WO2006103278A9 - Compresseur de fluide frigorigene - Google Patents

Compresseur de fluide frigorigene

Info

Publication number
WO2006103278A9
WO2006103278A9 PCT/EP2006/061198 EP2006061198W WO2006103278A9 WO 2006103278 A9 WO2006103278 A9 WO 2006103278A9 EP 2006061198 W EP2006061198 W EP 2006061198W WO 2006103278 A9 WO2006103278 A9 WO 2006103278A9
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve plate
suction
refrigerant compressor
compressor according
Prior art date
Application number
PCT/EP2006/061198
Other languages
German (de)
English (en)
Other versions
WO2006103278A1 (fr
Inventor
Guenther Zippl
Alfred Freiberger
Mathias Ponhold
Original Assignee
Acc Austria Gmbh
Guenther Zippl
Alfred Freiberger
Mathias Ponhold
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AT0019505U external-priority patent/AT8401U1/de
Application filed by Acc Austria Gmbh, Guenther Zippl, Alfred Freiberger, Mathias Ponhold filed Critical Acc Austria Gmbh
Priority to US11/887,286 priority Critical patent/US20090136365A1/en
Priority to DE502006002068T priority patent/DE502006002068D1/de
Priority to CN2006800108560A priority patent/CN101151462B/zh
Priority to EP06725446A priority patent/EP1864021B1/fr
Publication of WO2006103278A1 publication Critical patent/WO2006103278A1/fr
Publication of WO2006103278A9 publication Critical patent/WO2006103278A9/fr

Links

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 boiling refrigerant is vaporized by absorbing energy from the space to be cooled in the evaporator and finally superheated and pumped by the refrigerant compressor to a higher energy level, where there is heat over a
  • Capacitor releases and via a choke, in the one
  • 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 the
  • Volumes is constructed, and has the aforementioned inlet opening and an outlet opening, which is close to the
  • 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 just before entering the compressor housing and the first volume of the suction muffler, a heating by more than 2O 0 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 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.
  • Pressure contact edge enclosed area 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 compressed refrigerant can be quickly transported away from the valve plate and its heat output to the valve plate can be prevented or reduced.
  • 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 Suction channel and valve plate as this is the case between cylinder cover and valve plate in known cylinder heads.
  • Fig.l an axonometric view of a piston-cylinder unit together with inventive cylinder head
  • FIG. 2 shows a front view of a cylinder head according to the invention
  • FIG. 3 shows an axonometric view of a piston-cylinder unit together with cylinder head according to the invention without a clamping element
  • FIG. 4 shows an axonometric sectional detail view of a cylinder head according to the invention
  • FIG. 5 shows a view in the direction of the crankshaft axis on a cylinder head including the cylinder housing and the crankcase
  • FIG. 7 shows a view in the direction of the crankshaft axis on a cylinder head including the cylinder housing and crankcase without clamping element
  • FIG. 8a shows an axonometric view of the component forming the pressure channel in section 9 shows an alternative embodiment of a cylinder head according to the invention
  • FIG. 11 is a detail view of Fig.10
  • FIG. 13 shows a further alternative embodiment of a cylinder head according to the invention
  • Fig.14 is a sectional view taken along plane B of Fig.13
  • Fig.16 is a sectional view taken along plane C of Fig.15
  • FIG.17 another alternative embodiment of a cylinder head according to the invention
  • Fig.18 is a sectional view taken along plane D of Fig.17
  • 19 is a sectional view of a cylinder head according to the invention with O-ring seal
  • FIG. 22 shows an additional, further embodiment variant of a cylinder head according to the invention according to FIG. 21
  • Fig.23 is a sectional view taken along plane F of Fig.22
  • Figs. 24-31 are sectional views of an alternative sealing system 32 shows an additional, alternative embodiment of a cylinder head according to the invention
  • FIG. 33 shows a sectional view along plane G from FIG. 32
  • Fig.35 is a sectional view taken along plane H of Fig.34
  • FIG. 37 shows an axonometric view of the cylinder housing together with clamping element according to FIG.
  • Fig.l shows an axonometric view of a cylinder head according to the invention, wherein sections of the
  • Cylinder housing 1, the valve plate 2, and the suction muffler 3, together with intake 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.l and Fig.2 show an embodiment of a cylinder head according to the invention in a fully assembled state, ie. with a clamping element 7, whereas Figure 3 shows the same cylinder head according to the invention, however, without clamping element 7.
  • 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 Fig.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 in the leading away from the valve plate 2 section 8a of the pressure channel 8 is arranged 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.
  • the components 8, 9 are pressed against the valve plate 2 by a clamping element 7.
  • Embodiment according to Fig.l clamping member 7 shown 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
  • FIG. 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 the pressure contact edge 13 is pressed against the valve plate.
  • FIG. 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.
  • FIG. 6 shows a section along the line AA of Figure 2.
  • the component 8 according to the invention can be seen very well, which forms the pressure channel and this completely encased.
  • 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 ,
  • FIG. 7 shows, like FIG. 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 component 8 forming the pressure channel is very clearly visible, as well as the distance Z between the component 8 and the valve plate 2.
  • 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 limit 26 in the form of a stop, as can be seen from Fig.8a. 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.
  • FIG. 9 shows an alternative embodiment variant of a cylinder head according to the invention, in which, in addition to the components 8, 9 forming the pressure and suction channel, the valve plate 2 is fastened to the cylinder housing 1 via a clamping element 7 with the clamping sections 7a and 7b.
  • the disclosed in Figure 9 embodiment of a cylinder head according to the invention is entirely without screws. In other words, the entire cylinder head is merely clamped.
  • FIG. 10 shows a sectional view of the alternative embodiment variant from FIG. 9, wherein the distance Z which inhibits the heat transfer between pressure channel 8 and valve plate 2 or between suction channel 9 and valve plate 2 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 in this embodiment at an undercut 27 on the cylinder housing 1, as is clearly visible in the detail view in Figure 11 , 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.
  • FIG. 12 shows a section along the plane A from FIG. 9. In this view is very clear the one - piece of the
  • 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.
  • 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.
  • FIGS. 13 and 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 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 the edge region not over the entire circumference but is executed interrupted, in which case Openings form openings in this clamping section, through which the components 8,9 are guided away from the cylinder head or towards the cylinder head, so that actually several clamping sections 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 Ia has an undercut, in which the clamping element 7 with its clamping portion 7b can be latched.
  • the valve plate 2, which closes the cylinder housing 1 at the end and is axially surmounted by its portions Ia, is clamped in this case by the clamping portions 7b, which are latched to the undercut of the portion Ia, against the cylinder housing 1.
  • the clamped 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 Ia is provided with openings 18 through which the components 8,9 away from the cylinder head or to Cylinder head are led out.
  • 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 of 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.
  • valve plate 2 shows an alternative embodiment variant of a possible sealing of the connection of pressure channel 8 or suction channel 9 with the valve plate 2 on the basis of an additional, further embodiment variant of a device according to the invention 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 Druckrobeante 13 of the pressure channel forming member 8 and at the Saug.kante 17 of the Suction passage forming component 9 arranged sealing extension 22 (see also Fig.8 and 8a) engages.
  • Suction channel forming member 9 (see also Fig.8 and 8a) is a sealing bead 23 is provided, in which a the outline of the
  • 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 the same tightness a much lower required pressing force between pressure ⁇ or suction port 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.
  • 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 .
  • Gasket 23 is the V-shape or U-shape according to Figures 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.
  • FIG. 24 shows a simple embodiment of the sealing system with V-shaped sealing bead 23 and pin-shaped sealing extension 22.
  • FIG. 25 shows a sealing bead 23 formed by two ribs projecting from the valve plate 2, which cooperates with a peg-shaped sealing extension 22.
  • the peg-shaped sealing extension 22 is flattened at its free end.
  • Fig.26 two pin-shaped sealing projections 22 are provided on the pressure channel 8, which limit a V-shaped sealing bead 23, in which a arranged on the valve plate 2 pin-shaped sealing projection 22 engages.
  • 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
  • the cone-shaped sealing projections 22 are provided at their free end region with a chamfer.
  • FIGS. 27 to 31 show further developments of the sealing system just described, with the peg-shaped sealing projections 22 also being rounded at their free end region.
  • 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. 22 and 23 show further views of the additional, further embodiment variant of the cylinder head according to the invention from FIG.
  • 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 8, 9 forming the pressure or suction channel 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 37 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.
  • Pressure valve 15 in this case, as already described above, is arranged in the component 8.
  • Fig.39 shows the orientation of the pressure valve 15, as
  • clamping element 7a Clamping section 7b. clamping section

Landscapes

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

Abstract

L'invention concerne un compresseur de fluide frigorigène encapsulé de façon hermétique, comportant un boîtier de compresseur hermétique contenant une unité piston/cylindre comprimant un fluide frigorigène, dont le cylindre (1) est fermé par l'intermédiaire d'un disque de soupape (2) présentant un alésage de pression (10) et un alésage d'aspiration (16). Un canal d'aspiration et un canal de pression servent respectivement à aspirer le fluide frigorigène par l'intermédiaire d'une soupape d'aspiration dans l'alésage d'aspiration (16), et à comprimer ledit fluide sortant de l'alésage de pression, dans le canal de pression, par l'intermédiaire d'une soupape de pression (15), le canal d'aspiration contenant de préférence un amortisseur de bruits d'aspiration (3). L'invention vise à mettre en oeuvre un tel compresseur de fluide frigorigène permettant de réduire considérablement la température d'aspiration et la température d'expulsion. A cet effet, le canal de pression est constitué par un composant (8) entourant entièrement le canal de pression, connecté de façon étanche au disque de soupape (2) le long d'une arête de contact de pression (13) formée par une section terminale du composant (8), l'alésage de pression (10) et la partie mobile de la soupape de pression (15) étant disposés dans la surface entourée par l'arête de contact de pression (13).
PCT/EP2006/061198 2005-03-31 2006-03-30 Compresseur de fluide frigorigene WO2006103278A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US11/887,286 US20090136365A1 (en) 2005-03-31 2006-03-30 Refrigerant Compressor
DE502006002068T DE502006002068D1 (de) 2005-03-31 2006-03-30 Kältemittelkompressor
CN2006800108560A CN101151462B (zh) 2005-03-31 2006-03-30 致冷剂压缩机
EP06725446A EP1864021B1 (fr) 2005-03-31 2006-03-30 Compresseur de fluide frigorigene

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT0019505U AT8401U1 (de) 2005-03-31 2005-03-31 Kältemittelverdichter
ATGM195/2005 2005-03-31
ATGM223/2005 2005-04-12
AT0022305U AT8477U1 (de) 2005-03-31 2005-04-12 Kältemittelverdichter

Publications (2)

Publication Number Publication Date
WO2006103278A1 WO2006103278A1 (fr) 2006-10-05
WO2006103278A9 true WO2006103278A9 (fr) 2008-02-07

Family

ID=36578775

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/061198 WO2006103278A1 (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
AT8477U1 (de) 2006-08-15
ATE414225T1 (de) 2008-11-15
WO2006103278A1 (fr) 2006-10-05
EP1864021A1 (fr) 2007-12-12
EP1864021B1 (fr) 2008-11-12
US20090136365A1 (en) 2009-05-28
DE502006002068D1 (de) 2008-12-24

Similar Documents

Publication Publication Date Title
EP2193058B1 (fr) Groupe moteur-pompe
DE3507831C2 (fr)
DE3813539C2 (de) Hermetischer Kühl-Kompressor
EP0734494B1 (fr) Pompe a piston pour l'acheminement d'un fluide hydraulique
EP0925446B1 (fr) Pompe a piston radial pour alimentation haute pression en carburant
DE10115506A1 (de) Kolbenkompressor variabler Verdrängung
DE10157702A1 (de) Ventilbefestigungsstruktur eines Kolbenverdichters
EP1888918B1 (fr) Compresseur de fluide frigorigene
EP1869323B1 (fr) Compresseur frigorifique
DE4218631C2 (de) Kühlungskompressor mit einem profilierten Kolben
WO2006013143A1 (fr) Pompe a piston a rendement ameliore
DE102007026119A1 (de) Differenzialdruckventil
EP3482076B1 (fr) Couvercle de tête de cylindre pour un compresseur de réfrigérant
DE19603109C2 (de) Kolben-Kältemittelkompressor mit verbesserter Dichtfunktion
EP1864021B1 (fr) Compresseur de fluide frigorigene
DE10312355B4 (de) Kolbenverdichter
AT12789U1 (de) Druckschalldämpfer für einen hermetisch gekapselten kältemittelverdichter
DE112009004280B4 (de) Ventilplattenvorrichtung für einen Kompressor
DE10244565B4 (de) Zylinderkopfanordnung für einen Kolbenverdichter
AT8985U1 (de) Kältemittelverdichter
DE112006002191T5 (de) Hubkolbenmaschine
DE112009003662T5 (de) Kühlschrank-Kompressor in Spiralbauart
EP2238349B1 (fr) Compresseur à piston comportant une plaque de soupape présentant une soupape à lamelle
DE102004003137A1 (de) Kompressionsvorrichtung für gasförmige Medien
EP1375919B1 (fr) Compresseur, en particulier pour un système à resort pneumatique pour un véhicule

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2006725446

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 11887286

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 200680010856.0

Country of ref document: CN

NENP Non-entry into the national phase

Ref country code: DE

WWW Wipo information: withdrawn in national office

Country of ref document: DE

NENP Non-entry into the national phase

Ref country code: RU

WWW Wipo information: withdrawn in national office

Country of ref document: RU

WWP Wipo information: published in national office

Ref document number: 2006725446

Country of ref document: EP