DE2946190A1 - COUPLING FOR FLUIDS - Google Patents

Description

description

The invention relates to a fluid coupling that is particularly suitable is to control the escape of a fluid from a pressure vessel ^ u which contains pressurized gas. The pressure vessel, for which the coupling is advantageously applicable, take gases under

2:; chr high pressure on, e.g. B. at a pressure of over 200 kp / cm (3000 pounds per square inch).

According to the invention, a coupling is proposed which has a fastening or connection device for a pressure vessel for pneumatic fluids, the connection device having a locking device which is in a locking position is movable to connect the pressure vessel to the connection device, or in a release position to to release the pressure vessel from the connection device. A manually adjustable control device is also provided, with which the locking device is adjustable, this manually adjustable control device at the same time Valve for controlling the escape of the fluid from the pressure vessel controls. The manually adjustable control device can be formed by a rotatably mounted cam, the control surface of which acts on the locking device and the valve to move these parts in the longitudinal direction of the connecting device. The cam can be rotatably mounted in the walls of the connection device, the axis of rotation of the cam not coincides with the axis of the connecting device. Made by hand adjustable control device enables the production of a flow path to a consumer point only when the \ rretierungseinrichtung is in its locking position. On the other hand, the locking device can only be in ? inor unlocked position when the flow path from the pressure vessel to the consumer point is closed and lcr in the system between the valve and the consumer point

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prevailing pressure is relieved.

The locking device can be movable in the longitudinal direction have tubular part which is slidably mounted in the housing is and on its outside a first cylinder surface as well a second cylindrical surface with a smaller diameter than the diameter of the first cylinder surface, where i the both cylinder surfaces connected to each other via an inclined surface are. An inner section of the housing can be designed in such a way that it connects to the first and the second cylindrical surface as well as the inclined surface cooperates. The inclined surface has a series of cages that are circular in cross section which are connected to the inner surface of the longitudinally displaceable part, each cage having a locking body, such as z. B. contains a ball which is received within the longitudinally movable tubular member when this is in the unlocked position, but is moved radially into the locking position when the tubular Veil is moved in the longitudinal direction and the inner wall of the housing rests against the inclined surface. The neck of the pressure vessel has an undercut, e.g. B. a circumferential groove, in we .eher the locking body are added. The longitudinally movable part can be resiliently pressed into the locking position are, and the rotatably mounted cam can be moved in three operating positions: a first operating position in which the longitudinally displaceable part is held in the unlocked position, a second operating position in which the cam has no influence on the position of the longitudinally displaceable part, and a third operating position, in which the cam is displaceable in the longitudinal direction Part holds in the locking or locking position.

If a pressure vessel is connected to a consumer point, care must be taken to ensure that the valve is operated no leak occurs. A beneficial way to

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Ensuring an effective seal is that the pressure prevailing in the system is used to control the valve actuation device to move into a position in which the pressure is used to create an additional connection to the To seal the atmosphere.

For this purpose it can be provided that an actuating device, which is provided for actuating the valve of the pressure vessel, with a piston movable in the longitudinal direction a central bore and a valve actuating member which is also provided with a central bore and is displaceable in the longitudinal direction which is slidably mounted in a guide channel and wherein the valve actuating member has a Has enlarged head which cooperates with the central bore of the piston and with the guide channel. How it works of the valve is such that when the bore of the piston cooperates with the enlarged head, its central bore is in communication with the pressure vessel, the area difference between the area at the end of the valve actuator, which faces the pressure vessel and the face of the piston causes the piston and valve actuator be moved to the pressure vessel until the enlarged head comes to rest against the guide channel.

The guide channel is preferably an integral component of the tubular part movable in the longitudinal direction, which is a Forms part of the locking device, and the piston is preferably slidable within the longitudinally movable tubular part stored.

The construction may be such that the piston with the valve actuator to one in the neck of the pressure vessel arranged valve moves when the neck of the pressure vessel is locked in the housing and the cam of the second operating position moved into the third operating position

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will. If this is arranged in the neck of the pressure vessel Valve is actuated, then a first flow path is duich the central bores of the longitudinally movable valve actuator and the piston is made to a consumer or delivery point, and the valve actuating gliod is converted the pistons move until the enlarged head constricts the guide channel comes to the plant.

When the cam moves from the third operating position into the two to Operating position is moved, there are two operating states. The first operating state occurs while the cam acts on the piston to move it away from the pressure vessel, thereby that the seal between the piston and the enlarged head is broken and the pressure which is in the system prevails between the valve and the consumer point, is relieved to the atmosphere through this opening. The second The operating state in which the cam acts on the piston in order to move the piston away from the pressure vessel results in that the enlarged head is entiernt from the guide channel and the piston and valve actuator of the Move the pressure vessel away. If that's in the throat of the pressure age located valve is closed, then causes the area difference between the central bore of the piston in which the pressure acts on the enlarged head, and the bore cm other end of the valve actuator that the seal between the piston and the enlarged head is broken and moving the valve actuator to the pressure vessel. This results in the in the system between the valve and the pressure prevailing at the consumer or feed point is relieved into the atmosphere through this opening.

The bore in the piston can receive a damper which, for. B. is formed by a porous sintered body to noise the Cc to reduce the flowing gas, which both from the pressure vessel to the consumer point and from the consumer point pours into the atmosphere.

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Further features, details and advantages of the invention emerge from the following description of exemplary embodiments based on the drawing. Show in it:

Fig. 1 is a front view of the pressure vessel according to the invention;

Figure 2 is a schematic view of the various positions through which the cam operated lever moves can be, as well as the housing in which the pressure vessel is received;

3 is a schematic sectional view of the cam and the housing for receiving the cam;

Fig. 4 is a sectional view along the line B-B of Fig. 3 with the pressure vessel removably received in the housing;

FIG. 5 shows a sectional view along the line AA according to FIG. 3 with the pressure vessel firmly mounted and sealed in the housing; FIG.

6 shows a sectional view along the line B-B according to FIG. 3 with the pressure vessel fixedly mounted in the housing, wherein however, the pressure vessel is connected to the feed point, and

7 shows a schematic perspective exploded view of the housing in which the pressure vessel is received will.

In the figure 1, a pressure vessel 1 is shown, which in the fully charged state gas at a pressure of approximately 560 kp / cm (8000 pounds per square inch psi). The pressure vessel has a neck 2 which has a first cylindrical surface on its outer surface 3, a groove 4 and a second cylinder surface 5 as well as a section 6 with one facing away from the first cylinder surface 3 Has direction decreasing diameter.

The pressure vessel 1 can be fastened to a fastening device 200 as shown in FIGS. 4, 5 and 6

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As will be described below, the fastening device has Means with which the pressure vessel in a certain Position is lockable, as well as means for opening the valve arranged in the neck of the pressure vessel, so that the Content can get to a foodstuff. Some specific parts the fastening device are in schematic perspective An exploded view is shown in FIG. 7.

Figure 2 shows a cam control lever 7, which is on an annular Housing part 8 is mounted. The cam control lever 7 rotates around the axis 9 and can be in three operating positions are rotated, which are indicated by the arrows 10, 11 and 12. The operating control unit indicated by the arrow 10 should are referred to as "bottle release position", the operating position indicated by the arrow 11 as "closed position" and the operating position marked by the arrow 12 as the "open position".

The annular housing 8 has an axis 13 which the /.chse 9 does not cut. The annular housing 8 has an upper tubular portion 14, a cylinder portion 15 in which a cam 16 is rotatably mounted (see Fig. 3), a cylinder portion 17 and a cylinder portion 18, which is a larger Having outer diameter than the cylinder sections 14 and 17.

From Figure 3 it can be seen that the cam control lever "· has a molded ring section 19 and a molded cylinder section 20 with a smaller diameter than the ring section 19, in which an annular groove 21 is provided, and a cylinder section 22 which is connected to the Cylinder section 20 is connected via the cam 16, and a zylinderförniigen threaded connector 23 which has a smaller diameter than the cylinder section 22 Zy.

The cylindrical pipe part 15 has bores in its jacket and 25, which serve to accommodate the cylinder parts 20 and 22, respectively.

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Eie bores 24 and 25 are arranged so that the axis 9 about which the cam 16 rotates, not the axis 13 of the annular Housing 8 cuts, but is arranged at a distance d from this axis. The bore 2 5 has an annular groove 26, and seals 27 and 28 are arranged in the annular grooves 21 and 26, respectively.

A shoulder 28a of the ring section 19 cooperates with a shoulder 29 of the cylinder section 15, and a nut 30 is screwed onto the cylinder connector 23 and acts on a surface 31 of the cylinder section 15.

A display device is provided which has a bore 32 which is arranged in the shoulder 29 and in which a spring 33 is received, which presses a ball 34 resiliently against the shoulder 28a. There are two recesses in the shoulder 28a 34a (only one of which is shown), which cooperate with the ball 34 when the cam 16 is either in the "open position" or in the "closed position".

Fig. 4 is a sectional view taken along line B-B of fig. 3 and shows that the pressure vessel 1 is freely along the Axis 13 can be moved (the illustration shows the "P'laschen release position"). On the inner surface of the tubular Cylinder section 18 is an internal thread 39. A tubular insert 40 has an external thread 41, which in the internal thread 39 of the tubular cylinder section 18 is screwed in. The tubular insert 40 abuts the shoulder, which delimits the inner end of the tubular cylinder section 18, and its inner edge has a bevel 42 on.

Inside the annular housing 8 are a piston 35 and a sleeve 36. The outer surface of the sleeve 36 interacts with the Inner surface 37 of the annular housing 8 together. The bushing 36 has bores 38 through which the cam 16 engages. The socket 36 is resiliently counteracted by means of a spring 101

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pressed the cylinder portion 18. In the area of the tubular Cylinder section 18, the socket 36 has a series of passages 43, each containing a locking ball 44, the Diameter of the wall thickness of the socket 36 corresponds. The outside diameter of the bushing 36 decreases behind the section in which the passages 43 are arranged, and the bushing interacts with the inner surface of the tubular insert 40 in this area. A wall 45 is located transversely in the bore of the bushing 36 in the area between the bores 38 and the passages 43 which carries a stop 47, and the wall and the stop have a central bore 46 with a seat 48. Through the wall 45 extends a ring of through bores 104.

The piston 36 has a tubular shape and is on the inner surface the bush 36 slidably mounted. The piston 35 has an end face 103 and bores 49 through which the cam 1 <i reaches through, the walls of the bores 49 interacting with the cam 16.

The outer surface of the piston 35 has in the area of the stop :; 47 an annular groove 50 in which a seal 100 is arranged. The inside diameter of the piston 35 is larger than the outside diameter of the stop 47.

See through the bore of the piston 35 extends in the area between the bores 49 and the annular groove 50 a wall 51, which contains a stepped bore, the first portion 52 of which opens into a seat 53 and the second portion 54 of which is a larger one Has diameter and a damper 55 receives.

In the bore 46 of the wall 45 there is a valve actuating member in the axial direction 56 movable, which has a thickened rounded head 57 and a central bore 58. Head 57 has a seat 105 which cooperates with the seat 48 and a seat 59 which cooperates with the seat 53. On rOm

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The end of the valve operating member 56 opposite the head 57 is the central bore 58 on the outside of the valve operating member arranged diametrical slots 60 connected to the outer surface, and the valve actuator 56 has a point 102 at its end.

The neck 2 of the pressure vessel 1 has a at its outer end Section 61 with a decreasing diameter, which opens into a bore 62 which is connected to the valve actuating member 56 cooperates and which has an annular groove 63 with a seal 64 arranged therein. At that end of the bore 62, which is opposite to the portion 61 with the decreasing diameter, a seat 65 is provided.

A ball 66 is pressed against the seat 65 by means of a spring 67 (see Fig. 5) to seal the pressure vessel 1 when it is not in use.

It is now the mode of operation of the device according to the invention to be discribed.

When the cam control lever 7 is in the "bottle release position" (see FIG. 4), the cam 16 holds the bushing 36 against the spring force of the spring 101, so that the locking balls 44 align with the inner surface of the socket 36. The neck 2 of the pressure vessel 1 can then be introduced unhindered into the tubular cylinder section 18 of the bushing 36. A twisting motion of the cam control lever 7 in the "closed position" shown in FIG in the direction of the pressure vessel 1, so that the Rnstkugoln 44 move along the bevel 42 of the tubular insert 40 and possibly against the inner surface of the tubular insert 40 create. In this position they cooperate with the groove 4 of the neck 2, so that in this arrangement the locking balls 4 4 on a smaller inner diameter than the first cylinder surface

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3 and the second cylindrical surface 5 of the outer surface of the neck 2 is arranged are. If the pressure vessel 1 and the neck 2 Ln are in the "closed position", then it is not possible to use the To pull parts out of the fastening device, since dab ^ i the Bushing 36 in the direction of the force of spring 101 against cam 16 would be moved. It is possible to use the neck 2 of the pressure vessel 1 to be inserted into the cylinder section 15 when the Noc: ciistrolever 7 is in the "closed position". We ·! the section 6 of the neck 2 with the decreasing diameter gey> n die Locking balls 44 pressed and forcibly moves the bushing 36 against it the force of the spring 101 to the locking balls 44 along of bevel 42 begin to move. At the point in time at which the locking balls 44 are arranged on an inner diameter which corresponds to the diameter of the second cylinder surface 5, the bushing 36 stops moving until the groove 4 of the neck 2 cooperates with the locking balls 44 and the socket under the Influence of the spring 101 in the direction of the pressure vessel 1 move ι lets until the walls of the bores 38 touch the cam 16, as shown in FIG.

A rotary movement of the cam control lever 7 from the "closed position" in the "open position", as shown in Figure 6, causes the cam 16 against the opposite Surface of the bores 38 pushes to keep the socket 36 in place to lock in relation to the pressure vessel 1. The rotational movement of the cam 16 also causes the piston 35 to move in the direction moves to the pressure vessel 1, and while the piston 35 moves, the seat 53 contacts the seat 59 of the enlarged rounded Head 57 of valve actuator 56. Another Rotational movement of the cam 16 in the "open position" cause that the tip 102 of the valve actuator 56 against the ball 66, which is located in the neck 2, and lifts it off the Si.z 65.

In this way, the interior of the pressure vessel 1 with

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oiner feed point 68 connected via the diametrical Slots 60, the central bore 58 of the valve operating member> 6, the first bore section 52, the second bore section > 4 with the damper 55 arranged therein, around the cam 16 and through the tubular piston 35.

If the SpoiscstolIe 68 is under pressure, then the end face is 103 at the end of the piston 35 on which the pressure acts, ■ greater than the area of the tip 102 of the valve operating member > 6, on which the same pressure acts. The force of the spring 67, which acts on the ball 66, and the resulting force, which acts on the piston 35, causes the piston in "direction: ium pressure vessel 1 to the seat 105 of the enlarged rounded Moves the head 57 and interacts with the seat 48 of the wall 45. The walls of the bores 49 of the piston 35 are now from «Learn cam 16 released.

As can be seen from FIGS. 2 and 3, a pressure indicator in the form of a Bourdon tube is located on the cam control lever 7 {Ohre 69 is provided, which over a channel 70 of the ring section 19 of the valve actuating lever and via a channel 71 through the cylinder section 20 can be acted upon with pressure.

When the cam control lever 7 from the "open position" to the "Closed position" is moved, then the piston 35 and the valve actuator 56 can perform two movements.

The first movement is that the rounded head 57 remains on the seat 53 while the piston 35 is removed from the pressure vessel 1 is pulled away by the cam 16 until the ball 66 reaches the seat 65 i-r. When this happens, the force of the spring 67 drops, which acts on the tip 102, and there on a first area of the rounded head 57, which is delimited by the bore section> 2, and a second area, which is from the tip 102 ■ is formed, the same pressures act and the first area is larger

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than the second range, the valve operating member moves 56 to the pressure vessel 1, whereby the feed point 68 is connected to the atmosphere, which is rounded off Head 57 and in the bores 104 of the wall 45 is located.

The second movement is that while the piston 35 is pulled away, the rounded head 57 on the seat 48 in contact with the seat 105 remains, since the force dos acting on the rounded head 57 pressure, which is a function of the bore portion 52 is greater than the combined forces of the pressure and the spring 67 acting on the tip 1C2 works. Once the seat 59 is separated from the seat 53, the feed point 68 wire to atmosphere as previously described vented towards and the valve actuator moves toward piston 35.

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Claims (1)

Expectations λ .J coupling for a fluid with a tubular housing, which has at its one end a connection device for receiving the neck with a valve of a pressure vessel arranged therein, a locking device being provided in the connection device for locking the neck in the connection device and in the tubular housing a cam is arranged which is rotatable from the outside of the housing a \ v. \ in order to move a valve actuating member in the axial direction, characterized in that the locking device has a bushing (36) which the valve actuating member (35,56 ) and is also movable in the axial direction by the cam (16) so that the locking device is locked when the cam is in the valve open position (12). 030024/0662 ORIGINAL INSPECTED 2. Coupling according to claim 1, characterized in that the valve operating member has a first part (35) which is in engagement with the cam, and a second part (56) which is provided for valve actuation, the two Parts are axially displaceable relative to one another, and that a flow path (60,58,52,55) from the connection device to one Exit (68) of the housing is formed when the cam is in the valve open position (12), while a flow path (see Fig. 5) between the exit (68) and the atmosphere is produced when the cam is in a middle position (11), which is between the valve actuation position and «In a position (10) is provided in which the locking device is unlocked (see Fig. 4). J. Coupling according to claim 1 or 2, characterized in that the parts of the valve actuating device (35,56) in corresponding Bores of the bush (36) are axially slidably mounted. \. Coupling according to one of Claims 1 to 3, characterized in that the first part (35) of the valve actuating member 3 has an axial bore (52) with a seat (53), while the second part (56) has a head (57) which is movable against the seat (53). ~>. Coupling according to one of Claims 1 to 4, characterized in that that the cam (16) is formed by a cam rod which extends through the housing bore and bores (38,49) in the bushing (36) or the valve actuating member (35) extends through. 5. Coupling according to claim 5, characterized in that the axis of rotation (9) of the cam rod is perpendicular and offset to The longitudinal axis (13) of the tubular housing is arranged. 030024/0662 29Λ6 1 Γι 7. Coupling according to one of claims 1 to 6, characterized in that that the socket (36) radial bores (43) with dar.n arranged balls (44) and that the housing bore of the tubular housing is stepped (42) so that the balls (Ί4) forcibly moved radially inward when the bushing (36) is moved by the cam (16) as soon as the cam is out of the Release position (10, see Fig. 4) is moved into the Ventilöffnungsstellunq (12, see Fig. 6). 030024/0662