EP0284987B1 - Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune - Google Patents

Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune Download PDF

Info

Publication number
EP0284987B1
EP0284987B1 EP88104660A EP88104660A EP0284987B1 EP 0284987 B1 EP0284987 B1 EP 0284987B1 EP 88104660 A EP88104660 A EP 88104660A EP 88104660 A EP88104660 A EP 88104660A EP 0284987 B1 EP0284987 B1 EP 0284987B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
control
regulator
regulating device
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
EP88104660A
Other languages
German (de)
English (en)
Other versions
EP0284987A2 (fr
EP0284987A3 (en
Inventor
Gerhard Beutler
Hermann Maier
Clemens Krebs
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0284987A2 publication Critical patent/EP0284987A2/fr
Publication of EP0284987A3 publication Critical patent/EP0284987A3/de
Application granted granted Critical
Publication of EP0284987B1 publication Critical patent/EP0284987B1/fr
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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a control device according to the preamble of claim 1.
  • the delivery rate settings of the pumps are indefinite because, due to the approximately constant working pressure, no relationship can be derived which would allow a uniform delivery rate setting for all pumps, i.e. enables parallel operation. Therefore, the pumps can take any delivery settings at any time, e.g. one pump can be in maximum and the other pump in minimum delivery setting. This has the following disadvantages.
  • the pumps oscillate at a swivel angle, even if the total amount delivered does not change. This results in losses and noises.
  • the pumps are deliberately set to slightly different controller characteristics.
  • the first pump regulates eg at 200 bar, the second at 205 bar and the third at 210 bar.
  • the load is thus clearly defined and the pendulum is avoided, although the pumps are subject to different wear due to different loads.
  • an increase in pressure in stages is predetermined in this known method.
  • the invention is based on the object of designing a control device of the type described at the outset in such a way that hydraulic synchronous operation or parallel operation is achieved while ensuring uniform loading of the machines with one another.
  • an additional control signal is included in the control, which is generated as a function of the volume setting of the machines and which is given to the associated controllers as an average setpoint.
  • the achieved by the inventive design synchronization of the pump results from the fact that each controller is supplied with a correction signal in dependence of the (position) deviation X is -X is to be formed, of each of the volume setting of the associated machine essentially linearly dependent control signal and the setpoint signal formed as the mean value of the control signals. There is no significant increase in pressure in the controller characteristic curve, because this is reduced again by regulating the pumps to the same delivery rate.
  • the solution according to the invention is characterized by low losses.
  • the embodiment according to claim 6 leads to a simple and practical construction in machines with reversible throughput direction.
  • the design according to claim 8 includes simple and practical features for remote control of the pressure regulator.
  • the pumps denoted by 1 are connected by line sections 2 to a common working pressure line 3 leading to a consumer B, the number of pumps being able to be increased as desired, which is illustrated by the position symbol 4, which denotes connections for further possible pumps.
  • the pump units are identical to one another.
  • Each adjusting device 5 of the pumps 1 is assigned a pressure regulator 6 with a first proportional control valve 7 in the form of a pressure compensator, the slide 8 of which regulates the passage of a connecting line 9 which starts from the associated working pressure line section 2 and into the piston chamber 10 of a cylinder 11 of the adjusting device 5 flows.
  • the slide 8 is acted upon by a line section 12 with the working pressure against a valve spring 15, the spring force of which is optionally adjustable.
  • the piston annular space 16 of the cylinder 11, in which a compression spring 17 is arranged for the purpose of resetting the adjusting device 5, is connected to the connecting line 9 by a line section 18 and can thus be subjected to the working pressure.
  • the pressure regulator 6 described so far including an adjustable nozzle, designated 19, in a discharge line 20 extending from the piston chamber 10 and a parallel line 21 connected to the latter and originating from the control valve 7 is of a conventional design and is therefore known, so that a functional description can be dispensed with in detail. It should be emphasized that the pressure regulators 6 set a working pressure which, apart from a slight change in pressure, can be regarded as essentially constant. The slight change in pressure in the working pressure in the control range of the pressure regulator 6 is due to the progressive characteristic curve of the springs 15 and 17, as well as to the friction and self-adjusting forces of the adjusting device 5, and is about 3 bar in the case of conventional pressure regulators 6.
  • each pump 1 is assigned a control means, generally designated 25, which acts on a second control valve 37 to be described with a control signal which is dependent on the respective delivery rate setting of the associated pump 1 and with a setpoint signal common to all pumps.
  • the control means 25 is formed by a pressure relief valve 26, which is arranged in a line 27, which continues from the outlet of the pressure relief valve 26 as a discharge line 28, and which branches off behind a throttle 29 from a line 30 which starts from the connecting line 9 containing the working pressure .
  • the control means 25 generates in the beginning after the restrictor 29 section 31 of the line 30 a depending on the particular delivery setting of the associated pump 1 control signal X is.
  • An actuator 32 in the form of a plunger or stylus 33 is used to transmit the respective setting corresponding to the delivery quantity setting, which abuts at one end an inclined surface 35 present on the adjusting piston 34 of the cylinder 11 outside the latter and acts on the slide of the pressure relief valve 26 by means of a spring 36 and applied against the inclined surface 35 is.
  • the adjusting element 32 is displaceably mounted in its longitudinal direction, so that when the adjusting piston 34 is adjusted longitudinally, it performs a longitudinal movement which adjusts the pressure limiting valve.
  • the aforementioned second control valve (proportional control valve), designated 37 is arranged in the form of a pressure compensator, the slide 38 of which is connected on the one hand by a line section 39 to the line 30 and on the other hand by a line section 41 to a connecting line 42, to which the control valve 37 associated with the other pump 1 or all the existing control valves 37 are also connected by means of the line sections 41.
  • the line 30 and the connecting line 42 are short-circuited in the region of each control valve 37 by a connecting line 43 which circumvents the latter and in which a throttle 44 is arranged.
  • the throttles 44 generate a control signal X soll in the connecting line 42, which is common to all the control valves 37.
  • the slide 38 of which is acted upon on both sides by a valve spring 45, 46, of which the spring force of the valve spring 46 is adjustable, the pressure signals X is and X is to be weighed against one another, as a result of which the control valve 37 is in line 47 correction signal X K generated, which the control valve 7 is a control deviation X is -X is to be signaled.
  • the line 48 can be loaded externally with any pressure or, in a simplified manner, be connected to the line section 31 at the node 49. A connection of line 48 to line 9 would also be possible, similar to the embodiment to be described in FIG. 3.
  • the arrangement is such that the pressure relief valve 26 opens when the adjusting device 5 is pivoted in, ie during an adjusting movement of the adjusting piston 34 to the left, as a result of which the control signal X is or the control pressure present in the connecting line 31 is reduced, ie it becomes a this adjustment is degressive pressure signal X and generated by means of the control valve 37 a progressive pressure signal X m.
  • the latter acts on the slide 8 of the control valve 7 against the working pressure.
  • the working pressure at the control valve 7 is no longer only in equilibrium with the force of the spring 15 (controller setting), but the controller setting increases as a function of the control deviation X ist -X soll by the pressure signal X K.
  • the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.
  • the desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.
  • the configuration according to the invention is suitable for pumps which can be set in both delivery directions.
  • the first control valves 7 are connected to a common remote control valve 52, which can be formed by a pressure limiting valve.
  • the second control valves 51 are formed by adjustable throttles 53, which are each arranged in line sections 54, which originate from line sections 55 holding the control signal X K and lead to a common connecting line 56 connected to the outlet, in which the remote control valve 52 is arranged.
  • An essential difference from the first exemplary embodiment is that the line sections 55 containing the control signal X K are connected directly to the connecting line 9 containing the working pressure via line sections 57 with throttles 58.
  • valve 51 immediate connection line 59 provided with a throttle 60, to which is the pressure signal X and to the pressure signal X containing lines 31 are connected 42 also in the embodiment of Fig. 2, wherein the slide of the control valve 51 by comparable with the embodiment according to FIG. 1 line sections 61, 62 on the one hand is connected to the pressure signal X, and on the other hand to the pressure signal X is simultaneously acted upon.
  • valve springs 63, 64 are provided on both sides of the slide, of which the valve spring 64 is adjustable.
  • the pressure limiting valve 26 opens when the adjusting device 5 is pivoted in by a certain amount, as a result of which the pressure signal X ist is generated by pressure relief in the line section 31. Due to the pressure relief, the slide of the control valve 51 is shifted slightly to the left, as a result of which the passage in the control valve 51 is throttled and an increasing pressure is built up in the line section 55, which progressively acts on the slide 8 of the control valve 6 to support the force of the valve spring 15, as a result of which the pressure increase in the controller characteristic is reached.
  • the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.
  • the desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.
  • the or all control valves 7 or pressure regulator 6 can be controlled simultaneously with only one control element.
  • a control valve 71 is arranged in the connecting line 9 connecting the working pressure line to the piston chamber 10 of the cylinder 11 of the adjusting device 5, the slide 72 of which, on the one hand, is connected to that of the pressure relief valve 26 set pressure signal X, and on the other hand to the averaged pressure signal X can be acted upon, and that in principle corresponds to 37 in FIG. 1 the second control valve.
  • control valve 71 immediate connection line 43 is provided with the restrictor 44, on the one hand to the pressure signal X should compound containing line 42, and on the other hand connected to the containing the working pressure connection pipe 9 via the restrictor 29th
  • the slide 72 of the control valve 71 is also acted upon on both sides by the forces of valve springs 73, 74, the force of the valve spring 74 being adjustable.
  • a control valve 76 which is common to all pumps 1 is provided and which is arranged in a line 77 branching off from the working pressure line 3, from which to each adjusting device 5
  • Line section 78 branches off with a throttle 79, which is between the control valve 71 and Piston chamber 10 of the adjusting device 5 is connected to the connecting line 9.
  • the control valve 76 thereby regulates the pressure in the piston chamber 10 of all pumps and thus the adjustment device 5 of all pumps simultaneously.
  • the pressure signal X ist is weighed against the averaged pressure signal X soll at the control valve 71 and the valve slide 72 assumes a position dependent on the control deviation X ist -X soll .
  • control valve 76 which is a pressure control valve in the present exemplary embodiment, is acted upon by the line section 82 connected to the working pressure line 3 against a valve spring 83 with working pressure.
  • control valves 37, 51 and 71 are centered on the center due to the action of valve springs on both sides. They are thus able on the one hand and / or on the other hand to process signals effective pressure, which is depending on the size of the existing control deviation X -X should effected.
  • a throttle 84 or 85 is assigned to the control valve 71 both on the input side and on the output side toward the outlet.
  • FIG. 4 shows, as an exemplary embodiment, a sectional view of a pressure limiting valve 26 in an enlarged view.
  • the actuating element 32 acts on the one hand her makeup CDn and on the other hand engaging on the slide 87 spring 88 on the slider 87 of the pressure relief valve 26, which is the control signal X by means of control edges 89 that is, the slider 87 regulates acting control pressure.
  • the valve housing 93 is screwed into the housing of the cylinder 11 or an attachment part of the same.
  • the slide 87 is located in an adjusting bush 94, which can be adjusted axially in the valve housing 93 by means of a thread 95 by turning an attack element, here a hexagon socket 96, and can be locked by means of a lock nut 97 screwed onto the adjusting bush 94.
  • port 98 e.g. 1 and 2 can be connected to the line 27, and a transverse bore 99 which intersects the bore 91 in the adjusting bush 94 and which corresponds to the line 27, an input throttle 100 is arranged which corresponds to the throttles 29.
  • the line 31 can be connected to the connection 101.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Operation Control Of Excavators (AREA)

Claims (8)

  1. Dispositif de régulation destiné à au moins deux machines hydrostatiques qui sont en relation par l'intermédiaire d'au moins une conduite sous pression commune, et dont le débit de sortie, ou d'entrée est variable, dans lequel à chaque machine est affecté un dispositif de réglage comportant un piston de réglage hydraulique et un dispositif de régulation pour la régulation de son réglage de débit,
       caractérisé par le fait que
       à chaque dispositif de régulation (6) est affecté un moyen de commande (25, 51, 71) qui applique au dispositif de réglage correspondant (6) un signal de correction (XK), qui est produit en fonction d'un signal de commande (Xréel) qui dépend selon une fonction sensiblement linéaire de la position de réglage de débit instantanée de la machine concernée (1), et d'une valeur nominale (Xnominal) qui est de préférence une valeur moyenne hydraulique des signaux de commande (Xréel) de toutes les machines (1).
  2. Dispositif de régulation selon la revendication 1,
       caractérisé par le fait que
       le moyen de commande est susceptible d'être commandé au moyen d'un dispositif de mesure de course qui coopère avec le dispositif de réglage (5) ou avec une pièce rapportée sur celui-ci.
  3. Dispositif de régulation selon la revendication 2,
       caractérisé par le fait que
       le dispositif de mesure de course est formé par une surface oblique (35) située sur une partie du dispositif de réglage (5), de préférence sur le piston de réglage (34) et par un élément de réglage (32) qui palpe la surface oblique (35).
  4. Dispositif de régulation selon l'une des revendications 1 à 3,
       caractérisé par le fait que
       le moyen de commande présente un étranglement réglable ou une valve de régulation de pression, en particulier une valve de limitation de pression (26).
  5. Dispositif de régulation selon l'une des revendications 2 à 4,
       caractérisé par le fait que
       les machines (1) sont agencées pour fonctionner en débitant dans les deux sens et que les dispositifs de mesure de course se trouvent dans leur position médiane lorsque les dispositifs de réglage (5) sont en position zéro.
  6. Dispositif de régulation selon l'une des revendications 1 à 5,
       caractérisé par le fait que l'on prévoit
       une valve de régulation (7) sous forme de balance de pression qui peut être soumise d'une part à la pression de travail, à l'encontre d'un ressort (15) de valve, et d'autre part, à un signal de correction (XK).
  7. Dispositif de régulation selon l'une des revendications 1 à 6,
       caractérisé par le fait que
       le moyen de commande présente une deuxième valve de régulation (37 ; 51 ; 71) sous forme d'une balance de pression qui peut être soumise d'une part au signal de commande (Xréel) qui est fonction du réglage de débit de la machine (1) concernée, et d'autre part, à la valeur moyenne (Xnominal) des signaux de commande (Xréel).
  8. Dispositif de régulation selon l'une des revendications 1 à 7,
       caractérisé par le fait que
       chaque régulateur (6) est relié à une valve de commande à distance commune (52) au moyen de conduits dérivés (54).
EP88104660A 1987-04-02 1988-03-23 Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune Expired - Lifetime EP0284987B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3711050 1987-04-02
DE19873711050 DE3711050A1 (de) 1987-04-02 1987-04-02 Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen

Publications (3)

Publication Number Publication Date
EP0284987A2 EP0284987A2 (fr) 1988-10-05
EP0284987A3 EP0284987A3 (en) 1989-12-27
EP0284987B1 true EP0284987B1 (fr) 1991-09-18

Family

ID=6324676

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104660A Expired - Lifetime EP0284987B1 (fr) 1987-04-02 1988-03-23 Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune

Country Status (2)

Country Link
EP (1) EP0284987B1 (fr)
DE (2) DE3711050A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4025638C1 (fr) * 1990-08-13 1991-12-05 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
DE19601544C1 (de) * 1996-01-17 1997-07-24 Hydrokraft Gmbh Förderstromregler
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1188948B (de) * 1960-07-16 1965-03-11 Metallwerk Glockerau G M B H Arbeitsfluessigkeitsmengen-Regeleinrichtung fuer hydrostatische Pumpen und Motoren
GB1056655A (en) * 1964-11-16 1967-01-25 Ifield & Sons Pty Ltd R J Torque control means for variable displacement hydraulic pumps
DE2017656A1 (de) * 1969-04-23 1970-11-05 Pensa, Carlo, Esino Lario, Como (Italien) Hydraulische FördermengeneinsteHvorrichtung für eine oder mehrere Pumpen
US4055046A (en) * 1976-12-22 1977-10-25 Caterpillar Tractor Co. Control system having override for fluid operated work elements
CA1104033A (fr) * 1977-02-24 1981-06-30 Commercial Shearing, Inc. Dispositif de commande a compensation de pression et de debit, a couple constant et element de detection de viscosite
DE8335902U1 (de) * 1983-12-14 1987-06-04 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-Regeleinrichtung für eine verstellbare Hydropumpe

Also Published As

Publication number Publication date
EP0284987A2 (fr) 1988-10-05
DE3711050A1 (de) 1988-10-20
EP0284987A3 (en) 1989-12-27
DE3864867D1 (de) 1991-10-24
DE3711050C2 (fr) 1992-02-13

Similar Documents

Publication Publication Date Title
EP0294776B1 (fr) Circuit de commande pour un organe de réglage hydraulique
DE2505780A1 (de) Regeleinrichtung fuer eine pumpe
DE19906230B4 (de) Einrichtung und Verfahren zur Kopplung einer Vielzahl von Pumpen
EP0471166B1 (fr) Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables
EP0284987B1 (fr) Régulateur pour au moins deux machines hydrostatiques en relation par une conduite sous pression commune
DE10219850B3 (de) Regeleinrichtung mit Grenzwertregelventil
DE3844401C2 (de) Regeleinrichtung für eine Verstellpumpe
DE19626793C1 (de) Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen
EP0284988B1 (fr) Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
DE3919175C2 (fr)
DE3711049C2 (fr)
EP0284989B1 (fr) Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune
EP1934487A1 (fr) Dispositif de commande hydraulique
DE3413913A1 (de) Verstelleinrichtung fuer das verdraengungsvolumen einer verdraengermaschine
EP0746690B1 (fr) Systeme regulateur pour pompe hydraulique
DE3528781C2 (fr)
CH625979A5 (en) Adjusting device for a sheet levelling machine for the adjustment of the levelling gap
DE3703576A1 (de) Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
DE3027819A1 (de) Vorrichtung zur regelung einer verstellpumpe
EP0331958A2 (fr) Dispositif de commande hydraulique
DE19808127C2 (de) Leistungsregeleinrichtung
DE19831587C2 (de) Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe
DE19756600C1 (de) Leistungsregelventil
EP0954703B1 (fr) Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques
EP1304482B1 (fr) Dispositif de réglage de la puissance totale

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: A2

Designated state(s): DE FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT SE

RHK1 Main classification (correction)

Ipc: F04B 49/08

17P Request for examination filed

Effective date: 19900102

17Q First examination report despatched

Effective date: 19910207

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

REF Corresponds to:

Ref document number: 3864867

Country of ref document: DE

Date of ref document: 19911024

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
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
EAL Se: european patent in force in sweden

Ref document number: 88104660.1

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: IT

Payment date: 20060331

Year of fee payment: 19

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

Ref country code: SE

Payment date: 20070313

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20070316

Year of fee payment: 20

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

Ref country code: GB

Payment date: 20070322

Year of fee payment: 20

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

Ref country code: FR

Payment date: 20070319

Year of fee payment: 20

EUG Se: european patent has lapsed
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: 20080322

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070323