EP4062067B1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP4062067B1
EP4062067B1 EP19805654.1A EP19805654A EP4062067B1 EP 4062067 B1 EP4062067 B1 EP 4062067B1 EP 19805654 A EP19805654 A EP 19805654A EP 4062067 B1 EP4062067 B1 EP 4062067B1
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EP
European Patent Office
Prior art keywords
pressure chamber
scroll
scroll compressor
compressor according
venturi nozzle
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
EP19805654.1A
Other languages
German (de)
English (en)
Other versions
EP4062067A1 (fr
Inventor
Hans Gerards
Lukas LÖHMER
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.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
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Filing date
Publication date
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP4062067A1 publication Critical patent/EP4062067A1/fr
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Publication of EP4062067B1 publication Critical patent/EP4062067B1/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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a scroll compressor with a high-pressure chamber and a low-pressure chamber, an orbiting displacement spiral arranged on a driven eccentric unit, which engages in a fixed spiral, the displacement spiral and the fixed spiral delimiting a compression chamber, and a counter-pressure chamber adjacent to the displacement spiral, which via a gas connection channel is fluidly connected to the high-pressure chamber and is fluidly connected to the compression chamber via a fluid passage provided on the displacement spiral.
  • Such scroll compressors are from the prior art, for example from DE 10 2017 105 175 B3 , well known and include a high pressure chamber, a low pressure chamber and an orbiting displacement spiral.
  • the orbiting displacement spiral engages with a fixed spiral in such a way that a compression chamber is formed between the displacement spiral and the fixed spiral.
  • a counter-pressure chamber is provided between the low-pressure chamber and the displacement spiral, with a pressure prevailing in the counter-pressure chamber which acts on the orbiting displacement spiral.
  • the pressure prevailing in the counter-pressure chamber and acting on the displacement spiral causes a resulting force in the axial direction, whereby the at least slightly axially movable displacement spiral is pressed against the fixed spiral and the spirals are thus sealed from one another.
  • the pressure prevailing in the counter-pressure chamber is adjusted in such a way that the counter-pressure chamber is connected to the gas connection channel via a gas connection channel
  • High pressure chamber is fluidly connected and is fluidly connected to the compression chamber via a fluid passage which is provided on the orbiting displacement spiral.
  • the pressure prevailing in the counter-pressure chamber is established as a function of the pressure prevailing in the compression chamber. In this way, a contact pressure between the displacement spiral and the fixed spiral required for the tightness of the arrangement can be adjusted depending on the pressure acting in the compression chamber, thereby avoiding too high a contact pressure, which would lead to a loss in performance of the scroll compressor.
  • a lubricating oil is added to the fluid to be compressed.
  • the fluid-oil mixture is also present after compression and is conveyed into the counter-pressure chamber via the gas connection channel.
  • the disadvantage of this is that the oil collects in the counter-pressure chamber and too high a proportion of oil in the counter-pressure chamber causes an undesirable pressure change in the counter-pressure chamber. Such an undesirable pressure change leads to a leak between the displacement scroll and the fixed scroll, which reduces the efficiency of the scroll compressor.
  • the task is therefore to provide a scroll compressor with a counter-pressure chamber which can be operated reliably with a high degree of efficiency.
  • a Venturi nozzle is provided in the fluid passage, which has at least one transverse opening at its constriction, the transverse opening being fluidly connected to the counter-pressure chamber, so that a suction jet pump is created, oil suction from the counter-pressure chamber is effected, whereby a through a Undesirable pressure changes in the counter-pressure chamber caused by too high an oil content can be reliably prevented and a reduction in the efficiency of the scroll compressor can be reliably prevented.
  • Oil extraction from the counter-pressure chamber occurs by accelerating the fluid flow flowing through the fluid passage through the constriction of the venturi nozzle, with the increase in flow velocity leading to an increase in dynamic pressure and a reduction in static pressure.
  • the reduced static pressure and thus the negative pressure prevailing in the counter-pressure chamber causes the oil accumulated in the counter-pressure chamber to flow from the counter-pressure chamber through the transverse opening into the Venturi nozzle.
  • the oil is carried along by the fluid flow between the counter-pressure chamber and the compression chamber and is blown into the compression chamber. Starting from the compression chamber, the fluid flows into the high-pressure chamber.
  • the transverse opening is fluidly connected to the counter-pressure chamber via a flow channel, the flow channel being provided on the displacement spiral.
  • the flow channel preferably opens into the counter-pressure chamber at the lowest point of the displacement spiral. This allows the oil accumulated at the lowest point of the counter-pressure chamber to be reliably sucked out of the counter-pressure chamber.
  • the Venturi nozzle has a plurality of transverse openings, which are arranged distributed over the circumference, whereby the oil sucked out of the counter-pressure chamber is uniform Fluid flow channel can be supplied to the Venturi nozzle and can be entrained in it.
  • the Venturi nozzle preferably has an annular groove on the outer peripheral surface, the annular groove being fluidly connected to the transverse bores.
  • the annular groove together with a peripheral surface of the displacement spiral adjacent to the Venturi nozzle, delimits an annular channel through which the extracted oil can flow reliably and evenly to all transverse bores.
  • the fluid passage is arranged in a web area of the displacement spiral.
  • the web area is provided on the side facing away from the fixed spiral and between two adjacent guide openings, with a guide pin attached to the compressor housing engaging in each of the guide openings.
  • the orbiting displacement spiral is guided by the guide pins engaging in the guide openings and rotation of the displacement spiral is prevented.
  • other recesses can also be provided on the displacement spiral, which are separated from one another by a web.
  • the Venturi nozzle has a certain length, and by arranging the fluid passage in the web area, the Venturi nozzle can be arranged completely within the displacement spiral. Furthermore, the web area can be thickened in order to have sufficient strength of the web area despite the passage of fluid.
  • the Venturi nozzle is preferably pressed into the passage, whereby the Venturi nozzle can be attached to the displacement spiral inexpensively, quickly and reliably.
  • the fluid passage has two adjoining axial sections, the axial sections have different diameters from one another, with the Venturi nozzle resting on the front side on a radial shoulder between the two axial sections.
  • the transverse opening preferably has a diameter of 0.5 to 1.0 mm.
  • at least the transverse opening is produced by a laser process.
  • the transverse opening with a relatively small diameter can be produced in a simple and reliable manner by the laser process.
  • an inlet of the gas connection channel is arranged in front of an oil separator in the flow direction of a compressed fluid.
  • the oil separator serves to separate the lubricating oil from the fluid introduced into a cooling circuit.
  • the high-pressure chamber is fluidly connected to the low-pressure chamber via an oil return channel.
  • the oil guide channel serves to return the lubricating oil released from the fluid, with the oil being separated from the gas by the oil separator.
  • the separated oil collects at the lowest point in the high-pressure chamber, with the oil return channel extending from the lowest point in the high-pressure chamber to the low-pressure chamber.
  • a throttle is provided in the oil return channel, which controls the oil return flow to the low-pressure chamber.
  • a scroll compressor which has a counter-pressure chamber that is fluidly connected to the high-pressure chamber via the gas connection channel and to the compression chamber via a fluid passage provided on the displacement spiral, with oil accumulation in the counter-pressure chamber being prevented by a Venturi nozzle arranged in the fluid passage
  • the Venturi nozzle uses the principle of a suction jet pump to extract oil from the counter-pressure chamber.
  • FIG. 1 shows a scroll compressor 2.
  • the scroll compressor 2 comprises a multi-part compressor housing 10 with a first compressor housing part 12, a second compressor housing part 14 which adjoins the first compressor housing part 12 axially and a third compressor housing part 16 which adjoins the second compressor housing part 14.
  • the first compressor housing part 12, which second compressor housing part 14 and the third compressor housing part 16 delimit an engine compartment 18.
  • the second compressor housing part 14 and the third compressor housing part 16 delimit a compressor compartment 20.
  • An electric motor 22 with a stator 24 and a rotor 26 is arranged in the engine compartment 18.
  • the rotor 26 is attached to a rotor shaft 28.
  • the rotor shaft 28 extends from the engine compartment 18 through a central opening 29 of the second compressor housing part 14 into the compressor chamber 20.
  • the rotor shaft 28 is rotatably mounted in two shaft bearings 40, 42 via two end-side shaft bearing sections 30, 34 about a rotor shaft rotation axis.
  • the first shaft bearing 40 is arranged in the engine compartment 18 and supports the first shaft bearing section 30.
  • the second shaft bearing 42 is arranged in the compressor compartment 20 and supports the second shaft bearing section 34.
  • a shaft sealing ring 43 is provided on the side of the second shaft bearing 42 facing the engine compartment 18 , which rests on the radial inside of the rotor shaft 28 and is supported on the radial outside by the second compressor housing part 14.
  • the shaft sealing ring 43 fluidly seals the engine compartment 18 from the compressor compartment 20.
  • a compressor unit 58 is arranged in the compressor chamber 20 and has an orbiting displacement spiral 60 and a fixed spiral 62, the orbiting displacement spiral 60 and the fixed spiral 62 delimiting a compression chamber 61.
  • the orbiting displacement spiral 60 is arranged via an eccentric shaft bearing 64 on an eccentric unit 50 attached to the rotor shaft 28.
  • the fixed scroll 62 is fixedly arranged in the compressor housing 10, with the fixed scroll 62 being axially supported by the second compressor housing part 14 and the third compressor housing part 16.
  • the refrigerant is introduced into the engine compartment 18 of the scroll compressor 2 through a compressor inlet 85, with the refrigerant flowing through the engine compartment 18 into the compressor compartment 20 and the compression chamber 61.
  • a compressor inlet 85 By rotating the rotor shaft 28 and thus the eccentric unit 50 around the rotor axis of rotation, an orbiting movement of the displacement spiral 60 is generated.
  • the orbiting displacement spiral 60 and the fixed spiral 62 are designed in such a way that the orbiting movement of the displacement spiral 60 a refrigerant is conveyed from a radially external inlet 66 of the compression chamber 61 to a radially internal outlet 68 of the compression chamber 61 and is thereby compressed.
  • the compressor chamber 20 has a high-pressure chamber 80 and a counter-pressure chamber 82.
  • the high-pressure chamber 80 is delimited by the third compressor housing part 16 and by the fixed spiral 62 and is fluidly arranged between the outlet 68 and a compressor outlet 84, with the refrigerant flowing from the outlet 68 via the high-pressure chamber 80 to the compressor outlet 84.
  • the refrigerant flows into a coolant circuit of a motor vehicle.
  • the high-pressure chamber 80 has an oil separation chamber 86, which is fluidly arranged immediately in front of the compressor outlet 84 and has an oil separator 88.
  • the oil separator 88 is designed as a cyclone separator, with the refrigerant flowing through the oil separator 88 to the compressor outlet 84 and the oil released from the refrigerant settling at the bottom of the oil separation chamber 86, i.e. at the lowest point of the high-pressure chamber 80.
  • an inlet 89 of an oil return channel 90 is provided at the bottom of the oil separation chamber 86, which fluidly connects the oil separation chamber 86 and thus the high-pressure chamber 80 with a low-pressure chamber 87, the engine compartment 18 forming the low-pressure chamber 87.
  • the oil return channel 90 extends through the third compressor housing part 16, the fixed spiral 62 and through the second compressor housing part 14, with a filter 130 being arranged in the oil return channel 90.
  • the counter-pressure chamber 82 is delimited by the second compressor housing part 14 and the orbiting displacement spiral 60, the pressure prevailing in the counter-pressure chamber 82 acting on the axially displaceable, orbiting displacement spiral 60 and resulting in an axial load the displacement spiral results.
  • This axial load leads to an improved seal between the end faces of the orbiting displacement spiral 60 and the fixed spiral 62.
  • the counter-pressure chamber 82 is fluidly connected to the high-pressure chamber 80 via a gas connection channel 100.
  • the gas connection channel 100 runs from the high-pressure chamber 80 through the fixed spiral 62 and through the second compressor housing part 14. Furthermore, the counter-pressure chamber 82 is fluidly connected to the compression chamber 61 via a fluid passage 70.
  • a Venturi nozzle 71 is arranged in the fluid passage 70, the Venturi nozzle 71 having a plurality of transverse bores 741, 742 at its constriction 72, which are fluidly connected to the counter-pressure chamber 82 via a flow channel 78.
  • the Venturi nozzle 71 is in Figure 2 shown.
  • the transverse bores 741, 742 extend radially and are fluidly connected to one another via an annular channel 76 provided on the outer peripheral surface of the Venturi nozzle 71, the annular channel 76 being fluidly connected to the counter-pressure chamber 82 via the flow channel 78.
  • the annular channel 76 is delimited by a circumferential annular groove 77 made on the outer peripheral surface of the Venturi nozzle 71 and by a surface of the displacement spiral 60 that rests on the outer peripheral surface.
  • the Venturi nozzle 71 is, as in Figure 3 shown, arranged in a thickened web region 114 on a side of the displacement spiral 60 facing away from the fixed spiral 62, the web region 114 being formed between two recesses 110, 112 provided on the displacement spiral 60.
  • the circular recess 110 is a guide opening for guiding the displacement spiral 60 during operation of the scroll compressor 2, with a guide pin attached to the compressor housing 10 and not shown in the figures engaging in each guide opening 110.
  • the recess 112 is a cavity to reduce the weight of the displacement spiral 60.
  • the fluid passage 70 When assembling the Venturi nozzle 71, it is pressed into the fluid passage 70, the fluid passage 70 having two axial sections 731, 732.
  • the first axial section 731 has a diameter corresponding to the outer peripheral surface of the Venturi nozzle 71 and a length corresponding to the Venturi nozzle 71.
  • the second axial section 732 has a smaller diameter compared to the first axial section 731, as a result of which there is a radially extending shoulder 79 between the two axial sections 731, 732.
  • the Venturi nozzle 71 works on the principle of a suction jet pump and is used to remove an oil from the counter-pressure chamber 82, the oil together with the fluid, which is conveyed from the high-pressure chamber 80 into the counter-pressure chamber 82, via the gas connection channel 100 into the counter-pressure chamber 82 flows in and settles in the counter-pressure chamber 82.
  • a proportion of oil that is too high leads to a reduction in the contact pressure between the displacement spiral 60 and the fixed spiral 62, as a result of which the efficiency of the scroll compressor 2 is impaired.
  • the oil is removed from the counter-pressure chamber 82 by the fluid mass flow occurring during operation of the scroll compressor 2 through the fluid passage 70 is accelerated by the constriction 72 of the Venturi nozzle 71, whereby the static pressure in the area of the constriction 72 drops and a negative pressure is created relative to the counter-pressure chamber 82.
  • the negative pressure also exists in the transverse bores 741, 742, with the oil deposited at the bottom of the counter-pressure chamber 82 flowing to the Venturi nozzle 71 through the negative pressure via the flow channel 78.
  • the oil is entrained by the fluid flowing through the Venturi nozzle 71 and blown into the compression chamber 61. Starting from the compression chamber 61, the oil flows into the high-pressure chamber 80.
  • a scroll compressor 2 is thus created, which reliably prevents the oil from accumulating in the counter-pressure chamber 82.

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

Claims (11)

  1. Compresseurs à spirales avec
    une chambre haute pression (80) et une chambre basse pression (87),
    une spirale de déplacement (60) disposée et orbitante sur une unité excentrique entraînée (50), qui s'engage dans une spirale fixe (62), la spirale de déplacement (60) et la spirale fixe (62) délimitant une chambre de compression (61), et
    une chambre de contre-pression (82) adjacente à la spirale de déplacement (60), qui est reliée fluidiquement à la chambre haute pression (80) par un canal de connexion de gaz (100) et qui est reliée fluidiquement à la chambre de compression (61) par un passage de fluide (70) prévu sur la spirale de déplacement (60),
    caractérisé en ce que
    dans le passage de fluide (70) est prévu une buse Venturi (71) qui comprend au niveau de son rétrécissement (72) au moins une ouverture transversale (741, 742), l'ouverture transversale (741, 742) étant en liaison fluidique avec la chambre de contre-pression (82).
  2. Compresseur à spirales selon la revendication 1,
    caractérisé en ce que
    l'ouverture transversale (741, 742) est en communication fluidique avec la chambre de contre-pression (82) par l'intermédiaire d'un canal d'écoulement (78), le canal d'écoulement (78) étant prévu sur la spirale de déplacement (60).
  3. Compresseur à spirales selon la revendication 2,
    caractérisé en ce que
    le canal d'écoulement (78) débouche dans la chambre de contre-pression (82) au point le plus bas de la spirale de déplacement (60).
  4. Compresseur à spirales selon l'une des revendications précédentes, caractérisé en ce que
    la buse de Venturi (71) comprend plusieurs ouvertures transversales (741, 742) réparties sur la circonférence.
  5. Compresseur à spirales selon la revendication 4,
    caractérisé en ce que
    la buse de Venturi (71) comprend une rainure annulaire (77) sur la surface périphérique extérieure, la rainure annulaire (77) étant en connexion fluidique avec les ouvertures transversales (741, 742).
  6. Compresseur à spirales selon l'une des revendications précédentes, caractérisé en ce que
    le passage de fluide (70) est disposé dans une zone d'âme (114) de la spirale de déplacement (60).
  7. Compresseur à spirales selon l'une des revendications précédentes, caractérisé en ce que
    la buse de Venturi (71) est pressée dans le passage de fluide (70).
  8. Compresseur à spirales selon l'une des revendications précédentes, caractérisé en ce que
    le passage de fluide (70) comprend deux tronçons axiaux (731, 732) se raccordant l'un à l'autre, les tronçons axiaux (731, 732) comprenant des diamètres différents l'un de l'autre, la buse Venturi (71) étant en appui frontal sur un épaulement radial (79) entre les deux tronçons axiaux (731, 732).
  9. Compresseur à spirales selon l'une des revendications précédentes, caractérisé en ce que
    l'ouverture transversale (741, 742) comprend un diamètre de 0,5 à 1,0 mm.
  10. Compresseur à spirales selon l'une des revendications précédentes,
    caractérisé en ce que
    une entrée du canal de connexion de gaz (100) est située en amont d'un séparateur d'huile (88) dans le sens d'écoulement d'un fluide comprimé.
  11. Compresseur à spirales selon l'une des revendications précédentes,
    caractérisé en ce que
    la chambre haute pression (80) est en communication fluidique avec la chambre basse pression (87) par l'intermédiaire d'un canal de retour d'huile (90).
EP19805654.1A 2019-11-18 2019-11-18 Compresseur à spirales Active EP4062067B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2019/081644 WO2021098941A1 (fr) 2019-11-18 2019-11-18 Compresseur à spirales

Publications (2)

Publication Number Publication Date
EP4062067A1 EP4062067A1 (fr) 2022-09-28
EP4062067B1 true EP4062067B1 (fr) 2023-11-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19805654.1A Active EP4062067B1 (fr) 2019-11-18 2019-11-18 Compresseur à spirales

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EP (1) EP4062067B1 (fr)
WO (1) WO2021098941A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06193570A (ja) * 1992-12-25 1994-07-12 Hitachi Ltd 密閉形スクロール圧縮機
JP2003097457A (ja) * 2001-09-19 2003-04-03 Hitachi Ltd スクロール圧縮機
JP5272031B2 (ja) * 2011-03-10 2013-08-28 日立アプライアンス株式会社 スクロール圧縮機
DE102017105175B3 (de) 2017-03-10 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Verdrängerspirale, Fahrzeugklimaanlage und Fahrzeug
CN109185131A (zh) * 2018-10-29 2019-01-11 珠海凌达压缩机有限公司 涡旋压缩机、空调及车辆

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WO2021098941A1 (fr) 2021-05-27
EP4062067A1 (fr) 2022-09-28

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