EP0205942B1 - Hydraulic transmission - Google Patents

Hydraulic transmission Download PDF

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Publication number
EP0205942B1
EP0205942B1 EP86107003A EP86107003A EP0205942B1 EP 0205942 B1 EP0205942 B1 EP 0205942B1 EP 86107003 A EP86107003 A EP 86107003A EP 86107003 A EP86107003 A EP 86107003A EP 0205942 B1 EP0205942 B1 EP 0205942B1
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EP
European Patent Office
Prior art keywords
cam
pressure
piston
motor
cylinder
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Expired
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EP86107003A
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German (de)
French (fr)
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EP0205942A1 (en
Inventor
Alfred Dr. Christ
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Sulzer Escher Wyss AG
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Sulzer Escher Wyss AG
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Priority to AT86107003T priority Critical patent/ATE35722T1/en
Publication of EP0205942A1 publication Critical patent/EP0205942A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/02—Systems with continuously-operating input and output apparatus

Definitions

  • the invention relates to a device for the hydraulic transmission of mechanical power and for the simultaneous translation of the speed.
  • a typical example of such a transmission is to transfer the power of a low-pressure water turbine, which is to be installed as deep as possible, to a generator, which is preferably built up at machine floor level. Due to the small gradient, the turbines have to rotate slowly, with the typical speed in the range of 100 rpm. lies.
  • the generator should run as quickly as possible, e.g. B. between 1000-1500 U / min., Because this results in cheaper designs than slow-running four-pole generators.
  • a gear ratio of 1:10 or 1:15 would be desirable here. Even if it were possible according to the arrangement, such a large transmission ratio would cause difficulties in a gearbox or belt drive, in particular because of the small size of the pinion, respectively. of the small belt pulley.
  • the hydraulic direct current transmissions with oil pump, pressure transmission line, oil motor, return line, supplemented by an auxiliary system, which provides for feeding, cooling and filtering, are known for power transmissions of all kinds.
  • the object of the invention is to remedy this.
  • a cam disk of a cylinder piston pump driven by a drive shaft with a cam track with n essentially sinusoidal elevations and depressions on the circumference has a sine curve arranged in the area of a sine curve Number of plungers and pistons and an equal number of transmission lines, each with a hydraulic cylinder filled with hydraulic medium, attached to the cylinder of the piston via a same number of cylinders with pistons of a cylinder-piston engine, which are also attached without a valve, a drive, the cam track being designed so that the rotation is even the cam disk of the pump and the shaft of the motor the volume of the system filled with hydraulic medium, d.
  • Pump cylinder displacement, transmission line and engine cylinder displacement always remain constant, for which purpose a space of selectable pressure is provided, which is connected to all transmission lines via throttle units.
  • Figure 7 shows another embodiment of an applicable motor.
  • the power transmission with speed transmission is ensured by means of a device which works on the principle of hydraulic AC power transmission.
  • the power is transferred from a pump P as a drive to a motor M.
  • a cam disk 2 with generally n, essentially sinusoidal elevations and depressions is provided on the circumference of a cam track 3.
  • n 4 is shown.
  • the cam track is actuated by rollers 17 or tappets 4, pistons 5 in cylinders 6 in a likewise essentially sinusoidal cycle.
  • the transmission lines 7 filled with hydraulic fluid six of which are shown in FIG. 1, lead to the hydraulic motor M.
  • Each of the transmission lines is connected to a cylinder 8 without a valve, and the cylinders are preferably arranged in a star shape around a crank drive 10. All pistons 9 of the hydraulic motor act on this crank drive 10. It is this crank drive 10 which, with its crank-connecting rod ratio and the roller-diameter ratio on the drive shaft 1, determines the exact contour of the cam track 3. The contour is determined in such a way that with uniform rotation of the pump and the motor in all cylinder transmission line systems 6, 7, 8 filled with the hydraulic fluid, ie in the pump cylinder displacement plus the transmission line space plus the engine cylinder the displacement, the enclosed fluid volumes are constant over time.
  • a feed device which can feed in or take out small amounts of hydraulic fluid from a room 11 of selectable pressure, each connected via a throttle unit 12 to a point of a transmission line 7.
  • this feed device it is possible to achieve a smooth run, to prevent the tappets 4 from lifting off the cam disk 2 or the cam track 3, and to ensure that the transmission synchronizes itself when the vehicle starts off. At the same time, the manufacturing accuracy of the cam shape or cam track 3 is subject to significantly lower requirements.
  • the pressure that one chooses in this space 11 depends on the transmitted power and possibly also on the speed. It is expediently set so that it is in the range of 70-130% of the time pressure average in a transmission line.
  • This pressure is provided with a small auxiliary pump and an adjustable pressure limiter, both not shown, via a feed line 33 which leads into the room 11.
  • the throttle units 12, which are connected between the space 11 and the transmission lines 7, can, as shown in detail in FIG. 2, as parallel multiple throttles, for example with two throttle points 14 and 13 connected in parallel with a flow area of the same size or different size are formed, wherein the flow paths can optionally be released or blocked with valves 15, 16.
  • the tappets 4, which move the pistons 5 arranged around the cam disk 2 are advantageously designed as roller tappets with rollers 17 in order to avoid sliding wear. If still greater forces have to be mastered, then several rollers 17 are used to actuate a plunger 19, which are then combined to form a bogie-like structure 18 and act in this way on the piston 5, as is shown in detail in FIG. 4 is shown.
  • sliding shoe tappets of hydrodynamic operation can also be used, or preferably also pressure shoe tappets with hydrostatic lubrication known per se.
  • the pressure lubricating fluid for these hydrostatic impacts 21 is advantageously taken from the cylinder space of the cylinder 6 or the transmission line 7 via throttle bores 23 and 22.
  • the feed device must then be dimensioned in accordance with this fluid consumption.
  • the dimensioning of such hydrostatically supported plungers must take into account the difference in the radius of curvature of the cam surface 3.
  • the tappet surface which is in hydrostatically supported contact with the cam disk surface 3 can be subdivided into narrow, transversely positioned individual surfaces 24, 25 which are movable relative to one another, as is shown in detail in FIG.
  • the arrangement of the tappets 4 on the circumference of the cam disk 2 depends of course on the construction of the motor M. If e.g. B. a crank drive 10 is provided with six star-shaped cylinders, the selected ratio, for example from 1: 4 on a quadrant of the cam plate in a uniform angular arrangement, each with 15 ° intermediate angle, to arrange the six plungers.
  • additional tappets 4 with their pistons 5 and cylinders 6 can be arranged on the cam disk exactly opposite the first ones. Their position is indicated on the left in FIG. 1 with dashed lines. The opposite cylinders then always work together on a transmission line 7. A connecting line leads from the opposite cylinder to the relevant transmission line. Such a connecting line is indicated by dashed lines and designated 20.
  • crank drive 10 can be used in the driven motor M, the slave, whether with cylinders 8 arranged in a cross or star shape, all of which act on a single crank with their pistons 9, or the cylinders can also be in Be arranged in a row and work on a corresponding crankshaft.
  • the motor M can be combined in a compact manner with a toothed drive, or the multiple crank drive can be replaced by a prismatic body 29 which moves on an eccentric track and which is acted upon by the pistons via hydrostatically supported plungers.
  • a prismatic body 29 which moves on an eccentric track and which is acted upon by the pistons via hydrostatically supported plungers.
  • Such a motor is shown schematically in FIG. 7.
  • hydrostatic forces are advantageously transferred support elements, pressure shoes 31, used between the piston and eccentric prism 29, which conduct the pressure fluid from the cylinder volume via throttle channels 30 into the pressure pockets of the tappets in a manner known per se.
  • At least 3 hydrostatic pockets are required for all-round alignment of the pressure shoe, but in practice four are preferred, and here too there is the possibility of feeding in the pressure fluid required by the hydrostatic elements by means of the feed device. At the same time, a low fluid flow or Replacement achieved, which prevents excessive heating of the fluid due to constant, albeit small, friction losses.
  • Such a cylinder-piston engine has cylinders 8 arranged in a star shape, the pistons of which act as a tappet on a prismatic body 29 moving on an eccentric track in a non-positive and positive manner.
  • the eccentric movement of the prismatic body 29 is transferred to a pinion to be absorbed by a transmission gear.
  • At least two gear wheels 27 meshing with the pinion move the prismatic body 29 rotating on the eccentrics 28 along an eccentric path.
  • the forces and movements are transmitted from the transmission lines 7 via the pistons of the motor to the prismatic surfaces 32 of the prismatic body 29 via the pressure shoes 31, which are fed hydrostatically through the throttle channels 30.
  • the transmission capacity of the described motor is determined by the ratio between the gears 27 and given the pinion 26.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Glass Compositions (AREA)
  • Lubricants (AREA)
  • Transplanting Machines (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Abstract

The apparatus has at least one cam plate driven by a drive shaft in a piston pump or hydraulic pressure generator. The cam plate has a cam track or surface with at least two substantially sinusoidal protrusions and recesses or depressions on its circumference or perimeter. The rotation of this cam plate drives a crankshaft of a hydraulic piston and cylinder drive unit or motor by means of at least one plunger or cam follower or tappet and a piston through at least one transmission pipeline or conduit filled with a hydraulic medium. This transmission pipeline is attached without valves to the cylinder of the piston and is connected by means of an also valveless cylinder with a piston of the hydraulic piston and cylinder drive unit or motor. The cam track or surface is so structured that during uniform rotation of the cam plate of the piston pump or hydraulic pressure generator and the crankshaft of the hydraulic piston and cylinder drive unit or motor, the volume of that part of the system filled with the hydraulic medium, i.e. the total volume including the pump piston displacement, cylinder dead space and the volume of the transmission pipeline or conduit, plus the volume of the motor piston displacement, remains constant over time.

Description

Die Erfindung betrifft eine Vorrichtung zum hydraulischen Übertragen von mechanischer Leistung und zur gleichzeitigen Übersetzung der Drehzahl.The invention relates to a device for the hydraulic transmission of mechanical power and for the simultaneous translation of the speed.

Es geht beispielsweise darum, eine Leistungsübertragung eines vergleichsweise langsam laufenden Antriebs auf einen vergleichsweise rasch laufenden Leistungsaufnehmer zu ermöglichen, wobei der Antrieb und der Leistungsaufnehmer örtlich so weit voneinander entfernt sein können, dass ein Riemenantrieb oder ein Getriebe von üblicher Bauart nicht anwendbar ist.For example, it is a matter of enabling power to be transmitted from a comparatively slow-running drive to a comparatively fast-running power pickup, the drive and the power pickup being able to be so far apart from one another that a belt drive or a gearbox of a conventional type cannot be used.

Ein typisches Beispiel einer solchen Übertragung ist es, die Leistung einer Niederdruck-Wasserturbine, die möglichst tief einzubauen ist, auf einen Generator zu übertragen, der vorzugsweise auf Maschinenbodenhöhe aufgebaut ist. Bedingt durch das kleine Gefälle müssen die Turbinen langsam drehen, wobei die typische Drehzahl im Bereich von 100 U/min. liegt. Der Generator hingegen sollte möglichst rasch laufen, z. B. zwischen 1000-1500 U/min., denn damit ergeben sich günstigere Bauarten als bei langsam laufenden vierpoligen Generatoren.A typical example of such a transmission is to transfer the power of a low-pressure water turbine, which is to be installed as deep as possible, to a generator, which is preferably built up at machine floor level. Due to the small gradient, the turbines have to rotate slowly, with the typical speed in the range of 100 rpm. lies. The generator, however, should run as quickly as possible, e.g. B. between 1000-1500 U / min., Because this results in cheaper designs than slow-running four-pole generators.

Ein Übersetzungsverhältnis von 1:10 oder 1:15 wäre hier also erwünscht. Selbst wenn es anordnungsmässig möglich wäre, würde ein so grosses Übersetzungsverhältnis bei einem Getriebe oder Riemenantrieb Schwierigkeiten bereiten, insbesondere wegen der Kleinheit des Zahnritzels resp. des kleinen Riemen-Pulleys.A gear ratio of 1:10 or 1:15 would be desirable here. Even if it were possible according to the arrangement, such a large transmission ratio would cause difficulties in a gearbox or belt drive, in particular because of the small size of the pinion, respectively. of the small belt pulley.

Das oben Erwähnte zeigt den Bedarf einer stark ins Schnelle übersetzenden Leistungsübertragungsvorrichtung einer anderen Bauweise.The above shows the need for a high speed power transmission device of another construction.

Für Leistungsübertragungen allerArten sind die hydraulischen Gleichstrom-Übertragungen mit Ölpumpe, Druckübertragungsleitung, Ölmotor, Rückfluss-Leitung, ergänzt durch ein Hilfssystem, das für Einspeisung, Kühlung und Filterung sorgt, bekannt.The hydraulic direct current transmissions with oil pump, pressure transmission line, oil motor, return line, supplemented by an auxiliary system, which provides for feeding, cooling and filtering, are known for power transmissions of all kinds.

Aus der US-A-2 597 050 ist eine hydraulische Wechselstrom-Übertragung bekannt, in der ein System mit jeweils nebeneinander angeordneten Ölpumpen, Druckübertragungsleitungen, Ölmotoren und einem Ausgleichsbehälter gezeigt ist, welches von an einer Welle nebeneinander angeordneten Nocken angetrieben ist, jedoch keine Möglichkeit einer Drehzahlübersetzung erkennen lässt.From US-A-2 597 050 a hydraulic alternating current transmission is known, in which a system with oil pumps, pressure transmission lines, oil motors and an expansion tank arranged side by side is shown, which is driven by cams arranged side by side on a shaft, but not possible reveals a speed ratio.

Für hohe Leistungen, hier wird z. B. an den Megawatt-Bereich gedacht, müssen allgemein ziemlich hohe Drücke verarbeitet werden. Daraus ergibt sich das dem Fachmann bekannte Problem erheblichen Lärms von Pumpe und Motor und ebenso das Problem des Übertragungswirkungsgrades, der wohl bestenfalls in den Bereich bis 80% zu liegen kommt, nicht aber in den Bereich von 90% und mehr, wie es bei einem Getriebe-oder Riemenantrieb erreichbar wäre.For high performance, here z. B. thought of the megawatt range, generally quite high pressures must be processed. This results in the problem of considerable noise from the pump and motor, which is known to the person skilled in the art, and likewise the problem of the transmission efficiency, which is probably at best in the range up to 80%, but not in the range of 90% and more, as is the case with a transmission -or belt drive would be reachable.

Die Aufgabe der Erfindung ist es, hier Abhilfe zu schaffen.The object of the invention is to remedy this.

Erfindungsgemäss wird diese Aufgabe an der Vorrichtung der eingangs beschriebenen Art dadurch erfüllt, dass zur n-fachen Übersetzung eine mittels einer Antriebswelle angetriebene Nockenscheibe einer Zylinderkolbenpumpe mit einer Nockenbahn mit n im wesentlichen sinusförmige Erhebungen und Einsenkungen am Umfang aufweisenden Sinuskurven über eine im Bereich einer Sinuskurve angeordnete Anzahl Stössel und Kolben und eine gleiche Anzahl von jeweils am Zylinder des Kolbens ventil los angesetzten, mit Hydraulikmedium gefüllten Übertragungsleitungen über eine gleiche Anzahl von ebenfalls ventillos angesetzten Zylindern mit Kolben eines Zylinderkolbenmotors einen Antrieb antreibt, wobei die Nokkenbahn so ausgelegt ist, dass bei gleichmässiger Drehung der Nockenscheibe der Pumpe und der Welle des Motors das Volumen des mit Hydraulikmedium gefüllten Systems, d. h. PumpenzylinderHubraum, Übertragungsleitung und Motorzylinder-Hubraum immer konstant bleiben, wozu ein Raum wählbaren Druckes vorgesehen ist, der über Drosseleinheiten mit allen Übertragungsleitungen verbunden ist.According to the invention, this object is achieved on the device of the type described in the introduction in that, for the n-fold translation, a cam disk of a cylinder piston pump driven by a drive shaft with a cam track with n essentially sinusoidal elevations and depressions on the circumference has a sine curve arranged in the area of a sine curve Number of plungers and pistons and an equal number of transmission lines, each with a hydraulic cylinder filled with hydraulic medium, attached to the cylinder of the piston via a same number of cylinders with pistons of a cylinder-piston engine, which are also attached without a valve, a drive, the cam track being designed so that the rotation is even the cam disk of the pump and the shaft of the motor the volume of the system filled with hydraulic medium, d. H. Pump cylinder displacement, transmission line and engine cylinder displacement always remain constant, for which purpose a space of selectable pressure is provided, which is connected to all transmission lines via throttle units.

Im weiteren wird der Erfindungsgegenstand anhand von Zeichnungen näher beschrieben und erklärt. Auf den Zeichnungsblättern zeigen in schematischer Weise:

  • Figur 1 ein erstes Ausführungsbeispiel der erfindungsgemässen Vorrichtung,
  • Figur 2 eine Drosseleinheit,
  • Figur 3 bis Figur 6 vier verschiedene Ausführungsformen des Zylinders mit Kolben und Stössel, und
The subject of the invention is described and explained in more detail below with the aid of drawings. The drawing sheets show in a schematic way:
  • FIG. 1 shows a first exemplary embodiment of the device according to the invention,
  • FIG. 2 shows a throttle unit,
  • Figure 3 to Figure 6 four different embodiments of the cylinder with piston and tappet, and

Figur 7 ein anderes Ausführungsbeispiel eines anwendbaren Motors.Figure 7 shows another embodiment of an applicable motor.

Die Leistungsübertragung mit Drehzahlübersetzung wird mittels einer Vorrichtung gewährleistet, die nach dem Prinzip der hydraulischen Wechselstrom-Leistungsübertragung arbeitet. Dazu wird die Leistung von einer Pumpe P als Antrieb auf einen Motor M übertragen. Auf einer Antriebswelle 1 einer Pumpe P ist eine Nockenscheibe 2 mit im allgemeinen n, im wesentlichen sinusförmigen Erhebungen und Einsenkungen am Umfang einer Nockenbahn 3 vorgesehen. In Figur 1 ist n = 4 dargestellt. Die Nockenbahn betätigt über Rollen 17 bzw. Stössel 4, Kolben 5 in Zylindern 6 in ebenfalls im wesentlichen sinusförmigem Takt. Von den Zylindern 6 führen die mit einem Hydraulikfluid gefüllten Übertragungsleitungen 7, in Fig. 1 sind sechs Stück gezeichnet, zum Hydromotor M. Jede der Übertragungsleitungen istventillos mit einem Zylinder 8 verbunden, und die Zylinder sind vorzugsweise sternförmig um einen Kurbelantrieb 10 angeordnet. Auf diesen Kurbelantrieb 10 wirken alle Kolben 9 des Hydromotors ein. Dieser Kurbelantrieb 10 ist es auch, der mit seinem Kurbel-Pleuel-Verhältnis sowie dem Rollen-Durchmesserverhältnis auf der Antriebswelle 1 die genaue Kontur der Nockenbahn 3 bestimmt. Die Kontur wird so bestimmt, dass bei gleichmässiger Drehung der Pumpe und des Motors in allen mit dem Hydraulikfluid gefüllten Zylinder-Übertragungsleitungssystemen 6,7,8, d. h. in dem Pumpenzylinderhubraum plus dem Übertragungsleitungsraum plus dem Motorzylinderhubraum, die eingeschlossenen Fluidvolumina zeitlich konstant sind.The power transmission with speed transmission is ensured by means of a device which works on the principle of hydraulic AC power transmission. For this purpose, the power is transferred from a pump P as a drive to a motor M. On a drive shaft 1 of a pump P, a cam disk 2 with generally n, essentially sinusoidal elevations and depressions is provided on the circumference of a cam track 3. In Figure 1, n = 4 is shown. The cam track is actuated by rollers 17 or tappets 4, pistons 5 in cylinders 6 in a likewise essentially sinusoidal cycle. From the cylinders 6, the transmission lines 7 filled with hydraulic fluid, six of which are shown in FIG. 1, lead to the hydraulic motor M. Each of the transmission lines is connected to a cylinder 8 without a valve, and the cylinders are preferably arranged in a star shape around a crank drive 10. All pistons 9 of the hydraulic motor act on this crank drive 10. It is this crank drive 10 which, with its crank-connecting rod ratio and the roller-diameter ratio on the drive shaft 1, determines the exact contour of the cam track 3. The contour is determined in such a way that with uniform rotation of the pump and the motor in all cylinder transmission line systems 6, 7, 8 filled with the hydraulic fluid, ie in the pump cylinder displacement plus the transmission line space plus the engine cylinder the displacement, the enclosed fluid volumes are constant over time.

Beim Übertragen von grossen Leistungen ist es offensichtlich, dass recht hohe Drücke in den mit Hydraulikmedium gefüllten Leitungen vorkommen. Dies führt infolge der, wohl geringen, Kompressibilität zu Effekten zeitlich leicht veränderter Volumina: Die Volumina nehmen zu bzw. ab im umgekehrten Takt des Druckes.When transferring high power, it is obvious that there are quite high pressures in the lines filled with hydraulic medium. As a result of the, probably low, compressibility, this leads to the effects of slightly changed volumes: the volumes increase or decrease in the reverse rhythm of the pressure.

Auch eventuelle Hydraulikmedium-Leckagen zwischen Kolben und Zylindern führen langsam zu einem Fluidfüllungs-Manko. Damit besteht auch die Gefahr, dass z. B. die Rollen 17 von der Nokkenbahn 3 abheben, womit die Anlage dann sehr rauh läuft oder überhaupt aus dem Tritt fällt.Any leaks of hydraulic medium between the pistons and cylinders also slowly lead to a fluid filling shortcoming. There is also a risk that z. B. lift the rollers 17 from the cam track 3, so that the system then runs very rough or even falls out of step.

Um das zu verhindern, ist eine Einspeisevorrichtung vorgesehen, die aus einem Raum 11 wählbaren Druckes, über je eine Drosseleinheit 12 mit einer Stelle einer Übertragungsleitung 7 verbunden, geringe Mengen von Hydraulikfluid einspeisen oder entnehmen kann.In order to prevent this, a feed device is provided which can feed in or take out small amounts of hydraulic fluid from a room 11 of selectable pressure, each connected via a throttle unit 12 to a point of a transmission line 7.

Dank dieser Einspeisevorrichtung gelingt es, einen ruhigen Lauf hinzubringen, zu verhindern, dass die Stössel 4 von der Nockenscheibe 2 bzw. der Nockenbahn 3 abheben, und zu gewährleisten, dass die Übertragung beim Anfahren von selbst synchronisiert. Gleichzeitig werden auch an die Herstellungsgenauigkeit der Nockenform bzw. der Nockenbahn 3 bedeutend geringere Anforderungen gestellt.Thanks to this feed device, it is possible to achieve a smooth run, to prevent the tappets 4 from lifting off the cam disk 2 or the cam track 3, and to ensure that the transmission synchronizes itself when the vehicle starts off. At the same time, the manufacturing accuracy of the cam shape or cam track 3 is subject to significantly lower requirements.

Der Druck, den man in diesem Raum 11 wählt, hängt von der übertragenen Leistung und eventuell auch von der Drehzahl ab. Er wird zweckmässigerweise so eingestellt, dass er im Bereich von 70-130% des zeitlichen Druckmittelwertes in einer Übertragungsleitung liegt. Dieser Druck wird bereitgestellt mit einer kleinen Hilfspumpe und einem einstellbaren Druckbegrenzer, beide nicht gezeichnet, über eine Speiseleitung 33, die in den Raum 11 führt.The pressure that one chooses in this space 11 depends on the transmitted power and possibly also on the speed. It is expediently set so that it is in the range of 70-130% of the time pressure average in a transmission line. This pressure is provided with a small auxiliary pump and an adjustable pressure limiter, both not shown, via a feed line 33 which leads into the room 11.

Die Drosseleinheiten 12, die zwischen den Raum 11 und die Übertragungsleitungen 7 geschaltet sind, können, wie es im einzelnen in der Figur 2 gezeigt ist, als parallel geschaltete Mehrfachdrosseln, beispielsweise mit zwei parallel geschalteten Drosselstellen 14 und 13 mit gleich grosser oder verschieden grosser Durchströmfläche ausgebildet werden, wobei wahlweise die Durchströmwege mit Ventilen 15, 16 freigegeben oder gesperrt werden können.The throttle units 12, which are connected between the space 11 and the transmission lines 7, can, as shown in detail in FIG. 2, as parallel multiple throttles, for example with two throttle points 14 and 13 connected in parallel with a flow area of the same size or different size are formed, wherein the flow paths can optionally be released or blocked with valves 15, 16.

Wie es in Figur 3 gut zu sehen ist, werden die Stössel 4, die die um die Nockenscheibe 2 angeordneten Kolben 5 bewegen, vorteilhafterweise, um gleitenden Verschleiss zu vermeiden, als Rollenstössel mit Rollen 17 ausgebildet. Wenn noch grössere Kräfte zu bewältigen sind, so kommen auch mehrere Rollen 17 zur Betätigung eines Stössels 19 zur Anwendung, die dann zu einem Drehgestell-ähnlichen Gebilde 18 zusammengefasst werden und in dieser Weise auf den Kolben 5 einwirken, wie es im Detail in Figur 4 gezeigt ist.As can be clearly seen in FIG. 3, the tappets 4, which move the pistons 5 arranged around the cam disk 2, are advantageously designed as roller tappets with rollers 17 in order to avoid sliding wear. If still greater forces have to be mastered, then several rollers 17 are used to actuate a plunger 19, which are then combined to form a bogie-like structure 18 and act in this way on the piston 5, as is shown in detail in FIG. 4 is shown.

Alternativ zu den mit Rollen 17 versehenen Stösseln 4 können auch Gleitschuh-Stössel hydrodynamischer Arbeitsweise verwendet werden, oder vorzugsweise auch Druckschuh-Stössel mit an sich bekannter hydrostatischer Schmierung. Wie es der Figur 5 entnehmbar ist, wird das Druck-Schmierfluid für diese hydrostatischen Stössei 21, mit Vorteil von dem Zylinderraum des Zylinders 6 bzw. der Übertragungsleitung 7 über Drosselbohrungen 23 und 22 entnommen. Entsprechend diesem Fluidverbrauch muss dann die Einspeisevorrichtung dimensioniert werden. Selbstverständlich ist bei der Bemessung solcher hydrostatisch abgestützten Stössel der Krümmungsradius-Verschiedenheit der Nockenoberfläche 3 Rechnung zu tragen. Gegebenenfalls ist die mit der Nockenscheibenfläche 3 in hydrostatisch abgestütztem Kontakt stehende Stösseloberfläche zu unterteilen in gegeneinander bewegliche, schmale, quergestellte Einzeloberflächen 24, 25, wie es im Detail in Figur 6 gezeigt ist.As an alternative to the tappets 4 provided with rollers 17, sliding shoe tappets of hydrodynamic operation can also be used, or preferably also pressure shoe tappets with hydrostatic lubrication known per se. As can be seen from FIG. 5, the pressure lubricating fluid for these hydrostatic impacts 21 is advantageously taken from the cylinder space of the cylinder 6 or the transmission line 7 via throttle bores 23 and 22. The feed device must then be dimensioned in accordance with this fluid consumption. Of course, the dimensioning of such hydrostatically supported plungers must take into account the difference in the radius of curvature of the cam surface 3. If necessary, the tappet surface which is in hydrostatically supported contact with the cam disk surface 3 can be subdivided into narrow, transversely positioned individual surfaces 24, 25 which are movable relative to one another, as is shown in detail in FIG.

Die Anordnung der Stössel 4 am Umfang der Nockenscheibe 2 hängt selbstverständlich von der Konstruktion des Motors M ab. Wenn z. B. ein Kurbelantrieb 10 mit sechs sternförmig angeordneten Zylindern vorgesehen ist, sind beim gewählten Übersetzungsverhältnis beispielsweise von 1:4 auf einem Quadranten der Nockenscheibe in gleichmässiger Winkelanordnung, mit je 15° Zwischenwinkel, die sechs Stössel anzuordnen.The arrangement of the tappets 4 on the circumference of the cam disk 2 depends of course on the construction of the motor M. If e.g. B. a crank drive 10 is provided with six star-shaped cylinders, the selected ratio, for example from 1: 4 on a quadrant of the cam plate in a uniform angular arrangement, each with 15 ° intermediate angle, to arrange the six plungers.

Um die Nockenscheibe vor einseitig wirkenden Kräften der Stössel zu bewahren, können weitere Stössel 4 mit ihren Kolben 5 und Zylindern 6 den ersten genau gegenüberliegend an der Nockenscheibe angeordnet werden. Ihre Position ist in Figur 1 links mit gestrichelten Linien angedeutet. Immer die gegenüberliegenden Zylinder arbeiten dann gemeinsam auf eine Übertragungsleitung 7. Von dem gegenüberliegenden Zylinder führt jeweils eine Verbindungsleitung zur betreffenden Übertragungsleitung. EinesolcheVerbindungsleitung ist gestrichelt angedeutet und mit 20 bezeichnet.In order to protect the cam disk from unilaterally acting forces of the tappet, additional tappets 4 with their pistons 5 and cylinders 6 can be arranged on the cam disk exactly opposite the first ones. Their position is indicated on the left in FIG. 1 with dashed lines. The opposite cylinders then always work together on a transmission line 7. A connecting line leads from the opposite cylinder to the relevant transmission line. Such a connecting line is indicated by dashed lines and designated 20.

Allgemein können noch mehr Zylinder am Umfang angeordnet werden, wobei alle in gleicher Phase arbeitenden Zylinder am Umfang parallel geschaltet werden. Damit sind wohl mehr Zylinder nötig, aber die Stössel werden kleineren Kräften ausgesetzt und können daher gegebenenfalls einfacher aufgebaut sein.In general, even more cylinders can be arranged on the circumference, with all cylinders working in the same phase being connected in parallel on the circumference. This means that more cylinders are required, but the tappets are exposed to smaller forces and can therefore be of simpler construction if necessary.

Bei dem angetriebenen Motor M, dem Nehmer, kann, wie schon erwähnt, ein Kurbelantrieb 10 verwendet werden, sei es mit kreuz- oder sternförmig angeordneten Zylindern 8, die alle mit ihren Kolben 9 auf eine einzige Kurbel einwirken, oder die Zylinder können auch in Reihe angeordnet sein und an einer entsprechenden Kurbelwelle arbeiten.As already mentioned, a crank drive 10 can be used in the driven motor M, the slave, whether with cylinders 8 arranged in a cross or star shape, all of which act on a single crank with their pistons 9, or the cylinders can also be in Be arranged in a row and work on a corresponding crankshaft.

Wenn höhere Übersetzungsverhältnisse gefordert werden, kann der Motor M in kompakter Weise mit einem Zahnantrieb kombiniert werden, oder der Mehrfachkurbelantrieb kann ersetzt werden durch einen auf einer Exzenterbahn sich bewegenden prismatischen Körper 29, der via hydrostatisch abgestützte Stössel mit Kräften von den Kolben beaufschlagt wird. Ein solcher Motor ist in Figur 7 schematisch gezeigt. Um die Kompaktheit des ganzen Motorblocks noch weiter zu steigern, werden vorteilhafterweise hydrostatische Kraftübertragungselemente, Druckschuhe 31, zwischen Kolben und Exzenterprisma 29 verwendet, die in an sich bekannter Weise das Druckfluid aus dem Zylindervolumen über Drosselkanäle 30 in die Drucktaschen der Stössel leiten. Zur allseitigen Ausrichtung des Druckschuhes sind mindestens 3 hydrostatische Taschen nötig, in der Praxis werden jedoch vier bevorzugt, auch hier bietet sich die Möglichkeit an, mittels der Einspeisevorrichtung das von den hydrostatischen Elementen benötigte Druckfluid einzuspeisen. Gleichzeitig wird damit ein geringer Fluid-Durchfluss resp. Ersatz erreicht, womit ein übermässiges Erwärmen des Fluids infolge stetiger, wenn auch kleiner, Reibungsverluste vermieden wird.If higher gear ratios are required, the motor M can be combined in a compact manner with a toothed drive, or the multiple crank drive can be replaced by a prismatic body 29 which moves on an eccentric track and which is acted upon by the pistons via hydrostatically supported plungers. Such a motor is shown schematically in FIG. 7. In order to further increase the compactness of the entire engine block, hydrostatic forces are advantageously transferred support elements, pressure shoes 31, used between the piston and eccentric prism 29, which conduct the pressure fluid from the cylinder volume via throttle channels 30 into the pressure pockets of the tappets in a manner known per se. At least 3 hydrostatic pockets are required for all-round alignment of the pressure shoe, but in practice four are preferred, and here too there is the possibility of feeding in the pressure fluid required by the hydrostatic elements by means of the feed device. At the same time, a low fluid flow or Replacement achieved, which prevents excessive heating of the fluid due to constant, albeit small, friction losses.

Ein solcher Zylinderkolbenmotor weist sternförmig angeordnete Zylinder 8 auf, deren Kolben als Stössel auf einen auf einer Exzenterbahn sich bewegenden prismatischen Körper 29 kraft- und formschlüssig wirken. Die exzentische Bewegung des prismatischen Körpers 29 wird über ein übersetzendes Getriebe auf ein die übertragene Leistung aufzunehmendes Ritzel überführt. Mindestens zwei mit dem Ritzel kämmende Zahnräder 27 bewegen den auf den Exzentern 28 umlaufenden prismatischen Körper 29 entlang einer exzentrischen Bahn. Über die hydrostatisch durch die Drosselkanäle 30 angespeisten Druckschuhe 31 übertragen sich die Kräfte und die Bewegungen aus den Übertragungsleitungen 7 über die Kolben des Motors auf die prismatischen Flächen 32 des prismatischen Körpers 29. Das Übersetzungsvermögen des beschriebenen Motors ist durch das Verhältnis zwischen den Zahnrädern 27 und dem Ritzel 26 gegeben.Such a cylinder-piston engine has cylinders 8 arranged in a star shape, the pistons of which act as a tappet on a prismatic body 29 moving on an eccentric track in a non-positive and positive manner. The eccentric movement of the prismatic body 29 is transferred to a pinion to be absorbed by a transmission gear. At least two gear wheels 27 meshing with the pinion move the prismatic body 29 rotating on the eccentrics 28 along an eccentric path. The forces and movements are transmitted from the transmission lines 7 via the pistons of the motor to the prismatic surfaces 32 of the prismatic body 29 via the pressure shoes 31, which are fed hydrostatically through the throttle channels 30. The transmission capacity of the described motor is determined by the ratio between the gears 27 and given the pinion 26.

Claims (11)

1. Device for the hydraulic transmission of mechanical power and the simultaneous conversion of the speed of rotation, characterized in that, for a conversion factor of n, a cam disc (2) coupled to the drive shaft (1 ) of a cylinder piston pump has a cam surface (3) with n sine waves consisting of substantially sinusoidal projections and depressions, and drives a number of tappets (4) connected to pistons (5) in cylinders (6), without valves coupled to the same number of transmission lines (7) and filled with hydraulic medium, the transmission lines (7) each communicating with respective cylinders (8) with pistons (9), also without valves, of a cylinder piston motor, the cam (3) being that with even rotation of the cam disc (2) of the pump and the shaft of the motor (10), the volume of the system fillet with hydraulic medium; i.e. pump cylinder swept volume (16), transmission line (7) and motor cylinder swept volume, always remains constant, a pressure chamber (11), with a pressure which can be selected, being provided which chamber is connected via choke units (12) to all the transmission lines (7).
2. Device according to Claim 1, characterized in that each choke unit (12) consists of at least two chokes (13, 14) connected in parallel with equal or different flow cross-sections, whose flow paths can be opened or closed optionally, by means of valves (15, 16).
3. Device according to Claim 1, characterized in that the pressure in space (11) is selected according to the speed and the transmitted power.
4. Device according to Claim 1, characterized in that the pressure in space (11) is selected in the range of 70-130% of the average value of the pressure in the transmission lines (7).
5. Device according to Claim 1, characterized in that tappets (4) actuated by the cam surface of cam (3) are provided with rollers (17), which roll on the cam (3).
6. Device according to Claim 5, characterized in that several rollers (17) are combined in groups (18) similar to bogies which act on the tappet push rod (19) and the piston (5).
7. Device according to Claim 1, characterized in that tappets (4) are fitted at various places on the periphery of the cam disc (3) and the cylinders (8) of all these tappets (4) which move in the same phase are connected in parallel via connecting lines (20).
8. Device according to Claim 1, characterized in that the tappets (4) are provided with hydrostatic sliding pressure shoes (21), the requisite pressure liquid being extracted via choke bores (22 or 23) from the cylinder transmission line system (6, 7 in fig. 5, 6).
9. Device according to Claims 1 and 8, characterized in that the hydrostatic sliding pressure shoes are divided into at least two individual pressure shoes (24 and 25) moving relative to one another, so that by the division the dimension of each pressure shoe in the circumferential direction of the cam is reduced.
10. Device according to Claim 1, characterized in that the cylinder piston motor has cylinders arranged in a star shape and that the connecting rods of the pistons are connected to a common crank drive (10).
11. Device according to Claim 1, characterized in that for further altering the conversion factor the cylinder piston motor has cylinders arranged in a star shape, the pistons of which act as tappets on a prismatic body (29) moving on an eccentric track in a force locking and form locking way, where the eccentric movement of the prismatic body (29) is transmitted via a gearbox (27, 26) to the pinion taking up the transmitted power, where at least two gearwheels (27) meshing with the pinion (26) move the prismatic body (29) running on the eccentrics (28) and where the forces and movements from the transmission lines (7) are transmitted via pressure shoes (31 ) fed hydrostatically by means of choke channels (30), via the pistons of the motor to the prismatic surfaces (32) of the body (29).
EP86107003A 1985-05-29 1986-05-23 Hydraulic transmission Expired EP0205942B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86107003T ATE35722T1 (en) 1985-05-29 1986-05-23 HYDRAULIC TRANSMISSION DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2260/85 1985-05-29
CH2260/85A CH668302A5 (en) 1985-05-29 1985-05-29 HYDRAULIC POWER TRANSMISSION WITH SPEED TRANSLATION.

Publications (2)

Publication Number Publication Date
EP0205942A1 EP0205942A1 (en) 1986-12-30
EP0205942B1 true EP0205942B1 (en) 1988-07-13

Family

ID=4229616

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EP86107003A Expired EP0205942B1 (en) 1985-05-29 1986-05-23 Hydraulic transmission

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US (1) US4781025A (en)
EP (1) EP0205942B1 (en)
JP (1) JPS61278657A (en)
AT (1) ATE35722T1 (en)
CH (1) CH668302A5 (en)
DE (1) DE3660390D1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4936096A (en) * 1986-12-08 1990-06-26 Vanderjagt John A Drive mechanism
US5743090A (en) * 1995-09-29 1998-04-28 Barrowman; Andrew W. Hydraulic torque transmitter and synchronizer
DE69810516T2 (en) 1998-04-27 2003-09-25 Andrew W Barrowman HYDRAULIC TORQUE TRANSMISSION DEVICE
AUPQ553900A0 (en) * 2000-02-10 2000-03-02 Bresland, Claude Neil Torque conversion system
US20090249781A1 (en) * 2008-04-02 2009-10-08 Gilbert Jr Ed System and method of increasing the output energy of a motor by transferring the output energy through a plurality of hydraulic networks
US20110138803A1 (en) * 2008-04-02 2011-06-16 Gilbert Jr Ed System of Transferring and Storing Energy and Method of Use Thereof
GB2484890A (en) 2010-08-17 2012-05-02 Artemis Intelligent Power Ltd Ring cam ensuring smooth follower handover between segments
KR101355267B1 (en) 2010-08-17 2014-01-27 아르테미스 인텔리전트 파워 리미티드 Fluid-working machine with multi-lobe ring cam

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Publication number Priority date Publication date Assignee Title
US386116A (en) * 1888-07-17 du bois
US862867A (en) * 1906-03-28 1907-08-06 Lewis Watson Eggleston Pneumatic pumping apparatus.
US1547409A (en) * 1922-12-02 1925-07-28 Forges Chantiers Mediterranee Hydraulic transmission
US1931952A (en) * 1928-02-02 1933-10-24 Charles Maurice Hydraulic power-transmitting system
US2198965A (en) * 1938-06-18 1940-04-30 L A B Corp Hydraulic torque transmission system
US2297610A (en) * 1939-10-17 1942-09-29 Liquidometer Corp Apparatus for transmitting rotary motion
US2597050A (en) * 1942-06-25 1952-05-20 Olaer Marine Hydraulic transmission for reproducing mechanical motions at remote points
US3816029A (en) * 1972-10-03 1974-06-11 Duriron Co Pumping unit for constant pulseless flow
US3959703A (en) * 1974-12-24 1976-05-25 Sidney Rosen Speed control for pump of filling machines
PH10374A (en) * 1975-09-05 1977-02-16 Roces M Improvement of hydraulic coupling and speed multiplying mechanism

Also Published As

Publication number Publication date
ATE35722T1 (en) 1988-07-15
EP0205942A1 (en) 1986-12-30
JPS61278657A (en) 1986-12-09
DE3660390D1 (en) 1988-08-18
CH668302A5 (en) 1988-12-15
US4781025A (en) 1988-11-01

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