EP3011181B1 - Compresseur de liquide de refroidissement - Google Patents

Compresseur de liquide de refroidissement Download PDF

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Publication number
EP3011181B1
EP3011181B1 EP14730912.4A EP14730912A EP3011181B1 EP 3011181 B1 EP3011181 B1 EP 3011181B1 EP 14730912 A EP14730912 A EP 14730912A EP 3011181 B1 EP3011181 B1 EP 3011181B1
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EP
European Patent Office
Prior art keywords
lubricant
bearing
bearing housing
housing
compressor
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
EP14730912.4A
Other languages
German (de)
English (en)
Other versions
EP3011181A1 (fr
Inventor
Klaus Feller
Roni LÖRCH
Tihomir Mikulic
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 EP3011181A1 publication Critical patent/EP3011181A1/fr
Application granted granted Critical
Publication of EP3011181B1 publication Critical patent/EP3011181B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C29/026—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
    • 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
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C29/0092—Removing solid or liquid contaminants from the gas under pumping, e.g. by filtering or deposition; Purging; Scrubbing; Cleaning

Definitions

  • the invention relates to a refrigerant compressor, in particular a screw compressor, comprising a compressor housing, a compressor element arranged in the compressor housing and driven by a drive, at least one bearing unit for at least one element of the drive, which comprises at least one bearing housing and at least one roller bearing arranged in the bearing housing.
  • the invention is therefore based on the object of improving a refrigerant compressor of the type described at the outset in such a way that an optimal lubricant supply to the rolling bearing in the bearing housing is possible.
  • This object is achieved according to the invention in a refrigerant compressor of the type described at the outset by supplying lubricant to the bearing housing from a lubricant distribution system, by assigning a lubricant metering unit to the bearing housing, which has a filter receiving chamber, and by arranging a filter body in the filter receiving chamber.
  • the advantage of the solution according to the invention can be seen in the fact that with this it is possible to meter the flow of the lubricant through the filter body to the rolling bearing in the bearing housing and at the same time to reduce the probability of damage to the rolling bearing. that the lubricant flow is filtered through the filter body again immediately before entering the rolling bearing, so that particles that are also floating in the lubricant distribution system are also filtered out and cannot enter the rolling bearing.
  • the filter body takes on the throttling function for the flow of the lubricant.
  • an inlet channel extends from the filter receiving chamber to a lubricant chamber adjacent to the roller bearing, following the filter receiving chamber.
  • this inlet channel has no additional functions to take over.
  • the lubricant metering unit has a throttle bore arranged between the filter receiving chamber and a lubricant chamber adjacent to the roller bearing, which, in addition to the filter body, has a throttling effect on the lubricant flow supplied to the lubricant chamber, so that overall the throttle effect of the lubricant metering unit through the filter body and the throttle bore is created.
  • Such a throttle bore has the advantage that its throttling effect is supplemented by the throttling effect of the filter body, and thus it can also be ensured in the bearing housing for various operating states of a reliable lubricant distribution system of the rolling bearing.
  • the filter body not only has a throttling effect on the lubricant flow, but the filter body allows the throttle bore to be made as a very thin, fine bore, without the risk that this throttle bore will become blocked due to particles carried by the lubricant distribution system.
  • bearing housing has a housing element in which the lubricant metering unit is arranged, in particular integrated.
  • the housing element could, for example, be a housing section that receives the roller bearing.
  • the housing element, which receives the lubricant metering unit is designed as a bearing housing cover of the bearing housing.
  • the housing element is designed as a bearing housing ring of the bearing housing.
  • the lubricant metering unit is integrated in the bearing housing cover.
  • One solution provides that the lubricant metering unit feeds the lubricant to a lubricant chamber of the bearing housing, from which the lubricant can then enter the rolling bearing.
  • the lubricant metering unit feeds the lubricant to the lubricant chamber, the lubricant collecting at a deepest point in the lubricant chamber and then entering the rolling bearing.
  • the lubricant metering unit is provided with a nozzle bore downstream of the filter receiving chamber, which generates a lubricant jet directed at the rolling bearing in the bearing housing and thus specifically applies the lubricant, for example, to the rolling elements of the rolling bearing.
  • the filter body used according to the invention has a further advantage, namely in that the nozzle bore can be designed as a very fine bore and because of the additional filter effect of the filter body, clogging of the nozzle bore by particles carried in the lubricant distribution system is avoided.
  • a particularly favorable solution provides that the throttle bore of the lubricant metering unit is arranged in such a way that it acts as a nozzle bore.
  • the filter body can be formed from different materials.
  • the filter body prefferably be made of sintered metal, for which purpose bronze or stainless steel can be used as the material.
  • the filter body is made of plastic which is neutral in terms of refrigerant and lubricant, in particular a sintered porous plastic, for example also a compacted or baked plastic granulate, can be used.
  • the compressor element could be a piston or a scroll element with an appropriately designed drive for it.
  • the compressor element is a screw rotor of a screw compressor and that the drive as elements comprises shaft sections supporting the screw rotor, at least one of which is mounted according to the present invention.
  • the shaft sections arranged on the suction side and / or the shaft sections arranged on the high pressure side are supported according to the present invention.
  • FIG. 1 The illustrated embodiment of a refrigerant compressor according to the invention comprises an overall housing 10 which has a compressor housing 12, a motor housing 14 arranged on one side of the compressor housing 12 and a pressure housing 16.
  • the screw rotors 26, 28 extend from a low-pressure side 36 to a high-pressure side 38, the low-pressure side 36 being assigned a refrigerant supply channel 42, while an in on the high-pressure side 38 Fig. 1
  • a high-pressure outlet (not shown) is provided, from which the compressed refrigerant enters the pressure housing 16 via an outflow channel 44, namely into an end chamber 46, from which it then passes through two lubricant separators 52, 54 arranged in the pressure housing 16, through which the lubricant flows the compressed refrigerant is separated and supplied to an oil sump 56 arranged in the pressure housing 16, wherein the refrigerant compressed to high pressure also emerges from the pressure housing 16 through a high pressure outlet, not shown.
  • the screw rotors 26, 28 are supported in the region of the low-pressure side 36 of the screw rotors 26, 28 by means of bearing units 62, 64 arranged in the compressor housing, which support bearing shaft sections 66, 68 of the screw rotors 26, 28.
  • screw rotors 26, 28 are supported in the region of their high-pressure side by bearing units 72, 74, which likewise support shaft sections 76, 78 of the screw rotors 26, 28.
  • the bearing units 72, 74 are arranged in a bearing housing 82 on the high-pressure side, which is fixedly connected to the compressor housing 12 and projects into the pressure housing 16 following the compressor housing 12.
  • the screw rotors 26, 28 are driven by a drive motor 84 arranged in the motor housing 14, the motor shaft 86 of which, for example, integrally merges into the bearing shaft section 66 and carries a rotor 92, which in this exemplary embodiment can also be rotated coaxially to the axis of rotation 32 of the bearing shaft section 66.
  • the drive motor 84 has a stator 94, which is arranged in the motor housing 14 in a rotationally fixed manner.
  • the drawn-in refrigerant first flows through the motor housing 14 in order to cool the rotor 92 and the stator 94, and then passes into the refrigerant supply channel 42, which the refrigerant to be drawn in on the low-pressure side 36 of the screw rotor 26, 28 feeds.
  • a lubricant supply system designated as a whole by 100, which receives a filter unit from the lubricant sump 56, which is under high pressure, a filter unit 102 and then supplies the lubricant from the filter unit 102 to the individual bearing units 62, 64, 72, 74.
  • the lubricant supply system 100 comprises a lubricant distribution system 104 leading from the filter unit 102 to the bearing units 62, 64.
  • the bearing shaft sections 66, 68 are rotatably accommodating roller bearings 112, 114 each in bearing housings 116, 118, which on the one hand hold and with the outer bearing rings 122, 124 of the roller bearings 112, 114
  • Receiving holes 126, 128 provided wall areas 132, 134 of the compressor housing 12 are formed and are closed on a side facing away from the respective screw rotor 26, 28 by bearing housing covers 136, 138, so that there are lubricant chambers 142, 144 in the bearing housings 116, 118, which contain the lubricant is to be supplied for lubrication of the roller bearings 112, 114.
  • lubricant must be supplied to these lubricant chambers 142, 144 to a sufficient extent in order to be able to ensure reliable and permanent lubrication of the roller bearings 112, 114, but on the other hand too much lubricant supplied to the lubricant chambers 142, 144 leads to splashing and crushing losses in the region of the roller bearings 112 , 114, which increase the power consumption of the drive motor 84 and thus deteriorate the coefficient of performance of the refrigerant compressor.
  • each of the bearing housings 116, 118 is provided with a lubricant metering unit 152, 154, which is integrated, for example, in the respective bearing housing cover 136, 138.
  • lubricant metering units 152, 154 The function and mode of operation of the lubricant metering units 152, 154 is explained below by way of example with reference to the lubricant metering unit 154, integrated in the bearing housing cover 138, the corresponding explanations for the lubricant metering unit 152, integrated in the bearing housing cover 136.
  • the bearing housing cover 138 comprises an outer ring body 162, which is inserted with its radially outer peripheral surface 164 into the corresponding receiving bore, in this case the receiving bore 128.
  • An end wall, designated as a whole by 166, is formed on the ring body 162 and delimits an interior 168 enclosed by the annular body 162 on a side facing away from the respective screw rotor 26, 28, while the interior 168 faces the respective rolling bearing, in this case the rolling bearing 114 has an opening 172 so that the corresponding lubricant chamber 144 can extend into the interior 168.
  • the ring body 162 comprises a circumferential groove 174, which extends from the peripheral surface 164 and serves to pass on the lubricant supplied by the lubricant distribution system 104, for example to the bearing housing cover 138.
  • the lubricant metering unit 154 comprises in the in Fig. 3 illustrated first exemplary embodiment of the same, a filter receiving chamber 182 extending from the groove 174 into the ring body 162 and into which a filter body 184 is inserted.
  • An inlet channel 186 extends from the filter receiving chamber 182, preferably coaxially thereto, to the interior 168.
  • the filter receiving chamber 182 and the inlet channel 186 are designed as bores, the filter receiving chamber 182 having a larger diameter with respect to a central axis 188 than the inlet channel 186 adjoining it coaxially, so that the transition from the filter receiving chamber 182 into the inlet channel 186 forms a step 192 against which the filter body 184 rests and through which the filter body 184 is secured against migration into the interior 168.
  • the filter body 184 is preferably made of a porous material, so that the filter body 184, by selecting the porosity thereof, acts as a flow restrictor for the supplied lubricant and is therefore able to restrict the supply of lubricant into the corresponding lubricant chamber 144 in such a way that sufficient lubricant, however, not too much lubricant is supplied to the respective lubricant chamber, in this case the lubricant chamber 144.
  • the filter body 184 can be formed from different materials.
  • the filter body 184 is made of sintered metal, in which case bronze or stainless steel can be used as the material.
  • the filter body 184 is formed from plastic which is neutral in terms of refrigerant and lubricant, it being possible in particular to use a sintered porous plastic and / or a compacted baked plastic granulate.
  • the inlet channel 186 adjoining the filter receiving chamber 182 does not have a flow-preventing effect, but is irrelevant to the question of metering the amount of lubricant supplied to the lubricant chamber 144.
  • the lubricant then collects, for example at least in part, in the lubricant chamber 144 at the lowest point in the direction of gravity in the form of a lubricant bath 190 and passes from there into the roller bearing 114.
  • the inlet channel 186 adjoining the filter receiving chamber 182 does not open directly into the interior 168 of the ring body 162, but passes into a throttle bore 194 which, in addition to the filter body 184, has a throttling effect on the supplied lubricant flow, so that in this case the lubricant metering unit 154 'on the one hand exerts a throttling effect through the filter body 184 and on the other hand through the throttle bore 194, the throttle bore 194 preferably being oriented radially to the axis of rotation 34 of the corresponding roller bearing, in this case the roller bearing 114.
  • the inlet channel 186 running radially to the axis of rotation 34 of the associated roller bearing 114 merges into a nozzle bore 196 which lies within the opening 172 of the interior 186 facing the roller bearing 114, but extends in particular parallel or slightly obliquely to the axis of rotation 34 of the associated roller bearing 114 and thus generates a lubricant jet 198 directed directly at the roller bearing 114, in particular at the rolling elements of the same, so that a direct lubricant is supplied to the roller bearing 114 in order to optimize the lubricant distribution in the roller bearing 114.
  • the inlet channel 186 to the interior 168 of the ring body 162 is closed.
  • the lubricant distribution system 104 "'supplies not only the bearing units 62 and 64 but also the bearing units 72 and 74 with lubricant.
  • each of the bearing units 72 and 74 comprises a set of roller bearings 202, 204 and 206, which are arranged in the high-pressure-side bearing housing, designated as a whole by 82, and with their bearing outer rings 212, 214, 216 in receiving bores 222 and 224, respectively, provided for them
  • Bearing housing 82 sit, the receiving bores 222, 224 being surrounded by wall areas 226, 228 of the high-pressure side bearing housing 82 and also being delimited by wall areas 232, 234 on their side facing the high-pressure sides 38 of the screw rotors 26, 28, which are defined by the shaft sections 76 and 78 are penetrated and close tightly with them, so that the wall regions 232, 234 form a tight seal between the high-pressure sides 38 of the screw rotors 26, 28 and the receiving bores 222, 224.
  • Bearing housing rings 242, 244, which are inserted into the receiving bores 222, 224, are located on the opposite sides of the high-pressure sides 38 of the screw rotors 26, 28 and are thus arranged between the respective wall regions 232, 234 and the nearest roller bearing 202.
  • Such bearing housing rings 242, 244 can either, as in Fig. 6 and 7 shown, be arranged at the end of the roller bearings 202, 204, 206 or between two of the roller bearings 202, 204, 206.
  • the bearing housing rings 242, 244 delimit lubricant chambers 252, 254 arranged between them and the closest roller bearings 202, from which a lubricant supply to the roller bearings 202, 204 and 206 takes place, for example through the respective bearings.
  • each of these bearing housing rings 242, 244 comprises an annular body 262 with a peripheral surface 264 abutting the wall regions 226, 228, and an inner space 266 opposite the peripheral surfaces 264, which is part of the respective lubricant chamber 254.
  • a groove 274 extends into the ring body 262 in the same way as in the case of the bearing housing covers 136, 138.
  • the filter receiving chamber 182 extends with the filter body 184 and an inlet channel 186 adjoining the filter receiving chamber 182, which opens into the interior 266 of the bearing housing ring 244.
  • the lubricant metering unit 152, 154 is therefore also provided in each of the bearing housing rings 242, 244 Has annular body 262 extending filter receiving chamber 182, in which the filter body 144 is inserted and from which the inlet channel 186 extends to the interior 266 of the bearing housing ring 244.
  • the lubricant metering unit 152, 154 is configured in the same way as described in the previous exemplary embodiments and has the same effect as in the case of these exemplary embodiments.
  • the bearing housing ring 244 can also be used between two of the roller bearings 202, 204, 206.
  • the lubricant metering unit 154 is designed in the same way as described in the third exemplary embodiment of the bearing housing cover 136, 138 of the first exemplary embodiment of the refrigerant compressor according to the invention, so that reference can be made in full to the description of the third exemplary embodiment, the lubricant metering unit 154" in this case is integrated into the ring body 262 and the ring body 262 has no interior 266.
  • the annular body 262 has the nozzle bore 196 which extends from the inlet channel 186 and into the lubricant chamber 254 and is directed onto the first roller bearing 202, which generates the lubricant jet 198, which is directed in particular at roller bodies of the first roller bearing 202.
  • a third exemplary embodiment of a bearing ring 244 "according to the invention, shown in FIG Fig. 10 , is designed such that it can preferably be used between two of the roller bearings 202, 204, 206, opposing nozzle bores 196a, b being provided, each of which generates a lubricant jet 198a, b, so that the lubricant jets 198a, b are in each other spread opposite directions.
  • the third exemplary embodiment is designed in the same way as the second exemplary embodiment, so that reference is made in full to this.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rolling Contact Bearings (AREA)

Claims (11)

  1. Compresseur à réfrigérant, en particulier compresseur à vis, comprenant un logement de compresseur (12), un élément de compresseur (26, 28) disposé dans le logement de compresseur (12) et entraîné par un entraînement (84, 86, 66, 68 76, 78), au moins une unité de palier (62, 64, 72, 74) pour au moins un élément (66, 68) de l'entraînement (84, 86, 66, 68, 76, 78), laquelle comprend au moins un logement de palier (116, 118, 82) et au moins un palier à roulement (112, 114, 202, 204, 206) disposé dans le logement de palier (116, 118, 82),
    dans lequel du lubrifiant est amené au logement de palier (116, 118, 82) par un système de distribution de lubrifiant (104), et une unité de dosage de lubrifiant (152, 154) est associée au logement de palier (116, 118, 82),
    caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) présente une chambre de logement de filtre (182), et qu'un corps filtrant (184) est disposé dans la chambre de logement de filtre (182).
  2. Compresseur à réfrigérant selon la revendication 1, caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) présente un canal d'arrivée (186), lequel s'étend depuis la chambre de logement de filtre (182) jusqu'à une chambre de lubrifiant (142, 144, 252, 254) jouxtant le palier à roulement (112, 114, 202).
  3. Compresseur à réfrigérant selon la revendication 1 ou 2, caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) présente un alésage d'étranglement (194) disposé entre la chambre de logement de filtre (182) et une chambre de lubrifiant (142, 144, 252, 254) jouxtant le palier à roulement (112, 114, 202).
  4. Compresseur à réfrigérant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) est intégrée dans le logement de palier (116, 118, 82).
  5. Compresseur à réfrigérant selon la revendication 4, caractérisé en ce que le logement de palier (116, 118, 82) présente un élément de logement (136, 138, 242, 244), dans lequel l'unité de dosage de lubrifiant (152, 154) est disposée.
  6. Compresseur à réfrigérant selon la revendication 5, caractérisé en ce que l'élément de logement est un couvercle de logement de palier (136, 138) du logement de palier (116, 118).
  7. Compresseur à réfrigérant selon la revendication 5, caractérisé en ce que l'élément de logement est un anneau de logement de palier (242, 244) du logement de palier (82).
  8. Compresseur à réfrigérant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) amène le lubrifiant à la chambre de lubrifiant (142, 144, 252, 254) .
  9. Compresseur à lubrifiant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'unité de dosage de lubrifiant (152, 154) est pourvue d'un alésage de buse (196) disposé en aval de la chambre de logement de filtre (182), lequel génère un jet de lubrifiant (198) dirigé sur le palier à roulement (112, 114, 202) dans le logement de palier (116, 118, 82).
  10. Compresseur à réfrigérant selon la revendication 9, caractérisé en ce que l'alésage de buse (196) agit simultanément en tant qu'alésage d'étranglement de l'unité de dosage de lubrifiant (152, 154) .
  11. Compresseur à réfrigérant selon l'une quelconque des revendications précédentes, caractérisé en ce que l'élément de compresseur est un rotor à vis (26, 28) d'un compresseur à vis.
EP14730912.4A 2013-06-18 2014-06-17 Compresseur de liquide de refroidissement Active EP3011181B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013106344.6A DE102013106344B4 (de) 2013-06-18 2013-06-18 Kältemittelverdichter
PCT/EP2014/062729 WO2014202611A1 (fr) 2013-06-18 2014-06-17 Compresseur de liquide de refroidissement

Publications (2)

Publication Number Publication Date
EP3011181A1 EP3011181A1 (fr) 2016-04-27
EP3011181B1 true EP3011181B1 (fr) 2020-02-26

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP14730912.4A Active EP3011181B1 (fr) 2013-06-18 2014-06-17 Compresseur de liquide de refroidissement

Country Status (6)

Country Link
US (1) US10508839B2 (fr)
EP (1) EP3011181B1 (fr)
CN (1) CN105283669B (fr)
DE (1) DE102013106344B4 (fr)
RU (1) RU2659420C2 (fr)
WO (1) WO2014202611A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107002679B (zh) * 2014-12-17 2019-12-13 开利公司 具有油关闭阀的螺杆压缩机和方法
US20170022984A1 (en) * 2015-07-22 2017-01-26 Halla Visteon Climate Control Corp. Porous oil flow controller
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RU2016101119A (ru) 2017-07-24
RU2659420C2 (ru) 2018-07-02
DE102013106344A1 (de) 2014-12-18
DE102013106344B4 (de) 2015-03-12
CN105283669B (zh) 2018-04-03
WO2014202611A1 (fr) 2014-12-24
US10508839B2 (en) 2019-12-17
US20160097572A1 (en) 2016-04-07
EP3011181A1 (fr) 2016-04-27
CN105283669A (zh) 2016-01-27

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