EP3161320A1 - Pompe à canal latéral - Google Patents

Pompe à canal latéral

Info

Publication number
EP3161320A1
EP3161320A1 EP15729508.0A EP15729508A EP3161320A1 EP 3161320 A1 EP3161320 A1 EP 3161320A1 EP 15729508 A EP15729508 A EP 15729508A EP 3161320 A1 EP3161320 A1 EP 3161320A1
Authority
EP
European Patent Office
Prior art keywords
pump
side channel
motor
working chamber
cooling circuit
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.)
Granted
Application number
EP15729508.0A
Other languages
German (de)
English (en)
Other versions
EP3161320B1 (fr
Inventor
Heiner KÖSTERS
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.)
Sterling Industry Consult GmbH
Original Assignee
Sterling Industry Consult GmbH
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 Sterling Industry Consult GmbH filed Critical Sterling Industry Consult GmbH
Publication of EP3161320A1 publication Critical patent/EP3161320A1/fr
Application granted granted Critical
Publication of EP3161320B1 publication Critical patent/EP3161320B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal 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
    • 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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5813—Cooling the control unit
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/006—Regenerative pumps of multistage type the stages being axially offset

Definitions

  • the invention relates to a side channel pump with a Pum ⁇ pen housing.
  • a side channel pump with a Pum ⁇ pen housing In the pump housing a provided with a Sei ⁇ tenkanal working chamber and a motor are arranged. An impeller in the working chamber rotates with a shaft driven by the motor.
  • the invention is based on the object to present a side channel pump, which does not overheat when sucking in gas. Based on the cited prior art, the object is achieved with the features of claim 1. Before ⁇ geous embodiments are given in the dependent claims.
  • the side channel pump comprises a cooling circuit ⁇ extending from the working chamber to the engine and from the engine to a suction portion of the pump.
  • ⁇ channel pump gas If the sides sucks ⁇ channel pump gas, the gas is compressed in the working chamber, so that in the working chamber, a higher pressure is applied than at the inlet of the pump.
  • a sucking section area of the pump is referred to, by which the medium is conveyed to the outlet of the pump and in which the pressure is nied ⁇ engined than in the portion of the working comber from which the cooling circuit is fed.
  • the invention has recognized that a portion of the pumped medium can be used as a cooling medium.
  • the cooling By providing the cooling as a closed circuit in which the cooling medium is conducted from the working chamber to the engine and back to a suction portion of the pump, a steady stream of the cooling medium can be maintained through which heat is removed from the engine.
  • the invention has recognized, in particular, that the cooling circuit has an effect even when gaseous medium is conveyed. Although the cooling is then regularly not so effective that It would allow continuous operation of the side channel pump. This is also not necessary, because only the time ⁇ space is to bridge, until the sucked liquid follows the gas. For this purpose, it is sufficient if a dry operation for a period of time in the order of minutes is possible. This is many times longer than conventional pumps, which overheat within a few seconds if no liquid medium is delivered.
  • the cooling circuit at the same time also represents a leakage flow, through which the efficiency of the pump is reduced. It is therefore desirable not to let more cooling medium flow through the cooling circuit than required.
  • the applied across the cooling circuit pressure difference is therefore smaller than the pressure difference between see the output port of the side channel pump and the inlet opening of the side channel pump. Further preferably, the pressure difference across the cooling circuit is not greater than the pressure difference across a working chamber.
  • the side channel pump according to the invention is regularly more ⁇ stage, thus includes a plurality of side channels provided with working chambers.
  • an impeller rotates.
  • the output side of a first working chamber is preferably connected to the input side of a subsequent working chamber.
  • the cooling circuit can be fed from a working chamber whose output side is connected to the outlet opening of the pump.
  • the cooling circuit is fed from the output side of the working chamber.
  • the cooling circuit can branch off from a connecting line between the working chamber and the outlet opening of the pump.
  • the cooling circuit can open in the same working chamber from which the cooling circuit is fed.
  • Another Be ⁇ rich same working chamber then forms the suction section in the context of the invention.
  • the cooling circuit ⁇ run in a gap of the working chamber open, which is formed between the shaft and a shaft surrounding portion of the pump housing housing.
  • a gap that would make at ⁇ Otherwise a leak gap, used as part of the cooling ⁇ circuit.
  • the pressure difference across the cooling circuit is preferably less than 60%, more preferably less than 40% of the pressure difference between the inlet side and the outlet side of the working chamber, which is preferably the working chamber, and its outlet side is connected to the outlet opening.
  • the cooling circuit should be designed so that the heat is effectively removed from the engine.
  • the cooling circuit may extend between the rotor and the stator of the motor.
  • the cooling circuit extends in the longitudinal direction (ie parallel to the shaft) over the entire length of the motor.
  • Length of the motor refers to the section in which the rotor and the stator interact electrically.
  • the flow direction of the cooling medium may be such that the cooling medium approaches the working chamber as it moves through the motor.
  • the cooling medium may be first led from the working chamber to the remote end of the engine before entering the engine.
  • an electronic control unit for the motor can be accommodated in the pump housing.
  • the control electronics can in particular be designed to variably control the speed of the motor.
  • the side channel pump according to the invention is preferably designed so that in the longitudinal ⁇ becht seeks the motor between the control electronics and the working chamber is arranged.
  • the cooling circuit may include a portion disposed between the engine and the control electronics. In this design can be cooled with the cooling circuit at the same time also the control electronics.
  • the refrigeration cycle may include a plurality of channels disposed between the control electronics and the engine. The channels can be aligned in the radial direction. The flow direction of the cooling medium may be such that thedeme ⁇ dium in all the channels flows from outside to inside.
  • An annular gap can be formed between the pump housing and the motor.
  • the annular gap may extend circumferentially around the engine.
  • the cooling circuit can pass through the annular gap stretch.
  • the annular gap can also form a connecting channel between the output side of a working chamber and the outlet opening of the side channel pump.
  • the whole with the pump Shaped ⁇ -made medium moves through the annular gap.
  • a part of the medium can be led out of the annular gap through an outlet opening from the pump, while the other part moves as a cooling medium through the cooling circuit.
  • the cooling medium preferably forms only a small proportion of the total subsidized medium. The proportion may, for example clotting ⁇ ger than 10%, preferably less than 5%.
  • the engine may therefore be surrounded by an outer tube which extends circumferentially around the engine.
  • the outer tube may be in direct physical contact with the stator of the motor. In the longitudinal direction, the outer tube preferably extends at least over the length of the motor.
  • the outer tube may adjoin the annular gap and form an inner boundary for the annular gap. Due to the large-area contact between the outer tube and the annular gap, the heat can be dissipated effectively.
  • the engine may include an inner tube disposed between the stator and the rotor of the engine.
  • the inner tube ⁇ may be in direct physical contact with the stator.
  • a portion of the refrigeration cycle may extend through an annular gap between the inner tube and the rotor of the engine. Due to the large-area contact, the heat can be conducted both from the rotor and from the stator of the motor.
  • direct contact between the stator and the conveyed medium can be avoided by such an inner tube.
  • the cooling circuit is regularly insufficient to completely dissipate the heat generated in the rotor. So the engine heats up.
  • the motor and the surrounding housing according to the invention may be designed so that they have a high heat capacity. The heat ⁇ amount can be absorbed due to the high heat capacity in the motor and the temperature rise is limited.
  • the stator can be designed so that it associated therewith has a large mass and high varnishkapazi ⁇ ty.
  • the stator fills a Lekssab ⁇ section of the motor the gap between the inner tube and the outer tube completely, so that there are no cavities with heat-insulating effect.
  • the length section extends over the entire length of the motor.
  • a surrounding the winding heads of the stator space can be filled with a potting compound.
  • the inner pipe and the outer pipe of the engine can thus have the dual effect in that they on the one hand allow for a large-area contact to the cooling circuit and on the other hand define ei ⁇ NEN space can be cached within its excess heat ⁇ quantities.
  • the pump housing may be oriented ⁇ equipped with a vent valve, which opens when gaseous medium is conveyed, and which closes when the liquid medium is conveyed.
  • the gaseous medium can escape through the venting valve, so that as far as possible only liquid medium is conveyed through the outlet opening of the pump.
  • the bleeding Valve can be arranged between the output side of the working chamber and the outlet opening of the pump.
  • the venting valve opens in the annular gap between the outer tube and the pump housing.
  • the pump housing may have a plurality of venting valves .
  • One of the vent valves may be arranged in an upper portion of the pump housing, another breather ⁇ tion valves in a lower portion of the pump housing.
  • the pumps according to the invention are frequently used in installations in which it is of great importance that the pumped liquid does not escape to the outside. This purpose is useful when a side channel pump is used which is sealless. Sealless means that the end of the shaft on which the drive motor acts is located entirely within the pump housing. Since the shaft is not ge ⁇ passes through the casing to the outside, is at this point no shaft seal ER- conducive.
  • an impeller rotates.
  • the impeller is enclosed between two end faces of the working chamber, wherein the side channel is formed in one of the end surfaces.
  • the side channel corresponding to a recess in the end surface, which means that the interim ⁇ rule the impeller and the end face existing leak ⁇ gap is enlarged in the area of the side channel.
  • the Sei ⁇ tenkanal may outlet opening extending to the outlet port of the working chamber in an arcuate path from the input.
  • the arcuate path may substantially correspond to the path that the impeller also describes on the way from the inlet opening to the outlet opening. If the pump runs at overspeed as a fan and then liquid hits the input stage of the pump, this is associated with a sudden load on the pump.
  • the input stage of the pump should be designed to withstand this sudden load.
  • the input stage may be a centrifugal stage.
  • an impeller In a centrifugal stage, an impeller is provided with a plurality of passages extending from a central portion of the impeller to a peripheral portion of the impeller.
  • the pumping action of such a centrifugal stage results from the fact that the conveyed medium moves under the centrifugal force through the channel from the central area to the peripheral area.
  • the side channel pump according to the invention is provided with a control adapted to operate the pump at an overspeed when the working chamber of the pump is filled with gas and to reduce the speed to an operating speed when liquid enters the pump.
  • the controller is adapted to cause an active braking the pump.
  • the drive motor is designed so that it can pump even when operating with maxima ⁇ ler performance does not keep the overspeed after liquid has entered the pump.
  • the controller may therefore be arranged to wait for the liquid to enter until the speed has reduced itself to the desired operating speed and then increase the drive power so that the pump is kept constantly at the operating speed.
  • a preferred field of application of the pump according to the invention is the conveyance of liquefied gas from a tank. This takes place, for example, at LPG filling stations, where liquefied petrol vehicles are refueled from a tank that is often buried in the ground.
  • the tank is partially filled with liquid gas in the liquid state, the upper part of the tank and in particular the line which leads to the fiction, modern ⁇ pump are taken of vaporized liquefied gas.
  • the pressure in the tank and the line corresponds ie the vapor pressure of the liquefied gas when the pump is not in operation.
  • the suction power of the pump according to the invention is large enough that a reduction of the tempera ⁇ ture in the line is achieved, which means that the vapor pressure in the line is lower than the vapor pressure in the tank. Due to the pressure difference, the liquid from the tank rises into the pipe and can be sucked by the pump. With the method according to the invention it is therefore possible to convey the liquid gas in liquid form from the tank.
  • Fig. 1 a schematic representation of a erfindungsge ⁇ MAESSEN side channel pump
  • 2 shows an arrangement of a side channel pump according to the invention and a liquefied gas tank
  • FIG. 3 shows a further embodiment of a erfindungsge ⁇ MAESSEN side channel pump.
  • a shaft 14 is rotatably mounted in a pump housing 15.
  • the pump housing 15 is provided with an inlet opening 16 and an outlet opening 17, wherein the inlet opening 16 is arranged concentrically with the shaft 14. That the
  • Input opening 16 opposite end of Pumpengeophu ⁇ ses 15 is closed, so that the end of the shaft 14 is received in ⁇ within the housing 15.
  • the pump is sealless in the sense that there is no place where the interior and the exterior of the Pump are separated only by a shaft seal. This has the advantage that leakage of the conveyed medium can be reliably prevented.
  • a drive motor is accommodated in the pump housing 15 and comprises a rotor 19 connected to the shaft 14 and a stator 20.
  • a control electronics 35 the motor is controlled and in particular set the speed of the motor.
  • the pump according to the invention comprises two side channel stages, in each of which an impeller 22 rotates in a working chamber 23.
  • the impellers 22 have radially arranged wings with open vane spaces which are closely surrounded by the housing 15. Axial next to the impeller 22, the housing 15 forms an impeller 22 toward open Side channel 24, in which the fluid is conveyed by impulse exchange with the impeller 22.
  • the ⁇ A enters the end of the side channel 24 is located opposite a housing formed in the Ge ⁇ inlet opening of the working chamber 23, which is not visible in FIG. 1.
  • the medium entering through the inlet opening passes through the interstices of the wings to the side channel 24. From the outlet opening of the preceding working chamber 23, a channel 25 indicated only schematically in FIG.
  • the pump housing 15 extends through the pump housing 15 as far as the inlet ⁇ opening of the subsequent working chamber 23.
  • the pumped medium thus successively passes through the two side channel stages of the pump.
  • the input stage 26 of the pump is as centrifugal ge staltet ⁇ .
  • An impeller 27 connected to the shaft 14 is provided with channels 18 extending from a central portion to a peripheral portion of the impeller 27. The medium entering the channels 18 in the central area is moved outward by the centrifugal force. From the outer end of the impeller 27, a channel extends through the pump housing 15 to the inlet opening of the first working chamber 23.
  • the pump housing 15 surrounds the working chambers 23 of the pump and the motor 19, 20 at a distance, so that within the pump housing a working chambers 23 and the motor 19, 20 surrounding annular gap 40 is formed.
  • the output ⁇ side of the second side channel stage opens into the annular gap 40.
  • the outlet opening 17 of the pump is also on the
  • Annular gap 40 connected.
  • the conveyed by the pump medium thus moves from the output side of the second Side channel stage through the annular gap 40 to the outlet port 17 of the pump.
  • the stator 20 of the drive motor is surrounded by an outer tube 41.
  • the outer tube 41 extends along the motor and at the same time forms the inner boundary of the annular gap 40.
  • the stator 20 of the drive motor is limited by an inner tube 42.
  • the space between the inner tube 42 and the outer tube 41 is completely filled by the stator 20.
  • the stator 20 is in direct large-area contact with the inner tube 42 and the outer tube 41, so that a good heat transfer between the stator 20 and the inner tube 41 and the outer tube 42 is ensured.
  • the space between the stator 20 and the inner tube 42 and the outer tube 41 is filled with a heat-conducting potting compound 47.
  • the drive motor 19, 20 and the control electronics 35 extends from the annular gap 40, a plurality of channels 44 radially inwardly.
  • the channels 44 open into the motor gap 45 between the rotor 19 and the inner tube 42 of the stator 20.
  • the motor gap 45 extends over the entire length of the drive motor 19, 20 and merges into a gap 46 between the pump housing 15 and the
  • the gap 46 opens into the Ar ⁇ beitshunt 23 of the second side channel stage of the pump and is therefore referred to below as the chamber gap 46.
  • the channels 44, the engine gap 45 and the chamber gap 46 are components of a cooling circuit extending from the working chamber 23 of the second side channel stage through the Annular gap 40, the channels 44, the motor gap 45 and the Kam ⁇ merspalt 46 back into the working chamber 23 of the second side tenkanallace of the pump extends.
  • the cross section of the cooling circuit is substantially smaller than the cross section of the outlet opening 17, so that only a small portion of the conveyed medium moves as a cooling medium along the cooling circuit, while the larger proportion of ge faith ⁇ th medium leaves the pump through the outlet opening 17.
  • the cooling medium is in the cooling circuit by the pressure differential between the output side of the second side channel fans nallace the pump and the chamber gap 46 hold ⁇ ge in motion.
  • the pressure difference corresponds to about half the pressure difference between the input side and the output side of the second side channel stage of the pump.
  • the cooling circuit is designed so that it is in accordanceificflächi ⁇ contact with the inner tube 42 and the outer tube 41 of the stator 20 and thereby can dissipate heat from the stator 20 effectively.
  • the cooling circuit extends between the drive motor 19, 20 and the control electronics 35, so that at the same time the control electronics 35 is cooled.
  • the cooling medium is except for the stator 20 in a large-area contact with the rotor 19, so that this is also effectively cooled. After its return to the working chamber 23, the cooling medium mixes with the conveyed medium, which enters the working chamber 23 through the inlet opening, so that the heat absorbed by the cooling medium is distributed in the volume flow.
  • the cooling circuit is designed so that the erfindungsge ⁇ Permitted pump can be maintained in continuous operation at a constant operating ⁇ temperature when the pump requires a liquid medium. If, on the other hand, the pump conveys a gaseous medium, only a smaller amount of heat is removed and the pump heats up.
  • the motor is designed to have a high heat capacity.
  • Both the rotor 19 and the stator 20 are made very solid for this purpose.
  • the stator 20 has a high heat capacity will thereby he ⁇ sufficient that the space between the inner tube 42 is completely filled and the outer tube 41st
  • overheating is thus counteracted in two ways.
  • a massive amount of heat can be absorbed by the massive design.
  • a large amount of heat can be released by the large-area contact of the inner tube 42 and the outer tube 41 with the cooling circuit. This makes it possible to deliver gas over a period of, for example, more than 1 minute, without the pump overheating.
  • FIG. 1 An application example of the pump according to the invention is shown in FIG.
  • the pump 28 according to the invention is connected to a liquefied gas tank 29.
  • a riser 31 extends from the lower part of the tank 29 to the inlet opening 16 of the pump 28.
  • a conduit 34 is connected, which leads to a vehicle 32, which is to be refueled with LPG 30.
  • the flow rate of the pump is so great that it can not be completely absorbed by the car 32.
  • a separator 33 gas bubbles are separated from the flow and returned to the tank 29.
  • the tank 29 is filled to about one third with liquid gas 30. The remaining space in the tank 29 and in the
  • This speed is well above the speed at which the pump can be operated at maximum when fluid is being pumped.
  • the pump is operated at a speed of 3000 rpm, for example.
  • the liquid is conveyed with a volume flow of, for example, 35 m 3 / h.
  • the controller 35 is thus configured to operate the electric motor 21 at the low speed overspeed. As soon as liquid enters the pump, the resistance increases abruptly and the pump is slowed down. The controller 35 is designed so that it increases the power of the electric motor 21, as soon as the pump 28 is braked to operating ⁇ speed to keep the pump at this speed. This mode of operation is as long beibehal ⁇ th until the car is fully fueled 32nd Once this is the case, the pump 28 is turned off.
  • the pump housing 15 is provided with two vent valves 48, which open into the annular gap 46.
  • the vent valves 48 are open as long as gas is being delivered.
  • the vent Sven ⁇ tile 48 close when liquid medium is required. Referring to the embodiment of FIG. 2, the gas exiting through the vent valves 48, just like the gas separated with the separator 33, is directed back into the tank 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à canal latéral comprenant un carter de pompe (15) dans lequel sont disposés une chambre de travail (23) munie d'un canal latéral (24) et un moteur (19, 20), et comprenant une roue hélice (22), montée dans la chambre de travail (23), qui tourne avec un arbre (14) entraîné par le moteur (19, 20). Selon l'invention, un circuit de refroidissement (40, 44, 45, 46) s'étend de la chambre de travail (23) au moteur (19, 20) et du moteur (19, 20) à un étage d'aspiration (46) de la pompe. Le circuit de refroidissement (40, 44, 45, 46) est alimenté depuis une chambre de travail (23) dont le côté de sortie est relié à un orifice de sortie (17) de la pompe à canal latéral. La pompe permet d'aspirer du gaz sans que la pompe surchauffe.
EP15729508.0A 2014-06-24 2015-06-18 Pompe à canal latéral Active EP3161320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14173691 2014-06-24
PCT/EP2015/063741 WO2015197467A1 (fr) 2014-06-24 2015-06-18 Pompe à canal latéral

Publications (2)

Publication Number Publication Date
EP3161320A1 true EP3161320A1 (fr) 2017-05-03
EP3161320B1 EP3161320B1 (fr) 2021-02-24

Family

ID=51032957

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15729508.0A Active EP3161320B1 (fr) 2014-06-24 2015-06-18 Pompe à canal latéral

Country Status (4)

Country Link
US (1) US10704565B2 (fr)
EP (1) EP3161320B1 (fr)
CN (1) CN107076154B (fr)
WO (1) WO2015197467A1 (fr)

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DE102016103525A1 (de) * 2016-02-29 2017-08-31 Pierburg Gmbh Gebläse für einen Verbrennungsmotor
CN105673574B (zh) * 2016-03-18 2018-06-29 池泉 低噪音多级离心泵
CN109630427A (zh) * 2018-12-06 2019-04-16 广东威灵汽车部件有限公司 电子水泵及车辆
CN110185628B (zh) * 2019-05-30 2021-07-20 山东潍氢动力科技有限公司 多介质输送泵
CN110319027B (zh) * 2019-08-09 2024-05-28 苏州玲珑汽车科技有限公司 控制器侧面安装并附有冷却流道的汽车电子水泵及汽车
TWI715192B (zh) * 2019-09-12 2021-01-01 建準電機工業股份有限公司 流體輸送裝置
CN110725800A (zh) * 2019-11-12 2020-01-24 浙江理工大学 一种泵的电机散热及转速自动调节方法
EP4374077A1 (fr) 2021-07-21 2024-05-29 Pierburg Pump Technology GmbH Pompe à liquide à canal latéral électrique de véhicule automobile dotée d'un refroidissement par moteur
CN116428195A (zh) * 2023-03-29 2023-07-14 上海越圣智控环境科技有限公司 离心式冷媒泵

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FR2783884B1 (fr) * 1998-09-24 2000-10-27 Inst Francais Du Petrole Systeme de compression-pompage comportant une section de compression en fonctionnement alterne et son procede
EP1069313B1 (fr) * 1999-07-16 2005-09-14 Man Turbo Ag Turbo-compresseur
US6422838B1 (en) * 2000-07-13 2002-07-23 Flowserve Management Company Two-stage, permanent-magnet, integral disk-motor pump
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CN107076154B (zh) 2021-02-09
US10704565B2 (en) 2020-07-07
US20170130735A1 (en) 2017-05-11
CN107076154A (zh) 2017-08-18
WO2015197467A1 (fr) 2015-12-30
EP3161320B1 (fr) 2021-02-24

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