Classifications

• • 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 sealed refrigerant compressor, which is a hermetically sealed
• Compressor housing has, in the interior of a
• Refrigerant-compressing piston-cylinder unit operates on the cylinder head, a suction muffler (Muffler) is arranged, flows through the refrigerant to the intake valve of the piston-cylinder unit, according to the preamble of claim 1.
• a suction muffler (Muffler) is arranged, flows through the refrigerant to the intake valve of the piston-cylinder unit, according to the preamble of claim 1.
• Such refrigerant compressors have long been known and are mainly used in refrigerators or shelves.
• the annual production quantity is correspondingly high.
• the refrigerant process as such has long been known.
• the refrigerant is heated by energy absorption from the space to be cooled in the evaporator and finally superheated and by means of the refrigerant compressor to a higher
• Refrigerant in the cylinder of the piston-cylinder unit therefore causes as well as the lowering of the temperature during the compression process and the associated
• Discharge temperature a reduction of the required technical work for the compaction process.
• the suction of the refrigerant takes place via a suction pipe coming directly from the evaporator during an intake stroke of the piston-cylinder unit.
• the suction pipe opens in known hermetically sealed refrigerant compressors usually in the hermetically sealed compressor housing, usually in the vicinity of the inlet cross section in the suction muffler, from where the refrigerant flows into the suction muffler and from this directly to the intake valve of the piston-cylinder unit.
• the suction muffler serves primarily to keep the noise level of the refrigerant compressor during the intake as low as possible.
• suction mufflers are usually made of several volumes that communicate with each other, and an inlet cross-section, through which the refrigerant is sucked from the hermetically sealed compressor housing volume in the interior of the suction muffler, and an opening which is close to the intake valve of the piston-cylinder Unit is present.
• the mixture is essentially due to the fact that the intake valve of the piston-cylinder unit per cycle only over a crank angle range of approx. 180 ° is open and therefore only within this time window refrigerant can be sucked into the cylinder of the refrigerant compressor. Thereafter, during the compression cycle, the intake valve is closed.
• the cold refrigerant has an almost constant mass flow, even with the intake valve closed, whereby it flows with the intake valve closed and flows into the compressor housing and the moving piston-cylinder unit and their components cools, which in turn, however, a heating of the Refrigerant itself causes.
• due to the pressure oscillations during the compression phase further flow processes from the compressor housing to the suction muffler and vice versa, whereby an additional mixing is effected.
• Refrigerant compressors the outlet of the intake manifold for the
• Compressor housing can escape.
• one has the Saugrohrende designed so that in this an intermediate tube could be introduced.
• the intermediate tube was surrounded by a spiral spring, which is supported on the one hand at the inlet of the suction tube into the housing and on the other hand on the intermediate tube to achieve the connection of the suction tube to the suction muffler.
• all these known attempts to prevent mixing of the cold refrigerant from the evaporator with the heated refrigerant inside the compressor housing have only caused a reduction in this mixing, but not a complete inhibition.
• the intake silencer can be compensated from the intake manifold and via which the refrigerant located in the intake silencer can again flow out of it into the compressor housing. At the next Ansuagtakt then on the one hand located in the suction muffler or.
• the aim of the present invention is therefore to avoid this disadvantage and to provide a refrigerant compressor of the type mentioned, in which the refrigerant temperature at the beginning of the compression process, and thus necessarily when sucking into the cylinder of the piston-cylinder unit, is kept as low as possible , Wherein the flow losses are kept as far as possible during intake. It is a further object of the present invention to minimize the pressure fluctuations occurring in the interior of the compressor housing and in the suction muffler and to keep the noise level as low as possible when flowing over into the equalizing volume.
• the associated with the creation of the compensation volume due to the flow processes in the compensation volume and in the compressor housing noise be minimized so that it does not disturb the operator disturbing noise, which is particularly important for household refrigerators.
• a slightly larger compensation volume production technology can be made easier.
• the smallest flow cross-section in the compensation volume has a cross-sectional area which corresponds to 1/4 to 3/4 of the cross-sectional area of the intake opening. This ensures that the pressure difference is small, thereby reducing the flow losses and on the other hand, the noise attenuation to the outside is large.
• the cross-section of the compensation volume may not exceed 1, 5 times the
• the characterizing features of claim 5 are provided, according to which the compensating volume is formed by a cross-sectionally substantially U-shaped compensating tube, which at least partially wraps around the suction muffler.
• the characterizing features of claims 6 to 9 describe a preferred embodiment of the connection of intake manifold and inlet cross-section in the suction muffler.
• claims 10 and 11 describe two different embodiments of a hermetically sealed refrigerant compressor, in which the inlet cross section is formed in the suction muffler and the transition from suction muffler in the compensating volume once separated and once coincides.
• the most advantageous embodiment variant is to be selected here, wherein in the case where the inlet cross section in the suction muffler and the transition of suction muffler in the equalization volume coincide another preferred embodiment according to the characterizing features of claims 12 to 14 is provided ,
• This variant has the advantage that a tight connection between the intake manifold and suction muffler is not required.
• Fig. 1 is a front view of a hermetically sealed refrigerant compressor according to the invention with a cut
• FIG. 2 shows a side view of a hermetically sealed refrigerant compressor according to the invention in section
• Fig. 3 is a front view of a hermetically sealed refrigerant compressor according to the invention in section
• Fig. 4 is a sectional view of a suction muffler according to the prior art
• Fig.5 is another sectional view of a known suction muffler
• Fig. 6 is a sectional view of a suction muffler according to the invention with a closed intake valve
• Fig .7 is a sectional view of a suction muffler according to the invention with an open intake valve
• Fig. 8 shows an oblique view of the suction muffler according to the invention in the compressor housing
• Fig. 9 shows an alternative embodiment of a suction muffler according to the invention
• FIG. 10 shows an additional alternative embodiment of a suction muffler according to the invention
• Fig. 11 is a detail view of a hermetically sealed connection between the suction muffler and intake manifold
• Fig. 12 shows a detailed view of an alternative embodiment of a hermetically sealed connection between the suction muffler and intake manifold
• FIG. 13 shows a detailed view of a further alternative embodiment of a hermetically sealed one
• Fig. 14 is a detail view of a compound of a
• FIG. 15 is a detail view of a compound of a plastic hose with a suction tube
• Fig. 16 is a detail view of a compound of a plastic hose with a suction tube
• Fig. 17 is a detail view of a compound of a plastic hose with a suction pipe
• Fig. 18 is a detail view of a compound of a plastic hose with a suction tube
• Fig. 19 is an oblique view of an alternative Saugschalldämpfers invention
• Fig. 20 is a further oblique view of the invention
• FIG. 21 is a sectional view of the suction muffler according to the invention from FIG. 19
• FIG. 22 shows a further sectional view of the suction muffler according to the invention from FIG. 19
• FIGS. 1, 2 and 3 each show a sectional view through a hermetic-type refrigerant compressor
• FIG. 1 and 3 each show a view in the direction of arrow A from FIG.
• a piston-cylinder engine unit is mounted elastically via springs 2.
• the piston-cylinder-motor unit consists essentially of a cylinder housing 3 and the therein a lifting movement performing piston 4, and a crankshaft bearing 5, which is arranged perpendicular to the cylinder axis 6.
• the crankshaft bearing 5 receives a crankshaft 7 and protrudes in a centric bore 8 of the rotor 9 of an electric motor 10.
• At the upper end of the crankshaft 7 is a connecting rod bearing 12, via which a connecting rod and subsequently the piston 4 is driven.
• the crankshaft 7 has a lubricating oil bore 13 and is fixed in the region 14 on the rotor 9.
• On the cylinder head 15 of the suction muffler 16 is arranged to reduce the noise during the intake of the refrigerant to a minimum.
• Fig. 4 shows a sectional view through a suction muffler 16 according to the prior art.
• the suction muffler 16 is, as already apparent from FIGS. 1, 2 and 3, arranged inside the hermetically sealed compressor housing 1 on the cylinder head 15.
• cold refrigerant flows when using such a known suction muffler 16 via a suction pipe 17 in the interior of the compressor housing 1 in the vicinity of the inlet cross section 18 of the suction muffler 16, where it is mixed with the already located in the compressor housing 1, warm refrigerant and heated.
• Suction mufflers 16 generally consist of a plurality of series-connected and / or parallel-connected volume Vl, V2, V n , which are connected to each other via tubes, and a ⁇ labscheideö réelle 31 at the lowest point.
• the cold refrigerant flows via the suction pipe 17 into the interior of the compressor housing 1 where, due to the design, a first mixing takes place with the hot refrigerant already present in the compressor housing 1. Then, the already mixed and heated refrigerant flows through the inlet cross section 18 in the first volume Vl and then in the second volume V2 of the suction muffler 16 and mixes again in both Vl and V2 with the already existing there warm refrigerant, thereby again heating the refrigerant takes place.
• these known Suction mufflers is the heating between the outlet of the suction pipe 17 and shortly before the intake port 24 in the suction muffler 16 between 3OK and 40K, depending on the performance of the refrigerant compressor.
• FIG. 5 shows a suction muffler 16, likewise known from the prior art, namely from WO03 / 038280, whose inlet cross-section 18 is, however, tightly connected to the suction tube 17.
• the cold refrigerant coming from the suction pipe 17 can not mix with the warmer refrigerant located in the compressor housing 1 before it is sucked into the suction muffler 16.
• a compensating volume 21 is connected, via which the required due to the direct connection of the suction muffler 16 with the suction pipe 17 pressure equalization can take place in which a connection to both the suction muffler 16 and in the interior of the compressor housing. Due to the required pressure equalization, however, flow states of the refrigerant occur, which can lead to flow losses which negate the energy gain which is achieved by the reduction of the refrigerant temperature at the beginning of the compression phase.
• FIG. 6 An embodiment of a suction muffler according to the invention is shown in FIG. 6.
• the suction muffler 16 is shown in Fig. 6 in sectional view. 1, 2 and 3 also show already refrigerant compressor with such a suction muffler according to the invention 16.
• the inlet cross-section 18 of the suction muffler 16 is connected via a schematically illustrated, hermetically sealed connection 19 connected to the suction tube 17 coming from the evaporator.
• a tight connection 19 may in principle any known to those skilled, preferably elastic compound serve, such as a simple rubber hose, but must be tightly connected to the suction muffler 16 and the suction pipe 17. Examples of such compounds are shown in FIG. 11 to FIG.
• the suction muffler 16 according to the invention limits a filling volume 20 (the arrangement of a plurality of filling volumes is conceivable and customary).
• a compensation volume 21 is arranged, which is formed by a U-shaped equalization tube 22.
• the U-shaped compensation tube 22 shown has the advantage of limiting a sufficient compensation volume 21 and, on the other hand, requiring only little additional space, as well as producing the required flow conditions which minimize the mentioned losses.
• the compensation volume 21 or. the equalizing pipe 22 communicates with the interior of the compressor housing 1 via a compensating opening 23 and via the transition opening 26 with the filling volume 20 of the suction silencer 16.
• Fig. 6 shows the flow pattern of the refrigerant with the intake valve closed, that is located behind the intake opening 24 of the suction muffler 16 on the side of the valve plate facing the piston, by means of arrows.
• FIG. 7 shows the same suction muffler 16 according to the invention together with the flow pattern when the intake valve is open. In this case, the refrigerant is sucked in both from the equalizing volume 21 and from the filling volume 20 and the suction pipe 17.
• the refrigerant in the compensating volume 21 has a lower temperature than the warm refrigerant located inside the compressor housing 1, the mixing temperature of the refrigerants from the mentioned intake ranges is lower than the mixing temperature of the refrigerants when using suction mufflers known from the prior art, whereby mentioned above, unwanted temperature increase is prevented.
• Warm refrigerant can due to the feature of the invention that the compensating volume 21, the 0, 5 to 3 times the stroke volume of the piston of the piston-cylinder unit is not from the interior of the compressor housing in the suction muffler, in the embodiment in the volume 20, arrive.
• the smallest flow cross-section 32 in the compensating volume 21 has a cross-sectional area corresponding to 1/4 to 3/4 of the cross-sectional area of the suction port 24 ensures that the pressure difference between the suction muffler 16 and the interior of the compressor housing 1 is low and at the same time the noise attenuation in the interior of the compressor housing is large. This also contributes to an enlargement of the compensating volume, wherein this is at least half, preferably 0, 5 to 3 times the stroke volume of the piston of the piston-cylinder unit.
• Fig. 8 shows, for better clarity, an oblique view of the suction muffler 16 according to the invention in the compressor housing 1 without piston-cylinder-motor unit.
• Fig. 9 shows an alternative embodiment of a suction muffler 16 according to the invention together with
• the equalizing volume 21 and the suction muffler 16 are formed by a jacket tube 34 which on the one hand surrounds the suction opening 24 and opens into this and on the other hand, an end portion of the
• Suction tube 17 encloses along a section.
• the cold refrigerant flowing out of the suction pipe 17 flows into the section of the jacket tube 34 forming the filling volume 20 of the suction muffler 16 during the suction cycle.
• the filling volume 20 of the suction muffler 16 can no longer receive any further refrigerant from the suction pipe 17 due to the closed suction valve Therefore, the refrigerant flows back into the compensating volume 21, which is likewise formed by a section of the jacket tube 34, and displaces the warm refrigerant contained therein via the compensation opening 23 into the interior of the compressor housing 1.
• FIGS. 5 and 6 describe the formation of a boundary layer 25, which is movable depending on the suction cycle, between hot and cold refrigerant.
• cold refrigerant can be sucked into the cylinder both from the intake manifold 17 and from the compensation volume 21 of the shroud tube 34.
• the boundary layer, the line designated 33 which in this embodiment at the same time the inlet cross section 18 in the suction muffler 16 and. the Transition opening 26 forms, not in the direction of suction port 24 is exceeded to prevent mixing of hot and cold refrigerant before the intake process.
• FIG. 9a shows a further alternative embodiment variant of a suction muffler 16 with compensating volume 21, in which the suction muffler 16 still has an additional volume 20 in comparison to that of FIG. Otherwise, this variant is identical to that shown in FIG.
• Fig. 10 shows an additional alternative embodiment of a suction muffler 16 according to the invention.
• the reference numerals have been retained accordingly.
• the design of the compensation volume is in principle freely selectable as long as the features according to the invention of the compensation volume 21, which is located upstream of the outlet opening of the suction tube 17, regarding its volume and the smallest flow cross-section 32 observed. Only then can optimal energy savings be achieved and the efficiency of the refrigerant compressor be improved accordingly.
• Suction mufflers 16 are constructed is as long as secondary as long as the features of the invention are realized and the gas column or. the boundary layer 25 can oscillate in the compensation volume.
• the suction muffler 16 in the embodiment according to FIG. 9 only from a substantially conically extending volume 20, in the embodiment of FIG. 9a from a substantially conically extending volume 20a and the volume 20 and in the embodiment of FIG .10 from the volumes V2 and Vl.
• the parallel or Serial arrangement of additional volumes of the suction muffler 16 is of course possible at any time and requires improved sound-absorbing properties of the suction muffler 16th
• the compensating volume 21 in the embodiment according to FIG. 9 consists of a cylindrical volume, in the embodiment according to FIG. 9a also of a cylindrical volume and in the embodiment according to FIG. 10 of the volume 21a and 21b.
• the further arrangement of equalization volumes, parallel or serial, is of course possible, these, such as 21b contribute to the sound attenuation.
• the smallest flow cross-section 32 according to the invention can be realized either by a diaphragm as shown in FIGS. 9, 9a and 10, or by a spatial constriction as shown in FIG.
• the entire compensating volume 21 can have a constant cross section with the features according to the invention.
• FIGS. 11 to 18 show different embodiments of the hermetically sealed connection of suction pipe 17 and suction muffler 16 according to the invention. Only if this connection is actually tight, in other words, if no warm refrigerant is sucked from compressor housing 1 into suction muffler 16 does this unfold Balancing volume 21 its optimal effect, provided it is a variant as described in Fig. 6 and Fig. 7.
• the simplest connection is shown in FIG. In this case, the elastic bellows 19 is slipped over the suction tube 17, without further fixation, but preferably glued.
• FIGS. 12 and 13 show a more complex but also more stable connection.
• the wall of the compressor housing 1 has an inwardly directed extension 28 on which the elastic plastic tube 19 is slipped, which simultaneously projects into the inlet cross section 18 of the suction muffler 16.
• the plastic tube 19, which may also be designed as an elastic tube is surrounded by a coil spring 27, which provides the necessary stability and fixation.
• an O-ring 29 is arranged, which is responsible for the required tightness.
• the suction muffler 16 has a correspondingly directed into the interior of the compressor housing 1 extension.
• FIGS. 14 to 18 show different fastening possibilities 30 between elastic connecting means 19 and suction tube 17, which can be embodied either as toothing (FIG. 17, FIG. 18) or as barbs (FIG. 16) arranged on the elastic connecting means or as simple paragraphs (Fig. 14, Fig. 15).
• Fig. 19, Fig. 20, Fig. 21, and Fig. 22 show another embodiment of a suction muffler 16 together Compensation volume 21 as already described schematically in FIGS. 9, 9a and 10.
• the suction tube 17 is thereby brought close to the inlet cross section 18 of the suction muffler 16.
• the inlet cross-section 18 is connected by means of plastic hose 19 tightly connected to the suction pipe 17.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Compressor (AREA)

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• 2005
  • 2005-12-22 EP EP05825178A patent/EP1828603B1/fr active Active
  • 2005-12-22 US US11/793,871 patent/US20080008603A1/en not_active Abandoned
  • 2005-12-22 AT AT05825178T patent/ATE393880T1/de not_active IP Right Cessation
  • 2005-12-22 WO PCT/EP2005/057110 patent/WO2006067218A1/fr active IP Right Grant
  • 2005-12-22 CN CN200580047247A patent/CN100587268C/zh active Active
  • 2005-12-22 DE DE502005003926T patent/DE502005003926D1/de active Active

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