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WO2008077812A1 - Hydraulic gearing - Google Patents

Hydraulic gearing Download PDF

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Publication number
WO2008077812A1
WO2008077812A1 PCT/EP2007/063888 EP2007063888W WO2008077812A1 WO 2008077812 A1 WO2008077812 A1 WO 2008077812A1 EP 2007063888 W EP2007063888 W EP 2007063888W WO 2008077812 A1 WO2008077812 A1 WO 2008077812A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
wing
radial recess
recess
radial
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.)
Ceased
Application number
PCT/EP2007/063888
Other languages
German (de)
French (fr)
Inventor
Josef Stollberger
Franz Stuhlbacher
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2008077812A1 publication Critical patent/WO2008077812A1/en
Anticipated expiration legal-status Critical
Ceased 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/30—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F03C2/302—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movements defined in sub-groups F03C2/02 and relative reciprocation between members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/30—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F03C2/308—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in F03C2/08 and having a hinged member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F04C2/336—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/26—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type with liquid chambers not shaped as bodies of revolution or shaped as bodies of revolution eccentric to the main axis of the gearing
    • F16H39/28—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type with liquid chambers not shaped as bodies of revolution or shaped as bodies of revolution eccentric to the main axis of the gearing with liquid chambers formed in rotary members

Definitions

  • the invention relates to a hydraulic transmission with harmonious transition of the pressure medium between two trained as a cell rotor displacement machines with a radially displaceable first wing having first impeller and a radially displaceable and pivotable second wing having second impeller, wherein the first impeller is disposed within the second impeller and the first wing of the first impeller along a cylindrical tread of the surrounding second impeller are guided and the second impeller and the guide body are rotatably connected to each other, each second wing at one end both radially displaceable, and pivotable in a radial recess of the second impeller and at the other End is immovably, but pivotally mounted in a recess of the guide body, and wherein per radial recess of the second impeller at least one overflow channel is provided, which at least in one position d the second wing produces a flow connection between the second working space and a compensation space delimited by the second displacement body, the side flanks and the bottom of the radial recess.
  • the strip-shaped second wings are rotatably and radially displaceably mounted in the second impeller.
  • at least one flow connection is provided, which at least in a position of the second wing penetration of the pressure medium in the plane defined by the flanks of the recess and the second wing compensation space, or an outflow of the pressure medium from this compensation space allowed.
  • the flow connection is formed by overflow in the thickening of the wing.
  • the object of the invention is to avoid these disadvantages and to reduce the mechanical and hydraulic load and increase the service life in a transmission of the type mentioned. According to the invention this is achieved in that the overflow channel is formed by at least one lateral pocket in the radial recess, wherein the pocket is swept in at least one position of the second impeller from the second wing, wherein preferably the flow through the lateral pocket by the stroke of the second Wing is controlled.
  • At least one first working space is formed between the two running wheels and at least one second working space is formed between the second running wheel and a guide body surrounding it.
  • first and one second lateral pocket are provided per recess, wherein the first and the second pockets are arranged on opposite flanks of the recesses, and wherein preferably the first and second pockets are arranged radially offset from one another.
  • the first and second pockets have an area which has the same radial distance from the axis of the second impeller, in a middle stroke position of the second wing, a flow connection between two working spaces adjacent to the wing above the compensation space is created.
  • Each second wing acts together with the pockets of the recess as a stroke-controlled valve which on the one hand causes a pressure relief of the compensation chamber and on the other hand creates a pressure equalization between the compensation chamber and the adjacent second working spaces on both sides of the respective second wing in a central position of the wing.
  • the second wing has a substantially club-like cross section with first and second thickenings at its ends, wherein the second thickening is guided in the radial recess.
  • the second thickening has concavely curved side edges.
  • FIG. 5 shows the second impeller in a section along the line V - V in Fig. 3.
  • FIG. 6 shows a detail of the second impeller in a view according to the arrows VI - VI in Fig. 3;
  • Fig. 8 shows an inventive hydraulic transmission in another embodiment in a cross section.
  • the hydraulic transmission 1 has a housing 2, in which a first impeller 3 and a second impeller 4 are arranged. Both wheels 3, 4 are designed as displacement machines forming vane cell rotor.
  • the first impeller 3 has radial first recesses 5, in which the first vanes 6 are arranged radially displaceable.
  • Analog also has the second impeller 4 second radial recesses 7, in which second wings 8 are arranged displaceably.
  • first working space 10 functioning as a displacement and swallowing space is formed.
  • the first wings 6 run along the first running surface 9 formed by a cylindrical or slightly conical inner circumferential surface of the second running wheel 4.
  • the second impeller 4 is fixedly connected to end elements 51, 52, which seal the working spaces 10, 13 on the front side.
  • the second impeller 4 evenly distributed around the circumference radial connecting channels 15, 15a, wherein in the embodiment shown in Fig. 1 between two adjacent second radial recesses 7, a connecting channel 15, 15a is arranged.
  • the distance between the sealing edges 6a of two adjacent first wings 6 is smaller than the distance between two connecting channels 15, 15a.
  • the second wings 8 are pivotally arranged in second recesses 7 of the second impeller 4 and in third recesses 44 of the guide body 11.
  • the second wing 8 has a substantially club-like cross section with thickenings 8a, 8b at both ends.
  • the first thickening 8a is arranged pivotably but immovably in the third recess 44 of the guide body 11.
  • the second wings 8 are laterally inserted into the groove-shaped third recess 44 and are positively connected to the guide body 11.
  • the second thickenings 8b of the wings 8 are arranged in second radial recesses 7 of the second impeller 4 and have concavely curved side edges 8c, the second wings 8 in the second recesses 7 being both radially displaceable and pivotable.
  • the second wings 8 in their recesses perform a piston movement. It is important that the hydraulic oil, which at the bottom of the wings 8 from the expansion chamber 82nd displaced or sucked into this, can flow freely.
  • each recess 7 has formed overflow channels formed by pockets 80, 81, so that the pressure medium can flow in certain positions of the wings 8 into or out of the second recesses 7.
  • a pressure equalization between the formed by the side flanks 7 a, 7 b, the bottom 7 c of the recess 7 and the bottom 8 d of the second wing 8 compensating space 82 and the second working space 13 can be through the first pocket 80 in a lower first stroke position of the second wing and through reach the second pocket 81 in an upper second stroke position of the second wing 8.
  • the pockets 80, 81 are arranged so that each second wing 8 is pressed in the upper second position of the lifting movement by the hydraulic pressure against the sealing surface 85 and thus seals the working area. In the lower first stroke position, the second wing 8 is pressed against the sealing surfaces 86 and is also tight in the work area.
  • Fig. 1 and Fig. 8 are second wing 8 in the lower first stroke position with A, second wing 8 in the upper second stroke position with B and second wing 8, which are in an intermediate position, denoted by C.
  • the first and second pockets 80, 81 are arranged on opposite side flanks 7a, 7b of the radial recess 7 at different radial distance from the axis 4a of the second impeller 4.
  • the pockets 80, 81 on an overlap region 83 at the same radial distance from the axis 4a of the second impeller 4.
  • the overlapping area 83 creates a flow connection between the second working spaces 13a, 13b on both sides of the wing 8 in the intermediate position C of the second wing 8, as shown in FIGS. 1 and 8.
  • the pockets 80, 81 do not extend over the full width b of the second impeller 4, but are spaced from its end faces.
  • the formed guide surfaces 84 ensure that the second wings 8 are always guided correctly in the recesses 7.
  • the pockets 80, 81 perform a valve function together with the second wings 8.
  • This makes it possible to supply the hydraulic oil directly to the equalizing space 82 as provided in the embodiment shown in FIG. 8.
  • the connecting channels 15a open between the first working space 10 and the second working space 13 directly into the compensation chambers 82 of the recesses 7 a.
  • This embodiment can be used especially with second wheels 4 with a small diameter in order to avoid spatial constraints in the production of the connecting channels 15.
  • Another advantage is that the hydraulic oil which, when driving, for example, the first impeller 3, between the first and second working space 10th and 13 is conveyed, flows directly and without detours through the expansion chamber 82, whereby flow losses can be avoided.
  • the acting as a pump first impeller 3 and acting as a machine second impeller 4 form a substantially closed hydraulic circuit between the working space 10 and 13th

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Wind Motors (AREA)
  • Hydraulic Motors (AREA)

Abstract

The invention relates to a hydraulic gearing (1) with a harmonious transition of the pressure medium between two positive-displacement machines designed as cell rotors, with a first impeller (3) which has radially displaceable first vanes (6) and a second impeller (4) which has radially displaceable and pivotable second vanes (8), wherein the first impeller (3) is arranged within the second impeller (4), and the first vanes (6) of the first impeller (3) are guided along a cylindrical running surface (9) of the surrounding second impeller (4). Every second vane (6) is arranged at one end both in a radially displaceable and also pivotable manner in a radial recess (7) of the second impeller (4). In order to equalize the pressure, at least one flow passage is formed between an equalizing space (82), which is bounded by the second vane (8) and the side flanks (7a, 7b) and the base (7c) of the radial recess (7), and the working space (13) of the second impeller (4). In order to reduce the loading on the gearing (1) and to extend the service life, it is provided that the overflow passage is formed by at least one lateral pocket (80, 81) in the radial recess (7), wherein the pocket (80, 81) is brushed over by the second vane (8) in at least one position of the second impeller (4).

Description

Hydraulisches Getriebe Hydraulic transmission

Die Erfindung betrifft ein hydraulisches Getriebe mit harmonischem Übergang des Druckmediums zwischen zwei als Zellenläufer ausgebildeten Verdrängungsmaschinen mit einem radial verschiebbare erste Flügel aufweisenden ersten Laufrad und einem radial verschiebbare und schwenkbare zweite Flügel aufweisenden zweiten Laufrad, wobei das erste Laufrad innerhalb des zweiten Laufrades angeordnet ist und die ersten Flügel des ersten Laufrades entlang einer zylindrischen Lauffläche des umgebenden zweiten Laufrades geführt sind und das zweite Laufrad und der Führungskörper miteinander drehverbunden sind, wobei jeder zweite Flügel an einem Ende sowohl radial verschiebbar, als auch schwenkbar in einer radialen Ausnehmung des zweiten Laufrades und am anderen Ende unverschiebbar, aber schwenkbar in einer Ausnehmung des Führungskörpers angeordnet ist, und wobei pro radialer Ausnehmung des zweiten Laufrades zumindest ein Überströmkanal vorgesehen ist, welcher zumindest in einer Stellung des zweiten Flügels eine Strömungsverbindung zwischen dem zweiten Arbeitsraum und einem durch den zweiten Verdrängungskörper, den Seitenflanken und dem Boden der radialen Ausnehmung begrenzten Ausgleichsraum herstellt.The invention relates to a hydraulic transmission with harmonious transition of the pressure medium between two trained as a cell rotor displacement machines with a radially displaceable first wing having first impeller and a radially displaceable and pivotable second wing having second impeller, wherein the first impeller is disposed within the second impeller and the first wing of the first impeller along a cylindrical tread of the surrounding second impeller are guided and the second impeller and the guide body are rotatably connected to each other, each second wing at one end both radially displaceable, and pivotable in a radial recess of the second impeller and at the other End is immovably, but pivotally mounted in a recess of the guide body, and wherein per radial recess of the second impeller at least one overflow channel is provided, which at least in one position d the second wing produces a flow connection between the second working space and a compensation space delimited by the second displacement body, the side flanks and the bottom of the radial recess.

Aus der AT 502.908 Al, deren Inhalt durch Referenz in die vorliegende Anmeldung aufgenommen wird, ist ein hydraulisches Getriebe der eingangs genannten Art bekannt. Die leistenförmig ausgebildeten zweiten Flügel sind drehbar und radial verschiebbar im zweiten Laufrad gelagert. Dabei ist zwischen dem zweiten Flügel und der Ausnehmung jeweils zumindest eine Strömungsverbindung vorgesehen, welche zumindest in einer Position des zweiten Flügels ein Eindringen des Druckmediums in den durch die Flanken der Ausnehmung und den zweiten Flügel aufgespannten Ausgleichsraum, bzw. ein Ausströmen des Druckmediums aus diesem Ausgleichsraum erlaubt. Die Strömungsverbindung wird dabei durch Überströmkanäle in der Verdickung des Flügels gebildet. Diese Ausbildung hat allerdings den Nachteil, dass der Durchfluss durch den Überströmkanal vom Schwenkwinkel des zweiten Flügels abhängig ist, was bewirkt, dass in bestimmten Stellungen des zweiten Flügels der Durchfluss durch die Strömungskanäle zu gering ist. Dies führt zu hohen Belastungen des Getriebes und wirkt sich nachteilig auf die Standzeit der Bauteile des Getriebes aus.From AT 502.908 Al, whose content is incorporated by reference in the present application, a hydraulic transmission of the type mentioned is known. The strip-shaped second wings are rotatably and radially displaceably mounted in the second impeller. In this case, between the second wing and the recess in each case at least one flow connection is provided, which at least in a position of the second wing penetration of the pressure medium in the plane defined by the flanks of the recess and the second wing compensation space, or an outflow of the pressure medium from this compensation space allowed. The flow connection is formed by overflow in the thickening of the wing. However, this design has the disadvantage that the flow through the overflow is dependent on the pivot angle of the second wing, which causes the flow through the flow channels is too low in certain positions of the second wing. This leads to high loads of the transmission and has a detrimental effect on the service life of the components of the transmission.

Aufgabe der Erfindung ist es, diese Nachteile zu vermeiden und bei einem Getriebe der eingangs genannten Art die mechanische und hydraulische Belastung zu verringern und die Standzeiten zu erhöhen. Erfindungsgemäß wird dies dadurch erreicht, dass der Überstromkanal durch zumindest eine seitliche Tasche in der radialen Ausnehmung gebildet ist, wobei die Tasche in zumindest einer Stellung des zweiten Laufrades vom zweiten Flügel überstrichen wird, wobei vorzugsweise die Strömung durch die seitliche Tasche durch den Hub des zweiten Flügels gesteuert ist.The object of the invention is to avoid these disadvantages and to reduce the mechanical and hydraulic load and increase the service life in a transmission of the type mentioned. According to the invention this is achieved in that the overflow channel is formed by at least one lateral pocket in the radial recess, wherein the pocket is swept in at least one position of the second impeller from the second wing, wherein preferably the flow through the lateral pocket by the stroke of the second Wing is controlled.

Durch die hubgesteuerten Strömungskanäle kann unabhängig von der Winkelstellung des zweiten Flügels ein ausreichender Druckausgleich zwischen dem Ausgleichsraum und dem Arbeitsraum gewährleistet werden. Die mechanische Belastung des zweiten Laufrades lässt sich somit wesentlich reduzieren.By the stroke-controlled flow channels, a sufficient pressure equalization between the compensation chamber and the working space can be ensured regardless of the angular position of the second wing. The mechanical load of the second impeller can thus be significantly reduced.

Zwischen den beiden Laufrädern ist zumindest ein erster Arbeitsraum und zwischen dem zweiten Laufrad und einem diesen umgebenden Führungskörper zumindest ein zweiter Arbeitsraum ausgebildet.At least one first working space is formed between the two running wheels and at least one second working space is formed between the second running wheel and a guide body surrounding it.

Besonders vorteilhaft ist es, wenn pro Ausnehmung zumindest eine erste und eine zweite seitliche Tasche vorgesehen ist, wobei die erste und die zweite Taschen an gegenüberliegenden Flanken der Ausnehmungen angeordnet sind, und wobei vorzugsweise die ersten und zweiten Taschen radial versetzt zueinander angeordnet sind. Dadurch, dass erste und zweite Taschen einen Bereich aufweisen, welcher den gleichen radialen Abstand von der Achse des zweiten Laufrades hat, wird in einer mittleren Hubstellung des zweiten Flügels eine Strömungsverbindung zwischen zwei dem Flügel benachbarten Arbeitsräumen über dem Ausgleichsraum geschaffen. Jeder zweite Flügel wirkt zusammen mit den Taschen der Ausnehmung als hubgesteuertes Ventil, welches einerseits eine Druckentlastung des Ausgleichsraumes bewirkt und andererseits in einer mittleren Stellung des Flügels einen Druckausgleich zwischen dem Ausgleichsraum und den benachbarten zweiten Arbeitsräumen beidseits des jeweiligen zweiten Flügels schafft.It is particularly advantageous if at least one first and one second lateral pocket are provided per recess, wherein the first and the second pockets are arranged on opposite flanks of the recesses, and wherein preferably the first and second pockets are arranged radially offset from one another. Characterized in that the first and second pockets have an area which has the same radial distance from the axis of the second impeller, in a middle stroke position of the second wing, a flow connection between two working spaces adjacent to the wing above the compensation space is created. Each second wing acts together with the pockets of the recess as a stroke-controlled valve which on the one hand causes a pressure relief of the compensation chamber and on the other hand creates a pressure equalization between the compensation chamber and the adjacent second working spaces on both sides of the respective second wing in a central position of the wing.

Der zweite Flügel weist einen im Wesentlichen keulenartigen Querschnitt mit ersten und zweiten Verdickungen an seinen Enden auf, wobei die zweite Verdickung in der radialen Ausnehmung geführt ist. Um eine sichere Linienabdichtung in der Ausnehmung unabhängig von Schwenkbewegungen zu erreichen ist es vorteilhaft, wenn die zweite Verdickung konkav gekrümmte Seitenflanken aufweist.The second wing has a substantially club-like cross section with first and second thickenings at its ends, wherein the second thickening is guided in the radial recess. In order to achieve a secure line seal in the recess independently of pivoting movements, it is advantageous if the second thickening has concavely curved side edges.

Die axiale Erstreckung der Strömungskanäle ist vorzugsweise geringer als die in axialer Richtung des zweiten Laufrades gemessene Breite des zweiten Laufrades. Die Strömungskanäle sind dabei von den Stirnseiten des zweiten Laufrades beabstandet. Dadurch wird eine genaue Führung der zweiten Flügel in jeder Hubposition gewährleistet. Das zweite Laufrad weist zumindest einen radialen Verbindungskanal zur Strömungsverbindung der ersten und der zweiten Arbeitsräume auf. Die Verbindungskanäle können beispielsweise durch Durchgangsbohrungen im zweiten Laufrad zwischen jeweils zwei radialen Ausnehmungen gebildet sein.The axial extension of the flow channels is preferably less than the measured in the axial direction of the second impeller width of the second impeller. The flow channels are spaced from the end faces of the second impeller. This ensures accurate guidance of the second wings in each stroke position. The second impeller has at least one radial connecting channel for the flow connection of the first and the second working spaces. The connecting channels can be formed for example by through holes in the second impeller between two radial recesses.

In einer besonders bevorzugten Ausführung der Erfindung ist vorgesehen, dass zumindest ein radialer Verbindungskanal - ausgehend vom ersten Arbeitsraum - direkt in die Ausnehmung, vorzugsweise im Bereich des Bodens der Ausnehmung, einmündet. Dadurch können radiale Durchgangsbohrungen im Laufrad zwischen jeweils zwei Ausnehmungen vermieden werden, was insbesondere bei Laufrädern mit relativ kleinem Durchmesser mit hohem Herstellungsaufwand und entsprechenden Platzproblemen bei der Anordnung der Verbindungskanäle verbunden wäre. Das Hydraulikmedium gelangt somit auf direktem Weg vom ersten Arbeitsraum in den Ausgleichsraum der Ausnehmung, wodurch hydraulische Verluste verringert werden können.In a particularly preferred embodiment of the invention, it is provided that at least one radial connecting channel-starting from the first working space-opens directly into the recess, preferably in the region of the bottom of the recess. As a result, radial through holes in the impeller between each two recesses can be avoided, which would be particularly associated with wheels with a relatively small diameter with high production costs and corresponding space problems in the arrangement of the connecting channels. The hydraulic medium thus passes directly from the first working space into the compensation space of the recess, whereby hydraulic losses can be reduced.

Die Erfindung wird im Folgenden anhand der Figuren näher erläutert. Es zeigen :The invention will be explained in more detail below with reference to FIGS. Show it :

Fig. 1 ein erfindungsgemäßes hydraulisches Getriebe in einem Querschnitt;1 shows an inventive hydraulic transmission in a cross section.

Fig. 2 einen zweiten Flügel in einer Seitenansicht;2 shows a second wing in a side view;

Fig. 3 ein zweites Laufrad in einer Seitenansicht;3 shows a second impeller in a side view;

Fig. 4 das zweite Laufrad in einem Schnitt gemäß der Linie IV - IV in Fig. 3;4 shows the second impeller in a section along the line IV - IV in Fig. 3.

Fig. 5 das zweite Laufrad in einem Schnitt gemäß der Linie V - V in Fig. 3;5 shows the second impeller in a section along the line V - V in Fig. 3.

Fig. 6 ein Detail des zweiten Laufrades in einer Ansicht gemäß den Pfeilen VI - VI in Fig. 3;6 shows a detail of the second impeller in a view according to the arrows VI - VI in Fig. 3;

Fig. 7 das Detail VII des zweiten Laufrades aus Fig. 3; undFig. 7 shows the detail VII of the second impeller of Fig. 3; and

Fig. 8 ein erfindungsgemäßes hydraulisches Getriebe in einer anderen Ausführungsvariante in einem Querschnitt.Fig. 8 shows an inventive hydraulic transmission in another embodiment in a cross section.

Das hydraulische Getriebe 1 weist ein Gehäuse 2 auf, in welchem ein erstes Laufrad 3 und ein zweites Laufrad 4 angeordnet sind. Beide Laufräder 3, 4 sind als Verdrängungsmaschinen bildende Flügelzellenläufer ausgebildet. Das erste Laufrad 3 weist radiale erste Ausnehmungen 5 auf, in welchen die ersten Flügel 6 radial verschiebbar angeordnet sind. Analog weist auch das zweite Laufrad 4 zweite radiale Ausnehmungen 7 auf, in welchen zweite Flügel 8 verschiebbar angeordnet sind.The hydraulic transmission 1 has a housing 2, in which a first impeller 3 and a second impeller 4 are arranged. Both wheels 3, 4 are designed as displacement machines forming vane cell rotor. The first impeller 3 has radial first recesses 5, in which the first vanes 6 are arranged radially displaceable. Analog also has the second impeller 4 second radial recesses 7, in which second wings 8 are arranged displaceably.

Zwischen dem ersten Laufrad 3 und einer inneren Mantelfläche des zweiten Laufrades 4 ist ein, als Verdrängungs- und Schluckraum fungierender, erster Arbeitsraum 10 ausgebildet. Die ersten Flügel 6 laufen entlang der durch eine zylindrische oder leicht konische innere Mantelfläche des zweiten Laufrades 4 gebildeten ersten Lauffläche 9.Between the first impeller 3 and an inner circumferential surface of the second impeller 4, a first working space 10 functioning as a displacement and swallowing space is formed. The first wings 6 run along the first running surface 9 formed by a cylindrical or slightly conical inner circumferential surface of the second running wheel 4.

Zwischen dem zweiten Laufrad 4 und einem drehbar gelagerten Führungskörper 11 ist ein als Schluck- und Verdrängungsraum fungierender zweiter Arbeitsraum 13 ausgebildet. Mit IIa ist ein drehfester Tragring bezeichnet.Between the second impeller 4 and a rotatably mounted guide body 11 acting as a swallowing and displacement space second working space 13 is formed. IIa is a non-rotating support ring.

Das zweite Laufrad 4 ist fest mit Abschlusselementen 51, 52 verbunden, welche die Arbeitsräume 10, 13 stirnseitig abdichten.The second impeller 4 is fixedly connected to end elements 51, 52, which seal the working spaces 10, 13 on the front side.

Zur Strömungsverbindung zwischen dem ersten Arbeitsraum 10 und dem zweiten Arbeitsraum 13 weist das zweite Laufrad 4 gleichmäßig um den Umfang verteilte radiale Verbindungskanäle 15, 15a auf, wobei im in Fig. 1 dargestellten Ausführungsbeispiel jeweils zwischen zwei benachbarten zweiten radialen Ausnehmungen 7 ein Verbindungskanal 15, 15a angeordnet ist. Der Abstand der Dichtkanten 6a zweier benachbarter erster Flügel 6 ist dabei kleiner als der Abstand zweier Verbindungskanäle 15, 15a.For the flow connection between the first working chamber 10 and the second working chamber 13, the second impeller 4 evenly distributed around the circumference radial connecting channels 15, 15a, wherein in the embodiment shown in Fig. 1 between two adjacent second radial recesses 7, a connecting channel 15, 15a is arranged. The distance between the sealing edges 6a of two adjacent first wings 6 is smaller than the distance between two connecting channels 15, 15a.

Die zweiten Flügel 8 sind schwenkbar in zweiten Ausnehmungen 7 des zweiten Laufrades 4 und in dritten Ausnehmungen 44 des Führungskörpers 11 angeordnet.The second wings 8 are pivotally arranged in second recesses 7 of the second impeller 4 and in third recesses 44 of the guide body 11.

Der zweite Flügel 8 weist einen im Wesentlichen keulenartigen Querschnitt mit Verdickungen 8a, 8b an beiden Enden auf. Die erste Verdickung 8a ist dabei schwenkbar, aber unverschiebbar in der dritten Ausnehmung 44 des Führungskörpers 11 angeordnet. Die zweiten Flügel 8 werden seitlich in die nutförmige dritte Ausnehmung 44 eingeschoben und sind formschlüssig mit dem Führungskörper 11 verbunden.The second wing 8 has a substantially club-like cross section with thickenings 8a, 8b at both ends. The first thickening 8a is arranged pivotably but immovably in the third recess 44 of the guide body 11. The second wings 8 are laterally inserted into the groove-shaped third recess 44 and are positively connected to the guide body 11.

Die zweiten Verdickungen 8b der Flügel 8 sind in zweiten radialen Ausnehmungen 7 des zweiten Laufrades 4 angeordnet und weisen konkav gekrümmte Seitenflanken 8c auf, wobei die zweiten Flügel 8 in den zweiten Ausnehmungen 7 sowohl radial verschiebbar, als auch schwenkbar sind. Bei einer Umdrehung des zweiten Laufrades 4 samt Führungskörper 11 führen die zweiten Flügel 8 in ihren Ausnehmungen eine Kolbenbewegung durch. Dabei ist es wichtig, dass das Hydrauliköl, welches an der Unterseite der Flügel 8 aus dem Ausgleichsraum 82 verdrängt oder in diesen angesaugt wird, frei fließen kann. Zu diesem Zweck weist jede Ausnehmung 7 eingeformte, durch Taschen 80, 81 gebildete Überströmkanäle auf, so dass das Druckmedium in bestimmten Stellungen der Flügel 8 in die oder aus den zweiten Ausnehmungen 7 strömen kann. Ein Druckausgleich zwischen dem durch die Seitenflanken 7a, 7b, den Boden 7c der Ausnehmung 7 und die Unterseite 8d des zweiten Flügels 8 gebildeten Ausgleichsraum 82 und dem zweiten Arbeitsraum 13 lässt sich durch die erste Tasche 80 in einer unteren ersten Hubstellung des zweiten Flügels und durch die zweite Tasche 81 in einer oberen zweiten Hubstellung des zweiten Flügels 8 erreichen. Die Taschen 80, 81 sind so angeordnet, dass jeder zweite Flügel 8 in der oberen zweiten Stellung der Hubbewegung durch den hydraulischen Druck gegen die Dichtfläche 85 gedrückt wird und somit den Arbeitsbereich abdichtet. In der unteren ersten Hubstellung wird der zweite Flügel 8 gegen die Dichtflächen 86 gedrückt und ist ebenfalls im Arbeitsbereich dicht. In Fig. 1 und Fig. 8 sind zweite Flügel 8 in der unteren ersten Hubstellung mit A, zweite Flügel 8 in der oberen zweiten Hubstellung mit B und zweite Flügel 8, welche sich in einer Zwischenstellung befinden, mit C bezeichnet.The second thickenings 8b of the wings 8 are arranged in second radial recesses 7 of the second impeller 4 and have concavely curved side edges 8c, the second wings 8 in the second recesses 7 being both radially displaceable and pivotable. In one revolution of the second impeller 4 together with the guide body 11, the second wings 8 in their recesses perform a piston movement. It is important that the hydraulic oil, which at the bottom of the wings 8 from the expansion chamber 82nd displaced or sucked into this, can flow freely. For this purpose, each recess 7 has formed overflow channels formed by pockets 80, 81, so that the pressure medium can flow in certain positions of the wings 8 into or out of the second recesses 7. A pressure equalization between the formed by the side flanks 7 a, 7 b, the bottom 7 c of the recess 7 and the bottom 8 d of the second wing 8 compensating space 82 and the second working space 13 can be through the first pocket 80 in a lower first stroke position of the second wing and through reach the second pocket 81 in an upper second stroke position of the second wing 8. The pockets 80, 81 are arranged so that each second wing 8 is pressed in the upper second position of the lifting movement by the hydraulic pressure against the sealing surface 85 and thus seals the working area. In the lower first stroke position, the second wing 8 is pressed against the sealing surfaces 86 and is also tight in the work area. In Fig. 1 and Fig. 8 are second wing 8 in the lower first stroke position with A, second wing 8 in the upper second stroke position with B and second wing 8, which are in an intermediate position, denoted by C.

Die ersten und zweiten Taschen 80, 81 sind an gegenüberliegenden Seitenflanken 7a, 7b der radialen Ausnehmung 7 in unterschiedlichem radialen Abstand von der Achse 4a des zweiten Laufrades 4 angeordnet. Dabei weisen die Taschen 80, 81 einen Überlappungsbereich 83 mit gleichem radialen Abstand von der Achse 4a des zweiten Laufrades 4 auf. Durch den Überlappungsbereich 83 entsteht eine Strömungsverbindung zwischen den zweiten Arbeitsräumen 13a, 13b beidseits des Flügels 8 in der Zwischenstellung C des zweiten Flügels 8, wie in Fig. 1 und Fig. 8 dargestellt ist. Die Taschen 80, 81 erstrecken sich dabei nicht über die volle Breite b des zweiten Laufrades 4, sondern sind von dessen Stirnflächen beabstandet. Durch die ausgebildeten Führungsflächen 84 ist sichergestellt, dass die zweiten Flügel 8 immer richtig in den Ausnehmungen 7 geführt sind.The first and second pockets 80, 81 are arranged on opposite side flanks 7a, 7b of the radial recess 7 at different radial distance from the axis 4a of the second impeller 4. In this case, the pockets 80, 81 on an overlap region 83 at the same radial distance from the axis 4a of the second impeller 4. The overlapping area 83 creates a flow connection between the second working spaces 13a, 13b on both sides of the wing 8 in the intermediate position C of the second wing 8, as shown in FIGS. 1 and 8. The pockets 80, 81 do not extend over the full width b of the second impeller 4, but are spaced from its end faces. The formed guide surfaces 84 ensure that the second wings 8 are always guided correctly in the recesses 7.

Durch die beschriebene Lösung ergibt sich, dass die Taschen 80, 81 zusammen mit den zweiten Flügeln 8 eine Ventilfunktion ausüben. Dies macht es möglich, das Hydrauliköl direkt dem Ausgleichsraum 82 zuzuführen, wie im in Fig. 8 dargestellten Ausführungsbeispiel vorgesehen ist. Dabei münden die Verbindungskanäle 15a zwischen dem ersten Arbeitsraum 10 und dem zweiten Arbeitsraum 13 direkt in die Ausgleichsräume 82 der Ausnehmungen 7 ein. Diese Ausführung ist besonders bei zweiten Laufrädern 4 mit geringem Durchmesser einsetzbar, um räumliche Zwänge bei der Fertigung der Verbindungskanäle 15 zu vermeiden. Ein weiterer Vorteil ist, dass das Hydrauliköl, welches bei Antrieb zum Beispiel des ersten Laufrades 3, zwischen dem ersten und zweiten Arbeitsraum 10 und 13 gefördert wird, direkt und ohne Umwege durch den Ausgleichsraum 82 strömt, wodurch Strömungsverluste vermieden werden können.By the described solution it follows that the pockets 80, 81 perform a valve function together with the second wings 8. This makes it possible to supply the hydraulic oil directly to the equalizing space 82 as provided in the embodiment shown in FIG. 8. Here, the connecting channels 15a open between the first working space 10 and the second working space 13 directly into the compensation chambers 82 of the recesses 7 a. This embodiment can be used especially with second wheels 4 with a small diameter in order to avoid spatial constraints in the production of the connecting channels 15. Another advantage is that the hydraulic oil which, when driving, for example, the first impeller 3, between the first and second working space 10th and 13 is conveyed, flows directly and without detours through the expansion chamber 82, whereby flow losses can be avoided.

Zur Steuerung der Drehzahl, Drehrichtung und des Drehmomentes des Abtriebsstranges sind beispielsweise Exzenter 22 aufweisende Verstellmechanismen 30 vorgesehen, welche nicht Gegenstand dieser Anmeldung sind. Die Funktion der Verstellmechanismen ist beispielsweise in der AT 502.908 Al näher erläutert.To control the speed, direction of rotation and the torque of the output train eccentric 22 having adjusting mechanisms 30 are provided, for example, which are not the subject of this application. The function of the adjustment mechanisms is explained in greater detail in, for example, AT 502,908 A1.

Das als Pumpe wirkende erste Laufrad 3 und das als Maschine wirkende zweite Laufrad 4 bilden einen im Wesentlichen geschlossenen hydraulischen Kreislauf zwischen dem Arbeitsraum 10 und 13. The acting as a pump first impeller 3 and acting as a machine second impeller 4 form a substantially closed hydraulic circuit between the working space 10 and 13th

Claims

PATENTANSPRÜCHE 1. Hydraulisches Getriebe (1) mit harmonischem Übergang des Druckmediums zwischen zwei als Zellenläufer ausgebildeten Verdrängungsmaschinen mit einem radial verschiebbare erste Flügel (6) aufweisenden ersten Laufrad (3) und einem radial verschiebbare und schwenkbare zweite Flügel (8) aufweisenden zweiten Laufrad (4), wobei das erste Laufrad (3) innerhalb des zweiten Laufrades (4) angeordnet ist und die ersten Flügel (6) des ersten Laufrades (3) entlang einer zylindrischen Lauffläche (9) des umgebenden zweiten Laufrades (4) geführt sind und das zweite Laufrad (4) und der Führungskörper (11) miteinander drehverbunden sind, wobei jeder zweite Flügel (8) an einem Ende sowohl radial verschiebbar, als auch schwenkbar in einer radialen Ausnehmung (7) des zweiten Laufrades (4) und am anderen Ende unverschiebbar, aber schwenkbar in einer Ausnehmung (44) des Führungskörpers (11) angeordnet ist, und wobei pro radialer Ausnehmung1. Hydraulic transmission (1) with harmonious transition of the pressure medium between two trained as a cell rotor displacement machines with a radially displaceable first wing (6) having first impeller (3) and a radially displaceable and pivotable second wing (8) having second impeller (4) , wherein the first impeller (3) within the second impeller (4) is arranged and the first vanes (6) of the first impeller (3) along a cylindrical running surface (9) of the surrounding second impeller (4) are guided and the second impeller (4) and the guide body (11) are rotationally connected to each other, wherein each second wing (8) at one end both radially displaceable, and pivotally in a radial recess (7) of the second impeller (4) and immovable at the other end, but pivotally mounted in a recess (44) of the guide body (11) is arranged, and wherein per radial recess (7) des zweiten Laufrades (4) zumindest ein Überströmkanal vorgesehen ist, welcher zumindest in einer Stellung des zweiten Flügels (8) eine Strömungsverbindung zwischen dem zweiten Arbeitsraum (13) und einem durch den zweiten Verdrängungskörper (8), den Seitenflanken (7a, 7b) und dem Boden (7c) der radialen Ausnehmung (7) begrenzten Ausgleichsraum (82) herstellt, dadurch gekennzeichnet, dass der Überstromkanal durch zumindest eine seitliche Tasche (80, 81) in der radialen Ausnehmung (7) gebildet ist, wobei die Tasche (80, 81) in zumindest einer Stellung des zweiten Laufrades (4) vom zweiten Flügel (8) überstrichen wird.(7) of the second impeller (4) at least one overflow channel is provided, which at least in a position of the second wing (8) has a flow connection between the second working space (13) and through the second displacement body (8), the side edges (7a, 7b) and the bottom (7c) of the radial recess (7) limited compensating space (82) manufactures, characterized in that the overflow channel is formed by at least one lateral pocket (80, 81) in the radial recess (7), wherein the pocket (80, 81) in at least one position of the second impeller (4) is swept by the second wing (8). 2. Getriebe (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Strömung durch die seitliche Tasche (80, 81) durch den Hub des zweiten Flügels2. Transmission (1) according to claim 1, characterized in that the flow through the lateral pocket (80, 81) through the stroke of the second wing (8) gesteuert ist.(8) is controlled. 3. Getriebe (1) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass pro Ausnehmung (7) zumindest eine erste und eine zweite seitliche Tasche (80, 81) vorgesehen ist, wobei die erste und die zweite Taschen (80, 81) an gegenüberliegenden Flanken (7a, 7b) der Ausnehmungen (7) angeordnet sind.3. Transmission (1) according to claim 1 or 2, characterized in that per recess (7) at least a first and a second lateral pocket (80, 81) is provided, wherein the first and the second pockets (80, 81) opposite flanks (7a, 7b) of the recesses (7) are arranged. 4. Getriebe (1) nach Anspruch 3, dadurch gekennzeichnet, dass die ersten und zweiten Taschen (80, 81) radial versetzt zueinander angeordnet sind.4. Transmission (1) according to claim 3, characterized in that the first and second pockets (80, 81) are arranged radially offset from one another. 5. Getriebe (1) nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die ersten und zweiten Taschen (80, 81) zumindest einen von der Achse (4a) des zweiten Laufrades (4) gleich beabstandeten Bereich aufweisen. 5. Transmission (1) according to claim 3 or 4, characterized in that the first and second pockets (80, 81) have at least one of the axis (4a) of the second impeller (4) equidistant area. 6. Getriebe (1) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass bei einem einen im Wesentlichen keulenartigen Querschnitt mit ersten und zweiten Verdickungen (8a, 8b) an beiden Enden aufweisenden zweiten Flügel (8), wobei die zweite Verdickung (8b) in der radialen Ausnehmung (7) geführt ist, die zweite Verdickung (8b) konkav gekrümmte Seitenflanken (8c) aufweist.6. gear (1) according to one of claims 1 to 5, characterized in that in a substantially club-like cross section with first and second thickenings (8 a, 8 b) at both ends having second wing (8), wherein the second thickening ( 8b) is guided in the radial recess (7), the second thickening (8b) has concavely curved side edges (8c). 7. Getriebe (1) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass bei Ausbildung eines zwischen den beiden Laufrädern (3, 4) zumindest ersten Arbeitsraumes (10) und zwischen dem zweiten Laufrad (4) und einem diesen umgebenden Führungskörper (11) zweiten Arbeitsraumes (13), wobei das zweite Laufrad (4) zumindest einen radialen Verbindungskanal (15, 15a) zur Strömungsverbindung der ersten und der zweiten Arbeitsräume (10, 13) aufweist, zumindest ein radialer Verbindungskanal (15a) in die radiale Ausnehmung (7), vorzugsweise im Bereich des Bodens (7c) der radialen Ausnehmung (7), einmündet.7. Transmission (1) according to one of claims 1 to 6, characterized in that when forming a between the two wheels (3, 4) at least first working space (10) and between the second impeller (4) and a surrounding guide body ( 11) second working space (13), wherein the second impeller (4) at least one radial connecting channel (15, 15a) for flow connection of the first and the second working spaces (10, 13), at least one radial connecting channel (15a) in the radial recess (7), preferably in the region of the bottom (7c) of the radial recess (7), opens. 8. Getriebe (1) nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die in Richtung der Achse (4a) des zweiten Laufrades (4) gemessene axiale Erstreckung (e) der ersten und/oder zweiten Tasche (80, 81) geringer ist als die in axialer Richtung gemessene Breite (b) des zweiten Laufrades (4), wobei vorzugsweise die radiale Ausnehmung (7) von den Stirnseiten (4b, 4c) des zweiten Laufrades (4) beabstandet ist.8. gear (1) according to one of claims 1 to 7, characterized in that in the direction of the axis (4a) of the second impeller (4) measured axial extent (e) of the first and / or second pocket (80, 81) is smaller than the width measured in the axial direction (b) of the second impeller (4), wherein preferably the radial recess (7) from the end faces (4b, 4c) of the second impeller (4) is spaced. 2007 12 13 Fu/Ka 2007 12 13 Fu / Ka
PCT/EP2007/063888 2006-12-22 2007-12-13 Hydraulic gearing Ceased WO2008077812A1 (en)

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ATA2138/2006 2006-12-22

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Publication number Priority date Publication date Assignee Title
CN107218215A (en) * 2017-08-03 2017-09-29 郭素英 Vane type volumetric pump
WO2023246204A1 (en) * 2022-06-24 2023-12-28 清华大学 Dual-mode compressor

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Publication number Priority date Publication date Assignee Title
GB205815A (en) * 1922-10-20 1924-09-18 Rudolf Loehnert Improvements in or relating to hydraulic change speed gears
DE19532703C1 (en) * 1995-09-05 1996-11-21 Guenther Beez Pump or hydraulic motor with inner and outer rotors
WO2007006064A1 (en) * 2005-07-07 2007-01-18 Josef Stollberger Hydraulic drive

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB205815A (en) * 1922-10-20 1924-09-18 Rudolf Loehnert Improvements in or relating to hydraulic change speed gears
DE19532703C1 (en) * 1995-09-05 1996-11-21 Guenther Beez Pump or hydraulic motor with inner and outer rotors
WO2007006064A1 (en) * 2005-07-07 2007-01-18 Josef Stollberger Hydraulic drive

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107218215A (en) * 2017-08-03 2017-09-29 郭素英 Vane type volumetric pump
CN107218215B (en) * 2017-08-03 2019-01-01 郭素英 Vane type volumetric pump
WO2023246204A1 (en) * 2022-06-24 2023-12-28 清华大学 Dual-mode compressor

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