prevent that thus foregoing undesirable temperature from raising by the known pumping muffler of prior art.Because feature of the present invention, compensation volume 21 is 0.5 to 3 times of pistons work piston-cylinder unit pistons work volume, and hot refrigerant can not arrive in the pumping muffler from compressor, arrives dress in this embodiment and irritates in the volume 20.Because the minimum flow cross in the compensation volume 21 has the fact of the cross-section area that is equivalent to suction port 24 cross-section areas 1/4 to 3/4, guaranteed that the pressure difference between pumping muffler 16 and compressor housing 1 inside is very little, simultaneously big at the noise damping of compressor.Help to enlarge compensation volume in addition, wherein it be at least pistons work piston-cylinder unit pistons work volume at least half, especially 0.5 to 3 times.
Make the flow losses minimum by pumping muffler of the present invention simultaneously, and refrigerant can flow into compensation volume 21 without a doubt or flow out from its inside, and refrigeration processes not played adverse effect.
For the property that better comes into plain view, Fig. 8 represents of the present invention not with the oblique drawing of the pumping muffler 16 in the compressor housing 1 of piston cylinder electric motor units.
Fig. 9 represents a kind of alternative embodiment of pumping muffler 16 of the present invention together with compensation volume 21.Here compensation volume 21 and pumping muffler 16 are made of a sleeve pipe 34, and it surrounds and feed suction port 24 on the one hand, on the other hand along a certain section latter end that surrounds pumping tube 17.Sucking the section that cycle period flows into sleeve pipe 34 and constitutes the dress filling volume 20 of pumping muffler 16 from the cold refrigerant of pumping tube 17 outflows.When the compression cycle of following,, the dress of suction valve closure pumping muffler 16 no longer sucks remaining refrigerant from pumping tube 17 because irritating volume 20, therefore a section of being back to equally by sleeve pipe 34 of refrigerant constitutes in the compensation volume 21, and will be in the hot refrigerant of its inside is clamp-oned compressor housing 1 by compensating port 23 inside.
Here also with Fig. 5 the same with described in 6, between heat and cold refrigerant, also form one with the boundary layer 25 that sucks shuttling movement.Suck circulation time at the next one and both also from the compensation volume 21 of sleeve pipe 34, sucked cold refrigerant to clutch release slave cylinder from pumping tube 17.Here importantly, the boundary layer is no more than the line of representing with 33 to suction port 24 directions, and it constitutes the entrance cross-section 18 of pumping muffler 16 simultaneously or crosses ferry 26 in the present embodiment, to prevent that hot and cold refrigerant is mixed.
Simultaneously do not allow to clamp-on in the compressor housing 1 from compensation volume 21 from the cold refrigerant of pumping tube 17, therefore the back of the line of representing with 23 (compensating ports) is not passed in boundary layer 25 in Fig. 9, therefore irrelevant with embodiment, thus require the volume of compensation volume 21 and cooling power also accurately to mate by of the present invention with the swept volume of pistons work piston-cylinder unit.
Fig. 9 a represents the another kind of alternative embodiment of pumping muffler 16 together with compensation volume 21, and wherein comparing among pumping muffler 16 and Fig. 9 also has an additional volume 20.This in other respects scheme is with identical in the scheme shown in Fig. 9.
Figure 10 represents a kind of additional selectable form of implementation of pumping muffler 16 of the present invention.Correspondingly keep reference character constant.As can knowing by a large amount of different structural types, the Mechanical Builds of compensation volume can freely be selected in principle, if keep aspect its volume and the minimum flow cross compensation volume 21 be arranged on pumping tube 17 outlet upstreams by feature of the present invention.So just, can realize maximum energy-saving, and correspondingly improve the efficient of coolant compressor.
How the different compensation volume 21 and the structure of pumping muffler is less important if being made, as long as realize that feature of the present invention and gas column or boundary layer 25 can to-and-fro motion in compensation volume.
Therefore pumping muffler 16 only is made up of a conical basically dress filling volume 20 that distributes in pressing the embodiment of Fig. 9, in the embodiment of pressing Fig. 9 a, irritate volume 20 and form, and in pressing the embodiment of Figure 10, form by cavity V2 and V1 by a conical basically cavity 20a who distributes and a dress.Certainly at any time can be in parallel or series connection the additional cavities of pumping muffler 16 is set, and cause pumping muffler 16 better acoustic attenuation performances.
Figure 11 to 18 expression pumping tube 17 and pumping muffler 16 by the different embodiments that is tightly connected of the present invention.If just this is connected in fact also and seals, in other words, if there is not hot refrigerant to suck pumping muffler 16 from compressor housing 1, compensation volume 21 its optimum efficiencies of performance, its prerequisite is the embodiment that adopts as shown in Fig. 6 and Fig. 7.
Figure 11 represents the simplest connection.Elastic bellows 19 only is enclosed within on the pumping tube 17 in this case, and further unfixing, especially bonding.
Figure 12 and 13 represents complicated but also more firm being connected.
The wall of compressor housing 1 has the flange 28 of one day to inside in Figure 12, and elastomeric plastics flexible pipe 19 is enclosed within above it, and it stretches into the entrance cross-section 18 of pumping muffler 16 simultaneously.The plastic flexible pipe 19 that also can make spring tube is surrounded by a helical spring 27, and it provides necessary stability and fixes.One O type circle 29 not only had been set respectively in flange 28 zones but also in entrance cross-section 18 zones, and it is responsible for desired seal.
Pumping muffler 16 also has one correspondingly towards the flange of compressor housing 1 inside in Figure 13.
Different fixedly possibility between Figure 14 to 18 expression elastic coupling element 19 and the pumping tube 17, it both can make tooth (Figure 17, Figure 18), also can make the barb (Figure 16) that is arranged on the elastic coupling element or simple step (Figure 14, Figure 15).
As the compensation volume described in Fig. 9,9a and 10 21 together with a kind of embodiment of pumping muffler 16 in owing to as described in reason eliminated this necessity that is tightly connected between pumping muffler 16 and the pumping tube 17.
Figure 19, Figure 20, Figure 21 and Figure 22 represent that pumping muffler 16 is together with as another embodiment of the compensation volume 21 crossed of illustrative in Fig. 9,9a and 10.Wherein pumping tube 17 is extended near the entrance cross-section 18 of pumping muffler 16 always.Entrance cross-section 18 is tightly connected by means of plastic flexible pipe 19 and pumping tube 17.
For see the clearer reason remaining parts of in Figure 19,20,21 and 22, not drawing coolant compressor.
Claims (14)
1. hermetically enclosed coolant compressor, it has the compressor housing (1) of a gas tight seal, the pistons work piston-cylinder unit of one compression refrigerant is at the internal work of compressor housing, this pistons work piston-cylinder unit has and comprises the suction valve that is arranged on the suction port (24) in its valve plate, wherein in the work cylinder head (15) of piston cylinder, be provided with one and have the pumping muffler (16) that a dress is irritated volume (20), refrigerant flows to the suction valve of pistons work piston-cylinder unit by it, and pumping muffler (16) has an entrance cross-section (18), refrigerant flows into pumping muffler (16) by it, and a compensation volume (21) that is connected with pumping muffler (16) and compressor housing (1) inside is set, refrigerant is characterized by in the to-and-fro motion of compensation volume the inside: compensation volume (21) is 0.5 to 3 times of the pistons work volume of pistons work piston-cylinder unit.
2. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: the minimum flow cross (32) in the compensation volume (21) has a cross-section area that is equivalent to suction port (24) cross-section area 1/4 to 3/4.
3. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: the cross-section area of compensation volume (21) mostly is 1.5 times of piston basal area of piston cylinder unit most.
4. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: compensation volume (21) has a circular cross section, and the length of compensation volume (21) and its diameter ratio are greater than 10.
5. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: compensation volume (21) becomes the expansion pipe (22) of U-shaped to constitute by a cross section basically, and this expansion pipe to small part is surrounded pumping muffler (16).
6. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: being connected by an elastomeric plastics flexible pipe (19) of being made up of PTEE, acrylonitrile, butadiene or fluorine rubber of the entrance cross-section (18) of pumping muffler (16) and pumping tube (17) made.
7. by the hermetically enclosed coolant compressor of claim 6, it is characterized by: the elastomeric plastics flexible pipe is a bellows.
8. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: pumping tube (17) is provided with barb.
9. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: pumping tube (17) is provided with latch elements, and described latch elements and plastic flexible pipe (19) are gone up corresponding latch elements acting in conjunction.
10. by the hermetically enclosed coolant compressor of claim 1, it is characterized by: entrance cross-section (18) and the connection mouth (26) between compensation volume (21) and dress filling volume (20) are arranged in the different sections of pumping muffler housing.
11. each the hermetically enclosed coolant compressor by claim 1 to 3 is characterized by: entrance cross-section (18) is the connection mouth (26) between compensation volume (21) and the dress filling volume (20) simultaneously.
12. hermetically enclosed coolant compressor by claim 11, it is characterized by: compensation volume (21) is made of a sleeve pipe (34), this sleeve pipe closely surrounds suction port (24) or entrance cross-section (18) on the one hand, be connected with the vaporizer of coolant compressor along one section encirclement at least on the other hand, stretch into the refrigerant pumping tube (17) of compressor housing (1) inside and towards compressor housing (1).
13., it is characterized by by the hermetically enclosed coolant compressor of claim 12: pumping tube (17) in sleeve pipe (34) until approaching suction port (24).
14. by the hermetically enclosed coolant compressor of claim 13, it is characterized by: sleeve pipe (34) and pumping muffler (16) are made of one.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT0093304U AT7831U1 (en) | 2004-01-29 | 2004-12-22 | REFRIGERANT COMPRESSOR |
| ATGM933/2004 | 2004-12-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101111677A CN101111677A (en) | 2008-01-23 |
| CN100587268C true CN100587268C (en) | 2010-02-03 |
Family
ID=36601407
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200580047247A Active CN100587268C (en) | 2004-12-22 | 2005-12-22 | Hermetic refrigerant compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20080008603A1 (en) |
| EP (1) | EP1828603B1 (en) |
| CN (1) | CN100587268C (en) |
| AT (1) | ATE393880T1 (en) |
| DE (1) | DE502005003926D1 (en) |
| WO (1) | WO2006067218A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10320197A1 (en) * | 2002-12-20 | 2004-07-08 | Degussa Ag | Enveloped controlled-release peroxygen compounds, process for their preparation and their use |
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| BR112014015920A8 (en) * | 2011-12-26 | 2017-07-04 | Arcelik As | compressor comprising a connecting element |
| BR102014007254A2 (en) * | 2014-03-26 | 2015-12-08 | Whirlpool Sa | fluid selector device for reciprocating compressor and acoustic filter provided with fluid selector device |
| CN103925190B (en) * | 2014-03-31 | 2017-06-06 | 扎努西电气机械天津压缩机有限公司 | Improve the freezer compressor air suction silencer of gettering efficiency |
| KR20160055497A (en) * | 2014-11-10 | 2016-05-18 | 엘지전자 주식회사 | Reciprocating compressor and a method for assembling the same |
| BR102014029659B1 (en) * | 2014-11-27 | 2022-01-11 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | ACOUSTIC SUCTION FILTER AND SUCTION LINE INCLUDING ACOUSTIC SUCTION FILTER |
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| CN109844313B (en) * | 2016-08-23 | 2021-06-01 | 思科普有限责任公司 | Suction muffler |
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- 2005-12-22 AT AT05825178T patent/ATE393880T1/en not_active IP Right Cessation
- 2005-12-22 EP EP05825178A patent/EP1828603B1/en active Active
- 2005-12-22 DE DE502005003926T patent/DE502005003926D1/en active Active
- 2005-12-22 WO PCT/EP2005/057110 patent/WO2006067218A1/en active IP Right Grant
- 2005-12-22 US US11/793,871 patent/US20080008603A1/en not_active Abandoned
- 2005-12-22 CN CN200580047247A patent/CN100587268C/en active Active
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| US4793775A (en) * | 1984-10-13 | 1988-12-27 | Aspera S.R.L. | Hermetic motor-compressor unit for refrigeration circuits |
| US4730695A (en) * | 1986-01-10 | 1988-03-15 | Necchi Societa Per Azioni | Muffler for hermetic compressor |
| CN1133007C (en) * | 1998-12-31 | 2003-12-31 | Lg电子株式会社 | Working-fluid intaking structure for hermetic compressor |
| CN1125920C (en) * | 1999-02-26 | 2003-10-29 | 巴西船用压缩机有限公司 | Suction muffler for hermetic Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1828603A1 (en) | 2007-09-05 |
| EP1828603B1 (en) | 2008-04-30 |
| US20080008603A1 (en) | 2008-01-10 |
| WO2006067218A1 (en) | 2006-06-29 |
| DE502005003926D1 (en) | 2008-06-12 |
| CN101111677A (en) | 2008-01-23 |
| ATE393880T1 (en) | 2008-05-15 |
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