EP0185236B1 - Rotary-piston machine - Google Patents

Rotary-piston machine Download PDF

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Publication number
EP0185236B1
EP0185236B1 EP85115187A EP85115187A EP0185236B1 EP 0185236 B1 EP0185236 B1 EP 0185236B1 EP 85115187 A EP85115187 A EP 85115187A EP 85115187 A EP85115187 A EP 85115187A EP 0185236 B1 EP0185236 B1 EP 0185236B1
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EP
European Patent Office
Prior art keywords
rotary piston
sleeves
shafts
shaft
rotary
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
Application number
EP85115187A
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German (de)
French (fr)
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EP0185236A2 (en
EP0185236A3 (en
Inventor
Kurt Jauch
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Individual
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Individual
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Publication date
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Priority to ES85550024A priority Critical patent/ES8701296A1/en
Publication of EP0185236A2 publication Critical patent/EP0185236A2/en
Publication of EP0185236A3 publication Critical patent/EP0185236A3/en
Application granted granted Critical
Publication of EP0185236B1 publication Critical patent/EP0185236B1/en
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    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/126—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with elements extending radially from the rotor body not necessarily cooperating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • Rotary piston machines of this type have long been known, for example from DE-PS 23 243, GB-PS 575 350 and DE-AS 1 002 562.
  • each of the rotary pistons has a peripheral surface which completely surrounds the associated shaft and is composed of at least one cylindrical head surface, at least one likewise cylindrical foot surface and flanks which are, for example, involute-shaped and connect adjacent ends of associated head and foot surfaces with one another.
  • the two rotary pistons mesh with one another in the manner of a gear and their peripheral surfaces roll against each other when either one of the two shafts is driven so that the rotary piston machine pumps a fluid as a pump or blower, or when a fluid is supplied to the machine under pressure that drives the two rotary pistons , so that the machine releases a torque to the outside as a motor.
  • the gear-type intermeshing rotary pistons of known generic machines can only slip against one another without slip in those points in which imaginary pitch circles of the two rotary pistons touch each other. If, as is customary, the two shafts are connected to one another by gears of equal size that mesh directly with one another, then their pitch circles and also the pitch circles of the two rotary pistons are of the same size; their diameter corresponds to the center distance of the two shafts. In all points of the two rotary pistons that are not on the associated pitch circle, a slip is superimposed on their pitching motion, which increases with increasing distance from the pitch circle and reaches a maximum amount when a cylindrical head surface of a rotary piston rolls on the cylindrical base surface of another rotary piston.
  • the invention is therefore based on the object of developing a rotary piston machine in such a way that the flow losses are reduced and, insofar as they are unavoidable, less adversely affect the control behavior of the machine than before.
  • the invention keeps frictional resistances and the signs of wear caused thereby extremely low, since the rotatability of the sleeves according to the invention ensures this. that their lateral surfaces serving as foot surfaces roll on the top surfaces of the rotary pistons essentially without slip. A slight slippage can occur at the beginning of the engagement of a head surface with a foot surface until this foot surface has been accelerated to a peripheral speed which corresponds to that of the head surface.
  • each of the shafts is connected to each sleeve supported on it by a freewheel. This prevents the sleeves from being periodically braked to an angular velocity by frictional resistance, which is smaller than that of the associated shaft.
  • FIG. 1 to 3 has a housing 10 which is essentially composed of an upper, glasses-like cover plate 11 in FIG. 1 with two bearing inserts 12, only one of which is shown, a frame-like gear plate 13, also a frame-like one Cylinder plate 14 and a lower cover plate 15.
  • a shaft journal 16 of a shaft 17 extends through the illustrated bearing insert 12.
  • the shaft 17 and a shaft 18 are mounted parallel to each other in one of the bearing inserts 12 and in the lower cover plate 15.
  • An essentially annular sector-shaped rotary piston 27 or 28 is fastened to each of the webs 23, 24 with screws 25 or 26 or by brazing or spot welding or the like.
  • Each of the rotary pistons 27, 28 has a circular cylindrical head surface 29 or 30, which rests on the wall of the associated cylinder space 21 or 22 almost without play and thus in a sealing manner. 3 extends over an arc of 180 ° and is delimited in the circumferential direction by two involute flanks 31 and 32, respectively.
  • Each rotary piston 27, 28, as shown in FIG. 1, has a flat end face sealingly against the gear plate 13 or the lower cover plate 15.
  • a roller bearing 33 or 34 designed as a needle bearing in the illustrated example, is arranged, on which a sleeve 35 or 36 made of hardened steel is mounted.
  • the sleeves 35, 36 each have a circular cylindrical outer surface, which is essentially free of play and thus sealingly rests on a corresponding inner surface of the associated rotary piston 27 or 28 and is referred to below as the base surface 37 or 38.
  • the sleeves 37 and 38 are completely the same; their foot surfaces 37 and 38 have a diameter.
  • the two shafts 17, 18 rotate in the direction of arrow 41 and 42; a pneumatic or hydraulic delivery or working medium passes through an inlet 43 into the overlap region of the two cylinder spaces 21, 22 and flows out through an outlet 44.
  • a pneumatic or hydraulic delivery or working medium passes through an inlet 43 into the overlap region of the two cylinder spaces 21, 22 and flows out through an outlet 44.
  • inlet 43 and outlet 44 are separated from one another by the rotary pistons 27, 28 and sleeves 35, 36.
  • Each of the rotary pistons 27, 28 lies with its radially inner cylindrical surface on the base surface 37 or 38 of the associated sleeve 35 or 36 in such a way that it strives to take it along at the angular velocity of the two shafts 17, 18.
  • the top surface 29 or 30 of each rotary piston 27, 28 comes into engagement with the base surface 38 or 37 of the opposite sleeve 36 or 35; the sleeve in question is accelerated in such a way that the foot surface formed on it assumes the peripheral speed of the head surface rolling on it, so that the rolling takes place without slippage.
  • the angular velocity of the sleeve 35 or 36 concerned thus increases temporarily - in the embodiment according to FIGS. 1 to 3 for half a revolution.
  • the angular velocity of the sleeve 35 or 36 in question drops again to the amount of the angular velocity of the shaft 17 or 18, which is coaxial with it.
  • the periodic acceleration of the sleeves 35 and 36, which is carried out on the rotary piston 28 or 27 is required, takes place almost instantaneously, since the sleeves have only a low inertial mass and since the rolling, as described, takes place under radial prestress and is therefore capable of transmitting sufficient circumferential forces.
  • the sleeves 35 and 36 rest with one of their end faces on the gear plate 13 and on the cover plate 15, respectively.
  • the sleeves 35 and 36 should be fitted particularly closely between the gear plate 13 and cover plate 15 so that they seal in the desirable manner. Then, however, there are frictional resistances which endeavor to brake the sleeves 35 and 36 to a standstill in the time intervals in which they are not driven by a rotary piston 28 or 27 which is rolling on them.
  • each of the roller bearings 33 and 34 is preferably designed as a freewheel, via which each of the shafts 17 and 18 forces each of the associated sleeves 35 and 36 in the direction of the arrow 41 and 42, respectively takes along.
  • the rotary piston machine according to FIG. 4 differs from that shown in FIGS. 1 to 3 essentially in that each of the two rotary pistons 27 and 28 is divided into two sections of the same size as annular sectors. which are diametrically opposed to each other on the associated shaft 17 or 18. As a result, the shafts 17, 18 are free from imbalance, and the rotary piston machine is therefore suitable for higher speeds.
  • the two sections of the rotary piston 27 each extend over approximately 150 °, while the two sections of the rotary piston 28 each extend over approximately 30 ".
  • the two rotary pistons 27 and 28 thus complement each other as in the embodiment according to FIG 1 to 3 to a total of 360 ° minus a small angle which corresponds to a slight play between the intermeshing flanks 31 and 32.
  • the machine shown in Fig. 4 is primarily intended as a motor operated by compressed air.
  • FIG. 5 shows a further variant which is particularly suitable for high-speed, oil-operated engines.
  • This variant can be referred to as a synthesis from the two previous variants. It is common to the variant shown in FIGS. 1 to 3 that the two shafts 17, 18 are assigned the same size rotary lobes; the commonality with Fig. 4 is that each of the shafts 17, 18 are assigned two diametrically opposite rotary pistons 27 and 28 respectively. 5 each rotary piston 27 or 28 thus extends over 90 °. This ensures that the rotary piston machine runs particularly smoothly even at high speeds, for example 6000 per minute.
  • a fitting piece 45 shown in FIGS. 1 and 3 can be installed between each web 23, 24 and the associated rotary piston 27 and 28, respectively, which fixes the rotary piston in a precisely determined position .
  • the shafts 17 and 18 can be sealed directly axially next to the cylinder spaces 21 and 22. however, it is more advantageous if shaft seals 46 and 47 are each arranged at an axial distance from the two cylinder spaces 21 and 22 and a pressure relief duct 48 or 49 is worked into the gear plate 13 or the lower cover plate 15 in between. Depending on the type of working or delivery medium of the rotary lobe machine, the pressure relief ducts 48, 49 lead into the free environment, as shown in FIG. 1, into an oil reservoir or the like.
  • channels 50 which emanate from the head surfaces 29 and 30 in the area of the cylinder spaces 21, 22 under higher pressure and which open out on the adjacent flanks 31 and 32, respectively .
  • Such channels 50 have the course shown in FIG. 3 using the example of the rotary piston 27 when the rotary piston machine operates as a motor and is accordingly supplied with pressure oil or the like from the inlet 43.
  • flanks 31 and 32 which are preferably involute in profile, are preferably arc-shaped or arrow-shaped in the longitudinal direction, that is to say are designed like curved or arrow teeth, so that they do not come into contact with one another suddenly, but as gently as possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft eine Drehkolbenmaschine mit

  • - einem Gehäuse, in dem zwei Zylinderräume zwischen einem Einlaß und einem Auslaß einander radial überschneidend ausgebildet sind,
  • -zwei Wellen, die sich durch je einen der Zylinderräume erstrecken und zu gegensinniger Drehung miteinander verbunden sind, und
  • - zwei zueinander komplementären Drehkolben, die an je einer der Wellen befestigt sind und je eine zur zugehörigen Welle gleichachsige Kopffläche aufweisen, die periodisch mit dem Gehäuse und, im Überschneidungsbereich der beiden Zylinderräume, mit je einer zur Welle des komplementären Drehkolbens gleichachsigen Fußfläche Dichtungszonen bilden.
The invention relates to a rotary piston machine
  • a housing in which two cylinder spaces between an inlet and an outlet are radially overlapping,
  • two shafts, each of which extends through one of the cylinder spaces and is connected to one another in the opposite direction, and
  • - Two mutually complementary rotary pistons, which are fastened to one of the shafts and each have a top surface coaxial with the associated shaft, which form sealing zones periodically with the housing and, in the overlapping area of the two cylinder chambers, with a foot surface coaxial with the shaft of the complementary rotary piston.

Drehkolbenmaschinen dieser Gattung sind seit langem bekannt, beispielsweise aus der DE-PS 23 243, der GB-PS 575 350 und der DE-AS 1 002 562. Bei solchen bekannten Maschinen weist jeder der Drehkolben eine Umfangsfläche auf, welche die zugehörige Welle vollständig umschließt und sich zusammensetzt aus mindestens einer zylindrischen Kopffläche, mindestens einer ebenfalls zylindrischen Fußfläche und Flanken, die beispielsweise evolventenförmig gestaltet sind und benachbarte Enden zusammengehöriger Kopf- und Fußflächen miteinander verbinden. Die beiden Drehkolben greifen zahnradartig ineinander und ihre Umfangsflächen wälzen sich aneinander ab, wenn entweder eine der beiden Wellen angetrieben wird, damit die Drehkolbenmaschine als Pumpe oder Gebläse ein Fluid fördert, oder wenn der Maschine ein Fluid unter Druck zugeführt wird, das die beiden Drehkolben antreibt, damit die Maschine als Motor ein Drehmoment nach außen abgibt.Rotary piston machines of this type have long been known, for example from DE-PS 23 243, GB-PS 575 350 and DE-AS 1 002 562. In such known machines, each of the rotary pistons has a peripheral surface which completely surrounds the associated shaft and is composed of at least one cylindrical head surface, at least one likewise cylindrical foot surface and flanks which are, for example, involute-shaped and connect adjacent ends of associated head and foot surfaces with one another. The two rotary pistons mesh with one another in the manner of a gear and their peripheral surfaces roll against each other when either one of the two shafts is driven so that the rotary piston machine pumps a fluid as a pump or blower, or when a fluid is supplied to the machine under pressure that drives the two rotary pistons , so that the machine releases a torque to the outside as a motor.

Die zahnradartig ineinandergreifenden Drehkolben bekannter gattungsgemäßer Maschinen können sich ebenso wie normale Zahnräder nur in solchen Punkten schlupffrei aneinander abwälzen, in denen gedachte Wälzkreise der beiden Drehkolben einander berühren. Wenn die beiden Wellen, wie üblich, durch unmittelbar miteinander kämmende, gleichgroße Zahnräder miteinander verbunden sind, dann sind deren Wälzkreise und ebenso die Wälzkreise der beiden Drehkolben gleich groß; ihr Durchmesser stimmt mit dem Achsabstand der beiden Wellen überein. In allen nicht auf dem zugehörigen Wälzkreis liegenden Punkten der beiden Drehkolben ist deren Wälzbewegung ein Schlupf überlagert, der mit zunehmendem Abstand vom Wälzkreis zunimmt und einen größten Betrag jeweils dann erreicht, wenn eine zylindrische Kopffläche eines Drehkolbens sich an der zylindrischen Fußfläche eines anderen Drehkolbens abwälzt.The gear-type intermeshing rotary pistons of known generic machines, like normal gearwheels, can only slip against one another without slip in those points in which imaginary pitch circles of the two rotary pistons touch each other. If, as is customary, the two shafts are connected to one another by gears of equal size that mesh directly with one another, then their pitch circles and also the pitch circles of the two rotary pistons are of the same size; their diameter corresponds to the center distance of the two shafts. In all points of the two rotary pistons that are not on the associated pitch circle, a slip is superimposed on their pitching motion, which increases with increasing distance from the pitch circle and reaches a maximum amount when a cylindrical head surface of a rotary piston rolls on the cylindrical base surface of another rotary piston.

Um zu verhindern, daß dieser Schlupf im Betrieb erhebliche Reibungswiderstände hervorruft und zu einer raschen Zerstörung der Umfangsflächen der Drehkolben führt, ist es bei gattungsgemäßen Maschinen bisher üblich. den Achsabstand der beiden Wellen so zu wählen, daß zwischen den einander zugeordneten Kopf- und Fußflächen der beiden Drehkolben stets ein Spalt freibleibt: dieser Spalt muß im Ruhezustand verhältnismäßig groß sein, da die beiden Wellen im Betrieb von Druckkräften des strömenden Mediums zueinander hin gebogen werden können. Der Spalt zwischen Kopf- und Fußflächen, die sich somit nur theoretisch aneinander abwälzen, hat jedoch den Nachteil, daß ein vor allem im Teillastbetrieb erheblicher Anteil des strömenden Mediums zwischen den beiden Drehkolben hindurchströmt, wodurch Leistungsverluste auftreten und eine genaue Regelung der bekannten Maschinen erschwert oder sogar unmöglich gemacht wird. Vor allem als hydraulische oder pneumatische Drehkolbenmotoren haben bekannte gattungsgemäße Maschinen im Teillastbetrieb ein unbefriedigendes Regelverhalten; sie können bei Unterschreitung eines bestimmten Fluiddurchsatzes je Zeiteinheit plötzlich stehenbleiben, da das gesamte Fluid zwischen den Drehkolben hindurchströmt.In order to prevent this slippage from causing considerable frictional resistance during operation and to rapid destruction of the peripheral surfaces of the rotary lobes, it has so far been common in generic machines. to choose the center distance of the two shafts so that there is always a gap between the associated top and bottom surfaces of the two rotary pistons: this gap must be relatively large in the idle state, since the two shafts are bent towards each other during the operation of compressive forces of the flowing medium can. The gap between the top and bottom surfaces, which thus only roll theoretically against each other, has the disadvantage that a significant proportion of the flowing medium flows between the two rotary pistons, particularly in part-load operation, which results in power losses and makes precise control of known machines difficult or is even made impossible. Especially as hydraulic or pneumatic rotary lobe motors, known generic machines have an unsatisfactory control behavior in part-load operation; they can suddenly stop when the fluid flow falls below a certain level, since all the fluid flows between the rotary pistons.

Der Erfindung liegt deshalb die Aufgabe zugrunde, eine Drehkolbenmaschine derart weiterzubilden, daß die Strömungsverluste vermindert werden und, soweit sie unvermeidlich sind, das Regelverhalten der Maschine weniger beeinträchtigen als bisher.The invention is therefore based on the object of developing a rotary piston machine in such a way that the flow losses are reduced and, insofar as they are unavoidable, less adversely affect the control behavior of the machine than before.

Die Aufgabe ist bei einer Drehkolbenmaschine der eingangs beschriebenen Gattung erfindungsgemäß dadurch gelöst,

  • - daß zwischen jedem Drehkolben und der zugehörigen Welle mindestens eine Hülse abgedichtet angeordnet ist, gegenüber diesem Drehkolben auf der zugehörigen Welle drehbar gelagert ist und die zu " dieser Welle gleichachsige Fußfläche bildet, und
  • - daß jede der Fußflächen an der Kopffläche des komplementären Drehkolbens spielfrei abwälzbar ist.
The object is achieved according to the invention in a rotary piston machine of the type described in the introduction in that
  • - That between each rotary piston and the associated shaft, at least one sleeve is arranged in a sealed manner, is rotatably mounted on the associated shaft with respect to this rotary piston and forms the foot surface which is coaxial with this shaft, and
  • - That each of the foot surfaces on the top surface of the complementary rotary piston can be rolled without play.

Durch die spielfreie Abwälzung zwischen Kopf-und Fußflächen wird das hydraulische oder pneumatische Förder- oder Arbeitsmedium, mit dem die erfindungsgemäße Drehkolbenmaschine als Pumpe oder Motor betrieben wird, so gut wie vollständig daran gehindert, zwischen den genannten Flächen hindurchzuströmen. Strömungsverluste zwischen dem Gehäuse und den Kopfflächen sowie den Stirnflächen der Drehkolben lassen sich, wie schon bei bekannten gattungsgemäßen Drehkolbenmaschinen, verhältnismäßig gering halten; bei der erfindungsgemäßen Maschine sind somit die Strömungsverluste insgesamt gering und bleiben deshalb ohne wesentlichen Einfluß auf das Regelverhalten.Due to the play-free rolling between head and foot surfaces, the hydraulic or pneumatic delivery or working medium with which the rotary piston machine according to the invention is operated as a pump or motor is virtually completely prevented from flowing between the surfaces mentioned. Flow losses between the housing and the head surfaces and the end faces of the rotary lobes can, as in the case of known rotary lobe machines of the generic type, be kept relatively low; in the machine according to the invention the flow losses are thus low overall and therefore have no significant influence on the control behavior.

Gleichzeitig werden durch die Erfindung Reibungswiderstände und dadurch bedingte Verschleißerscheinungen äußerst gering gehalten, da die Drehbarkeit der erfindungsgemäßen Hülsen dafür sorgt. daß deren als Fußflächen dienende Mantelflächen sich im wesentlichen schlupffrei an den Kopfflächen der Drehkolben abwälzen. Ein geringfügiger Schlupf kann allenfalls zu Beginn des Eingriffs einer Kopffläche mit einer Fußfläche solange auftreten, bis diese Fußfläche auf eine Umfangsgeschwindigkeit beschleunigt worden ist, die mit derjenigen der Kopfflache übereinstimmt. Wegen der Drehbarkeit der Hüisen ist es jedoch ausgeschlossen, daß sich ein etwaiger Verschleiß an einer bestimmten Stelle konzentriert; wenn überhaupt, nutzen sich die Fußflächen derart gleichmäßig ab, daß sie rund bleiben.At the same time, the invention keeps frictional resistances and the signs of wear caused thereby extremely low, since the rotatability of the sleeves according to the invention ensures this. that their lateral surfaces serving as foot surfaces roll on the top surfaces of the rotary pistons essentially without slip. A slight slippage can occur at the beginning of the engagement of a head surface with a foot surface until this foot surface has been accelerated to a peripheral speed which corresponds to that of the head surface. However, because of the rotatability of the sleeves, it is impossible for any wear to concentrate at a certain point; if at all, the foot surfaces wear so evenly that they remain round.

Die erfindungsgemäße Drehkolbenmaschine kann dadurch weitergebildet sein,

  • - daß die Hülsen mit je mindestens einem Wälzlager auf der zugehörigen Welle gelagert sind und
  • - daß die aneinander abwälzbaren Kopf- und Fußflächen radial zueinander hin vorgespannt sind.
The rotary piston machine according to the invention can be further developed
  • - That the sleeves are mounted with at least one roller bearing on the associated shaft and
  • - That the mutually rollable head and foot surfaces are radially biased towards each other.

Durch diese Maßnahmen wird die Abdichtung zwischen Kopf- und Fußflächen noch verbessert und ihr Verschleiß besonders gering gehalten.These measures improve the seal between the head and foot surfaces and keep their wear particularly low.

Es ist besonders vorteilhaft, wenn jede der Wellen mit jeder auf ihr gelagerten Hülse durch einen Freilauf verbunden ist. Dadurch wird verhindert, daß die Hülsen durch Reibungswiderstände periodisch auf eine Winkelgeschwindigkeit abgebremst werden können, die kleiner als diejenige der zugehörigen Welle ist.It is particularly advantageous if each of the shafts is connected to each sleeve supported on it by a freewheel. This prevents the sleeves from being periodically braked to an angular velocity by frictional resistance, which is smaller than that of the associated shaft.

Eine bevorzugte Ausführungsform der Erfindung ist ferner dadurch gekennzeichnet,

  • - daß jeder Drehkolben über mindestens einen ringförmigen Steg mit der zugehörigen Welle verbunden ist, und
  • - daß jede Hülse axial neben dem zugehörigen Steg abdichtend angeordnet ist.
A preferred embodiment of the invention is further characterized in that
  • - That each rotary piston is connected to the associated shaft via at least one annular web, and
  • - That each sleeve is arranged sealingly axially next to the associated web.

Diese Ausführungsform kann dadurch weitergebildet sein,

  • - daß auf jeder der Wellen zwei Hülsen, durch einen mittig angeordneten Steg voneinander getrennt gelagert sind,
  • - daß die Hülsen mit je einer vom zugehörigen Steg abgewandten Stirnfläche gegen das Gehäuse abdichten und
  • - daß die Stege einen geringfügig kleineren Außendurchmesser haben als die zugehörigen Hülsen.
This embodiment can be developed by
  • that two sleeves are mounted on each of the shafts, separated from one another by a central web,
  • - That the sleeves seal with an end face facing away from the associated web against the housing and
  • - That the webs have a slightly smaller outer diameter than the associated sleeves.

Ausführungsbeispiele der Erfindung werden im folgenden anhand schematischer Zeichnungen mit weiteren Einzelheiten erläutert. Es zeigt:

  • Fig. 1 einen Längsschnitt einer erfindungsgemäßen Drehkolbenmaschine,
  • Fig. 2 den Querschnitt 11-11 in Fig. 1,
  • Fig. 3 den Querschnitt 111-111 in Fig. 1,
  • Fig. 4 einen der Fig. entsprechenden Querschnitt einer abgewandelten Drehkolbenmaschine und
  • Fig. 5 einen der Fig. 3 entsprechenden Querschnitt einer weiteren abgewandelten Drehkolbenmaschine.
Exemplary embodiments of the invention are explained in more detail below with the aid of schematic drawings. It shows:
  • 1 shows a longitudinal section of a rotary lobe machine according to the invention,
  • 2 shows the cross section 11-11 in Fig. 1,
  • 3 shows the cross section 111-111 in FIG. 1,
  • Fig. 4 is a cross-section corresponding to the Fig. Of a modified rotary engine and
  • 5 shows a cross section corresponding to FIG. 3 of a further modified rotary piston machine.

Die in Fig. 1 bis 3 dargestellte Drehkolbenmaschine hat ein Gehäuse 10, das sich im wesentlichen zusammensetzt aus einer in Fig. 1 oberen, brillenartigen Deckplatte 11 mit zwei Lagereinsätzen 12, von denen nur einer gezeichnet ist, einer rahmenartigen Getriebeplatte 13, einer ebenfalls rahmenartigen Zylinderplatte 14 und einer unteren Deckplatte 15. Durch den dargestellten Lagereinsatz 12 erstreckt sich ein Wellenzapfen 16 einer Welle 17. Die Welle 17 und eine Welle 18 sind parallel zueinander in je einem der Lagereinsätze 12 und in der unteren Deckplatte 15 gelagert.1 to 3 has a housing 10 which is essentially composed of an upper, glasses-like cover plate 11 in FIG. 1 with two bearing inserts 12, only one of which is shown, a frame-like gear plate 13, also a frame-like one Cylinder plate 14 and a lower cover plate 15. A shaft journal 16 of a shaft 17 extends through the illustrated bearing insert 12. The shaft 17 and a shaft 18 are mounted parallel to each other in one of the bearing inserts 12 and in the lower cover plate 15.

Auf den beiden Wellen 17 und 18 ist innerhalb der rahmenartigen Getriebeplatte 13 je ein Zahnrad 19 bzw. 20 befestigt; diese beiden Zahnräder sind gleich und kämmen gemäß Fig. 2 nahezu spielfrei miteinander.On the two shafts 17 and 18, a gear 19 and 20 is fixed within the frame-like gear plate 13; these two gears are the same and mesh with each other almost without play according to FIG. 2.

In der Zylinderplatte 14 sind gemäß Fig. 3 gleich achsig mit je einer der beiden Wellen 17 und 18 zwei Zylinderräume 21 und 22 ausgebildet, deren Durchmesser etwas größer ist als der Achsabstand der beiden Wellen, so daß die beiden Zylinderräume einander überschneiden. Im axial mittleren Bereich jedes Zylinderraums 21, 22 ist an der zugehörigen Welle 17 bzw. 18 ein kreisringförmiger Steg 23 bzw. 24 einstückig ausgebildet.In the cylinder plate 14, according to FIG. 3, with one of the two shafts 17 and 18, two cylinder spaces 21 and 22 are formed with the same axis, the diameter of which is slightly larger than the center distance of the two shafts, so that the two cylinder spaces overlap one another. In the axially central region of each cylinder space 21, 22, an annular web 23 or 24 is formed in one piece on the associated shaft 17 or 18.

An jedem der Stege 23, 24 ist mit Schrauben 25 bzw. 26 oder durch Hartlöten oder Punktschweißen oder dergleichen ein im wesentlichen kreisringsektorförmiger Drehkolben 27 bzw. 28 befestigt. Jeder der Drehkolben 27, 28 hat eine kreiszylindrische Kopffläche 29 bzw. 30, die nahezu spielfrei und somit abdichtend an der Wand des zugehörigen Zylinderraums 21 bzw. 22 anliegt. Jeder der beiden Drehkolben 27,28 erstreckt sich gemäß Fig. 3 über einen Bogen von 180° und ist in Umfangsrichtung durch zwei evolventenförmige Flanken 31 bzw. 32 begrenzt. Seitlich liegt jeder Drehkolben 27, 28 gemäß Fig. 1 mit je einer ebenen Stirnfläche abdichtend an der Getriebeplatte 13 bzw. der unteren Deckplatte 15 an.An essentially annular sector-shaped rotary piston 27 or 28 is fastened to each of the webs 23, 24 with screws 25 or 26 or by brazing or spot welding or the like. Each of the rotary pistons 27, 28 has a circular cylindrical head surface 29 or 30, which rests on the wall of the associated cylinder space 21 or 22 almost without play and thus in a sealing manner. 3 extends over an arc of 180 ° and is delimited in the circumferential direction by two involute flanks 31 and 32, respectively. Each rotary piston 27, 28, as shown in FIG. 1, has a flat end face sealingly against the gear plate 13 or the lower cover plate 15.

Auf jeder der Wellen 17, 18 ist beiderseits des zugehörigen kreisringförmigen Stegs 23 bzw. 24 je ein im dargestellten Beispiel als Nadellager ausgebildetes Wälzlager 33 bzw. 34 angeordnet, auf dem eine Hülse 35 bzw. 36 aus gehärtetem Stahl gelagert ist. Die Hülsen 35, 36 haben je eine kreiszylindrische Außenfläche, die im wesentlichen spielfrei und somit abdichtend an einer entsprechenden Innenfläche des zugehörigen Drehkolbens 27 bzw. 28 anliegt und im folgenden als Fußfläche 37 bzw. 38 bezeichnet wird. Die Hülsen 37 und 38 sind vollständig gleich; ihre Fußflächen 37 bzw. 38 haben einen Durchmesser. der geringfügig - um allenfalls wenige hundertstel Millimeter, größer als der Außendurchmesser des zugehörigen ringförmigen Stegs 23 bzw. 24 und so gewählt ist, daß jede Fußfläche 37, 38 einer Hülse 35 bzw. 36 an der Kopffläche 30 bzw. 29 des mit der jeweils anderen Hülse 36 bzw. 35 gleichachsigen Drehkolbens 28 bzw. 27 unter radialer Vorspannung abwälzbar ist.On each of the shafts 17, 18, on each side of the associated annular web 23 or 24, a roller bearing 33 or 34, designed as a needle bearing in the illustrated example, is arranged, on which a sleeve 35 or 36 made of hardened steel is mounted. The sleeves 35, 36 each have a circular cylindrical outer surface, which is essentially free of play and thus sealingly rests on a corresponding inner surface of the associated rotary piston 27 or 28 and is referred to below as the base surface 37 or 38. The sleeves 37 and 38 are completely the same; their foot surfaces 37 and 38 have a diameter. the slightly - at most a few hundredths of a millimeter, larger than the outer diameter of the associated annular web 23 or 24 and is chosen so that each foot surface 37, 38 of a sleeve 35 or 36 on the head surface 30 or 29 of the other Sleeve 36 or 35 coaxial rotary piston 28 or 27 can be rolled under radial prestress.

Unabhängig davon, ob die dargestellte Drehkolbenmaschine als Pumpe oder als Motor arbeitet, drehen sich die beiden Wellen 17, 18 in Richtung des Pfeils 41 bzw. 42; dabei gelangt ein pneumatisches oder hydraulisches Förder- oder Arbeitsmedium durch einen Einlaß 43 in den Überschneidungsbereich der beiden Zylinderräume 21, 22 und strömt durch einen Auslaß 44 ab. In jeder möglichen Drehwinkelstellung der beiden Wellen 17, 18 sind Einlaß 43 und Auslaß 44 durch die Drehkolben 27, 28 und Hülsen 35, 36 voneinander getrennt.Regardless of whether the rotary lobe machine shown works as a pump or as a motor, the two shafts 17, 18 rotate in the direction of arrow 41 and 42; a pneumatic or hydraulic delivery or working medium passes through an inlet 43 into the overlap region of the two cylinder spaces 21, 22 and flows out through an outlet 44. In each possible rotational angle position of the two shafts 17, 18, inlet 43 and outlet 44 are separated from one another by the rotary pistons 27, 28 and sleeves 35, 36.

Jeder der Drehkolben 27, 28 liegt mit seiner radial inneren Zylinderfläche derart auf der Fußfläche 37 bzw. 38 der zugehörigen Hülse 35 bzw. 36 auf, daß er bestrebt ist, diese mit derWinkelgeschwindigkeit der beiden Wellen 17,18 mitzunehmen. Im Verlauf jeder Umdrehung der beiden Wellen 17 und 18 kommt die Kopffläche 29 bzw. 30jedes Drehkolbens 27,28 mit der Fußfläche 38 bzw. 37 der gegenüberliegenden Hülse 36 bzw. 35 zeitweise in Eingriff; dabei wird die betreffende Hülse derart beschleunigt, daß die an ihr ausgebildete Fußfläche die Umfangsgeschwindigkeit der sich an ihr abwälzenden Kopffläche annimmt, so daß die Abwälzung schlupffrei stattfindet. Die Winkelgeschwindigkeit der betroffenen Hülse 35 bzw. 36 nimmt also vorübergehend - bei der Ausführungsform gemäß Fig. 1 bis 3 für eine halbe Umdrehung - zu.Each of the rotary pistons 27, 28 lies with its radially inner cylindrical surface on the base surface 37 or 38 of the associated sleeve 35 or 36 in such a way that it strives to take it along at the angular velocity of the two shafts 17, 18. In the course of each revolution of the two shafts 17 and 18, the top surface 29 or 30 of each rotary piston 27, 28 comes into engagement with the base surface 38 or 37 of the opposite sleeve 36 or 35; the sleeve in question is accelerated in such a way that the foot surface formed on it assumes the peripheral speed of the head surface rolling on it, so that the rolling takes place without slippage. The angular velocity of the sleeve 35 or 36 concerned thus increases temporarily - in the embodiment according to FIGS. 1 to 3 for half a revolution.

Nach dem Ende der Abwälzung sinkt die Winkelgeschwindigkeit der betroffenen Hülse 35 bzw. 36 wieder auf den Betrag der Winkelgeschwindigkeit der mit ihr gleichachsigen Welle 17 bzw. 18. Die periodische Beschleunigung der Hülsen 35 und 36, die für deren spielfreie Abwälzung am Drehkolben 28 bzw. 27 erforderlich ist, findet nahezu augenblicklich statt, da die Hülsen nur eine geringe träge Masse haben und da die Abwälzung, wie beschrieben, unter radialer Vorspannung stattfindet und somit zur Übertragung ausreichender Umfangskräfte imstande ist.After the end of the rolling, the angular velocity of the sleeve 35 or 36 in question drops again to the amount of the angular velocity of the shaft 17 or 18, which is coaxial with it. The periodic acceleration of the sleeves 35 and 36, which is carried out on the rotary piston 28 or 27 is required, takes place almost instantaneously, since the sleeves have only a low inertial mass and since the rolling, as described, takes place under radial prestress and is therefore capable of transmitting sufficient circumferential forces.

Die Hülsen 35 und 36 liegen mit je einer ihrer Stirnflächen an der Getriebeplatte 13 bzw. an der Deckplatte 15 an. Die Hülsen 35 und 36 sollten besonders eng zwischen Getriebeplatte 13 und Deckplatte 15 eingepaßt sein, damit sie in der wünschenswerten Weise abdichten. Dann entstehen aber Reibungswiderstände, die bestrebt sind, die Hülsen 35 und 36 in den Zeitintervallen, in denen sie nicht von einem sich an ihnen abwälzenden Drehkolben 28 bzw. 27 angetrieben werden, bis zum Stillstand abzubremsen.The sleeves 35 and 36 rest with one of their end faces on the gear plate 13 and on the cover plate 15, respectively. The sleeves 35 and 36 should be fitted particularly closely between the gear plate 13 and cover plate 15 so that they seal in the desirable manner. Then, however, there are frictional resistances which endeavor to brake the sleeves 35 and 36 to a standstill in the time intervals in which they are not driven by a rotary piston 28 or 27 which is rolling on them.

Um eine so weitgehende Abbremsung der Hülsen 35 und 36 zu verhindern, ist jedes der Wälzlager 33 und 34 vorzugsweise als Freilauf ausgebildet, über den jede der Wellen 17 und 18 jede der zugehörigen Hülsen 35 bzw. 36 in Richtung des Pfeils 41 bzw. 42 zwangsweise mitnimmt.In order to prevent the sleeves 35 and 36 from being braked as far as possible, each of the roller bearings 33 and 34 is preferably designed as a freewheel, via which each of the shafts 17 and 18 forces each of the associated sleeves 35 and 36 in the direction of the arrow 41 and 42, respectively takes along.

Die Drehkolbenmaschine gemäß Fig. 4 unterscheidet sich von der in Fig. 1 bis 3 dargestellten im wesentlichen dadurch, daß jeder der beiden Drehkolben 27 und 28 in zwei gleichgroße kreisringsektorförmige Abschnitte unterteilt ist. die einander diametral gegenüber an der zugehörigen Welle 17 bzw. 18 befestigt sind. Infolgedessen sind die Wellen 17, 18 frei von Unwucht, und die Drehkolbenmaschine eignet sich deshalb für höhere Drehzahlen. Die beiden Abschnitte des Drehkolbens 27 erstrecken sich im Beispiel gemäß Fig. 4 über je etwa 150°, während die beiden Abschnitte des Drehkolbens 28 sich über je etwa 30" erstrecken. Die beiden Drehkolben 27 und 28 ergänzen sich also wie bei der Ausführungsform gemäß Fig. 1 bis 3 auf insgesamt 360° abzüglich eines kleinen Winkels, der einem geringfügigen Spiel zwischen den miteinander kämmenden Flanken 31 und 32 entspricht. Die in Fig. 4 dargestellte Maschine ist vor allem als druckluftbetriebener Motor vorgesehen.The rotary piston machine according to FIG. 4 differs from that shown in FIGS. 1 to 3 essentially in that each of the two rotary pistons 27 and 28 is divided into two sections of the same size as annular sectors. which are diametrically opposed to each other on the associated shaft 17 or 18. As a result, the shafts 17, 18 are free from imbalance, and the rotary piston machine is therefore suitable for higher speeds. In the example according to FIG. 4, the two sections of the rotary piston 27 each extend over approximately 150 °, while the two sections of the rotary piston 28 each extend over approximately 30 ". The two rotary pistons 27 and 28 thus complement each other as in the embodiment according to FIG 1 to 3 to a total of 360 ° minus a small angle which corresponds to a slight play between the intermeshing flanks 31 and 32. The machine shown in Fig. 4 is primarily intended as a motor operated by compressed air.

In Fig. 5 ist eine weitere Variante dargestellt, die vor allem für schnellaufende, ölbetriebene Motoren geeignet ist. Diese Variante kann als Synthese aus den beiden vorangehenden Varianten bezeichnet werden. Mit der in Fig. 1 bis 3 dargestellten Variante ist ihr gemeinsam, daß beiden Wellen 17, 18 gleichgroße Drehkolben zugeordnet sind; die Gemeinsamkeit mit Fig. 4 besteht darin, daß jeder der Wellen 17, 18 zwei einander diametral gegenüberliegende Drehkolben 27 bzw. 28 zugeordnet sind. Gemäß Fig. 5 erstreckt sich somit jeder Drehkolben 27 oder 28 über 90°. Damit wird erreicht, daß die Drehkolbenmaschine auch bei hohen Drehzahlen von beispielsweise 6000 pro Minute besonders ruhig läuft.5 shows a further variant which is particularly suitable for high-speed, oil-operated engines. This variant can be referred to as a synthesis from the two previous variants. It is common to the variant shown in FIGS. 1 to 3 that the two shafts 17, 18 are assigned the same size rotary lobes; the commonality with Fig. 4 is that each of the shafts 17, 18 are assigned two diametrically opposite rotary pistons 27 and 28 respectively. 5 each rotary piston 27 or 28 thus extends over 90 °. This ensures that the rotary piston machine runs particularly smoothly even at high speeds, for example 6000 per minute.

Bei beiden Ausführungsformen gemäß Fig 1 bis 3 einerseits und Fig 4 andererseits kann zwischen jedem Steg 23. 24 und dem zugehörigen Drehkolben 27 bzw. 28 ein in Fig- 1 und 3 dargestelltes Paßstück 45 eingebaut sein, das den Drehkolben in einer genau bestimmten Lage fixiert.In both embodiments according to FIGS. 1 to 3 on the one hand and FIG. 4 on the other hand, a fitting piece 45 shown in FIGS. 1 and 3 can be installed between each web 23, 24 and the associated rotary piston 27 and 28, respectively, which fixes the rotary piston in a precisely determined position .

Die Wellen 17 und 18 können unmittelbar axial neben den Zylinderräumen 21 und 22 abgedichtet sein. es ist jedoch vorteilhafter, wenn Wellendichtungen 46 und 47 in je einem axialen Abstand von den beiden Zylinderräumen 21 und 22 angeordnet sind und dazwischen je ein Druckentlastungskanal 48 bzw. 49 in die Getriebeplatte 13 bzw. in die untere Deckplatte 15 eingearbeitet ist. Je nach Art des Arbeits- oder Fördermediums der Drehkolbenmaschine führen die Druckentlastungskanäle 48, 49 in die freie Umgebung, wie in Fig. 1 dargestellt, in einen Ölvorratsbehälter oder dergleichen.The shafts 17 and 18 can be sealed directly axially next to the cylinder spaces 21 and 22. however, it is more advantageous if shaft seals 46 and 47 are each arranged at an axial distance from the two cylinder spaces 21 and 22 and a pressure relief duct 48 or 49 is worked into the gear plate 13 or the lower cover plate 15 in between. Depending on the type of working or delivery medium of the rotary lobe machine, the pressure relief ducts 48, 49 lead into the free environment, as shown in FIG. 1, into an oil reservoir or the like.

Die frühzeitige Entstehung eines Öldrucks zwischen den paarweise zusammenwirkenden Flanken 31 und 32 kann durch Kanäle 50 gefördert werden, die in dem unter höherem Druck stehenden Bereich der Zylinderräume 21,22 von den Kopfflächen 29 und 30 ausgehen und an der benachbarten Flanke 31 bzw. 32 münden. Solche Kanäle 50 haben den in Fig. 3 am Beispiel des Drehkolbens 27 dargestellten Verlauf, wenn die Drehkolbenmaschine als Motor arbeitet und dementsprechend vom Einlaß 43 aus mit Drucköl oder dergleichen versorgt wird.The early development of an oil pressure between the flanks 31 and 32 interacting in pairs can be promoted by channels 50 which emanate from the head surfaces 29 and 30 in the area of the cylinder spaces 21, 22 under higher pressure and which open out on the adjacent flanks 31 and 32, respectively . Such channels 50 have the course shown in FIG. 3 using the example of the rotary piston 27 when the rotary piston machine operates as a motor and is accordingly supplied with pressure oil or the like from the inlet 43.

Die im Profil vorzugsweise evolventenförmigen Flanken 31 und 32 sind in Längsrichtung vorzugsweise bogen- oder pfeilförmig, sind also wie Bogen-oder Pfeilverzahnungen ausgebildet, damit sie nicht schlagartig, sondern möglichst sanft miteinander in Eingriff kommen.The flanks 31 and 32, which are preferably involute in profile, are preferably arc-shaped or arrow-shaped in the longitudinal direction, that is to say are designed like curved or arrow teeth, so that they do not come into contact with one another suddenly, but as gently as possible.

Claims (6)

1. A rotary piston engine, comprising
- a casing (10) in which two cylinder chambers (21, 22) are formed so as to overlap each other radially between an inlet (43) and an outlet (44),
- two shafts (17, 18), each extending through a respective one of the cylinder chambers (21, 22) and both being interconnected for rotation in opposite directions, and
-two complementary rotary pistons (27.28), each fixed to a respective one of the shafts (17, 18) and each including an addendum face (29, 30) coaxial with the corresponding shaft, the addendum faces periodically forming sealing zones with the casing (10) and, in the overlapping area of the two cylinder chambers (21, 22), with a respective dedendum face (38, 37) each of which is coaxial with the shaft (18, 17) of the complementary rotary piston (28, 27), characterized in that
- at least one sleeve (35, 36) is arranged between each rotary piston (27, 28) and the associated shaft (17, 18), in sealed fashion with respect to the respective rotary piston, is supported for rotation on the corresponding shaft (17, 18), and forms the dedendum face (37, 38) coaxial with this shaft, and
- in that each of the dedendum faces (37, 38) is adapted to roll off without clearance on the addendum face (30, 29) of the complementary rotary piston (28, 27).
2. The rotary piston engine as claimed in claim 1, characterized in that
- the sleeves (35, 36) each are supported on the corresponding shaft (17, 18) by at least one roller or ball bearing (33, 34), and in that
-the addendum and dedendum faces (29. 38: 30, 37) adapted to roll off each other are biased towards each other in radial direction.
3. The rotary piston engine as claimed in claim 1 or 2, characterized in that each of the shafts (17, 18) is connected by free-wheel means to each of the sleeves (35, 36) it carries.
4. The rotary piston engine as claimed in one of claims 1 to 3, characterized in that
- each rotary piston (27, 28) is connected with the corresponding shaft (17, 18) by at least one annular web (23, 24), and
- in that each sleeve (35, 36) is sealingly arranged axially next to the corresponding web (23, 24).
5. The rotary piston engine as claimed in claim 4, characterized in that
- two sleeves (35, 36) separated from each other by a centrally disposed web (23, 24) are supported on each of the shafts (17, 18),
- in that the sleeves (35, 36) each seal against the casing (10) by a respective end face remote from the corresponding web (23, 24), and in that
- the webs (23, 24) have a slightly smaller outer diameter than the corresponding sleeves (35, 36).
EP85115187A 1984-12-17 1985-11-29 Rotary-piston machine Expired EP0185236B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
ES85550024A ES8701296A1 (en) 1984-12-17 1985-12-17 Rotary piston fluid machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3445979A DE3445979C1 (en) 1984-12-17 1984-12-17 Rotary lobe machine
DE3445979 1984-12-17

Publications (3)

Publication Number Publication Date
EP0185236A2 EP0185236A2 (en) 1986-06-25
EP0185236A3 EP0185236A3 (en) 1988-02-03
EP0185236B1 true EP0185236B1 (en) 1989-09-27

Family

ID=6252991

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85115187A Expired EP0185236B1 (en) 1984-12-17 1985-11-29 Rotary-piston machine

Country Status (4)

Country Link
US (1) US4697999A (en)
EP (1) EP0185236B1 (en)
JP (1) JPS61182422A (en)
DE (2) DE3445979C1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3627962A1 (en) * 1986-08-18 1988-03-17 Kurt Jauch Rotary internal combustion engine
EP3144494B1 (en) * 2015-09-21 2018-11-07 Fuelsave GmbH Exhaust gas energy recovery system and method for exhaust gas energy recovery

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE246546C (en) *
US1257744A (en) * 1917-03-08 1918-02-26 Robert Schorr Rotary pump or compressor.
GB207065A (en) * 1922-12-29 1923-11-22 Alfred Hugh Tyler Improvements in or relating to rotary pumps, blowers, and the like
US2451603A (en) * 1944-10-04 1948-10-19 Virgil D Barker Rotary pump
DE1255848B (en) * 1961-12-27 1967-12-07 Daimler Benz Ag Rotary piston machine
US3799713A (en) * 1972-03-22 1974-03-26 Waukesha Foundry Co Positive displacement pump

Also Published As

Publication number Publication date
EP0185236A2 (en) 1986-06-25
DE3445979C1 (en) 1986-01-30
EP0185236A3 (en) 1988-02-03
US4697999A (en) 1987-10-06
JPS61182422A (en) 1986-08-15
JPH0252096B2 (en) 1990-11-09
DE3573290D1 (en) 1989-11-02

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