EP1869323B1 - Compresseur frigorifique - Google Patents

Compresseur frigorifique Download PDF

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Publication number
EP1869323B1
EP1869323B1 EP06725444A EP06725444A EP1869323B1 EP 1869323 B1 EP1869323 B1 EP 1869323B1 EP 06725444 A EP06725444 A EP 06725444A EP 06725444 A EP06725444 A EP 06725444A EP 1869323 B1 EP1869323 B1 EP 1869323B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve plate
suction
refrigerant compressor
channel
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.)
Not-in-force
Application number
EP06725444A
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German (de)
English (en)
Other versions
EP1869323A1 (fr
Inventor
Walter Brabek
Günther ZIPPL
Alfred Freiberger
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
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 AT0022305U external-priority patent/AT8477U1/de
Priority claimed from AT0005906U external-priority patent/AT8985U1/de
Application filed by ACC Austria GmbH filed Critical ACC Austria GmbH
Publication of EP1869323A1 publication Critical patent/EP1869323A1/fr
Application granted granted Critical
Publication of EP1869323B1 publication Critical patent/EP1869323B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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 housing 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 in the suction hole and compressed via a pressure valve from the pressure bore into the pressure channel, wherein the suction channel is formed by a channel-shaped component which is sealed along a Saug.kante with the valve plate and the suction hole provided with a preferred Suction muffler connects, according to the preamble of claim 1 or 2.
  • 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.
  • 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, which also has the suction bore and the pressure bore.
  • 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 completely fills at least in the pressure channel forming portion due to the construction of the cylinder cover and thus with the part of this pressure channel forming valve plate in Touch comes.
  • 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 designs due to their cylinder cover construction of the initially mentioned objective, namely a reduction of the suction temperature and the Ausschiebetemperatur, run counter.
  • claims 1 or 2 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 can guaranteed.
  • the formation of the sealing bead in conjunction with the sealing projections requires a much lower required pressing force between pressure or suction port and valve plate than is the case between cylinder cover and valve plate in known cylinder heads.
  • the known embodiments described above also have the disadvantage that the refrigerant heats up too much 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 in the compressor housing.
  • an independent component is provided which forms the pressure channel and this completely sheathed. By directly connecting this component with the pressure bore, a complete thermal separation of the pressure channel from the valve plate takes place.
  • These components allow the direct, hot refrigerant to escape directly through the pressure hole in the Pressure channel, without having to flow along a portion 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, in this way, the heat transfer from the valve plate to the suction hole and thus into the suction channel can be reduced, whereby the intake temperature can be lowered.
  • 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 through Pressure contact edge enclosed area is more than 1/12.
  • the component forming the pressure channel has a directly leading to the pressure bore, leading away from the valve plate portion and a subsequent section to this section further, relative to the cylinder bore radially outwardly, 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 for example, can be produced by injection molding from plastic, whereby the heat transfer from the pressure channel into the interior of the compressor housing, from the interior of the compressor housing into the suction channel and in the region of the suction or pressure contact edge in the valve plate can be further reduced.
  • the characterizing features of claim 10 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 enables a pre-assembling of pressure channel and pressure valve or together with the features of claim 10, a pre-assembling of pressure channel and pressure valve, including suction channel.
  • the clamping element is latched according to the characterizing features of claim 16 with an end portion provided on the cylinder housing undercuts.
  • the cylinder housing may be further provided with a step in which the valve plate is at least partially recessed to allow positioning thereof, since positioning, as known by screwing in conventional cylinder heads of refrigerant compressors, due to the clamping is no longer possible , wherein a preferred embodiment provides that those facing away from the piston 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 on Cylinder housing is fixed, but the pressure or suction duct forming components are clamped to the valve plate, thus a combination of clamping and screwing.
  • Fig.1 shows an axonometric view of a cylinder head, wherein portions 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.1 and Fig.2 show an embodiment of a cylinder head in a fully assembled state, ie. with a clamping element 7, whereas Figure 3 However, the same cylinder head 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 and 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 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 13 at the valve plate is pressed.
  • Figure 5 shows a view of the cylinder head 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 three 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 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 Pressure chamber 8a to prevent pressure increases when pushing the refrigerant out of 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, 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 fig.11 is clearly visible.
  • Clearly visible in fig.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 is connected tightly to the valve plate 2.
  • Suction hole 16 Within the enclosed by the suction contact edge 17 surface is the Suction hole 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.
  • 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 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, the interruptions form openings in this clamping section in this case which the components are 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. That area in which the individual arms of the cross meet is cylindrical and causes the clamping of the components 8, 9.
  • Fig.17 and Fig.18 show another alternative embodiment of a cylinder head, 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.
  • the Fig.19 and 20 each show a sectional view of cylinder heads, 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 required in a cylinder head.
  • 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 a cylinder head according to the invention.
  • the valve plate 2 to be provided with a sealing bead 23, in which a the outline of the sealing bead 23 on the valve plate 2 in Substantially corresponding, arranged at the DruckCountante 13 of the pressure channel forming member 8 and at the Saug.kante 17 of the suction channel forming member 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.
  • required surface pressure is the same in both systems, however, the sealing surfaces differ substantially, namely a long wide seal in the case of the paper seal and a short narrow sealing surface in the case of the sealing bead 23 - sealing system 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 comes to a kind of teeth between the pressure channel or suction channel forming components 8,9 and the valve plate 2.
  • 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 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 of the valve plate 2 already pins 28, which serve for positional positioning of the pressure valve 15 (corresponding to the receiving devices 19), are 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 opening limit 26 for the pressure valve 15 is, as already in Figure 21 or 35 shown, integrated in the component 8.
  • 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (22)

  1. Compresseur d'agent réfrigérant blindé hermétiquement, avec un carter de compresseur hermétiquement étanche, à l'intérieur duquel travaille une unité cylindre-piston comprimant un agent réfrigérant, dont le carter de cylindre (1) est fermé au moyen d'un tiroir de soupape (2) comportant une prise de pression (10) et un alésage d'aspiration (16), et dans lequel sont prévus un canal d'aspiration ainsi qu'un canal de pression, par lesquels l'agent réfrigérant est aspiré dans l'alésage d'aspiration (16) par le biais d'une soupape d'aspiration (32) et comprimé dans le canal de pression, à partir de la prise de pression (10), par le biais d'une soupape de pression (15), le canal d'aspiration étant formé par une pièce en forme de canal (9), qui est étroitement reliée au tiroir de soupape (2) le long d'une arête de contact à aspiration (17) et relie l'alésage d'aspiration (16) à un silencieux d'aspiration (3) prévu de préférence, caractérisé en ce que des moulures d'étanchéité (23) ou des prolongements d'étanchéité (22), de préférence en forme de V, sont prévus dans le tiroir de soupape (2), et la surface frontale de la pièce (9) formant le canal d'aspiration qui est tournée vers le tiroir de soupape (2) est pourvue, le long de son arête de contact à aspiration (17), de prolongements d'étanchéité (22) ou de moulures d'étanchéité (23) coïncidant essentiellement avec les moulures d'étanchéité (23) ou prolongements d'étanchéité (22) de préférence en forme de V, les prolongements d'étanchéité (22) étant conçus différemment des moulures d'étanchéité (23) dans leur forme géométrique, et/ou présentant un volume différent.
  2. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 1, caractérisé en ce que le canal de pression est formé par une pièce indépendante (8) enrobant entièrement le canal de pression, qui est étroitement reliée au tiroir de soupape (2), le long d'une arête de contact à pression (13) formée par un tronçon terminal de la pièce (8).
  3. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 ou 2, caractérisé en ce que la prise de pression (10) et la pièce mobile de la soupape de pression (15) sont disposées à l'intérieur de la surface entourée par l'arête de contact à pression (13).
  4. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 3, caractérisé en ce que le rapport entre la surface de section transversale de la prise de pression (10) et la surface entourée par l'arête de contact à pression (13) est supérieur à 1/12.
  5. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 4, caractérisé en ce que la surface entourée par l'arête de contact à pression (13) dépasse de moins de 50% la surface des pièces mobiles de la soupape de pression (15).
  6. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 5, caractérisé en ce que la pièce (8) formant le canal de pression comporte un tronçon (8a) s'éloignant du tiroir de soupape (2), immédiatement consécutif à la prise de pression (10), ainsi qu'un autre tronçon (8b) consécutif à ce tronçon (8a), qui s'étend radialement vers l'extérieur par rapport à l'alésage de cylindre, de préférence parallèlement au tiroir de soupape (2), en respectant de préférence un espace par rapport à celui-ci.
  7. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 6, caractérisé en ce que le tronçon (8a) s'éloignant du tiroir de soupape (2) et/ou l'autre tronçon (8b) du canal de pression (8) est/sont fabriqué(s) en plastique.
  8. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 6 ou 7, caractérisé en ce qu'un matériau isolant, de préférence en caoutchouc ou en plastique, est disposé entre l'autre tronçon (8b) et le tiroir de soupape (2).
  9. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 8, caractérisé en ce que la pièce (8) formant le canal de pression et la pièce (9) formant le canal d'aspiration sont constituées chacune d'une seule pièce ou de préférence constituées solidairement d'une seule pièce, les deux pièces (8, 9) constituées solidairement d'une seule pièce se touchant le long d'une paroi intermédiaire, de préférence au moins le long de nervures de liaison.
  10. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 9, caractérisé en ce que la soupape de pression (15) fermant la prise de pression (10) est fixée dans la pièce (8) formant le canal de pression.
  11. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 10, caractérisé en ce qu'une chambre de pression (8a), dont le volume ne chute pas en-dessous d'un minimum prédéfini, est prévue dans la pièce (8) formant le canal de pression.
  12. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 11, caractérisé en ce que la chambre de pression (8a) est disposée immédiatement à la suite de la prise de pression (10) dans la pièce (8) formant le canal de pression.
  13. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 12, caractérisé en ce qu'il est prévu un élément de serrage (7), qui serre le tiroir de soupape (2), au moins le long d'un tronçon de son pourtour, mais de préférence le long de l'ensemble du pourtour, contre le carter de cylindre (1).
  14. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 13, caractérisé en ce que l'élément de serrage (18) comporte une section transversale essentiellement en forme de J.
  15. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 13 ou 14, caractérisé en ce que l'élément de serrage (7) est conçu en forme d'anneau circulaire.
  16. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 13 à 15, caractérisé en ce qu'une ou plusieurs contre-dépouilles (27) susceptibles d'être bloquées par enclenchement avec un tronçon terminal de l'élément de serrage (7) sont prévues sur le carter de cylindre (1).
  17. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 16, caractérisé en ce que l'autre tronçon terminal de l'élément de serrage (7) forme un premier tronçon de serrage (7b) serrant le tiroir de soupape (2) contre le carter de cylindre (1).
  18. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 13 à 17, caractérisé en ce que l'élément de serrage (7) comporte au moins un autre tronçon de serrage (7a) serrant les pièces (8, 9) formant le canal de pression ou le canal d'aspiration contre le tiroir de soupape (2) ou dans l'alésage d'aspiration (16) et/ou la prise de pression (10).
  19. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 13 à 18, caractérisé en ce qu'il est prévu un autre élément de serrage (29), susceptible d'être bloqué par enclenchement sur l'élément de serrage (7) et serrant les pièces (8, 9) formant le canal de pression ou le canal d'aspiration contre la tiroir de soupape (2) ou dans l'alésage d'aspiration (16) et/ou la prise de pression (10).
  20. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 1 à 12, caractérisé en ce que pour la fixation du tiroir de soupape (2) sur le carter de cylindre (1), des éléments de fixation (11) séparés sont prévus ou un élément de fixation (7b) séparé est prévu.
  21. Compresseur d'agent réfrigérant blindé hermétiquement selon la revendication 20, caractérisé en ce que les éléments de fixation séparés sont des vis (11).
  22. Compresseur d'agent réfrigérant blindé hermétiquement selon l'une des revendications 20 ou 21, caractérisé en ce qu'il est prévu un élément de serrage susceptible d'être bloqué par enclenchement sur le carter de cylindre (3) et serrant les pièces (8, 9) formant le canal de pression ou le canal d'aspiration contre le tiroir de soupape (2) ou dans l'alésage d'aspiration (16) et/ou la prise de pression (10).
EP06725444A 2005-04-12 2006-03-30 Compresseur frigorifique Not-in-force EP1869323B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0022305U AT8477U1 (de) 2005-03-31 2005-04-12 Kältemittelverdichter
AT0005906U AT8985U1 (de) 2005-03-31 2006-01-27 Kältemittelverdichter
PCT/EP2006/061196 WO2006108767A1 (fr) 2005-04-12 2006-03-30 Compresseur frigorifique

Publications (2)

Publication Number Publication Date
EP1869323A1 EP1869323A1 (fr) 2007-12-26
EP1869323B1 true EP1869323B1 (fr) 2009-11-11

Family

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Application Number Title Priority Date Filing Date
EP06725444A Not-in-force EP1869323B1 (fr) 2005-04-12 2006-03-30 Compresseur frigorifique

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US (1) US20090214367A1 (fr)
EP (1) EP1869323B1 (fr)
CN (1) CN101180465B (fr)
AT (1) ATE448405T1 (fr)
DE (1) DE502006005341D1 (fr)
WO (1) WO2006108767A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102297118B (zh) 2011-09-30 2013-10-09 黄石东贝电器股份有限公司 分离式隔热排气消音装置及采用其的制冷压缩机
BR112014017398A8 (pt) * 2012-01-20 2017-07-04 Kaercher Gmbh & Co Kg Alfred bomba de pistão para um aparelho de limpeza a alta pressão
KR101854933B1 (ko) 2013-04-24 2018-05-04 엘지전자 주식회사 압축기용 머플러 및 이를 구비한 압축기
WO2017191228A1 (fr) * 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
KR101951651B1 (ko) * 2017-05-18 2019-02-25 뉴모텍(주) 소형 공기 압축기
KR102345324B1 (ko) * 2020-08-28 2021-12-31 엘지전자 주식회사 리니어 압축기

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3332259A1 (de) * 1983-09-07 1985-03-28 Danfoss A/S, Nordborg Kaeltemaschinenverdichter
US5129793A (en) * 1990-10-24 1992-07-14 Copeland Corporation Suction muffler
US5288212A (en) * 1990-12-12 1994-02-22 Goldstar Co., Ltd. Cylinder head of hermetic reciprocating compressor
IT230572Y1 (it) * 1992-12-21 1999-06-07 Gold Star Co Dispositivo di soppressione del rumore per un compressore ermetico a stantuffo
DE19923733C2 (de) * 1999-05-22 2002-06-20 Danfoss Compressors Gmbh Sauggasleitung für einen Kältemittelverdichter
BR0105694B1 (pt) * 2001-10-29 2009-05-05 filtro de sucção para compressor hermético alternativo.
DE10341138A1 (de) * 2003-09-06 2005-04-07 Danfoss Compressors Gmbh Kältemittelverdichter

Also Published As

Publication number Publication date
WO2006108767A1 (fr) 2006-10-19
CN101180465B (zh) 2011-06-22
CN101180465A (zh) 2008-05-14
DE502006005341D1 (de) 2009-12-24
WO2006108767A9 (fr) 2007-09-13
EP1869323A1 (fr) 2007-12-26
US20090214367A1 (en) 2009-08-27
ATE448405T1 (de) 2009-11-15

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