EP0482378B1 - Refroidisseur d'air pour pompes hydrauliques à huile - Google Patents

Refroidisseur d'air pour pompes hydrauliques à huile Download PDF

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Publication number
EP0482378B1
EP0482378B1 EP91116497A EP91116497A EP0482378B1 EP 0482378 B1 EP0482378 B1 EP 0482378B1 EP 91116497 A EP91116497 A EP 91116497A EP 91116497 A EP91116497 A EP 91116497A EP 0482378 B1 EP0482378 B1 EP 0482378B1
Authority
EP
European Patent Office
Prior art keywords
cooling
air
cooler
separate
pump
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.)
Expired - Lifetime
Application number
EP91116497A
Other languages
German (de)
English (en)
Other versions
EP0482378A1 (fr
Inventor
Bodo Dipl.-Ing. Jansen
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.)
Rahmer & Jansen GmbH
Original Assignee
Rahmer & Jansen 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 Rahmer & Jansen GmbH filed Critical Rahmer & Jansen GmbH
Priority to AT9191116497T priority Critical patent/ATE104751T1/de
Publication of EP0482378A1 publication Critical patent/EP0482378A1/fr
Application granted granted Critical
Publication of EP0482378B1 publication Critical patent/EP0482378B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04D29/4246—Fan casings comprising more than one outlet

Definitions

  • the invention relates to an air cooler according to the preamble of claim 1.
  • Such air coolers which are also referred to as cooling pump carriers, are used to cool the hydraulic oil by means of air in order to dissipate the heat loss.
  • the amount of heat to be dissipated is generally at least 15 to 25% of the installed drive power. For this reason, the use of appropriate coolers is necessary if the heat radiation surface of the oil tank and the other units is not sufficient.
  • oil-water coolers and oil-air coolers are also referred to as cooling pump carriers, the latter mostly being preferred because of the lower installation effort and the lower operating costs.
  • coolers In the oil-air coolers, a distinction is made in the oil hydraulics to separately arranged coolers, in which the air is blown through the cooling fins by means of an electrically operated axial fan and, on the other hand, so-called cooling pump carriers onto which the invention is directed.
  • cooling pump carriers onto which the invention is directed.
  • known coolers of this type the air from the radial fan mounted on the drive shaft is blown through the heat sink arranged concentrically around the fan.
  • the cooling pump bracket is a space-saving solution, since the cooler is integrated in the bellhousing, which is required anyway to flange the pump onto the motor. As a result of this, the installation space available for the cooler is very limited, since this is largely determined by the diameter of the motor on the one hand and by the installation length of the bellhousing on the other hand. The wavelength of the motor and pump and the installation dimensions of the shaft coupling have an influence on the latter dimension.
  • a bellhousing cooler in which the cooler extends over the entire circumference of the radial fan.
  • the cooler is composed of four elements which adjoin one another in terms of their circumference.
  • the cooling channels formed by the elements are flowed through in the circumferential direction by the pump medium to be cooled and air flows all around radially between the cooling fins.
  • the air enters in the area of two elements lying opposite one another and in the area of the other two elements displaced by 90 ° in the circumferential direction.
  • the cooler extends over the entire circumference and there is a screw on the pressure side of the radial fan in which the air is whirled around in a circle.
  • the air sucked in through the suction openings is deflected several times so that it can reach the internal suction area of the radial fan. This causes considerable flow losses.
  • the cheaper tube coolers While in the ring coolers the tool costs and the manufacturing costs are very expensive, the cheaper tube coolers have the disadvantage that the required amount of heat is not dissipated in most applications. Due to the small cross-section, the finned tube only allows part of the oil flow to be cooled or only the leak oil to pass through, and the relatively short tube length also does not offer a sufficiently large cooling surface. In addition, the tubes are smooth-walled on the inside, so that generally no turbulent but only a laminar flow is formed in the oil flow, which leads to an unfavorable heat transfer due to the layer formation in the liquid flow. For these reasons, the effect of the tube cooler is unsatisfactory.
  • a common design feature of bellhousing coolers that have become known so far is that cooling air inlet and outlet take place directly alongside one another on the entire circumference of the cooler.
  • This has two major drawbacks.
  • at least one air boundary layer results from the opposing air movements, in which vortex formation occurs, the movement components of which cancel each other out.
  • at least some of the heated, exiting air can return to the cooler with the intake air and heat up continuously in a cycle.
  • the heating of the intake air leads to a decrease in the temperature difference between air and oil, with which the thermal output of the cooler is reduced proportionally.
  • there is the described reduction in the flow velocity of the air and thus the amount of air per unit of time which likewise have a very disadvantageous influence on the air-side heat transfer and the amount of heat dissipated.
  • the invention has for its object to provide an air cooler of the type mentioned, i.e. to create a cooling pump carrier, which has an improved cooling effect and can therefore be used not only as a leak oil cooler, but in particular as a main flow cooler due to sufficient cross sections. Not only should the efficiency be improved, but it should also be possible to produce at low cost.
  • the cooling air inlet and cooling air outlet are separated from one another on the circumference.
  • the cooler which is divided into individual heat sinks, is only arranged where the air is discharged.
  • the free areas serve the cooling air entry, so that a mixture of emerging, heated cooling air and suction air is avoided. This improves efficiency.
  • commercially available, straight or prismatic heat sinks can be used, which can be dimensioned sufficiently to achieve any desired liter output (flow rate), are much cheaper than ring coolers, for example, and which dissipate a significantly higher heat output than the tube coolers described.
  • the heat sink can also be arranged so that the pressure chambers can be designed as pressure channels, depending on how much space is available. This enables a largely straight-line air flow through the cooling fins. Depending on what is structurally permissible, the coolers can be pulled apart to achieve an optimal length of the pressure channels and thus an optimal flow of air.
  • the heat sinks are essentially straight, mass-produced and commercially available components that are integrated into the bellhousing, preferably so that they face each other.
  • the suction openings - again preferably two - are through which the cooling air enters the suction chamber and finally axially into the radial fan.
  • a further increase in the oil flow rate can be achieved in that the two heat sinks (claim 2) are connected in parallel, so that two parallel or even two separate cooling circuits are possible.
  • the air cooler is designed as specified in claim 5, then a good and fluidically effective division of the cooling air exiting radially from the radial fan is ensured.
  • the cooling air is distributed evenly over the heat sinks, ensuring that the cooling air enters the heat sinks as effectively as possible.
  • the bellhousing cooler 9 shown in the drawing is arranged between a drive motor 6 and a pump 7 or screwed to these parts, an elastic, structure-borne sound-absorbing intermediate element 8 being provided between bellhousing cooler 9 and pump 7.
  • the bellhousing cooler consists of a radial fan 10 which is mounted on the drive shaft 11 in the area of a clutch 12.
  • pressure chambers 1 and 1a are provided, which are separated from one another by lugs 2 and 2a, as is apparent when viewing FIG. 1.
  • These lugs 2, 2a also serve as air guiding surfaces which direct the cooling air in such a way that it strikes the air channels of the heat sinks 5 and 5a as perpendicularly as possible.
  • the pressure chambers 1 and 1a practically form pressure channels, by means of which it is possible to blow the escaping air as straight as possible through the cooling fins. Depending on the installation conditions, these pressure channels can be designed in such a way that optimal flow conditions and thus a correspondingly good cooling are guaranteed.
  • the air enters through suction openings 3 and 3a into a suction chamber 13 on one side of the radial fan 10 (see FIG. 2).
  • the inlet opening for the cooling air in the radial fan is formed by edges 4, so that a kind of funnel is created for axial entry into the interior of the radial fan.
  • the two heat sinks 5 and 5a are opposite to each other.
  • the scope is divided so that there are separate areas for cooling air inlet and cooling air outlet, so that there is no undesired mixing.
  • the heat sinks are of conventional construction, so that so-called turbulator plates are used both in the oil-carrying channels and in the air passages. As a result, laminar flow in the oil channels is avoided even with smaller amounts of oil and at speeds of oil and air, and good heat transfer is thus achieved.
  • splitting the cooler into at least two separate heat sinks enables operation as indicated in Fig. 5, i.e. the heat sinks are connected in parallel. If two parallel liquid flows - and not two separate cooling circuits - are provided, then the arrangement of the heat sinks according to FIG. 5 is selected such that the sum of the frictional resistances of the liquid flow through the heat sink 5 is equal to the sum of the frictional resistances through the heat sink 5a, so that a uniform distribution of the cooling flows between the two heat sinks is guaranteed.
  • the design of the bellhousing cooler is chosen so that it can be mounted in a vertical arrangement on a lid, for example the container lid of a hydraulic tank, as shown in FIG. 3, as well as in FIG. 4 in a horizontal arrangement in connection with a foot motor or separately on Bellhousing foot to be flanged.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (5)

  1. Dispositif de refroidissement par air pour pompes hydrauliques à huile, qui est intégré dans le support de pompe destiné au bridage de la pompe (7) sur le moteur d'entraînement (6),
       comportant un ventilateur radial (10) monté sur l'arbre d'entraînement (11) doté d'une chambre d'aspiration axiale (13) et d'un radiateur disposé autour de celle-ci, caractérisé par le fait que le radiateur est subdivisé en plusieurs, de préférence deux, corps de refroidissement (5, 5a) séparés, présentant entre eux un écart dans le sens périphérique auxquels arrivent un nombre correspondants de courants (1, 1a) d'air de refroidissement séparés,
       et que des orifices d'aspiration (3, 3a) conduisant à la chambre d'aspiration sont disposés de façon décalée par rapport aux corps de refroidissement sur la périphérie dans la zone définie par l'écart entre ces corps de refroidissement.
  2. Dispositif de refroidissement par air selon la revendication 1, caractérisé par le fait que les corps de refroidissement (5, 5a) sont montés en parallèle par rapport au flux d'huile hydraulique qui doit être refroidi (figure 5).
  3. Dispositif de refroidissement par air selon la revendication 1 ou 2, caractérisé par le fait que les deux corps de refroidissement (5, 5a) et les orifices d'aspiration (3, 3a) sont les uns et les autres disposés à la périphérie de façon diamétralement opposée, le diamètre sur lequel sont situés les corps de refroidissement étant sensiblement perpendiculaire au diamètre sur lequel sont situés les orifices d'aspiration.
  4. Dispositif de refroidissement par air selon une ou plusieurs des revendications 1 à 3, caractérisé par le fait que les chambres de pression formées par les courants d'air séparés (1, 1a) sont séparées les unes des autres par des saillies qui s'approchent tangentiellement par l'extérieur du bord du ventilateur, et qui sont disposées et conformées de façon telle que l'air de refroidissement attaque sensiblement perpendiculairement la surface d'entrée du corps de refroidissement correspondant (5, 5a).
  5. Dispositif de refroidissement par air selon l'une ou plusieurs des revendications précédentes, caractérisé par le fait que l'entrée d'air axiale, à la sortie de la chambre d'aspiration (13) et à l'entrée du ventilateur radial (10) est constituée par un bord (4) circulaire rentré vers l'intérieur en forme de trémie.
EP91116497A 1990-10-25 1991-09-27 Refroidisseur d'air pour pompes hydrauliques à huile Expired - Lifetime EP0482378B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT9191116497T ATE104751T1 (de) 1990-10-25 1991-09-27 Luftkuehler fuer hydraulikoelpumpen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4033954 1990-10-25
DE4033954 1990-10-25

Publications (2)

Publication Number Publication Date
EP0482378A1 EP0482378A1 (fr) 1992-04-29
EP0482378B1 true EP0482378B1 (fr) 1994-04-20

Family

ID=6417039

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91116497A Expired - Lifetime EP0482378B1 (fr) 1990-10-25 1991-09-27 Refroidisseur d'air pour pompes hydrauliques à huile

Country Status (3)

Country Link
EP (1) EP0482378B1 (fr)
AT (1) ATE104751T1 (fr)
DE (1) DE59101440D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9402736U1 (de) * 1993-06-23 1994-07-07 Ktr Kupplungstechnik Gmbh, 48432 Rheine Pumpenträger mit integriertem Ölkühler
EP0665379B2 (fr) * 1994-01-11 2003-08-27 Ktr Kupplungstechnik Gmbh Support d'une pompe avec refroidisseur d'huile intégré
ITBO20120298A1 (it) * 2012-05-31 2013-12-01 Spal Automotive Srl Unita' di ventilazione.
ITBO20120682A1 (it) 2012-12-18 2014-06-19 Spal Automotive Srl Macchina elettrica
JP6319514B2 (ja) * 2015-04-28 2018-05-09 株式会社デンソー 送風機

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2750967C2 (de) * 1977-11-15 1979-12-06 Flutec Fluidtechnische Geraete Gmbh, 6603 Sulzbach Vorrichtung zum Verbinden eines Antriebsmotors und einer Pumpe
GB2017216B (en) * 1978-03-13 1982-10-27 Imi Fluidair Ltd Rotary positive-displacement fluid-machines
GB2088960A (en) * 1980-11-13 1982-06-16 Imi Fluidair Ltd Rotary Positive-displacement Gas Compressors
DE3312490A1 (de) * 1983-04-07 1984-10-11 Flutec Fluidtechnische Geräte GmbH, 6603 Sulzbach Vorrichtung zum verbinden je eines gehaeuses eines antriebsmotors und einer pumpe

Also Published As

Publication number Publication date
DE59101440D1 (de) 1994-05-26
ATE104751T1 (de) 1994-05-15
EP0482378A1 (fr) 1992-04-29

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