EP0846861B1 - Pompe annulaire à engrenages continuellement variable - Google Patents

Pompe annulaire à engrenages continuellement variable Download PDF

Info

Publication number
EP0846861B1
EP0846861B1 EP97112646A EP97112646A EP0846861B1 EP 0846861 B1 EP0846861 B1 EP 0846861B1 EP 97112646 A EP97112646 A EP 97112646A EP 97112646 A EP97112646 A EP 97112646A EP 0846861 B1 EP0846861 B1 EP 0846861B1
Authority
EP
European Patent Office
Prior art keywords
adjusting ring
annular gear
pressure
pump
set forth
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.)
Expired - Lifetime
Application number
EP97112646A
Other languages
German (de)
English (en)
Other versions
EP0846861A1 (fr
Inventor
Siegfried A. Dipl.-Ing. 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
Priority claimed from DE29703369U external-priority patent/DE29703369U1/de
Application filed by Individual filed Critical Individual
Priority to CA002219062A priority Critical patent/CA2219062C/fr
Priority to JP9326670A priority patent/JPH10169571A/ja
Priority to MXPA/A/1997/009436A priority patent/MXPA97009436A/xx
Priority to BR9706122A priority patent/BR9706122A/pt
Priority to CN97120306A priority patent/CN1114041C/zh
Priority to KR1019970065854A priority patent/KR100287915B1/ko
Priority to US08/984,794 priority patent/US6126420A/en
Priority to ARP970105700A priority patent/AR010678A1/es
Publication of EP0846861A1 publication Critical patent/EP0846861A1/fr
Publication of EP0846861B1 publication Critical patent/EP0846861B1/fr
Application granted granted Critical
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • 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
    • F04C2/084—Toothed wheels
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow

Definitions

  • the invention relates to an adjustable gerotor pump according to the preamble of Claim 1, in its specific delivery rate [delivery volume / speed] can be changed.
  • a good solution is a gerotor pump as an internal gear pump, which none Crescent moon needed because the tooth shape is chosen so that by tooth head contact each tooth chamber is reliably sealed by the neighboring tooth chambers is, so that a good volumetric efficiency is achieved.
  • Gerotor pumps have the possibility that the center distance of the inner rotor to the external rotor or the angular position of the eccentric axis, in relation to the housing and thus be changed in relation to the inlet and outlet openings in the housing can.
  • a constructive solution could be that the external rotor in one Eccentric ring is mounted, which is rotatably arranged and adjustable in the housing. For a delivery rate adjustment up to An angle adjustment is close to zero, which is very desirable when starting cold the eccentric axis of 90 ° is required.
  • the control spring would also have to do this drive very long distances, which is because of the required soft characteristic would lead to dimensions that are difficult to achieve. Because especially at Motor vehicle engines and automatic transmissions very frequent and fast speed changes would take place, the eccentric ring high spin and Delays experience what leads to large adjustment forces, to large adjustment resistances and would lead to high wear. That too is Large control rooms are at great risk of contamination.
  • the invention solves the problem of small control paths and quick, precise reaction the control of variable gerotor pumps through the characteristic features of Claim 1.
  • the negative ratio of the angle of rotation the eccentric axis or the planet carrier to the angle of rotation of the pinion or Planet gear equal to the number of teeth of the pinion if the number of teeth difference between ring gear and pinion is one.
  • the circumference or the pitch circle of the external toothing on the adjusting ring is proportional is large, e.g. has 16 teeth, is the negative angle adjustment the eccentric axis 16 times the angle of rotation of the adjusting ring around its own Axis. Accordingly, the adjustment ring performs small angular rotations and thus small adjustment paths because it only has a small rolling movement in the housing performs.
  • the toothing of an adjustment gear designed as an internal gear is preferred a trochoid or a between the adjusting ring and the housing Cycloid internal gear.
  • Kidney-shaped housing openings forming low and high pressure openings paint over the danger of cavitation on the suction side and that of the Pinch oil on the pressure side.
  • the adjusting ring seen in the axial direction the opposite side to the kidney-shaped low-pressure and high-pressure openings circumferential, through the housing wall closed connection groove that together with built-in connecting grooves in the area the webs connecting expanding and compressing conveyor cells.
  • a channel connection is proposed between these working chambers allows a compensation oil flow, so that excessive pressure peaks at the pinch oil point and extreme negative pressures at the cavitation point can be avoided.
  • a zero stroke pump reduces the construction effort, because after that only the compression chamber in the gerotor pump itself has the high pressure leads.
  • the momentary pole is when the delivery rate is reduced, that is the pitch point around which the adjusting ring rotates in each rotational position changes in such a way that in the closed position of the adjusting ring hydrostatic force component of the compacting workspace no longer a moment exerts on the adjusting ring, the pump is not quite when using a spring adjust to zero.
  • the high-pressure working area also points the largest cross-sectional area in the axial direction, which may to inadmissibly large axial deflection of the housing and in particular the Lid leads.
  • the external toothing of the adjustment gear is preferably made in one piece with the Adjustment ring, especially by sintering.
  • the external teeth can basically also formed by a stamped sheet metal ring on the adjusting ring become.
  • the internal toothing can advantageously be punched on the housing Sheet metal ring are formed.
  • the internal toothing of the adjustment gearbox made in one piece with the housing, which then is preferably also sintered together with the internal toothing.
  • the inner rotor of the pump can be shrunk onto the shaft, preferably Axial connecting channels are provided between the shaft shrink fit and the inner rotor are.
  • the inner rotor is integral with the Shaft executed.
  • gerotor pump according to the invention is to be used as a high pressure pump, then high demands on the construction must be met.
  • Particularly advantageous is the teeth of the ring gear set to avoid rapid wear to train on one of the two runners as roles. This also works with slow-running high-pressure rotary piston machines.
  • rollers are so that the machine does not become too large in diameter preferably arranged on the inner rotor.
  • the radial compensating force can then also be used to adjust the delivery rate Toothed ring pump can advantageously be used if the chambers in the Interlocking of the adjustment gear via channels and preferably a control rotary valve within limits both in their number and in their rotational position can be changed, as is also slow with the above mentioned running high-pressure rotary piston machines can be used.
  • the control rotary valve can be adjusted in angle to adjust the position of the high and low pressure chambers.
  • Throttles are preferably provided in the channels to the control rotary valve, and the control rotary valve has control bores around the chambers in the leakage spaces to connect to the tank.
  • the adjustment of the adjustment ring is not directly hydraulic as above described, but made mechanically according to claim 6, then serve the high-pressure cells between the teeth of the adjustment gear only the force and thus the tension compensation in the adjusting ring to minimize its deformation.
  • the number and choice of the high pressure cells are selected so that the adjusting ring due to the internal working pressure field, the tooth heads of the toothing of the Adjusting gear keeps in touch contact.
  • both parts, the Adjustment ring with its external teeth and the housing ring with its internal teeth are produced with sufficient accuracy using the sintering process. It can namely enough tooth play will then be provided to bridge the manufacturing tolerances.
  • the axial play of the adjusting ring in the housing is advantageously essential executed smaller than the axial play of the ring gear set.
  • a gerotor pump shown in FIGS. 1 a to 2 has an inner rotor 3 and an external rotor 4, one with their external and internal teeth Form gear ring 5.
  • the external toothing of the inner rotor 3 has one Tooth less than the internal toothing of the external rotor 4.
  • the inner rotor 3 is shrunk onto a rotationally driven shaft 2. Between the shaft shrink fit and the inner rotor 3 are axial connecting channels 48 intended.
  • Both the shaft 2 and thus the inner rotor 3 and the outer rotor 4 are in a pump housing, parts of which are designated 1, 1 'and 1 ", rotatable stored.
  • the axis of rotation of the external rotor 4 is spaced parallel, i.e. eccentric, to the axis of rotation of the inner rotor 3.
  • the eccentricity or the distance between these two axes of rotation is designated 17.
  • the inner rotor 3 and the outer rotor 4 form a fluid delivery space between them.
  • This fluid delivery chamber is sealed off from one another in a pressure-tight manner Conveyor cells 7 divided.
  • the individual conveyor cells 7 are each between two successive teeth of the inner rotor 3 and the internal teeth of the External rotor 4 formed by two successive teeth of the inner rotor Head or flank contact 6 with two successive, opposite Have teeth of the inner toothing of the outer rotor 4.
  • Kidney-shaped adjoining the conveyor cells 7 are located in the housing Except grooves 8 and 9, which a fluid inflow and outflow to and form from the conveyor cells 7.
  • the groove 8 forms the low-pressure opening for supplying the fluid
  • Groove 9 the high pressure opening for the fluid drain.
  • the groove 8 extends from near a location of deepest tooth engagement in the area of a web 11 on the housing side almost semicircular up to close to a place of slight tooth meshing, that of a further housing-side web 10 diametrically opposite the web 11 is covered.
  • the groove 9 on the high pressure side in Figure 1a extends in Housing mirror-symmetrical to groove 8 on the opposite side of the both webs 10 and 11.
  • the external rotor 4 is in a ring 14 added, which in turn can be adjusted relative to the housing.
  • This adjustment ring 14 is the outer rotor 4 by means of its outer circumference 13 a sliding pivot bearing 12 is freely rotatable.
  • the adjusting ring 14 has one External toothing 24 which meshes with an internal toothing 24 '.
  • the internal toothing 24 ' is non-rotatably connected to the housing. Your center falls with the Rotation axis of the inner rotor 3 together.
  • the internal toothing is in the exemplary embodiment 24 'formed on a stamped sheet metal ring 27 on the housing part 1 "or rigidly attached to the housing part 1 (FIG. 2).
  • the internal toothing 24 ' could, however, also be formed directly in one piece on the housing.
  • the housing with the internal toothing 24 'and the adjusting ring 14 with the external toothing 24 form an adjustment gear 20 for adjusting the angular position of the External rotor 4 to inner rotor 3.
  • the internal toothing 24 ' has at least one tooth more than the external teeth 24 of the adjusting ring 14.
  • the tooth difference is exactly one.
  • the Difference in the diameter of the root circle of the internal toothing 24 'and the tip circle the external teeth 24 double the eccentricity 17.
  • the pump of the embodiment according to Figures 1a to 2 is by mechanical Actuating means adjusted.
  • a two-armed rocker arm 41, 43 is around an axis 42 spaced parallel from the axis of rotation of the inner rotor 3 between two end positions, namely those of Figures 1a and 1c, pivotable back and forth.
  • the pivoting movement of the rocker arm 41, 43 is achieved by means not shown motorized.
  • the storage of the rocker arm 41, 43 takes place in the between the two side housing parts 1 'and 1 "clamped middle housing part 1.
  • the axis of rotation 42 of the rocker arm 41, 43 lies in the zero position of FIG.
  • the aforementioned angle ⁇ is the angle around which the adjusting ring 14 is turned its own axis rotates when the rocker arm 41 is actuated.
  • the pump is shown in section A-A of Figure 1b.
  • the rotary drive Shaft 2 is in the two housing halves 1 'and 1 "in the longitudinal direction the shaft 2 are arranged side by side and between them Include rotating parts of the gerotor pump, rotatably slide bearings and by means of sealed with a seal to the outside.
  • the fluid supply and discharge are in the housing part 1 '' provided; the two slot openings 8 and 9 in both housing halves 1 ' and 1 ".
  • the adjusting ring 14 is only at one axial end with the external toothing 24 provided.
  • the sheet metal ring 27 in turn is on a circular ring cylinder 1 attached, which surrounds the adjusting ring 14 and an intermediate housing between the two housing halves 1 'and 1 ".
  • the inner peripheral surface of the Intermediate housing 1 and the outer peripheral surface of the adjusting ring 14 form in their non-toothed areas rolling cylinder surfaces 26 and 29 over which the Adjustment ring 14 due to the adjustment gear 20 slip-free compared to the circular cylindrical Intermediate housing 1 rolls.
  • the pitch circles 15, 16 of the adjustment gear are in the rolling cylinder surfaces 26 and 29.
  • the adjusting ring 14 has seen in the axial direction on the opposite side to the kidney-shaped low pressure and high pressure openings 8, 9 a whole or semicircular all-round connecting groove closed by the housing wall 1 ' 45 which, together with connecting grooves 46 and 47 (FIG. 5) that expand and compress in the area of the webs 10, 11 Conveying cells 7 connects.
  • Figures 3a and 3b show a zero stroke pump, which is between a regulated Position, the zero position, and a single end position for maximum delivery rate is adjustable.
  • measures have been taken to use the delivery rate V ⁇ limit increasing speed of the inner rotor 3. That from adjusting ring 14 and External rotor 4 formed component is against the force of a pressure spring trained control spring 36 adjusted, namely by the high pressure work space 35 of the pump used as a cylinder space above the external rotor 4 as a control piston becomes.
  • the control spring 36 is between a first, torsionally rigid linkage on the outside Scope of the adjusting ring 14 and a second linkage designed as a pivot bearing biased to pressure on the housing such that they always the adjusting ring 14 tries to push it into its end position for maximum promotion.
  • the High-pressure working chamber of the pump which also functions as a cylinder working chamber 35 to be used, lie over the inner peripheral surface of the outer rotor 4 in such a way that the adjusting ring 14 against the force of the control spring 36 in the adjusting mechanism 20 is twisted.
  • the pump regulates itself with increasing speed and thus accompanying increasing pressure on the pressure side automatically to ideally in the zero position shown in Figure 3b.
  • the use of the pump work space 35 as a cylinder space for the adjustment of the Adjusting gear 20 reduces the construction work of the pump.
  • the high-pressure working space 35 is also between at least one space 86 the adjusting ring 14 and the inner wall of the intermediate housing 1, on the the internal toothing of the adjustment gear 20 is also connected.
  • the pressure field 86 thus formed over the high-pressure working space 35 presses the adjusting ring 14 against the radially opposite the pressure field 86 and the working space 35 Teeth 87 of the internal toothing 24 'of the adjustment gear 20.
  • the pressure chambers are such that in the position of Fig. 3b with respect to the instantaneous pole M of the adjusting gear 20, a spring 36 which is sufficiently stressing arises.
  • FIG. 21 Another possibility of reducing a gerotor pump with increasing Figures 4a, 4b and 5 show the rotational speed the adjustment gear, now designated 21, is designed as a partial internal gear with an only partially externally toothed adjusting ring 14 and one accordingly only partially internally toothed sheet metal ring 27.
  • the partial outer toothing is 22 and the partial internal teeth designated 23.
  • the two partial gears 22 and 23 serve for the slip-free rolling of the rolling circular cylinder surfaces 26 and 29 of the adjusting ring 14 and the housing in the control range.
  • the sealing piece 89 On the housing is a sealing piece which extends over the width of the adjusting ring 14 89 arranged.
  • the sealing piece 89 is cylindrical in cross section, in the exemplary embodiment circular cylindrical.
  • the sealing piece 89 presses sealingly against it Opposite on the adjusting ring 14 trained as a counter-seal Thickening or tooth head-like point 88.
  • Sealing piece 89 and thickening 88 are the partial toothings 22 and 23 arranged approximately diametrically opposite, so that between the sealing point 88, 89 formed in this way and the partial toothing 22, 23 over the outer circumferential surface of the adjusting ring 14 within a room 28 can build up a pressure on the outer circumference of the adjusting ring 14 pressing and using the adjusting ring as an adjusting piston against the force of one Control spring 32, which is comparable to the control spring 36 of the previous example, adjusted.
  • the sealing piece 89 is, seen from the control spring 32, on the back the bead-shaped for articulating the control spring 32 on the adjusting ring Thickening 88, pressing against this thickening 88, mounted on the housing.
  • the pressure chamber 28 used as an adjusting cylinder over the outer circumference of the Adjustment ring 14 there is high pump pressure.
  • the room 28 is on the outside
  • the circumference of the adjusting ring 14 is approximately above the high-pressure groove opening 9 and is with the groove opening 9 by radial channels 9a recessed in the housing.
  • the sealing piece 89 formed by a sealing sleeve which is about an axis of rotation of the inner rotor 3rd parallel axis is rotatably mounted in the housing. Also connecting the expanding and compressing delivery cells of the pump by the rotating Connecting groove 45 and the two radial connecting grooves 46 and 47, as in In connection with the embodiment of Figure 1 have been described can be seen very well in FIG.
  • control pumps are shown, which are particularly suitable for use as high pressure pumps.
  • the teeth of the inner rotor 51 by rollers 50 in the embodiment circular cylindrical Rollers formed, which are rotatably supported about axes parallel to the axis of rotation of the inner rotor 51 are.
  • the inner rotor 51 is made in one piece with its drive shaft, as can be seen in particular in FIG. 6b.
  • the Adjustment ring 14 in the area of its outer peripheral surface, which is seen radially extends over the high pressure side of the pump, with the pressure of the high pressure side applied.
  • the outer extending over the low pressure side of the pump
  • the circumferential surface of the adjusting ring 14 is subjected to the low pressure.
  • the adjustment gear 20 by means of its teeth 52, 53 pressure-tight chambers 56 'on the high pressure side and pressure tight chambers 56 "on the low pressure side.
  • the pressure-tight chambers 56 'and 56 are via channels 58 in a housing part 57 ( Figure 6b) with the pressure and suction spaces, i.e. with the high pressure and the Low pressure side of the pump connected.
  • the channels 58 open into the tooth root areas the internal toothing 53 in the intermediate housing 55.
  • 57 are in the housing part at least one connecting channel 60 to a slot opening 9 and one diametrically Opposing further connecting channel 61, which in the other groove opening 8th flows, provided.
  • the connecting channels 60 and 61 are connected by means of a control rotary valve 59 connected to channels 58. As shown in Figures 6b, 7a and 7b, this Control rotary valve 59 on an annular cylindrical rotating body in the housing part 57 rotatably received concentrically to the shaft 2 and in this recording controlled angle adjustable.
  • this Control rotary valve 59 on an annular cylindrical rotating body in the housing part 57 rotatably received concentrically to the shaft 2 and in this recording controlled angle adjustable.
  • By connecting channels 60 and 58 or 61 and 58 are accordingly the two slot openings 8 and 9 each with their rear, pressure chambers formed by the teeth 52, 53 of the adjustment gear 56 'and 56 "connected. These chambers 56' and 56" are thus below the Pressure of the slot opening assigned to them.
  • connection between the channels 60 and 58 or 61 and 58 is via throttles 74 and 75 in channels 60 and 61 and channel end portions 62 and 63, these channel end portions 62 and 63, in the exemplary embodiment simple bores, via connecting channels in the Rotary body of the control rotary valve 59 to the near the root circle of the internal toothing 53 opening channels 58 can be connected.
  • control rotary valve 59 By turning the control rotary valve 59, the position of the high pressure and the low pressure chambers 56 'and 56 " are selectively chambers 56 'corresponding to the angular position of the control rotary valve and 56 ".
  • Control grooves are optionally channels 60 and 61 with their assigned Channels 58 or by means of control bores 76, 78 in the rotating body, the second pair of channels 77 and 79 connected to the leak spaces 80 to the tank 81. hereby the pressure chambers 56 ', 56 "are optionally printed or with the leakage spaces connected.
  • the resultant Force vector can also be changed in a controlled manner, at least with regard to its direction can, such that it laterally at the pivot point of the adjusting ring 14 If the momentary pole M points past, the force vector of the partial pressure field acts of the chambers 56 'and 56 "via the lever arm thus formed as the adjusting moment on the adjusting ring 14.
  • the adjusting ring 14 rotates under the action of this Moments in its equilibrium position, in which the adjusting torque acting from outside and the moment of the working pressure field between the inside and the External rotor 51, 54 in equilibrium with respect to the respective instantaneous pulse M. stand. In this way, a demand-oriented funding rate can be achieved.
  • a flushing and regulating pump 72 is arranged, which in the case of a closed circuit via check valves 73 in the low pressure range greatly reduced pressure replaces the external leak oil.
  • the control rotary valve and the housing part 57 as shown in FIG. 7a, the control bores 76, 77 and 78, 79 on which the chambers 56 'and 56 "with the leakage spaces Connect 80 to the fluid reservoir.
  • This control is known as commutation in orbital rotary piston motors. For example, if there are sixteen chambers 56 ', then thirty commutator holes provided in the control ring 59, which alternate with the suction and Pressure slot openings are connected. Because such controls basically are known, explanations are not required.
  • a rocker arm 64 acts in one the rocker arm 41, 43 for adjusting the adjusting ring 14 in the exemplary embodiment of Figures 1a to 2 comparable way.
  • the rocker arm 64 is in the housing limited pivotable about an axis that is parallel to the axis of rotation of the inner rotor 3 runs. With one free end it is connected to the ball bearing Rotating body of the control rotary valve 59 coupled.
  • the simply straight rocker arm 64 is with its on the opposite side beyond its axis of rotation End hinged to two linear adjustment means 65, which the rocker arm 64 around its Swivel the axis of rotation back and forth. As a result, the rotary body of the control rotary valve 59 adjusted within a limited angular range.
  • FIGS. 8a to 8c show the three essential adjustment phases of the gerotor pump shown in Figures 6a to 7b.
  • the pump according to Figures 8a to 8c is designed as a high-pressure reversing pump.
  • FIGS. 9a to 9c A self-regulating high-pressure pump is shown in FIGS. 9a to 9c.
  • the Embodiment of Figures 9a to 9c is explicitly only a zero stroke pump shown with a spring-loaded pressure piece 93 on one side 94 of the housing. It is only indicated on the side opposite the pressure piece 93 95 of the housing a second mirror image arrangement with a second, spring-loaded Thrust piece 93 '.
  • the pump becomes pressure piece 93 ' a zero stroke pump for both directions of rotation.
  • the adjusting ring 14 is against a flank via the pressure piece 93, on which a control spring 117 acts the external teeth 24 of the adjusting ring 14 in a position for maximum promotion biased in one direction.
  • the control spring 117 acts in the manner of before described control springs 32 and 36.
  • the second pressure piece 93 ' which also together with its control spring from the other side against a tooth flank of the External toothing 24 can be pressed, presses the adjusting ring 14 in the direction of the maximum funding in the opposite direction.
  • a pressure piece 93 or the other pressure piece 93 ' depending on the desired direction of rotation, in side engagement with the external toothing 24.
  • the zero stroke pump can do this be prepared that depending on the conditions at the installation site as left or clockwise pump can be installed by the housing for both directions of rotation is prepared and when installing the pump that for the desired Required direction of rotation including spring is installed.
  • the pump could even be further developed into a reversing pump by using an adjusting means for example an actuating cylinder, pressing the position on the control spring 117 the control spring 117 changes in a controlled manner.
  • the adjustment ring 14 is, as already in connection with Figures 6a to 8c described, pressurized on its outer peripheral surface by the Teeth 24, 24 'of the adjustment gear with the high pressure side and the low pressure side connected chambers 91 'and 91 "are formed High pressure side and the low pressure side via channels 92 'and 92 ", in the foot area the external teeth 24 'open with the respective chambers 91' and 91 ".
  • groove 96 provided in the housing connecting several of the chambers 91 'or 91 "to one another becomes special good, continuous adjustment of the external pressurization of the adjusting ring 14 reached.
  • the force acting on the adjusting ring 14 is smaller than that caused by the pressure in the outer pressure chambers 91 'and 91 "force exerted on the adjusting ring 14, which in in the same way for the others with such pressure fields regulating themselves Pumping applies.
  • This is achieved in that the pressurized acting radially Area in work spaces 90 'and 90 "is smaller than the pressurized radially acting surface of the pressure chambers 91 'and 91' '.
  • the position of the adjustment ring 14 is thus determined by the resulting force vector due to the pressure in the Workrooms 90 'and 90 "and the pressure rooms 91' and 91" determined.
  • FIG. 10 shows a variant of the self-regulating zero stroke or reversing pump 9a-9c, but the teeth of the inner rotor again are integrally formed with the inner rotor.
  • the counter toothing 103 is by means of a high-speed milling cutter shaped, the radius of which is equal to the radius 104 of the external teeth 100.
  • the Rotary axis of the milling cutter i.e.
  • the housing part 102 can thus initially in one piece in the die casting process without intermediate housing getting produced.
  • the toothing 103 is then with the milling operation described worked out. This way it becomes a particularly economical one Production of the housing part having the internal toothing of the adjustment gear 102 possible.
  • the housing is in two parts the housing part 102 having the internal toothing and a cover part 111.
  • the housing part 102 could in principle, as in the previously described exemplary embodiments also, be divided into two yourself again with one of the previously described Housing parts 55 comparable intermediate housing part.
  • the adjusting ring 14 again at least on one of its axial sides on a circumferential groove 45 which over the two other axial grooves 46 and 47, which in turn preferably in the cover-like Housing part 111 are formed in the area of the webs between the suction area 114 and the printing area 115 establishes a channel connection between the Squeeze chamber 112 and the cavitation chamber 113.
  • the pump is in turn by means of a control spring 117 automatically cut off.
  • the control spring 117 acts on the pressure element 93 External teeth 100 of the adjusting ring 14.
  • a second control spring 117 In the formation of a self-regulating Reversing pump can again be provided a second control spring 117.
  • a funding characteristic of this type is particularly useful for motor vehicles advantageous in which a pump according to the invention from the motor vehicle engine is driven, the pump speed in a fixed relationship to the motor speed stands.
  • Motor vehicles require in the lower engine speed range, i.e. from the start, immediately large amounts of oil. After reaching a predetermined engine speed and the associated pump speed and delivery is over the no or no speed range connected to the specified engine speed significant increase in the delivery rate of the pump is required.
  • the funding rate would continue to increase unrestricted with increasing pump speed, would exceed the actual Need are promoted with a corresponding unnecessarily high Power requirement for the pump.
  • a higher oil pressure is required.
  • control spring system 117 To achieve the desired funding characteristics, namely with a steep one Increase in the delivery rate in the lower speed range, one in comparison slow rise or even zero rise in the middle speed range and finally again a steeper increase in the upper speed range, will be a soft one first control spring and a harder second control spring, which together form a control spring system 117, connected in series.
  • the control spring system 117 is under tension installed so that it hardly gives way in the lower speed range.
  • the soft first spring begins to compress until it reaches upper end of the middle speed range against the harder second control spring Stop comes to rest. With a further increase in speed, the delivery characteristic then determined by the harder second control spring.
  • the pump according to the invention can not only be used as a lubricant pump can be used, it can also advantageously be the oil for a hydraulic Valve clearance compensation and / or in particular as a pump for a valve timing adjustment be used. It can be used alone for each of the applications mentioned or used in combination.
  • the invention is suitable for these purposes
  • the pump is basically available in all of the described versions, because, due to their infinitely variable adjustability, everyone desired funding characteristics can be adjusted very precisely.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (24)

  1. Pompe annulaire à engrenages réglable en continu, comportant
    a) un carter fixe,
    b) un rotor intérieur (3) entraíné et monté tournant dans le carter au moyen d'un arbre (2), et
    c) un rotor extérieur (4) également monté tournant et engrenant avec le rotor intérieur (3),
    d) la différence du nombre de dents de la couronne dentée (5) formée du rotor intérieur (3) et du rotor extérieur (4) est égale à un, avec une forme des dents pour laquelle, par contact (6) de la tête des dents, il se forme un grand nombre de cellules de refoulement (7) étanches les unes par rapport aux autres, qui s'expansent et se compriment,
    e) avec des ouvertures basse pression et haute pression (8, 9) en forme de haricot, fixes dans le carter, disposées latéralement dans la zone des cellules de refoulement (7) et qui sont séparées les unes des autres par des cloisons (10, 11),
    f) et avec un anneau de réglage (14) dans lequel le rotor extérieur (4) est supporté sur son diamètre extérieur (13) et qui peut rouler, par son cercle périphérique extérieur ou cercle partiel (15), sur un cercle périphérique intérieur ou cercle partiel (16), afin de faire varier la position angulaire de l'axe d'excentrique (excentricité 17) de la couronne dentée (5) par rapport au carter,
    g) la différence entre les diamètres des deux cercles périphériques ou cercles partiels (15, 16) étant égale au double de l'excentricité (17) de la couronne dentée (5),
    caractérisée en ce que
    h) il est formé un engrenage intérieur (24, 24' ; 22, 23 ; 52, 53Z ; 100, 103) complet ou partiel par une denture extérieure (24 ; 22, 52, 100) sur l'anneau de réglage (15) et par une denture intérieure (24'; 23 ; 53 ; 103) côté carter, qui sont en engrènement entre elles, ce qui fait que les cercles périphériques ou partiels (15, 16) de l'anneau de réglage (14) et du carter roulent les uns sur les autres sans glissement.
  2. Pompe annulaire à engrenages selon la revendication 1, caractérisée en ce que les cercles périphériques ou partiels (15, 16), roulant sans glissement les uns sur les autres, de l'anneau de réglage (14) et du carter, sont formés par les cercles partiels de l'engrenage intérieur (24, 24' ; 22, 23 ; 52, 53; 100, 103) et ces cercles partiels présentent la même excentricité que la couronne dentée (5).
  3. Pompe annulaire à engrenages selon la revendication 1 ou 2, caractérisée en ce que la denture intérieure (24' ; 23 ; 53 ; 103) comporte, pour l'engrènement avec la denture extérieure (24 ; 22, 52, 100), au moins, de préférence précisément, une dent de plus que la denture extérieure (24 ; 22, 52, 100), dans le cas de dentures seulement partielles, cette différence étant rapportée à des dentures imaginées complètes.
  4. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que des dents (24 ; 22, 52, 100) de la denture extérieure ne sont disposées que sur le côté de l'anneau de réglage (14), pour former l'engrenage intérieur, et en ce que la largeur restante de l'anneau de réglage (14) sert de surface cylindrique de roulement (26, 29).
  5. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que pour former une pompe à course zéro sur le côté refoulement, un volume (28) compris entre une paroi du carter formant le cercle périphérique intérieur (16) et une paroi de l'anneau de réglage (14), formant le cercle périphérique extérieur (15), est alimenté en pression, et l'anneau de réglage (14) est utilisé comme piston de réglage (31) contre un ressort de régulation (2), pour actionner le mouvement de régulation de l'anneau de réglage (14).
  6. Pompe annulaire à engrenages selon l'une des revendications 1 à 4, caractérisée en ce que pour former une pompe réversible sont prévus des moyens (40, 41, 42, 43, 44) qui permettent l'actionnement mécanique du mouvement de régulation de l'anneau de réglage (14) dans les deux sens à partir de la position non régulée (position zéro) de la pompe annulaire à engrenages dans la position de refoulement.
  7. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce qu'entre l'anneau de réglage (14) et le carter est disposée au moins une zone de pression (86) étanche, reliée à la haute pression et agissant radialement, qui presse de manière étanche l'anneau de réglage (14) sur le côté opposé, vu radialement, par ses têtes de dent (87) ou emplacements (88) similaires à des têtes de dent, contre les têtes de dent ou emplacements (89) similaires à des têtes de dent du carter.
  8. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que sur le carter est prévue au moins une pièce d'étanchéité (89) qui présente, sur sa face arrière (85), entre le carter et la pièce d'étanchéité, au moins une zone de pression étanche, qui presse de manière étanche la ou les pièces d'étanchéité (89) contre la ou les têtes de dent ou emplacements (88) similaires à des têtes de dent de l'anneau de réglage (14), de préférence en l'alimentant en haute pression.
  9. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que pour former une pompe à course zéro, la chambre de travail (35) constituant la pression agit comme cylindre de réglage, par l'intermédiaire du rotor extérieur (4), sur l'anneau de réglage (14), et il est prévu un ressort de régulation (36) qui tend à déplacer l'anneau de réglage (14) en direction du volume de refoulement maximal.
  10. Pompe annulaire à engrenages selon l'une des revendications précédentes, en particulier pour une pression de travail élevée, caractérisée en ce que les dents de la couronne dentée (5), formant les cellules de refoulement, sont réalisées sur l'un des deux rotors (51, 54) en tant que rouleaux (50) qui sont montés tournants dans le rotor (51, 54) respectif.
  11. Pompe annulaire à engrenages selon l'une des revendications 2 à 10, caractérisée en ce que la denture (24, 24' ; 22, 23 ; 52, 53 ; 100, 103) du mécanisme de réglage (20 ; 21) s'étend sur toute la largeur de la couronne dentée (5).
  12. Pompe annulaire à engrenages selon l'une des revendications 2 à 11, caractérisée en ce que le mécanisme de réglage forme des chambres (56', 56") étanches à la pression qui sont en liaison, dans une partie (57) du carter, par des canaux (58), avec les compartiments de refoulement ou d'aspiration de la pompe.
  13. Pompe annulaire à engrenages selon la revendication précédente, caractérisée en ce que les chambres (56', 56") opposées, tant par leur nombre que par leur position, sont alimentées en haute pression par une soupape tournante de commande (59) et en basse pression par des canaux (58, 60, 61, 62, 63).
  14. Pompe annulaire à engrenages selon la revendication 12 ou 13, caractérisée en ce que la somme des surfaces soumises à la haute pression dans les chambres de refoulement (56', 56") entre l'anneau de réglage (14) et le carter, sont réalisées plus petites en ce qui concerne l'effet de leur force que la somme des surfaces soumises à pression des chambres de travail (35) dans la denture de la pompe.
  15. Pompe annulaire à engrenages selon l'une des revendications 1 à 14, caractérisée en ce que pour former une pompe de course zéro, la force d'un ressort tend à faire tourner l'anneau de réglage (14) dans le sens du refoulement maximal ; de préférence la force du ressort est transmise, au moyen d'une pièce de pression (93), à un flanc de dent (94) de la denture extérieure (24 ; 100) de l'anneau de réglage (14).
  16. Pompe annulaire à engrenages selon la revendication précédente, caractérisée en ce que plusieurs chambres de dent (91"), situées sur le côté refoulement, entre la partie de carter (55) formant la denture intérieure du mécanisme de réglage et la denture extérieure de l'anneau de réglage (14), sont reliées, par des canaux (92'), à la haute pression, et les chambres de dent (91") opposées et correspondantes sont reliées à la basse pression par des canaux (92").
  17. Pompe annulaire à engrenages selon la revendication 15 ou 16, caractérisée en ce que les canaux (92') sont disposés de manière qu'ils puissent être séparés de la haute pression et/ou reliés à celle-ci, les uns après les autres, avec débit décroissant, par le mouvement de rotation de l'anneau de réglage (14).
  18. Pompe annulaire à engrenages selon l'une des revendications 15 à 17, caractérisée en ce que sur les deux côtés (94, 95) du carter sont disposées des pièces de pression (93) et, pour former une pompe réversible, les pièces de pression (93) peuvent être actionnées au moyen de cylindres de réglage.
  19. Pompe annulaire à engrenages selon l'une des revendications 15 à 18, caractérisée en ce que dans la zone du mécanisme de réglage (20 ; 21), entre l'anneau de réglage (14) et le carter (1 ; 55), les rainures (96) s'étendant dans la direction périphérique et qui relient entre elles des chambres de dent (91', 91") de la denture (24, 24'), sur le côté haute pression ou sur le côté basse pression ou sur les deux côtés, dans une longueur qui convient pour l'accord des forces hydrauliques dans ces zones, sont pratiquées dans la partie de carter (1') disposée latéralement.
  20. Pompe annulaire à engrenages selon l'une des revendications 15 à 19, caractérisée en ce qu'un système de régulation à ressort (117), destiné à produire la force de ressort, comporte au moins deux ressorts et, dans une première zone de régulation de quantité, il existe une courbe caractéristique de ressort souple avec une petite croissance de la force et, dans une deuxième zone suivante de régulation de quantité, une autre courbe caractéristique avec une plus grande croissance de la force sur le parcours de régulation.
  21. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que l'anneau de réglage (14) comporte au moins sur un côté axial une rainure périphérique (45) qui réalise, à travers au moins deux autres rainures axiales (46, 47) qui sont disposées de préférence dans une partie de carter (111) de type couvercle, une liaison en canal entre l'espace d'écrasement (112) et l'espace de cavitation (113) dans les zones des cloisons entre la zone d'aspiration (114) et la zone de refoulement (115).
  22. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce que l'anneau de réglage (14) présente, sur son diamètre extérieur, des dents extérieures (100) de forme circulaire, pour former le mécanisme de réglage, et le carter (102) est réalisé en tant que denture intérieure (103) par roulement de l'anneau de réglage (14) avec l'excentricité (17) commune à la couronne dentée (5).
  23. Procédé de fabrication de la pompe annulaire à engrenages selon la revendication 22, caractérisé en ce que le carter (102) est fabriqué par un procédé de moulage sous pression- et la forme des dents de la denture intérieure (103) est formée au moyen d'une fraise cylindrique.
  24. Pompe annulaire à engrenages selon l'une des revendications précédentes, caractérisée en ce qu'elle est utilisée pour alimenter un moyen de réglage à actionnement hydraulique pour le réglage et l'ajustage des temps de commande de soupapes d'un moteur à combustion interne commandé par soupapes.
EP97112646A 1996-12-04 1997-07-23 Pompe annulaire à engrenages continuellement variable Expired - Lifetime EP0846861B1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
CA002219062A CA2219062C (fr) 1996-12-04 1997-10-27 Pompe a engrenages a couronne infiniment variable
JP9326670A JPH10169571A (ja) 1996-12-04 1997-11-27 無限可変リングギアポンプ
CN97120306A CN1114041C (zh) 1996-12-04 1997-12-03 可无限变化的环形齿轮泵
BR9706122A BR9706122A (pt) 1996-12-04 1997-12-03 Bomba de engrenagem com coroa de aro dentado infinitamente variável
MXPA/A/1997/009436A MXPA97009436A (en) 1996-12-04 1997-12-03 Infinated regulation gear pump infin
KR1019970065854A KR100287915B1 (ko) 1996-12-04 1997-12-04 무한 가변 링 기어 펌프
US08/984,794 US6126420A (en) 1996-12-04 1997-12-04 Infinitely variable ring gear pump
ARP970105700A AR010678A1 (es) 1996-12-04 1997-12-04 Bomba de engranajes anulares de regulacion infinita

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE29621073 1996-12-04
DE29621073U 1996-12-04
DE29703369U DE29703369U1 (de) 1996-12-04 1997-02-25 Stufenlos verstellbare Zahnringpumpe
DE29703369U 1997-02-25

Publications (2)

Publication Number Publication Date
EP0846861A1 EP0846861A1 (fr) 1998-06-10
EP0846861B1 true EP0846861B1 (fr) 2003-03-19

Family

ID=26059702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97112646A Expired - Lifetime EP0846861B1 (fr) 1996-12-04 1997-07-23 Pompe annulaire à engrenages continuellement variable

Country Status (3)

Country Link
EP (1) EP0846861B1 (fr)
AT (1) ATE235003T1 (fr)
ES (1) ES2192242T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202007018987U1 (de) 2006-04-19 2010-05-27 Schwäbische Hüttenwerke Automotive GmbH Verstellbare Rotationspumpe mit Verschleißminderung
DE202014106121U1 (de) 2014-12-17 2015-01-15 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit kompakter Stellstruktur zur Verstellung des Fördervolumens

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29816658U1 (de) 1998-09-16 2000-02-03 Trochocentric (International) AG, Jona, Schweiz Massenausgleichssystem mit einer Schmierölpumpe für Hubkolbenmotoren
ITBO20020275A1 (it) * 2002-05-10 2003-11-10 Pierburg Spa Pompa rotativa a portata variabile , in particolare per olio
DE10338212A1 (de) * 2003-08-20 2005-03-10 Zahnradfabrik Friedrichshafen Volumenstromvariable Rotorpumpe
DE202004004231U1 (de) * 2004-03-17 2005-07-28 Härle, Hermann Volumenstromveränderbare Verdrängerpumpe
JP5141993B2 (ja) 2008-08-01 2013-02-13 アイシン精機株式会社 オイルポンプ
UA119134C2 (uk) 2012-08-08 2019-05-10 Аарон Фьюстел Роторні пристрої з розширюваними камерами, що мають регульовані проходи для робочого плинного середовища, а також системи, що мають такі пристрої
JP5814218B2 (ja) * 2012-11-30 2015-11-17 株式会社山田製作所 内接歯車式ポンプ

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01104991A (ja) * 1986-08-27 1989-04-21 Sumitomo Electric Ind Ltd 可変容量歯車ポンプ
DE4231690A1 (de) * 1992-09-22 1994-03-24 Walter Schopf Innenzahnradpumpe mit variierbarer Förderleistung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202007018987U1 (de) 2006-04-19 2010-05-27 Schwäbische Hüttenwerke Automotive GmbH Verstellbare Rotationspumpe mit Verschleißminderung
DE202014106121U1 (de) 2014-12-17 2015-01-15 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit kompakter Stellstruktur zur Verstellung des Fördervolumens
EP3034780A1 (fr) 2014-12-17 2016-06-22 Schwäbische Hüttenwerke Automotive GmbH Pompe rotative comprenant une structure compacte destinee au reglage d'un volume d'alimentation

Also Published As

Publication number Publication date
ES2192242T3 (es) 2003-10-01
ATE235003T1 (de) 2003-04-15
EP0846861A1 (fr) 1998-06-10

Similar Documents

Publication Publication Date Title
DE3333647C2 (de) Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor
EP0362906B1 (fr) Pompe à engrènement interne
DE19542653C2 (de) Automatikgetriebe für ein motorbetriebenes Fahrzeug
DE19545492A9 (de) Drehmomentfühler sowie damit ausgestattetes Kegelscheibenumschlingungsgetriebe
EP1776525A1 (fr) Moteur a piston rotatif hydrostatique
EP0712997A2 (fr) ContrÔle des soupapes avec pompe à engrenages internes avec réglage de l'aspiration
WO2005116403A1 (fr) Commande du courant de fuite d'intervalle d'une machine a engrenages
EP2208890A2 (fr) Pompe volumétrique rotative
EP2235374A2 (fr) Pompe à engrenage intérieur, à volume variable
EP0846861B1 (fr) Pompe annulaire à engrenages continuellement variable
EP1685328B1 (fr) Pompe double ou multiple
EP1735534A1 (fr) Pompe volumetrique a debit volumetrique variable
DE4421255C1 (de) Füllstücklose Innenzahnradpumpe
DE4135904A1 (de) Kolbenpumpe, insbesondere radialkolbenpumpe
DE29703369U1 (de) Stufenlos verstellbare Zahnringpumpe
DE4224075A1 (de) Hydraulisches Antriebs- und Bremssystem
AT504984B1 (de) Ein- und auslasssteuerung für eine axialkolbenmaschine
DE4304897A1 (en) Continuously variable-ratio gearbox - has rotary vane pump with double rotor and adjustment mechanism to compensate eccentricity.
EP2119869A2 (fr) Hydromachine
DE3737961A1 (de) Innenzahnradpumpe
EP1074740B1 (fr) Machine hydrostatique à piston rotatif
DE19520405C2 (de) Hydraulischer Kreiskolbenmotor
WO2008125106A1 (fr) Moteur à pistons rotatifs
DE102010005984B4 (de) Regelölpumpe
DE10230407B4 (de) Innenzahnradpumpe mit variabler Abdichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT DE ES FR GB IT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;RO;SI

17P Request for examination filed

Effective date: 19980709

AKX Designation fees paid

Free format text: AT DE ES FR GB IT SE

RBV Designated contracting states (corrected)

Designated state(s): AT DE ES FR GB IT SE

17Q First examination report despatched

Effective date: 20010622

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT DE ES FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20030319

REF Corresponds to:

Ref document number: 59709557

Country of ref document: DE

Date of ref document: 20030424

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2192242

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20031222

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20160725

Year of fee payment: 20

Ref country code: GB

Payment date: 20160721

Year of fee payment: 20

Ref country code: DE

Payment date: 20160722

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20160720

Year of fee payment: 20

Ref country code: FR

Payment date: 20160721

Year of fee payment: 20

Ref country code: AT

Payment date: 20160721

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20160715

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59709557

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20170722

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK07

Ref document number: 235003

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170723

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20170722

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20180508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20170724