WO1996003582A1 - Compresseur a gaz - Google Patents

Compresseur a gaz Download PDF

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Publication number
WO1996003582A1
WO1996003582A1 PCT/EP1995/002763 EP9502763W WO9603582A1 WO 1996003582 A1 WO1996003582 A1 WO 1996003582A1 EP 9502763 W EP9502763 W EP 9502763W WO 9603582 A1 WO9603582 A1 WO 9603582A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve plate
gas compressor
compressor according
valve
cylinder
Prior art date
Application number
PCT/EP1995/002763
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
Karl-Fritz Kammhoff
Original Assignee
Bitzer Kühlmaschinenbau Gmbh & Co. Kg
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 DE4440903A external-priority patent/DE4440903A1/de
Application filed by Bitzer Kühlmaschinenbau Gmbh & Co. Kg filed Critical Bitzer Kühlmaschinenbau Gmbh & Co. Kg
Publication of WO1996003582A1 publication Critical patent/WO1996003582A1/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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/02—Elasticity

Definitions

  • the invention relates to a gas compressor, in particular a refrigerant compressor, with a compressor housing, with a piston which can be moved in an oscillating manner in a cylinder of the compressor housing, with a valve plate closing the cylinder, with a compression chamber delimited by the piston, the cylinder and the valve plate and with a lamellar valve as an outlet valve, the lamella of which has a front tongue area for closing an outlet opening passing through the valve plate on a side facing away from the compression chamber.
  • Such gas compressors are known from the prior art.
  • the problem with these gas compressors is that, on the one hand, the largest possible cross-sections of the outlet openings are to be aimed at, but on the other hand this creates large harmful spaces in the area of the outlet openings, which lead to poor delivery rates when there are a large number of gases, in particular certain refrigerants, if high compression ratios required are.
  • the invention is therefore based on the object of improving a gas compressor of the generic type in such a way that as little damage space as possible is available despite the large outlet openings.
  • This object is achieved according to the invention in a gas compressor of the type described at the outset in that the valve plate has a depression which extends from an upper side thereof which faces away from the compression chamber in the direction of an underside thereof which faces the compression chamber, in that the outlet opening in the region of a Bottom of the recess and that the tongue area of the lamella is also in the recess.
  • the solution according to the invention has the great advantage that the provision of the depression makes it possible to arrange the outlet opening in the bottom of the depression, which has a smaller thickness than the valve plate outside the depression.
  • outlet opening is located in the area of the floor that has the smallest thickness, since this also allows the smallest damage area to be reached.
  • the bottom in the region of the outlet opening has a thickness equal to or less than approximately half the thickness of the valve plate outside the depression. It is particularly advantageous, in particular in order to arrange the lamella of the lamella valve in a functionally advantageous manner, if the bottom of the depression has a flat area of the bottom surface which overlaps the lamella, since this creates a defined and advantageous bearing surface for the lamella so that it is able to seal the outlet opening with the required quality.
  • the flat region is preferably arranged such that it surrounds the outlet opening.
  • the flat area has at least one shape of the surface extension corresponding to the shape of the lamella and the entire lamella overlaps the flat area so that the entire lamella rests on a flat surface and thus with the known lamellae of known lamella valves in optimally a seal can be achieved.
  • the flat region it is particularly expedient for the flat region to run essentially parallel to the underside of the valve plate, so that the lamella also extends approximately parallel to the underside of the valve plate and as a whole is embedded in the recess, preferably recessed therein.
  • the flat region extends at an acute angle to the underside of the valve plate 24, so that the recess extends into the valve plate from the top side to different degrees.
  • a particularly favorable solution provides that the flat region extends from the top of the valve plate in the direction of the underside, that is, it slopes down as an oblique surface from the top toward the bottom.
  • This solution has the advantage that the bottom of the depression each has only a small area of the smallest thickness and then the thickness of the bottom always increases and the overall weakening of the valve plate is therefore as small as possible.
  • it is preferably always provided that the outlet opening lies in the region of the bottom with the smallest thickness.
  • the retaining screw can be fastened more easily, since it can be arranged in an area of greater thickness of the floor and thus ensures that it is securely received in the floor.
  • valve plate receiving the depression can be produced in a wide variety of ways.
  • a simple embodiment provides that the depression is worked into the valve plate by mechanical, preferably machining, and that the bottom of the depression is an integral part of the one-piece valve plate.
  • An alternative expedient solution provides that the valve plate is constructed in two parts from a lower plate and a support element, the lower plate having the outlet opening.
  • This solution has the advantage that it is not necessary to incorporate the recess into the valve plate and the lower plate, which is continuous and has only the outlet opening, can be made of a different material than the support element. In this case, for example, provision is made to produce the lower plate from a high-strength steel strip.
  • the lower plate has a smaller thickness, while the support element additionally provides the required stiffening for the lower plate. This creates the possibility of achieving great stability in the area of the bottom of the depression.
  • a particularly advantageous embodiment provides that the lower plate forms the bottom of the depression, while the support element has an opening which forms a lateral boundary of the depression. This creates in a particularly simple manner the possibility of providing the floor with a floor surface that is as flat as possible, in this case the top of the lower plate in the region of the opening in the support element.
  • the bottom plate and the preferably plate-shaped support element are advantageously sealed off from one another, for example by means of a coating, an inserted seal or other means.
  • the lower plate is connected to the supporting element in a cylinder-covering inner region. Such a connection can be made by gluing, welding, soldering or other types of connection.
  • a particularly simple solution provides that the lower plate is connected to the support element by means of a screw connection of the lamellar valve; this is an alternative or in addition to gluing or welding the two to each other an advantageous solution, since the retaining screw connection which is required anyway for the lamellar valve can simultaneously be used to connect these parts.
  • the lower plate and the support plate are connected to the compressor housing via a common screw connection, preferably clamped together between a cylinder head cover and a cylinder head flange of the compressor housing.
  • a sealing surface surrounding the outlet opening is formed by a valve sealing edge which is raised in relation to the bottom surface.
  • the provision of a raised valve sealing edge creates the advantage of making the seal in the tongue area less sensitive to dirt and, moreover, of being able to work the valve sealing edge more precisely in order to obtain the best possible support and thus sealing of the tongue area at the valve sealing edge.
  • the outlet opening is formed by an insert inserted into an outlet opening with the sealing surface surrounding the outlet opening. Such an insert makes it possible to machine the sealing surface carried by the insert before inserting it and thus to produce it as precisely as possible, so that precise machining of the sealing surface carried by the insert in the recess itself is no longer necessary.
  • the fastening seat is also formed by an insert, since the fastening seat can thus be processed more easily before the insert is inserted into the valve plate.
  • the intended inserts are preferably screwed in, pressed in, soldered in or welded in.
  • inlet valves are also lamellar valves.
  • the lamella valve is arranged in the depression provided according to the invention.
  • valve plate is overlapped by a cylinder head cover and is connected to the cylinder head cover in its inner region spanning the cylinder, and that the valve plate is connected to the cylinder head cover forms a composite component which has sufficient rigidity against bending of the valve plate against overpressure in the cylinder and underpressure in the cylinder relative to the cylinder head, ie towards and away from the piston.
  • the cylinder head cover has a support which is guided to and connected to the valve plate, this support, according to the invention, supporting the valve plate in the inner region spanning the cylinder.
  • the support is preferably screwed to the valve plate and thereby forms a unit which both stabilizes the valve plate against bending away from the piston and also in the direction of the piston.
  • valve plate is connected to the cylinder head cover at several points in the inner region in order to achieve an even better stiffening of the valve plate.
  • a web also runs from one edge of the cylinder head cover to the respective support, which web rests with a foot region on the upper side of the valve plate and additionally supports this against a connection from the piston and also also in turn also Support stiffened relative to the edge of the cylinder head cover and thus also stabilizes the support itself.
  • a particularly advantageous solution provides that the support is part of a partition between a pressure chamber and a suction chamber, which are located between the valve plate and the cylinder head cover.
  • the support could be of any design. It is particularly expedient if the support is formed by a support foot which leads from the cylinder head cover to the valve plate, the support foot preferably being integrally formed on the cylinder head cover.
  • the support leg can in turn either be part of the partition, as already stated, or it is advantageously provided that the support leg sits to the side of the partition.
  • an advantageous variant provides a screw penetrating the valve plate, which passes through the support and in which a gas-tight seal is provided between a head of the screw and the contact surface.
  • a gas-tight seal can be achieved, for example, by gluing in the head of the screw, for example in the case of a screw lying with its head in the valve plate, in that its head is glued into the valve plate. But it is also possible to solder or weld the head.
  • a blind hole is preferably provided, in which a screw connecting the valve plate and the support of the cylinder head cover is inserted.
  • a blind hole in which the screw engages is provided in the valve plate, or a blind hole is provided in the support in which a screw penetrating the valve plate is screwed.
  • the cylinder head cover is in turn supported on the compressor housing outside the inner region, preferably placed on it in a conventional manner and in particular is screwed to it.
  • valve plate could, for example, be made from all possible materials, such as ceramic, steel, etc. It is particularly advantageous if the valve plate is made of a material with a high modulus of elasticity.
  • Figure 1 is a partial longitudinal section through a gas compressor according to the invention.
  • FIG. 2 shows a cross section along line II-II in FIG. 1;
  • Fig. 3 is a partially shown section along line III-III in Fig. 1;
  • FIG. 4 shows an enlarged detail of a region of a valve plate carrying a multi-plate valve according to the invention
  • FIG. 5 shows a representation similar to FIG. 4 of a first variant of the first exemplary embodiment
  • 6 shows a representation similar to FIG. 4 of a second variant of the first exemplary embodiment
  • FIG. 7 shows a plan view similar to FIG. 3 of a section of the valve plate in the second variant of the first exemplary embodiment with a catcher not shown;
  • FIG. 8 shows a representation similar to FIG. 4 of a third variant of the first exemplary embodiment
  • FIG. 9 shows a representation similar to FIG. 7 of the third variant of the first exemplary embodiment
  • FIG. 10 shows a representation similar to FIG. 4 of a second exemplary embodiment
  • FIG. 11 shows a representation similar to FIG. 10 of a first variant of the second exemplary embodiment
  • FIG. 12 shows a cross section through a third exemplary embodiment along line XII-XII in FIG. 13;
  • FIG. 13 shows a representation similar to FIG. 3 of the third exemplary embodiment. ;
  • FIG. 14 shows a representation similar to FIG. 12 of a first variant of the third exemplary embodiment
  • FIG. 15 shows a representation similar to FIG. 12 of a second variant of the third exemplary embodiment
  • FIG. 16 shows a representation similar to FIG. 12 of a third variant of the third exemplary embodiment.
  • a first exemplary embodiment of a gas compressor according to the invention, in particular a refrigerant compressor, shown in FIGS. 1, 2, 3 and 4 comprises a cylinder housing designated as a whole as 10, in which at least one piston 12, preferably two pistons, can be moved in an oscillating manner, wherein each piston 12 is driven by a connecting rod 14 from a crankshaft 16 which is mounted in a crankshaft housing 18 and can be driven by a drive wheel 20.
  • the piston 12 runs in a cylinder 22 which is closed off from the crankshaft housing 18 by a valve plate 24.
  • the valve plate 24 in turn overlaps a cylinder head cover 26 which is connected by screws 28 to a cylinder head flange 30 surrounding the cylinder 22, the valve plate 24 being clamped between the cylinder head cover and the cylinder head flange 30 and the screw 28 passing through a bore 32 in the valve plate.
  • the cylinder head cover 26 furthermore forms a suction chamber 36 and a pressure chamber 38 over an inner region 34 of the valve plate 24 which overlaps the cylinder 22, as shown in FIG. 2, both of which are separated from one another by a partition 40, the partition 40 is led down from a cover plate 42 of the cylinder head cover to the valve plate 24 and rests with its foot surface 44 on the valve plate 24 in a sealing manner.
  • the pressure chamber 38 leads via an opening 46 (Fig.
  • valve plate 24 in the valve plate 24 to a pressure channel 48, and from there to a pressure port 50 of the refrigerant compressor, while a suction port 52 of the refrigerant compressor is connected to a suction channel 54, which in turn via an opening 56 in the valve plate 24 opens into the suction space 36 above the same.
  • inlet openings 58 When the piston 12 is sucked in, gas, in particular refrigerant, is sucked in from the suction chamber 36 via inlet openings 58 into a compression chamber 60 delimited between the piston 12, the cylinder 22 and the valve plate 24, the inlet openings 58 being provided with conventional lamella valves as inlet valves are that are not shown in the drawing.
  • the gas is compressed in the compression space 60 and leaves it through at least one outlet opening 62 in the valve plate 24, the outlet opening 62 being provided with a lamella valve designated as a whole as 64 as the outlet valve.
  • the volume of the compression space is essentially determined by the distance between the valve plate and the piston, which is required to prevent the piston 12 from striking the valve plate 24 due to the mechanical tolerances. This means that the valve plate 24 is also designed so that the distance between the piston 12 and the valve plate 24 is minimal.
  • the compressed gas in particular refrigerant, flows through the outlet opening 62 into the pressure chamber 38, from there into the pressure channel 48 and to the pressure connection 50. As shown in FIG.
  • the lamella valve 64 comprises a lamella 66 which has a front tongue area 68 with which the outlet opening 62 can be covered, the tongue area sealingly abutting an upper edge 70 of the outlet opening 62. Furthermore, the lamella 66 comprises a clamping area 72, which has a clamping opening 74 which passes through a retaining screw 76 passing through the valve plate 24.
  • a catcher On the clamping area 72 there is a catcher, designated as a whole by 78, with a clamping end 80, which likewise has an opening 82 through which the retaining screw 76 passes.
  • a holding sleeve 84 acts on this clamping end 80 and is acted upon by a holding nut 86 screwed onto the holding screw 76.
  • the catcher 78 extends with a catching arm 90 over the lamella 66 in the direction of the tongue area 68 and also overlaps it, the catching arm 90 having a catching surface 92 facing the lamella 66, which starts from the clamping end 80 continuously bulges away from the lamella 66 which is in the rest position.
  • the lamella 66 lies on a bottom surface 94 of a recess 96, the latter extending from a top 98 of the valve plate 24 in the direction of a bottom 100 and having recess walls 102 which extend from the top 98 to extend to the bottom surface 94.
  • the lamella 66 lying flat on the bottom surface 94 in the rest position is pressed in the clamping area 72 by the clamping 80 of the catcher 78 against the bottom surface 94, the clamping end 80 being held by the retaining screw 76 passing through a bottom 104, the retaining nut 86 via the retaining sleeve 84 is applied.
  • the bottom surface 94 is supported by the bottom 104 of the recess 96, which is an integral part of the valve plate 24, but has a thickness which is more than half less than the thickness of the valve plate 24 outside the recess 96.
  • This floor 104 is penetrated by the outlet opening 62, the outlet opening being delimited by opening walls 106 due to the small thickness of the floor 104, which have a small extension in an outlet direction 108 and thus result in a minimal damage space 110 of the outlet opening 62.
  • the lamella valve designated as a whole as 64 now works in such a way that, when the pressure in the compression chamber 60 rises, the lamella 66 initially engages with the rear area facing the clamping area 72 on the catching surface 92 and bends more and more as the pressure increases, so that at maximum open lamella valve, the front tongue area 68 rests on the catching surface 92. It is thereby achieved that the spring force of the lamella 66 counteracting the opening of the lamellar valve 64 increases with increasing opening of the lamella, and thus the lamella, depending on the pressure building up in the compression chamber 60, applies more or less strongly to the catching surface 92 and opens the outlet opening 110 to a greater or lesser extent.
  • the recess 96 is preferably machined into the valve plate 24 by milling, a precise machining of the bottom surface 94 being necessary in order to obtain a flat contact surface for the lamella 66.
  • the depression 96 is machined into the valve plate 24 in the same way.
  • the outlet opening 62 is formed by a bush 112 inserted into an opening 110 in the bottom 104, which in turn has a valve sealing edge 114 on which the lamella 66 rests in the rest position.
  • a fastening insert 118 penetrated by the retaining screw 76 is inserted, which forms a fastening seat 120 in the form of a flat surface for the clamping area 72 of the lamella 66.
  • the fastening seat 120 and the valve sealing edge 114 preferably act in a plane 122 which runs parallel to the bottom surface 94, the bushing 112 and the fastening insert 118 being provided with a shoulder in order to relatively position the valve sealing edge 114 and the fastening seat 120 level 122 must be precisely defined.
  • the clamping area 72 is pressed against the fastening seat 120, specifically by the clamping end 80 of the catcher 78, on which the holding nut 86 acts via the holding sleeve 84.
  • the advantage of the first variant is that both the valve sealing edge 114 and the fastening seat 120 against which the lamella 66 rests can be precisely pre-machined due to the insertable parts 112 and 118, so that a precise machining of the bottom surface 94 can be omitted.
  • valve sealing edge 114 and the fastening seat 120 are raised in relation to the bottom surface 94, so that the first variant 64 of the lamella valve is less susceptible to the impurities deposited on the bottom surface 94.
  • the first variant of the valve arrangement is of the same design as the basic variant, so that full reference is made to the explanations for this.
  • the bottom 104 of the recess 96 is formed by a lower plate 130, which is part of the valve plate 24 'and is preferably made of unbreakable steel, in particular one break-proof steel strip.
  • the valve plate 24 ' also comprises a support element 132 resting on the lower plate 130, which is connected to the lower plate 130 and contributes to the stiffening thereof.
  • the support element 132 and the lower plate 130 are preferably glued or welded or soldered to one another over a large area, the support element 132 having an opening 134 whose walls form the recess walls 102, so that the depression 96 as a whole is formed by the walls 102 of the opening 134 which extend to an upper side of the lower plate 130, which at the same time forms the bottom surface 94 in the region of the depression 96.
  • the second variant of the valve arrangement with the lamellar valve 64 is designed in the same way as the basic form around the first variant, so that the same reference numerals are used for the same parts and reference is made to the embodiment of the previous variants.
  • valve plate 24 ′ is likewise formed from the lower plate 130 and the support element 132.
  • a projection 136 is formed on the support element 132, which overlaps the clamping end 80 of the catcher 78 and has a bore 138 which is penetrated by the retaining screw 76.
  • the clamping end 80 of the catcher 78 and the clamping area 72 of the lamella 66 lie in an undercut 138 between the projection 136 and the lower plate 130, the undercut 138 being dimensioned in such a way that it exactly accommodates the clamping end 80 and the clamping area 72 and thus the retaining screw 86 acts on the projection 136 and clamps the clamping end 80 and the clamping area 72 between the projection 136 and the lower plate 130.
  • the third variant shown in FIGS. 8 and 9, is designed in the same way as the second variant, shown in FIGS. 6 and 7, so that reference is made in full to the explanations in this regard.
  • the recess 196 is also incorporated into the valve plate 24, but in such a way that a bottom surface 194 of the recess 196 is at an acute angle a to the underside 100 of the valve plate 24 extends, starting from the top 98.
  • the outlet opening 62 is placed in such a way that it opens into a deepest part of the recess 196, the lamella 66 preferably being oriented such that its clamping area 72 near the top 98 in a higher area of the floor surface 94 opens and the tongue area 68 rests on the lowest area of the floor surface 94, in which the outlet opening 62 opens, in the rest position.
  • the catcher 78 is aligned in the same way as in the first exemplary embodiment, so that full reference can be made to the first exemplary embodiment with regard to the function of this second exemplary embodiment of the lamellar valve 164.
  • the base surface 194 is to be machined precisely in the same way as in the basic variant of the first exemplary embodiment, in order to provide the most precise possible flat contact surface for the lamella 66.
  • a central axis 76a of the retaining screw 76 preferably extends perpendicular to the bottom surface 194, so that the retaining screw 76 is inserted obliquely into the valve plate 24, but it is also possible to align the central axis 76a perpendicularly to the underside 100.
  • the second embodiment of the solution according to the invention has the advantage that the bottom 204 of the recess 196 can only be made as thin as possible in a small area essentially surrounding the outlet opening 62, so that the overall weakening of the stability of the valve plate 24 is less than in the case of first exemplary embodiment and nevertheless the smallest possible damage space 110 of the outlet opening 62 can be reached.
  • the recess 196 is machined in such a way that a sealing edge 114 raised against the base surface 194 remains and a raised fastening seat 120 for the clamping area 72 of the lamella 66.
  • This has the advantage that the most precise possible machining of the sealing surface 114 raised against the base surface 94 and the raised fastening seat 120 can be carried out more easily.
  • This solution is particularly expedient in the case of a cast valve plate in which the sealing edge 114 and the fastening seat 120 are pre-cast in a raised manner with respect to the bottom surface 194 and then only machining of the sealing edge 114 and the fastening seat 120 is necessary.
  • the fastening seat 120 and the sealing surface 114 are both in turn in a common plane 122 ', which preferably runs parallel to the bottom surface 194 and thus also at an angle a to the underside 100 of the valve plate 24.
  • valve plate 24 is made of a much thinner material than in the first two embodiments.
  • the material that is used for the valve plate 24 ′′ is preferably a material with a high modulus of elasticity.
  • valve plate 24 Due to the small thickness of the valve plate 24 ", there is a greater deflection of the valve plate 24" in the direction of the piston 12 during the suction stroke and away from the piston 12 during the compression stroke, which as such is not acceptable.
  • valve plate 24 ′′ forms an integral component with the cylinder head cover 26 ′, the valve plate 24 ′′ and the cylinder head cover 26 ′ not only being firmly connected to one another around the cylinder 22 as a result are that the valve plate 24 "is clamped between the cylinder head cover 26 'and the cylinder head flange by the screws 28.
  • the cylinder head cover 26 ' is provided with support feet 210 which extend from the cover plate 42' in the direction of the upper side 98 and which can be screwed to the valve plate 24 "by means of screws 212.
  • the support feet 210 lie freely in the inner region 34 which overlaps the cylinder 22 of the valve plate 24 "and lie with a foot surface 214 on the top 98, so that the inner region 34 of the valve plate 24" due to the support feet 210 and the screws 212 passing through them both against movement in the direction of the piston 12 and away from it in addition is supported via the cover plate 42 '.
  • a cylinder-side end 218 of the screws 212 is screwed into a blind hole 220 in the valve plate 24 ′′.
  • two support feet 210 are provided which support the inner region 34 and which are additionally integrated in the partition 40 and form part of the same.
  • stiffening webs 222 are provided in addition to the support feet, which, starting from an edge 224 of the cylinder head cover 26 ′ screwed to the cylinder head flange 30 by means of the screws 28, extend to the partition 40 and extend with foot surfaces 226 on the top 98 of the valve plate 24 "and thus support the valve plate 24" against movement away from the piston 12, but at the same time form an additional stiffening for the support feet 210 and thus an additional stiffening for the valve plate 24 "and the cylinder head cover 26 'formed integral component.
  • the same lamellar valves 64 are used as in the first two exemplary embodiments, although in the simplest case the provision of a depression 94 or 194 can be omitted, since the valve plate 24 ′′ and the cylinder head cover 26 form due to the formation of a uniform composite component 'The thickness of the valve plate 24 "is reduced and thus the damage space in the outlet opening 62 is reduced.
  • the seal between the cylinder head cover 26 'and the valve plate 24 "takes place in all, also in the exemplary embodiments described above, by means of a cylinder head gasket 230, which has one eye for each of the screws 212.
  • the cylinder head cover 26' sits with both the edge 224 as well as with the foot surfaces 216 on the cylinder head gasket 230.
  • the cylinder head gasket 230 also extends between the foot surfaces 226 and the valve plate 24".
  • a through hole 232 is provided in the valve plate, through which the screw 212 extends essentially completely with its cylinder-side end 234, but only to the extent that that it does not protrude beyond the underside 100 of the valve plate 24 ". In this case, however, it is necessary to achieve gas-tightness in the area of the bore 232 and the cylinder-side end 234, for example by gluing the thread.
  • a hole 241 with a countersink 242 for a countersunk screw 244 is provided, this countersunk screw 244 with its head 246 sits so deep in the countersink 242 that the head 246 does not protrude beyond the underside 100 of the valve plate 24 ".
  • the countersunk screw 244 preferably has a slot, or more appropriately an Allen key, which allows better torque transmission when tightening.
  • a shaft 248 passes through the support foot 210 and a nut 252 is screwed onto an end 250 of the screw 244 on the cylinder head, with which the cylinder head cover 26 'is acted upon.
  • the bore 240 is provided with the countersink 242 in the same way as in the second variant, and the screw 244 also has a countersunk head 246 which does not protrude beyond the underside 100 of the valve plate 24 ′′.
  • the screw 244 also has a countersunk head 246 which does not protrude beyond the underside 100 of the valve plate 24 ′′.
  • there is no bore penetrating the respective support feet 210 but a blind bore 254 in each of the support feet 210, into which the screw 244 can be screwed.
  • a seal in the area of the head 246 between the valve plate 24 ′′ and the screw is therefore not necessary, but the gas tightness to the cylinder space 216 is ensured by the blind bore 254 and the cylinder head gasket 230 which is present anyway.

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

Abstract

Compresseur à gaz comprenant un carter, un piston se déplaçant dans un cylindre du carter, une plaque de soupape (98) fermant le cylindre, un espace de compression limité par le piston, le cylindre et la plaque de soupape (98), une soupape à lamelle (66) servant de soupape d'échappement, disposée sur la plaque de soupape (98) et dont la lamelle (66) présente, sur un côté opposé à l'espace de compression, une zone avant en languette (68) pour la fermeture d'un orifice d'échappement (62) traversant la plaque de soupape. L'invention a pour but d'améliorer ce compresseur de manière à réduire le plus possible l'espace nuisible (110), en dépit de l'existence de grands orifices d'échappement. A cet effet, le compresseur selon l'invention est caractérisé en ce que la plaque de soupape (98) présente un évidement (96) s'étendant de la partie supérieure de la plaque de soupape opposée à l'espace de compression, en direction de la partie inférieure de cette plaque faisant face à cet espace de compression, en ce que l'orifice d'échappement (62) est situé dans une partie du fond (94) de l'évidement (96) et en ce que la zone en languette (68) de la lamelle (66) est située, de même, dans l'évidement (96).
PCT/EP1995/002763 1994-07-27 1995-07-14 Compresseur a gaz WO1996003582A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4426566 1994-07-27
DEP4426566.2 1994-07-27
DEP4440903.6 1994-11-17
DE4440903A DE4440903A1 (de) 1994-07-27 1994-11-17 Gasverdichter

Publications (1)

Publication Number Publication Date
WO1996003582A1 true WO1996003582A1 (fr) 1996-02-08

Family

ID=25938725

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/002763 WO1996003582A1 (fr) 1994-07-27 1995-07-14 Compresseur a gaz

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WO (1) WO1996003582A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT14139U1 (de) * 2013-10-17 2015-05-15 Secop Austria Gmbh Kältemittelverdichter
WO2016102053A1 (fr) * 2014-12-22 2016-06-30 Gea Bock Gmbh Compresseur

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1408638A (en) * 1920-06-03 1922-03-07 Ingersoll Rand Co Compressor
US2151746A (en) * 1936-07-14 1939-03-28 Westinghouse Electric & Mfg Co Compressor valve structure
FR1573460A (fr) * 1967-09-01 1969-07-04
DE2755735A1 (de) * 1977-02-22 1978-08-24 Motor N P Klappenventilanordnung fuer kolbenkompressoren
GB2037405A (en) * 1978-12-01 1980-07-09 Danfoss As A reciprocating-piston compressor cylinder
US4730550A (en) * 1985-08-08 1988-03-15 Thomas Industries, Inc. Piston cup and cylinder assembly
US4752190A (en) * 1986-06-18 1988-06-21 Tecumseh Products Company Compressor cylinder head
EP0582712A1 (fr) * 1992-03-03 1994-02-16 Matsushita Refrigeration Company Compresseur hermetique

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1408638A (en) * 1920-06-03 1922-03-07 Ingersoll Rand Co Compressor
US2151746A (en) * 1936-07-14 1939-03-28 Westinghouse Electric & Mfg Co Compressor valve structure
FR1573460A (fr) * 1967-09-01 1969-07-04
DE2755735A1 (de) * 1977-02-22 1978-08-24 Motor N P Klappenventilanordnung fuer kolbenkompressoren
GB2037405A (en) * 1978-12-01 1980-07-09 Danfoss As A reciprocating-piston compressor cylinder
US4730550A (en) * 1985-08-08 1988-03-15 Thomas Industries, Inc. Piston cup and cylinder assembly
US4752190A (en) * 1986-06-18 1988-06-21 Tecumseh Products Company Compressor cylinder head
EP0582712A1 (fr) * 1992-03-03 1994-02-16 Matsushita Refrigeration Company Compresseur hermetique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT14139U1 (de) * 2013-10-17 2015-05-15 Secop Austria Gmbh Kältemittelverdichter
WO2016102053A1 (fr) * 2014-12-22 2016-06-30 Gea Bock Gmbh Compresseur
CN107208617A (zh) * 2014-12-22 2017-09-26 基伊埃博客股份有限公司 压缩机
CN107208617B (zh) * 2014-12-22 2020-06-05 基伊埃博客股份有限公司 压缩机

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