EP1864021B1 - Compresseur de fluide frigorigene - Google Patents

Compresseur de fluide frigorigene Download PDF

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Publication number
EP1864021B1
EP1864021B1 EP06725446A EP06725446A EP1864021B1 EP 1864021 B1 EP1864021 B1 EP 1864021B1 EP 06725446 A EP06725446 A EP 06725446A EP 06725446 A EP06725446 A EP 06725446A EP 1864021 B1 EP1864021 B1 EP 1864021B1
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EP
European Patent Office
Prior art keywords
pressure
valve plate
suction
refrigerant compressor
compressor according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP06725446A
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German (de)
English (en)
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EP1864021A1 (fr
Inventor
Günther ZIPPL
Alfred Freiberger
Mathias Ponhold
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Secop Austria GmbH
Original Assignee
ACC Austria GmbH
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Publication date
Priority claimed from AT0019505U external-priority patent/AT8401U1/de
Application filed by ACC Austria GmbH filed Critical ACC Austria GmbH
Priority to AT06725446T priority Critical patent/ATE414225T1/de
Publication of EP1864021A1 publication Critical patent/EP1864021A1/fr
Application granted granted Critical
Publication of EP1864021B1 publication Critical patent/EP1864021B1/fr
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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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • 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
    • F04B39/125—Cylinder heads

Definitions

  • the present invention relates to a hermetically sealed refrigerant compressor with a hermetically sealed compressor housing, in the interior of which a refrigerant-compressing piston-cylinder unit operates, whose cylinder is closed by means of a pressure bore and a suction bore having valve plate and a suction channel and a pressure channel are provided via which refrigerant is sucked via a suction valve into the suction bore and is compressed via a pressure valve from the pressure bore into the pressure channel, wherein a suction muffler is preferably arranged in the suction channel according to the preamble of claim 1.
  • Such refrigerant compressors have long been known and are mainly used in refrigerators or shelves. Accordingly high is the annually produced quantity.
  • the refrigerant process as such has long been known.
  • the boiling refrigerant is vaporized by energy absorption from the space to be cooled in the evaporator and finally superheated and pumped by the refrigerant compressor to a higher energy level, where it emits heat through a condenser and via a throttle, in which a pressure reduction and the cooling of the refrigerant , is transported back to the evaporator.
  • hermetic refrigerant compressors In known hermetic refrigerant compressors according to the prior art is due to design a strong heating of the refrigerant on its way from the evaporator (refrigerator) to the intake valve of the piston-cylinder unit.
  • the suction channel usually opens directly into the interior of the hermetically sealed compressor housing in the vicinity of the inlet opening in a suction muffler, which reduces the intake noise of the piston-cylinder unit and is usually constructed of a plurality of interconnected volumes, as well as having the aforementioned inlet opening and an outlet opening which bears tightly against the suction bore of the valve plate.
  • the described known variant embodiment has the disadvantage that the refrigerant heats up too strongly on its way from the inlet to the interior of the compressor housing to the suction bore. Measurements have shown that between a point in the suction channel shortly before entering the compressor housing and the first volume of the suction muffler, a heating by more than 20 ° C takes place. The main cause of this undesirable heating of the refrigerant is the fact that the fresh refrigerant flowing from the suction channel into the compressor housing is mixed with refrigerant already present in the compressor housing.
  • Any known refrigerant compressor in any case have an identical structure of the piston-cylinder unit, in particular of the cylinder housing, which is closed with a valve plate and an adjoining cylinder cover.
  • the cylinder cover preferably covers the entire Valve plate from which also has the suction hole and the pressure hole.
  • On the valve plate and the suction hole temporarily closing suction valve and the pressure bore temporarily occluding pressure valve are arranged.
  • the cylinder cover is usually provided with a recess for the suction channel, or for the end portion of the suction muffler, which opens into the suction hole.
  • the heated by the compression process refrigerant is forced through the pressure valve and the pressure bore from the cylinder in the cylinder cover, where it due to the construction of the cylinder cover this at least in the pressure channel forming portion, fully fills and thus with the part of this pressure channel forming valve plate , come in contact.
  • the temperature of the valve plate corresponds due to this fact substantially the temperature of the compressed refrigerant. Since the gas in the interior of the cylinder over more than 300 ° crank angle is colder than the valve plate, there is a heat flow from directly the valve plate or indirectly from the valve plate to the cylinder wall and from there to the gas inside the cylinder, which adversely affects the Energy efficiency.
  • the high temperature prevailing in the cylinder cover also causes a heat flow in the direction of the end section of the suction muffler, which is indeed surrounded by the cylinder cover, whereby, however, the refrigerant coming from the suction muffler, which is still to be compressed, is also undesirably heated.
  • the known refrigerant compressor constructions due to their cylinder cover construction of the initially mentioned objective, namely a reduction of the suction temperature and the Ausschiebetemperatur run counter.
  • the components according to the invention enable the direct, compressed refrigerant to escape directly via the pressure bore into the pressure channel without having to flow off along a section of the valve plate. Only the region of the valve plate which directly surrounds the pressure bore comes into contact with the hot refrigerant at its side facing away from the piston. As a result, the heat transfer from the hot, already compressed refrigerant to the valve plate over conventional cylinder heads in refrigerant compressors can be drastically reduced.
  • valve plate and the cylinder wall remain cooler and thereby allow a dissipation of heat from the interior of the cylinder housing, or prevent the inflow of heat into the gas in the cylinder. Furthermore, this way too the heat transfer from the valve plate to the suction hole and thus be reduced in the suction channel, whereby the intake temperature can be lowered.
  • the characterizing features of claim 2 that portion of the pressure channel which impinges on the valve plate, that is, that portion which lies within the pressure contact edge, can be accurately dimensioned and optimized with respect to heat transfer. It is necessary on the one hand, that the pressure bore is within this range and on the other hand, the transition between the pressure channel and the pressure bore is formed aerodynamically and still allows a tight connection. Since according to the invention, the pressure channel or more precisely the last portion of these channels substantially perpendicular to the pressure bore and thus impinges on the valve plate to prevent heat transfer from the valve plate to the pressure channel or vice versa, the shape of the pressure contact edge can be chosen so that the refrigerant flows around the valve plate only along a small area.
  • the ratio of the cross-sectional area of the pressure bore to the area enclosed by the pressure-contact edge is more than 1/12.
  • the component forming the pressure channel has a directly adjoining the pressure bore, leading away from the valve plate section and an adjoining this section further section, relative to the cylinder bore radially outwards, preferably at a distance from the valve plate preferably runs parallel thereto.
  • the portion leading away from the valve plate and / or the further portion of the pressure channel is made of poorly conductive plastic, whereby the heat output of the compressed refrigerant can be further reduced.
  • an insulating material preferably made of rubber or plastic, to further reduce the heat transfer from the compressed refrigerant to the valve plate.
  • the component comprising the two channels can for example be injection molded from plastic, whereby the heat transfer from the pressure channel into the interior of the compressor housing, from the interior of the compressor housing in the suction channel and in the suction or pressure contact edge in the valve plate again reduced can be.
  • the characterizing features of claim 8 provide that the pressure bore occluding pressure valve is arranged in the pressure channel forming member. This allows the valve plate easier, ie. be manufactured in fewer steps, since the provision of a fastening for the pressure valve in the valve plate is no longer required. At the same time, the realization of this feature allows a pre-assembling of pressure channel and pressure valve or together with the features of claim 7, a pre-assembling of pressure channel and pressure valve, including suction channel.
  • the clamping element is latched according to the characterizing features of claim 14 with an end portion provided on the cylinder housing undercuts.
  • the cylinder housing is provided with a step according to the characterizing features of claim 16, in which the valve plate is at least partially recessed to allow a positioning thereof, as a positioning, as is known by screwing in conventional cylinder heads of refrigerant compressors, due to the clamping is no longer possible, with a preferred embodiment according to the characterizing features of claim 17 provides that the piston facing away from the surface of the valve plate is flush with the cylinder housing.
  • the fastening of the components forming the suction or pressure channel takes place on the valve plate by means of further clamping legs arranged on the clamping element.
  • a separate further clamping element is provided, which clamps the suction or pressure channel forming components to the valve plate, said separate clamping element can be latched to the clamping element.
  • valve plate by means of separate fasteners, such as screws, is attached to the cylinder housing, but the pressure or suction channel forming components are clamped to the valve plate, thus a combination of Clamping and screwing.
  • claims 23 and 24 describe a preferred embodiment of the tight connection of the suction or pressure channel forming components to the valve plate in order to prevent leakage of the refrigerant from the channels into the interior of the compressor housing guaranteed can.
  • the formation of the sealing bead in conjunction with the sealing projections requires a much lower required pressing force between printing or
  • Fig.1 shows an axonometric view of a cylinder head according to the invention, wherein portions of the cylinder housing 1, the valve plate 2, and the suction muffler 3 together with the intake opening 3a are visible.
  • the basic structure of the subject hermetically sealed refrigerant compressor is known per se.
  • the piston-cylinder-motor unit consists essentially of a cylinder housing 1 and the therein a stroke advancing piston 4, and a crankshaft bearing 5 in a crankcase 5a, which is arranged perpendicular to the cylinder axis 6.
  • the crankshaft bearing 5 receives a crankshaft (not shown) and protrudes into a central bore of the rotor Electric motor (also not drawn).
  • a suction muffler 3 is arranged to reduce the noise during the intake of the refrigerant to a minimum.
  • Fig.1 and Fig.2 show a variant of a cylinder head according to the invention in a fully assembled state, ie. with a clamping element 7, whereas Figure 3 the same cylinder head according to the invention, however, without clamping element 7 shows.
  • Both components 8,9 are independent of each other and in particular also independent of the valve plate 2, with which, however, along a contact edge, namely a pressure contact edge 13 or a suction contact edge 17, which will be discussed in more detail later, are tightly connected.
  • limit the components 8.9 which can also be referred to with pressure channel 8 and suction channel 9, each a completely self-sufficient channel, they completely encase until it hits the valve plate.
  • the component 8 forming the pressure channel has a section 8a leading directly to the pressure bore 10 away from the valve plate 2 and a further section 8b adjoining this section 8a, which is essentially radially outward relative to the cylinder bore, preferably at a distance Z to the valve plate 2 is preferably parallel thereto (see also Figure 10 and 11 ).
  • the distance Z between the component 8 and the valve plate 2 causes optimum isolation of the valve plate 2 from the pressure channel, so that a heat transfer from the compressed, hot refrigerant in the pressure channel 8 on the valve plate 2 and on the suction channel 9 is strongly prevented.
  • the component 8 forms a pressure chamber, which is arranged in the leading away from the valve plate 2 section 8a of the pressure channel 8 and a defined minimum volume does not fall below depending on the cooling capacity.
  • This pressure chamber which is also referred to in the following with 8a, serves to avoid possible pressure surges when expelling the refrigerant from the cylinder.
  • the pressure channel 8 is then transferred to the further section 8b, which leads the refrigerant out of the compressor housing.
  • clamping element 7 is substantially Y-shaped and arched away from the piston 4 and is used exclusively for clamping the components 8,9 against the valve plate 2.
  • the clamping element 7 itself is secured by screws 11 to the valve plate 2. The screws 11 are also used to attach the valve plate 2 to the cylinder housing. 1
  • Figure 4 shows the previously described cylinder head according to the invention with partially cut clamping element 7 and partially cut valve plate 2.
  • the clamping element 7 presses with its one clamping portion 7a on a portion of the pressure channel forming member 8, whereby this against the valve plate 2 or more precisely via the pressure contact edge 13th pressed against the valve plate.
  • Figure 5 shows a view of the cylinder head according to the invention in the direction of the crankshaft axis.
  • the structure of the cylinder head according to the invention can be seen very well, in particular the clamping element 7, the valve plate 2 and the cylinder housing 1, all of which are connected to each other via the screws 11.
  • Figure 6 shows a section along the line AA Fig.2 ,
  • the component 8 according to the invention can be seen very well, which forms the pressure channel and this completely encased.
  • the clamping element 7, which clamps the component 8 with its end portion 8c in the form of the pressure contact edge 13 against the valve plate 2 with its portion 7a.
  • the distance Z can be seen very well, which is formed between the further portion 8b of the component 8 and the valve plate 2 and a heat transfer from the compressed, hot refrigerant-containing pressure channel 8 on the valve plate 2 and thus further into the cylinder interior 12th or in the suction channel 9, which is not visible in this sectional view, prevented.
  • the compressed refrigerant in the first section 8a of the pressure channel 8 is led away from the valve plate and then led away at a distance Z in the radial direction with respect to the cylinder bore from the cylinder housing 1 without the compressed refrigerant having further contact with the valve plate 2 ,
  • Figure 7 shows how Figure 5 a view of the cylinder head according to the invention in the direction of the crankshaft axis, but without clamping element 7, so that the pressure channel forming member 8 is very well visible, as well as the distance Z between the component 8 and the valve plate. 2
  • Fig.8 and Fig. 8a Both show that end portion of the portion 8a of the pressure channel forming member 8, which is sealed to the valve plate 2, which is not apparent in these figures, via the pressure contact edge 13. This, adjacent to the valve plate 2 and thus Connected end portion forms according to the invention a pressure chamber 8a to prevent pressure increases during expulsion of the refrigerant from the cylinder.
  • the section 8a is further provided with receiving devices 19 in the form of pins, in which an end portion of a pressure valve 15 is suspended.
  • the pressure valve 15 is formed in a conventional manner as a leaf spring element.
  • That end section which can be suspended in the receiving devices serves as a fixed attachment section, whereas the free end section 15a opposite this end section alternately releases or closes the pressure bore 10 located immediately behind it in the valve plate 2 as a function of the compression cycle.
  • the component 8 according to the invention is further provided with an opening limitation 26 in the form of a stop, as is apparent from Figure 8a is apparent. This opening limitation serves to limit the opening travel of the pressure valve 15.
  • the inventive arrangement of the pressure valve 15 in the component 8 allows the prefabrication of these two parts along a separate production line.
  • Component 8 together with pressure valve 15 and opening limit 26 can then be easily and quickly connected by means of clamping element 7 with the valve plate 2.
  • the conventional way of attaching the pressure valve 15 to the valve plate 2, for example by riveting is then no longer necessary, resulting in a significant simplification and, above all, acceleration of the manufacturing process.
  • Figure 9 shows an alternative embodiment of a cylinder head according to the invention, in which in addition to the pressure and suction passage forming components 8,9 and the valve plate 2 is fixed via a clamping element 7 with the clamping portions 7a and 7b on the cylinder housing 1.
  • Figure 10 shows a sectional view of the alternative embodiment Figure 9 , wherein the heat transfer between the pressure channel 8 and valve plate 2 and between the suction channel 9 and valve plate 2 inhibiting distance Z is very clearly visible.
  • the clamping element 7 consists in this case of a clamping portion 7b, which surrounds the valve plate 2 in its edge region over the entire circumference and snaps into this embodiment at an undercut 27 on the cylinder housing 1, as in the detail view in Figure 11 is clearly visible.
  • Clearly visible in Figure 11 is also the dead space seal 14, which is arranged between the valve plate 2 and the cylinder housing 1, and the suction valve 32nd
  • the clamping element 7 has an additional clamping portion 7a, which is formed substantially U-shaped and the components 8,9 clamped against the valve plate 2.
  • Figure 12 shows a section along the plane A from Figure 9 , In this view, the integrality of the clamping element 7 with the clamping portions 7a and 7b can be seen very clearly.
  • the transition of the pressure channel forming member 8 is shown in the pressure bore 10.
  • the component 8 according to the invention is tightly connected to the valve plate 2 along the pressure contact edge 13. Within the enclosed by the pressure contact edge 13 surface is the pressure bore 10, and the movable part of the pressure valve 15. The area enclosed by the pressure contact edge 13 surface is also the only portion of the valve plate 2, which comes into contact with the compressed refrigerant from the cylinder.
  • suction contact edge 17 along which the suction channel 9 tightly the valve plate 2 is connected.
  • suction bore 16 Within the area enclosed by the suction contact edge 17 is the suction bore 16.
  • the area enclosed by the suction contact edge 17 is at the same time the only portion of the valve plate 2 which comes into contact with the refrigerant drawn into the cylinder.
  • the cylinder housing 1 has a shoulder 27, in which the valve plate 2 is at least partially, but preferably completely sunk, whereby at the same time a positioning of the valve plate 2 is achieved.
  • FIG. 13 and FIG. 14 both show a further alternative embodiment of a cylinder head according to the invention.
  • the clamping element 7 is executed divided in the region of its clamping portion 7a, so that each component 8.9 has a clamping element 7 assigned to it.
  • Fig.15 and Fig.16 Both show an additional embodiment variant of a cylinder head according to the invention with an alternatively formed clamping element 7.
  • the clamping portion 7b of the clamping element 7 surrounds the valve plate 2 in its edge region not over the entire circumference but is executed interrupted, the interruptions form openings in this clamping section, through which the components 8,9 away from the cylinder head and out to the cylinder head, so that actually several clamping portions 7b are present.
  • the individual clamping portions 7b snap in the same manner as already described in the above-mentioned embodiments at an undercut 27 on the cylinder housing 1 a.
  • the clamping portion 7a is formed cross-shaped in this embodiment, each one arm of this cross merges into a clamping portion 7b.
  • the area where the individual arms of the cross meet is included made cylindrical and causes the clamping of the components 8.9.
  • Fig.17 and Fig.18 show another alternative embodiment of a cylinder head according to the invention, in which the clamping element 7, both the components 8,9 and the valve plate 2 clamped against the cylinder housing 1.
  • the cylinder housing 1 is formed laterally raised, wherein the raised portion 1a has an undercut, in which the clamping element 7 with its clamping portion 7b can be latched.
  • the valve plate 2, which terminates the cylinder housing 1 at the end and is axially surmounted by its portions 1a, is clamped in this case by the clamping portions 7b, which are latched to the undercut of the portion 1a, against the cylinder housing 1.
  • the clamping portion 7a which in turn integrally forms with the clamping portion 7b, the clamping element 7, clamps the components 8,9 against the valve plate 2.
  • the raised portion 1a is provided with openings 18 through which the components 8,9 away from the cylinder head or to Cylinder head are led out.
  • Fig.19 and 20 each show a sectional view of cylinder heads according to the invention, in which on the one hand an O-ring seal 20 and on the other hand, a paper seal 21 for sealing the connection of the suction channel 9 and also the pressure channel 8 with the valve plate 2 are used.
  • This type of seal is already known from the prior art, but there is the sealing of the connection of the valve plate with the cylinder cover, which is no longer necessary in a cylinder head according to the invention.
  • Figure 21 shows an alternative embodiment of a possible sealing of the connection of the pressure channel 8 and the suction channel 9 with the valve plate 2 based on an additional, further embodiment of an inventive Cylinder head.
  • the valve plate 2 to be provided with a sealing bead 23, in which a the contour of the sealing bead 23 on the valve plate 2 substantially corresponding to the DruckANDante 13 of the pressure channel forming member 8 and at the Saug.kante 17 of the Suction passage forming component 9 9 arranged sealing extension 22 (see also 8 and 8a ) intervenes.
  • a reverse embodiment is conceivable, ie. at the pressure contact edge 13 of the pressure channel forming member 8 and at the Saugumblekante 17 of the suction channel forming member 9 (see also 8 and 8a ), a sealing bead 23 is provided, in which a corresponding to the contour of the sealing bead 23, arranged on the valve plate 2 sealing projection 22 engages.
  • the sealing extension 22 In order to ensure a sealing of the connection, the sealing extension 22 must either have a larger volume than the sealing bead 23 or the shape of the sealing extension 22 is different from that of the sealing bead 23.
  • the applied during assembly of the cylinder head pressing forces, in particular the clamping forces of the clamping element 7 then cause the flow of the sealing extension 22 in the sealing bead 23 or of parts of the sealing extension 22 due to the high local surface pressure.
  • sealing bead 23 in conjunction with the sealing projections 22 requires for the same tightness a much lower required pressing force between the pressure or suction passage 8.9 and valve plate 2 than is the case between cylinder cover and valve plate 2 in known cylinder heads.
  • surface pressure required is the same for both systems, the sealing surfaces are quite different, namely a long wide seal in the case of the paper seal and a short narrow one Sealing surface in the case of the sealing bead 23 - sealing extension 22 system.
  • the sealing system works independently of the material pairings used. So conventional material pairings are possible, such as metal (valve plate 2) - metal (components 8,9) or metal (valve plate 2) - flowable plastic (components 8,9) or plastic (valve plate 2) - flowable plastic (components 8 , 9).
  • the surface pressure required for the present application can be given as 5 to 20 N / mm 2 .
  • a particularly preferred geometric shape of the sealing bead 23 is the V-shape or U-shape according to FIGS Fig.24 to 31 , those of the sealing extension 23, the pin shape, wherein the free end of the sealing extension is preferably flattened or rounded.
  • Figure 24 shows a simple embodiment of the sealing system with V-shaped sealing bead 23 and pin-shaped sealing extension 22nd
  • Figure 25 shows a sealing bead 23 formed by two projecting from the valve plate 2 ribs, which cooperates with a pin-shaped sealing extension 22.
  • the peg-shaped sealing extension 22 is flattened at its free end.
  • two peg-shaped sealing projections 22 are provided on the pressure channel 8, which limit a V-shaped sealing bead 23, in which engages a arranged on the valve plate 2 pin-shaped sealing extension 22.
  • sealing beads 23 are arranged on the valve plate 2, in which the two arranged on the pressure channel 8 sealing projections 22 engage, so that a kind of toothing between the pressure channel or suction channel forming components 8,9 and the valve plate 2 comes.
  • the cone-shaped sealing projections 22 are provided at their free end region with a chamfer.
  • Fig.27 to 31 show developments of the sealing system just described, wherein the peg-shaped sealing projections 22 are executed rounded at its free end.
  • the sealing system according to the invention can be used both in the cylinder heads described in this application according to the invention as well as in cylinder heads according to the prior art, ie using cylinder covers. In the latter case, the cylinder cover the sealing extension 22 and the sealing bead 23 and the valve plate 2, the corresponding counterpart.
  • FIGS. 32 to 35 show an additional alternative embodiment of a cylinder head according to the invention with the components 8.9.
  • the valve plate 2 is, with the exception of the suction or pressure bore 16.10 coated with a plastic jacket 25 which faces away from the cylinder housing 1 and a cylinder housing facing portion.
  • Those components forming the pressure or suction channel 8, 9 are integrated into the plastic layer 25, ie. are also made of plastic.
  • the production takes place in this case in several steps.
  • valve plate 2 with plastic 25 overmolded (insert technology), wherein on the side facing away from the cylinder housing 1 side of the valve plate 2 already pins 28, which serve for positional positioning of the pressure valve 15 (according to the receiving devices 19), be sprayed with.
  • valve plate 2 The attachment of the valve plate 2 on the cylinder housing 1 by means of clamping element 7, as already in the previous embodiments.
  • Fig.36 and 37th show a variant of a cylinder head, in which in addition to the clamping element 7, a further clamping element 29 is provided. This is according to the invention attached to the clamping element 7 and locked with this.
  • a pressure valve 15 forming, plate-shaped element 30, preferably made of metal is provided, which is clamped by the clamping element 7 to the valve plate 2.
  • the components 8,9 are made in this case as a one-piece plastic part.
  • the components 8, 9 are adhesively bonded to the valve plate 2, the pressure valve 15 in this case being arranged in the component 8, as already described above.
  • Fig.39 shows the orientation of the pressure valve 15, as a leaf spring, relative to the valve plate 2, wherein the components 8.9 have been omitted to illustrate the readability of the drawing.

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Claims (24)

  1. Compresseur pour agent frigorifique hermétiquement enfermé, avec un boîtier de compresseur étanche à l'intérieur duquel travaille un ensemble cylindre-piston comprimant un agent frigorifique et dont le boîtier du cylindre (1) est fermé au moyen d'une plaque porte-soupape (2) comportant un trou de compression (10) et un trou d'aspiration (16), un canal d'aspiration ainsi qu'un canal de compression étant prévus par l'intermédiaire desquels un agent frigorifique est aspiré par une soupape d'aspiration (32) dans le trou d'aspiration (16) et comprimé du trou de compression (10) dans le canal de compression par une soupape de compression (15), le canal d'aspiration étant formé par une pièce (9) en forme de canal qui relie le trou d'aspiration (16) à un amortisseur du bruit d'aspiration (3) préférentiellement prévu, caractérisé en ce que le canal de compression est formé par une pièce (8) indépendante qui enveloppe complètement le canal de compression et qui est reliée de façon étanche à la plaque porte-soupape (2) le long d'un bord de contact par pression (13) formé par un tronçon d'extrémité de la pièce (8), le trou de compression (10) et la partie mobile de la soupape de compression (15) étant disposés à l'intérieur de l'aire entourée par le bord de contact par pression (13).
  2. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 1, caractérisé en ce que le rapport entre l'aire de la section transversale du trou de compression (10) et l'aire entourée par le bord de contact par pression (13) est égale à plus d'1/12.
  3. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 1 ou 2, caractérisé en ce que l'aire emprisonnée par le bord de contact par pression est supérieure à l'aire des parties mobiles de la soupape de compression de moins de 50 %.
  4. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la pièce (8) formant le canal de compression comporte un tronçon (8a) qui est immédiatement adjacent au trou de compression (10) et qui s'éloigne de la plaque porte-soupape (2) et qu'elle comporte un autre tronçon (8b) qui est situé dans le prolongement de ce tronçon (8a) et qui, en référence au trou du cylindre, s'étend radialement vers l'extérieur, de préférence à distance de la plaque porte-soupape (2), de préférence parallèlement à celle-ci.
  5. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le tronçon (8a) s'éloignant de la plaque porte-soupape (2) et/ou l'autre tronçon (8b) du canal de compression (8) est/sont réalisés en matière plastique.
  6. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 5, caractérisé en ce qu'un matériau isolant, de préférence réalisé en caoutchouc ou en matière plastique, est disposé entre l'autre tronçon (8b) et la plaque porte-soupape (2).
  7. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la pièce (8) formant le canal de compression et celle (9) formant le canal d'aspiration sont chacune réalisées d'un seul tenant, ou forment de préférence une même pièce monobloc, les deux pièces (8, 9) formant une même pièce monobloc se touchant le long d'une cloison, de préférence cependant au moins le long d'entretoises.
  8. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la soupape de compression (15) fermant le trou de compression (10) est fixée dans la pièce (8) formant le canal de compression.
  9. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'une chambre de mise en pression (8a) dont le volume n'est pas inférieur à un volume minimum défini au préalable est prévue dans la pièce (8) formant le canal de compression.
  10. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 9, caractérisé en ce que la chambre de compression (8a) est disposée directement dans le prolongement du trou de compression (10) dans la pièce (8) formant le canal de compression.
  11. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'est prévu un élément de serrage (7) qui serre la plaque porte-soupape (2), du moins le long d'un tronçon de son pourtour, de préférence cependant tout le long du pourtour, sur le boîtier du cylindre (1).
  12. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 11, caractérisé en ce que l'élément de serrage (18) comporte une section de préférence en J.
  13. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 11 ou 12, caractérisé en ce que l'élément de serrage (7) est réalisé sous forme de couronne.
  14. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 13, caractérisé en ce qu'une ou plusieurs contre-dépouilles (27) sont prévues sur le boîtier du cylindre (1), ces contre-dépouilles étant aptes à s'encliqueter dans un tronçon d'extrémité de l'élément de serrage (7).
  15. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 14, caractérisé en ce que l'autre tronçon d'extrémité de l'élément de serrage (7) forme un premier tronçon de serrage (7b) qui serre la plaque porte-soupape (2) contre le boîtier du cylindre (1).
  16. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 15, caractérisé en ce que le boîtier du cylindre comporte un épaulement (31) dans lequel la plaque porte-soupape (2) est noyée du moins en partie.
  17. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 16, caractérisé en ce que la surface de la plaque porte-soupape (2) détournée du piston (4) affleure le boîtier du cylindre (1).
  18. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 17, caractérisé en ce que l'élément de serrage (7) comporte au moins un autre tronçon de serrage (7a) qui serre des pièces (8, 9) formant le canal de compression ou le canal d'aspiration contre la plaque porte-soupape (2) ou dans le trou d'aspiration (16) et/ou dans le trou de compression (10).
  19. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 11 à 17, caractérisé en ce qu'un autre élément de serrage (29) est prévu qui est apte à s'encliqueter sur l'élément de serrage (7) et qui serre des pièces (8, 9) formant le canal de compression ou le canal d'aspiration contre la plaque porte-soupape (2) ou dans le trou d'aspiration (16) et/ou dans le trou de compression (10).
  20. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 10, caractérisé en ce que des éléments de fixation (11) distincts sont prévus ou un élément de fixation distinct (7b) est prévu pour fixer la plaque porte-soupape (2) sur le boîtier du cylindre (1).
  21. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 20, caractérisé en ce que les éléments de fixation distincts sont des vis (11).
  22. Compresseur pour agent frigorifique hermétiquement enfermé selon la revendication 20 ou 21, caractérisé en ce qu'est prévu un élément de serrage qui est apte à s'encliqueter sur le boîtier du cylindre (3) et qui serre des pièces (8, 9) formant le canal de compression ou le canal d'aspiration contre la plaque porte-soupape (2) ou dans le trou d'aspiration (16) et/ou dans le trou de compression (10).
  23. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 22, caractérisé en ce que des nervures d'étanchéité (23) de préférence en V sont prévues dans la plaque porte-soupape (2) et que la face d'extrémité tournée vers la plaque porte-soupape (2) de la pièce (8, 9) formant le canal d'aspiration ou le canal de compression est équipée, le long du bord de contact par aspiration ou pression (13, 17) de celle-ci, de prolongements d'étanchéité (22) correspondant sensiblement aux nervures d'étanchéité (23) en V, les prolongements d'étanchéité (22) ayant une forme géométrique différente de celle des nervures d'étanchéité (23) et/ou ayant un volume différent.
  24. Compresseur pour agent frigorifique hermétiquement enfermé selon l'une quelconque des revendications 1 à 22, caractérisé en ce que des prolongements d'étanchéité (22) sont prévus dans la plaque porte-soupape (2) et que la face d'extrémité tournée vers la plaque porte-soupape (2) de la pièce (8, 9) formant le canal d'aspiration ou le canal de compression est équipée, le long du bord de contact par aspiration ou pression (13, 17) de celle-ci, de prolongements d'étanchéité (22) correspondant sensiblement aux nervures d'étanchéité (23), les prolongements d'étanchéité (22) ayant une forme géométrique différente de celle des nervures d'étanchéité (23) et/ou ayant un volume différent.
EP06725446A 2005-03-31 2006-03-30 Compresseur de fluide frigorigene Active EP1864021B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT06725446T ATE414225T1 (de) 2005-03-31 2006-03-30 Kältemittelkompressor

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0019505U AT8401U1 (de) 2005-03-31 2005-03-31 Kältemittelverdichter
AT0022305U AT8477U1 (de) 2005-03-31 2005-04-12 Kältemittelverdichter
PCT/EP2006/061198 WO2006103278A1 (fr) 2005-03-31 2006-03-30 Compresseur de fluide frigorigene

Publications (2)

Publication Number Publication Date
EP1864021A1 EP1864021A1 (fr) 2007-12-12
EP1864021B1 true EP1864021B1 (fr) 2008-11-12

Family

ID=36578775

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06725446A Active EP1864021B1 (fr) 2005-03-31 2006-03-30 Compresseur de fluide frigorigene

Country Status (5)

Country Link
US (1) US20090136365A1 (fr)
EP (1) EP1864021B1 (fr)
AT (2) AT8477U1 (fr)
DE (1) DE502006002068D1 (fr)
WO (1) WO2006103278A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT10393U1 (de) * 2007-12-27 2009-02-15 Acc Austria Gmbh Kältemittelverdichter
BR102012025279B1 (pt) * 2012-10-03 2021-09-21 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda Compressor de refrigeração tendo um sistema de descarga de gás
CN112443475A (zh) * 2019-08-27 2021-03-05 安徽美芝制冷设备有限公司 曲轴箱、压缩机和制冷设备

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4352377A (en) * 1981-07-27 1982-10-05 White Consolidated Industries, Inc. Compressor discharge valve
DE3332259A1 (de) * 1983-09-07 1985-03-28 Danfoss A/S, Nordborg Kaeltemaschinenverdichter
US4723896A (en) * 1987-04-30 1988-02-09 White Consolidated Industries, Inc. Compressor discharge valve assembly
JP2845561B2 (ja) * 1990-04-06 1999-01-13 松下冷機株式会社 密閉型電動圧縮機
US5288212A (en) * 1990-12-12 1994-02-22 Goldstar Co., Ltd. Cylinder head of hermetic reciprocating compressor
BR9102288A (pt) * 1991-05-28 1993-01-05 Brasileira S A Embraco Empresa Conjunto abafador de succao para compressor hermetico
CN1247897C (zh) * 1995-04-20 2006-03-29 Lg电子株式会社 密闭式压缩机
DE19915918C2 (de) * 1999-04-09 2001-05-31 Danfoss Compressors Gmbh Kältemittelkompressor und Verfahren zu seiner Montage
BR0105694B1 (pt) * 2001-10-29 2009-05-05 filtro de sucção para compressor hermético alternativo.

Also Published As

Publication number Publication date
WO2006103278A1 (fr) 2006-10-05
ATE414225T1 (de) 2008-11-15
WO2006103278A9 (fr) 2008-02-07
DE502006002068D1 (de) 2008-12-24
EP1864021A1 (fr) 2007-12-12
AT8477U1 (de) 2006-08-15
US20090136365A1 (en) 2009-05-28

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