US3093115A - Fluid actuated control mechanism for a brake and similar apparatus - Google Patents
Fluid actuated control mechanism for a brake and similar apparatus Download PDFInfo
- Publication number
- US3093115A US3093115A US3584A US358460A US3093115A US 3093115 A US3093115 A US 3093115A US 3584 A US3584 A US 3584A US 358460 A US358460 A US 358460A US 3093115 A US3093115 A US 3093115A
- Authority
- US
- United States
- Prior art keywords
- piston
- cylinder
- hub
- annular
- pistons
- 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
Links
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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
- B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
- B60T17/08—Brake cylinders other than ultimate actuators
- B60T17/10—Two or more cylinders acting on the same brake with means for rendering them effective selectively or successively, the number of effective cylinders being variable
Definitions
- the pistons In known dual action fluid pressure actuators of this type, the pistons have a very substantial axial length and thus occupy a good portion of the total length of the cylinder. To obtain the required actuating force with the thus relatively short available stroke, the diameters of the pistons and cylinders must be substantially increased. This increases the total area of contact between the cylinders and the pistons, requiring very accurate fitting of the parts for proper operation. In addition, the arrangements are bulky and cumbersome.
- the single figure is an axial sectional view of a dual action fluid pressure actuator embodying the invention.
- the fluid pressure actuator of the invention includes a cylinder 1 in which are mounted, for axial sliding movement, a service piston S and an emergency piston S
- a service pressure fluid inlet nipple 2 and an emergency pressure fluid inlet nipple 3 are mounted through the end wall F of cylinder 1, nipple 2 being disposed substantially coaxially of the cylinder and nipple 3 being offset radially from nipple 2.
- a relatively small diameter tubular rod or conduit 4 has its outer end seated in and connected in fluid tight relation to the nipple 2, and is disposed, with annular clearance, through a relatively larger diameter tubular rod or conduit 6, the annular clearance or passage between conduits or rods 4 and 6 being indicated at 5.
- a piston rod including generally tubular sleeve 7, extends through the other end of the cylinder 1 and a plug or diaphragm is secured in fluidatight relation in the inner end of sleeve 7.
- the conduit or tubular rod 6 is secured in fluid-tight relation in an axial recess in the end of plug or diaphragm 8, and the opposite end of tubular rod or conduit 6 is anchored, in fluid tight relation, in the central passage through the annular piston 8,.
- conduit 4 which is immov- "ice able relative to cylinder 1
- the inner end of conduit 4 terminates somewhat short of the inner end of conduit 6 and of the base of the recess in plug or diaphragm 8, to establish communication between the interior of conduit 4 and the annular space 5.
- a push rod P has its inner end seated in a concave crecess in the opposite end of the plug or diaphragm 8, and the outer end of push rod P is formed with an eye 10 for connection to the mechanism or apparatus to be actuated.
- a suitable packing 9 is disposed between the end wall of a reduced diameter extension from the cylinder 1 and the outer surface of tubular sleeve 7 of the piston rod.
- the service piston S and the emergency piston S have a very short axial length, the combined axial length occupying only a small portion of the total axial length of the cylinder 1.
- the axially very short peripheries of the two annular pistons S and S are indicated at M and M and it will be noted that, in each case, the axial length is only just sufficient to provide a suitable seat for the packing rings g and g of the two annular pistons.
- the service piston S which is nearer to the piston rod 7, has its web deflected out of an axial plane and extending toward the web of the emergency piston S to provide an abutment projecting axially beyond one end of the peripheral surface M Nevertheless, the extent of the deflection of the web of annular piston S is such that there is a clearance space between this web and the radially or diametrically extending web of the piston S This clearance space forms a first pressure chamber C, for connection to a source of fluidunder pressure for application of service fluid pressure.
- the emergency piston S has a central annular extension which extends outwardly toward end wall F a greater distance than does the rim portion M of piston S to abut the end wall F and maintain a "clearance between the latter and the rim portion M of the piston S
- the emergency application nipple 3 communicates with the second pressure chamber C which is the working chamber tor the emergency piston S
- a fluid tight packing g' is disposed between a second central annular exacts to force the emergency piston S toward the wall F and to force the service piston S inwardly, thus moving the push rod P, and the eye 10, toward the right as viewed in the drawing.
- the rims M and M are in abutment so that the inward movement of the emergency piston S is transmitted to the service piston S and thus to the piston rod 7 and the push rod P having the connection eye 10.
- the aforemen- 3 tioned coil spring restores the parts to the position shown in the drawing.
- the total surface area of contact between the pistons and the cylinder is greatly reduced, particularly in an axial direction.
- the degree of accurate machining involved is also greatly reduced.
- a dual action fluid pressure actuator for brakes and similar apparatus comprising, in combination, a relatively elongated cylinder; a first annular piston slidable axially in said cylinder, and having a relatively large diameter rim, a relatively smaller diameter hub, and a generally radially extending web interconnecting said rim and said hub; a piston rod extending through one end of said cylinder and having an outer end formed for connection to the apparatus to be actuated; a first tubular rod connected at one end to the inner end of said piston rod and having its opposite end connected to the inner end of said hub of said first piston and communicating with the opening through the latter; the outer end of the hub of said first piston having a substantially centrally axially extending annular recesstherein, and the major portion of the outer surface of the web of said first piston being substantially flush with the outer end of the hub thereof; a second annular piston slidable axially in said cylinder and disposed between said first piston and the opposite end of said cylinder said second piston having a relatively large
- said piston rod includinug a plug having an axial recess in which said one end of said first tubular rod is seated and secured and into which the inner end of said second tubular rod partially extends, a tubular sleeve embracing said plug and extending through such one end of said cylinder, and a push rod seated in a recess in the other end of said plug and having its outer end formed for such connection to the apparatus to be actuated.
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Actuator (AREA)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT1597259 | 1959-01-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3093115A true US3093115A (en) | 1963-06-11 |
Family
ID=11148412
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US3584A Expired - Lifetime US3093115A (en) | 1959-01-31 | 1960-01-20 | Fluid actuated control mechanism for a brake and similar apparatus |
Country Status (3)
Country | Link |
---|---|
US (1) | US3093115A (de) |
DE (1) | DE1185934B (de) |
FR (1) | FR1245144A (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3264951A (en) * | 1964-01-17 | 1966-08-09 | Berg Mfg & Sales Co | Brake actuator |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1387663A (fr) * | 1963-04-06 | 1965-01-29 | Magneti Marelli Spa | Dispositif à double effet, pour la commande de freins par un fluide sous pression |
DE1229863B (de) * | 1963-11-12 | 1966-12-01 | Westinghouse Bremsen Apparate | Druckmittelzweikreisbremse, insbesondere fuer Kraftfahrzeuge |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB625711A (en) * | 1947-05-08 | 1949-07-01 | Automotive Prod Co Ltd | Improvements in or relating to fluid pressure operated ram-and-cylinder devices |
GB705403A (en) * | 1951-04-23 | 1954-03-10 | Davey Paxman And Company Ltd | Improvements in or relating to the remote control of mechanisms |
GB743603A (en) * | 1954-05-25 | 1956-01-18 | Benton & Stone Ltd | Fluid-operated reciprocatory mechanisms |
US2831464A (en) * | 1954-02-19 | 1958-04-22 | Gen Motors Corp | Fluid pressure motor |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1558374A (en) * | 1924-09-08 | 1925-10-20 | Lengel Company | Air-brake mechanism |
DE735807C (de) * | 1941-09-30 | 1943-05-26 | Bosch Gmbh Robert | Staubabdichtung fuer Bremszylinder, insbesondere fuer Strassenfahrzeuge |
DE872453C (de) * | 1943-06-22 | 1953-04-02 | Bosch Gmbh Robert | Bremszylinder, insbesondere fuer Druckmittel-Kraftfahrzeugbremsen |
FR1146357A (fr) * | 1956-03-30 | 1957-11-12 | Westinghouse Freins & Signaux | Perfectionnements aux équipements de freinage pour véhicules sur rail ou sur route |
-
1959
- 1959-12-22 FR FR40015A patent/FR1245144A/fr not_active Expired
-
1960
- 1960-01-20 DE DEF30342A patent/DE1185934B/de active Pending
- 1960-01-20 US US3584A patent/US3093115A/en not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB625711A (en) * | 1947-05-08 | 1949-07-01 | Automotive Prod Co Ltd | Improvements in or relating to fluid pressure operated ram-and-cylinder devices |
GB705403A (en) * | 1951-04-23 | 1954-03-10 | Davey Paxman And Company Ltd | Improvements in or relating to the remote control of mechanisms |
US2831464A (en) * | 1954-02-19 | 1958-04-22 | Gen Motors Corp | Fluid pressure motor |
GB743603A (en) * | 1954-05-25 | 1956-01-18 | Benton & Stone Ltd | Fluid-operated reciprocatory mechanisms |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3264951A (en) * | 1964-01-17 | 1966-08-09 | Berg Mfg & Sales Co | Brake actuator |
Also Published As
Publication number | Publication date |
---|---|
DE1185934B (de) | 1965-01-21 |
FR1245144A (fr) | 1960-11-04 |
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