WO2018197458A1 - Compresseur - Google Patents

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Publication number
WO2018197458A1
WO2018197458A1 PCT/EP2018/060426 EP2018060426W WO2018197458A1 WO 2018197458 A1 WO2018197458 A1 WO 2018197458A1 EP 2018060426 W EP2018060426 W EP 2018060426W WO 2018197458 A1 WO2018197458 A1 WO 2018197458A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
fluid
separator
chamber
wall
Prior art date
Application number
PCT/EP2018/060426
Other languages
German (de)
English (en)
Inventor
Budi Rinaldi
Björn FAGERLI
Original Assignee
Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg
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 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg filed Critical Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg
Priority to KR1020197032880A priority Critical patent/KR20190129132A/ko
Priority to JP2019557615A priority patent/JP2020517858A/ja
Priority to CN201880027497.2A priority patent/CN110582644A/zh
Priority to US16/608,564 priority patent/US20200191146A1/en
Publication of WO2018197458A1 publication Critical patent/WO2018197458A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture 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
    • 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
    • F04C29/02—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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2240/40—Electric motor
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/98—Lubrication

Definitions

  • the invention relates to a compressor for compressing a fluid, having a compressor part mounted in a compressor housing for conveying the fluid from a low-pressure side inlet to a high-pressure side outlet.
  • a compressor is understood to be, in particular, a refrigerant compressor, preferably an electromotive compressor, for an air conditioning system of a motor vehicle.
  • an air conditioning system is installed regularly, which can cool the vehicle interior in the manner of a compression refrigeration machine.
  • a refrigerant such as R-134a (1, 1, 1, 2-tetrafluoroethane) or R-774 (CO2) is performed.
  • the refrigerant is compressed by means of a compressor or compressor, which leads to a pressure and temperature increase of the refrigerant.
  • the compressor is operated by an electric motor.
  • the (refrigerant) compressor downstream of a condenser which is in thermal contact with the environment of the vehicle. As a result, takes place in the condenser, a temperature decrease of the refrigerant, which is then passed into a fluidically downstream evaporator. In the evaporator, the refrigerant is released to the original pressure, which is why the temperature of the refrigerant is further lowered.
  • the evaporator is downstream of another heat exchanger, which is in thermal contact with a fan line of the air conditioner stands, which leads into the interior of the vehicle.
  • thermal energy is transferred from the thermally contacted component to the refrigerant, which leads to a cooling of the component and a heating of the refrigerant.
  • the refrigerant is supplied to the compressor again.
  • a first low-pressure side compressor element of a compressor part and a fixed second high-pressure side compressor element of the compressor part for compressing the fluid and a high-pressure chamber and a separator are arranged one behind the other in the flow direction.
  • a lubricant that mixes with the gaseous refrigerant during operation.
  • the lubricant serves to reduce friction which occurs during operation in the compressor between the first compressor element and the second, fixed high-pressure side compressor element.
  • the lubricant fulfills a sealing function, so that any (refrigerant) leaks arising between the compressor elements are largely reduced or completely avoided, which increases the efficiency of the refrigerant compressor.
  • the refrigerant mixed with lubricant flows compressedly in the compressor from the compressor part into a high-pressure chamber, which in turn is coupled to the separation device by means of a through-passage.
  • the oil is separated from the refrigerant, so that the separated oil is or can be recycled to the compressor via a valve and a lubricant channel and the refrigerant is passed on to the refrigerant circuit via an outlet of the separating device as oil-free as possible.
  • the separation device has a deposition chamber connected to the outlet and a coaxially arranged separator, so that an annular space is formed between the separator and an inner wall of the deposition chamber.
  • the passage of the separator is designed as a round hole, wherein the fluid from the high-pressure chamber via the passage in the annulus of the deposition chamber flows.
  • the fluid flows through a flow cross section from the high-pressure chamber into the separation chamber which is adapted to the delivery volume occurring in accordance with the operation and which is determined by the clear width of the through-channel. Since the cross-sectional area of the flow cross-section must be adapted to the delivery volume occurring in accordance with the operation, the fluid flow branches into two partial streams, which are guided along opposite sides of the separator in opposite directions. This causes an undesirable vortex formation in the annulus between the separator and the chamber inner wall of the deposition chamber.
  • the invention has for its object to provide a particularly suitable compressor, wherein the funded fluid flows through the deposition chamber with the least possible vortex formation.
  • the inventive device comprises a compressor for compressing a fluid, in particular a refrigerant, wherein the compressor is connected in a refrigerant circuit of an air conditioning fluidly between a heat exchanger and a condenser.
  • the compressor has the task to increase the pressure of the pumped fluid.
  • the compressor has a (compressor) housing with a housing bottom and a compressor part mounted in the housing for conveying the fluid from a low-pressure side inlet to a high-pressure side outlet.
  • a lubricant is present, which mixes in operation with the gaseous refrigerant. It serves to reduce friction in the compressor part and in its drive and performs a sealing function in the compressor part, by leaks between a first low-pressure side compressor element and a second fixed high pressure side compressor element as far as possible reduced or completely prevented.
  • the lubricant should be separated from the fluid before being transferred to the coolant circuit.
  • the oil collected and separated in a (lubricant) reservoir may be returned to the compressor section via a valve and lubricant passage, resulting in improved lubrication of the compressor elements and reducing friction in the compressor section.
  • Further advantageous by the separation of the lubricant from the fluid is an improved heat transfer to the heat exchanger of the refrigerant circuit, which increases the efficiency of the air conditioning (the air conditioning or air conditioning system).
  • a separation device for separating the lubricant contained in the fluid is introduced into the housing bottom, wherein the separation device has a cylindrical separator chamber connected to the outlet with a coaxially mounted therein separator.
  • the fluid flows out of the compressor part into a high-pressure chamber of the compressor housing downstream of this in terms of flow.
  • the high-pressure chamber is fluidly coupled by means of a through-passage in a common intermediate wall of the deposition chamber and the high-pressure chamber to the separation device.
  • the through-channel is introduced in such a way that it opens radially offset from the central center axis of the coaxially arranged in the deposition chamber and in particular cylindrical separator, which ensures a targeted guiding the flow along only one side of the separator.
  • the compressor is an electromotive refrigerant compressor for an air conditioning system of a vehicle.
  • the air conditioner is used, for example, to cool an interior of the vehicle or to cool an energy store for driving an electric motor-driven vehicle.
  • the heat exchanger is in thermal contact with any energy cells of a high-voltage energy storage or with a fan line, which leads into the interior of the motor vehicle.
  • there is a transfer of thermal energy to the refrigerant which leads to a cooling of the component in contact with the heat exchanger and to a heating of the refrigerant.
  • the condenser is used to match the temperature of the refrigerant to the ambient temperature or at least a decrease in the temperature of the refrigerant and is preferably in thermal contact with the environment.
  • the compressor part is designed as a scroll compressor.
  • This works as a refrigerant compressor in the manner of a positive displacement pump, wherein an electric motor eccentrically drives a movable scroll member with respect to a stationary scroll member, thereby compressing a fluid.
  • the scroll parts form the compressor elements of the compressor part and are hereby typically designed as a nested spiral or scroll pair.
  • one of the spirals is stationary with respect to the compressor housing and at least partially engages in a second, orbitally driven second spiral by means of an electric motor.
  • Under an orbiting motion is in this case in particular an eccentric circular trajectory to understand, in which the second spiral itself does not rotate about its own axis. This results in each orbital movement between the spirals, two substantially crescent-shaped refrigerant chambers whose volume in the course of the movement reduce (compress).
  • the refrigerant is discharged via an outlet in the fixed scroll part in the high-pressure chamber.
  • the lubricant is expediently a (lubricating) oil, the term oil not to be understood as limiting mineral oils. Rather, fully synthetic or semi-synthetic oils, such as silicone oils, or other oily liquids such as hydraulic fluid or coolants can be used.
  • the separation device separates the lubricant from the fluid in the manner of a centrifugal separator (cyclone separator).
  • the tangential in the deposition chamber inflowing fluid is guided helically (cyclone-like) along the separator in the particularly cylindrical deposition chamber. Centrifugal forces act on the mixture of refrigerant and lubricant as a separation mechanism.
  • the lubricant reservoir is partially closed with a cone to form a ring slot.
  • the compressor housing with housing bottom and the deposition chamber of the separator are formed by a pressure-casting process.
  • the through-channel is introduced into the intermediate wall between the separation chamber and the high-pressure chamber in such a way that the conveyed fluid flows tangentially to the separator into the separation chamber, whereby a particularly suitable positioning of the through-channel is provided.
  • the fluid flows under an angle, for example, less than 90 ° with respect to the housing bottom.
  • the passageway can be introduced into the intermediate wall such that the inflow direction of the fluid is perpendicular to the housing bottom, whereby the flow direction of the fluid through the passageway is substantially identical to the conveying direction of the fluid by means of the compressor part and less turbulence arises at the passageway.
  • the direction of inflow here means the direction tangential to the separator, in which the fluid flows into the precipitator chamber.
  • the invention is based on the consideration that the undesired vortex formation in the annular space between the separator and the chamber inner wall of the deposition chamber can be considerably reduced if the flow of the fluid selectively passes along only one side of the separator.
  • the passageway opening into the annular space should be positioned as completely as possible azimuthally offset from the diameter course of the separator.
  • the clear width of the passage channel does not exceed the gap width of an annular gap formed between the separator and an inner wall of the separator can.
  • the inside width of the through-channel is smaller than or equal to the gap width of the annular gap.
  • the passage channel has an inner wall which is oriented tangentially to the inflow direction of the fluid into the annular gap.
  • the inner wall of the passage channel is oriented parallel to the direction of flow of the fluid into the deposition chamber, which is why advantageously less turbulence arises when flowing in the passageway.
  • the cylindrical deposition chamber extends radially to the housing bottom of the suitable pot-shaped compressor housing.
  • the passage is elongated along this radial direction.
  • the flow cross-section formed by the inside width of the through-channel as the fluid flows from the high-pressure chamber into the separation chamber is adapted to the delivery volume of the fluid occurring during operation.
  • the flow cross-section formed by the clear surface of the passage channel of the high-pressure chamber in the deposition chamber should be adapted to the operating volume occurring according to volume and the inside diameter of the passage channel is preferably smaller than or equal to the gap width of the gap formed between the separator and the inner wall of the deposition chamber As a result, the passageway along the central center axis of the separator is elongated.
  • the through-channel is offset radially with respect to the center axis of the separation device or with respect to the center axis of the precipitator.
  • the offset including the clear width of the through-channel is advantageously smaller than or equal to the Radius of the cylindrical Abscheidekannnner.
  • a branch of a partial flow of the fluid is avoided, which would be guided along the separator in the direction opposite to the eddy-free flow Umströmungssinn, would collide with the eddy-free path and would lead to the formation of vortices.
  • the passage is particularly advantageous slot-like recess of the partition.
  • the shape of the passage channel has, in an expedient embodiment, essentially a rectangular cross-sectional shape.
  • the cross-sectional shape of the through-channel is elliptical or oval.
  • the shape of the passage channel is the operating flow rate adjusted so that the passage only changes its inside width along the axis of the deposition chamber.
  • the through-channel between the deposition chamber and the high-pressure chamber is adapted to the operating volume of the refrigerant required in such a way that the pumped fluid flows through the separation chamber with only slight vortex formation.
  • the separation chamber is formed between an inner wall of the housing bottom facing the compressor part and the high-pressure chamber, the deposition chamber projecting at least partially axially into the high-pressure chamber.
  • the housing bottom has an annular wall which axially overhangs the deposition chamber, forming an inner and an outer annular region.
  • the through-passage from the high-pressure chamber into the separation chamber is arranged radially offset in the inner ring region in the direction of the outlet, so that the fluid flow is particularly advantageously along a Cyclone-like path is guided around the separator of the deposition chamber. In particular, this achieves improved separation of the lubricant from the refrigerant.
  • the compressor part suitably rests on the annular wall.
  • the high-pressure chamber is formed by the housing bottom and the annular wall and by the compressor part.
  • additional, sealing elements of the high pressure chamber are not necessary, which is space-saving and fluidic particularly advantageous.
  • the advantages achieved by the invention are in particular that the vortex formation of the fluid flow in the deposition chamber is considerably reduced by the particularly suitable arrangement and design of the through-channel, taking into account the required delivery volume.
  • the cross-sectional shape of the through-channel is adapted such that for the purpose of advantageous Einström s the clear width of the through-channel does not exceed the gap width of the annular space formed between the separation chamber and the separator (annular gap) and is advantageously elongated along the axis of the deposition chamber.
  • the lubricant separates from the refrigerant improved and is not forwarded in the refrigerant circuit, which is why there is better heat transfer between the heat exchangers and the refrigerant in the refrigerant circuit. Furthermore, due to the improved separation, the lubrication of the compressor part is improved by the separated and recycled lubricant, resulting in a reduced wear and thus an increased life of the compressor follows. In addition, the efficiency of the compressor is improved.
  • Show: 1 shows a longitudinal section of a compressor with a housing and with a compressor part and housing bottom side of a separation device
  • Fig. 2 in a plan view of the compressor housing with a view of the bottom side
  • Fig. 3 is a sectional view taken along the line III-III in Figure 2, the separator and the flow path of a fluid through the passageway and in the separator, and
  • Fig. 4 shows the sectional view of Fig. 3 with the center axis of the separator offset passage and without the flow path of the fluid in the separator.
  • the illustrated in Fig. 1 in a sectional view of compressor 2 for compressing a fluid F is preferably installed as an electromotive refrigerant compressor in a refrigerant circuit, not shown, an air conditioning system of a motor vehicle.
  • the compressor 2 has a compressor housing 4 with a housing bottom 6 and a compressor part 8 mounted in the housing 4.
  • the compressor part 8 has a first, with respect to the compressor housing 4 fixed compressor element 8a and a therein engaging movable second compressor element 8b, which is moved by means of shaft 10 and a motor shaft 12 by an electric motor, not shown.
  • the compressor part 8 is designed here as a scroll compressor.
  • a lubricant S which serves to lubricate the compressor part 8 and which fulfills a sealing function, so that leaks are avoided between the compressor elements 8a and 8b.
  • a refrigerant K and the lubricant S mix to the fluid F.
  • the compressor housing 4 is executed pot-shaped. The radial direction with respect to the compressor housing 4 and the axial direction perpendicular to the housing bottom 6 in the direction of the compressor part 8 are denoted by R and A in the adjacent directional diagram.
  • a separation device 14 is introduced, which is connected to an outlet 16.
  • the separation device 14 has a cylindrical separation chamber 18 and a hollow cylindrical separator 20 arranged coaxially therein.
  • the separation device 14 serves to separate the lubricant S contained in the fluid F into a lubricant reservoir 26 in the manner of a centrifugal separator.
  • the fluid F flowing in via a through-passage 27 into the separation chamber 18 with an inflow direction E (FIG. 3) flows around the separator 20 in the separation chamber 18 helically (cyclone-like) in the direction of the lubricant reservoir 26, the fluid K and K contained in the fluid F. acting on the lubricant contained in the fluid S lubricant centrifugal force acts as a separation mechanism.
  • the refrigerant K separated from the lubricant S flows through the hollow cylindrical separator 20 and the outlet 16 into the refrigerant circuit.
  • the direction of inflow E is understood to mean the direction tangential to the separator 20, in which the fluid F flows into the precipitator chamber 18.
  • the separated lubricant S is returned via a valve or a throttle 28 and via a lubricant channel 30 to the stationary compressor element 8b.
  • the throttle 26 is seated in the compressor housing 4 a.
  • the recycled lubricant S then flows through guide contours to bearings 32 of the electric motor, not shown, in order to lubricate and / or to cool.
  • the radial direction of the separation device 14 perpendicular to the inflow direction E and the radial direction of the separation device 14 parallel to the inflow direction E are denoted by Y and Z, respectively (FIG. 2).
  • the housing bottom 6 has a separating wall 18 superior annular wall 34. This divides the space encompassed by the stationary compressor part 8b and the compressor housing 4 into an inner annular region 36 and an outer annular region 38.
  • a high - pressure chamber 40 is formed from the inner annular region 36, bounded by the housing bottom 6, the annular wall 34 and on the Ring wall 34 resting compressor element 8b formed.
  • the deposition chamber 18 is formed between an inner wall 41 of the housing bottom 6 and the high pressure chamber 40, wherein the deposition chamber 18 projects at least partially in the axial direction A in the high pressure chamber 40.
  • the through-channel 27 fluidly couples the high-pressure chamber 40 with the separation chamber 18.
  • the through-channel 27 is introduced into an intermediate wall 44 between the separation chamber 18 and the high-pressure camera 40 such that the through-channel 27 is displaced along the radial direction Y of the separation device 14 to the axial direction X of the separation device 14 opens into the deposition chamber 18.
  • the passage 27 in the inner ring portion 36 of the annular wall 34 is arranged such that the passage 27 is offset in the axial direction X of the separator 14 and in the radial direction R of the compressor housing 4 to the outlet.
  • the fluid F flows on the low-pressure side of the compressor part 8 through an inlet 46 into the compressor part 8.
  • the compressor part 8 which is a scroll compressor here, compresses the fluid F in the manner of a positive displacement pump.
  • the fluid F is compressed in a compressor sub-chamber 47 and then flows out of the compressor part 8 through a high pressure-side compressor part outlet 48 into the high-pressure chamber 40.
  • FIG. 2 shows the cup-shaped compressor housing 4 with the compressor part 8 removed, viewed along the axial direction A on the housing bottom 6 of the compressor housing 4.
  • the annular wall 34 projects beyond the separating device 14 to form the inner annular region 36 and the outer annular region 38 not shown compressor part 8 and the housing bottom 6 of the compressor housing 4, the annular wall 34 forms the high-pressure chamber 40th
  • the compressor housing 4 has, along a flange surface 49, screw receptacles 50 for fastening the compressor 2 to a drive module, not shown, in which the motor of the compressor 2 is introduced.
  • screw receptacles 50 for fastening the compressor 2 to a drive module, not shown, in which the motor of the compressor 2 is introduced.
  • only two screw receptacles 50 are provided with a reference numeral in FIG.
  • the passage chamber 18 extends in the radial direction R to the housing bottom 6 of the compressor housing 4.
  • the passage 27 is offset in the inner ring portion 36 in the radial direction R to the outlet 16 of the deposition chamber 18 and along the axial direction X of the separator 14 elongated.
  • the passage 27 is designed as a slot-like recess of the intermediate wall 44, wherein the recess has a substantially rectangular cross-sectional shape.
  • the cross-sectional shape of the through channel 27 may be executed slot-like or oval.
  • Fig. 3 shows in a sectional view taken along the line III-III in Fig. 2 introduced in the housing bottom 6 of the compressor housing 4 separating device 14 with a view of the radially offset passage 27. This can be seen in the intermediate wall 44 between the high-pressure chamber 40 and the deposition chamber 18th positioned so that the conveyed fluid F flows tangentially to the separator 20 with the inflow direction E in the deposition chamber 18.
  • the through-channel 27 has an inner wall 55, which is oriented tangentially to the inflow direction E of the fluid F in the through-channel 27.
  • the fluid F flows into the separation chamber 18 such that both the inflow direction E and the inner wall 55 of the through-channel 27 are oriented perpendicular to the housing bottom 6.
  • the opposite side of the inner wall 55 of the through-channel 27 is designated 55b (off-axis side).
  • the flow cross-section formed by the clear surface of the through-channel 27 when the fluid F flows from the high-pressure camera 40 into the separation chamber 18 is adapted to the delivery volume required according to the operation.
  • the passage 27 is adapted to the correspondingly required delivery volume such that the inside diameter a of the passage 27 is preferably smaller than the gap width b (a ⁇ b) between the separator 20 and an inner wall 56 of the deposition chamber 18 formed annular gap 58 is.
  • the passage 27 is elongated along the axial direction X of the separator 14.
  • the fluid F flows tangentially into the annular gap 58 and only one side of the separator 20 along a vortex-free path 60.
  • Fig. 4 shows in the sectional view of FIG. 3, the introduced in the housing base 6 separating device 14 with the passage 27 with the clear width a and the gap formed by the inner wall 56 of the deposition chamber 18 and the separator 20 with the gap width b.
  • the fluid F flows tangentially into the annular gap 58 formed between the separator 20 and the inner wall 56 of the deposition chamber 18.
  • the fluid F is consequently guided selectively only on one side of the precipitator 20 along a vortex-free path 60 (FIG. 3).
  • the offset c is the distance between the radial direction Z of the separator 14 parallel to the inflow direction E and the central axis X facing side 55a of the inner wall 55 of the through-channel 27.

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

Abstract

L'invention concerne un compresseur (2), en particulier un compresseur de réfrigérant à moteur électrique, pour la compression d'un fluide (F), comprenant un boîtier de compresseur (4) avec un fond de boîtier (6), et comprenant un élément de compression (8) monté dans le boîtier (4) pour l'acheminement du fluide (F) d'une entrée côté basse pression (46) vers une sortie côté haute pression (16), un dispositif de séparation (14) étant placé dans le fond de boîtier (6), lequel comprend une chambre de séparation cylindrique (18) connectée à la sortie (16) et un séparateur (20) disposé coaxialement dans celle-ci pour la séparation des lubrifiants (24) contenus dans le fluide (F), et une chambre à haute pression (40) du boîtier de compresseur (4) étant couplée fluidiquement à la chambre de séparation (18) au moyen d'un canal de passage (27), et le canal de passage (27) étant placé de telle façon dans une paroi intermédiaire (44) entre la chambre à haute pression (40) et la chambre de séparation (18) qu'il débouche dans la chambre de séparation (18) décalé radialement et du côté extérieur par rapport au séparateur (20).
PCT/EP2018/060426 2017-04-27 2018-04-24 Compresseur WO2018197458A1 (fr)

Priority Applications (4)

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KR1020197032880A KR20190129132A (ko) 2017-04-27 2018-04-24 압축기
JP2019557615A JP2020517858A (ja) 2017-04-27 2018-04-24 圧縮機
CN201880027497.2A CN110582644A (zh) 2017-04-27 2018-04-24 压缩机
US16/608,564 US20200191146A1 (en) 2017-04-27 2018-04-24 Compressor

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DE102017207145.1 2017-04-27
DE102017207145.1A DE102017207145A1 (de) 2017-04-27 2017-04-27 Verdichter

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WO (1) WO2018197458A1 (fr)

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Publication number Priority date Publication date Assignee Title
US11162479B2 (en) 2019-11-18 2021-11-02 Kerr Machine Co. Fluid end
US11578710B2 (en) 2019-05-02 2023-02-14 Kerr Machine Co. Fracturing pump with in-line fluid end
US11578711B2 (en) 2019-11-18 2023-02-14 Kerr Machine Co. Fluid routing plug
US11635068B2 (en) 2019-11-18 2023-04-25 Kerr Machine Co. Modular power end
US11644018B2 (en) 2019-11-18 2023-05-09 Kerr Machine Co. Fluid end
US11686296B2 (en) 2019-11-18 2023-06-27 Kerr Machine Co. Fluid routing plug
US11808254B2 (en) 2019-11-18 2023-11-07 Kerr Machine Co. Fluid end assembly
US11808364B2 (en) 2021-11-11 2023-11-07 Kerr Machine Co. Valve body
US11920583B2 (en) 2021-03-05 2024-03-05 Kerr Machine Co. Fluid end with clamped retention
US11946465B2 (en) 2021-08-14 2024-04-02 Kerr Machine Co. Packing seal assembly

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11747064B2 (en) 2020-03-30 2023-09-05 Carrier Corporation Integrated oil separator with flow management
CN112727754B (zh) * 2021-01-13 2023-05-09 上海海立新能源技术有限公司 具有强化冷却功能的涡旋压缩机
DE102021202705A1 (de) 2021-03-19 2022-09-22 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Abscheidevorrichtung sowie Verdichter

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010029727A1 (en) * 2000-04-17 2001-10-18 Shigeki Iwanami Compressor with oil separator
JP2005163793A (ja) * 2004-12-24 2005-06-23 Denso Corp 圧縮機
US20090285708A1 (en) * 2008-05-16 2009-11-19 Kabushiki Kaisha Toyota Jidoshokki Scroll type compressor
EP3156650A1 (fr) * 2013-12-20 2017-04-19 Valeo Japan Co., Ltd. Compresseur

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69823117T2 (de) * 1997-08-29 2005-04-28 Kabushiki Kaisha Toyota Jidoshokki, Kariya Spiralverdichter
JP2000249431A (ja) * 1999-02-25 2000-09-14 Mitsubishi Heavy Ind Ltd 油分離器
JP4211477B2 (ja) * 2003-05-08 2009-01-21 株式会社豊田自動織機 冷媒圧縮機のオイル分離構造
JP2005023847A (ja) * 2003-07-02 2005-01-27 Zexel Valeo Climate Control Corp 圧縮機
JP2006097495A (ja) * 2004-09-28 2006-04-13 Sanden Corp 圧縮機
CN2871925Y (zh) * 2005-12-21 2007-02-21 上海三电贝洱汽车空调有限公司 车用涡旋压缩机
JP2007192047A (ja) * 2006-01-17 2007-08-02 Sanden Corp 圧縮機
KR101042393B1 (ko) * 2008-07-02 2011-06-17 주식회사 두원전자 오일 분리기
US20170022984A1 (en) * 2015-07-22 2017-01-26 Halla Visteon Climate Control Corp. Porous oil flow controller

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010029727A1 (en) * 2000-04-17 2001-10-18 Shigeki Iwanami Compressor with oil separator
JP2005163793A (ja) * 2004-12-24 2005-06-23 Denso Corp 圧縮機
US20090285708A1 (en) * 2008-05-16 2009-11-19 Kabushiki Kaisha Toyota Jidoshokki Scroll type compressor
EP3156650A1 (fr) * 2013-12-20 2017-04-19 Valeo Japan Co., Ltd. Compresseur

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11578710B2 (en) 2019-05-02 2023-02-14 Kerr Machine Co. Fracturing pump with in-line fluid end
US11952986B2 (en) 2019-05-02 2024-04-09 Kerr Machine Co. Fracturing pump arrangement using a plunger with an internal fluid passage
US11592011B2 (en) 2019-05-02 2023-02-28 Kerr Machine Co. Fracturing pump with in-line fluid end
US11635151B2 (en) 2019-11-18 2023-04-25 Kerr Machine Co Modular power end
US11686296B2 (en) 2019-11-18 2023-06-27 Kerr Machine Co. Fluid routing plug
US11560884B2 (en) 2019-11-18 2023-01-24 Kerr Machine Co. Fluid end
US11346339B2 (en) 2019-11-18 2022-05-31 Kerr Machine Co. High pressure pump
US11578711B2 (en) 2019-11-18 2023-02-14 Kerr Machine Co. Fluid routing plug
US11300111B2 (en) * 2019-11-18 2022-04-12 Kerr Machine Co. Fluid routing plug
US11635068B2 (en) 2019-11-18 2023-04-25 Kerr Machine Co. Modular power end
US11162479B2 (en) 2019-11-18 2021-11-02 Kerr Machine Co. Fluid end
US11644018B2 (en) 2019-11-18 2023-05-09 Kerr Machine Co. Fluid end
US11359615B2 (en) 2019-11-18 2022-06-14 Kerr Machine Co. Fluid end
US11808254B2 (en) 2019-11-18 2023-11-07 Kerr Machine Co. Fluid end assembly
US11208996B2 (en) 2019-11-18 2021-12-28 Kerr Machine Co. Modular power end
US11846282B2 (en) 2019-11-18 2023-12-19 Kerr Machine Co. High pressure pump
US11859611B2 (en) 2019-11-18 2024-01-02 Kerr Machine Co. Fluid routing plug
US11920583B2 (en) 2021-03-05 2024-03-05 Kerr Machine Co. Fluid end with clamped retention
US11946465B2 (en) 2021-08-14 2024-04-02 Kerr Machine Co. Packing seal assembly
US11808364B2 (en) 2021-11-11 2023-11-07 Kerr Machine Co. Valve body

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DE102017207145A1 (de) 2018-10-31
KR20190129132A (ko) 2019-11-19
CN110582644A (zh) 2019-12-17
JP2020517858A (ja) 2020-06-18
US20200191146A1 (en) 2020-06-18

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