EP0004120B1 - Gear-type machine with relief means for the liquid in the interengagement space between the teeth - Google Patents

Gear-type machine with relief means for the liquid in the interengagement space between the teeth Download PDF

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Publication number
EP0004120B1
EP0004120B1 EP79200119A EP79200119A EP0004120B1 EP 0004120 B1 EP0004120 B1 EP 0004120B1 EP 79200119 A EP79200119 A EP 79200119A EP 79200119 A EP79200119 A EP 79200119A EP 0004120 B1 EP0004120 B1 EP 0004120B1
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EP
European Patent Office
Prior art keywords
gears
helical gears
considered
lateral face
gear
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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.)
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EP79200119A
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German (de)
French (fr)
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EP0004120A3 (en
EP0004120A2 (en
Inventor
Theodorus Henricus Korse
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Korse Theodorus Henricus
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Korse Theodorus Henricus
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Publication of EP0004120A2 publication Critical patent/EP0004120A2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement

Definitions

  • the invention relates to a gear machine (pump or motor) with helical gears meshing in external or internal engagement, the shafts of which are rotatably mounted in the housing and / or housing cover or in bearing bodies arranged in the housing, the engagement area on the side surfaces facing the gearwheels, i.e. in the Housing wall and / or housing cover or in the bearing bodies, recesses are formed, of which the recesses on the pressure chamber side are connected to the pressure chamber and the recesses on the suction chamber side are connected to the suction chamber.
  • the recess on the pressure chamber side and the suction chamber side in a side surface facing the gearwheels are separated from one another by a web of a certain width.
  • FR-A-2 352 947 describes a straight-toothed gear machine with at least one recess, in which the distance between the recess parts to the connecting line of the center points is selected such that the changeover point of the sealing tooth engagement and the single engagement point of a gear pair coincide on the pressure side. Because of this asymmetrical reversal, the recess on the suction chamber side is arranged asymmetrically with respect to the recess on the pressure chamber side, with respect to the connecting line of the gearwheel centers.
  • FR-A-1355756 describes a gear machine with helical gears, in which a pressure space-side or suction space-side recess is arranged in a side surface.
  • a backlash of zero or almost zero is aimed for in order to achieve a greatly reduced flow rate fluctuation and torque fluctuation.
  • Zero or almost zero is understood to mean a backlash that is less than the usual backlash of z. B. 0.3 mm. This is achieved in that in the case of this straight toothing with no or almost no flank play, the web width between the recess on the pressure chamber side and on the suction chamber side is reduced to half the value - compared to that of the same toothing with flank play. The problem of squeezing the hydraulic fluid and cavitation in an enclosed tooth gap occurs even more than in the case of a gear machine with backlash.
  • the invention has for its object to provide a gear machine of the type mentioned, in which the available squeezing areas are so large that the hydraulic fluid can flow into the squeezing oil chamber without squeezing or risk of cavitation and can also flow out of it again.
  • the pressure chamber side and the suction chamber side recess on the leading end face of the helical toothing are thus offset by a distance V in the suction chamber side compared to the pressure chamber side or the suction chamber side recess on the trailing end side of the helical toothing.
  • the web width is unchanged from that of the comparable spur toothing of the same face cut.
  • the size of the displacement of the recesses is independent of whether there is backlash or not.
  • the technical progress that can be achieved with the invention is based on several advantages.
  • the available squeezing surfaces of the recesses are considerably larger and can also flow into the squeezing oil space and also flow out of it again via the gaps of the tooth flanks, which partially lie outside the mechanical engagement area.
  • Only through this advantage according to the invention is it possible for the displacement process to take place undisturbed, for the theoretical fluctuation in the flow rate to be minimal, and for the hydraulic fluid to flow in or out of the enclosed tooth space undisturbed without the risk of being crushed or cavitated.
  • the tooth shows wheel machine with a low technical effort to a very low sound pressure level, ie compared to a known gear machine with the same flow rate, the speed can be higher and the stroke volume can be smaller in the gear machine according to the invention at the same sound pressure level.
  • the gear machine according to FIGS. 1 to 3 has a housing 1 which is closed on both sides by housing covers 2 and 3.
  • the housing 1 has a continuous housing opening 4 which is formed by two intersecting bores 5 and 6.
  • the housing opening 4 has approximately the shape of an eight.
  • two bearing bodies 7 and 8 are arranged, in the bearing bores 9 and 10, a driving gear 11 is rotatably mounted.
  • two bearing bodies 12 and 13 are arranged in the bore 6, in whose bearing bores 14 and 15 the driven gear wheel 16 is rotatably mounted.
  • the gears 11 and 16 are rotatably supported with their shafts directly in the housing 1a or in the housing cover 2a.
  • the driving gear 11 has right-hand teeth; the driven gear 16 has left-rising teeth.
  • the driving gear 11 is driven clockwise.
  • recesses 19, 20, 21, 22 are provided in order to achieve a maximum squeezing area and a minimal flow fluctuation so that with decreasing volume of the enclosed tooth gap, the enclosed tooth gap is connected to the pressure chamber D via the recesses 19 and 21 displaced by a distance V from one another, and that with increasing volume of the enclosed tooth gap the enclosed tooth gap is connected via the recesses displaced by a distance V from one another 20 and 22 is connected to the suction chamber S.
  • Fig. 4 is given for a helical toothing with backlash, how the recesses 19 to 22 are designed;
  • the center distance extends from the center M, of the driving helical gear 11 with right-hand teeth to the center M 2 of the driven helical gear 16 with left-hand teeth.
  • the pole P lies on the center of the connecting line from M to M 2.
  • the thin solid line 23 follows the contours of the toothing on the front trailing end face 18 of the helical toothing.
  • the thin dash-dotted line 24 follows the contour of the toothing on the rear leading end face 17 of the helical toothing.
  • the thick line 25 represents the contour of the helical toothing in the center of the wheel.
  • the helical toothing is drawn for the position in which the enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 26 reaches its minimum in the wheel center.
  • the pressure changeover process takes place at this very moment, ie the tooth gap is separated from the pressure chamber D and connected to the suction chamber S.
  • the recesses of the helical toothing with backlash are matched to this pressure changeover process.
  • the straight web edges 27 and 28 of the essentially rectangular recesses 19 and 20 of parallel to M i , M 2 are left on the rear leading end face 17 of the helical toothing fenden lines formed by the two in this rear leading end face 17 lying on the engagement plane 29 contact points 30 and 31.
  • the straight web edges 32 and 33 of the substantially rectangular recesses 21 and 22 of lines running parallel to M i , M 2 are through the two contact points 34 lying in this front trailing end face 18 on the engagement plane 29 and 35 formed.
  • the line of symmetry 88 to the web edges 27, 28 is offset in the direction of the suction space S by a distance% and the line of symmetry 89 to the web edges 32, 33 is offset in the direction of the pressure space D by a distance% to the connecting line M i M 2
  • the recesses 19, 21 and 20, 22 shifted by the distance V.
  • the depth 36 of the recesses 19 to 22 is a few millimeters and the width 37 of the recesses 19 to 22 is approximately equal to the tooth height.
  • the recesses 19, 20 and 21, 22 on the pressure chamber side and suction chamber side, respectively, located on one end face of the toothing, are separated from one another by a web with the width 38.
  • the web width 38 is, compared to the web width 39 of the comparable straight toothing shown in FIG. 5 with the same face cut, still large.
  • the squeezing surfaces available for the straight toothing for a torsion angle ⁇ 1 are shown in FIG. 5 and the squeezing surfaces available for the helical toothing in FIG. 6.
  • the squeezing surface 40 is available on both end faces of the straight toothing.
  • the squeezing surface 41 is available on the leading end face 17 and the squeezing surface 42 is available on the trailing end face 18.
  • a squeezing surface with a gap 43 is available.
  • the recesses 19 to 22 on the two end faces 17, 18 of the helical toothing can also have a somewhat different shape.
  • the recesses must always be designed in such a way that the enclosed tooth gap is connected to the pressure chamber D via the recesses 19, 21 on the pressure chamber side only with decreasing size of the area of the enclosed tooth gap in the wheel center and that only with increasing size of the area of the enclosed tooth gap in the wheel center the enclosed tooth gap is connected to the suction space S via the recesses 20, 22 on the suction space side.
  • helical gearing can be used in an analogous manner by moving the recesses on the pressure chamber and suction chamber side by a distance% in the direction of the suction chamber S and the displacement of the recess on the pressure chamber and suction chamber side by a distance% in according to the invention on the trailing end In the direction of pressure chamber D, the size of the squeezing area can be increased considerably.
  • the web width 77 is equal to the web width 54 of the comparable straight toothing without or almost without backlash, as can be seen from FIGS. 8 and 9.
  • the recesses are designed such that, with the volume of an enclosed tooth gap decreasing, the enclosed tooth gap via the recesses 55 and 56 with the pressure chamber D displaced by a distance V from one another is connected, and that as the volume of the enclosed tooth gap increases, the included tooth gap is connected to the suction chamber S via the recesses 57 and 58 on the suction chamber side displaced by a distance V from one another.
  • FIG. 9 shows how the recesses 55, 56, 57, 58 according to the invention are designed.
  • the thin solid line 60 follows the contours of the helical teeth on the front trailing end 61 of the helical teeth.
  • the thin dash-dotted line 62 follows the contours of the Helical teeth on the rear leading end face 63 of the helical teeth.
  • the thick line 64 represents the contour of the helical toothing in the center of the wheel.
  • the helical toothing is drawn in the position in which an enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 59 is smallest in the center of the wheel.
  • the pressure reversal process must take place, i. H. the tooth space is separated from the pressure chamber D and connected to the suction chamber S.
  • the recesses 55 to 58 of the helical toothing are matched to this pressure reversing process with no or almost no backlash.
  • the straight web edges 65 and 66 of the substantially rectangular recesses 56 and 58 of lines running parallel to M i M 2 are on the rear leading end face 63 of the helical toothing through the contact points 69 lying in this rear leading end face 63 on the engagement planes 68 and 67 or 70 formed.
  • the line of symmetry 90 to the web edges 65, 66 is in the direction of the suction space S by the distance and the line of symmetry 91 to the web edges 71, 72 is in the direction of the pressure space D by the same distance offset to the connecting line M 1 M 2 .
  • the depth 75 of the recesses 55 to 58 is a few millimeters.
  • the width 76 of the recesses 55 to 58 is approximately equal to the tooth height.
  • the recesses 56, 58 and 55, 57 on the pressure chamber side and suction chamber side, respectively, located on one end face of the helical toothing, are separated from one another by a web with the width 77.
  • the web width 77 has remained unchanged compared to the web width 54 of the comparable straight toothing shown in FIG. 8 without or almost without backlash with the same face cut.
  • the recesses 55 to 58 on the two end faces 61, 63 of the helical toothing can also have a slightly different shape: the recesses must always be designed such that, with the size of the area of an enclosed tooth gap in the center of the wheel being removable, the enclosed tooth gap is above the pressure chamber-side recesses 55, 56 is connected to the pressure chamber D and that with increasing size of an area of the enclosed tooth gap in the center of the wheel, the enclosed tooth gap is connected to the suction chamber S via the recesses 57, 58 on the suction chamber side.
  • notches 78, 79, 80, 81, 82, 83, 84, 85 are made, which are from the root circles 86, 87 and contours of the tooth flank of the adjacent gearwheel on the root circle are formed at an angle of rotation ⁇ 1 at which the area of an enclosed M 1 or M 2 side tooth gap in the wheel center reaches its minimum.
  • These notches 78 to 85 increase the available squeezing area even more.
  • the construction of the notches 79, 81, 82, 84 is shown only for the angle of rotation cp, at which the area of the enclosed tooth space on the M z side reaches its minimum in the center of the wheel.

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

Description

Die Erfindung betrifft eine Zahnradmaschine (Pumpe oder Motor) mit im Ausseneingriff oder Inneneingriff kämmenden schrägverzahnten Zahnrädern, deren Wellen in Gehäuse und/oder Gehäusedeckel oder in im Gehäuse angeordneten Lagerkörpern drehbar gelagert sind, wobei im Eingriffsbereich an den den Zahnrädern zugewandten Seitenflächen, also in der Gehäusewand und/ oder Gehäusedeckel oder in den Lagerkörpern, Ausnehmungen ausgebildet sind, von denen die druckraumseitigen Ausnehmungen mit dem Druckraum und die saugraumseitigen Ausnehmungen mit dem Saugraum verbunden sind. Die druckraumseitige und die saugraumseitige Ausnehmung in einer den Zahnrädern zugewandten Seitenfläche sind durch einen Steg bestimmter Breite voneinander getrennt.The invention relates to a gear machine (pump or motor) with helical gears meshing in external or internal engagement, the shafts of which are rotatably mounted in the housing and / or housing cover or in bearing bodies arranged in the housing, the engagement area on the side surfaces facing the gearwheels, i.e. in the Housing wall and / or housing cover or in the bearing bodies, recesses are formed, of which the recesses on the pressure chamber side are connected to the pressure chamber and the recesses on the suction chamber side are connected to the suction chamber. The recess on the pressure chamber side and the suction chamber side in a side surface facing the gearwheels are separated from one another by a web of a certain width.

Bekannte Zahnradmaschinen dieser Art mit Geradverzahnung haben den Nachteil, dass der im Eingriffsbereich der Verzahnung gebildete Quetschölraum sein Volumen sehr schnell ändert, wodurch die Druckflüssigkeit durch die verhältnismässig kleinen Ausquetschflächen der Ausnehmungen den Quetschölraum schwierig einströmen und auch wieder aus ihm ausströmen kann. Die Druckflüssigkeit in diesem Quetschölraum wird trotz eventueller theoretisch richtig dimensionierter Ausnehmungen stark gequetscht und dekomprimiert, was Druckpulsationen, Kavitation und Geräusche zur Folge hat.Known gear machines of this type with straight toothing have the disadvantage that the pinch oil space formed in the engagement area of the toothing changes its volume very quickly, as a result of which the pressure fluid can flow in and out of the pinch oil space with difficulty due to the relatively small squeezing areas of the recesses. The pressure fluid in this pinch oil chamber is squeezed and decompressed despite possible theoretically correctly dimensioned recesses, which results in pressure pulsations, cavitation and noise.

Dies kann bei der meistens verwendeten Geradverzahnung schwierig vermieden werden, weil die Grösse der Ausquetschfläche als Funktion des Verdrehungswinkels des treibenden Rades nicht grösser sein kann als im Fall von optimal ausgelegten Ausnehmungen, d.h. Ausnehmungen, die etwa symmetrisch zum Pol im Eingriffsbereich möglichst an beiden Stirnseiten der Verzahnung angeordnet sind.This is difficult to avoid with the most commonly used spur gearing because the size of the squeezing surface as a function of the angle of rotation of the driving wheel cannot be greater than in the case of optimally designed recesses, i.e. Recesses that are arranged approximately symmetrically to the pole in the engagement area as possible on both end faces of the toothing.

Die FR-A-2 352 947 beschreibt eine geradverzahnte Zahnradmaschine mit mindestens einer Ausnehmung, bei der der Abstand zwischen den Ausnehmungsteilen zur Verbindungslinie der Mittelpunkte so gewählt ist, dass an der Druckseite der Umsteuerpunkt des dichtenden Zahneingriffs und der Einzeleingriffspunkt eines Zahnradpaares zusammenfallen. Wegen dieser unsymmetrischen Umsteuerung ist die saugraumseitige Ausnehmung gegenüber der druckraumseitigen Ausnehmung, bezüglich der Verbindungslinie der Zahnradmittelpunkte, unsymmetrisch angeordnet.FR-A-2 352 947 describes a straight-toothed gear machine with at least one recess, in which the distance between the recess parts to the connecting line of the center points is selected such that the changeover point of the sealing tooth engagement and the single engagement point of a gear pair coincide on the pressure side. Because of this asymmetrical reversal, the recess on the suction chamber side is arranged asymmetrically with respect to the recess on the pressure chamber side, with respect to the connecting line of the gearwheel centers.

Die FR-A-1355756 beschreibt eine Zahnradmaschine mit schrägverzahnten Zahnrädern, bei der in einer Seitenfläche eine druckraumseitige oder saugraumseitige Ausnehmung angeordnet ist.FR-A-1355756 describes a gear machine with helical gears, in which a pressure space-side or suction space-side recess is arranged in a side surface.

Bei einer weiteren bekannten Zahnradmaschine wird zur Erreichung einer stark verminderten Förderstromschwankung und Drehmomentschwankung ein Flankenspiel von null oder nahezu null angestrebt. Dabei wird unter null oder nahezu null ein Flankenspiel verstanden, das geringer als das übliche Flankenspiel von z. B. 0,3 mm ist. Dies wird dadurch erreicht, dass bei dieser Geradverzahnung ohne oder nahezu ohne Flankenspiel die Stegbreite zwischen der druckraumseitigen und saugraumseitigen Ausnehmung - verglichen mit der der gleichen Verzahnung mit Flankenspiel - auf den halben Wert reduziert wird. Noch stärker als bei einer Zahnradmaschine mit Flankenspiel tritt hier das Problem der Quetschung der Druckflüssigkeit und der Kavitation in einer eingeschlossenen Zahnlücke auf.In another known gear machine, a backlash of zero or almost zero is aimed for in order to achieve a greatly reduced flow rate fluctuation and torque fluctuation. Zero or almost zero is understood to mean a backlash that is less than the usual backlash of z. B. 0.3 mm. This is achieved in that in the case of this straight toothing with no or almost no flank play, the web width between the recess on the pressure chamber side and on the suction chamber side is reduced to half the value - compared to that of the same toothing with flank play. The problem of squeezing the hydraulic fluid and cavitation in an enclosed tooth gap occurs even more than in the case of a gear machine with backlash.

Der Erfindung liegt die Aufgabe zugrunde, eine Zahnradmaschine der eingangs genannten Art zu schaffen, bei der die zur Verfügung stehenden Ausquetschflächen so gross sind, dass die Druckflüssigkeit ohne Quetschung oder Kavitationsgefahr in den Quetschölraum einströmen und auch wieder aus ihm ausströmen kann.The invention has for its object to provide a gear machine of the type mentioned, in which the available squeezing areas are so large that the hydraulic fluid can flow into the squeezing oil chamber without squeezing or risk of cavitation and can also flow out of it again.

Diese Aufgabe wird'gemäss der Erfindung dadurch gelöst, dass die druckraumseitige und saugraumseitige Ausnehmung an der voreilenden Stirnseite der Schrägverzahnung aus der Symmetrielage zum Pol um eine Distanz % quer zur Verbindungslinie der zwei Mittelpunkte der Zahnräder in Richtung Saugraum verschoben ist und dass die druckraumseitige und saugraumseitige Ausnehmung an der nacheilenden Stirnseite der Schrägverzahnung aus der Symmetrielage zum Pol um eine gleich grosse Distanz 1/2 quer zur Verbindungslinie der zwei Mittelpunkte der Zahnräder in Richtung Druckraum verschoben ist. Die druckraumseitige und die saugraumseitige Ausnehmung an der voreilenden Stirnseite der Schrägverzahnung sind also gegenüber der druckraumseitigen bzw. der saugraumseitigen Ausnehmung an der nacheilenden Stirnseite der Schrägverzahnung um eine Distanz V in saugraumseitiger Richtung versetzt.This object is achieved according to the invention in that the pressure-space side and saugraumseitige recess on the leading end side of the helical gear from the symmetry position to the pole by a distance% to the line connecting the two center points of the gears is shifted in the direction of the suction chamber transversely and in that the pressure-space side and saugraumseitige ' Recess on the trailing end of the helical toothing is shifted from the symmetry position to the pole by an equally large distance 1/2 transversely to the connecting line of the two center points of the gear wheels in the direction of the pressure chamber. The pressure chamber side and the suction chamber side recess on the leading end face of the helical toothing are thus offset by a distance V in the suction chamber side compared to the pressure chamber side or the suction chamber side recess on the trailing end side of the helical toothing.

Die Stegbreite ist gegenüber derjenigen der vergleichbaren Geradverzahnung gleichen Stirnschnittes unverändert. Die Grösse der Verschiebung der Ausnehmungen ist unabhängig davon, ob ein Flankenspiel vorhanden ist oder nicht.The web width is unchanged from that of the comparable spur toothing of the same face cut. The size of the displacement of the recesses is independent of whether there is backlash or not.

Der mit der Erfindung erzielbare technische Fortschritt beruht auf mehreren Vorteilen. Insbesondere sind gegenüber der vergleichbaren Geradverzahnung die zur Verfügung stehenden Ausquetschflächen der Ausnehmungen wesentlich grösser und kann auch über die Spalte der teilweise ausserhalb des mechanischen Eingriffsbereiches liegenden Zahnflanken Druckflüssigkeit in den Quetschölraum einströmen und auch wieder aus ihm ausströmen. Nur durch diesen erfindungsgemässen Vorteil ist es möglich, dass der Verdrängungsvorgang ungestört stattfinden kann, die theoretische Förderstromschwankung minimal ist und die Druckflüssigkeit ohne die Gefahr einer Quetschung oder Kavitation in die eingeschlossene Zahnlücke ungestört hinein oder aus ihr heraus fliessen kann. Da bei dieser erfindungsgemässen Zahnradmaschine nicht nur die hydraulischen Geräusche, sondern auch die mechanischen Geräusche geringer sind, weist die Zahnradmaschine bei einem geringen technischen Aufwand einen sehr niedrigen Schalldruckpegel auf, d. h. verglichen mit einer bekannten Zahnradmaschine gleich grossen Förderstroms, kann bei der Zahnradmaschine gemäss der Erfindung bei gleichem Schalldruckpegel die Drehzahl höher und das Hubvolumen kleiner sein.The technical progress that can be achieved with the invention is based on several advantages. In particular, compared to the comparable straight toothing, the available squeezing surfaces of the recesses are considerably larger and can also flow into the squeezing oil space and also flow out of it again via the gaps of the tooth flanks, which partially lie outside the mechanical engagement area. Only through this advantage according to the invention is it possible for the displacement process to take place undisturbed, for the theoretical fluctuation in the flow rate to be minimal, and for the hydraulic fluid to flow in or out of the enclosed tooth space undisturbed without the risk of being crushed or cavitated. Since not only the hydraulic noises, but also the mechanical noises are lower in this gearwheel machine according to the invention, the tooth shows wheel machine with a low technical effort to a very low sound pressure level, ie compared to a known gear machine with the same flow rate, the speed can be higher and the stroke volume can be smaller in the gear machine according to the invention at the same sound pressure level.

Da die theoretische Förderstromschwankung einer schrägverzahnten und einer vergleichbaren geradverzahnten Zahnradmaschine ungefähr gleich ist, ist auch die durch diese theoretische Förderstromschwankung verursachte Druckpulsation für beide Zahnradmaschinen ungefähr gleich gross.Since the theoretical flow fluctuation of a helical gear and a comparable straight toothed gear machine is approximately the same, the pressure pulsation caused by this theoretical flow fluctuation is approximately the same for both gear machines.

Die Erfindung ist in der Zeichnung an mehreren Ausführungsbeispielen veranschaulicht. Es zeigen:

  • Fig. 1 den Schnitt 1-I der Zahnradmaschine nach Fig. 2,
  • Fig. 1a den Längsschnitt durch eine abgewandelte Ausführungsform der Erfindung,
  • Fig. 2 den Schnitt 11-11 aus Fig. 1,
  • Fig. 3 den Schnitt III-III aus Fig. 2,
  • Fig. 4 die Ausnehmungen für eine Schrägverzahnung mit Flankenspiel,
  • Fig. 5 die Ausquetschfläche einer mit der Schrägverzahnung nach Fig. 4 vergleichbaren Geradverzahnung mit Flankenspiel bei einem bestimmten Verdrehungswinkel ϕ1,
  • Fig. 6 die Ausquetschfläche einer Schrägverzahnung nach Fig. 4 für denselben Verdrehungswinkel ϕ1 nach Fig. 5,
  • Fig. 7 eine abgewandelte Ausführungsform für die Ausnehmungen (bei einer Schrägverzahnung mit Flankenspiel), konform Fig. 4,
  • Fig. 8 eine mit der Schrägverzahnung nach Fig. 9 vergleichbare Geradverzahnung ohne Flankenspiel,
  • Fig. 9 die Ausnehmungen für eine Schrägverzahnung ohne oder nahezu ohne Flankenspiel,
  • Fig. 10 den Schnitt III-III aus Fig. 2, jedoch bei einer Zahnradmaschine ohne oder nahezu ohne Flankenspiel,
  • Fig. 11 eine abgewandelte Ausführungsform für die Ausnehmungen an der hinteren voreilenden Stirnseite einer Schrägverzahnung ohne Flankenspiel und
  • Fig. 12 die Ausführungsform nach Fig. 11 mit den Ausnehmungen an der vorderen nacheilenden Stirnseite.
The invention is illustrated in the drawing using several exemplary embodiments. Show it:
  • 1 shows the section 1-I of the gear machine according to FIG. 2,
  • 1a shows the longitudinal section through a modified embodiment of the invention,
  • 2 shows the section 11-11 of Fig. 1,
  • 3 shows the section III-III from FIG. 2,
  • 4 the recesses for helical teeth with backlash,
  • 5 shows the squeezing surface of a spur toothing comparable to the helical toothing according to FIG. 4 with backlash at a certain angle of rotation ϕ 1 ,
  • 6 shows the squeezing surface of a helical toothing according to FIG. 4 for the same angle of rotation ϕ 1 according to FIG. 5,
  • 7 shows a modified embodiment for the recesses (with helical teeth with backlash), conforming to FIG. 4,
  • 8 shows a straight toothing comparable to the helical toothing according to FIG. 9 without backlash,
  • 9 the recesses for a helical toothing without or almost without backlash,
  • 10 shows the section III-III from FIG. 2, but in a gear machine without or almost without backlash,
  • Fig. 11 shows a modified embodiment for the recesses on the rear leading end face of a helical toothing without backlash and
  • Fig. 12 shows the embodiment of FIG. 11 with the recesses on the front trailing end.

Die Zahnradmaschine nach den Figuren 1 bis 3 hat ein Gehäuse 1, das beidseitig durch Gehäusedeckel 2 und 3 verschlossen ist. Das Gehäuse 1 hat eine durchgehende Gehäuseöffnung 4, die durch zwei sich überschneidende Bohrungen 5 und 6 gebildet ist. Die Gehäuseöffnung 4 hat dadurch etwa die Form einer Acht. In der Bohrung 5 sind zwei Lagerkörper 7 und 8 angeordnet, in deren Lagerbohrungen 9 bzw. 10 ein treibendes Zahnrad 11 drehbar gelagert ist. Ebenso sind in der Bohrung 6 zwei Lagerkörper 12 und 13 angeordnet, in deren Lagerbohrungen 14 und 15 das getriebene Zahnrad 16 drehbar gelagert ist.The gear machine according to FIGS. 1 to 3 has a housing 1 which is closed on both sides by housing covers 2 and 3. The housing 1 has a continuous housing opening 4 which is formed by two intersecting bores 5 and 6. The housing opening 4 has approximately the shape of an eight. In the bore 5, two bearing bodies 7 and 8 are arranged, in the bearing bores 9 and 10, a driving gear 11 is rotatably mounted. Likewise, two bearing bodies 12 and 13 are arranged in the bore 6, in whose bearing bores 14 and 15 the driven gear wheel 16 is rotatably mounted.

Die Zahnradmaschine nach Fig. 1a besteht aus einem Gehäuse 1a mit nur einem Gehäusedeckel 2a. Die Zahnräder 11 und 16 sind mit ihren Wellen unmittelbar im Gehäuse 1a bzw. im Gehäusedekkel 2a drehbar gelagert.1a consists of a housing 1a with only one housing cover 2a. The gears 11 and 16 are rotatably supported with their shafts directly in the housing 1a or in the housing cover 2a.

Das treibende Zahnrad 11 hat rechtssteigende Zähne; das getriebene Zahnrad 16 hat linkssteigende Zähne. Das treibende Zahnrad 11 ist im Uhrzeigersinn angetrieben. In den Lagerkörpern 7 und 12 an der voreilenden Stirnseite 17 der Schrägverzahnung und in den Lagerkörpern 8 und 13 an der nacheilenden Stirnseite 18"der Schrägverzahnung sind zur Erreichung einer maximalen Ausquetschfläche und einer minimalen Förderstromschwankung Ausnehmungen 19, 20, 21, 22 so angebracht, dass bei abnehmendem Volumen der eingeschlossenen Zahnlücke die eingeschlossene Zahnlücke über die um eine Distanz V zueinander verschobenen druckraumseitigen Ausnehmungen 19 und 21 mit dem Druckraum D verbunden ist, und dass bei zunehmendem Volumen der eingeschlossenen Zahnlücke die eingeschlossene Zahnlücke über die um eine Distanz V zueinander verschobenen saugraumseitigen Ausnehmungen 20 und 22 mit dem Saugraum S verbunden ist.The driving gear 11 has right-hand teeth; the driven gear 16 has left-rising teeth. The driving gear 11 is driven clockwise. In the bearing bodies 7 and 12 on the leading end face 17 of the helical toothing and in the bearing bodies 8 and 13 on the trailing end face 18 "of the helical toothing, recesses 19, 20, 21, 22 are provided in order to achieve a maximum squeezing area and a minimal flow fluctuation so that with decreasing volume of the enclosed tooth gap, the enclosed tooth gap is connected to the pressure chamber D via the recesses 19 and 21 displaced by a distance V from one another, and that with increasing volume of the enclosed tooth gap the enclosed tooth gap is connected via the recesses displaced by a distance V from one another 20 and 22 is connected to the suction chamber S.

Da bei abnehmendem Volumen der eingeschlossenen Zahnlücke die Fläche der eingeschlossenen Zahnlücke in Radmitte kleiner wird und bei zunehmendem Volumen der eingeschlossenen Zahnlücke die Fläche der eingeschlossenen Zahnlücke in Radmitte grösser wird, kann ganz genau bestimmt werden, für welchen Verdrehungswinkel ϕ↑ des treibenden Zahnrades 11 die eingeschlossene Zahnlücke ihr kleinstes Volumen erreicht und wann der sogenannte Druckumsteuervorgang stattfinden muss.Since the area of the enclosed tooth gap in the center of the wheel becomes smaller as the volume of the enclosed tooth gap decreases and the area of the enclosed tooth gap in the center of the wheel increases with increasing volume of the enclosed tooth gap, it can be determined exactly for which angle of rotation ϕ ↑ of the driving gear 11 the included one Tooth gap reaches its smallest volume and when the so-called pressure changeover process has to take place.

Aus Fig. 4 ist für eine Schrägverzahnung mit Flankenspiel angegeben, wie die Ausnehmungen 19 bis 22 konzipiert sind; Der Achsenabstand reicht vom Mittelpunkt M, des treibenden schrägverzahnten Zahnrades 11 mit rechtssteigenden Zähnen bis zum Mittelpunkt M2 des getriebenen schrägverzahnten Zahnrades 16 mit linkssteigenden Zähnen. Auf der Mitte der Verbindungslinie von M, mit M2 liegt der Pol P. Die dünne durchgezogene Linie 23 folgt den Konturen der Verzahnung an der vorderen nacheilenden Stirnseite 18 der Schrägverzahnung. Die dünne strichpunktierte Linie 24 folgt der Kontur der Verzahnung an der hinteren voreilenden Stirnseite 17 der Schrägverzahnung. Die dicke Linie 25 stellt die Kontur der Schrägverzahnung in Radmitte dar. Die Schrägverzahnung ist für die Position gezeichnet, in der die eingeschlossene Zahnlücke ihr kleinstes Volumen erreicht oder in der die schraffierte Fläche der eingeschlossenen Zahnlücke 26 in Radmitte ihr Minimum erreicht.From Fig. 4 is given for a helical toothing with backlash, how the recesses 19 to 22 are designed; The center distance extends from the center M, of the driving helical gear 11 with right-hand teeth to the center M 2 of the driven helical gear 16 with left-hand teeth. The pole P lies on the center of the connecting line from M to M 2. The thin solid line 23 follows the contours of the toothing on the front trailing end face 18 of the helical toothing. The thin dash-dotted line 24 follows the contour of the toothing on the rear leading end face 17 of the helical toothing. The thick line 25 represents the contour of the helical toothing in the center of the wheel. The helical toothing is drawn for the position in which the enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 26 reaches its minimum in the wheel center.

Genau in diesem Augenblick findet der Druckumsteuervorgang statt, d.h. die Zahnlücke wird vom Druckraum D getrennt und mit dem Saugraum S verbunden. Auf diesen Druckumsteuervorgang sind die Ausnehmungen der Schrägverzahnung mit Flankenspiel abgestimmt. Dabei werden an der hinteren voreilenden Stirnseite 17 der Schrägverzahnung die geraden Stegkanten 27 und 28 der im wesentlichen rechteckigen Ausnehmungen 19 und 20 von parallel zu Mi, M2 verlaufenden Linien durch die beiden in dieser hinteren voreilenden Stirnseite 17 auf der Eingriffsebene 29 liegenden Berührungspunkte 30 und 31 gebildet. Ebenso werden an der vorderen nacheilenden Stirnseite 18 der Schrägverzahnung die geraden Stegkanten 32 und 33 der im wesentlichen rechteckigen Ausnehmungen 21 und 22 von parallel zu Mi, M2 verlaufenden Linien durch die beiden in dieser vorderen nacheilenden Stirnseite 18 auf der Eingriffsebene 29 liegenden Berührungspunkte 34 und 35 gebildet.The pressure changeover process takes place at this very moment, ie the tooth gap is separated from the pressure chamber D and connected to the suction chamber S. The recesses of the helical toothing with backlash are matched to this pressure changeover process. In this case, the straight web edges 27 and 28 of the essentially rectangular recesses 19 and 20 of parallel to M i , M 2 are left on the rear leading end face 17 of the helical toothing fenden lines formed by the two in this rear leading end face 17 lying on the engagement plane 29 contact points 30 and 31. Likewise, on the front trailing end face 18 of the helical toothing, the straight web edges 32 and 33 of the substantially rectangular recesses 21 and 22 of lines running parallel to M i , M 2 are through the two contact points 34 lying in this front trailing end face 18 on the engagement plane 29 and 35 formed.

Die Symmetrielinie 88 zu den Stegkanten 27, 28 ist in Richtung Saugraum S um eine Distanz % und die Symmetrielinie 89 zu den Stegkanten 32, 33 ist in Richtung Druckraum D um eine Distanz % zu der Verbindungslinie MiM2 versetzteThe line of symmetry 88 to the web edges 27, 28 is offset in the direction of the suction space S by a distance% and the line of symmetry 89 to the web edges 32, 33 is offset in the direction of the pressure space D by a distance% to the connecting line M i M 2

Aus Fig. 3 sind die um die Distanz V verschobenen Ausnehmungen 19, 21 und 20, 22 ersichtlich. Die Tiefe 36 der Ausnehmungen 19 bis 22 beträgt einige Millimeter und die Breite 37 der Ausnehmungen 19 bis 22 ist etwa gleich der Zahnhöhe. Die auf jeweils einer Stirnseite der Verzahnung liegenden druckraumseitigen und saugraumseitigen Ausnehmungen 19, 20 bzw. 21, 22 sind durch einen Steg mit der Breite 38 voneinander getrennt. Die Stegbreite 38 ist, verglichen mit der Stegbreite 39 der aus Fig. 5 ersichtlichen vergleichbaren Geradverzahnung mit demselben Stirnschnitt, unverändert gross.3 shows the recesses 19, 21 and 20, 22 shifted by the distance V. The depth 36 of the recesses 19 to 22 is a few millimeters and the width 37 of the recesses 19 to 22 is approximately equal to the tooth height. The recesses 19, 20 and 21, 22 on the pressure chamber side and suction chamber side, respectively, located on one end face of the toothing, are separated from one another by a web with the width 38. The web width 38 is, compared to the web width 39 of the comparable straight toothing shown in FIG. 5 with the same face cut, still large.

Um die stark unterschiedliche Grösse der Ausquetschfläche der Schrägverzahnung mit derjenigen der vergleichbaren Geradverzahnung vergleichen zu können, sind für einen Verdrehungswinkel ϕ1 die zur Verfügung stehenden Ausquetschflächen der Geradverzahnung in Fig. 5 und die zur Verfügung stehenden Ausquetschflächen der Schrägverzahnung in Fig. 6 abgebildet. Wie Fig. 5 zeigt, steht an beiden Stirnseiten der Geradverzahnung die Ausquetschfläche 40 zur Verfügung. Wie Fig. 6 zeigt, steht auf der voreilenden Stirnseite 17 die Ausquetschfläche 41 und auf der nacheilenden Stirnseite 18 die Ausquetschfläche 42 zur Verfügung. Zusätzlich steht eine Ausquetschfläche mit einem Spalt 43 zur Verfügung. Hieraus folgt eindeutig, dass die schrägverzahnte Zahnradmaschine mit der erfindungsgemässen Anordnung der Ausnehmungen 19, 20, 21, 22 eine grössere Ausquetschfläche und deshalb eine bessere Durchströmung hat als die vergleichbare geradverzahnte Zahnradmaschine.In order to be able to compare the greatly different size of the squeezing surface of the helical toothing with that of the comparable straight toothing, the squeezing surfaces available for the straight toothing for a torsion angle ϕ 1 are shown in FIG. 5 and the squeezing surfaces available for the helical toothing in FIG. 6. As shown in FIG. 5, the squeezing surface 40 is available on both end faces of the straight toothing. As FIG. 6 shows, the squeezing surface 41 is available on the leading end face 17 and the squeezing surface 42 is available on the trailing end face 18. In addition, a squeezing surface with a gap 43 is available. It clearly follows from this that the helical gear machine with the arrangement of the recesses 19, 20, 21, 22 according to the invention has a larger squeezing area and therefore a better flow than the comparable straight gear machine.

Natürlich können die Ausnehmungen 19 bis 22 an den beiden Stirnseiten 17, 18 der Schrägverzahnung auch eine etwas andere Gestalt haben. Die Ausnehmungen müssen aber immer so gestaltet sein, dass nur bei abnehmender Grösse der Fläche der eingeschlossenen Zahnlücke in Radmitte die eingeschlossene Zahnlücke über die druckraumseitigen Ausnehmungen 19, 21 mit dem Druckraum D verbunden ist und dass nur bei zunehmender Grösse der Fläche der eingeschlossenen Zahnlücke in Radmitte die eingeschlossene Zahnlücke über die saugraumseitigen Ausnehmungen 20, 22 mit dem Saugraum S verbunden ist.Of course, the recesses 19 to 22 on the two end faces 17, 18 of the helical toothing can also have a somewhat different shape. However, the recesses must always be designed in such a way that the enclosed tooth gap is connected to the pressure chamber D via the recesses 19, 21 on the pressure chamber side only with decreasing size of the area of the enclosed tooth gap in the wheel center and that only with increasing size of the area of the enclosed tooth gap in the wheel center the enclosed tooth gap is connected to the suction space S via the recesses 20, 22 on the suction space side.

Bei dem Ausführungsbeispiel nach Fig. 7 ist von den im wesentlichen rechteckigen Ausnehmungen 19, 20, 21, 22 mit geraden Stegkanten 27, 28, 32, 33 ausgegangen worden. Zusätzlich sind bei diesen Ausnehmungen an den Schnittpunkten der Stegkanten 27,28,32,33 mit der Eingriffsebene 29 Einkerbungen 44, 45, 46, 47 angebracht, die von dem Fusskreis 48, 4.9 und der fusskreisseitigen Kontur 50, 51, 52, 53 der Zahnflanke des benachbarten Zahnrades bei einem Verdrehungswinkel ϕ1 gebildet sind, bei dem die Fläche der eingeschlossenen Zahnlücke in Radmitte ihr Minimum erreicht. Durch diese erfindungsgemässen Einkerbungen 44 bis 47 vergrössert sich die zur Verfügung stehende Ausquetschfläche noch mehr.7, the essentially rectangular recesses 19, 20, 21, 22 with straight web edges 27, 28, 32, 33 were assumed. In addition, with these recesses at the intersection of the web edges 27, 28, 32, 33 with the engagement plane 29, notches 44, 45, 46, 47 are made, which are defined by the root circle 48, 4.9 and the root circle contour 50, 51, 52, 53 Tooth flank of the adjacent gearwheel is formed at an angle of rotation, 1 at which the area of the enclosed tooth gap in the wheel center reaches its minimum. These notches 44 to 47 increase the available squeezing area even more.

Auch bei einer Zahnradmaschine ohne Flankenspiel kann mittels Schrägverzahnung auf analoge Weise durch erfindungsgemässe Verschiebung der druckraumseitigen und saugraumseitigen Ausnehmungen an der voreilenden Stirnseite um eine Distanz % in Richtung Saugraum S und die erfindungsgemässe Verschiebung der druckraumseitigen und saugraumseitigen Ausnehmung an der nacheilenden Stirnseite um eine Distanz % in Richtung Druckraum D die Grösse der Ausquetschfläche beachtlich erhöht werden. Die Stegbreite 77 ist gleich der Stegbreite 54 der vergleichbaren Geradverzahnung ohne oder nahezu ohne Flankenspiel, wie aus Fig. 8 und 9 ersichtlich ist.Even in the case of a gear machine without backlash, helical gearing can be used in an analogous manner by moving the recesses on the pressure chamber and suction chamber side by a distance% in the direction of the suction chamber S and the displacement of the recess on the pressure chamber and suction chamber side by a distance% in according to the invention on the trailing end In the direction of pressure chamber D, the size of the squeezing area can be increased considerably. The web width 77 is equal to the web width 54 of the comparable straight toothing without or almost without backlash, as can be seen from FIGS. 8 and 9.

Auch hier gilt in gleicher Weise, dass zur Erreichung einer maximalen Ausquetschfläche und eines ungestörten Fördervorganges die Ausnehmungen so gestaltet sind, dass bei abnehmendem Volumen einer eingeschlossenen Zahnlücke die eingeschlossene Zahnlücke über die um eine Distanz V zueinander verschobenen druckraumseitigen Ausnehmungen 55 und 56 mit dem Druckraum D verbunden ist, und dass bei zunehmendem Volumen der eingeschlossenen Zahnlücke die eingeschlossene Zahnlücke über die um eine Distanz V zueinander verschobenen saugraumseitigen Ausnehmungen 57 und 58 mit dem Saugraum S verbunden ist.It also applies here in the same way that, in order to achieve a maximum squeezing area and an undisturbed conveying process, the recesses are designed such that, with the volume of an enclosed tooth gap decreasing, the enclosed tooth gap via the recesses 55 and 56 with the pressure chamber D displaced by a distance V from one another is connected, and that as the volume of the enclosed tooth gap increases, the included tooth gap is connected to the suction chamber S via the recesses 57 and 58 on the suction chamber side displaced by a distance V from one another.

Da bei abnehmendem Volumen einer eingeschlossenen Zahnlücke die Grösse der Fläche der eingeschlossenen Zahnlücke in Radmitte kleiner wird und bei zunehmendem Volumen dieser eingeschlossenen Zahnlücke 59 die Grösse der Fläche der eingeschlossenen Zahnlücke 59 in Radmitte grösser wird, kann auf die gleiche Weise wie für die Schrägverzahnung mit Flankenspiel bestimmt werden, für welchen Verdrehungswinkel ϕ↑ des treibenden Zahnrades 11 diese eingeschlossene Zahnlücke ihr kleinstes Volumen erreicht und wann also der Druckumsteuervorgang stattfinden muss.Since the size of the area of the enclosed tooth gap in the center of the wheel becomes smaller as the volume of an enclosed tooth gap decreases and the size of the area of the enclosed tooth gap 59 increases in the center of the wheel as the volume of this included tooth gap 59 increases, it can be done in the same way as for the helical teeth with backlash be determined for which angle of rotation ϕ ↑ of the driving gear 11 this enclosed tooth gap reaches its smallest volume and therefore when the pressure changeover process must take place.

In Fig. 9 ist für eine Schrägverzahnung mit dem gleichen Stirnschnitt wie die Schrägverzahnung gemäss Fig. 4, aber ohne oder nahezu ohne Flankenspiel angegeben, wie die erfindungsgemässen Ausnehmungen 55, 56, 57, 58 gestaltet sind. Die dünne durchgezogene Linie 60 folgt den Konturen der Schrägverzahnung an der vorderen nacheilenden Stirnseite 61 der Schrägverzahnung. Die dünne strichpunktierte Linie 62 folgt den Konturen der Schrägverzahnung an der hinteren voreilenden Stirnseite 63 der Schrägverzahnung. Die dicke Linie 64 stellt die Kontur der Schrägverzahnung in Radmitte dar.For a helical toothing with the same face cut as the helical toothing according to FIG. 4, but without or almost without backlash, FIG. 9 shows how the recesses 55, 56, 57, 58 according to the invention are designed. The thin solid line 60 follows the contours of the helical teeth on the front trailing end 61 of the helical teeth. The thin dash-dotted line 62 follows the contours of the Helical teeth on the rear leading end face 63 of the helical teeth. The thick line 64 represents the contour of the helical toothing in the center of the wheel.

Die Schrägverzahnung ist in derjenigen Position gezeichnet, in der eine eingeschlossene Zahnlükke ihr kleinstes Volumen erreicht oder in der die schraffierte Fläche der eingeschlossenen Zahnlükke 59 in Radmitte am kleinsten ist. Genau in diesem Augenblick muss der Druckumsteuervorgang stattfinden, d. h. die Zahnlücke wird vom Druckraum D getrennt und mit dem Saugraum S verbunden. Auf diesen Druckumsteuervorgang sind die Ausnehmungen 55 bis 58 der Schrägverzahnung ohne oder nahezu ohne Flankenspiel abgestimmt.The helical toothing is drawn in the position in which an enclosed tooth gap reaches its smallest volume or in which the hatched area of the enclosed tooth gap 59 is smallest in the center of the wheel. At this very moment, the pressure reversal process must take place, i. H. the tooth space is separated from the pressure chamber D and connected to the suction chamber S. The recesses 55 to 58 of the helical toothing are matched to this pressure reversing process with no or almost no backlash.

Dabei werden an der hinteren voreilenden Stirnseite 63 der Schrägverzahnung die gerade Stegkanten 65 und 66 der im wesentlichen rechteckigen Ausnehmungen 56 und 58 von parallel zu MiM2 verlaufenden Linien durch die in dieser hinteren voreilenden Stirnseite 63 auf den Eingriffsebenen 68 und 67 liegenden Berührungspunkte 69 bzw. 70 gebildet. Ebenso werden an der vorderen nacheilenden Stirnseite 61 der Schrägverzahnung die geraden Stegkanten 71 und 72 der im wesentlichen rechteckigen Ausnehmungen 55 und 57 von parallel zu MiM2 verlaufenden Linien durch die beiden in dieser vorderen nacheilenden Stirnseite 61 auf den Eingriffsebenen 63 und 67 liegenden Berührungspunkte 73 bzw. 74 gebildet. Die Symmetrielinie 90 zu den Stegkanten 65, 66 ist in Richtung Saugraum S um die Distanz

Figure imgb0001
und die Symmetrielinie 91 zu den Stegkanten 71, 72 ist in Richtung Druckraum D um die gleiche Distanz
Figure imgb0002
zu der Verbindungslinie M1M2 versetzt.In this case, the straight web edges 65 and 66 of the substantially rectangular recesses 56 and 58 of lines running parallel to M i M 2 are on the rear leading end face 63 of the helical toothing through the contact points 69 lying in this rear leading end face 63 on the engagement planes 68 and 67 or 70 formed. Likewise, on the front trailing end face 61 of the helical toothing, the straight web edges 71 and 72 of the essentially rectangular recesses 55 and 57 of lines running parallel to M i M 2 through the two contact points lying in this front trailing end face 61 on the engagement planes 63 and 67 73 and 74 formed. The line of symmetry 90 to the web edges 65, 66 is in the direction of the suction space S by the distance
Figure imgb0001
and the line of symmetry 91 to the web edges 71, 72 is in the direction of the pressure space D by the same distance
Figure imgb0002
offset to the connecting line M 1 M 2 .

Wie aus Fig. 10 ersichtlich ist, beträgt die Tiefe 75 der Ausnehmungen 55 bis 58 einige Millimeter. Die Breite 76 der Ausnehmungen 55 bis 58 ist etwa gleich der Zahnhöhe. Die auf jeweils einer Stirnseite der Schrägverzahnung liegenden druckraumseitigen und saugraumseitigen Ausnehmungen 56, 58 bzw. 55, 57 sind durch einen Steg mit der Breite 77 voneinander getrennt. Die Stegbreite 77 ist, verglichen mit der Stegbreite 54 der aus Fig. 8 ersichtlichen vergleichbaren Geradverzahnung ohne oder nahezu ohne Flankenspiel mit demselben Stirnschnitt, unverändert geblieben.As can be seen from FIG. 10, the depth 75 of the recesses 55 to 58 is a few millimeters. The width 76 of the recesses 55 to 58 is approximately equal to the tooth height. The recesses 56, 58 and 55, 57 on the pressure chamber side and suction chamber side, respectively, located on one end face of the helical toothing, are separated from one another by a web with the width 77. The web width 77 has remained unchanged compared to the web width 54 of the comparable straight toothing shown in FIG. 8 without or almost without backlash with the same face cut.

Natürlich können die Ausnehmungen 55 bis 58 an den beiden Stirnseiten 61, 63 der Schrägverzahnung auch eine etwas andere Gestalt haben: Die Ausnehmungen müssen aber immer so gestaltet sein, dass bei abnehmbarer Grösse der Fläche einer eingeschlossenen Zahnlücke in Radmitte die eingeschlossene Zahnlücke über die druckraumseitigen Ausnehmungen 55, 56 mit dem Druckraum D verbunden ist und dass bei zunehmender Grösse einer Fläche der eingeschlossenen Zahnlücke in Radmitte die eingeschlossene Zahnlücke über die saugraumseitigen Ausnehmungen 57, 58 mit dem Saugraum S verbunden ist.Of course, the recesses 55 to 58 on the two end faces 61, 63 of the helical toothing can also have a slightly different shape: the recesses must always be designed such that, with the size of the area of an enclosed tooth gap in the center of the wheel being removable, the enclosed tooth gap is above the pressure chamber-side recesses 55, 56 is connected to the pressure chamber D and that with increasing size of an area of the enclosed tooth gap in the center of the wheel, the enclosed tooth gap is connected to the suction chamber S via the recesses 57, 58 on the suction chamber side.

Bei dem Ausführungsbeispiel nach den Figuren 11 und 12 ist von den im wesentlichen rechteckigen Ausnehmungen 55, 56, 57, 58 mit geraden Stegkanten 71, 65, 72, 66 ausgegangen worden. Zusätzlich sind bei diesen Ausnehmungen an den Schnittpunkten der Stegkanten 71, 65, 72, 66 mit den Eingriffsebenen 67 und 68 Einkerbungen 78, 79, 80, 81, 82, 83, 84, 85 angebracht, die von den Fusskreisen 86, 87 und den fusskreisseitigen Konturen der Zahnflanke des benachbarten Zahnrades bei einem Verdrehungswinkel ϕ1 gebildet sind, bei dem die Fläche einer eingeschlossenen Ml- oder M2-seitigen Zahnlücke in Radmitte ihr Minimum erreicht. Durch diese erfindungsgemässen Einkerbungen 78 bis 85 vergrössert sich die zur Verfügung stehende Ausquetschfläche noch mehr. In Fig. 11 und 12 ist nur für den Verdrehungswinkel cp, bei dem die Fläche der eingeschlossenen Mz-seitigen Zahnlücke in Radmitte ihr Minimum erreicht, die Konstruktion der Einkerbungen 79, 81, 82, 84 abgebildet.In the exemplary embodiment according to FIGS. 11 and 12, the essentially rectangular recesses 55, 56, 57, 58 with straight web edges 71, 65, 72, 66 have been assumed. In addition, with these recesses at the intersection of the web edges 71, 65, 72, 66 with the engagement planes 67 and 68, notches 78, 79, 80, 81, 82, 83, 84, 85 are made, which are from the root circles 86, 87 and contours of the tooth flank of the adjacent gearwheel on the root circle are formed at an angle of rotation ϕ 1 at which the area of an enclosed M 1 or M 2 side tooth gap in the wheel center reaches its minimum. These notches 78 to 85 increase the available squeezing area even more. 11 and 12, the construction of the notches 79, 81, 82, 84 is shown only for the angle of rotation cp, at which the area of the enclosed tooth space on the M z side reaches its minimum in the center of the wheel.

Figure imgb0003
Figure imgb0003
Figure imgb0004
Figure imgb0004

Claims (5)

1. A gear pump or gear motor comprising a pair of intermeshing driving and driven helical gears (11, 16), a housing surrounding said gears and providing pressure ports and suction ports leading to said gears, pressure port connected and suction port connected relief grooves (19, 20, 21, 22 or 55, 56, 57, 58), formed in the meshing area in the housing and/or the stationary parts, positioned in the pump, said relief grooves facing the lateral faces of the helical gears; said pressure port connected and suction port connected relief grooves (19, 20 or 56, 58) at the leading lateral face (17 resp. 63) of the helical gears having been shifted, out of the symmetrical position with respect to the plane through the two rotation axes, over a distance v/2 in the direction of the suction port, said pressure port connected and suction port connected relief grooves (21, 22 or 55, 57) at the lagging lateral face (18 resp. 61) of the helical gears having been shifted, out of the symmetrical position with respect to the plane through the two rotation axes, over a distance % in the direction of the pressure port, said distance % having been given that value, that an enclosed toothcavity (26, 59) is connected via the pressure port connected relief grooves (19, 21 or 55, 56) with the pressure port, only with decreasing size of the area of the enclosed tooth cavity, considered in the transversal plane through the middle of the gears and that an enclosed tooth cavity is connected via the suction port connected relief grooves (20, 22 or 57, 58) with the suction port, only with increasing size of the area of the enclosed tooth cavity, considered in the transversal plane through the middle of the gears.
2. In a gear pump or gear motor as in claim 1 comprising a pair of helical gears, meshing with tooth clearance; straight land edges (27, 28) of somewhat rectangular relief grooves (19, 20) at the leading lateral face (17) of the helical gears go through the contact points, positioned on the pressureline at said leading lateral face, said land edges running parallel with the line of centers and straight land edges (32, 33) of somewhat rectangular relief grooves (21, 22) at the lagging lateral face of the helical gears go through the contactpoints, positioned on the pressureline at said lagging lateral face, said land edges running parallel with the line of centers, said helical gears being considered for a rotation angle, for which the size of the area of the enclosed tooth cavity, considered in the transversal plane through the middle of the gears, reaches its minimum.
3. A gear pump or gear motor as in claim 1 or 2 wherein in the land somewhat triangular notches (44, 45, 46, 47) have been formed which, starting from the intersection point of a land edge with the pressureline, follow the contours of the toothflank along the foot in the direction of the most adjacent rootcircle and of said rootcircle, said helical gears being considered for a rotation angle, for which the size of the area of the enclosed tooth cavity (26), considered in the transversal plane through the middle of the gears, reaches its minimum.
4. In a gear pump or gear motor as in claim 1 comprising a pair of helical gears, meshing with no or nearly no tooth clearance; straight land edges (65, 66) of somewhat rectangular relief grooves (56, 58) at the leading lateral face (61) of the helical gears go through the contactpoints (69, 70), positioned on the pressurelines at said leading lateral face, said land edges running parallel with the line of centers and straight land edges (71, 72) of somewhat rectangular relief grooves (55, 57) at the lagging lateral face (61) of the helical gears go through the contactpoints (73, 74), positioned on the pressurelines at said lagging lateral face, said land edges running parallel with the line of centers, said helical gears being considered for a rotation angle for which the size of the area of an enclosed tooth cavity at the side of the driving or of the driven gear, considered in the transversal plane through the middle of the gears, reaches its minimum.
5. A gear pump or gear motor as in claim 1 or 4 wherein in the land somewhat triangular notches (78, 79, 80, 81, 82, 83, 84, 85) have been formed which, starting from an intersectionpoint of a land edge with a pressureline, follow the contours of the toothflank along the foot in the direction of the most adjacent rootcircle and of said rootcircle, said helical gears being considered for a rotation angle for which the size of the area of an enclosed tooth cavity at the side of the driving or the driven gear, considered in the transversal plane through the middle of the gears, reaches its minimum.
EP79200119A 1978-03-10 1979-03-09 Gear-type machine with relief means for the liquid in the interengagement space between the teeth Expired EP0004120B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2810563 1978-03-07
DE2810563A DE2810563C2 (en) 1978-03-10 1978-03-10 Gear machine (pump or motor)

Publications (3)

Publication Number Publication Date
EP0004120A2 EP0004120A2 (en) 1979-09-19
EP0004120A3 EP0004120A3 (en) 1979-10-03
EP0004120B1 true EP0004120B1 (en) 1983-04-06

Family

ID=6034123

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79200119A Expired EP0004120B1 (en) 1978-03-10 1979-03-09 Gear-type machine with relief means for the liquid in the interengagement space between the teeth

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US (1) US4290739A (en)
EP (1) EP0004120B1 (en)
DE (1) DE2810563C2 (en)

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Also Published As

Publication number Publication date
DE2810563C2 (en) 1982-10-28
EP0004120A3 (en) 1979-10-03
EP0004120A2 (en) 1979-09-19
US4290739A (en) 1981-09-22
DE2810563A1 (en) 1979-09-13

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