EP3540229B1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP3540229B1
EP3540229B1 EP19171627.3A EP19171627A EP3540229B1 EP 3540229 B1 EP3540229 B1 EP 3540229B1 EP 19171627 A EP19171627 A EP 19171627A EP 3540229 B1 EP3540229 B1 EP 3540229B1
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EP
European Patent Office
Prior art keywords
compressor
compressor body
sliding
coupling
support surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19171627.3A
Other languages
German (de)
English (en)
Other versions
EP3540229A1 (fr
Inventor
Dimitri Gossen
Muzaffer Ceylan
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
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Publication of EP3540229A1 publication Critical patent/EP3540229A1/fr
Application granted granted Critical
Publication of EP3540229B1 publication Critical patent/EP3540229B1/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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/801—Wear plates

Definitions

  • the invention relates to a compressor comprising a compressor housing, a scroll compressor unit arranged in the compressor housing with a first, stationary compressor body and a second compressor body movable relative to the stationary compressor body, the first and second spiral ribs of which, in the form of an involute of a circle, mesh with one another to form compressor chambers, when the second compressor body is moved on an orbital path relative to the first compressor body, an axial guide which supports the movable compressor body against movements in the direction parallel to a central axis of the stationary compressor body and guides it in movements in the direction transverse to the central axis, a drive motor which has an eccentric drive drives for the scroll compressor unit, which has a driver driven by the drive motor and rotating on a path around a central axis of the drive shaft, which is connected to a Driver receptacle of the second compressor body cooperates, and a clutch preventing the second compressor body from rotating itself.
  • the clutch preventing self-rotation has at least two sets of clutch elements comprising at least two clutch elements.
  • Such a coupling can be implemented in the most varied of ways.
  • one of the coupling elements is held on the carrier unit.
  • the coupling element sets are thus arranged and designed in such a way that they are effective directly between the carrier unit and the compressor body base of the second compressor body, so that a compact design can be implemented.
  • the coupling preventing the self-rotation has more than two sets of coupling elements.
  • one of the coupling elements is formed by a pin body.
  • one of the coupling elements is designed as a cylindrical receptacle.
  • one of the coupling elements is designed as an annular body arranged in the cylindrical receptacle. It is preferably provided that the ring body sits loosely, that is to say with play, in the cylindrical receptacle and can thus move relative to the cylindrical receptacle.
  • Such a design of the coupling element sets has the great advantage that, on the one hand, they ensure optimal lubrication and, on the other hand, enable low-noise movement of the second compressor body relative to the first compressor body, since there are two damping lubricant films in each of the coupling element sets, namely on the one hand a lubricant film between the pin body and the ring body and on the other hand a lubricant film between the ring body and the cylindrical receptacle in which the ring body is arranged.
  • the sliding body and the coupling element sets could be arranged separately from one another.
  • the sliding body could extend around the coupling element sets on the outside or vice versa.
  • the coupling element sets penetrate the sliding body so that lubricant can thereby be transported between the sliding body and the coupling element sets, in particular if the coupling element sets reach through openings in the sliding body.
  • the invention provides that the compressor body base of the second compressor body is provided with pockets which have openings facing the cylindrical receptacles of the coupling element sets.
  • Such pockets with openings facing the cylindrical receptacles have the advantage that lubricant is carried along by these during the orbiting movement of the second compressor body base and thus lubricant can always be transported to the cylindrical receptacles.
  • the effect of the pockets is particularly favorable if the openings of the pockets can be positioned in an overlapping manner with two cylindrical receptacles arranged one after the other in the circumferential direction, that is, that in this case the openings of the pockets have such an angular extent that they during the orbiting movement of the Compressor body base can connect two pockets to each other in individual rotary positions and thus can advantageously transport lubricant from one cylindrical receptacle to the other cylindrical receptacle.
  • a horizontal course of the central axis of the stationary compressor body means that the central axis runs approximately parallel to a horizontal when the compressor according to the invention is operated, the term "approximately parallel” being understood to mean that the angle between the central axis and the horizontal when the Compressor according to the invention in the normal operating state is a maximum of 30 °, even better a maximum of 20 °.
  • the drive shaft of the drive motor runs essentially horizontally, the same relationships apply to the angle between the central axis of the drive shaft and a horizontal line as to the alignment of the central axis of the stationary compressor body relative to the Horizontal.
  • the compressor housing is also made of an aluminum alloy, in order to be able to construct the compressor according to the invention as weight-saving as possible.
  • the compressor also has better resistance to external weather influences.
  • the sliding body could be movable one-dimensionally either relative to the compressor body base or relative to the carrier element.
  • the sliding body can be moved two-dimensionally relative to the compressor body base and relative to the carrier element.
  • the movability of the sliding body can be realized particularly expediently when the sliding body is guided by a two-dimensional guide with play relative to the compressor body base or relative to the carrier element.
  • the two-dimensional movability of the sliding body can be implemented in a simple manner and determined with regard to the permitted extent.
  • the sliding body can perform a limited guide orbital movement relative to the compressor base or relative to the carrier element.
  • the orbital movement is expediently defined by a guide orbital radius that is smaller than the compressor orbital radius of the movable compressor body.
  • the guide orbital radius for the sliding body is at values that are equal to 0.5 times the compressor orbital radius. It is better if the values of the guide orbital radius are 0.3 times the compressor orbital radius or less, even better 0.2 times the compressor orbital radius or less.
  • the guide orbital radius is 0.01 times the compressor orbital radius or more, even better 0.05 times the compressor orbital radius or more.
  • the guide has a first guide element which is arranged on the sliding body and has a second guide element which is connected either to the compressor body base or to the carrier element.
  • the guide with play has as guide elements a guide pin and a guide recess which interacts with the guide pin and which can be moved two-dimensionally relative to one another in that the one engaging in the guide recess Guide pin is movable within the guide recess due to its smaller diameter in relation to the diameter of the guide recess.
  • the axial support surface from individual partial surfaces which are arranged on the second compressor body.
  • the axial support surface is designed as an annular surface that encircles the center axis of the movable compressor body.
  • annular surface allows a reliable, uniform and safe support of the second compressor body and, at the same time, the build-up of a homogeneous lubricating film, which is very important for the guiding properties and the wear resistance.
  • the axial support surface could be supported on individual surface areas of the sliding body.
  • the axial support surface is supported on an annular surface of the sliding body that runs around the central axis.
  • the annular surface of the sliding body is preferably dimensioned so that it is larger than the annular surface of the axial support surface, so that the axial support surface is always supported over the entire surface of the annular surface of the sliding body during the orbiting movement of the second compressor body.
  • the axial support surface is adjoined radially on the outside and / or radially on the inside by an edge surface which is set back relative to a plane in which the axial support surface extends runs.
  • edge surface directly adjoins the axial support surface and thus also extends as far as the plane in which the axial support surface extends, and then with increasing distance from the axial support surface at an increasing distance from the plane in which it extends the axial support surface extends.
  • edge surface directly adjoins the axial support surface and thus also extends as far as the plane in which the axial support surface extends, and then with increasing distance from the axial support surface at an increasing distance from the plane in which it extends the axial support surface extends.
  • Such a, for example, step-shaped or wedge-shaped course of the edge surface promotes the supply of lubricant to the axial support surface from an outside thereof.
  • the supply of lubricant between the axial support surface and the sliding body can furthermore be promoted by the fact that the axial support surface and / or a sliding support surface carrying the axial support surface are provided with micro-depressions, for example material-related and / or incorporated and / or embossed depression structures, which absorb lubricant and are available hold and distribute.
  • the sliding support surface could also be formed from partial surfaces.
  • the sliding support surface is designed as an annular surface running around the central axis of the stationary compressor body.
  • the carrier element has a carrier surface on which the sliding body is supported with the sliding support surface.
  • This carrier surface could also be formed from individual partial surfaces.
  • the support surface is designed as an annular surface encircling the center axis of the stationary compressor body.
  • the supply of lubricant between the carrier element and the sliding body can furthermore be promoted by the fact that the sliding support surface and / or a carrier surface carrying the sliding support surface are provided with micro-depressions, e.g. hold and distribute.
  • the sliding body could have any shape.
  • the sliding body is plate-shaped, in particular as an annular disk.
  • the first stationary compressor body is made of cast steel.
  • Such a first compressor body made of cast steel has optimal stability and fatigue strength.
  • the second compressor body is made from an aluminum alloy, in particular from cast aluminum alloy.
  • the production of the second compressor body from an aluminum alloy has the advantage that this second compressor body has a low mass, which is particularly advantageous if the second compressor body is to move at high speed on the orbital path around the central axis of the first compressor body.
  • a material pairing of aluminum alloy and cast steel between the first and the second compressor body also has the advantage of good running properties with high fatigue strength and durability.
  • the sliding body could be made of any material, which, however, should result in an optimal material pairing for the second compressor body and the carrier element.
  • the sliding body is formed from spring steel.
  • the formation of the sliding body from spring steel has the advantage on the one hand that there is a favorable material pairing for the second compressor body made of aluminum, and on the other hand the advantage that an optimal material pairing for the carrier element can be produced as a result.
  • the formation of the second sliding body from spring steel also has great advantages for reasons of cost, since spring steel is an inexpensive material from which the shape suitable for the sliding body can be produced in a simple manner by cutting or punching.
  • the carrier element could be made of steel or also of the material of the compressor housing.
  • the carrier element is made of sintered material, for example sintered metal.
  • the carrier element has a carrier surface, formed by an open-pored sintered material, on which the sliding body is supported with its sliding support surface.
  • Such an open-pored sintered material for forming the carrier surface has the great advantage that it can advantageously absorb lubricant and then also release it for lubrication between the carrier surface and the sliding support surface.
  • the lubricant can in particular be held in the open pores of the sintered material, so that a lubricant film can thereby easily be permanently maintained between the carrier surface and the sliding support surface.
  • a further compressor of the type described above provides that the axial guide supports the second compressor body on an axial support surface formed by it in a sliding manner transversely to the central axis and that the axial support surface is supported by a compressor body base carrying the spiral rib is formed.
  • Such a solution is particularly advantageous in terms of production technology, since no separate part is required for the formation of the support surface, but the support surface itself can be formed by the compressor body base.
  • driver receptacle is integrated in the compressor body base, so that no further part is required for this either.
  • the driver receptacle is arranged in the direction parallel to the central axis of the movable compressor body without protruding from the support surface on the compressor body base, so that the forces acting on the driver receptacle when driving the second compressor body in the direction parallel to the central axis between the support surface and the spiral ribs on the second compressor body act and thus the tilting moments acting on the second compressor body during operation of the scroll compressor unit are kept small.
  • FIG. 1 The illustrated embodiment of a compressor according to the invention, designated as a whole by 10, for a gaseous medium, in particular a refrigerant, comprises a compressor housing, designated as a whole by 12, which has a first end housing section 14, a second end housing section 16 and one between the end housing sections 14 and 16 Has intermediate section 18.
  • a scroll compressor unit designated as a whole by 22, is provided in the first housing section 14, which has a first compressor body 24 arranged in a stationary manner in the compressor housing 12, in particular in the first housing section 14, and a second compressor body 26 movable relative to the stationary compressor body 24.
  • the first compressor body 24 comprises a compressor body base 32 above which a first spiral rib 34 rises and the second compressor body 26 also comprises a compressor body base 36 above which a second spiral rib 38 rises.
  • the compressor bodies 24 and 26 are arranged relative to one another in such a way that the spiral ribs 34, 38 intermesh around one another, as in FIG Fig. 3 shown to form between them at least one, preferably several compression chambers 42, in which a compression of the gaseous medium, for example refrigerant, takes place in that the second compressor body 26 with its central axis 46 around a central axis 44 of the first compressor body 24 on an orbital path 48 moves with a compressor orbital path radius VOR, the volume of the compressor chambers 42 being reduced and ultimately compressed gaseous medium exiting through a central outlet 52, while gaseous medium to be sucked in is sucked in through the circumferentially opening compressor chambers radially outwardly based on the central axis 44.
  • a compression of the gaseous medium for example refrigerant
  • the sealing of the compression chambers 42 relative to one another also takes place in particular in that the spiral ribs 34, 38 are provided with axial sealing elements 54 and 58 on the end face, which abut the respective bottom surface 62, 64 of the respective other compressor body 26, 24 in a sealing manner, the bottom surfaces 62 , 64 are formed by the respective compressor body base 36 or 32 and lie in a plane running perpendicular to the central axis 46.
  • the scroll compressor unit 22 is received as a whole in a first housing body 72 of the compressor housing 12, which has an end cover section 74 and a cylindrical ring section 76 which is integrally formed on the end cover section 74 and which, in turn, with an annular shoulder 78 into an end sleeve 82 of an intermediate section 18 central housing body 84 engages, the central housing body 84 being closed on a side opposite the first housing body 72 by a second housing body 86 which forms an inlet chamber 88 for the gaseous medium.
  • the first housing body 72 with the cylindrical ring section 76 encloses a receptacle 92 for the scroll compressor unit 22, which has a support surface 94 for the compressor body base 32 of the first compressor body 24.
  • the first compressor body 24 is fixed immovably in the receptacle 92 against all movements parallel to the support surface 94.
  • the first compressor body 24 is thus fixed in a stationary manner within the first housing body 72 and thus also within the compressor housing 12 in an exactly defined position.
  • the axial guide 96 formed by a carrier element 112, which is made in particular of an open-pored sintered material and which has a carrier surface 114 facing the axial support surface 102, on which, however, not the compressor body base 36 rests with the axial support surface 102, but on which a whole with 116 designated in particular plate-shaped sliding body 116 with a sliding support surface 118 rests, wherein the sliding body 116 with a sliding support surface 122 opposite the sliding support surface 118 supports the axial support surface 102 against movements parallel to the central axis 44 but guides it in a sliding manner with respect to movements transverse to the central axis 44.
  • the axial guide 96 provides that when the second compressor body 26 moves on the orbital path 48 around the central axis 44 of the first compressor body 24, on the one hand the second compressor body 26 with the compressor body base 36 and its axial support surface 102 moves relative to the sliding body 116 , on the other hand the sliding body 116 in turn moves relative to the carrier element 118.
  • sliding between the compressor body base 36 and the sliding body 116 takes place through a movement of the axial support surface 102 relative to the sliding support surface 122 of the sliding body 116 and, in addition, the sliding support surface 118 of the sliding body 116 is sliding relative to the carrier surface 114 of the carrier element 112.
  • the sliding support surface 122 and the sliding support surface 118 of the sliding body 116 are provided with depressions 123, in particular micro-depressions, which form receptacles for a lubricant and contribute to the distribution of the lubricant, as exemplified in FIG Fig. 6 shown in connection with the slide support surface 122.
  • the sliding body 116 is guided by a guide designated as a whole as 132 with play relative to the carrier element 112, the guide with play 132 being a in the sliding body 116 includes guide recess 134, which has a diameter DF, and includes a guide pin 136 anchored in the carrier element 112, the diameter DS of which is smaller than the diameter DF, so that half of the difference DF-DS defines a guide orbital radius FOR, with which the sliding body 116 can perform an orbiting movement relative to the carrier element 112.
  • the carrier element 112 is provided with radially outer pockets 142 which extend below an outer edge region 144 of the sliding body 116 and thus facilitate access of lubricant into an intermediate space 146 between the carrier surface 114 and the sliding support surface 118.
  • the intermediate space 146 is filled with a lubricating film 147, similar to the mode of operation of a hydrodynamic bearing.
  • the guide orbital radius FOR is 0.01 times the compressor orbital radius VOR or more, in particular 0.05 times the compressor orbital radius VOR or more.
  • the guide orbital radius FOR is 0.3 times the compressor orbital radius VOR or less, more preferably 0.2 times the compressor orbital radius VOR or less.
  • the carrier element 112 is made of an open-pored sintered material at least in the area of the carrier surface 114, improved lubrication is additionally ensured by the fact that lubricant enters the pores of the carrier element 112 and thus through the pores of the carrier element 112 in the area of the Support surface 114 for building up the lubricating film 147 in the space 146 is available.
  • the sliding body 116 itself is designed as a plate-shaped, ring-shaped part made of spring steel and thus the sliding support surface 118 facing the carrier surface 114 represents a smooth spring steel surface, the formation of the lubricating film 147 in the space 146 is additionally promoted. Furthermore, the material pairing of open-pored sintered material, which is softer than spring steel in the area of the support surface 114, and the spring steel in the area of the sliding support surface 118 has advantageous long-term running properties due to its wear resistance.
  • the compressor body base 36 is in a radially outer and a radially inner edge region 152 with a relative to the axial support surface 102 inclined and opposite to the axial support surface 102,
  • the edge surface 154 running set back is provided which, together with the sliding support surface 122, leads to a wedge-shaped gap 158 opening radially outward or radially inward, which facilitates the access of lubricant to the gap 148.
  • the axial support surface 102 and the interacting with this sliding support surface 122 as well as the carrier surface 114 and the interacting with this sliding support surface 118 are all arranged radially outside of a plurality of coupling element sets 162, which are at the same radial distances from the central axis 44 and at the same angular intervals circumferentially around the central axis 44 and together form a coupling 164 which prevents self-rotation of the second movable compressor body 26.
  • Each of these sets of coupling elements 162 comprises, as in FIGS Fig. 4 , 6 to 8 shown, as the first coupling element 172 is a pin body 174 which has a cylindrical jacket surface 176 and with this cylindrical jacket surface 176 engages in a second coupling element 182.
  • the second coupling element 182 is formed by an annular body 184 which has a cylindrical inner surface 186 and a cylindrical outer surface 188, which are arranged coaxially to one another.
  • This second coupling element 182 is guided in a third coupling element 192, which is designed as a receptacle 194 provided in the carrier element 112 for the ring body 184 and which has a cylindrical inner wall surface 196.
  • a diameter DI of the inner wall surface 196 is greater than a diameter DRA of the cylindrical outer surface 188 of the ring body 184 and a diameter DRI of the cylindrical inner surface 186 is necessarily smaller than the diameter DRA of the cylindrical outer surfaces 188 of the ring body 184, with the diameter DRI of the cylindrical Inner surface 186 is greater than a diameter DSK of the cylindrical outer surface 176 of the pin body 174.
  • each coupling element set 162 in turn forms an orbital guide, the maximum orbital radius of which corresponds to OR for the orbiting movement DI / 2- (DRA-DRI) -DSK / 2.
  • the movable compressor body 26 is guided relative to the stationary compressor body 24 by the coupling 164 in such a way that that, as in the Figures 9-14 shown, in each case one of the coupling element sets 162 is effective to prevent the self-rotation of the second movable compressor body 26, for example, with six coupling element sets 162 after passing through an angular range of 60 °, the effectiveness of each coupling element set 162 from one coupling element set 162 to the next following coupling element set 162 in the direction of rotation changes.
  • each coupling element set 162 has three coupling elements 172, 182 and 192 and in particular an annular body 184 is effective between the respective pin body 174 and the respective receptacle 194, on the one hand the wear resistance of the coupling element sets 162 is improved, on the other hand the lubrication in the area thereof is improved and, moreover, the generation of noise caused by the coupling element sets 162, which is caused by the change in the effectiveness of one coupling element set 162 to the other coupling element set 162, is also reduced.
  • the coupling element sets 162 experience sufficient lubrication, in particular lubrication between the cylindrical outer surface 176 of the pin body 174 and the cylindrical inner surface 186 of the ring body 184 as well as lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196 of the Recording 194.
  • the coupling element sets 162 pass through the sliding body 116, in particular the pin body 174 openings 198 ( Fig. 7 ) of the sliding body 116 reach through, whereby lubricant from the lubricating films 147 and 149 can be supplied to the coupling element sets 162.
  • the compressor body base 36 is as in FIGS Fig. 8 and 15th shown, between the bores 202 receiving the first coupling elements 172 pockets 204 are provided, which in the flat side 98 delimiting the compressor body base 36 have an opening 206 which has such an angular extent in relation to the central axis 46 of the compressor body base 36 that it, as in FIG Fig. 15 shown, in individual rotational positions with two receptacles 194 of the coupling element sets 162 that follow one another in the direction of rotation can overlap, so that the pockets 204 are able to effect an exchange of lubricant between successive coupling element sets 162 and thus enable a uniform supply of lubricant to all coupling element sets 162.
  • the pockets 204 are preferably arranged in such a way that they extend on both sides of a geometric circular arc 208 around the central axis 46 which intersects the bores 202 in the middle in order to always achieve an optimal overlap with the receptacles 194.
  • the concept according to the invention of the lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous when the central axes 44 and 46 of the compressor bodies 24 and 26 normally run horizontally, i.e. at a maximum angle of 30 ° to a horizontal the compressor housing 12, in particular in the area of the first housing body 72 at a point lowest in the direction of gravity, forms a lubricant bath 210, from which lubricant is whirled up during operation and absorbed and distributed in the manner described.
  • the movable compressor body 24 is driven by a drive motor designated as a whole by 212, which has in particular a stator 214 held in the central housing body 84 and a rotor 216 arranged inside the stator 214, which is arranged on a drive shaft 218 which is coaxial to the central axis 44 of the stationary compressor body 24 runs.
  • a drive motor designated as a whole by 212, which has in particular a stator 214 held in the central housing body 84 and a rotor 216 arranged inside the stator 214, which is arranged on a drive shaft 218 which is coaxial to the central axis 44 of the stationary compressor body 24 runs.
  • the drive shaft 218 is supported on the one hand in a bearing unit 222 arranged between the drive motor 212 and the scroll compressor unit 22 and in the central housing body 84 and on the other hand in a bearing unit 224 which is arranged on a side of the drive motor 212 opposite the bearing unit 222.
  • the bearing unit 224 is supported, for example, in the second housing body 86, which closes off the central housing body 84 on a side opposite the first housing body 72.
  • the drive shaft 218 drives the movable compressor body 26 via an eccentric drive designated as a whole as 232, which moves orbiting about the central axis 44 of the stationary compressor body 24.
  • the eccentric drive 232 comprises in particular an eccentric pin 234 held in the drive shaft 218, which moves a driver 236 on an orbital path around the central axis 44, which is rotatably mounted on the eccentric pin 234 and in turn is rotatably mounted in a pivot bearing 238, the pivot bearing 238 being a Rotation of the driver 236 relative to the movable compressor body 26 allowed.
  • the driver 236 is rotatable to a limited extent relative to the eccentric pin 234 and relative to the driver receptacle 242 and enables the radius of the orbital movement of the movable compressor body 26 to be adjusted in order to keep the spiral ribs 34 and 38 in contact with one another.
  • the second compressor body 26 is provided with a driver receptacle 242 which receives the rotary bearing 238.
  • the driver receptacle 242 is set back relative to the flat side 98 of the compressor body base 36 and is thus arranged integrated in the compressor body base 36, so that the driving forces acting on the movable compressor body 26 on a side of the spiral rib 38 facing Flat side 98 of the compressor body base 36 are effective and thus drive the movable compressor body 26 with a low tilting moment, which is axially supported on the axial support surface 102 and guided transversely to the central axis 44 between the driver receptacle 242 and the electric motor 212 when viewed through the axial guide 96 in the direction of the central axis 44 is.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (14)

  1. Compresseur comprenant
    un carter de compresseur (12),
    une unité compresseur à spirale agencée (22) dans le carter de compresseur (12) et pourvue d'un premier corps de compresseur stationnaire (24) et d'un deuxième corps de compresseur (26), mobile par rapport au premier corps de compresseur stationnaire (24), dont les premières et deuxièmes nervures en spirale (34, 38), configurées en forme de développante de cercle, s'engrènent l'une dans l'autre tout en formant des chambres de compression (42) lorsque le deuxième corps de compresseur (26) est déplacé par rapport au premier corps de compresseur (24) sur une trajectoire orbitale (48),
    un guide axial (96), lequel soutient le corps de compresseur mobile (26) à l'encontre de déplacements dans une direction parallèle à un axe médian (44) du corps de compresseur stationnaire (24) et conduit ledit corps de compresseur mobile (26) pour des déplacements dans une direction transversale à l'axe médian (44),
    un moteur d'entraînement (212) entraînant un entraînement excentrique (232) destiné à l'unité compresseur à spirale (22), lequel présente un entraîneur (236) entraîné par le moteur d'entraînement (212) et circulant sur une trajectoire autour d'un axe médian (44) d'un arbre d'entraînement (218), ledit entraîneur coopérant avec un logement d'entraîneur (242) du deuxième corps de compresseur (26),
    et un accouplement (164) empêchant une autorotation du deuxième corps de compresseur (26),
    l'accouplement (164) empêchant l'autorotation présente au moins deux jeux d'éléments d'accouplement (162) comprenant au moins deux éléments d'accouplement (172, 182, 192) et l'un (172) des éléments d'accouplement étant formé par un corps de goupille (174),
    l'un (182) des éléments d'accouplement étant configuré en forme de corps annulaire (184) disposé dans un logement cylindrique (194),
    caractérisé en ce que la base (36) du deuxième corps de compresseur (26) est pourvue de poches (204) qui présentent des orifices (206) dirigés vers les logements cylindriques (194) des jeux d'éléments d'accouplement (162).
  2. Compresseur selon la revendication 1, caractérisé en ce que l'un des éléments d'accouplement (172) est maintenu contre la base du corps de compresseur (36).
  3. Compresseur selon la revendication 1 ou la revendication 2, caractérisé en ce que l'un des éléments d'accouplement (192) est maintenu contre l'élément de support (112).
  4. Compresseur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'accouplement (164) empêchant l'autorotation présente plus de deux jeux d'éléments d'accouplement (162).
  5. Compresseur selon la revendication 4, caractérisé en ce que les jeux d'éléments d'accouplement (162) sont disposés tout autour de l'axe médian (44) de la trajectoire orbitale (48) à des distances angulaires identiques.
  6. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le corps annulaire (184) est logé sans attache dans le logement cylindrique (194) avec un jeu.
  7. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que les orifices (206) des poches (204) peuvent être positionnés en se chevauchant avec respectivement deux logements cylindriques (194) disposés successivement dans le sens périphérique.
  8. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'axe médian (44) du corps de compresseur stationnaire (24) est couché et que, en particulier, un arbre d'entraînement (218) du moteur d'entraînement (212) est couché.
  9. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le carter de compresseur (12) est fabriqué dans un alliage d'aluminium.
  10. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le guide axial (96) soutient de manière coulissante le deuxième corps de compresseur (26) contre une face d'appui axiale (102), formée par ce dernier, transversalement à l'axe médian (44), et en ce que la face d'appui axiale (102) est formée par une base (36), portant la nervure en spirale (38), du deuxième corps de compresseur (26).
  11. Compresseur selon la revendication 10, caractérisé en ce que le logement d'entraîneur (242) est intégré dans la base (34) du corps de compresseur.
  12. Compresseur selon la revendication 10, caractérisé en ce que le logement d'entraîneur (242) est disposé sur la base du corps de compresseur (36) parallèlement à l'axe médian (44) sans dépasser de la face d'appui (102).
  13. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le guide axial (96) soutient une base (36), portant la nervure en spirale (38), du deuxième corps de compresseur (26) contre une face d'appui axiale (102) du fait que la face d'appui axiale (102) repose de manière coulissante transversalement à l'axe médian (102), sur un corps coulissant (116) qui, de son côté, est soutenu de manière coulissante transversalement à l'axe médian (64), sur un élément de support (112) disposée dans le carter de compresseur (12).
  14. Compresseur selon la revendication 13, caractérisé en ce que le corps coulissant (116) peut être déplacé en deux dimensions par rapport à la base (36) du corps de compresseur et par rapport à l'élément de support (112), et en ce que, en particulier, le corps coulissant (116) est guidé, par un guide en deux dimensions avec un jeu (132), de manière mobile par rapport à la base (36) du corps de compresseur et/ou par rapport à l'élément de support (112).
EP19171627.3A 2014-09-17 2015-09-09 Compresseur à spirales Active EP3540229B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102014113435.4A DE102014113435A1 (de) 2014-09-17 2014-09-17 Kompressor
PCT/EP2015/070568 WO2016041824A2 (fr) 2014-09-17 2015-09-09 Compresseur
EP15760194.9A EP3194782B1 (fr) 2014-09-17 2015-09-09 Compresseur à spirales

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP15760194.9A Division EP3194782B1 (fr) 2014-09-17 2015-09-09 Compresseur à spirales

Publications (2)

Publication Number Publication Date
EP3540229A1 EP3540229A1 (fr) 2019-09-18
EP3540229B1 true EP3540229B1 (fr) 2021-11-03

Family

ID=54065372

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Application Number Title Priority Date Filing Date
EP19171627.3A Active EP3540229B1 (fr) 2014-09-17 2015-09-09 Compresseur à spirales
EP15760194.9A Active EP3194782B1 (fr) 2014-09-17 2015-09-09 Compresseur à spirales

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP15760194.9A Active EP3194782B1 (fr) 2014-09-17 2015-09-09 Compresseur à spirales

Country Status (5)

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US (2) US10634141B2 (fr)
EP (2) EP3540229B1 (fr)
CN (2) CN106795768B (fr)
DE (1) DE102014113435A1 (fr)
WO (1) WO2016041824A2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014113435A1 (de) 2014-09-17 2016-03-17 Bitzer Kühlmaschinenbau Gmbh Kompressor
KR102080622B1 (ko) 2015-03-06 2020-02-25 한온시스템 주식회사 스크롤 압축기
WO2017144098A1 (fr) * 2016-02-25 2017-08-31 Bitzer Kühlmaschinenbau Gmbh Compresseur
DE102017111778B4 (de) 2017-05-30 2019-09-19 Hanon Systems Vorrichtung zum Verdichten eines gasförmigen Fluids
JP6711331B2 (ja) 2017-08-11 2020-06-17 株式会社Ｓｏｋｅｎ スクロール圧縮機
DE102020133438A1 (de) 2020-12-14 2022-06-15 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine, insbesondere Scrollkompressor oder -expander und Kälteanlage
JP2022112858A (ja) * 2021-01-22 2022-08-03 三菱重工サーマルシステムズ株式会社 圧縮機
KR102630534B1 (ko) * 2022-01-14 2024-01-29 엘지전자 주식회사 스크롤 압축기

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Also Published As

Publication number Publication date
CN106795768A (zh) 2017-05-31
WO2016041824A2 (fr) 2016-03-24
US20170184107A1 (en) 2017-06-29
EP3194782B1 (fr) 2019-05-01
EP3194782A2 (fr) 2017-07-26
EP3540229A1 (fr) 2019-09-18
US11396877B2 (en) 2022-07-26
CN106795768B (zh) 2019-11-26
DE102014113435A1 (de) 2016-03-17
US10634141B2 (en) 2020-04-28
US20200217319A1 (en) 2020-07-09
WO2016041824A3 (fr) 2016-06-02
CN110925196A (zh) 2020-03-27

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