NO783043L - PRESSURE CONTROLLER ON A DRAWER BRAKE VALVE IN AN INDIRECT ACTIVE PRESSURE AIR BRAKE - Google Patents
PRESSURE CONTROLLER ON A DRAWER BRAKE VALVE IN AN INDIRECT ACTIVE PRESSURE AIR BRAKEInfo
- Publication number
- NO783043L NO783043L NO783043A NO783043A NO783043L NO 783043 L NO783043 L NO 783043L NO 783043 A NO783043 A NO 783043A NO 783043 A NO783043 A NO 783043A NO 783043 L NO783043 L NO 783043L
- Authority
- NO
- Norway
- Prior art keywords
- pressure
- chamber
- piston
- spring
- brake
- Prior art date
Links
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
- B60T15/02—Application and release valves
- B60T15/04—Driver's valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
- B61H13/00—Actuating rail vehicle brakes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
- Braking Systems And Boosters (AREA)
- Regulating Braking Force (AREA)
- Braking Arrangements (AREA)
Description
Oppfinnelsen vedrorer en trykkregulator ved en forerbremseventil i en indirekte virkende trykkluftbrerase, The invention relates to a pressure regulator at a pilot brake valve in an indirectly acting compressed air glacier race,
med en til en mateledning koblet trykkreguleringsventil, som •er betjenbar av et stempel som på den ene side er belastet med en regulerbar fjær og på den annen side er påvirkbart av reguleringstrykket. with a pressure regulation valve connected to a supply line, which •is operated by a piston which is loaded on one side with an adjustable spring and on the other side is influenced by the regulation pressure.
Tidligere kjent er en trykkregulator av denne art (sveistisk patentskrift 344.749), ved hvilken stemplet på Previously known is a pressure regulator of this kind (Swedish patent document 344,749), in which the stamp on
den ene side er belastet med reguleringstrykket og på den annen side av atmosfæretrykket og av en regulerbar fjær. one side is loaded with the regulation pressure and on the other side by the atmospheric pressure and by an adjustable spring.
Denne utforming av trykkregulatoren har den ulempe at det er påkrevd med forholdsvis store og sterke fjærer, f.eks. vil det for et reguleringstrykk på 5 bar kreves fjær-krefter på omtrent 50 kg. This design of the pressure regulator has the disadvantage that relatively large and strong springs are required, e.g. for a regulation pressure of 5 bar, spring forces of approximately 50 kg are required.
Den oppgave som ligger til grunn, for oppfinnelsen The task underlying the invention
er å utforme trykkregulatoren slik at det kan anvendes vesent-lig mindre fjærer. is to design the pressure regulator so that significantly smaller springs can be used.
Trykkregulatoren ifblge oppfinnelsen erkarakterisert vedat stemplet er utformet som differensialstempel som avgrenser to kammere og at differensialstemplet i det ene kammer belastes med reguleringstrykk og i det andre kammer ved siden av fjærkraften med et konstant lufttrykk. The pressure regulator according to the invention is characterized by the fact that the piston is designed as a differential piston which delimits two chambers and that the differential piston in one chamber is loaded with regulating pressure and in the other chamber next to the spring force with a constant air pressure.
Oppfinnelsen skal i det folgende nærmere forklares ved hjelp av to utforelseseksempler som er fremstilt på teg-ningen, som viser: Fig. 1 et skjematisk riss av trykkregulatoren i henhold til et fbrste utforelseseksempel, og In the following, the invention will be explained in more detail with the help of two exemplary embodiments which are shown in the drawing, which show: Fig. 1 a schematic diagram of the pressure regulator according to a first exemplary embodiment, and
fig. 2 et skjematisk riss av trykkregulatoren i fig. 2 a schematic diagram of the pressure regulator i
henhold til et andre utfbrelseseksempel. according to a second embodiment.
I henhold til fig. 1 er trykkbegrensningsanordning-en 10 koplet til en mateledning 11 og et hovedstyreorgan 12 til en hovedluftledning 13. En trykkregulator 14 er på den ene side via en grenledning 15 koplet til en trykkbegrens-ningsanordning 10 og på den annen side via en annen grenledning 16 til hovedstyreorganet 12. Trykkregulatoren 14 har en trykkreguleringsventil som dannes av en ventiltallerken 17 som på den ene side samvirker med et stasjonært ventilsete 18 og på den annen side med et bevegelig ventilsete 19. Det bevegelige ventilsete 19 befinner seg ved enden av en stempelstang 20, som er festet til et differensialstempel, som består av et stort stempel 21 og et lite stempel 22. En fjær 23 avstotter seg på den ene side mot det lille stempel 22 og på den annen side mot en stotstang 24. Denne stotstang 24 trykkes ved hjelp av fjæren 23 mot en kamskive 25 som er festet til en dreibart lagret aksel 26. En forer-bremsearm 35 er festet til akselen 26 og tjener for betjening av den beskrevne trykkregulator 14.- Ventiltallerkenen 17 har en lufteboring 27 og er festet til et stempel 28. Et ovre ved hjelp av dette stempel 28 avgrenset kammer 29 samt et fbrst.e kammer 30, som befinner seg mellom ventiltallerken According to fig. 1, the pressure limiting device 10 is connected to a supply line 11 and a main control device 12 to a main air line 13. A pressure regulator 14 is on the one hand via a branch line 15 connected to a pressure limiting device 10 and on the other hand via another branch line 16 to the main control device 12. The pressure regulator 14 has a pressure control valve which is formed by a valve plate 17 which on the one hand cooperates with a stationary valve seat 18 and on the other hand with a movable valve seat 19. The movable valve seat 19 is located at the end of a piston rod 20, which is attached to a differential piston, which consists of a large piston 21 and a small piston 22. A spring 23 rests on one side against the small piston 22 and on the other side against a push rod 24. This push rod 24 is pressed by means of the spring 23 against a cam disc 25 which is attached to a rotatably supported shaft 26. A driver brake arm 35 is attached to the shaft 26 and serves to operate the described pressure regulator tor 14.- The valve disc 17 has an air bore 27 and is attached to a piston 28. An upper chamber 29 defined by this piston 28 as well as a first chamber 30, which is located between the valve disc
17 og det store stempel 21, er via grenledningen 16 forbundet . med hovedstyreorganet 12. Et andre kammer '31, som befinner seg mellom det ovre stempel 28 og ventiltallerkenen 17, samt et nedre kammer 32, som befinner seg nedenfor det lille stempel 22, er via grenledningen 15 forbundet med trykkbe-grensningsanordningen 10. Endelig er et midtre kammer 33, som befinner seg mellom det store og det lille stempel 21, henholdsvis 22, via en åpning 34 forbundet med atmosfæren. 17 and the large piston 21 are connected via branch line 16. with the main control member 12. A second chamber '31, which is located between the upper piston 28 and the valve plate 17, as well as a lower chamber 32, which is located below the small piston 22, is connected via the branch line 15 to the pressure limiting device 10. Finally, a middle chamber 33, which is located between the large and small piston 21, respectively 22, via an opening 34 connected to the atmosphere.
Den beskrevne trykkregulators virkemåte er som folger: Trykkbegrensingsanordningen 10 sorger for at den fra mate-ledningen 11 uttatte trykkluft alltid har en mest mulig konstant verdi, f.eks. 5 bar. I det andre kammer 31 samt i det nedre kammer 32 hersker dermed hele tiden et konstant trykk på 5 bar. The described pressure regulator's mode of operation is as follows: The pressure limiting device 10 ensures that the compressed air withdrawn from the supply line 11 always has the most constant possible value, e.g. 5 bars. In the second chamber 31 as well as in the lower chamber 32, a constant pressure of 5 bar prevails at all times.
Ved fullstendig frigjort bremse hersker også i hovedluftledningen 13 det maksimalt tillatelige trykk på 5 bar. For oppnåelse av dette trykk må hbvedstyreorganet 12 kunne When the brake is completely released, the maximum permissible pressure of 5 bar also prevails in the main air line 13. In order to achieve this pressure, the hbvedstyrorgan 12 must be able to
lede dette trykk inn i hovedluftledningen 13. Dette trykk på lead this pressure into the main air line 13. This pressure on
5 bar må derfor også herske i grenledningen 16, i det ovre kammer 29 samt i det forste kammer 30. Således hersker i det forste kammer 30 overfor det store stempel 21 og i det nedre kammer 32 nedenfor det lille stempel 22 det samme trykk. For at ikke noe trykkluft under disse trykkforhold skal kunne unnvike til atmosfæren fra det forste kammer 30 gjennom ven-tiltallerkenens 17 boring 27 må fjæren 23 forspennes tilsvarende sterkt. Denne forspenning oppnås ved at kamskiven 25 ved hjelp av fbrerbremsearmen 35 svinges til frigjorings-stilling. Svarende til de to stemplers 21 og 22 differanse kan fjæren 23 dimensjoneres forholdsvis liten. 5 bar must therefore also prevail in the branch line 16, in the upper chamber 29 and in the first chamber 30. Thus, the same pressure prevails in the first chamber 30 opposite the large piston 21 and in the lower chamber 32 below the small piston 22. In order that no compressed air under these pressure conditions can escape to the atmosphere from the first chamber 30 through the bore 27 of the valve plate 17, the spring 23 must be biased correspondingly strongly. This biasing is achieved by swinging the cam disc 25 to the release position with the help of the front brake arm 35. Corresponding to the difference between the two pistons 21 and 22, the spring 23 can be dimensioned relatively small.
For oppbremsing må trykket i hovedluftledningen 13 senkes. Svarende til det bnskede bremsetrinn svinges fbrerbremsearmen 35 og derved avspennes fjæren 23. Således minskes kraften som virker på det lille stempel_22_og på de to stempler 21, 22 vil senkes. Fra kammeret 30 kan gjennom boringen 27 luft unnvike til atmosfæren. Trykket i kammeret 30 vil derfor synke så.langt, til de krefter som ovenfra og nedenfra virker på differensialstemplet 21, 22 igjen er i balanse. Tilsvarende vil også trykket i hovedluftledningen 30 synke. For braking, the pressure in the main air line 13 must be lowered. Corresponding to the desired brake step, the spring brake arm 35 is swung and thereby the spring 23 is released. Thus the force acting on the small piston_22_ is reduced and on the two pistons 21, 22 will be lowered. From the chamber 30, air can escape to the atmosphere through the bore 27. The pressure in the chamber 30 will therefore drop until the forces acting on the differential piston 21, 22 from above and below are again in balance. Correspondingly, the pressure in the main air line 30 will also drop.
For frigjøringen av bremsen må trykket i hovedluftledningen 13 bkes. Svarende til det bnskede frigjbringstrinn svinges fbrerbremsearmen 35 og derved spennes fjæren 23. Således bkes kraften som virker på det. lille stempel 22 og To release the brake, the pressure in the main air line 13 must be released. Corresponding to the desired release step, the spring brake arm 35 is swung and thereby the spring 23 is tensioned. Thus, the force acting on it is bent. small stamp 22 and
de to stempler 21, 22 vil lbftes. Ventiltallerkenen 17 lbftes fra sitt sete 18 og trykkluft strbmmer fra det andre kammer 31 inn i det forste kammer 30. Trykket i kammeret 30 vil derfor stige helt til de krefter som ovenfra og nedenfra virker på differensialstemplet 21, 22 igjen er i balanse. Tilsvarende vil også trykket i hovedluftledningen 13 stige. the two pistons 21, 22 will be lbfted. The valve disc 17 is lifted from its seat 18 and compressed air flows from the second chamber 31 into the first chamber 30. The pressure in the chamber 30 will therefore rise until the forces acting on the differential piston 21, 22 from above and below are again in balance. Correspondingly, the pressure in the main air line 13 will also rise.
Når det gjelder utfbrelseseksemplet i henhold til fig. 2 er trykkfjæren 23 erstattet med en strekkfjær 36, i overensstemmelse dermed avstbtter seg en til strekkfjæren 36 festet stang 37 mot kamskivens 25 nedre side. Fjærens 36 strekkspenning kan dermed forandres likedan som trykkfjærens 23 trykkspenning og således kan trykket i hovedluftledningen As regards the embodiment according to fig. 2, the compression spring 23 is replaced by a tension spring 36, in accordance with this, a rod 37 attached to the tension spring 36 rests against the lower side of the cam disc 25. The tensile stress of the spring 36 can thus be changed in the same way as the compressive stress of the compression spring 23 and thus the pressure in the main air line can
13 styres. ' Med det for stemplene 21 og 22 viste stbrrelses- forhold kan det når det gjelder denne utforelsesform riktig-nok ikke oppnås noen trykklikhet i kammerne 30 og 32. Trykket i kammer 32 vil hele tiden være storre enn i kammer 30. 13 is managed. With the operating conditions shown for the pistons 21 and 22, as far as this embodiment is concerned, no pressure equality can be achieved in the chambers 30 and 32. The pressure in chamber 32 will always be greater than in chamber 30.
Claims (2)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH1091577A CH622742A5 (en) | 1977-09-07 | 1977-09-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
NO783043L true NO783043L (en) | 1979-03-08 |
Family
ID=4368177
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
NO783043A NO783043L (en) | 1977-09-07 | 1978-09-06 | PRESSURE CONTROLLER ON A DRAWER BRAKE VALVE IN AN INDIRECT ACTIVE PRESSURE AIR BRAKE |
Country Status (19)
Country | Link |
---|---|
EP (1) | EP0001135B1 (en) |
AT (1) | AT375606B (en) |
AU (1) | AU507693B1 (en) |
CH (1) | CH622742A5 (en) |
CS (1) | CS205056B2 (en) |
DD (1) | DD138628A5 (en) |
DE (1) | DE2860903D1 (en) |
DK (1) | DK379478A (en) |
ES (1) | ES473118A1 (en) |
FI (1) | FI63694C (en) |
GR (1) | GR64407B (en) |
HU (1) | HU177527B (en) |
IN (1) | IN148780B (en) |
IT (1) | IT1098495B (en) |
NL (1) | NL174810C (en) |
NO (1) | NO783043L (en) |
PL (1) | PL118848B1 (en) |
RO (1) | RO75429A (en) |
TR (1) | TR20019A (en) |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1155470B (en) * | 1960-06-11 | 1963-10-10 | Knorr Bremse Gmbh | Driver brake valve device for air brakes of rail vehicles |
DE1146520B (en) * | 1960-07-08 | 1963-04-04 | Westinghouse Bremsen Gmbh | Self-regulating driver brake valve for compressed air brake devices of rail vehicles |
-
1977
- 1977-09-07 CH CH1091577A patent/CH622742A5/de not_active IP Right Cessation
- 1977-10-24 NL NLAANVRAGE7711628,A patent/NL174810C/en not_active IP Right Cessation
-
1978
- 1978-08-17 GR GR57023A patent/GR64407B/en unknown
- 1978-08-21 EP EP78200144A patent/EP0001135B1/en not_active Expired
- 1978-08-21 DE DE7878200144T patent/DE2860903D1/en not_active Expired
- 1978-08-21 CS CS785464A patent/CS205056B2/en unknown
- 1978-08-24 AT AT0615978A patent/AT375606B/en not_active IP Right Cessation
- 1978-08-25 TR TR20019A patent/TR20019A/en unknown
- 1978-08-28 DK DK379478A patent/DK379478A/en not_active Application Discontinuation
- 1978-08-30 IN IN644/DEL/78A patent/IN148780B/en unknown
- 1978-08-31 FI FI782673A patent/FI63694C/en not_active IP Right Cessation
- 1978-09-01 AU AU39476/78A patent/AU507693B1/en not_active Expired
- 1978-09-04 RO RO7895105A patent/RO75429A/en unknown
- 1978-09-05 IT IT27311/78A patent/IT1098495B/en active
- 1978-09-06 HU HU78WE584A patent/HU177527B/en unknown
- 1978-09-06 PL PL1978209439A patent/PL118848B1/en unknown
- 1978-09-06 DD DD78207671A patent/DD138628A5/en unknown
- 1978-09-06 ES ES473118A patent/ES473118A1/en not_active Expired
- 1978-09-06 NO NO783043A patent/NO783043L/en unknown
Also Published As
Publication number | Publication date |
---|---|
AU507693B1 (en) | 1980-02-21 |
ATA615978A (en) | 1984-01-15 |
HU177527B (en) | 1981-10-28 |
RO75429A (en) | 1980-12-30 |
DD138628A5 (en) | 1979-11-14 |
PL209439A1 (en) | 1979-07-16 |
NL7711628A (en) | 1979-03-09 |
DE2860903D1 (en) | 1981-11-05 |
CH622742A5 (en) | 1981-04-30 |
FI63694C (en) | 1983-08-10 |
CS205056B2 (en) | 1981-04-30 |
FI782673A (en) | 1979-03-08 |
EP0001135B1 (en) | 1981-08-05 |
IT7827311A0 (en) | 1978-09-05 |
FI63694B (en) | 1983-04-29 |
NL174810B (en) | 1984-03-16 |
PL118848B1 (en) | 1981-10-31 |
GR64407B (en) | 1980-03-21 |
IN148780B (en) | 1981-06-13 |
EP0001135A1 (en) | 1979-03-21 |
TR20019A (en) | 1980-06-16 |
NL174810C (en) | 1984-08-16 |
ES473118A1 (en) | 1979-04-01 |
AT375606B (en) | 1984-08-27 |
DK379478A (en) | 1979-03-08 |
IT1098495B (en) | 1985-09-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US2161439A (en) | Control mechanism for hydraulic transmissions and pumps | |
US3425752A (en) | Air braking system for railway vehicles | |
US16760A (en) | Melodeon | |
NO783043L (en) | PRESSURE CONTROLLER ON A DRAWER BRAKE VALVE IN AN INDIRECT ACTIVE PRESSURE AIR BRAKE | |
KR850001986A (en) | Regulators installed on outlet connections of vessels such as gas containers | |
US2754843A (en) | Servomotor arrangement, more particularly for reducing valves | |
NO121114B (en) | ||
SE406893B (en) | DEVICE FOR ATTACHING A LOAD CARRIED OUT UNDER AN AIRCRAFT | |
US3353511A (en) | Operator assist device for sewing machines or the like | |
US2169629A (en) | Braking apparatus | |
NO794197L (en) | PRESSURE REGULATOR FOR A LINING VALVE IN AN INDIRECT EFFECTIVE PRESSURE BRAKE | |
NO149730B (en) | INDIRECT EFFECTIVE PRESSURE BRAKE | |
US4299428A (en) | Automatic load-dependent brake control device having wide range of pressure adjustment | |
US4304441A (en) | Variable load valve device having adjustable bias means to withhold proportional brake control during low level brake requirements | |
NO167078B (en) | ACCELERATING DEVICE BY INDIRECT EFFECTIVE PRESSURE BRAKES. | |
NO147982B (en) | DEVICE FOR INDIRECTLY EFFECTIVE LOADING COMPRESSIVE AIR BRAKE | |
DE311180C (en) | ||
US1029008A (en) | Treadle mechanism. | |
US17348A (en) | clarke | |
US1095261A (en) | Machine for use in the manufacture of boots and shoes. | |
NO119116B (en) | ||
US2155195A (en) | Adjustable thrust bearing for valve springs | |
DE890881C (en) | Air operated actuator | |
DE575774C (en) | Driver brake valve | |
DE79456C (en) | Grand piano mechanics |