EP0766788A1 - Adjustable hydrostatic radial-piston motor - Google Patents

Adjustable hydrostatic radial-piston motor

Info

Publication number
EP0766788A1
EP0766788A1 EP96902897A EP96902897A EP0766788A1 EP 0766788 A1 EP0766788 A1 EP 0766788A1 EP 96902897 A EP96902897 A EP 96902897A EP 96902897 A EP96902897 A EP 96902897A EP 0766788 A1 EP0766788 A1 EP 0766788A1
Authority
EP
European Patent Office
Prior art keywords
cam ring
eccentricity
radial piston
measuring device
piston machine
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.)
Granted
Application number
EP96902897A
Other languages
German (de)
French (fr)
Other versions
EP0766788B1 (en
Inventor
Volkmar Leutner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0766788A1 publication Critical patent/EP0766788A1/en
Application granted granted Critical
Publication of EP0766788B1 publication Critical patent/EP0766788B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/128—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the cylinders, e.g. by moving a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1213—Eccentricity of an outer annular cam

Definitions

  • the invention is based on a hydrostatic radial piston machine with an adjustable cam ring according to the preamble of claim 1.
  • Such a machine is generally known. It is used in a large number of hydraulic fields of application, since its use makes it possible to reduce the effort required for control and / or regulating valves. Main advantages in drives with such
  • radial piston machines are their low loss, as well as the quick and precise electrical controllability of the machine.
  • integrated, pressurized adjusting pistons are used in the machine housing, which act on the outer circumference of the cam ring along its direction of adjustment.
  • the eccentricity of the cam ring which is proportional to the delivery rate of the machine, can be used as a controlled variable and is detected by an inductive displacement sensor. This actual value is compared with a command value by an electronic control amplifier and is used to control the position of the cam ring.
  • this inductive displacement sensor cannot be arranged in any other way than in the extension of the adjusting pistons, as a result of which the machine, in its largest dimension, is further enlarged. Since the displacement sensor is an additional attachment, the construction effort of the machine also increases.
  • a hydrostatic radial piston pump with a measuring device for detecting the eccentricity of a rotatably mounted eccentric ring is known from DE 35 13 736 AI.
  • a hydraulic linkage transmits the deflection, dependent on the eccentricity of the eccentric ring, of a master tappet, which is supported on the inside of the eccentric ring, to a slave tappet.
  • This measuring device has a large number of mechanical components and requires a high outlay for the hydraulic coupling; the signal must be picked up in a rotating machine shaft.
  • the inventive, electro-hydraulically adjustable machine with the characterizing features of the main claim has the advantage that the means used consist of inexpensive measuring devices that are integrated into existing machine components or that existing machine components are used as sensors. As a result, neither the construction volume nor the construction effort of the machine increases.
  • a digital measurement signal is present, which is provided by an electronic circuit both for determining the eccentricity of the cam ring and for determining the speed of the rotor and possibly for others
  • the scanning time is flexible within certain limits, depending on the requirements of the application, in that the number of sliding shoes used as a measuring sensor can be varied. The smallest Sampling times can therefore be achieved if all sliding blocks are used as sensors. It is also advantageous that the measuring device works without contact and is therefore not subject to friction or wear, which is evident in a long service life with little maintenance.
  • FIG. 1 shows a radial piston machine in cross section, in a simplified representation
  • FIG. 2 shows a diagram with the course of the signal generated in the transducer as a function of the time or the angle of rotation of the rotor.
  • Fig.l shows a radial piston machine 10 whose housing 11 is closed by a cover, not shown.
  • a control pin 13 which is mounted in a stationary manner in the housing, projects centrally.
  • a rotor 14 is rotatably mounted on this part of the control pin, in which a plurality of radially running bores 15 form cylinders in which working pistons 16 slide.
  • These working pistons 16 are connected in an articulated manner to sliding shoes 17 which protrude from the bores 15 of the rotor and which are movably tied to a cylindrical cam ring 18 by means of retaining rings (not shown).
  • the inside of the cam ring forms the running surface for these sliding shoes 17.
  • the cam ring is from two hydraulic adjusting pistons 22 and 23 arranged in the housing, which are diametrically opposed and form an adjusting device, are fixed in their position.
  • the position of the cam ring 18 is within the recess, along that specified by the adjusting pistons 22 and 23
  • Rotated in Fig.l not recognizable control slots are connected via longitudinal channels 26 and openings also mounted in the control pin 13 with radially extending in the housing, penetrating to the outside channels. These channels 26 represent suction and pressure channels and lead the hydraulic medium into the machine 10 and out again under pressure.
  • the angular position of the rotor 14 on the control pin 13 is designed such that the webs located between the control slots in the control pin 13 lie in an area in which the working pistons 16 are at their dead centers.
  • the rotor 14 is set in rotation by a coupling shaft, also not shown, by a drive shaft mounted in the cover.
  • the radial piston machine 10 has a measuring device for detecting the eccentricity 20 of the cam ring 18 serving as the adjusting member, which has a transducer 27 in the cam ring 18 and a plurality of transducers.
  • the sliding shoes 17 of the working pistons 16 serve as measuring sensors. The signal triggered by them in the measuring sensor is fed to an electronic evaluation unit 28.
  • the mode of operation of the adjustable radial piston machine 10 is explained in the following, its basic function in connection with the hydraulic adjusting device being assumed to be known per se.
  • the stroke ring 18 is maximally extended to the left via the adjusting device, which results in an eccentricity 20 between the stroke ring 18 and the rotor 14.
  • the above-mentioned attachment of the sliding shoes to the lifting ring 18, in connection with its eccentric position relative to the rotor 14, forces the working piston 16, which is articulated via the sliding shoes 17, in the rotor 14 upon its rotating movement to force a lifting movement in the radial direction.
  • this lifting movement in conjunction with the kinematic conditions in the radial piston machine 10, the distance between two successive sliding shoes changes.
  • this emits a voltage as a signal as long as a slide shoe 17 is above it.
  • the sensor 27 For example, if the front edge 17.1 of the sliding block 17 in the direction of rotation reaches the sensor 27, this leads in the signal curve 30 to a voltage rise 32 to a higher level 33, which is maintained until the rear edge 17.2 of the sliding block 17 slides past the sensor 27 in the direction of rotation is.
  • the voltage signal then returns to the original level 34, as a result of which a falling edge 35 is formed in the signal curve 30.
  • the voltage signal remains at this lower level 34, after which a voltage rise 32 takes place again, etc.
  • the time delay 36 between the rising and falling voltage edges, which follow one another in the signal curve, is a direct measure of the distance between the associated sliding shoes, which, as already mentioned, is proportional to the eccentricity of the cam ring 18.
  • the signal curve 30 or 31 is then processed further in the form of evaluation electronics 28 such that a falling edge 35 in the signal curve starts a counter with a high-frequency counting sequence. This counter is stopped by a rising edge 32, the counting frequency being tuned once so that the counting result corresponds to the present eccentricity 20.
  • the eccentricity 20 of the cam ring 18 can thus be determined continuously over the entire adjustment range of the cam ring 18.
  • the evaluation electronics 28 record the time 42 between two rising voltage edges 32, which is inversely proportional to the machine speed.
  • the volume flow of the machine can be recorded using both measured variables, speed and eccentricity.
  • the possible sampling interval between two signals depends both on the rotor speed and on the number of slide shoes 17 of the machine used as a measuring value transmitter.
  • Working pistons with sliding shoes can, for example, display a sampling interval of approx. 5.7 ms, which is sufficient for most applications.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Measurement Of Length, Angles, Or The Like Using Electric Or Magnetic Means (AREA)
  • Hydraulic Motors (AREA)

Abstract

Proposed is a hydrostatic radial-piston motor (10) with an adjustable cylinder ring (18) which has integrated means designed to determine the eccentricity (20) between the cylinder ring (18) and the rotor (14). The eccentric position of the cylinder ring (18) leads, in conjunction with the rotating rotor (14) and the restraining of the guide shoes (17) on the cylinder ring (18), to a stroke action of the piston (16) in the radial direction. This, and kinematic conditions in the motor (10), leads to a change in the distance between two consecutive guide shoes (17). This change in distance takes place in proportion to the eccentricity (20) of the cylinder ring (18) and is determined by a measuring device. This measuring device has a signal transducer (27) which generates an amplified voltage signal as the guide shoes, which act as signal generators, move over it. This signal is fed to evaluation electronics (28) where it is used to determine the eccentricity, rotor rpm and other parameters.

Description

Verstellbare, hydrostatische RadialkolbenmaschineAdjustable, hydrostatic radial piston machine
Stand der TechnikState of the art
Die Erfindung geht aus von einer hydrostatischen Radialkolbenmaschine mit verstellbarem Hubring nach dem Oberbegriff des Anspruchs 1.The invention is based on a hydrostatic radial piston machine with an adjustable cam ring according to the preamble of claim 1.
Eine derartige Maschine ist allgemein bekannt. Sie wird in einer Vielzahl von Anwendungsbereichen der Hydraulik benutzt, da es durch ihren Einsatz möglich ist, den Aufwand an Steuer- und/oder Regelventilen zu verringern. Hauptvorteile bei Antrieben mit derartigenSuch a machine is generally known. It is used in a large number of hydraulic fields of application, since its use makes it possible to reduce the effort required for control and / or regulating valves. Main advantages in drives with such
Radialkolbenmaschinen ist neben der Einfachheit der Bauweise deren Verlustarmut, sowie die schnelle und präzise elektrische Ansteuerbarkeit der Maschine. Zur Ansteuerung werden in das Maschinengehäuse integrierte, druckbeaufschlagte Verstellkolben eingesetzt, die auf den äußeren Umfang des Hubrings entlang dessen Verstellrichtung einwirken. Die Exzentrizität des Hubrings, welche proportional zur Fördermenge der Maschine ist, läßt sich als Regelgröße verwenden und wird von einem induktiven Wegaufnehmer erfaßt. Dieser Istwert wird von einem elektronischen Regelverstärker mit einem Führungswert verglichen und dient zur Lageregelung des Hubrings. In manchen Anwendungsfällen ist es nun ungünstig, daß sich dieser induktive Wegaufnehmer nicht anders als in Verlängerung der Verstellkolben anordnen läßt, wodurch sich die Maschine in ihrer bereits größten Abmessung weiter vergrößert. Da der Wegaufnehmer ein zusätzliches Anbauteil darstellt erhöht sich zudem der Bauaufwand der Maschine. Ferner ist nach DE 35 13 736 AI eine hydrostatische Radialkolbenpumpe mit einer Meßeinrichtung zur Erfassung der Exzentrizität eines drehbar gelagerten Exzenterrings bekannt. Ein hydraulisches Gestänge überträgt dabei die von der Exzentrizität des Exzenterrings abhängige Auslenkung eines Geberstδßels, welcher sich auf der Innenseite des Exzenterrings abstützt, auf einen Nehmerstδßel. Dieser ist mit einem Spulenkern versehen, welcher entsprechend der vorhandenen Exzentrizität am Exzenterring unterschiedlich tief in eine Meßspule eintaucht und dort ein Meßsignal auslöst. Diese Meßeinrichtung weist eine Vielzahl von mechanischen Bauteilen auf und erfordert einen hohen Aufwand für die hydraulische Kopplung; dabei muß die Signalabnahme in einer rotierenden Maschinenwelle erfolgen.In addition to the simplicity of the construction, radial piston machines are their low loss, as well as the quick and precise electrical controllability of the machine. For actuation, integrated, pressurized adjusting pistons are used in the machine housing, which act on the outer circumference of the cam ring along its direction of adjustment. The eccentricity of the cam ring, which is proportional to the delivery rate of the machine, can be used as a controlled variable and is detected by an inductive displacement sensor. This actual value is compared with a command value by an electronic control amplifier and is used to control the position of the cam ring. In some applications, it is now unfavorable that this inductive displacement sensor cannot be arranged in any other way than in the extension of the adjusting pistons, as a result of which the machine, in its largest dimension, is further enlarged. Since the displacement sensor is an additional attachment, the construction effort of the machine also increases. Furthermore, a hydrostatic radial piston pump with a measuring device for detecting the eccentricity of a rotatably mounted eccentric ring is known from DE 35 13 736 AI. A hydraulic linkage transmits the deflection, dependent on the eccentricity of the eccentric ring, of a master tappet, which is supported on the inside of the eccentric ring, to a slave tappet. This is provided with a coil core which, depending on the eccentricity present on the eccentric ring, dips into a measuring coil at different depths and triggers a measuring signal there. This measuring device has a large number of mechanical components and requires a high outlay for the hydraulic coupling; the signal must be picked up in a rotating machine shaft.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße, elektrohydraulisch verstellbare Maschine mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die eingesetzten Mittel aus kostengünstigen Meßeinrichtungen bestehen, die in ohnedies vorhandene Bauteile der Maschine integriert sind bzw. daß vorhandene Bauteile der Maschine als Meßwertgeber verwendet werden. Dadurch vergrößern sich weder Bauvolumen noch Bauaufwand der Maschine.The inventive, electro-hydraulically adjustable machine with the characterizing features of the main claim has the advantage that the means used consist of inexpensive measuring devices that are integrated into existing machine components or that existing machine components are used as sensors. As a result, neither the construction volume nor the construction effort of the machine increases.
Weiterhin vorteilhaft ist es, daß ein digitales Meßsignal vorliegt, das von einer elektronischen Schaltung sowohl zur Bestimmung der Exzentrizität des Hubrings als auch zur Drehzahlbestimmung des Rotors und ggf. für weitereIt is also advantageous that a digital measurement signal is present, which is provided by an electronic circuit both for determining the eccentricity of the cam ring and for determining the speed of the rotor and possibly for others
Funktionen, wie z.B. zur Geräuschdämpfung der Maschine, benutzt werden kann.Functions such as for noise reduction of the machine.
Erwähnenswert ist auch, daß die Abtastzeit, entsprechend den Anforderungen des Einsatzfalles, in gewissen Grenzen flexibel ist, indem die Anzahl der als Meßwertgeber eingesetzten Gleitschuhe variiert werden kann. Die kleinsten Abtastzeiten lassen sich demnach erreichen, wenn alle Gleitschuhe als Meßwertgeber eingesetzt werden. Günstig ist ferner, daß die Meßeinrichtung berührungslos arbeitet und deshalb weder Reibung noch Verschleiß unterliegt, was sich in einer langen Lebensdauer bei geringer Wartung bemerkbar macht.It is also worth mentioning that the scanning time is flexible within certain limits, depending on the requirements of the application, in that the number of sliding shoes used as a measuring sensor can be varied. The smallest Sampling times can therefore be achieved if all sliding blocks are used as sensors. It is also advantageous that the measuring device works without contact and is therefore not subject to friction or wear, which is evident in a long service life with little maintenance.
Weitere vorteilhafte Ausgestaltungen ergeben sich aus den Unteransprüchen und der Beschreibung.Further advantageous embodiments result from the subclaims and the description.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is shown in the drawing and explained in more detail in the following description.
Es zeigen Fig.l eine Radialkolbenmaschine im Querschnitt, in vereinfachter Darstellung und Fig.2 ein Diagramm mit dem Verlauf des im Meßwertaufnehmer erzeugten Signals in Abhängigkeit der Zeit bzw. des Verdrehwinkels des Rotors.FIG. 1 shows a radial piston machine in cross section, in a simplified representation, and FIG. 2 shows a diagram with the course of the signal generated in the transducer as a function of the time or the angle of rotation of the rotor.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Fig.l zeigt eine Radialkolbenmaschine 10 deren Gehäuse 11 durch einen nicht dargestellten Deckel verschlossen ist. Im Gehäuse 11 ist eine nach aussen abgedichtete, im wesentlichen zylindrische Ausnehmung 12 ausgebildet, in die zentrisch ein im Gehäuse ortsfest gelagerter Steuerzapfen 13 hineinragt. Auf diesem Teil des Steuerzapfens ist ein Rotor 14 drehbar gelagert, in dem mehrere radial verlaufende Bohrungen 15 Zylinder bilden, in denen Arbeitskolben 16 gleiten. Diese Arbeitskolben 16 sind gelenkig mit Gleitschuhen 17 verbunden, die aus den Bohrungen 15 des Rotors herausragen und die mittels nicht näher dargestellten Halteringen beweglich an einen zylindrischen Hubring 18 gefesselt sind. Die Innenseite des Hubrings bildet dabei die Lauffläche für diese Gleitschuhe 17. Der Hubring wird von zwei, im Gehäuse angeordneten, hydraulischen Verstellkolben 22 und 23, welche sich diametral gegenüberliegen und eine Versteileinrichtung bilden, in seiner Lage fixiert. Die Position des Hubrings 18 ist innerhalb der Ausnehmung, entlang der von den Verstellkolben 22 und 23 vorgegebenenFig.l shows a radial piston machine 10 whose housing 11 is closed by a cover, not shown. In the housing 11, an essentially cylindrical recess 12 is sealed to the outside, into which a control pin 13, which is mounted in a stationary manner in the housing, projects centrally. A rotor 14 is rotatably mounted on this part of the control pin, in which a plurality of radially running bores 15 form cylinders in which working pistons 16 slide. These working pistons 16 are connected in an articulated manner to sliding shoes 17 which protrude from the bores 15 of the rotor and which are movably tied to a cylindrical cam ring 18 by means of retaining rings (not shown). The inside of the cam ring forms the running surface for these sliding shoes 17. The cam ring is from two hydraulic adjusting pistons 22 and 23 arranged in the housing, which are diametrically opposed and form an adjusting device, are fixed in their position. The position of the cam ring 18 is within the recess, along that specified by the adjusting pistons 22 and 23
Richtung variabel. Parallel zur Verstellrichtung angebrachte Abflachungen am äußeren Umfang des Hubrings 24 und am Gehäuse 25 dienen als Führung bei der Verschiebung des Hubrings in Verstellrichtung und sichern diesen gleichzeitig gegen Verdrehen. Im Steuerzapfen 13 sind in der Höhe desDirection variable. Flats on the outer circumference of the cam ring 24 and on the housing 25, which are provided parallel to the direction of adjustment, serve as guides for the displacement of the cam ring in the direction of adjustment and at the same time secure it against rotation. In the control pin 13 are in the amount of
Rotors in Fig.l nicht erkennbare Steuerschlitze ausgebildet, die über ebenfalls im Steuerzapfen 13 angebrachte Längskanäle 26 und Durchbrüche mit radial im Gehäuse verlaufenden, nach außen dringenden Kanälen verbunden sind. Diese Kanäle 26 stellen Saug- und Druckkanäle dar und führen das Hydraulikmedium in die Maschine 10 hinein und unter Druck wieder heraus. Die Winkellage des Rotors 14 auf dem Steuerzapfen 13 ist so ausgeführt, daß die zwischen den Steuerschlitzen im Steuerzapfen 13 gelegenen Stege in einem Bereich liegen, in dem sich die Arbeitskolben 16 in ihren Totpunkten befinden. Der Rotor 14 wird über eine ebenfalls nicht dargestellte Kupplung von einer im Deckel gelagerten Treibwelle in Drehbewegung versetzt.Rotated in Fig.l not recognizable control slots are connected via longitudinal channels 26 and openings also mounted in the control pin 13 with radially extending in the housing, penetrating to the outside channels. These channels 26 represent suction and pressure channels and lead the hydraulic medium into the machine 10 and out again under pressure. The angular position of the rotor 14 on the control pin 13 is designed such that the webs located between the control slots in the control pin 13 lie in an area in which the working pistons 16 are at their dead centers. The rotor 14 is set in rotation by a coupling shaft, also not shown, by a drive shaft mounted in the cover.
Wie Fig.l zeigt, weist die Radialkolbenmaschine 10 zur Erfassung der Exzentrizität 20 des als Verstellorgan dienenden Hubrings 18, eine Meßeinrichtung auf, die über einen Meßwertaufnehmer 27 im Hubring 18 und über mehrere Meßwertgeber verfügt. Dabei dienen als Meßwertgeber die Gleitschuhe 17 der Arbeitskolben 16. Das von ihnen im Meßwertaufnehmer ausgelöste Signal wird einer Auswerteelektronik 28 zugeleitet.As Fig.l shows, the radial piston machine 10 has a measuring device for detecting the eccentricity 20 of the cam ring 18 serving as the adjusting member, which has a transducer 27 in the cam ring 18 and a plurality of transducers. The sliding shoes 17 of the working pistons 16 serve as measuring sensors. The signal triggered by them in the measuring sensor is fed to an electronic evaluation unit 28.
Die Wirkungsweise der verstellbaren Radialkolbenmaschine 10 wird im Folgenden erläutert, wobei deren grundsätzliche Funktion in Zusammenhang mit der hydraulischen VerStelleinrichtung als an sich bekannt vorausgesetzt wird. Bei der in Fig.l als linksdrehend dargestellten Radialkolbenmaschine 10 ist über die VerStelleinrichtung der Hubring 18 maximal nach links ausgestellt, wodurch sich eine Exzentrizität 20 zwischen Hubring 18 und Rotor 14 ergibt. Die eingangs erwähnte Fesselung der Gleitschuhe an den Hubring 18, in Verbindung mit dessen exzentrischer Lage zum Rotor 14, zwingt den über die Gleitschuhe 17 gelenkig verbundenen Arbeitskolben 16 im Rotor 14 bei dessen Drehbewegung eine Hubbewegung in radialer Richtung auf. Als Folge dieser Hubbewegung, in Verbindung mit den kinematischen Verhältnissen in der Radialkolbenmaschine 10, verändert sich der Abstand zwischen zwei aufeinanderfolgenden Gleitschuhen.The mode of operation of the adjustable radial piston machine 10 is explained in the following, its basic function in connection with the hydraulic adjusting device being assumed to be known per se. In the radial piston machine 10 shown in FIG. 1 as rotating to the left, the stroke ring 18 is maximally extended to the left via the adjusting device, which results in an eccentricity 20 between the stroke ring 18 and the rotor 14. The above-mentioned attachment of the sliding shoes to the lifting ring 18, in connection with its eccentric position relative to the rotor 14, forces the working piston 16, which is articulated via the sliding shoes 17, in the rotor 14 upon its rotating movement to force a lifting movement in the radial direction. As a result of this lifting movement, in conjunction with the kinematic conditions in the radial piston machine 10, the distance between two successive sliding shoes changes.
Diese Veränderung des Abstandes bezogen auf den vorhandenen Abstand bei Neutralposition der Maschine (Hubringexzentrizität = 0) ist proportional zur Exzentrizität 20 des Hubrings 18 und wird deshalb zur Erfassung dieser Exzentrizität 20 herangezogen.This change in the distance in relation to the existing distance in the neutral position of the machine (cam ring eccentricity = 0) is proportional to the eccentricity 20 of the cam ring 18 and is therefore used to detect this eccentricity 20.
In Richtung der Verstellorgane 22 und 23 des Hubrings 18 nimmt besagter Abstand einen Extremwert an, weshalb es für eine möglichst genaue Erfassung der Exzentrizität 20 von Vorteil ist, wenn der Meßwertaufnehmer 27, wie es Fig.l zeigt, dort angeordnet ist.In the direction of the adjusting members 22 and 23 of the cam ring 18, said distance assumes an extreme value, which is why it is advantageous for the most accurate detection of the eccentricity 20 if the measuring sensor 27, as shown in FIG. 1, is arranged there.
Prinzipbedingt gibt dieser solange eine Spannung als Signal ab, wie sich ein Gleitschuh 17 über ihm befindet. Erreicht z.B. die in Drehrichtung vordere Kante 17.1 des Gleitschuhs 17 den Meßwertaufnehmer 27, so führt dies im Signalverlauf 30 zu einem Spannungsanstieg 32 auf ein höheres Niveau 33, das solange erhalten bleibt bis die in Drehrichtung hintere Kante 17.2 des Gleitschuhs 17 am Meßwertaufnehmer 27 vorbei geglitten ist. Das Spannungssignal geht dann auf das ursprüngliche Niveau 34 zurück, wodurch im Signalverlauf 30 eine abfallende Flanke 35 entsteht. Bis die Vorderkante des nachfolgenden Gleitschuhs 17.3 den Meßwertaufnehmer 27 erreicht hat, verbleibt das Spannungssignal auf diesem niedereren Niveau 34, danach erfolgt erneut ein Spannungsanstieg 32 usw..In principle, this emits a voltage as a signal as long as a slide shoe 17 is above it. For example, if the front edge 17.1 of the sliding block 17 in the direction of rotation reaches the sensor 27, this leads in the signal curve 30 to a voltage rise 32 to a higher level 33, which is maintained until the rear edge 17.2 of the sliding block 17 slides past the sensor 27 in the direction of rotation is. The voltage signal then returns to the original level 34, as a result of which a falling edge 35 is formed in the signal curve 30. Until the front edge of the subsequent sliding shoe 17.3 has reached the measuring sensor 27, the voltage signal remains at this lower level 34, after which a voltage rise 32 takes place again, etc.
Der zeitliche Verzug 36 zwischen den, im Signalverlauf aufeinanderfolgenden, ansteigenden und abfallenden Spannungsflanken ist ein direktes Maß für den zwischen den zugehörigen Gleitschuhen vorhandenen Abstand, welcher, wie zuvor bereits erwähnt, proportional zur Exzentrizität des Hubrings 18 ist.The time delay 36 between the rising and falling voltage edges, which follow one another in the signal curve, is a direct measure of the distance between the associated sliding shoes, which, as already mentioned, is proportional to the eccentricity of the cam ring 18.
Wird z.B. der Hubring 18 aus seiner Position nach Fig.l in seine Neutralposition bewegt, so wird im Meßwertaufnehmer 27 ein Signalverlauf 31 (gestrichelte Linie) nach Fig.2 erzeugt. Die Abstandsverkleinerung zwischen zwei aufeinanderfolgenden Gleitschuhen 17 äußert sich in einem geringeren zeitlichen Abstand 38 zwischen abfallender und ansteigender Signalflanke.E.g. the cam ring 18 moves from its position according to FIG. 1 to its neutral position, then a signal curve 31 (dashed line) according to FIG. 2 is generated in the measuring sensor 27. The reduction in distance between two successive sliding shoes 17 manifests itself in a shorter time interval 38 between the falling and rising signal edge.
Der Signalverlauf 30 oder 31 wird nun in der Form von einer Auswerteelektronik 28 weiterverarbeitet, daß eine abfallende Flanke 35 im Signalverlauf einen Zähler mit hochfrequenter Zählfolge startet. Gestoppt wird dieser Zähler durch eine ansteigenden Flanke 32, wobei die Zählfrequenz einmalig so abzustimmen ist, daß das Zählergebnis der vorliegenden Exzentrizität 20 entspricht. Die Exzentrizität 20 des Hubrings 18 läßt sich somit stetig über den gesamten Verstellbereich des Hubrings 18 ermitteln.The signal curve 30 or 31 is then processed further in the form of evaluation electronics 28 such that a falling edge 35 in the signal curve starts a counter with a high-frequency counting sequence. This counter is stopped by a rising edge 32, the counting frequency being tuned once so that the counting result corresponds to the present eccentricity 20. The eccentricity 20 of the cam ring 18 can thus be determined continuously over the entire adjustment range of the cam ring 18.
Zur Drehzahlerfassung des Rotors 14 wird von der Auswerteelektronik 28 die Zeit 42 zwischen zwei ansteigenden Spannungsflanken 32 erfaßt, die umgekehrt proportional zur Maschinendrehzahl ist. Über beide Meßgrößen, Drehzahl und Exzentrizität, läßt sich der Volumenstrom der Maschine erfassen. 89 - 7 - PCI7DE96/00313In order to record the speed of the rotor 14, the evaluation electronics 28 record the time 42 between two rising voltage edges 32, which is inversely proportional to the machine speed. The volume flow of the machine can be recorded using both measured variables, speed and eccentricity. 89 - 7 - PCI7DE96 / 00313
Bei einer derartigen Meßeinrichtung hängt das mögliche Abtastintervall zwischen zwei Signalen sowohl von der Rotordrehzahl als auch von der Zahl der als Meßwertgeber benutzten Gleitschuhe 17 der Maschine ab. Bei einer üblichen Industriedrehzahl von 1500 1/min und bei siebenIn such a measuring device, the possible sampling interval between two signals depends both on the rotor speed and on the number of slide shoes 17 of the machine used as a measuring value transmitter. At a normal industrial speed of 1500 rpm and at seven
Arbeitskolben mit Gleitschuhen läßt sich beispielsweise ein Abtastintervall von ca. 5,7 ms darstellen, was für die meisten Anwendungsfälle ausreichend ist.Working pistons with sliding shoes can, for example, display a sampling interval of approx. 5.7 ms, which is sufficient for most applications.
Selbstverständlich sind Änderungen an der gezeigtenOf course, changes to the shown
Ausführungsform möglich, ohne vom Gedanken der Erfindung abzuweichen. So eignen sich für das berührungslose Wirkungsprinzip der Meßeinrichtung verschiedene Verfahren, wobei ein induktives, ein optoelektronisches oder ein magnetisches Wirkungsprinzip besonders vorteilhaft ist. Embodiment possible without departing from the spirit of the invention. Various methods are suitable for the contactless principle of action of the measuring device, an inductive, an optoelectronic or a magnetic principle of action being particularly advantageous.

Claims

Ansprüche Expectations
1. Verstellbare, hydrostatische Radialkolbenmaschine (10) mit einem Gehäuse (11) , in dem auf einem Steuerzapfen (13) ein Rotor (14) drehbar gelagert ist, der mit einer Antriebswelle zusammenwirkt und der in radial angeordneten Bohrungen (15) Arbeitskolben (16) führt, deren aus den Bohrungen (15) ragende Enden mit am Arbeitskolben (16) gelenkig gelagerten Gleitschuhen (17) ausgestattet sind, welche sich an der Innenseite eines Hubrings (18) abstützen, der über eine Einrichtung relativ zum Rotor (14) exzentrisch verstellbar ist, die über mindestens einen Verstellkolben (22) verfügt, welcher auf den Außenumfang des Hubrings (18) entlang dessen Verstellrichtung einwirkt und mit Mitteln zur Erfassung der Exzentrizität des Hubrings, dadurch gekennzeichnet, daß die Mittel eine Meßeinrichtung und eine damit zusammenwirkende Auswerteelektronik (28) aufweisen, welche die Exzentrizität (20) des Hubrings aus dem Abstand zwischen zwei aufeinanderfolgenden Gleitschuhen (17) ableiten.1. Adjustable, hydrostatic radial piston machine (10) with a housing (11) in which a rotor (14) is rotatably mounted on a control pin (13), which cooperates with a drive shaft and which has working pistons (16) arranged in radially arranged bores (15) ) leads, the ends of which protrude from the bores (15) are equipped with sliding shoes (17) which are articulated on the working piston (16) and which are supported on the inside of a cam ring (18) which is eccentric via a device relative to the rotor (14) is adjustable, which has at least one adjusting piston (22), which acts on the outer circumference of the cam ring (18) along its direction of adjustment and with means for detecting the eccentricity of the cam ring, characterized in that the means include a measuring device and evaluation electronics interacting therewith 28), which derive the eccentricity (20) of the cam ring from the distance between two successive sliding shoes (17).
2. Radialkolbenmaschine (10) nach Anspruch 1, dadurch gekennzeichnet, daß die Meßeinrichtung einen, im Hubring (18) angeordneten, Meßwertaufnehmer (27) aufweist, der insbesondere an die Innenseite des Hubrings (18) grenzt.2. Radial piston machine (10) according to claim 1, characterized in that the measuring device has a, arranged in the cam ring (18), transducer (27), which in particular borders on the inside of the cam ring (18).
3. Radialkolbenmaschine (10) nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, daß die Meßeinrichtung als Meßwertgeber mindestens zwei Gleitschuhe (17) , die in Drehrichtung hintereinander liegen, verwendet. 3. Radial piston machine (10) according to one of claims 1 and 2, characterized in that the measuring device as a transmitter uses at least two sliding shoes (17) which are located one behind the other in the direction of rotation.
4. Radialkolbenmaschine (10) nach einem oder mehreren der Ansprüche 1,2,3, dadurch gekennzeichnet, daß der Meßwertaufnehmer in einem Bereich des Hubrings (18) angeordnet ist in dem der Abstand zwischen zwei vorbeigleitenden Gleitschuhen (17) einen Extremwert annimmt, d.h. im wesentlichen gleichachsig zu der von den Verstellkolben (22 und 23) vorgegebenen Richtung angeordnet ist.4. Radial piston machine (10) according to one or more of claims 1, 2, 3, characterized in that the measuring sensor is arranged in an area of the cam ring (18) in which the distance between two sliding shoes (17) sliding past takes on an extreme value, i.e. is arranged substantially coaxially to the direction specified by the adjusting pistons (22 and 23).
5. Radialkolbenmaschine (10) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Meßeinrichtung nach einem berührungslosen Wirkungsprinzip arbeitet.5. Radial piston machine (10) according to one of claims 1 to 4, characterized in that the measuring device operates according to a non-contact principle of action.
6. Radialkolbenmaschine (10) nach einem oder mehreren der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Hubring (18) im Gehäuse (11) gegen Verdrehung gesichert angeordnet ist, wozu Gleitflächen (24 und 25) an Hubring (18) und Gehäuse (11) ausgebildet sind, die insbesondere parallel zur Verstellrichtung verlaufen. 6. Radial piston machine (10) according to one or more of claims 1 to 5, characterized in that the cam ring (18) in the housing (11) is arranged secured against rotation, for which purpose sliding surfaces (24 and 25) on cam ring (18) and housing (11) are formed, which in particular run parallel to the direction of adjustment.
EP96902897A 1995-04-13 1996-02-24 Adjustable hydrostatic radial-piston motor Expired - Lifetime EP0766788B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19513987 1995-04-13
DE19513987A DE19513987C2 (en) 1995-04-13 1995-04-13 Adjustable, hydrostatic radial piston machine
PCT/DE1996/000313 WO1996032589A1 (en) 1995-04-13 1996-02-24 Adjustable hydrostatic radial-piston motor

Publications (2)

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EP0766788A1 true EP0766788A1 (en) 1997-04-09
EP0766788B1 EP0766788B1 (en) 2001-01-10

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US (1) US5752427A (en)
EP (1) EP0766788B1 (en)
JP (1) JP3921240B2 (en)
KR (1) KR100383156B1 (en)
CN (1) CN1079910C (en)
DE (2) DE19513987C2 (en)
WO (1) WO1996032589A1 (en)

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US5752427A (en) 1998-05-19
KR100383156B1 (en) 2003-08-27
DE19513987C2 (en) 1998-10-08
DE59606298D1 (en) 2001-02-15
DE19513987A1 (en) 1996-10-17
EP0766788B1 (en) 2001-01-10
JPH10501601A (en) 1998-02-10
CN1145658A (en) 1997-03-19
CN1079910C (en) 2002-02-27
JP3921240B2 (en) 2007-05-30
WO1996032589A1 (en) 1996-10-17

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