EP3214316B1 - Système et réducteur - Google Patents

Système et réducteur Download PDF

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Publication number
EP3214316B1
EP3214316B1 EP17000355.2A EP17000355A EP3214316B1 EP 3214316 B1 EP3214316 B1 EP 3214316B1 EP 17000355 A EP17000355 A EP 17000355A EP 3214316 B1 EP3214316 B1 EP 3214316B1
Authority
EP
European Patent Office
Prior art keywords
fan
air
transmission
fan blades
guide ring
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
EP17000355.2A
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German (de)
English (en)
Other versions
EP3214316A1 (fr
Inventor
Steffen Saar
Steffen Leonhard
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.)
SEW Eurodrive GmbH and Co KG
Original Assignee
SEW Eurodrive GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SEW Eurodrive GmbH and Co KG filed Critical SEW Eurodrive GmbH and Co KG
Publication of EP3214316A1 publication Critical patent/EP3214316A1/fr
Application granted granted Critical
Publication of EP3214316B1 publication Critical patent/EP3214316B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/288—Part of the wheel having an ejecting effect, e.g. being bladeless diffuser
    • 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F04D29/703—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps specially for fans, e.g. fan guards

Definitions

  • the invention relates to a system and a transmission series.
  • the DE 1 253 402 B discloses a noise reduction device on multi-bladed radial fans for ventilating electrical machines.
  • the fan blades are arranged irregularly according to a method described in more detail in the document, so that there are no adjacent pairs of fan blades which enclose the same angle.
  • a fan is known at the central hub fan blades are arranged at regular intervals.
  • the fan blades have a different curvature, so that their ends have irregular intervals.
  • a suction nozzle and an impeller for a fan with regularly arranged wings is known.
  • the suction nozzle has an elliptical cross section in a plane in which the axis of rotation of the fan is located.
  • the impeller is sheathed and has a similar elliptical cross-section as the suction nozzle.
  • the impeller is dimensioned such that after assembly of the fan, the sheath covers the stationary suction and rotates around it.
  • the fan has an inverted shell surrounding a hollow stump.
  • the hollow stump is connected to the shell by a set of oblique airfoils, the axial extent of the airfoils corresponding to the axial extent of the shell.
  • the fans consist of a radially outward open Fan, with a radially outwardly open annular air outlet opening is formed, which extends over the outer edges of the blades and rotates with the fan.
  • WO 97/09535 A discloses a radial impeller with regularly arranged fan blades, wherein the fan blades open in the radial direction are mounted between a front and a rear plate.
  • the fan blades are configured to extend radially farther outward on one of the two plates than on the other plate.
  • the invention is therefore based on the object to provide a system with at least one fan, in which the environmental impact is reduced.
  • the object is achieved in the case of the system according to the features indicated in claim 1 and in the transmission series according to the features specified in claim 9.
  • a fan with a fan with fan blades and a fan cover is included, the fan cover at least partially surrounds the fan and the fan cover has a range with axial air inlets, the fan blades in a first portion of the region with axial air inlets have a constant distance from the fan cover and in a second portion of the range with axial air inlets, the distance between the fan blades of the fan cover is greater than the constant distance in the first portion, in particular more than twice as large.
  • the fan blades are mounted on a base body, wherein the fan blades each have a plane of symmetry which contains the axis of rotation of the fan wheel.
  • the fan blades extend radially beyond the area with axial air inlets.
  • the cooling air is particularly advantageous sucked.
  • the fan wheel on a shaft of the transmission is arranged.
  • a separate motor for the drive of the fan is dispensable.
  • An advantageous embodiment of the system according to the invention is characterized in that a first fan blade to a first circumferentially adjacent fan blade has a first angular distance and the first fan blade to a second adjacent in the opposite direction fan blade has a second angular distance, wherein the first angular distance is smaller than the second Angular distance is.
  • the sequence in the circumferential direction of the angular distances from a respective wing to the fan blade adjacent in the circumferential direction comprises at least two different types of angular distance values.
  • the fan blades are not necessarily arranged regularly.
  • the advantage here is that the fan blades produce periodic excitations whose main frequency component is lower than would be the case if all angular distances were equal.
  • the frequency component is at most half that of a regular arrangement of the fan blades.
  • the fan blades in the circumferential direction, in particular along the circumference of the fan are irregularly spaced.
  • a large, and most preferably, the greatest possible reduction in the main frequency contribution of the fan blade-induced vibration excitations is advantageous reachable.
  • the noise pollution of the environment by the fan operation is thus at least subjectively reduced because the frequency of noise is placed below the hearing threshold or in areas in which the sensitivity to noise in human hearing is reduced.
  • resonance effects between the suggestions by the fan blades and vibrations by the operation of the transmission can be reduced.
  • each air duct is limited by at least fan blades, an air guide ring and / or a base body, wherein the cross section of the air channel has a minimum in the course from inside to outside.
  • air ducts are formed with a nozzle effect. These nozzles advantageously cause a directed flow of cooling air.
  • the minimum of the cross section of the air duct is effected by a minimum of the distance between the base body and the air guide ring, in particular by a minimum of the distance between the sectional figures of the body with an axial plane on the one hand and the air guide ring with the axial plane on the other.
  • the fan wheel advantageously comprises a main body, fan blades and an air guide ring, wherein the base body has a frustoconical region and form at least two fan blades, a segment of the frusto-conical region and a segment of the air guide a radially extending air channel whose cross-section has a minimum in the radial course.
  • the advantage here is that the fan is easily manufacturable, since the geometric properties of the air duct, in particular the nozzle shape, with the boundary surfaces of air guide ring and body is easy to manufacture and controllable.
  • the main body of the fan is occupied in addition to its holding function with a Heilleitmaschine. As a result, parts can be saved.
  • the cross section of the air guide ring is convex on its inner side and concave on its outer side, in particular shaped such that the wall thickness is substantially constant.
  • the consistency of the wall thickness depends on the manufacturing tolerances of the production technology and on the speeds at which the fan is used.
  • the outer shape of the air guide ring thus follows substantially the inner shape of the air guide ring, and it is an advantageous form of the air guide ring formed at the same time low material usage.
  • the advantage here is that for the Air guide little material must be used so that its mass moment of inertia is minimized.
  • the base body has a frustoconical region and the air guide ring is concentrically inscribed in a mathematical cone such that the air guide touches the mathematical cone in a first and a second axial region and in a third axial region between air guide ring and the mathematical cone a minimum distance is provided, wherein the third axial region is arranged between the first axial region and the second axial region, and at least two fan blades, a segment of the frusto-conical region and a segment of the air guide ring form an outwardly extending air channel.
  • the advantage here is that the constructional and manufacturing technology easy to handle geometric shapes, a nozzle-like air duct is available.
  • each air channel is characterized by a geometric size
  • the sequence of the geometric size of the air ducts is an irregular sequence in one revolution of the fan.
  • the geometric size of each air duct is the angle between the limiting fan blades or the angle of a limiting fan blade a fan-fixed reference direction.
  • the geometric size of each air duct is the angular position of the center of gravity or the center plane of the air duct or the angle of an excellent direction of the air duct to a fan-fixed reference direction.
  • the center of gravity formed by all the fan blades is in the center of the fan.
  • the maximum axial extent of the fan blades is greater than the maximum axial extent of the air guide ring.
  • the maximum axial extent of the fan blades is more than twice as large as the maximum axial extent of the air guide ring.
  • the advantage here is that a radial or laterally oblique discharge of the cooling air is made possible.
  • the fan is used in various transmissions or in general systems with fan.
  • the maximum radial extent of the fan blades is greater than the minimum radial extent of the air guide ring.
  • the advantage here is that large air outlets are formed, can be conducted through the cooling air to the housing to be cooled.
  • the fan blades on the suction side are axially retracted up to a radius, in particular by more than one third of the maximum axial extent of the fan blades.
  • the advantage here is that at a small distance from the fan, a fan cover can be placed, wherein at the intake ports or air inlets generated by the fan blades noise can be reduced.
  • each fan blade on a plane of symmetry in which preferably the axis of rotation of the fan is.
  • a rotationally invariable fan wheel is formed in a simple manner, and cooling air always flows in the same direction through the air channels.
  • the radial extent of the base body is smaller than the outer diameter of the fan wheel, in particular at least fifteen percent smaller than the inner diameter of the air guide ring.
  • the air ducts each form an air outlet, which comprises a radially aligned and an axially aligned portion.
  • the fan on different transmissions, especially directly in front of a housing wall or on a Kegelradtopf operable.
  • Important features of the invention of a transmission series with variants, each having a fan with fan and at least one gear stage, with an inventive Gear include, are that a fan wherein the fan as described above is formed according to the invention and that the fan is mounted in a first variant on the driving shaft of a bevel gear and that the fan mounted in a second variant on the driving shaft of a spur gear is.
  • air is preferably radially passable through air ducts and, in the second variant, air is directed through the air ducts at an angle to the radial direction and at an angle to the axial direction, in particular in an axial plane of the fan wheel obliquely to the axis of the fan wheel.
  • a housing wall of the transmission partially covers the air outlet of the air ducts in the first variant, in particular the axially oriented partial region of the air outlet.
  • FIG. 1 shows a fan for a fan of a transmission.
  • the fan wheel comprises at least one main body 10 with a hub 13, fan blades 11 and an air guide ring 12.
  • the fan is intended for mounting on a shaft of a gearbox.
  • the hub 13 is placed on the shaft for frictional connection with the same.
  • the fan wheel is driven by the shaft.
  • the shaft thus drives the fan blades 11, thereby producing an approximately radially or obliquely outwardly directed air flow.
  • This direction of the air flow is independent of the direction of rotation of the fan wheel, since each fan blade 11 has a plane of symmetry in which the axis of rotation of the fan wheel is located.
  • the main body 10, the air guide ring 12 and two adjacent fan blades 11 form air channels, is passed through the air flow.
  • FIG. 2 shows the back of the fan FIG. 1 , A support ring 20 of the main body 10 and the support edges 21 of each fan 11 are in a common plane.
  • the plane described is aligned parallel to the housing wall of the transmission and arranged at a small distance to this.
  • the fan with body, fan blades and guide ring is preferably made in one piece, in particular as a casting of aluminum or plastic, wherein in the case of use of plastic particularly preferably the plastic to avoid electrostatic charge is formed electrically conductive.
  • the fan is made of steel.
  • FIG. 3 shows a top view of the front of the fan after FIG. 1 ,
  • the fan blades 11 are mounted, wherein the fan blades 11 each have a plane of symmetry, which contains the axis of rotation of the fan.
  • the fan blades 11 are thus substantially, that is, apart from inclinations of the surfaces of the fan blades 11, perpendicular to an annular, frusto-conical region 35 of the base body 10th
  • Each fan blade 11 is arranged with respect to a fan-fixed reference direction 36 each at an angle w1.
  • the fan blades 11 are irregularly arranged: In particular, the difference amounts of each two angles w1 can not be represented as an integer multiple of a basic amount. Thus, resonance excitations are reduced by the fan blades 11, in particular, the frequency of the resonance excitations is reduced.
  • the fan is mounted on a gear shaft and the number of fan blades and the number of teeth of the gear shaft of the gear shaft have no common divider.
  • the number of fan blades and the number of teeth of each gear of the transmission has no common divider.
  • the irregular arrangement of the fan blades causes the excitation is generated during the passage of the fan blades 11 by a radially extending, fixed reference direction, the time course has a period that coincides with the rotation time of the fan.
  • w1.i denotes the angle w1 of the ith fan blade, where i is less than or equal to the total number n of the fan blades 11 -9 in the exemplary embodiment
  • the angle w1.1, w1.2, w1.3 is characterized by the consecutive sequence , ..., w1.n, w1.1, w1.2, w1.3, ... defines a periodic sequence of numbers whose smallest period length is just n.
  • the period length of the sequence of numbers is a number greater than one, preferably two, more preferably n / 2 or (n-1) / 2, whichever gives an integer in the latter alternatives.
  • the fan wheel on a mirror-symmetry plane, in which preferably the axis of rotation of the fan wheel is included.
  • the outer diameter of the main body 10 in FIG. 3 is much smaller than the outer diameter of the fan selected.
  • the outer diameter of the base body 10 is two-thirds of the outer diameter of the fan and thus of the air guide ring 12, and particularly preferably is the outer diameter of the body 10 reduced relative to the inner diameter of the air guide ring 12 by ten to twenty percent.
  • favorable flow conditions for the fan can be achieved.
  • the air guide ring 12 is composed of a first guide ring 33 and a second guide ring 34, which are each designed to be annular and frusto-conical.
  • the opening angle of the second guide ring 34 is selected larger than the opening angle of the first guide ring 33.
  • a first fan blade 31, a second fan blade 32, a segment 30 of the frusto-conical region 35 of the base body 10 and a segment 37 of the air guide ring 12 enclosed by the two fan blades 31, 32 form an air channel through which air flows during operation.
  • Each of these air ducts formed in this way has an opening angle or angular distance w2, ie the angle between the delimiting fan blades 31, 32, ie between two nearest neighbors, and an angle w3 of the center plane of the air duct with respect to a reference direction 36.
  • the opening angle w2 results thus in each case from the difference of the angle w1 to the limiting fan blades 31, 32.
  • the angle w3 differs in the example according to the FIG. 3 from the angles w1 to the limiting fan blades 31, 32 each by a constant, that is independent of the number of fan blades, amount.
  • the sequence of opening angles w2 and the sequence of angles w3 defines an irregular sequence of numbers.
  • angles w1, w2, w3 change accordingly.
  • excellent directions for example, directions of edges of the fan blades, are usable.
  • FIG. 4 shows a sectional view taken along in FIG FIG. 4 with AA designated axial plane.
  • the fan blades 11 have approximately rectangular recesses 40, so that the fan blades 11 in operation at a first area in the FIG. 4 from the top to be mounted fan cover at a shorter distance than in a second area.
  • This second area contains air inlets for the air supply to the fan, and by the recess 40 periodic vibration excitations at the air inlets are avoided by pasting the fan blades 10 in close proximity.
  • the main body 10 comprises at least one hub 13 for non-positive connection of the impeller on a shaft and a frusto-conical portion 35.
  • This frusto-conical portion 35 forms with the first guide ring 33 and the second guide ring 34 a nozzle-shaped air passage, wherein the nozzle-like constriction is approximately at the minimum Distance m is formed by air guide ring 12 and body 12.
  • This minimum distance m causes a minimum cross-section of the air channel delimited by a segment of the air guide ring 12, a segment of the frusto-conical region 35 and two adjacent fan blades 11, this cross section being assumed to be approximately at the same position as the minimum distance.
  • the exact position of the minimum cross section with respect to the minimum distance depends on the specific configuration of the cross section of the air guide ring 12 and the frusto-conical region.
  • the air guide ring 12 is formed at least from a first guide ring 33 and a second guide ring 34, wherein the opening angle of the frusto-conical first guide ring 33 is smaller than the opening angle of the frusto-conical second guide ring 34.
  • First guide ring 33 and second guide ring 34 are connected along a concentric ring.
  • the design of the opening angle of the guide rings 33, 34 is such that the air guide ring 12 can be inscribed into a conical surface 42, wherein the conical surface 42 contacts the air guide ring 12 at two concentric cutting circles 43, 44, but the conical surface 42 does not intersect the interior of the air guide ring 12 ,
  • the air guide ring 12 thus has an axial cross section, whose outer contour is concave.
  • a convex surface is formed on the inner side of the air guide ring 12 facing the shaft, where convex the property that the connecting line of two points on the inside of the air guide ring 12 always runs at least partially inside the air guide ring 12.
  • the inner contour of the cross section of the air guide ring 12 is thus curved with opposite signs as the outer contour of the cross section of the frusto-conical portion 35, in particular its radial outlet. Both contours are thus convex, with the convexities facing each other.
  • first guide ring 33 and second guide ring 34 results in a constriction and a minimum distance m, which causes a nozzle effect in the associated air duct.
  • the inside of the air guide ring is convex, but not described by two connected truncated cones, but by, for example, a parabolic or a circular arc-shaped cross-sectional contour. Even in these cases, a resulting cross-sectional constriction causes a nozzle effect with which an air flow can be conducted.
  • the air guide ring 12 does not extend axially over the entire length of the fan, in particular the fan blades 11. Rather, the second guide ring 34 terminates at an axial distance from the plane defined by the support ring 20. In this way, a radial opening 41 is formed for the air ducts through which - in the assembled state - air in the radial direction along the housing wall of the transmission can be conducted.
  • FIG. 5 shows a gear 50 with mounted fan 57.
  • a fan cover 51 surrounds the fan. For illustration is in FIG. 5 only one half of the fan cowl 51 is shown.
  • the hub 13 of the fan wheel sits on an intermediate part 54 and is non-positively connected thereto, wherein the intermediate part 54 in turn is arranged on a shaft 53 of the transmission and is at least positively connected thereto.
  • the shaft 53 is the driving shaft of the transmission 50.
  • the fan cover 51 has an annular area with air inlets 55, through which the fan draws air.
  • the axial orientation of the fan blades 11 causes, regardless of the direction of rotation is sucked in the same axial direction.
  • the suction side of the fan is clearly defined as the side through which the air flows.
  • the air ducts have an opening through which air therefore exits independently of the direction of rotation. Thus, an air outlet is formed.
  • the diameter of the area with air inlets 55 is equal to the inner diameter of the first guide ring 33.
  • the fan blades 11 strip past the air inlets 55 during a rotational movement.
  • the fan blades 11 each have a recess 40, so that only a portion of the area of the air inlets 55 is swept by the fan blades 11 at a small distance, while another, radially further inboard portion is covered at a greater distance.
  • the radial extent of the radially further inner subregion is greater than the radial extent of the radially outer subregion.
  • FIG. 6 shows the fan FIG. 5 in a side view.
  • the fan wheel is mounted above a bevel gear pot 61.
  • a gap 60 is provided between the fan cover 51 and the first guide ring 33.
  • the recess 40 of the fan blades 11 in the axial direction is about twice as long as the axial extent of the gap 60th
  • the provided along the radial boundary edge 22 of the fan blades 11 withdrawal of the second guide ring 34 allows mounting of the fan on a shaft which protrudes from a side wall of the transmission 50.
  • the fan is mounted directly in front of this side wall, and the moving of the fan blades 11 air flows radially outwards and thus along the housing wall.
  • the housing wall covers a portion of the air outlet of the air ducts, namely that portion which is axially aligned, the surface normal is thus arranged parallel to the shaft axis.
  • a series is formed in whose variants, such components that form the fan, in particular the fan, are uniformly used.
  • the variety of parts of the series is reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)

Claims (11)

  1. Système incluant un ventilateur (57) comportant une roue munie d'ailettes de ventilation (11), et un capot (51), le capot (51) du ventilateur entourant au moins en partie la roue dudit ventilateur, et ledit capot (51) du ventilateur présentant une région dotée d'admissions d'air axiales (55), sachant que les ailettes de ventilation (11) sont espacées d'une distance constante par rapport au capot (51) du ventilateur, dans une première zone partielle de la région dotée d'admissions d'air axiales et que, dans une seconde zone partielle de ladite région dotée d'admissions d'air axiales, la distance séparant lesdites ailettes de ventilation (11) d'avec ledit capot (51) du ventilateur est supérieure à la distance constante dans ladite première zone partielle, caractérisé par le fait que les ailettes de ventilation (11) sont implantées sur un corps de base (10), lesdites ailettes de ventilation (11) présentant, à chaque fois, un plan de symétrie qui contient l'axe de rotation de la roue du ventilateur ; et par le fait que lesdites ailettes de ventilation (11) sont en saillie au-delà de la région dotée d'admissions d'air axiales (55).
  2. Système selon la revendication 1, caractérisé par le fait que la distance séparant les ailettes de ventilation (11) d'avec le capot (51) du ventilateur est plus de deux fois supérieure, dans la seconde zone partielle, à celle de la première zone partielle.
  3. Système selon au moins l'une des revendications précédentes, lequel système est une transmission (50), caractérisé par le fait que la roue du ventilateur (57) est calée sur un arbre (53) de la transmission (50).
  4. Transmission (50) selon la revendication 3, caractérisée par le fait que la roue du ventilateur (57) est calée sur l'arbre menant (53) de ladite transmission (50).
  5. Transmission (50) selon la revendication 3 ou 4, caractérisée par le fait que la roue du ventilateur (57) est montée sur l'arbre menant d'un étage à engrenage conique, ou sur l'arbre menant d'un étage à engrenage cylindrique.
  6. Transmission (50) selon la revendication 5, caractérisée par le fait que le nombre des ailettes de ventilation (11), et le nombre de dents de la roue dentée de l'arbre menant (53), ne présentent aucun diviseur commun.
  7. Transmission (50) selon au moins l'une des revendications 3 à 6, caractérisée par le fait que le nombre des ailettes de ventilation (11), et le nombre de dents de chaque roue dentée de ladite transmission (50), ne présentent aucun diviseur commun.
  8. Transmission (50) selon au moins l'une des revendications 3 à 7, caractérisée par le fait qu'une paroi du carter de ladite transmission recouvre partiellement la sortie d'air des canaux de circulation d'air, en particulier la zone partielle à orientation axiale de ladite sortie d'air.
  9. Gamme de production de transmissions comprenant des variantes qui incluent, à chaque fois, un ventilateur équipé d'une roue et au moins un étage de transmission doté d'une transmission conforme à l'une des revendications précédentes, caractérisée par le fait que, dans une première variante, la roue du ventilateur est montée sur l'arbre menant d'un étage à engrenage conique ; et par le fait que, dans une seconde variante, ladite roue du ventilateur est montée sur l'arbre menant (53) d'un étage à engrenage cylindrique.
  10. Gamme de production de transmissions, selon la revendication 9, caractérisée par le fait que, dans la première variante, de l'air peut être guidé radialement par des canaux de circulation d'air et que de l'air peut être guidé par lesdits canaux de circulation d'air, dans la seconde variante, en décrivant un angle par rapport à la direction radiale ou en décrivant un angle par rapport à la direction axiale,
    en particulier dans un plan axial de la roue du ventilateur qui est incliné par rapport à l'axe de ladite roue du ventilateur.
  11. Gamme de production de transmissions, selon la revendication 9 ou 10, caractérisée par le fait que, dans la première variante, une paroi du carter de la transmission recouvre partiellement la sortie d'air des canaux de circulation d'air, en particulier la zone partielle à orientation axiale de ladite sortie d'air.
EP17000355.2A 2007-02-23 2008-01-22 Système et réducteur Active EP3214316B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007009369 2007-02-23
PCT/EP2008/000443 WO2008101577A2 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses
EP08707176.7A EP2122182B1 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP08707176.7A Division-Into EP2122182B1 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses
EP08707176.7A Division EP2122182B1 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses

Publications (2)

Publication Number Publication Date
EP3214316A1 EP3214316A1 (fr) 2017-09-06
EP3214316B1 true EP3214316B1 (fr) 2019-08-07

Family

ID=39316429

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08707176.7A Active EP2122182B1 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses
EP17000355.2A Active EP3214316B1 (fr) 2007-02-23 2008-01-22 Système et réducteur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08707176.7A Active EP2122182B1 (fr) 2007-02-23 2008-01-22 Roue de ventilateur, système et série de boîte de vitesses

Country Status (6)

Country Link
EP (2) EP2122182B1 (fr)
CN (2) CN103410775B (fr)
DE (1) DE102008010912B4 (fr)
HU (1) HUE045193T2 (fr)
PL (1) PL2122182T3 (fr)
WO (1) WO2008101577A2 (fr)

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EP3085997B1 (fr) * 2015-04-23 2020-07-22 Flender GmbH Déflecteur pour un engrenage et engrenage doté d'un déflecteur
CN104863893B (zh) * 2015-04-30 2017-09-22 广东美的制冷设备有限公司 风轮、风道、空气净化设备及风轮的制备方法
CN113054799B (zh) 2015-06-01 2022-07-26 深圳市大疆创新科技有限公司 用于耗散电机组件所产生热量的系统、套件和方法
WO2020164795A1 (fr) 2019-02-12 2020-08-20 Sew-Eurodrive Gmbh & Co. Kg Système d'entraînement comprenant un moteur électrique, une transmission et un adaptateur comprenant un ventilateur
CN113614413B (zh) 2019-03-26 2024-02-09 索尤若驱动有限及两合公司 具有风机装置的减速器
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Publication number Publication date
DE102008010912B4 (de) 2020-11-12
CN101617128B (zh) 2013-09-18
CN101617128A (zh) 2009-12-30
WO2008101577A3 (fr) 2008-10-16
CN103410775A (zh) 2013-11-27
CN103410775B (zh) 2016-08-10
EP2122182B1 (fr) 2019-05-01
EP2122182A2 (fr) 2009-11-25
EP3214316A1 (fr) 2017-09-06
PL2122182T3 (pl) 2019-10-31
WO2008101577A2 (fr) 2008-08-28
HUE045193T2 (hu) 2019-12-30
DE102008010912A1 (de) 2008-08-28

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