EP3797225B1 - Radiale strömungsmaschine - Google Patents

Radiale strömungsmaschine Download PDF

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Publication number
EP3797225B1
EP3797225B1 EP19720916.6A EP19720916A EP3797225B1 EP 3797225 B1 EP3797225 B1 EP 3797225B1 EP 19720916 A EP19720916 A EP 19720916A EP 3797225 B1 EP3797225 B1 EP 3797225B1
Authority
EP
European Patent Office
Prior art keywords
housing part
radial
gas
flow channel
gas outlet
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
EP19720916.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3797225A1 (de
EP3797225C0 (de
Inventor
Ronny ZWAHLEN
Daniel HILPERT
Peter Meier
Ernst Scherrer
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.)
Micronel AG
Original Assignee
Micronel AG
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
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Publication of EP3797225A1 publication Critical patent/EP3797225A1/de
Application granted granted Critical
Publication of EP3797225B1 publication Critical patent/EP3797225B1/de
Publication of EP3797225C0 publication Critical patent/EP3797225C0/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4253—Fan casings with axial entry and discharge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/164—Multi-stage fans, e.g. for vacuum cleaners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/165—Axial entry and discharge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible

Definitions

  • the present invention relates to a radial flow machine for sucking in and transporting a gas, in particular air.
  • the turbomachine can be used, for example, to generate an air flow, to extract air and/or to generate an overpressure and/or an underpressure of air or another gas
  • Flow machines which also include fans and compressors in particular, have been known for a long time and are used in a wide variety of applications.
  • the flow machines in question within the scope of this property right have a usually electrically driven impeller which rotates in a housing.
  • a gas such as air in particular, is sucked in, transported and compressed.
  • Fans are also often referred to as fans or blowers.
  • a specific class of turbomachines relates to radial turbomachines, in which the gas or the air is usually sucked in axially or parallel to the axis of rotation of the impeller.
  • the gas or air flow is deflected by 90° due to the rotation of the impeller and transported outwards in a radial direction, in order to then be blown out through a gas outlet.
  • radial turbomachines generally allow a relatively high pressure to be generated for a given amount of air.
  • the EP 1 746 290 A1 a two-stage centrifugal compressor in which an external fan is used to cool the motor.
  • the EP 0 385 298 A2 discloses a fan in which the air flow is drawn in axially, then transported radially outwards, deflected by almost 180° at the periphery of an impeller and then blown out through the engine compartment. Here, too, the air flow experiences strong deflections.
  • the fan disclosed in this document also has a large number of housing parts connected to one another, resulting in a large number of potentially leaky points.
  • the US 2013/0236303 A1 shows a fan in which a first housing part, which forms the engine compartment, together with a second housing part, which has the air inlet opening, forms a flow channel into which the sucked air is conveyed by an impeller in order to then be blown out.
  • the U.S. 2011/0135519 A1 discloses a fan with two housing parts, one of which forms a motor compartment and the other an axial gas inlet and a radial one gas outlet.
  • the WO 2011/062633 A1 discloses a compact fan having a central axial air inlet and a radial air outlet, both formed by a first housing part. A second housing part forms the back of the fan.
  • the DE 10 2016 210 948 A1 relates to a compressor with a compressor housing and an electric motor housing.
  • the compressor housing forms a gas inlet and a flow channel.
  • the electric motor housing forms a receiving space for a motor.
  • the WO 02/070139 A2 discloses a centrifugal fan in which the gas outlet is formed by an annular duct extending around the motor.
  • the first housing part or the second housing part forms the gas outlet at a radial distance from the axis of rotation and delimits it circumferentially.
  • the first housing part and the second housing part are each largely plate-shaped on the outside in the region of the flow channel.
  • the flow channel is preferably formed on the inner sides, that is to say on the sides of the first and second housing parts facing one another, in the form of a depression.
  • a plate-shaped outside of the first and second housing part in the area of the flow channel has other advantages. For example, drill and screw holes can easily be provided in order to connect the two housing parts to one another and/or to other components, or inscriptions etc. can simply be applied to the outside.
  • the first or the second housing part forms the gas outlet and delimits it all around, it is ensured in a particularly simple manner that no leaks can develop in the area of the gas outlet. Due to the radial distance between the gas outlet and the axis of rotation of the radial impeller, deflections of the gas flow between the gas inlet and the gas outlet can also be reduced to a minimum, which improves the efficiency of the turbomachine.
  • the first housing part preferably forms the gas outlet and delimits it all around.
  • the gas can then be conveyed out of the gas outlet in particular along the same or at least approximately the same direction as it was conveyed through the gas inlet is sucked in.
  • the gas outlet is preferably formed in particular by a gas outlet opening which is peripherally delimited by the material of the first housing part.
  • the radial flow machine is preferably a radial fan. However, it can also be a radial compressor, for example.
  • the gas inlet is usually arranged in the vicinity of the axis of rotation and the gas outlet is arranged at a distance from the axis of rotation, so that the gas is conveyed outwards in the radial direction between the gas inlet and the gas outlet.
  • the first housing part forms the engine compartment and can therefore also be referred to as the engine housing.
  • the motor compartment is preferably formed by a bag-like depression into which the drive motor can advantageously be inserted from the opening side along the axis of rotation.
  • the first housing part transitions into a projecting area, preferably in the radial direction, ie perpendicular to the axis of rotation.
  • the protruding area On its side facing away from the engine compartment, the protruding area preferably forms the flow channel, which is advantageously designed there in the form of a depression.
  • the gas outlet is preferably formed, for example in the form of an outlet socket, on the side of the cantilevered area which faces the engine compartment.
  • the flow channel formed on the side facing away then merges via a through-opening into the gas outlet on the side of the cantilevered area facing the engine compartment.
  • the outlet socket can have an internal or external thread for connection to a coupling element or a hose connection, for example, or it can be smooth on its outside or have peripheral ribs for sealing placement of a flexible hose.
  • Cooling ribs are preferably provided on the outside of the first housing part, in particular on the outside of the engine compartment, for passively dissipating thermal energy from the engine compartment.
  • the drive motor is preferably an electric motor.
  • the rotor is advantageously arranged on the inside and the stator on the outside.
  • the rotor is then preferably non-rotatably connected to the radial impeller via a drive shaft.
  • the gas can in particular be air. In principle, however, any other gaseous medium can be sucked in and transported by the radial impeller.
  • the second housing part forms the gas inlet, which is formed in particular by a gas inlet opening, which is preferably peripherally delimited by the material of the second housing part.
  • the gas inlet is preferably arranged concentrically to the axis of rotation. It is advantageously formed by an inlet connector which protrudes outwards on the side of the second housing part which is remote from the first housing part.
  • the inlet connector can have an internal or external thread for connection to a coupling element or a hose connection, for example, or it can be smooth on its outside for sealing placement of a flexible hose or have circumferential ribs.
  • the side of the second housing part that faces the first housing part preferably forms the flow channel, which is advantageously designed there in the form of a recess. The gas inlet then merges via a passage opening into the flow channel formed on the other side of the second housing part.
  • the flow channel is formed jointly by the first and the second housing part and is delimited by them.
  • the flow channel connects in particular the gas inlet with the gas outlet.
  • the flow channel preferably has an inner radial area and a peripheral area. In the radial area, the direction of movement of the gas has a radial component, so that the gas is transported radially outwards. In the peripheral area, on the other hand, the movement component of the gas along the circumferential direction or along the tangential direction clearly predominates.
  • the radial area preferably extends radially circumferentially to the gas inlet from the axis of rotation outwards and is also advantageously designed conically, with an opening angle directed towards the first housing part along the axis of rotation.
  • the radial area of the flow channel preferably serves to accommodate the radial impeller.
  • the radial impeller is therefore preferred in the flow channel, that is, in particular between the first and the second housing part arranged. On its radial outside, the radial area advantageously transitions into the peripheral area of the flow channel.
  • the peripheral area usually extends around the radial area and in particular the radial impeller and is used to convert the gas into an encircling ring or spiral flow.
  • the first and the second housing part preferably each form approximately half of the peripheral area of the flow channel.
  • the peripheral region preferably runs essentially along its entire extent in the circumferential direction within the same plane.
  • the cross-sectional area of the flow channel preferably increases along the circumferential direction in the radial area towards the gas outlet, in particular continuously. This takes into account the changing pressure conditions in the circumferential direction.
  • the enlargement of the cross-sectional area can be achieved, for example, by means of an increasing outer radius of the radial area and/or by means of a continuous widening of the flow channel in the direction of the axis of rotation.
  • the turbomachine preferably has at least one radial area and/or at least one peripheral area, which is formed and delimited jointly by the first housing part and the second housing part.
  • the flow channel thus advantageously has at least one section in which it is formed and delimited jointly by the first and the second housing part in cross section.
  • the radial impeller is designed to be set in a rotary motion about the axis of rotation by the drive motor in order to draw in gas through the gas inlet and convey it radially outwards.
  • the gas is transported radially outwards, due to the rotary movement of the radial impeller, the gas is additionally subjected to a movement component pointing in the circumferential direction, as a result of which the gas is advantageously already moving mainly along the circumferential direction towards the gas outlet when it reaches the peripheral region of the flow channel.
  • the flow channel is preferably connected to the gas outlet in a tangential, straight-line direction relative to the axis of rotation.
  • the transition from the peripheral area of the flow channel to the gas outlet takes place continuously. Become this way Deflections of the gas flow and turbulence between the flow channel and the gas outlet are minimized.
  • the gas outlet is thus preferably arranged radially outside the flow channel.
  • the first housing part and, even more advantageously, also the second housing part are advantageously produced as a whole in one piece and preferably as a cast element.
  • the cast element can in each case be made in particular from aluminum or zinc. Due to their one-piece design, the first and second housing parts are not only particularly easy to produce, but the number of potentially leaky points is reduced to a minimum.
  • the radial flow machine has a tightness according to IP 67 according to IEC Standard 60529. If the first and second housing parts are each produced as a cast element, a particularly robust turbomachine is also achieved.
  • first housing part also leads to optimal transfer of the motor heat to the surfaces of the first housing part delimiting the flow channel, especially when made from metal, and thus to efficient dissipation of the heat through the gas flow in the flow channel.
  • first housing part and/or the second housing part can, however, also be made in several pieces. However, at least the first housing part or the second housing part is advantageously formed in one piece.
  • the gas inlet is preferably an axial gas inlet, through which the gas is sucked into the flow channel in a direction that extends parallel to the axis of rotation of the radial impeller.
  • the gas outlet is preferably an axial gas outlet through which the gas is conveyed outwards in a direction which extends parallel to the axis of rotation of the radial impeller.
  • An axial gas outlet enables a particularly space-saving use of the turbomachine. In particular, this also makes it possible to arrange a plurality of such radial flow machines connected in series one behind the other in a space-saving manner.
  • the second housing part preferably has a deflection element, which in particular and preferably can represent an element formed in one piece on the second housing part.
  • the deflection element serves in particular to deflect the gas flowing out of the flow channel in the direction in which it is conveyed out of the turbomachine through the gas outlet to the outside.
  • the deflection element advantageously has a continuously curved surface, which serves to deflect the gas flow.
  • the deflection element is preferably designed to effect a deflection of the flowing gas by approximately 90°.
  • the deflection element protrudes at least partially into the gas outlet, in particular into the area of the gas outlet which is peripherally delimited by the first housing part. In this way, an optimal transition from the flow channel to the gas outlet, ie one that is as turbulence-free as possible for the gas flow, is achieved.
  • a sealing element is advantageously provided between the first housing part and the second housing part in order to seal the flow channel circumferentially towards the outside.
  • the sealing element can in particular be designed as an O-ring and inserted in a correspondingly provided groove on the first or second housing part.
  • the sealing element is preferably also arranged circumferentially around the gas inlet.
  • the sealing element is preferably also arranged circumferentially around the gas outlet. In this way, an optimal sealing of the Flow channel and in particular the gas outlet can be achieved.
  • Between the first and the second housing part there is then preferably a space which is completely sealed off from the outside except for the gas inlet and the gas outlet and which contains at least the flow channel, preferably at least the flow channel and the engine compartment.
  • the space that is sealed off from the outside preferably has a tightness overall that is designed according to IP 67 according to IEC Standard 60529.
  • the first housing part and preferably also the second housing part are advantageously made of a metal. This makes the turbomachine particularly robust. In addition, when made from metal, heat that is generated in the engine compartment can be dissipated to the outside particularly well.
  • the overall housing of the radial flow machine is advantageously formed essentially exclusively by the first and the second housing part.
  • the housing of the turbomachine is advantageously formed exclusively by the first and the second housing part.
  • “Essentially exclusively” means that the overall housing can have other components that are functionally irrelevant in terms of limiting the gas flow and the engine compartment, such as a cover for closing a compartment for accommodating an electronics unit. If there is a compartment for accommodating an electronic unit, this preferably represents part of the space that is completely sealed off from the outside, with the exception of the gas inlet and the gas outlet.
  • a sealing element designed in particular as an O-ring is then preferably present between the first housing part and the cover .
  • a connection plug which leads out of the engine compartment or the compartment with the electronics unit, is also advantageously connected to the first housing part and/or the cover in a sealing manner.
  • the flow machine can additionally have a coupling piece according to a development of the invention in order to connect the gas outlet to the gas inlet of a further radial flow machine.
  • the radial flow machine according to the invention is particularly suitable for industrial applications such as transport ("pick and place”), cleaning, air drying, etc. Applications can also be found in the paper industry in particular.
  • FIGS. 1 to 13 show different representations of preferred embodiments of a radial flow machine according to the invention. Elements with the same or similar functions are each provided with the same reference symbols.
  • the radial flow machine according to the embodiment shown has an extremely compact and robust design overall. This is due in particular to the simple design of the housing consisting essentially of only two housing parts 1 and 2 and the plate-shaped design of the two housing parts 1 and 2 in the area where they abut and where the gas passes through the turbomachine.
  • Both the first housing part 1 and the second housing part 2 are produced in one piece as a cast element made of metal.
  • the first housing part 1 is in the Figures 3 to 5 shown and forms, as is particularly the case in the figure 2 is clearly visible, an engine compartment 11, in which a drive motor 6 is accommodated. Since the engine compartment 11 is designed as a bag-like depression in the housing part 1 and is designed to be open toward the second housing part 2, the drive motor 6 can be easily inserted into the engine compartment 11 when the second housing part 2 is removed. Otherwise, the engine compartment 11 is surrounded all around by the first housing part 1 with the exception of the upper side which is closed by a cover 3 . This enclosing of the engine compartment 11 by the first housing part 1 enables optimal dissipation of heat from the engine compartment 11 .
  • the drive motor 6 is preferably an AC electric motor in which the rotor is advantageously arranged on the inside and the stator is advantageously arranged on the outside.
  • the drive motor 6 is advantageously designed for rotational speeds of up to 40,000 RPM.
  • the drive motor 6 is used to drive a drive shaft 61 and, via this, to drive a radial impeller 5 which is non-rotatably attached to the front end of the drive shaft 61 ( figure 9 ).
  • the rotational movement carried out by the radial impeller 5 during operation of the radial flow machine defines an axis of rotation R ( figure 2 ).
  • the first housing part 1 is designed to be open, but closed with the cover 3 already mentioned.
  • the cover 3 is also made in one piece as a whole and as a cast element made of metal.
  • screws are to be inserted through screw holes 31 of the cover 3 into corresponding threaded holes 18 provided on the first housing part 1 (see FIG figure 3 ) screwed in.
  • a compartment 13 which serves to accommodate an electronic unit 7.
  • the electronics unit 7 serves in particular to control and supply energy to the drive motor 6 and has a printed circuit board 71 with electronic components 711 mounted on the top and bottom.
  • a connection plug 72 is also attached to the circuit board 71 and protrudes outwards through a through-opening correspondingly provided in the cover 3 .
  • the connector plug 72 is used to connect an external control and power supply unit that is not shown in the figures.
  • a sealing element for example an O-ring, can be provided between the cover 3 and the first housing part 1, which is inserted, for example, into a groove provided on the first housing part 1 in order to seal off the compartment 13 and the engine compartment 11 from the outside.
  • the first housing part 1 has a sealing groove, into which a sealing element 32 is inserted, which can be designed in particular as an O-ring.
  • the sealing element 32 is used to seal the first housing part 1 against the cover 3 in the area of the compartment 13.
  • Another sealing element is advantageous, which is not shown in the figures and is preferably designed as an O-ring, between the connector plug 72 and the cover 3 arranged in order to provide a sealing of the compartment 13 to the outside surrounding the connector plug 72 .
  • the first housing part 1 has, in its area enclosing the engine compartment 11 , external cooling ribs 17 which serve to dissipate thermal energy from the engine compartment 11 .
  • the first housing part 1 transitions perpendicularly, ie radially outwards in relation to the axis of rotation R, into a circumferential projecting area 19.
  • the first housing part 1 is largely plate-shaped in this projecting area 19 , at least on its rearward side, that is to say in the direction of the engine compartment 11 .
  • the overhanging portion 19 has an approximately square shape as a whole.
  • a base 16 of the first housing part 1 extends from the cantilevered area 19 to the rear.
  • the first housing part 1 On the front side facing the second housing part 2, the first housing part 1 has a depression in the area of the projection 19, which forms a flow channel 8 together with a depression of the second housing part 2, which will be explained further below.
  • the flow channel 8 is arranged concentrically circumferentially to the axis of rotation R and has an inner radial region 81 which radially outwards into a surrounding outer peripheral region 82 passes.
  • the first housing part 1 is slightly recessed, but flat.
  • the first housing part 1 In the peripheral area 82, the first housing part 1 is recessed in an annular manner, the recess of the radial area 81 merging in the radial direction into the annular recess of the peripheral area 82.
  • the peripheral area 82 of the flow channel 8 is shown in the cross-sectional view according to FIG figure 2 limited by rounded boundary surfaces of the first housing part 1.
  • the peripheral area 82 of the flow channel 8 widens with respect to its cross-sectional area, as for example in FIG figure 5 is clearly visible, continuously in the circumferential direction.
  • the indentation formed in the first housing part 1, which forms the peripheral area 82 of the flow channel 8 merges tangentially and with a further widening cross-sectional area into a gas outlet 12.
  • the gas outlet 12 is formed by a gas outlet socket 121 which extends backwards parallel to the axis of rotation R on the rear side of the first housing part 1 .
  • the gas outlet socket 121 which is formed entirely by the first housing part 1, delimits a gas outlet opening through which the gas flowing out of the flow channel 8 can be blown out of the radial flow machine.
  • the gas outlet connector 121 has an internal thread for connecting, for example, an air line or a coupling element.
  • the recess which forms the peripheral area 82 of the flow channel 8 on the front side of the first housing part 1, merges continuously via a rounded surface into the gas outlet connector 121.
  • the indentation becomes increasingly deep towards the gas outlet 12 .
  • a continuous opening is thus formed in the first housing part 1 in the region of the gas outlet 12 .
  • the gas outlet connector 121 extends parallel to the axis of rotation R from the projecting area 19 to the rear.
  • the first housing part 1 has a sealing groove 14, into which a sealing element 4 in the form of an O-ring is used.
  • the sealing groove 14 and thus the sealing element 4 are not only arranged circumferentially around the flow channel 8 but also around the gas outlet 12 or around the through-opening formed by the gas outlet 12 .
  • the sealing element 4 serves to seal the first housing part 1 from the second housing part 2 in the area of the flow channel 8.
  • the second housing part 2 is in particular in the Figures 6 to 8 shown. Like it in the figure 6 As can be seen, the second housing part 2 has an overall largely plate-shaped outer shape, with the exception of a gas inlet connection 211 protruding on the front and a deflection element 22 protruding on the rear.
  • the second housing part 2 describes a largely square shape, corresponding to the shape of the projection 19 of the first housing part.
  • the gas inlet connector 211 is arranged concentrically to the axis of rotation R and extends outward parallel to this from the otherwise largely planar front side of the second housing part 2 .
  • a gas inlet opening extends continuously through the gas inlet connector 211 and the second housing part 2 and thus forms a gas inlet 21.
  • the gas inlet connector 211 has an internal thread 212 for connecting, for example, an air line or a coupling element.
  • a recess is formed concentrically and circumferentially to the gas inlet 21, which together with the recess of the first housing part 1 described above forms and delimits the flow channel 8.
  • the inner area of the depression of the second housing part 2, which forms the radial area 82 of the flow channel 8, has a conical front boundary surface with an opening angle directed along the axis of rotation R toward the first housing part 1.
  • the conical boundary surface which in particular in the figure 2 is clearly visible, corresponds to the likewise conical front side of the radial impeller 5.
  • annular indentation which forms the peripheral region 82 of the flow channel 8 , adjoins the conical boundary surface all the way around in the radial direction.
  • annular depression of the second housing part 2 also widens continuously along the circumferential direction and has a rounded boundary surface.
  • the depression which forms the peripheral area 82 of the flow channel 8 is continued in a tangential, straight direction to a deflection element 22 .
  • the deflection element 22 protrudes into the gas outlet 12 and in particular the gas outlet connector 121 of the first housing part 1 . It serves to deflect the gas flowing out of the flow channel 8 by about 90° with as little turbulence as possible and to guide it into the gas outlet connector 121 .
  • the deflection element 22 has a continuously rounded inner surface, along which the gas flow is deflected by approximately 90° in a direction extending parallel to the axis of rotation R.
  • the deflection element 22 also has a rounded boundary surface in the cross section of the gas flow, which continuously merges into the rounded boundary surface formed by the depression in the second housing part 2 that forms the peripheral region 82 of the flow channel 8 .
  • the second housing part 2 Around the recess, which forms the flow channel 8, the second housing part 2 has a sealing surface 23 that is generally planar.
  • the sealing surface 23 extends around both the gas inlet 21 and the deflection element 22 . It serves to support the sealing element 4 and thus as a sealing seat for sealing the flow channel 8 to the outside.
  • Screw holes 24 are provided in each of the corners of the second housing part 2 , through which screws can be screwed into the threaded holes 15 of the first housing part 1 in order to fasten the second housing part 2 to the first housing part 2 .
  • the flow channel 8 is thus formed on the one hand by a recess, which is formed on the side of the first housing part 1 facing the second housing part 2, and on the other hand by a corresponding recess, which is formed on the side of the second housing part 2 facing the first housing part 1 is trained.
  • the flow channel 8 has an approximately circular cross-sectional area throughout.
  • An approximately circular cross-sectional area is also present in the continuation of the flow channel 8 in the area of the deflection element 22 and in the gas outlet connector 121 . Due to this continuously circular cross-sectional area, a largely turbulence-free gas flow within the turbomachine is achieved.
  • the radial impeller 5, which in the figure 9 is shown, is attached to the drive shaft 61 in a rotationally fixed manner in the region of a hub 52 .
  • a circular inlet opening is formed in a front wall 53 of the radial impeller 5, which forms an air inlet area 55.
  • Impeller blades 51 arranged between the front wall 53 and a rear wall 54 each extend approximately radially outwards and, during operation, serve to transport the gas flowing into the air inlet region 55 radially outwards.
  • the gas leaves the radial impeller 5 via an air outlet area 56 arranged radially on the outside.
  • the space for the gas decreases in the radial direction outwards between the front wall 53 and the rear wall 54.
  • the gas is thus increasingly compressed as it is conveyed outwards.
  • the radial impeller 5 is arranged in the radial area 81 of the flow channel 8 , ie between the first housing part 1 and the second housing part 2 .
  • the sealing elements 4 and 32 is through the first housing part 1, the second Housing part 2 and the cover 3 limited interior, which includes the flow channel 8, the engine compartment 11 and the compartment 13, with the exception of the gas inlet 21 and the gas outlet 121 completely and preferably according to IP 67 according to IEC Standard 60529 sealed to the outside.
  • the engine compartment 11 and in the compartment 13 there is therefore preferably an increased pressure compared to the outside pressure during operation of the turbomachine, which pressure can in particular essentially correspond to the pressure in the flow channel 8 .
  • the radial impeller 5 is set in a rotary motion about the axis of rotation R by the drive motor 6 .
  • a gas or air is sucked in by the impeller blades 51 through the gas inlet connector 211 into the flow channel 8 and conveyed radially outwards in its radial region 81 .
  • the impeller blades 51 simultaneously move the gas in the circumferential direction, which thus reaches the peripheral area 82 of the flow channel 8 along a spiral from the radial area 81 .
  • the compressed gas reaches the deflection element 22 via the peripheral region 82 , where it is deflected by approximately 90° in a direction extending parallel to the axis of rotation R and is blown out through the gas outlet connector 121 .
  • the gas outlet port 121 of a first radial flow machine can be coupled to the gas inlet port 211 of a second radial flow machine, which is shown in FIGS figures 10 and 11 is shown.
  • the outlet pressure is thereby doubled, or correspondingly multiplied if even more radial flow machines of this type are connected in series.
  • a coupling piece 9 can be used to couple the two radial flow machines, which can be screwed into the internal thread of the gas outlet socket 121 of the first radial flow machine and into the internal thread 212 of the gas inlet socket 211 of the second radial flow machine.
  • the two turbomachines are mutually rotated by 180 ° to each other.
  • the gas outlet 12 of the second radial flow machine is then exactly aligned with the gas inlet 21 of the first radial flow machine.
  • each with a radial impeller 5 can be provided within the radial flow machine.
  • a corresponding embodiment is in the figures 12 and 13 shown.
  • the two radial impellers 5 are both attached to the drive shaft 61 in a rotationally fixed manner and can therefore be driven by the drive motor 6 .
  • An intermediate part 10 is arranged between the first housing part 1 and the second housing part 2 in the area between the two radial impellers 5 .
  • the intermediate part 10 delimits the flow channel 8 on both sides, that is to say towards the first housing part 1 on the one hand and towards the second housing part 2 on the other hand.
  • the gas flowing in through the gas inlet connector 211 of the second housing part 2 thus first reaches a first radial region 81 of the flow channel 8 in the region of the first radial impeller 5, which forms a first (high-pressure) stage of the turbomachine. From this first radial impeller 5, the gas is then conveyed radially outwards into a first peripheral area 82 and from there along the rear side of the first radial impeller 5 again in the direction of the axis of rotation R and axially through a through opening centrally arranged in the intermediate part 10. From this passage opening, the gas passes directly into a second radial area 81 of the flow channel 8, which is located in the area of the second radial impeller 5.
  • the second radial impeller 5 forms a second (low-pressure) stage of the turbomachine. From the second radial impeller 5, the gas is conveyed radially outwards into a second peripheral area 82 of the flow channel 5 and finally through the gas outlet connector 121 to the outside.
  • the first and the second radial impeller 5 and also the first and second radial area 81 and the first and second peripheral area 82 can each be designed and in particular dimensioned differently.
  • the intermediate part 10 which is preferably produced in one piece, in particular as a cast element, thus forms a further housing part of the radial flow machine.
  • the in Central passage opening provided between part 10 forms a gas inlet for the second (low-pressure) stage or a gas outlet for the first (high-pressure) stage of the turbomachine.
  • the first housing part 1 together with the intermediate part 10 or the second housing part 2 together with the intermediate part 10 can also be viewed as a multi-piece housing part 1, 10 or 2, 10.
  • the gas outlet can also be formed by the second housing part 2 and be delimited circumferentially by it.
  • the gas is then blown out of the gas outlet nozzle in the opposite direction to that in which it was sucked in through the gas inlet nozzle.
  • the deflection element is then formed on the first housing part 1 instead of on the second housing part 2 .
  • the radial impeller can also be any different than that in the figure 9 shown radial impeller 5 be configured.
  • the front wall 53 or the rear wall 54 can also be omitted. Preferably, however, for reasons of stability, both the front wall 53 and the rear wall 54 are present.
  • the coupling piece 9 can also be designed in any other way and can include a flexible connecting tube, for example.
  • REFERENCE LIST 1 First housing part 11 engine compartment 5 centrifugal impeller 12 gas outlet 51 impeller blades 121 gas outlet nozzle 52 hub 13 Academic subject 53 front wall 14 seal groove 54 back panel 15 threaded hole 55 air intake area 16 base 56 air outlet area 161 screw hole 17 cooling fins 6 drive motor 18 threaded hole 61 drive shaft 19 Projecting area 7 electronics unit 2

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP19720916.6A 2018-05-22 2019-05-06 Radiale strömungsmaschine Active EP3797225B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18173575 2018-05-22
PCT/EP2019/061552 WO2019223988A1 (de) 2018-05-22 2019-05-06 Radiale strömungsmaschine

Publications (3)

Publication Number Publication Date
EP3797225A1 EP3797225A1 (de) 2021-03-31
EP3797225B1 true EP3797225B1 (de) 2023-07-05
EP3797225C0 EP3797225C0 (de) 2023-07-05

Family

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EP19720916.6A Active EP3797225B1 (de) 2018-05-22 2019-05-06 Radiale strömungsmaschine

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US (1) US11754092B2 (zh)
EP (1) EP3797225B1 (zh)
JP (1) JP7307962B2 (zh)
KR (1) KR102653189B1 (zh)
CN (1) CN112513472A (zh)
WO (1) WO2019223988A1 (zh)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0765597B2 (ja) 1989-03-01 1995-07-19 株式会社日立製作所 電動送風機
GB2251035A (en) 1990-12-20 1992-06-24 Dunphy Oil And Gas Burners Lim Centrifugal fan
JPH07259798A (ja) * 1994-03-23 1995-10-09 Aisin Seiki Co Ltd 遠心送風機
EP1423203B1 (en) * 2001-03-05 2009-12-02 Robert Bosch LLC Compact centrifugal blower with annular stator
EP1746290A1 (de) 2005-07-20 2007-01-24 Rietschle Thomas Schopfheim GmbH Radialverdichter
US20080232962A1 (en) * 2007-03-20 2008-09-25 Agrawal Giridhari L Turbomachine and method for assembly thereof using a split housing design
DE102007053016A1 (de) 2007-11-05 2009-05-07 Gardner Denver Deutschland Gmbh Seitenkanalverdichter
US8973576B2 (en) * 2009-11-19 2015-03-10 Resmed Motor Technologies Inc Blower
US8702404B2 (en) * 2009-12-09 2014-04-22 Halla Visteon Climate Control Corporation Air blower for a fuel cell vehicle
ES2393720T3 (es) 2010-09-20 2012-12-27 Fiat Powertrain Technologies S.P.A. Unidad turbosobrealimentadora con un componente auxiliar asociado para un motor de combustión interna
US9017893B2 (en) * 2011-06-24 2015-04-28 Watt Fuel Cell Corp. Fuel cell system with centrifugal blower system for providing a flow of gaseous medium thereto
US8974178B2 (en) * 2012-01-17 2015-03-10 Hamilton Sundstrand Corporation Fuel system centrifugal boost pump volute
JP6155544B2 (ja) 2012-03-12 2017-07-05 日本電産株式会社 遠心ファン
CN102788022B (zh) * 2012-07-16 2014-12-17 华中科技大学 一种高可靠性的微型机械泵
JP6322121B2 (ja) 2014-10-29 2018-05-09 株式会社オティックス ターボチャージャ用のコンプレッサ構造
DE102016210464A1 (de) 2016-06-14 2017-12-14 Gardner Denver Deutschland Gmbh Verdichteranordnung
DE102016210948A1 (de) * 2016-06-20 2017-12-21 Continental Automotive Gmbh Elektro-Verdichter mit kompakter Lagerung

Also Published As

Publication number Publication date
EP3797225A1 (de) 2021-03-31
WO2019223988A1 (de) 2019-11-28
US20210199126A1 (en) 2021-07-01
CN112513472A (zh) 2021-03-16
KR20210030280A (ko) 2021-03-17
KR102653189B1 (ko) 2024-03-29
EP3797225C0 (de) 2023-07-05
JP7307962B2 (ja) 2023-07-13
US11754092B2 (en) 2023-09-12
JP2021524553A (ja) 2021-09-13

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