EP1995408B1 - Unité de pompage d'une pompe à palettes - Google Patents

Unité de pompage d'une pompe à palettes Download PDF

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Publication number
EP1995408B1
EP1995408B1 EP07425310.5A EP07425310A EP1995408B1 EP 1995408 B1 EP1995408 B1 EP 1995408B1 EP 07425310 A EP07425310 A EP 07425310A EP 1995408 B1 EP1995408 B1 EP 1995408B1
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EP
European Patent Office
Prior art keywords
vanes
rotor
vane
profile
stator
Prior art date
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Application number
EP07425310.5A
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German (de)
English (en)
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EP1995408A1 (fr
Inventor
Carlo Pachetti
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.)
O M P Officine Mazzocco Pagnoni Srl
Original Assignee
O M P Officine Mazzocco Pagnoni Srl
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Publication date
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Priority to EP07425310.5A priority Critical patent/EP1995408B1/fr
Publication of EP1995408A1 publication Critical patent/EP1995408A1/fr
Application granted granted Critical
Publication of EP1995408B1 publication Critical patent/EP1995408B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to a pumping unit for a variable displacement vane pump.
  • the pumping unit of the present invention comprises a plurality of vanes, a rotor and a stator having an internal profile for vane sliding action, and is specifically provided for an oil pump for use on variable displacement radial vane vehicle pumps.
  • the pump as a whole will not be described, but exclusively the pumping unit: vanes, rotor and internal profile of the stator, and any elements that may replace the respective components generally present on all current radial vane pumps.
  • the vanes are fixed, so that they can move in a desmodromic manner, by rings or possibly a piston that are floating and practically concentric with the stator ring, and on which the sides of the vanes opposite those that slide on the stator ring rest.
  • the vanes mechanically constrained by both the rings/piston and the internal profile of the stator, can move desmodromically inside their own drive cavities present in the rotor.
  • the vanes due to the lack of the action exercised by the centrifugal force and because of the sticking effect with their respective seat in the rotor caused by high oil viscosity, tend to remain stationary and completely inserted in their cavities, consequently annulling the specific pumping function of the pump.
  • the rings, or possibly the piston solve the problems described above by imposing the translation motion of the vanes against any hindrance to movement. But, because the rings or piston act against any type of action that attempts to prevent vane translation inside the cavities, said rings or piston in turn become a critical aspect for the pump.
  • any action that prevents vane translation (such as grit or excessive friction between the vane and its seat) generates forces between vane and ring that are discharged, generally amplified by the ring in question, to the other vanes (due to the fact that the vanes are activated in directions that differ from that which generates the overload action) and thus to the sliding surface of the stator, creating wear both between the vane and the rings/piston as well as between the vane and the stator surfaces.
  • the rings, or possibly the piston do not prevent the vanes whose centre of gravity is at a certain distance from the centre of rotation of the rotor, also because of the space occupied by the rings, from exercising a strong contact pressure between the vane heads and the stator at high revolution speed. Such strong contact pressure is provoked by the centrifugal forces which are consequently also high. This leads to extreme wear on both vanes and stator.
  • a further problem often encountered in radial vane pumps due to the use of rings/piston is that the rings/piston occupy radial space in the pump and therefore prevent pump use for certain applications where an extreme compactness in the direction of the diameter is required.
  • the object of the present invention is to provide a pumping unit, in particular for oil pumping and for vehicle application, free of the drawbacks described previously.
  • a pumping unit has been conceived in order to eliminate the aforesaid problems wherein the drawbacks connected with wear on the vane and stator profile caused by vane friction have been basically eliminated.
  • the present invention there is a considerable reduction in the centrifugal force and force of inertia acting on the vanes and causing these problems.
  • the vanes of the unit of the present invention cross the rotor diametrically, and both ends of each vane are simultaneously in contact with the stator profile, their centre of gravity is located very close to the rotor centre of rotation, and consequently centrifugal action and low level inertia are generated, these being proportional to the distance between the centre of gravity and the centre of rotation.
  • the present invention eliminates the need to use rings/piston, and consequently also all problems involving wear and failure; in fact, the desmodromic function performed by the rings/piston in traditional radial vane pumps is now intrinsically obtained through the combination of diametric vanes and stator profile.
  • the constraint of maintaining the two ends of the vane simultaneously in contact with the stator profile allows during the rotor rotation a desmodromic motion to be performed by the translation of the vane inside its cavity on the rotor.
  • the absence of rings which have to be housed within the rotor contributes towards reducing diametral rotor size considerably and consequently, this means that the diameter size of the pump which contains this type of pumping unit is also reduced to a large extent.
  • An example of a non-variable displacement pump with diametric vanes is given in FR440.750 .
  • the numeral 10 is used to indicate the pumping unit of the present invention.
  • This pumping unit 10 comprises a stator 12 inside which a cavity ( figures 1, 2 ) having a surface with a profile 12a is formed.
  • the profile 12a is defined by two profile portions: a first portion belonging to the sector defined by the points p, q, t, having any possible continuous decreasing curve up point q and increasing curve up to point t, among which also the semicircular curve shown in figures 1 and 2 , and a second portion belonging to the sector defined by points t, z, p having a non-semicircular curve; aim and shape of this geometry will be described more clearly further on.
  • a rotor 16 is housed inside the stator cavity 12.
  • the rotor 16 is driven in rotation by a motor shaft 16d integral with the rotor 16, partially shown in figure 2 , and supported inside the pump by means that are not illustrated, but which operate on said shaft 16d and on an upper portion 16c of the shaft 16d which is always integral with the rotor 16.
  • the shaft 16d rotates around a Z-Z axis (centre C1 in figure 1 ).
  • the rotor 16 and the portion 16c of the shaft 16d have a plurality of diametric openings 16b, which are three in number in the embodiment illustrated, but not necessarily limited to the number in this example.
  • a vane 21, 22, and 23 passes through each one of these diametric openings 16b.
  • the geometry of the vanes 21, 22, 23, see figure 3 or the equivalent vanes shown in figures 4-5 , identified respectively by numerals 31, 32, 33 and 41, 42 43.
  • Each of said vanes has a geometrical conformation conceived to permit a simultaneous free crossing action through centre C1 of rotor 16. More particularly, the vanes 21, 22, 23 in figure 3 , and those in figures 4-5 , have central openings 21b, 22b, 23b that form connecting branches between the two symmetrical parts of the vane, each one having a height of H/3, more generally, if the number of vanes is represented by Np, and the height by H, the height of the lowered branches will be H/Np.
  • vanes 21, 22, 23 (hereafter only these vanes will be referred to in the description since the same conditions apply throughout to the vanes in figures 4-5 in the same way) are inserted by vertical mounting only in the diametric openings 16b of rotor 16, and at the same time in the upper appendage 16c of the shaft 16d in the same sequence shown in figure 3 , in such a manner that branch H/3 of the vane 22 is positioned centrally in relation to the branches H/3 of the vanes 21, 23.
  • FIG 2 it is shown that the sectors of the portion 16c of shaft 16d forming a single piece with rotor 16 are centrally threaded so that they can be pushed by means of a conical screw 19 onto a reinforcement ring 18.
  • This solution creates a continuous surface on the portion 16c of shaft 16d because of the presence of the ring 18, this surface being conceived to cooperate successively with a bushing, thus making the rotor 16 more rigid and strong. This also permits vane disassembly and reassembly.
  • the profile 12a is realized in such a manner that all the points of the profile of the sector t, z, p are generated from the ends 21a 22a 23a of any one of the vanes when the corresponding opposite end slides on the generator profile of sector p, q, t moving from p to t.
  • this profile can also be an arc of circumference tangent to rotor 16 in point q. In this way, the distance of points p, t and q, z of the profile 12a will be the same as the length L of the vane.
  • each vane will be constrained to remain in constant contact with the profile 12a, thus forcing the vane in question to slide inside the opening 16b with a translation movement which can be defined as desmodromic.
  • an eccentricity e between rotor and stator as the distance between the rotor centre C1 and the stator centre C2, defined as that point, distant from C1 as half the difference between the vane length L and the diameter of the rotor Dr.
  • the profile 12a conceived as previously described is extremely advantageous when the pumping unit 10 is used also for variable displacement pumps. It is common knowledge that there is a variation in displacement according to the variation in eccentricity e and that displacement will be zero when the stator centre C2 is set over the position of the rotor centre C1. In order to maintain efficient the pumping function for any eccentricity value, the compartment 17a set over the Y-Y axis that separates the intake area from the pumping unit delivery must be hermetically sealed, that is, the clearance between the head of the vanes 21 and 22 and the profile 12a must be very small and less than 5/100 of millimetres, this being a value for which the fluid dynamics function of the pumping unit, even when the oil temperature is very high, is still guarantee.
  • the ratio e/L>0.08 could generate in compartment 17a clearance between vanes and stator profile higher than those necessary for a good volumetric performance of the pumping unit 10.
  • figure 4 shows a set of vanes 31, 32, 33 geometrically similar to those in figure 3 but having the prerogative of eliminating any clearance between vanes and the stator profile for any work eccentricity value of pumping unit 10 and in any angular position the vanes may assume in relation to the Y-Y axis.
  • the vanes 31, 32, 33 are each composed of three overlaid layers having a thickness of s/3 (where s is the thickness of the vane).
  • the two external layers 31a, 32a, 33a which are identical on all vanes, are geometrically configured like the vanes 21, 22, 23 but are slightly shorter by approximately 0.2 ⁇ 0.3 mm, while the internal layer contained between the previous two layers is composed of three elements: the two end sliding shoes 35 which are conceived to recover, when subjected to the centrifugal force, the clearance between vanes and stator profile and the central element 31b 32b, 33b that acts as a spacer for the sliding shoe and that together with the sliding shoe has a geometrical configuration equal to the vanes 21, 22, 23 and with the same length L.
  • the central body 31b, 32b, 33b of each vane has two rectangular openings, indicated with 35c, where the sliding shoes 35 are positioned by insertion of the respective rectangular projections 35a.
  • the sliding shoes are bound axially to the central body 31b, 32b, 33b of the vanes, being free to recover the radial clearance due to their sliding motion within the two container layers 31a, 32a, 33a of each vane.
  • the solution with layer vanes allows using steel for the external layers and plastic materials for the central element, and different suitable plastic materials for the spacer element and for the sliding shoes.
  • Figure 5 shows another embodiment of the vanes 41, 42, 43 wherein, compared to the vanes 21, 22, 23 in figure 3 , vertical projections 45 having a semicircular shape are provided protruding from opposite sides of the vane; the generatrices 45b of the highest points of these projections become the supporting and sliding points for the vanes inside the diametric openings 16b on the rotor.
  • This vane embodiment provides the transformation of the type of contact of the prismatic couple defined by the vane with its own seat 16b, from surface to surface contact to the contact between a surface and a line 45b.
  • This specific line-surface coupling which forms a cavity between the vane and hollow 16b, is capable of collecting small impurities that may be present in the machine oil without causing malfunction which prevents free vane sliding in their seats, as would occur in the case of surface to surface contact.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (7)

  1. Pompe à palettes à débit variable, comprenant une unité de pompage (10) ayant un stator (12), un rotor (16) et une pluralité de palettes (21, 22, 23, 31, 32, 33, 41, 42, 43) entraînées par ledit rotor (16) et définissant entre elles une pluralité de compartiments de pompage (17a), les palettes de ladite pluralité de palettes (21, 22, 23, 31, 32, 33, 41, 42, 43) ayant chacune un ensemble d'ouvertures (21b,22b,23b) dans une position centrale de celles-ci, et étant adaptées pour couper le rotor (16) diamétralement, en s'entrecroisant réciproquement entre elles librement au centre (C1) dudit rotor (16), chaque palette (21, 22, 23, 31, 32, 33, 41, 42, 43) étant insérée dans une ouverture diamétrale respective (16b) prévue dans ledit rotor (16) de manière que la rotation dudit rotor (16) génère le mouvement desdites palettes (21, 22, 23, 31, 32, 33, 41, 42, 43) avec les deux extrémités (21a, 22a, 23a) de chaque palette restant constamment en contact avec un profil (12a) à l'intérieur du stator (12), dans laquelle ladite pluralité de palettes (21, 22, 23, 31, 32, 33, 41, 42, 43) peut être généralement composée d'un nombre Np de palettes tel que Np≥3, ces palettes générant un nombre Nv de compartiments (17a) tel que Nv=2Np, dans laquelle une portion (t, z, p) dudit profil (12a) est générée par l'une quelconque desdites extrémités (21a,22a,23a) des palettes quand l'autre extrémité opposée correspondante décrit une courbe semi-circulaire (p, q, t) qui est tangente en un point (q) sur ledit rotor (16), en déterminant un centre de stator (C2) comme le point ayant une distance par rapport au centre (C1) dudit rotor (16) qui mesure la moitié de la différence entre la longueur (L) des palettes et le diamètre (Dr) dudit rotor (16), et par conséquent excentrée par rapport à (C1) d'une quantité e=C1-C2, dans laquelle ledit rotor comprend un profil externe (16a), caractérisée en ce que les palettes (21, 22) qui, conjointement audit profil (12a) du stator (12) et au profil (16a) du rotor (16), définissent un compartiment communicant (17a) entre l'aspiration d'huile et le refoulement d'huile, ont un dégagement (C1-C2*) avec ledit profil (12a) du stator (12) entre zéro et un maximum de 0,05 pour n'importe quelle valeur d'excentricité de fonctionnement (e), avec 0≤(C1-C2*)≤e quand Np≥3 et quand le rapport entre l'excentricité maximale (e) et la longueur de palette (L) est ≤0,08.
  2. Pompe selon la revendication 1, dans laquelle lesdites palettes (21, 22, 23) sont abaissées centralement au moyens desdites ouvertures (21b, 22b, 23b) et ont une hauteur égale à H/3 dans les zones abaissées, où H est la hauteur de la palette.
  3. Pompe selon la revendication 2, dans laquelle au moins deux desdites palettes (21, 23) ont la même forme et au moins une autre palette (22) a une forme qui est différente par rapport aux palettes précédentes.
  4. Pompe selon la revendication 3, dans laquelle, si Np est le nombre des palettes, la hauteur abaissée est égale à H/Np et le nombre de palettes ayant une même forme est Np/2 pour Np pair et (Np-1)/2)+1 pour Np impair.
  5. Pompe selon l'une quelconque des revendications précédentes, dans laquelle lesdites palettes (31, 32, 33) sont capables de rétablir le dégagement entre les extrémités de palette et ledit profil (12a) du stator (12) quand e/L>0,08 et dans laquelle, à l'intérieur de chacune desdites palettes (31, 32, 33), contenus entre deux couches (31a, 32a, 33a) de chaque palette (31, 32, 33), chacun ayant une épaisseur de s/3, deux patins coulissants (35) sont logés, dans une position axiale par rapport aux palettes (31, 32, 33) au moyen de saillies (35a) qui sont logées dans des sièges respectifs (35c) du corps central (31b, 32b, 33b) des palettes (31, 32, 33), ledit patin de coulissement (35) étant adapté pour coulisser dans une direction radiale par rapport audit corps central (31b, 32b, 33b), celui-ci étant également adapté pour coulisser par rapport auxdites deux couches de palette (31a, 32a, 33a).
  6. Pompe selon l'une quelconque des revendications 1 à 4, dans laquelle lesdites palettes (41, 42, 43) ont une paire de parties en saillie spécifiquement profilées (45) avec des génératrices (45b) qui reposent sur les ouvertures diamétrales respectives (16b) dudit rotor (16).
  7. Pompe selon l'une quelconque des revendications précédentes, dans laquelle ledit rotor (16) comprend une première portion (16d) sur un côté qui agit comme un arbre d'entraînement, solidaire dudit rotor (16), et sur le côté opposé, lui-même solidaire dudit rotor (16), une deuxième portion (16c) configurée dans des secteurs définis par les ouvertures (16b) dudit rotor (16), à l'intérieur duquel est logé un capuchon conique fileté (19) conçu pour pousser lesdits secteurs de ladite deuxième portion (16c) sur un anneau de renforcement (18) adapté pour coopérer avec une bague.
EP07425310.5A 2007-05-22 2007-05-22 Unité de pompage d'une pompe à palettes Active EP1995408B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07425310.5A EP1995408B1 (fr) 2007-05-22 2007-05-22 Unité de pompage d'une pompe à palettes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07425310.5A EP1995408B1 (fr) 2007-05-22 2007-05-22 Unité de pompage d'une pompe à palettes

Publications (2)

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EP1995408A1 EP1995408A1 (fr) 2008-11-26
EP1995408B1 true EP1995408B1 (fr) 2016-06-29

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021027524A1 (fr) * 2019-08-09 2021-02-18 汤斌 Pompe à rotor de translation et moteur

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR440750A (fr) * 1912-02-29 1912-07-19 Robert Abels Pompe rotative de refoulement
DE1001198B (de) * 1955-05-11 1957-01-17 Schmidt Paul Drehkolbenmaschine mit bewegbaren Kolben
FR2086986A5 (fr) * 1970-04-15 1971-12-31 Gonzalez Paul
DE3149720A1 (de) * 1981-12-15 1983-07-21 Schwäbische Hüttenwerke GmbH, 7080 Aalen Fluegelzellenluftpumpe
US5711268A (en) * 1995-09-18 1998-01-27 C & M Technologies, Inc. Rotary vane engine
JP2006063952A (ja) * 2004-08-30 2006-03-09 Toyota Motor Corp ベーンポンプ
DK176286B1 (da) * 2005-06-08 2007-06-11 Tetra Laval Holdings & Finance Indretning til indblanding af partikulært fyld såsom nougat- eller frugtstykker i spiseismasse og fremgangsmåde

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021027524A1 (fr) * 2019-08-09 2021-02-18 汤斌 Pompe à rotor de translation et moteur

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