EP2690252A1 - Trochoid internal gear machine - Google Patents

Trochoid internal gear machine Download PDF

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Publication number
EP2690252A1
EP2690252A1 EP12177581.1A EP12177581A EP2690252A1 EP 2690252 A1 EP2690252 A1 EP 2690252A1 EP 12177581 A EP12177581 A EP 12177581A EP 2690252 A1 EP2690252 A1 EP 2690252A1
Authority
EP
European Patent Office
Prior art keywords
housing
rotor
filler
wall
tooth
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.)
Withdrawn
Application number
EP12177581.1A
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German (de)
English (en)
Inventor
Siegfried A. Eisenmann
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP12177581.1A priority Critical patent/EP2690252A1/fr
Publication of EP2690252A1 publication Critical patent/EP2690252A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C2/086—Carter
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the invention relates to a trochoid internal gear machine for operating as a hydraulic pump or hydraulic motor according to the preamble of claim 1.
  • Such trochoid internal gear machines are characterized by an advantageous centric design with a relatively small number of teeth difference between the outer rotor and the inner rotor, by a cheap, elongated tooth engagement line and thus by a low-noise running of the gear transmission.
  • this machine as a hydraulic pump or as a hydraulic motor, there are further advantages, namely small delivery and thus small pressure pulsations.
  • Such trochoid internal gear machines are the quietest known hydraulic gear machines.
  • Known hydrostatic gear machines have a Trochoidenveriereung having internally toothed external rotor, also called ring gear, preferably nine to fifteen teeth whose tooth root width is preferably about twice the tooth space width at the root circle and wherein the distance of the mutually facing flanks of adjacent teeth of the ring gear on the Partial circle measured measured the distance of the tooth flanks of a tooth of the ring gear on the pitch circle is preferably about the same, with a preferably two or three teeth less than the ring gear having externally toothed internal rotor, also called pinion, which meshes with the ring gear.
  • the effective tooth profile of the one wheel, so the ring gear or pinion is equal to the determined by rolling this wheel on the other wheel profile.
  • Trochoid gearing in the strict sense, but also one in which at least one wheel has a Zykloidenverzahnung or a circular arc gearing, since in the latter the tooth flank profile is very similar to a Trochoidenverzahnung in the strict sense.
  • the trochoidal shape of the tooth flanks can also be replaced by other similar curves, since it depends less on a trochoidal shape of the tooth flanks than on the "approximate" tooth shape which usually arises in trochoid toothing.
  • a trochoid internal gear machine on which the present invention is based, is known from Austrian patents no. AT 330 582 B and AT 358 932 B known.
  • the versions published there have a number of teeth difference of preferably two or possibly also three teeth between the outer rotor or the ring gear and the inner rotor or the pinion.
  • a tooth number difference of two the free space between the tooth tip circles at the point compared to the deepest tooth engagement is very narrow, so that there arranged filler is very thin.
  • the number of sealing points along the filler piece is only between two and three on the inner rotor and between three and four on the outer rotor due to the teeth of the inner rotor and the outer rotor sliding along there.
  • the filler must sit exactly and immovably in the housing. From the AT 330 582 B an attachment of the filler is known, wherein the filler near its two located in the circumferential direction of the gear machine ends axial projections or, in other words, in its central region has two notches. The lying on both sides of the notches projections are pressed into two exactly complementary shaped openings of the two pumping chamber of the pump in the axial direction limiting flat end faces of the end plates. The projections on both sides of the notches can also be glued or soldered into the recesses.
  • the filler is preferably made of a well-tempered steel but sliding softer material, such as a corresponding sliding bronze.
  • the object of the invention is to improve the known from the prior art trochoid internal gear such that it is characterized by a simpler structure, a lower production cost, a reduced noise level, increased volumetric efficiency and increased pressure performance.
  • the invention is based on the recognition that an increase in the number of teeth difference between the number of teeth of the internal teeth of the external rotor and the number of teeth of the external teeth of the internal rotor brings from two to three significant advantages.
  • Trochoiden- Internal gear machine Due to smaller specific pressure on the shaft bearings, twice as many sealing points along the filler, a much smaller Striebeck'schen pressure on the tooth flanks in the tooth engagement, a smaller shaft deflection and thus less edge stress in the shaft bearings, it is possible to increase the pressure performance of Trochoiden- Internal gear machine to increase up to 200 to 250 bar.
  • first wall and a second wall are formed between the outer rotor and the inner rotor axially limited tooth spaces.
  • the filler is formed integrally with the first wall.
  • the filler according to the invention is not a separate part which must be connected to the first wall firmly and immovably, but the filler is itself part of the first wall.
  • the first wall in turn forms a part of the housing, so that the filler piece is integrally connected to the first housing wall and thus a part of the housing of the trochoidal internal gear machine.
  • the filler is formed slightly longer in the axial direction than the width of the moving set, so that it supports for its free end in a recess in the opposite wall, in particular, the opposite housing wall, can protrude.
  • the immediately adjacent to the moving set housing wall consists of a relatively thinner dimensioned steel plate, which is provided on the running side with a sliding bearing running layer. Inexpensive, this overlay is made as one of an aluminum-tin layer bonded by atomic bonding to the steel plate in the roll-plating process.
  • This intermediate plate a recess can now be punched, which can take the free end of the filler fit, so that it is extremely stable against radial vibrations.
  • This stampable intermediate plate also has the advantage that dimensionally accurate suction and pressure kidneys for the filling and emptying of the conveyor cells of the moving set can be produced inexpensively.
  • the trochoid internal gear machine according to the invention hereinafter also referred to as machine for short, is suitable both as a hydraulic pump, the shaft of the machine being driven to generate a hydraulic flow, and as a hydraulic motor, wherein the machine is subjected to a hydraulic pressure in order to drive the shaft ,
  • the machine has a housing in which an internally toothed external rotor with a trochoid toothing is rotatably mounted about a first geometric axis.
  • the outer rotor is formed by a ring gear with an internal toothing having a number of teeth of nine to fifteen teeth.
  • the internal teeth or the external rotor have a width B in the direction parallel to the first geometric axis.
  • the housing encloses the Outrunner all around.
  • the housing is preferably composed of a plurality of coupled housing sections.
  • an externally toothed inner rotor rotatably mounted about a second axis.
  • the second axis is spaced parallel to the first axis.
  • the inner rotor is rotationally fixed on a led out of the housing shaft, which serves as a hydraulic drive in the case of operation of the machine as a drive shaft and in the case of operation as a hydraulic motor as an output shaft.
  • the external teeth of the inner rotor which is formed by a pinion on the shaft, meshes in a section with the internal teeth of the outer rotor.
  • the internal gear or the inner rotor have the width B in the direction parallel to the first and to the second geometric axis.
  • the outer rotor and the inner rotor have the same width B.
  • the toothing geometries of the inner teeth of the outer rotor and the outer teeth of the inner rotor correspond to each other so that they can interlock, but they have a tooth number difference of three.
  • the inner rotor has three teeth less than the outer rotor.
  • the number of teeth of the outer rotor and the number of teeth of the inner rotor are divisible by 3, so that the possible number of teeth ratios 12:15, 9:12 and 6: 9 result between the inner rotor and the outer rotor.
  • the tooth flank profile of the external rotor is formed by a number of geometric flat circles with the same radii corresponding to the number of teeth of the internal teeth of the external rotor.
  • the centers of these flat circles lie on a common, concentric to the outer rotor circle whose center lies on the first axis.
  • Each of the flat circles spans one out of every three adjacent teeth imaginary group of teeth of the internal teeth of the outer rotor, wherein the flat circle each defines the opposite tooth flanks of the two outer teeth of the tooth group, so that the internal toothing is formed by a circular arc toothing.
  • the exact shape of the tooth flank of the inner rotor results from the mathematical calculation of the engagement points between the two tooth flanks of the outer rotor and the inner rotor by a virtual rolling according to the kinematics during the rotation of the moving set. As a parameter serves the angular position of the eccentric axis to the gears.
  • the tooth flank radii are considerably larger, so that the Striebeck flank pressure is greatly reduced.
  • the maintenance of a lubricating film between the loaded tooth flanks allows higher working pressures.
  • One of the two walls is formed integrally with a part of the housing and thus constitutes a housing wall.
  • an approximately crescent-shaped filling piece is arranged, which fills this free space over most of its length in the circumferential direction.
  • the filler has the basic shape of a crescent, in other words a crescent moon or a sickle, but the tips of the crescent are rounded or cut off. Therefore, the filler does not completely fill this crescent-shaped free space along its length in the circumferential direction, but for the most part. In other words, the vast majority of the free area is filled with the filler.
  • the filler is immovably coupled to the housing and stands still during rotation of the inner rotor and the outer rotor.
  • the filler is designed such that on the filler inside the
  • the filler piece is formed integrally with the first wall, ie with one of the two walls of the tooth space.
  • the wall and the filler piece are a single part, in particular a forged part, e.g. from an aluminum alloy, a cast part or a milled part.
  • the first wall and the filler are made of the same material.
  • the axial extent of the filler piece from the first wall in the axial direction parallel to the axes is greater than the width of the outer rotor and the inner rotor at least in one section.
  • the extension extension projects axially into a recess which is formed axially in the opposite second wall into it.
  • This recess in the second wall is formed such that the filler is fixed in the radial direction and / or in the circumferential direction with respect to the axes.
  • the recess in the second wall has a shape such that the protruding into it portion of the filler is accommodated in the radial direction accurately in the recess, so that the filler is stably supported against radial vibrations.
  • the filler rooted to the first wall passes in its ends in a radius which prevents a sharp corner and thus a fatigue-affecting notch in the first wall in both circumferential directions, whereby a fatigue break at the location of the transition of the filler in the housing wall is avoided.
  • the circumferential extent, ie the circumferential length of the portion of the filler, which protrudes into the recess accurately seen in the circumferential direction is so less than the circumferential extent of the remaining filler that the minimum radial thickness of the portion of the filler in the radial direction at least 50% to 70% of its maximum radial thickness.
  • the partial section protruding into the recess is at least 50% to 70% thick in its edge region, relative to its geometrically defined tooth head circle cylindrical surfaces, at its thickest point, which lies opposite the point of maximum tooth engagement of the toothings.
  • the subsection formed in particular as an extension extension comprises only about 50% to 70% of the circumferential length, ie the circumferential extent of the filler.
  • the recess in the second wall does not have to be made as thin by far as in the above-mentioned, known as the prior art machine.
  • the remaining left and right of the extension extension rest of the circumferential length of the filler serves to hold down or supporting the second wall, so that it does not stand out in this area of the terminal housing, if this is to be prevented.
  • the second wall in which, in particular, the recess for the partial section of the filler piece is formed, or alternatively the first wall, which is formed integrally with the filler piece, is formed by an intermediate plate.
  • this intermediate plate preferably has a flat, thin, plate-like shape and consists in particular of a machined and, in particular, coated sheet metal part, eg a sheet steel.
  • This running layer consists, for example, of an aluminum-tin layer rolled in the roll-plating process, in particular AlSn6.
  • the recess for receiving the partial section of the filler piece, the suction and pressure kidneys connected to the hydraulic connections for supplying and disposing the tooth spaces with hydraulic working fluid and screw through-holes for screws which hold the housing together, can be inexpensively formed in the intermediate plate as a punching die. or laser cutting recesses be formed, as the Machining a simple sheet metal part is associated with very low production costs.
  • the intermediate plate forms the first wall and thus is formed integrally with the filler.
  • the filler is, for example, a forged part, a machined casting or a milled part, which has a plate-like basic shape and from which the filler protrudes vertically.
  • a further aspect of the invention comprises that the housing has a front housing in which the shaft is mounted, an intermediate housing which radially encloses the outer rotor and the inner rotor and in which the outer rotor is mounted, and a connection housing in which the shaft is mounted and which includes the hydraulic connections for supply and disposal of the tooth spaces with working fluid comprises.
  • the front housing, the intermediate housing, the intermediate plate and the connection housing are sealingly sandwiched axially in the radial direction, in particular by means of axially extending screws.
  • the front housing is formed integrally with the first wall and the filler, wherein the intermediate plate axially between the intermediate housing and the terminal housing is disposed and separates the intermediate housing and the terminal housing from each other.
  • the terminal housing consists for example of a cast iron alloy containing iron
  • the front housing consists in particular of a forged aluminum alloy, or vice versa.
  • the intermediate housing consists of a pearlitic iron alloy produced in a powder metallurgical process.
  • bearings can be arranged, which are formed as a ternary 3-material bearing bushes. If the trochoid internal gear machine is to be operated as a hydraulic motor, it is advantageous if needle bearings are arranged to the left and to the right of the outer rotor and the inner rotor.
  • FIGS. 1 to 9 show the same embodiment from different views and in different degrees of detail, describe together, wherein in the explanation of the individual figures in part to the above already explained features and reference numerals will not be discussed again.
  • the trochoidal internal gear machine for operating as a hydraulic pump or hydraulic motor has a housing 1 which consists of a front housing 49, in which a shaft 30 is mounted in a shaft bearing 25, an intermediate housing 27, which has an external rotor 2 and one on the shaft 30 shrunk-in inner rotor 3 radially encloses and in which the outer rotor 2 is rotatably mounted, and a connection housing 26, in which the shaft 30 is also mounted in a shaft bearing 24 and which hydraulic connections 33, 34, composed.
  • the internally toothed external rotor 2 rotatably mounted in the housing 1 about a first axis 44 has a trochoidal internal toothing with twelve teeth which have a width B, as in FIG FIG. 2 shown.
  • the also in the housing 1 eccentrically to the outer rotor 2 rotatably mounted about a second axis 45, with the outer rotor 2 meshing inner rotor 3 is externally toothed and has the same width B as the outer rotor 2.
  • the inner rotor has nine teeth, so three teeth less than of the Outrunner, the numbers of teeth are each divisible by three.
  • the external toothing of the inner rotor 3 communicates with the internal toothing of the external rotor 2 in the upper section in a force-transmitting manner.
  • tooth spaces 41 and 42 are formed, as in the FIGS. 1 and 9 shown.
  • These tooth spaces 41 and 42 are axially bounded by a first wall 11 integrally formed with the front housing 49, in other words part of the front housing 49, and one of the first wall 11 spaced axially parallel second wall 16, as in FIG FIG. 2 shown.
  • the tooth flank profile of the external rotor 2 is defined by a number of geometric flat circles 10 corresponding to the number of teeth of the external rotor 2.
  • one of the twelve flat circles 10 is shown with the common radius r.
  • the geometric centers 39 and 39 'of these flat circles 10 and 10' are uniformly distributed on a common, concentric to the outer rotor 2 circle 37, also called pitch circle, in the FIGS. 1 and 9 is shown in dashed lines and the center lies on the first axis 44.
  • Each of the total of twelve flat circles 10, 10 'each spans one of three adjacent teeth 46, 47 and 48 existing tooth group 38 of the external rotor 2.
  • the tooth tip diameter of the inner rotor 3 is much smaller compared to the known machine, the specific load of the shaft bearings 24 and 25 according to the FIG. 2 lower. This allows a significant increase in the printing performance of the machine.
  • FIG. 1 and 2 hatched from top left to bottom right filler 4 fills to a large extent the space between the Zahnkopf Vietnamesezylinder lake 5 and 6, which slide with the smallest possible running clearance on the filler 4 along.
  • the filler 4 is thus designed such that on the filler 4 inside rotor side the Zahnkopf Vietnamesezylinder inhabit 5 of the inner rotor 3 and the outer rotor side, the Zahnkopf Vietnamesezylinder constitutional 6 of the outer rotor 2 seals slide along.
  • the tooth spaces are thus in one with a first hydraulic port 33, FIGS. 6 and 7 , connected first tooth space 41, FIGS. 1 and 9 , and one of them sealingly separated, with a second hydraulic port 34, FIGS.
  • FIG. 2 Likewise in FIG. 2 is the filler 4 as part of the drive-side wall 11 of the front housing 49 at its radially largest point 20, FIG. 3 , shown in longitudinal section.
  • FIG. 2 shown is the axial extent of the filler 4 of the first wall 11 in the axial direction parallel to the axes 44 and 45 greater than the width B of the outer rotor 2 and the inner rotor 3, so that over the width B of the outer rotor 2 and the inner rotor. 3 axially projecting in the axial direction portion 14 of the filler 4 axially in a recess 15 which is axially formed in the opposite second wall 16, protrudes accurately.
  • the recess 15 in the second wall 16 has a shape such that the protruding into it portion 14 of the filler 4 is received in the radial direction accurately in the recess 15, so that the filler 4 is stably supported against radial vibrations.
  • connection housing 26, in the FIG. 2 shown on the right can be made of a high-strength cast alloy, between the outer and inner rotor 2 and 3 and the cast-iron terminal housing 26, an intermediate plate 17, for example, a machined steel sheet, arranged with a run-side side run layer 18.
  • the running layer 18 may consist of an aluminum-tin layer, in particular AlSn6, rolled by the roll-plating method.
  • the intermediate plate 17 can then inexpensively receive the required recess 15 for the extension extension 14 of the filler 4.
  • this intermediate plate 17 also forms the second wall 16. A recess 15 to be machined in the connection housing 26, as required in the known machine, is thus saved.
  • a recess 15 to be machined is saved in the drive-side first wall 11 of the front housing, because the filler 4 is turned there in one piece, for example, by turning by means of an eccentric chuck, as is practiced today in large numbers.
  • the recess 15 for receiving the extension extension 14 of the filler 4, with the hydraulic connections 33 and 34 connected suction and pressure kidneys 21 and 22, FIGS. 1 and 9 for the supply and disposal of the tooth spaces 41 and 42 with hydraulic working fluid, and screw through-holes 23, FIG. 2 can be produced inexpensively in the intermediate plate 17 by means of punching or by means of laser cutting.
  • the front housing 49 is formed integrally with the first wall 11 and the filler 4.
  • the intermediate plate 17 is disposed axially between the intermediate housing 27 and the terminal housing 26 and separates the intermediate housing 27 and the terminal housing 26 from each other.
  • FIG. 3 shows the filler 4 in perspective with its extension extension 14, which detects only about 60% of the circumferential length of the filler.
  • the recess 15 in the second wall 16 in the intermediate plate 17 does not have to be made as thin as in the known machine mentioned above.
  • the left and right in the FIG. 3 shown rest of the Art Culturesus 35 and 36 in the circumferential direction serves to hold down the intermediate plate 17 so that it does not stand out in this area of the terminal housing 26.
  • the circumferential extent of the portion 14 of the filler 4 which projects into the recess 15, as seen in the circumferential direction is less than the circumferential extent of the remaining filler 4, that the minimum radial thickness 19 of the portion 14 of the filler 4 in the radial direction over 50% 70% of its maximum radial thickness is 20, as in FIGS. 3 and 4 illustrated.
  • the rooted to the first wall 11 filler 4 goes in both circumferential directions at its ends 12 in a radius 13 in the first wall 11 in order to avoid a notch effect in the transition of the filler 4 in the first wall 11.
  • the tooth tips of the inner rotor 3 are provided in a known manner, each with a scraping edge 29, see FIG. 5 which are able to withstand the relatively soft surface of the inner inner cylindrical surface 5 of the filler 4 to produce a very small chip processing to compensate for the manufacturing tolerances when editing this surface.
  • the fully assembled machine is driven, for example, as an extremely low speed pump under high working pressure.
  • the shaft 30 shifts in the shaft bearings 24 and 25 according to the course of Gümbel'schen semicircle of the sliding bearing theory on the surface of the shaft bearings 24 and 25, ie in the extreme eccentric displacement of the shaft 30 and thus also the inner rotor 3.
  • the scraping edges 29 of the teeth of the inner rotor 3 optimally work the inner cylindrical surface 5 of the filler 4 for the smallest possible clearance.
  • a highly viscous oil is used, whereby the resulting machining chips are filtered out. If the machine later works in high-speed operation, the shaft 30 moves away from the bearing surface in accordance with the sliding bearing theory, so that no high, unacceptable friction power can arise between the tooth tips of the inner rotor 3 and its inner cylinder surface 5, but at the same time optimally small Leckölspalt between the tooth tips and the filler 4.
  • the bearing blocks 31 and 32 are resiliently designed for the shaft bearings 24 and 25, so that at a given deflection of the shaft 30 under high load at high working pressure no inadmissible edge support arise at the bearing edges.
  • so-called ternary ternary bearing bushes with a galvanically applied lead-tin-copper overlay which provide a high adaptability to the Wave deformation and especially have an excellent Schmerbeinbettungs sparkle.
  • the shaft plain bearings are replaced by rolling bearings, for example by needle bearings, so that the engine can be easily approached even under load. When using plain bearings, the engine would be under self-locking condition at zero speed.
  • the intermediate housing 27 is provided on its axial sides with recesses 28 to increase the surface pressure for a better Reibschuss between the intermediate housing 27 and the adjacent walls of the front housing 49 and the intermediate plate 17.
  • the filler 4 is not formed in the wall of the front housing 49, but in the wall of the terminal housing 26. In addition, it is possible to form the filler 4 in one piece with the intermediate plate 17.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP12177581.1A 2012-07-24 2012-07-24 Trochoid internal gear machine Withdrawn EP2690252A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12177581.1A EP2690252A1 (fr) 2012-07-24 2012-07-24 Trochoid internal gear machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12177581.1A EP2690252A1 (fr) 2012-07-24 2012-07-24 Trochoid internal gear machine

Publications (1)

Publication Number Publication Date
EP2690252A1 true EP2690252A1 (fr) 2014-01-29

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105863739A (zh) * 2015-02-11 2016-08-17 丹佛斯有限公司 叶板单元机械

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2433360A (en) * 1945-01-25 1947-12-30 Hiram H Haight Gear pump
US3730656A (en) * 1971-03-22 1973-05-01 Dowty Technical Dev Ltd Hydraulic apparatus
AT330582B (de) 1973-04-13 1976-07-12 Hohenzollern Huettenverwalt Zahnradmaschine
AT358932B (de) 1976-10-01 1980-10-10 Hohenzollern Huettenverwalt Hydrostatische zahnradmaschine mit einem trochoidenzahnradpaar

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2433360A (en) * 1945-01-25 1947-12-30 Hiram H Haight Gear pump
US3730656A (en) * 1971-03-22 1973-05-01 Dowty Technical Dev Ltd Hydraulic apparatus
AT330582B (de) 1973-04-13 1976-07-12 Hohenzollern Huettenverwalt Zahnradmaschine
AT358932B (de) 1976-10-01 1980-10-10 Hohenzollern Huettenverwalt Hydrostatische zahnradmaschine mit einem trochoidenzahnradpaar

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105863739A (zh) * 2015-02-11 2016-08-17 丹佛斯有限公司 叶板单元机械
CN105863739B (zh) * 2015-02-11 2018-05-22 丹佛斯有限公司 叶板单元机械
US10415565B2 (en) 2015-02-11 2019-09-17 Danfoss A/S Vane cell machine

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