EP1344005B1 - Compresseur - Google Patents

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Publication number
EP1344005B1
EP1344005B1 EP01986418A EP01986418A EP1344005B1 EP 1344005 B1 EP1344005 B1 EP 1344005B1 EP 01986418 A EP01986418 A EP 01986418A EP 01986418 A EP01986418 A EP 01986418A EP 1344005 B1 EP1344005 B1 EP 1344005B1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
compressor body
scroll
compressed
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.)
Expired - Lifetime
Application number
EP01986418A
Other languages
German (de)
English (en)
Other versions
EP1344005A2 (fr
Inventor
Karl-Fr. Kammhoff
Friedhelm Ahrens
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and 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
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP1344005A2 publication Critical patent/EP1344005A2/fr
Application granted granted Critical
Publication of EP1344005B1 publication Critical patent/EP1344005B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps

Definitions

  • the invention relates to a compressor for refrigerants, as defined in the preamble of claim 1.
  • a compressor for refrigerants, as defined in the preamble of claim 1.
  • Such a compressor is known, for example, from JP-A-02196182
  • the advantage of the solution according to the invention is the fact that with this the possibility exists to cool both compressor body in the same way and thus achieve in both Verêtrkörpem at least a similar temperature distribution, so that both compressor bodies thermally similar expand and thus by a high Manufacturing precision achievable low, if not insignificant leakage is not degraded by unequal temperature distributions and thus unequal thermal expansions, so that overall the efficiency of the scroll compressor is thereby reduced.
  • the second compressor body in the region of the second spiral rib opposite rear side radially outside its driver of the refrigerant to be compressed um Jardinbar ensures the same effective cooling, in particular cooling as close as possible ensures the areas of the compressor body, in which the largest heat input occurs.
  • the first compressor body in the region of a rear side facing away from the first spiral rib can be rinsed by the refrigerant to be compressed.
  • the back of the respective compressor body is formed directly by a respective bottom supporting the respective spiral rib, so that as efficient as possible cooling of the spiral ribs takes place with the respective floor are connected.
  • the back of the compressor body represents the back of a one-piece, the bottom and the spiral ribs having part, in particular in the back of this built-in or connected to this, for example patch, Has elements.
  • both compressor bodies can be cooled by the refrigerant to be compressed in the region of an outer peripheral side with respect to the central axis.
  • cooling takes place essentially over the entire rear side or only in partial regions of the rear side.
  • a particularly favorable solution provides that the first compressor body is um réellebar in the region of its lying outside a high-pressure connection back of the refrigerant to be compressed.
  • a particularly large area namely the surface lying radially outside of the high-pressure connection, is provided for cooling the first compressor body, the high-pressure connection in particular also contributing at least partially to the fixation of the first compressor body in the housing.
  • a structurally particularly advantageous solution provides that between the back of the first compressor body and a distance from this extending partition of the housing is a flushable by the refrigerant to be compressed back cooling chamber.
  • the rear cooling chamber can be formed in various ways.
  • a particularly favorable solution provides that the rear cooling chamber encloses a holding receptacle for the first compressor body, so that substantially the back of the compressor body with the exception of the areas in which the holding receptacle is effective, on the rear cooling chamber can be cooled.
  • the holding receptacle is formed so that the rear-side cooling chamber runs around in an annular manner around the holding receptacle for the second compressor body.
  • the high-pressure connection for the first compressor body is integrated into the holding receptacle and thus runs through this holding receptacle.
  • a particularly efficient cooling of the first compressor body is given, although the holding receptacle is cooled by the rear cooling chamber, so that insofar as in the holding receptacle by the high-pressure refrigerant exiting a heat input takes place, a direct cooling of the holding receptacle itself can be done dissipate this heat.
  • the cooling of the compressor body can be improved by the fact that the rear cooling chamber merges into a circumferential cooling chamber enclosing an outer periphery of the first compressor body.
  • the peripheral cooling chamber encloses not only the outer periphery of the first compressor body, but also the outer periphery of the second compressor body.
  • a mechanically particularly advantageous solution provides that the first compressor body is supported by outer with respect to the central axis radially outwardly of the spiral ribs supporting elements.
  • peripheral cooling chamber extends around the outer support elements and thus cools the first compressor body via the outer support elements, in particular when the outer support elements are integrally formed on the first compressor body.
  • a particularly advantageous embodiment provides that the temperature of the adjacent to the refrigerant to be compressed in the rear cooling chamber surface of the first compressor body within a ring area, which is between about 50% and about 80%, more preferably about 60% and about 70%, a maximum radius of the spiral ribs is a maximum of 8 °, more preferably a maximum of 5 °, higher than the temperature of the second compressor body reaching and to be compressed refrigerant.
  • a particularly advantageous embodiment provides that the refrigerant to be compressed first flows around the second compressor body and then the first compressor body.
  • the refrigerant to be compressed could originate from any section of a refrigeration system. It is particularly advantageous if the Käitung serving for Küblung the compressor body Keitungsstoff is to be sucked by the scroll compressor refrigerant.
  • a particularly favorable conception provides that the refrigerant to be sucked cools the compressor bodies substantially immediately before it enters a suction region of the scroll compressor.
  • a particularly favorable solution provides that the refrigerant to be sucked flows at least in part from a peripheral side of the scroll compressor between the bottom of the first compressor body and the bottom of the second compressor body in the intake of the scroll compressor.
  • the refrigerant to be compressed at least in the form of a partial flow flows through the rear cooling chamber forcibly guided, so that by the forced operation of the partial flow under all operating conditions sufficiently intensive flushing of the rear cooling chamber is ensured.
  • a particularly advantageous embodiment of the solution according to the invention that operates stably in all operating ranges provides that the entire refrigerant to be sucked flows through the rear-side cooling chamber and then through at least one opening of the bottom of the first compressor body into the suction region of the scroll compressor, so that through this Forced operation of the refrigerant to be compressed, a sufficiently intensive flushing of the rear cooling chamber is ensured even at low flow rates.
  • the compressor according to the invention is usually also the drive motor to cool. This could be cooled separately.
  • An advantageous embodiment, however, provides that the refrigerant to be compressed cools the drive motor and the scroll compressor.
  • the refrigerant to be compressed first cools the drive motor and then cools the scroll compressor.
  • a sufficiently large heating of the refrigerant to be compressed before entry into the scroll compressor can be achieved in a simple manner in order to avoid liquid refrigerant in the scroll compressor.
  • the refrigerant to be compressed cools the drive motor peripherally.
  • the compressor according to the invention can be particularly easily conceived when the refrigerant to be compressed first flows around the second compressor body in the region of the rear side of the bottom, especially radially outside of the support body and then enters the suction of the scroll compressor, since thereby the refrigerant flowing through the drive motor can be used directly after the drive motor for cooling the second compressor body.
  • the refrigerant to be compressed flows around radially outer support elements of the scroll compressor with respect to the center axis of the first spiral rib prior to entry into the suction region.
  • an advantageous embodiment provides that the spiral ribs of one compressor body at the bottom of the other compressor body facing end faces in grooves inserted end seals.
  • face seals could be immovable in the grooves. It is particularly favorable if the face seals in the grooves are movable in the direction of the bottom of the other compressor body.
  • a particularly advantageous embodiment provides that the front side seals are acted upon by the respective higher pressure in the scroll compressor in the direction of the bottom of the other compressor body movable.
  • the face seals can be made of different materials. For example, it is known from the prior art to carry out the end seals of metal blades. A particularly favorable solution provides that the front side seals are made of plastic.
  • a Teflon compound is used with about 5% to about 20% coal and other strength-promoting additives.
  • the high-pressure outlet is associated with a check valve, which prevents backflow of the high-pressure refrigerant in the scroll compressor.
  • the check valve is designed so that it has a lying in the first compressor body seal seat.
  • check valve is arranged in a high pressure chamber on a side opposite the first compressor body side of the partition wall.
  • a first embodiment of a scroll compressor according to the invention shown in Fig. 1, comprises a designated as a whole with 10 housing in which a designated as a whole by 12 electric drive motor and a designated as a whole with 14 scroll compressor.
  • the scroll compressor 14 comprises a first compressor body 16 and a second compressor body 18, wherein the first compressor body 16 has a same raised above a bottom 20, formed in the form of a Kreisvolvente spiral rib 22 and the second compressor body 18 a rising above a bottom 24 second, in the form of a Kreisvolvente trained spiral rib 26, wherein the spiral ribs 22, 26 engage each other and sealingly abut each of the bottom 24 and 20 of the other compressor body 18, 16, so that between the spiral ribs 22, 26 and the base surfaces 20th , 24 chambers 28 form, in which a compression of a refrigerant takes place, which flows over a spiral ribs 22, 26 radially outwardly surrounding suction portion 30 with initial pressure and after the compression in the chambers 28 via an outlet 32, provided in the first compressor body 16, compressed to high pressure emerges.
  • the first compressor body 16 is fixedly held in the compressor housing 10, while the second compressor body 18 is supported around a central axis 34 on an orbital path relative to the first compressor body 16 is movable, wherein the spiral ribs 22 and 26 theoretically abut each other along a line of contact and the contact line also rotates during the movement of the second compressor body 18 on the orbital path about the central axis 34.
  • the drive motor 12 for driving the second compressor body 18 comprises a stator 40 which is fixedly disposed in the housing 10, and a rotor 42 which sits on a drive shaft 44 which in turn is rotatable about the central axis 34 in the housing 10 is stored.
  • driver unit For coupling the rotational movement of the drive shaft 44 with the second compressor body 18 a designated as a whole with 50 driver unit is provided, which comprises a trained as a cam eccentric 52 which is opposite to the central axis 34, in the radial direction, arranged with an offset.
  • the driver 52 engages in a trained example as a sleeve cam receiver 54 which is disposed on the bottom 24 of the second compressor body 18, on a spiral rib 26 opposite side thereof and in the direction of the drive motor 12 points.
  • the cam receiver 54 formed as an inner cylindrical surface 60, the cylinder axis intersects the one hand, the theoretically circular orbital path, on the other hand parallel to the central axis 34, but is offset from the central axis 34 offset by the radius of the orbital path.
  • the trained as an eccentric cam 52 is in turn also preferably designed as a cylindrical body with a cylinder surface 64 whose cylinder axis is also parallel to the central axis 34 and beyond a radial distance therefrom, which corresponds approximately to the radius of the orbital path.
  • the driver 52 is formed so that it rests with a driver surface on the driving surface acting as the inner cylindrical surface 60 of the cam receiver 54 in a portion of the same, but incidentally opposite the driving surface 60 without contact, as described in DE 199 10 460, on which is fully incorporated by reference to the structure and function of the driver unit.
  • an inlet 70 is provided for refrigerant to be compressed, through which the refrigerant to be compressed flows into an outer engine cooling chamber 72, which between an outer housing wall 74 and a the drive motor 12 surrounding shielding sleeve 76 is located.
  • the refrigerant to be compressed flows in the direction 78 to a side facing away from the scroll compressor 14 housing bottom 80, but is deflected before reaching the housing bottom 80 of an intermediate bottom 81 radially inwardly and passes through passages 82 of the shielding sleeve 76 and then flows into Direction 83 through the rotor 78 approximately parallel to the axis 34 through to a support member 84 which on the one hand has a bearing bush 86 for the drive shaft 44 and on the other hand has wings 88 on which the second compressor element 18 rests with one of the second spiral rib 26 opposite rear 90 of the bottom 24 and thus supported so that the second compressor body 18 is thereby secured against movement away from the first compressor body 16.
  • the refrigerant to be sucked flows around the support element 84, whereby a part of the refrigerant can flow through the support element 84 and thus reaches the rear side 90 of the bottom 24 and is deflected radially outwards by the latter into an outer cooling chamber 100, which on the one hand is supported by the outer housing wall 74 is enclosed and on the other hand surrounds the scroll compressor 14 radially outboard.
  • a rear-side cooling chamber 110 Adjoining this outer cooling chamber 100 is a rear-side cooling chamber 110, which lies between a rear side 112 of the bottom 20 of the first compressor body 16 and a partition wall 114 fixed in the housing 10, wherein the partition wall 114 carries a holding receptacle 116, with respect to which the first compressor body 16 in the region of the outlet 32 is a seal between the pressure side and suction side and with which the first compressor body 16, for example, also mounted on the partition wall 114.
  • the partition wall 114 in turn extends transversely through the housing 10 and defines a high pressure chamber 120 which lies between a housing cover 122 and the partition wall 114, wherein compressed refrigerant from the outlet 32 through the holding receptacle 116 into the high pressure chamber 120, preferably by a flow in Direction of the axis 34, enters.
  • the high pressure chamber 120 is still provided with a high pressure outlet 124 through which compressed refrigerant exits the high pressure chamber 120.
  • the rear cooling chamber 110 encloses annularly the holding receptacle 116 and is also bounded on the one hand by the partition wall 114 and the other by the bottom 20 of the first compressor body 16, wherein the rear side 112 of the bottom 20 with more than half of its surface adjacent to the rear cooling chamber 110 extending radially to the axis 34 outwardly to the outer cooling chamber 100 and merges into it.
  • the refrigerant to be compressed from the outer cooling chamber 100 enters the suction region 30 in that it in the radial direction of the outer cooling chamber 100 between an outer portion 128 of the bottom 20 and an outer portion 130 of the bottom 24 in the Intake portion 30 flows, which lies between the bottom 20 and the bottom 24 and also adjacent to radially outer ends of the spiral ribs 22 and 24.
  • the first compressor body 16 via outer support members 132, which preferably engage the bottom 20, supported on the support member 84, 132 breakthroughs 134 are provided between the support members, which is an entry of the refrigerant to be compressed from the outer cooling chamber 100 in the radial direction to the axis 34 in the intake 30 allow.
  • a flushing of the entire outer cooling chamber 100 and the rear cooling chamber 110 with the refrigerant to be sucked takes place by convection of the suctioned refrigerant supported by pressure oscillations due to the driven and moving on an orbital track second compressor body 18, to which the outer cooling chamber 100 via the Breakthroughs 134 adjacent intake area 30 adjacent.
  • the back 112 lies within a ring region RB which extends over a radius of approximately 50%. to about 80%, more preferably about 60% to about 70%, of the maximum radius R of the spiral rib 22 of the first compressor body 16 extends an average temperature which is at most 8 °, more preferably at most 5 °, above a temperature of the second Compressor body 18 reaching refrigerant is, so that the registered in the first compressor body 16 heat can be dissipated through the back 112.
  • the first compressor body 16 can be maintained at a temperature which substantially corresponds to the temperature of the second compressor body 18, so that the thermal expansion of the respective bottom 20 and 24 and the spiral ribs 22 and 26 is substantially identical and thus both Compressor body 16 and 18 have no appreciable temperature differences, which lead to a non-uniform thermal expansion and thus to a reduction of the seal in the region of the spiral ribs 22 and 26 and between the spiral ribs 22 and 26 and the respective bottoms 24 and 20 respectively.
  • the outlet 32 is disposed approximately coaxially with the axis 34 in the first compressor body 16 and opens into outlet channels 136, which pass through the holding receptacle 116.
  • the holding receptacle 116 directly adjacent to the rear cooling chamber 110 a discharge of heat from the holding receptacle 116 in the back cooling chamber 110 purging refrigerant is possible in a direct way.
  • the holding receptacle 116 is covered by a valve plate 138 disposed in the high pressure chamber 120 to prevent the high pressure refrigerant flowing through the holding receptacle 116 and entering the high pressure chamber 120 from flowing back into the scroll compressor 14 at all times the pressure at the high-pressure outlet 124 is lower than in the high-pressure chamber 120.
  • the axis 34 is placed so that it is eccentric to a cylinder axis 144 of the housing 10 to 12 in the range of electrical connections 137 for the supply of the electric drive motor a greater distance between the outer wall 74 of the housing 10 and the shield 76 to create.
  • the bottom 20 of the first compressor body 16 is provided in a region adjacent to the suction 30 sector with openings 150 which, as shown in Fig. 4, serve to Compressive refrigerant from the rear cooling chamber 110 to flow into the intake 30 between the floors 20 and 24 and thus forcibly fed to the incoming refrigerant to flow through the rear cooling chamber 110 and thus ensure that in the area of the back 112 of the bottom 20 as possible good flushing of the rear cooling chamber 110 and thus the best possible cooling of the first compressor body 16 takes place.
  • the apertures 150 are arranged so that the refrigerant to be compressed from the rear cooling chamber 110 flows directly into the suction region 30 between the bottoms 20 and 24.
  • a possibility of entry of refrigerant to be compressed from the outer cooling chamber 100 in the suction region 30 by a collar 152 enclosing the scroll compressor 14 is substantially prevented, so that the refrigerant to be compressed on its way from a flushing of the second compressor body 18 to the rinsing of the first compressor body 16, the outer cooling chamber 100 flows through substantially parallel to the axis 34 and the circumference cools the scroll compressor 14 via the sleeve 152, then flows into the rear cooling chamber 110, at least partially flows through them and then through the openings 150 in the Intake portion 30 of the scroll compressor 14 enters.
  • substantially the entire flow of the refrigerant to be sucked is introduced into the rear-side cooling chamber 110 and, due to turbulence and / or diffusion of the refrigerant to be compressed, leads to a flushing of the rear side 112 of the base 20.
  • the rear cooling chamber 110 is at least partially penetrated by the total inflowing into the intake 30 stream of refrigerant to be added before this current enters through the apertures 150 in the intake 30, so that by complementary diffusion or even forming eddy currents optimum flushing of the back Cooling chamber 110 and thus an optimal cooling of the first compressor body 16 and the holding receptacle 116 in the same manner as the second compressor body 18, so that both compressor body 16 and 18 preferably form the same temperature profile and thus achieve an optimized temperature control of both compressor body 16 and 18 that helps to improve the sealing of the scroll compressor 14 during operation.
  • a check valve 160 having a valve body 162 is disposed in the first compressor body 16.
  • a valve seat surface 164 is disposed in the first compressor body 16.
  • valve body 162 is acted upon by a spring 166 in the direction of the valve seat surface 164 and is thus lifted from the valve seat surface 164 only by the compressed, emerging from the outlet 32 refrigerant.
  • This check valve 160 is the fact that it can be arranged as close as possible to the outlet 32 without large damage volume.
  • each of the spiral ribs exemplified by the spiral rib 26 is provided with a face seal 170 formed in a groove 174 formed in an end face 172 of the respective spiral rib 26, comprising two lateral groove walls 176 and 178 and a groove base 180, is used, wherein the front side seal 170 is dimensioned such that it is movable in the groove 174 and thus in the direction of a base 182 of the bottom 20 of the other compressor body is acted upon.
  • the refrigerant to be compressed acts on the face seal so that it dissolves from the higher pressure chamber 28 a facing side wall 176 and rests against the side wall 178, the under lower pressure chamber 28b facing. Further, the refrigerant under higher pressure flows to the groove bottom 180 and thus causes the front side seal 170 lifts off the groove base 180 and is acted upon by the under higher pressure refrigerant against the base 182 and thus held in abutment against this.
  • the seal between the individual spiral ribs 26 and the base surfaces 182 of the respective other compressor body 20 can be improved in an advantageous manner and thus also increase the efficiency of the scroll compressor 14 additionally.
  • the face seals 170 made of a plastic material, preferably Teflon, in particular a Teflon compound with 5% to 20% coal or other strength-promoting additives produced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)

Claims (33)

  1. Compresseur pour réfrigérant, comprenant un carter (10),
    un compresseur à spirale (14) disposé dans le carter avec un premier corps de compresseur (16) disposé de façon fixe dans le carter et un second corps de compresseur (18) mobile par rapport au premier corps de compresseur, qui présente respectivement un fond et des premières et des secondes nervures spiralées (22, 26) s'élevant au-dessus du fond respectif, lesquelles s'engageant les unes dans les autres de telle sorte que, lors de la compression du réfrigérant, le second corps de compresseur peut être déplacé par rapport au premier corps de compresseur sur une trajectoire orbitale autour d'un axe médian, une chambre de refroidissement (110) côté arrière qui est contiguë au premier corps de compresseur (16) dans la zone de sa face arrière (112) opposée aux nervures spiralées, de sorte que le côté arrière (112) peut être lavé par le réfrigérant à comprimer par le compresseur à spirale (14) et peut ainsi être refroidi, et un entraînement pour le second corps de compresseur avec un moteur d'entraînement (12),
    caractérisé en ce que le réfrigérant à comprimer traverse au moins sous la forme d'un flux partiel la chambre de refroidissement (110) côté arrière avec un guidage forcé de telle sorte que le réfrigérant à aspirer s'écoule au moins en partie à la sortie de la chambre de refroidissement (110) côté arrière à travers un percement (150) dans le fond (20) du premier corps de compresseur (16) pour entrer dans la zone d'aspiration (30) du compresseur à spirale (14), et
    en ce que le second corps de compresseur (18) peut être lavé dans la zone de sa face arrière (90) opposée aux nervures spiralées par le réfrigérant à comprimer par le compresseur à spirale (14) et peut ainsi être refroidi.
  2. Compresseur selon la revendication 1, caractérisé en ce que le second corps de compresseur (18) peut être lavé par le réfrigérant à comprimer dans la zone de la face arrière (90) disposée en face de la seconde nervure spiralée (26), radialement à l'extérieur de son logement d'entraînement (54).
  3. Compresseur selon la revendication 1 ou 2, caractérisé en ce que le premier corps de compresseur (16) peut être lavé par le réfrigérant à comprimer dans la zone d'une face arrière (112) opposée à la première nervure spiralée (22).
  4. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que la face arrière (112, 90) du corps de compresseur (16, 18) concerné est formé directement par un fond (20, 24) portant la nervure spiralée (22, 26) concernée.
  5. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que les deux corps de compresseur (16, 18) peuvent être refroidis par le réfrigérant à comprimer dans la zone d'un côté périphérique (128, 130) extérieur par rapport à l'axe médian.
  6. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier corps de compresseur (16) peut être lavé par le réfrigérant à comprimer dans la zone de sa face arrière (112) disposée à l'extérieur d'un branchement de haute pression (32).
  7. Compresseur selon la revendication 6, caractérisé en ce qu'une chambre de refroidissement (110) côté arrière pouvant être lavée par le réfrigérant à comprimer est disposée entre la face arrière (112) du premier corps de compresseur (16) et une paroi de séparation (114), agencée à distance de cette face, du carter (10).
  8. Compresseur selon la revendication 7, caractérisé en ce que la chambre de refroidissement (110) côté arrière renferme un logement de retenue (116) s'étendant vers le premier corps de compresseur (16).
  9. Compresseur selon la revendication 8, caractérisé en ce que la chambre de refroidissement (110) côté arrière est agencée en forme d'anneau autour du logement de retenue (116) pour le premier corps de compresseur (16).
  10. Compresseur selon l'une quelconque des revendications 7 à 9, caractérisé en ce que la paroi de séparation (114) délimite une chambre de haute pression (120) du compresseur.
  11. Compresseur selon l'une quelconque des revendications 7 à 10, caractérisé en ce que la chambre de refroidissement (110) côté arrière fait place à une chambre de refroidissement (100) côté périphérique, renfermant un pourtour extérieur du premier corps de compresseur (16).
  12. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier corps de compresseur (16) est soutenu par des éléments de soutien (132) situés radialement par rapport à l'axe médian (34) à l'extérieur des nervures spiralées (22, 26).
  13. Compresseur selon la revendication 12, caractérisé en ce que la chambre de refroidissement (100) côté pourtour est agencée autour des éléments de soutien (132) extérieurs.
  14. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que la température de la face arrière (112) contiguë au réfrigérant à comprimer dans la chambre de refroidissement (110) côté arrière, du premier corps de compresseur (16) à l'intérieur d'une zone annulaire (RB), qui se situe entre environ 50 % et environ 80 % d'un rayon maximum des nervures spiralées (22, 26), est au maximum de 8° supérieure à la température du réfrigérant qui est à comprimer et atteint le second corps de compresseur (18).
  15. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le réfrigérant à comprimer lave d'abord le premier corps de compresseur (18) et ensuite le second corps de compresseur (16).
  16. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le réfrigérant servant au refroidissement des corps de compresseur (16, 18) est le réfrigérant qui doit être aspiré par le compresseur à spirale (14).
  17. Compresseur selon la revendication 16, caractérisé en ce que le réfrigérant à aspirer refroidit les corps de compresseur (16, 18) essentiellement directement avant son entrée dans une zone d'aspiration (30) du compresseur à spirale (14).
  18. Compresseur selon la revendication 16 ou 17, caractérisé en ce que le réfrigérant à aspirer entre au moins en partie par un côté périphérique du compresseur à spirale (14) entre le fond (20) du premier corps de compresseur (16) et le fond (24) du second corps de compresseur (18) dans la zone d'aspiration (30) du compresseur à spirale (14).
  19. Compresseur selon la revendication 18, caractérisé en ce que le réfrigérant à aspirer entre au moins en partie radialement par rapport à l'axe central (34) entre les fonds (20, 24) des corps de compresseur (16, 18) dans la zone d'aspiration (30) du compresseur à spirale (14).
  20. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'ensemble du réfrigérant à aspirer passe à travers la chambre de refroidissement (110) côté arrière et ensuite à travers le au moins un percement (150) dans le fond (20) du premier corps de compresseur (16) pour entrer dans la zone d'aspiration (30) du compresseur à spirale (14).
  21. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le réfrigérant à comprimer refroidit le moteur d'entraînement (12) et le compresseur à spirale (14).
  22. Compresseur selon la revendication 21, caractérisé en ce que le réfrigérant à comprimer refroidit d'abord le moteur d'entraînement (12) et ensuite le compresseur à spirale (14).
  23. Compresseur selon la revendication 22, caractérisé en ce que le réfrigérant à comprimer traverse le moteur d'entraînement (12) côté rotor.
  24. Compresseur selon la revendication 22 ou 23, caractérisé en ce que le réfrigérant à comprimer circule d'abord autour du moteur d'entraînement (12) côté pourtour.
  25. Compresseur selon l'une quelconque des revendications 22 à 24, caractérisé en ce que le réfrigérant à comprimer entoure d'abord le second corps de compresseur (18) et entre ensuite dans la zone d'aspiration (30) du compresseur à spirale (14).
  26. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que les nervures spiralées (22, 26) d'un corps de compresseur (18, 16) portent des joints de face frontale (170) insérés dans des rainures (174) sur leurs faces frontales (172) tournées vers le fond (24, 20) de l'autre corps de compresseur (18,16).
  27. Compresseur selon la revendication 26, caractérisé en ce que les joints de face frontale (170) peuvent être déplacés dans les rainures en direction du fond de l'autre corps de compresseur.
  28. Compresseur selon la revendication 27, caractérisé en ce que les joints de face frontale (170) sont alimentés par la pression respectivement supérieure dans le compresseur à spirale (14) et peuvent être déplacés en direction du fond (20) de l'autre corps de compresseur (16) concerné.
  29. Compresseur selon l'une quelconque des revendications 26 à 28, caractérisé en ce que les joints de face frontale (170) sont en matière plastique.
  30. Compresseur selon la revendication 29, caractérisé en ce que les joints de face frontale (170) comprennent du téflon comme composant principal.
  31. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un clapet antiretour (160) est attribué à la sortie de haute pression (32).
  32. Compresseur selon la revendication 31, caractérisé en ce que le clapet antiretour présente un siège de joint situé dans le premier corps de compresseur (16).
  33. Compresseur selon la revendication 31, caractérisé en ce que le clapet antiretour (138) est disposé dans une chambre de haute pression (120) sur un côté, faisant face au premier corps de compresseur (16), de la paroi de séparation (114).
EP01986418A 2000-12-22 2001-12-18 Compresseur Expired - Lifetime EP1344005B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10065821 2000-12-22
DE10065821A DE10065821A1 (de) 2000-12-22 2000-12-22 Kompressor
PCT/EP2001/014918 WO2002052205A2 (fr) 2000-12-22 2001-12-18 Compresseur

Publications (2)

Publication Number Publication Date
EP1344005A2 EP1344005A2 (fr) 2003-09-17
EP1344005B1 true EP1344005B1 (fr) 2006-09-06

Family

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EP01986418A Expired - Lifetime EP1344005B1 (fr) 2000-12-22 2001-12-18 Compresseur

Country Status (9)

Country Link
US (1) US6814551B2 (fr)
EP (1) EP1344005B1 (fr)
CN (1) CN1276178C (fr)
AT (1) ATE338925T1 (fr)
DE (2) DE10065821A1 (fr)
DK (1) DK1344005T3 (fr)
ES (1) ES2272557T3 (fr)
PT (1) PT1344005E (fr)
WO (1) WO2002052205A2 (fr)

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US9080446B2 (en) 2012-03-23 2015-07-14 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor with captured thrust washer
US9039384B2 (en) 2012-03-23 2015-05-26 Bitzer Kuehlmaschinenbau Gmbh Suction duct with adjustable diametric fit
US9057269B2 (en) 2012-03-23 2015-06-16 Bitzer Kuehlmaschinenbau Gmbh Piloted scroll compressor
US10233927B2 (en) 2012-03-23 2019-03-19 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor counterweight with axially distributed mass
US9920762B2 (en) 2012-03-23 2018-03-20 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor with tilting slider block
US9022758B2 (en) 2012-03-23 2015-05-05 Bitzer Kuehlmaschinenbau Gmbh Floating scroll seal with retaining ring
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US9441631B2 (en) 2012-03-23 2016-09-13 Bitzer Kuehlmaschinenbau Gmbh Suction duct with heat-staked screen
US9181949B2 (en) 2012-03-23 2015-11-10 Bitzer Kuehlmaschinenbau Gmbh Compressor with oil return passage formed between motor and shell
US9051835B2 (en) 2012-03-23 2015-06-09 Bitzer Kuehlmaschinenbau Gmbh Offset electrical terminal box with angled studs
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US8920139B2 (en) * 2012-03-23 2014-12-30 Bitzer Kuehlmaschinenbau Gmbh Suction duct with stabilizing ribs
US9909586B2 (en) 2012-03-23 2018-03-06 Bitzer Kuehlmaschinenbau Gmbh Crankshaft with aligned drive and counterweight locating features
US8876496B2 (en) 2012-03-23 2014-11-04 Bitzer Kuehlmaschinenbau Gmbh Offset electrical terminal box with angled studs
US9011105B2 (en) 2012-03-23 2015-04-21 Bitzer Kuehlmaschinenbau Gmbh Press-fit bearing housing with large gas passages
BR112015001500A2 (pt) 2012-07-23 2017-07-04 Emerson Climate Technologies revestimentos antidesgaste para superfícies de desgaste do compressor
IN2015MN00117A (fr) 2012-07-23 2015-10-16 Emerson Climate Technologies
CN104343693B (zh) * 2013-08-07 2017-02-08 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机高低压分隔组件及涡旋压缩机
CN105443377A (zh) 2014-06-10 2016-03-30 丹佛斯（天津）有限公司 涡旋压缩机
US9856874B2 (en) 2014-09-26 2018-01-02 Bitzer Kuehlmaschinenbau Gmbh Holding plate for piloted scroll compressor
US10626870B2 (en) 2015-06-11 2020-04-21 Bitzer Kuehlmaschinenbau Gmbh Ring weld blocker in discharge check valve
US9777731B2 (en) 2015-06-16 2017-10-03 Bitzer Kuehlmaschinenbau Gmbh Duct-mounted suction gas filter
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US9890784B2 (en) 2015-06-30 2018-02-13 Bitzer Kuehlmaschinenbau Gmbh Cast-in offset fixed scroll intake opening
US11078913B2 (en) 2015-06-30 2021-08-03 Bitzer Kuehlmaschinenbau Gmbh Two-piece suction fitting
US10408201B2 (en) * 2015-09-01 2019-09-10 PSC Engineering, LLC Positive displacement pump
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Also Published As

Publication number Publication date
CN1420967A (zh) 2003-05-28
CN1276178C (zh) 2006-09-20
US20030031570A1 (en) 2003-02-13
WO2002052205A3 (fr) 2002-12-19
DE50110963D1 (de) 2006-10-19
DK1344005T3 (da) 2007-01-08
ES2272557T3 (es) 2007-05-01
WO2002052205A2 (fr) 2002-07-04
PT1344005E (pt) 2006-12-29
US6814551B2 (en) 2004-11-09
DE10065821A1 (de) 2002-07-11
ATE338925T1 (de) 2006-09-15
EP1344005A2 (fr) 2003-09-17

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