US20200191146A1 - Compressor - Google Patents

Compressor Download PDF

Info

Publication number
US20200191146A1
US20200191146A1 US16/608,564 US201816608564A US2020191146A1 US 20200191146 A1 US20200191146 A1 US 20200191146A1 US 201816608564 A US201816608564 A US 201816608564A US 2020191146 A1 US2020191146 A1 US 2020191146A1
Authority
US
United States
Prior art keywords
wall
passage duct
separator
compressor
chamber
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.)
Abandoned
Application number
US16/608,564
Other languages
English (en)
Inventor
Budi Rinaldi
Björn Fagerli
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.)
Brose Fahrzeugteile SE and Co KG
Original Assignee
Brose Fahrzeugteile SE 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 Brose Fahrzeugteile SE and Co KG filed Critical Brose Fahrzeugteile SE and Co KG
Assigned to Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg reassignment Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FAGERLI, Björn, Rinaldi, Budi
Publication of US20200191146A1 publication Critical patent/US20200191146A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—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
    • 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
    • F04B39/123—Fluid connections
    • 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
    • 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
    • F04B39/16—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
    • 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 present disclosure relates to a compressor including an electric motor for use in an air-conditioning unit of a motor vehicle.
  • systems of this kind have a circuit which contains a refrigerant, e.g. R-134a (1,1,1,2-tetrafluoroethane) or R-774 (CO 2 ).
  • a refrigerant e.g. R-134a (1,1,1,2-tetrafluoroethane) or R-774 (CO 2 ).
  • the refrigerant is compressed by a compressor, leading to an increase in the pressure and temperature of the refrigerant.
  • the compressor is driven in by an electric motor.
  • a condenser Positioned downstream of the (refrigerant) compressor in terms of flow is a condenser, which is in thermal contact with the surroundings of the vehicle. As a consequence, the temperature of the refrigerant is lowered in the condenser, and the refrigerant is then passed into an evaporator positioned downstream in terms of flow. In the evaporator, the refrigerant is expanded to the original pressure, as a result of which the temperature of the refrigerant falls further.
  • a further heat exchanger Positioned downstream of the evaporator in terms of flow is a further heat exchanger, which is in thermal contact with a blower line of the air-conditioning unit leading into the interior of the vehicle.
  • thermal energy is transferred from the thermally contacted component to the refrigerant, leading to cooling of the component and heating of the refrigerant.
  • the refrigerant is fed back to the compressor.
  • a first low-pressure-side compressor element of a compressor part Arranged in series in the flow direction in the compressor of the circuit and, in the compressor, in the compressor housing, which has a housing bottom, there are a first low-pressure-side compressor element of a compressor part and a second high-pressure-side compressor element of the compressor part, the latter being mounted in a fixed manner, for compressing the fluid, as well as a high-pressure chamber and a separating device.
  • a lubricant which mixes with a gaseous refrigerant during operation.
  • the lubricant serves to reduce the friction which occurs during operation in the compressor between the first compressor element and the second, high-pressure-side compressor element, which is mounted in a fixed manner. Furthermore, the lubricant performs a sealing function, ensuring that any (refrigerant) leaks arising between the compressor elements are reduced to a very great extent or completely avoided, which increases the efficiency of the refrigerant compressor.
  • the refrigerant mixed with lubricant after being compressed by the compressor part in the compressor, flows into a high-pressure chamber which, in turn, is coupled to the separating device by a passage duct.
  • the oil is separated from the refrigerant, and the separated oil is thus or may thus be returned to the compressor via a valve and a lubricant duct, and the refrigerant is passed into the refrigerant circuit via an outlet of the separating device as far as possible without oil.
  • the separating device has a separating chamber connected to the outlet and, in the chamber, a coaxially arranged separator, with the result that an annular space is formed between the separator and an inner wall of the separating chamber.
  • the passage duct of the separating device is embodied as a round hole, wherein the fluid flows from the high-pressure chamber into the annular space of the separating chamber via the passage duct. In this process, the fluid flows from the high-pressure chamber into the separating chamber through a flow cross section matched to the delivery volume which occurs during operation and is determined by the clear width of the passage duct.
  • the fluid flow branches into two partial flows, which are guided in opposite directions of flow along the two sides of the separator. This entails unwanted eddy formation in the annular space between the separator and the chamber inner wall of the separating chamber.
  • One or more objects of the present disclosure may be to provide a compressor in which the fluid delivered flows through the separating chamber with as little eddy formation as possible.
  • a compressor for compressing a fluid, in particular a refrigerant, wherein the compressor is arranged between a heat exchanger and a condenser in terms of flow, in a refrigerant circuit of an air-conditioning system.
  • the compressor has the task of increasing the pressure of the fluid delivered.
  • the compressor has a (compressor) housing having a housing bottom and a compressor part, mounted in the housing, for delivering the fluid from a low-pressure-side inlet to a high-pressure-side outlet.
  • a lubricant which mixes with the gaseous refrigerant during operation. It serves to reduce friction in the compressor part and in the drive thereof and performs a sealing function in the compressor part in that it to a very great extent reduces or completely prevents leaks between a first low-pressure-side compressor element and a second, high-pressure-side compressor element, the latter being mounted in a fixed manner.
  • the lubricant should be separated from the fluid before being passed into the refrigerant circuit.
  • the oil separated off and collected in a (lubricant) reservoir can advantageously be returned to the compressor part via a valve and a lubricant passage, leading to improved lubrication of the compressor elements and reducing friction in the compressor part.
  • a further advantage conferred by the separation of the lubricant from the fluid is improved heat transfer to the heat exchanger of the refrigerant circuit, which increases the efficiency of the air-conditioning unit (of the air-conditioning or air-conditioning unit system).
  • a separating device for separating off the lubricant contained in the fluid is inserted into the housing bottom, wherein the separating device has a cylindrical separating chamber that is connected to the outlet and has a separator, which is arranged coaxially in the separating chamber.
  • the fluid flows out of the compressor part into a high-pressure chamber of the compressor housing, the chamber being positioned downstream of the part in terms of flow.
  • the high-pressure chamber is coupled to the separating device in terms of flow by a passage duct in a common intermediate wall of the separating chamber and the high-pressure chamber.
  • the passage duct is introduced in such a way that it opens in a manner offset radially with respect to the central center line of the separator, which is arranged coaxially in the separating chamber and is, in particular, cylindrical, this ensuring selective guidance of the flow along just one side of the separator.
  • the compressor is an electric-motor refrigerant compressor for an air-conditioning unit of a vehicle.
  • the air-conditioning unit is used to cool an interior of the vehicle or to cool an energy storage device for driving an electric-motor-operated vehicle, for example.
  • the heat exchanger is in thermal contact with any energy cells of a high voltage energy storage device or with a blower line leading into the interior of the motor vehicle. In this case, transfer of thermal energy to the refrigerant takes place, leading to cooling of the component in contact with the heat exchanger and to heating of the refrigerant.
  • the condenser may be used to adjust the temperature of the refrigerant to the ambient temperature or at least to lower the temperature of the refrigerant and may be in thermal contact with the surroundings.
  • the compressor part is appropriately embodied as a scroll compressor.
  • This operates as a refrigerant compressor in the manner of a positive displacement pump, wherein an electric motor drives a moving scroll part eccentrically relative to a fixed scroll part and, in doing so, compresses a fluid.
  • the scroll parts form the compressor elements of the compressor part and, in this case, are typically embodied as a nested pair of spirals or scrolls.
  • one of the spirals is fixed in relation to the compressor housing and engages at least partially in a second spiral, which is driven in an orbiting manner by an electric motor.
  • an orbiting movement should be taken to mean, in particular, an eccentric circular orbit in which the second spiral itself does not rotate about its own axis.
  • Two substantially crescent-shaped refrigerant chambers the volume of which is reduced (compressed) in the course of the movement, are thereby formed between the spirals during each orbiting movement.
  • the refrigerant is discharged into the high-pressure chamber via an outlet in the fixed scroll part.
  • the lubricant is expediently a (lubricating) oil, wherein the term “oil” should not be interpreted restrictively as mineral oils. On the contrary, it is also possible to use fully synthetic or partially synthetic oils, e.g. silicone oils, or other oil-like fluids such as hydraulic fluid or cooling lubricants.
  • the separating device separates the lubricant from the fluid in the manner of a centrifugal separator (cyclone separator).
  • the fluid flowing tangentially into the separating chamber is guided along the separator in a helical manner (in the manner of a cyclone) in the separating chamber, which is, in particular, cylindrical.
  • centrifugal forces act as a separating mechanism on the mixture of refrigerant and lubricant.
  • the lubricant reservoir is partially closed by a cone to form an annular slot in order to avoid the take-up of particles of the already separated lubricant by the fluid flow.
  • the compressor housing, together with the housing bottom, and the separating chamber of the separating device are formed by a diecasting method. Production which is particularly economical with materials and inexpensive is thereby ensured.
  • the passage duct is introduced in such a way into the intermediate wall between the separating chamber and the high-pressure chamber that the fluid delivered flows into the separating chamber tangentially to the separator, thereby ensuring particularly suitable positioning of the passage duct.
  • the fluid flows in at an angle of less than 90° to the housing bottom, for example.
  • the passage duct it is also possible for the passage duct to be introduced into the intermediate wall in such a way that the inflow direction of the fluid is perpendicular to the housing bottom, as a result of which the flow direction of the fluid through the passage duct is substantially identical with the delivery direction of the fluid by the compressor part, and less eddying arises at the passage duct.
  • the inflow direction should be taken to mean the direction tangential to the separator in which the fluid flows into the separating chamber.
  • the invention proceeds from the consideration that the unwanted eddy formation in the annular space between the separator and the chamber inner wall of the separating chamber can be reduced considerably if the flow of the fluid is guided selectively along only one side of the separator.
  • the passage duct opening into the annular space should be positioned as far as possible in a manner offset fully azimuthally with respect to the diameter of the separator.
  • the clear width of the passage duct exceeds the gap width of an annular gap formed between the separator and an inner wall of the separating chamber. In other words, the clear width of the passage duct is less than or equal to the gap width of the annular gap.
  • the passage duct 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 duct is oriented parallel to the inflow direction of the fluid into the separating chamber, as an advantageous result of which less eddying occurs at the passage duct during inflow.
  • the cylindrical separating chamber extends radially with respect to the housing bottom of the compressor housing, which is appropriately of pot-type shape.
  • the passage duct is of elongate shape along this radial direction.
  • the flow cross section, formed by the clear width of the passage duct, during the inflow of the fluid from the high-pressure chamber into the separating chamber is matched to the fluid delivery volume which occurs during operation.
  • the passage duct Since the flow cross section, formed by the clear area of the passage duct, from the high-pressure chamber into the separating chamber should be matched to the delivery volume which occurs during operation, and the clear width of the passage duct may be less than or equal to the gap width of the gap formed between the separator and the inner wall of the separating chamber, the passage duct is consequently of elongate design along the central center line of the separating device.
  • the passage duct is offset radially with respect to the center line of the separating device or with respect to the center line of the separator.
  • the offset including the clear width of the passage duct, is advantageously less than or equal to the radius of the cylindrical separating chamber.
  • the fluid flows tangentially into the gap formed between the separator and the inner wall of the separating chamber.
  • the fluid is guided selectively on only one side of the separator along an eddy-free path. Branching off of a partial flow of the fluid, which would be guided along the separator in the opposite direction of circulation from the eddy-free path, would collide with the eddy-free path and would lead to the formation of eddies, is avoided.
  • the passage duct is a slotted aperture in the intermediate wall.
  • the shape of the passage duct has a substantially rectangular cross-sectional shape.
  • the cross-sectional shape of the passage duct is elliptical or oval.
  • the shape of the passage duct is matched to the operational delivery rate in such a way that the clear width of the passage duct changes only along the axis of the separating chamber.
  • the passage duct between the separating chamber and the high-pressure chamber is matched in such a way to the operationally required delivery volume of the refrigerant that the fluid delivered flows through the separating chamber with only slight eddy formation.
  • the separating chamber is formed between an inner wall of the housing bottom, the wall facing the compressor part, and the high-pressure chamber, wherein the separating chamber projects at least partially axially into the high-pressure chamber.
  • the housing bottom has an annular wall which projects axially beyond the separating chamber, forming an inner and an outer annular region.
  • the passage duct from the high-pressure chamber into the separating chamber is arranged radially offset in the direction of the outlet in the inner annular region, with the result that the fluid flow is guided around the separator of the separating chamber in a particularly advantageous manner along a cyclone-type path. In particular, this ensures improved separation of the lubricant from the refrigerant.
  • the compressor part rests on the annular wall.
  • the high-pressure chamber is formed by the housing bottom, the annular wall and the compressor part.
  • additional sealing elements of the high-pressure chamber are not required, which saves space and is particularly advantageous in terms of flow.
  • the eddy formation of the fluid flow in the separating chamber is considerably reduced by virtue of the particularly suitable arrangement and embodiment of the passage duct, taking account of the required delivery volume.
  • the cross-sectional shape of the passage duct is here adapted in such a way that, for the purpose of advantageous inflow behavior, the clear width of the passage duct does not exceed the gap width of the annular space (annular gap) formed between the separating chamber and the separator and is advantageously of elongate design along the axis of the separating chamber.
  • the lubricant separates better from the refrigerant and is not carried into the refrigerant circuit, for which reason there is better heat transfer between the heat exchangers and the refrigerant in the refrigerant circuit. Furthermore, owing to the improved separation, the lubrication of the compressor part by the separated and returned lubricant is improved, resulting in reduced wear and thus a longer life of the compressor. Moreover, the efficiency of the compressor is improved.
  • FIG. 1 shows a longitudinal section through a compressor having a housing and a compressor part and of a separating device on the housing bottom side
  • FIG. 2 shows the compressor housing in a plan view, viewed in the direction of the bottom-side separating device, with a passage duct of slotted cross-sectional shape
  • FIG. 3 shows the separating device and the flow path of a fluid through the passage duct and in the separating device in a sectional illustration along the line in FIG. 2 , and
  • FIG. 4 shows the sectional illustration from FIG. 3 with a passage duct offset with respect to the center line of the separating device and without the flow path of the fluid in the separating device.
  • the compressor 2 illustrated in a sectional illustration in FIG. 1 for compressing a fluid F may be embodied as an electric-motor refrigerant compressor in a refrigerant circuit (not illustrated specifically) of an air-conditioning unit of a motor vehicle.
  • the compressor 2 has a compressor housing 4 having a housing bottom 6 and a compressor part 8 mounted in the housing 4 .
  • the compressor part 8 has a first compressor element 8 a , which is fixed relative to the compressor housing 4 , and a moving second compressor element 8 b , which engages therein and which is moved by shaft journals 10 and a motor shaft 12 by an electric motor (not illustrated specifically).
  • the compressor part 8 is embodied as a scroll compressor.
  • a lubricant S which is used to lubricate the compressor part 8 and performs a sealing function, thus avoiding leaks between the compressor elements 8 a and 8 b . Due to operating conditions, a refrigerant K and the lubricant S mix with the fluid F in this case.
  • the compressor housing 4 is embodied in the manner of a pot.
  • the radial direction in relation 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 in the adjacent direction diagram by R and A, respectively.
  • a separating device 14 which is connected to an outlet 16 , is inserted into the housing bottom 6 .
  • the separating device 14 has a cylindrical separating chamber 18 and a hollow-cylindrical separator 20 arranged coaxially therein.
  • the separating 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 into the separating chamber 18 in an inflow direction E ( FIG.
  • the inflow direction E should be taken to mean the direction tangential to the separator 20 in which the fluid F flows into the separating chamber 18 .
  • the separated lubricant S is fed back to the fixed compressor element 8 b via a valve or restrictor 28 and via a lubricant duct 30 .
  • the restrictor 26 is seated in the compressor housing 4 .
  • the returned lubricant S then flows via guide contours to rolling bearings 32 of the electric motor (not illustrated specifically) in order to lubricate and/or cool the bearings.
  • the axial direction of the separating device 14 i.e. the axial direction of the cylindrical separating chamber 18 and of the separator arranged coaxially therein, is denoted by X.
  • the radial direction of the separating device 14 perpendicular to the inflow direction E and the radial direction of the separating device 14 parallel to the inflow direction E are denoted by Y and Z, respectively ( FIG. 2 ).
  • the housing bottom 6 has an annular wall 34 projecting beyond the separating chamber 18 . This divides the space surrounded by the fixed compressor part 8 b and by the compressor housing 4 into an inner annular region 36 and into an outer annular region 38 .
  • a high-pressure chamber 40 is formed by the inner annular region 36 , bounded by the housing bottom 6 , the annular wall 34 and the compressor element 8 b resting on the annular wall 34 .
  • the separating chamber 18 is formed between an inner wall 41 of the housing bottom 6 and the high-pressure chamber 40 , wherein the separating chamber 18 projects at least partially into the high-pressure chamber 40 in the axial direction A.
  • the passage duct 27 couples the high-pressure chamber 40 to the separating chamber 18 in terms of flow.
  • the passage duct 27 is introduced into an intermediate wall 44 between the separating chamber 18 and the high-pressure chamber 40 in such a way that the passage duct 27 opens into the separating chamber 18 in a manner offset along the radial direction Y of the separating device 14 with respect to the axial direction X of the separating device 14 .
  • the passage duct 27 is arranged in such a way in the inner annular region 36 of the annular wall 34 that the passage duct 27 is offset in the axial direction X of the separating device 14 or in the radial direction R of the compressor housing 4 toward the outlet.
  • the fluid F flows into the compressor part 8 through an inlet 46 .
  • the compressor part 8 which in this case is a scroll compressor, compresses the fluid F in the manner of a positive displacement pump.
  • the fluid F is compressed in a compressor part chamber 47 and then flows out of the compressor part 8 into the high-pressure chamber 40 through a high-pressure-side compressor part outlet 48 .
  • FIG. 2 shows the pot-type compressor housing 4 with the compressor part 8 removed, looking at the housing bottom 6 of the compressor housing 4 along the axial direction A.
  • the annular wall 34 projects beyond the separating device 14 , forming the inner annular region 36 and the outer annular region 38 .
  • the annular wall 34 forms the high-pressure chamber 40 .
  • the compressor housing 4 has screw sockets 50 along a flange surface 49 to enable the compressor 2 to be fastened to a drive module (not illustrated), into which the motor of the compressor 2 is inserted.
  • a drive module not illustrated
  • only two screw sockets 50 are provided with a reference sign in FIG. 2 .
  • the separating chamber 18 extends in the radial direction R with respect to the housing bottom 6 of the compressor housing 4 .
  • the passage duct 27 is offset in the radial direction R toward the outlet 16 of the separating chamber 18 in the inner annular region 36 and is of elongate shape along the axial direction X of the separating device 14 .
  • the passage duct 27 is embodied as a slotted aperture in the intermediate wall 44 , wherein the aperture has a substantially rectangular cross-sectional shape.
  • the cross-sectional shape of the passage duct 27 can be of slotted or oval design.
  • FIG. 3 shows the separating device 14 inserted into the housing bottom 6 of the compressor housing 4 , looking toward the radially offset passage duct 27 , in a sectional illustration along the line in FIG. 2 .
  • this passage is positioned in the intermediate wall 44 between the high-pressure chamber 40 and the separating chamber 18 in such a way that the fluid F delivered flows into the separating chamber 18 tangentially to the separator 20 in the inflow direction E.
  • the passage duct 27 has an inner wall 55 , which is oriented tangentially to the inflow direction E of the fluid F in the passage duct 27 .
  • the fluid F flows into the separating chamber 18 in such a way that both the inflow direction E and the inner wall 55 of the passage duct 27 are oriented perpendicularly to the housing bottom 6 . That side of the inner wall 55 of the passage duct 27 , the distance c ( FIG.
  • the flow cross section, formed by the clear area of the passage duct 27 , during the inflow of the fluid F from the high-pressure chamber 40 into the separating chamber 18 is matched to the operationally required fluid delivery volume.
  • the passage duct 27 is here matched to the operationally required delivery volume in such a way that the clear width a of the passage duct 27 may be smaller than the gap width b (a ⁇ b) of an annular gap 58 formed between the separator 20 and an inner wall 56 of the separating chamber 18 .
  • the passage duct 27 is of elongate shape along the axial direction X of the separating device 14 .
  • the fluid F flows tangentially into the annular gap 58 and is guided exclusively along one side of the separator 20 , along an eddy-free path 60 .
  • Branching off of a second partial flow of the fluid F, indicated by the dashed arrows in FIG. 3 which would be guided along the separator 20 in the opposite direction of circulation from the eddy-free path 60 and would collide with the eddy-free path 60 , is thereby avoided.
  • FIG. 4 shows, in the sectional illustration of FIG. 3 , the separating device 14 inserted into the housing bottom 6 , with the passage duct 27 having the clear width a and the gap formed by the inner wall 56 of the separating chamber 18 and the separator 20 , having 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 separating chamber 18 .
  • the fluid F is guided selectively on only one side of the separator 20 along an eddy-free path 60 ( FIG. 3 ).
  • the passage duct 27 is in this illustrative embodiment offset along the radial direction Y of the separating device 14 relative to the center line X of the separating device 14 or relative to the center line X of the separator 20 , wherein the offset c together with the clear width a of the passage duct 27 is less than or equal to the radius d of the separating chamber 18 or the inner wall 56 thereof, i.e.
  • the offset c is the distance between the radial direction Z of the separating device 14 parallel to the inflow direction E and that side 55 a of the inner wall 55 of the passage duct 27 which faces the central center line X.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US16/608,564 2017-04-27 2018-04-24 Compressor Abandoned US20200191146A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017207145.1A DE102017207145A1 (de) 2017-04-27 2017-04-27 Verdichter
DE102017207145.1 2017-04-27
PCT/EP2018/060426 WO2018197458A1 (de) 2017-04-27 2018-04-24 Verdichter

Publications (1)

Publication Number Publication Date
US20200191146A1 true US20200191146A1 (en) 2020-06-18

Family

ID=62044746

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/608,564 Abandoned US20200191146A1 (en) 2017-04-27 2018-04-24 Compressor

Country Status (6)

Country Link
US (1) US20200191146A1 (ja)
JP (1) JP2020517858A (ja)
KR (1) KR20190129132A (ja)
CN (1) CN110582644A (ja)
DE (1) DE102017207145A1 (ja)
WO (1) WO2018197458A1 (ja)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11162479B2 (en) 2019-11-18 2021-11-02 Kerr Machine Co. Fluid end
US11578711B2 (en) 2019-11-18 2023-02-14 Kerr Machine Co. Fluid routing plug
US11578710B2 (en) 2019-05-02 2023-02-14 Kerr Machine Co. Fracturing pump with in-line fluid end
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
US11747064B2 (en) 2020-03-30 2023-09-05 Carrier Corporation Integrated oil separator with flow management
US11808364B2 (en) 2021-11-11 2023-11-07 Kerr Machine Co. Valve body
US11808254B2 (en) 2019-11-18 2023-11-07 Kerr Machine Co. Fluid end assembly
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
US12018662B2 (en) 2019-11-18 2024-06-25 Kerr Machine Co. High pressure pump
USD1034909S1 (en) 2021-05-19 2024-07-09 Kerr Machine Co. Crosshead frame

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Family Cites Families (13)

* 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
JP3721933B2 (ja) * 2000-04-17 2005-11-30 株式会社デンソー 圧縮機
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
JP2005163793A (ja) * 2004-12-24 2005-06-23 Denso 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
JP4992822B2 (ja) * 2008-05-16 2012-08-08 株式会社豊田自動織機 スクロール型圧縮機
KR101042393B1 (ko) * 2008-07-02 2011-06-17 주식회사 두원전자 오일 분리기
JP6238726B2 (ja) * 2013-12-20 2017-11-29 株式会社ヴァレオジャパン 圧縮機
US20170022984A1 (en) * 2015-07-22 2017-01-26 Halla Visteon Climate Control Corp. Porous oil flow controller

Cited By (23)

* 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
US11635068B2 (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
US11578711B2 (en) 2019-11-18 2023-02-14 Kerr Machine Co. Fluid routing plug
US11346339B2 (en) 2019-11-18 2022-05-31 Kerr Machine Co. High pressure pump
US11300111B2 (en) * 2019-11-18 2022-04-12 Kerr Machine Co. Fluid routing plug
US11635151B2 (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
US12018662B2 (en) 2019-11-18 2024-06-25 Kerr Machine Co. High pressure pump
US11208996B2 (en) 2019-11-18 2021-12-28 Kerr Machine Co. Modular power end
US11808254B2 (en) 2019-11-18 2023-11-07 Kerr Machine Co. Fluid end assembly
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
US11747064B2 (en) 2020-03-30 2023-09-05 Carrier Corporation Integrated oil separator with flow management
US11920583B2 (en) 2021-03-05 2024-03-05 Kerr Machine Co. Fluid end with clamped retention
USD1034909S1 (en) 2021-05-19 2024-07-09 Kerr Machine Co. Crosshead frame
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

Also Published As

Publication number Publication date
KR20190129132A (ko) 2019-11-19
WO2018197458A1 (de) 2018-11-01
DE102017207145A1 (de) 2018-10-31
CN110582644A (zh) 2019-12-17
JP2020517858A (ja) 2020-06-18

Similar Documents

Publication Publication Date Title
US20200191146A1 (en) Compressor
US10801495B2 (en) Oil flow through the bearings of a scroll compressor
US20200378659A1 (en) Lubricant management in an hvacr system
US8747088B2 (en) Open drive scroll compressor with lubrication system
US9689386B2 (en) Method of active oil management for multiple scroll compressors
CN104279783B (zh) 制冷循环
CN104179682A (zh) 涡旋式压缩机以及具有涡旋式压缩机的co2车辆空调系统
US10941772B2 (en) Suction line arrangement for multiple compressor system
CN206972519U (zh) 涡旋压缩机、涡旋压缩机组件及制冷系统
CN105829716B (zh) 提高压缩机轴承可靠性的方法
US11300328B2 (en) Oil control for climate-control system
US20230114913A1 (en) Compressor Having Lubrication System
CN105829715B (zh) 压缩机组件和用于可移动部件的润滑系统
CN112585356B (zh) 压缩机模块以及电动制冷压缩机
JP6160502B2 (ja) 冷凍サイクル装置
CN113316701A (zh) 用于气候控制系统的油控制
US11125233B2 (en) Compressor having oil allocation member
CN102606478A (zh) 回转式压缩机
US20200378664A1 (en) Lubricant management in an hvacr system

Legal Events

Date Code Title Description
AS Assignment

Owner name: BROSE FAHRZEUGTEILE GMBH & CO. KOMMANDITGESELLSCHAFT, WUERZBURG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:RINALDI, BUDI;FAGERLI, BJOERN;REEL/FRAME:050979/0566

Effective date: 20191023

STPP Information on status: patent application and granting procedure in general

Free format text: APPLICATION DISPATCHED FROM PREEXAM, NOT YET DOCKETED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION