PatentDe  


Dokumentenidentifikation EP0759389 03.04.1997
EP-Veröffentlichungsnummer 0759389
Titel Magnet-Drehschieberventil
Anmelder Westinghouse Air Brake Co., Wilmerding, Pa., US
Erfinder Brillant, Daniel, Norristown, Pennsylvania 19401, US
Vertreter derzeit kein Vertreter bestellt
Vertragsstaaten DE, FR, GB, IT
Sprache des Dokument En
EP-Anmeldetag 17.06.1996
EP-Aktenzeichen 961096765
EP-Offenlegungsdatum 26.02.1997
Veröffentlichungstag im Patentblatt 03.04.1997
IPC-Hauptklasse B60T 15/00

Beschreibung[en]
FIELD OF THE INVENTION

This invention pertains to valves for control of fluids, and more particularly applies to air valves for controlling air to a brake cylinder in a railroad braking system.

BACKGROUND OF THE INVENTION

Valves for control of compressed air to brake cylinders in railroad braking systems generally have three basic positions:

  • (1) A position in which air is admitted from a supply of compressed air to the brake cylinder, this compressed air serving to apply the brakes.
  • (2) A position in which air is exhausted from the brake cylinder, which causes the brakes to be released.
  • (3) A position, referred to as the lap position, in which air is neither supplied to, nor exhausted from the brake cylinder. This position is used to maintain the brake application forces approximately constant.

In the past, this function has been provided by a valve having a linear displacement spool. The spool is positioned inside a cylindrical housing and is moved axially to change from one valve position to another. An example of this is United States Patent 4,773,447 entitled ELECTROMAGNETIC VALVE, invented by Asaji Imanaka and Mitsuhiro Ikeda.

Valves of this type have the disadvantage that very precise machining is required, particularly in the bores where sealing is provided. Some of these valves require dynamic O-rings, which are subject to rubbing each time the valve position is changed. Some of these valves employ diaphragms. These valves require precise guiding, and various parts are needed for clamping the diaphragms.

Valves of the linear displacement type also have a large number of parts which must be assembled, and which must be disassembled for overhaul.

A gate valve in which fluid pressure is applied behind a sealing means is described in US-A-3,166,291 (which forms a basis for the preamble of claim 1) entitled "Valve construction and Method". In US-A-3,590,872 a rotary valve is described in which a disc control member having a confined flow passage is rotatable within a housing to bring the flow passage into alignment with an inlet and an outlet opening on opposite sides of the housing.

SUMMARY OF INVENTION

According to a first aspect, this invention provides a valve for controlling flow of air or other fluid from a supply to a destination. A first and a second member are required, each having an internal space for containing the fluid. Fluid from the supply is admitted to the internal space in the first member, and the internal space in the second member is connected to the destination. Each member has a surface for sealing with a port in it communicating with its internal space. The sealing surfaces are adjacent each other, and the two members move relative to each other with a shearing motion. A seal is provided on one of the members. The seal has an annular recess surrounding the port in the surface. A conformable sealing member having an annular form is placed in the annular recess. A spring is placed underneath it to press it against the surface of the other member. An O-ring is placed between the outer diameter of the conformable sealing member and the inside of the annular recess. This prevents leakage outside of the conformable sealing member. It also permits pressure of the fluid to be exerted on the conformable sealing member, so the pressure available for sealing increases with the pressure of the fluid. The force due to the fluid pressure is added to the force due to the spring. It should be noted that the O-ring is subjected to very little wear, because relative motion does not occur with every cycle of the valve. The conformable sealing member moves relative to the O-ring only as the conformable sealing member is worn away.

In an additional aspect, this invention provides a valve for controlling flow of a fluid from a supply to a volume wherein pressure is to be controlled, and for exhausting fluid from the volume to an exhaust port. A housing (which may have a plurality of components, such as a main body and a cover) has three ports: a supply port, a delivery port, and an exhaust port. A rotor is placed inside the housing, and means are provided for controlling its angular position. In a first position, a flowpath is provided through the rotor to join the supply port and the delivery port. In a second angular position, a flowpath is provided through the rotor to join the delivery port to the exhaust port. The rotor may also be positioned in a third angular position, which is a lap position in which no flowpaths are provided between ports. Seals between rotor and housing are provided to prevent loss of fluid from the supply port, loss from the delivery port, and loss to the exhaust port.

In a further aspect, this invention provides a valve for controlling flow of a fluid between a supply and a volume in which pressure is to be controlled, and between the volume and an exhaust port. In a first position, the valve provides connection between the supply and the volume where pressure is to be controlled. In a second position, the valve provides connection between the volume where pressure is to be controlled and exhaust. In a third position, which is a lap position, no flowpaths are established through the valve. The valve has a housing (which may have a plurality of components, such as a main body and a cover). A rotor is placed inside the housing. Inside the housing there are two axisymmetric surfaces, at two different axial positions. These may be planar surfaces perpendicular to the axis of the rotor. Seals are provided on the rotor pressing against these axisymmetric surfaces to prevent flow of fluid past either of the two axial positions. Fluid from the supply is introduced into the inside of the housing at an axial position between that of the two seals. A gap is provided between the housing and the rotor in the space between the two seals, so that fluid can flow around the rotor inside the housing. From this gap, the fluid flows into an internal space in the rotor. The rotor has an axisymmetric surface (which may be a planar surface perpendicular to its axis). A port is provided on this surface which communicates with the internal space inside the rotor. Two additional ports are provided in this surface, and these are connected to each other through a second passageway inside the rotor. The housing has an additional axisymmetric surface (which may be a planar surface perpendicular to the axis of the rotor). Two ports are provided on this surface, one is a delivery port connected to the volume in which pressure is to be controlled, and the other is for exhaust. Annular seals are provided surrounding each of the three ports on the axisymmetric surface of the rotor and seal against the axisymmetric surface of the housing. An annular seal is also provided surrounding the delivery port on the housing and seals against the axisymmetric surface on the rotor. Means are provided for positioning the rotor in three different positions. In one position, fluid from the first internal space in the rotor, which is the fluid being supplied, flows into the delivery port on the housing. In a second position, the supply space in the rotor is sealed off, and the delivery port is connected through the second passageway in the rotor to the exhaust port. In a third position, which is a lap position, each of the ports on these surfaces is sealed off, so that no flow to or from the delivery port occurs.

OBJECTS OF THE INVENTION

It is, therefore, a primary object of the present invention to provide a railroad air brake valve which is highly reliable.

Another object of the present invention is to provide a railroad air brake valve which requires a minimum amount of precision machining.

Yet another object of the present invention is to provide a railroad airbrake valve which is lightweight.

Still another object of the present invention is to provide a railroad air brake which does not require frequent overhaul.

Even another object of the present invention is to eliminate the need for precise machining of bores and replace it with the simpler machining of planar faces.

In addition to the various objects and advantages of the present invention described above, it should be noted that various other objects and advantages of the present invention will become more readily apparent to those persons who are skilled in the electric valve art from the following detailed description of the invention, particularly, when such description is taken in conjunction with the attached drawing(s) and with the appended claims.

BRIEF DESCRIPTION OF DRAWINGS

  • Figure 1 shows a sealing means which is used in the various embodiments of this invention.
  • Figure 2 shows a median section of one embodiment of this invention.
  • Figure 3 shows a perspective view of a rotor used in the embodiment of figure 2.
  • Figure 4 shows an end view of the housing in the embodiment of figure 2.
  • Figure 5 shows a median section of another embodiment of this invention.
  • Figure 6 shows an exploded view of the embodiment shown in figure 5.

BRIEF DESCRIPTION OF INVENTION AND PRESENTLY-PREFERRED EMBODIMENT

Prior to proceeding to a more detailed description of various embodiments of the present invention, for the sake of clarity and understanding of the invention, it should be noted that identical components having identical functions in each of the accompanying drawings have been identified with identical reference numerals throughout each of the several Figures illustrated herein.

Reference is now made to the drawings, figures 1 through 6. Figure 1 shows a seal which is used in this invention. A first component 2 has a first surface 13 and a fluid passage 4 communicating with a first port 3 in the first surface 13. The first component 2 is sealed against a second component 201 having a passage 203 communicating with a port 205 in a second surface 202. Surface 202 is characterized as being smooth. Preferably, it may be made by machining and polishing. The two components 2 and 201 can be moved relative to each other by a shearing motion in the plane of the surface 202. The seal provides a passage between fluid passage 4 in first component 2 and fluid passage 203 in second component 201. When the two components 2 and 201 are relatively moved by a shearing motion, passage 203 no longer lines up with passage 4. The seal prevents leakage of fluid from passage 4.

An annular recess 10 is formed in first component 2, surrounding the passage 4. The annular recess 10 has an inner diameter 9 and an outer diameter 11. A spring 6 is placed in recess 10 and a conformable sealing member 8 which has an axisymmetric form, is placed over the spring 6. Conformable sealing member 8 has an inner diameter 5 and an outer diameter 7. Preferably, sealing member 8 may be made of a soft, low friction material such as Teflon. It has a surface 16 for sealing against surface 202. An O-ring 18 is placed on the outside diameter 7 of the sealing member 8 to seal with the outer diameter 11 of the recess 10. ( The O-ring 18 could also be positioned in the surface at the outer diameter 11. ) The O-ring 18 prevents leakage of fluid around the outside diameter 7 of the sealing member 8. Another annular recess 12 may be formed at the bottom of the recess 10, and an annular recess 14 may be formed on the conformable sealing member 8. These annular recesses 12 and 14 position the spring 6. The device is assembled by bringing second component 201 and first component 2 together so that sealing member 8 and spring 6 are pressed into recess 10. The spring 6 may be a coil spring, a spring washer, or other resilient means.

Means (not shown) provide a relative shearing motion between the two components 2 and 201, so that in one position, passage 203 lines up with passage 4, while in another position, passage 4 is blocked off by surface 202, sealing means 8 and O-ring 18. Spring 6 keeps sealing member 8 pressed against surface 202 to prevent leakage.

It should be noted that in this design, fluid pressure in passage 4 is confined underneath member 8, and cooperates with the spring 6 to press the sealing member 8 against the surface 202. If the pressure of the fluid in passage 4 increases, the fluid force on sealing member 8 is increased. Hence, a high contact pressure between surface 16 of the sealing member 8 and surface 202 of second component 201 is provided when the fluid pressure is high. A low contact pressure is provided by spring 6 when the fluid pressure is low.

Figure 2 shows an embodiment of this invention which is a valve assembly employing six seals of the type shown in figure 1. This valve has three positions. In one position, it admits fluid from supply port 40 and passes it to discharge port 60. In another position, the discharge port 60 is exhausted through exhaust port 70. The third position is a lap position in which the passages are blocked off.

This embodiment of the invention has a housing 22 and a housing cover 24. A rotor 28, having axis 1, is placed inside the housing. Rotor 28 is turned by rotary electromagnetic means 32 through an optional flexible coupling 30 and bearing 34, which is kept in place by retaining ring 35. Bearing 34 and retaining ring 35 serve in part as a rotary bearing means for connecting rotor 28 and housing 22. Control of its angular position is facilitated by a torsion spring 36. The housing 22 is closed off at its right end by a coil cover 26.

Fluid from the fluid supply (not shown) is admitted to the housing through port 40. It passes through filter 42 and port 44 into gap 45 between housing 22 and rotor 28. A seal, generally shown as 92 is provided to the right of gap 45, pressing against machined face 90 on the inside of the housing 22. A seal, generally shown as 82 is provided to the left of gap 45, pressing against machined face 80 on the inside of the housing 22. Seals 82 and 92 are large-diameter versions of the seal shown in figure 1. Each of these passes entirely around the axis of the valve.

A transverse passageway 46 in the rotor passes fluid from gap 45 to passage 48 in the rotor. The transverse passage 46 also serves to equalize pressures on opposite sides of the rotor 28 in gap 45. Passage 48 terminates on the left face of the rotor at port 49.

In the relative angular position shown in figure 2, the supply passage 48 in the rotor 28 is lined up with the discharge passage 60.

A seal consisting of conformable sealing member 50, sealed on its outer diameter by O-ring 54, and pressed by spring 52, seals against smooth surface 25 on the housing cover 24. This seal prevents loss of fluid from passageway 48: Likewise, a seal consisting of conformable member 62 with O-ring 66 and pressed by spring 64 surrounds the discharge port 60 in the housing cover 24. This seal prevents loss of fluid from the discharge port when the valve is in the lap position in which port 60 is closed off by surface 29 on the rotor 28. An exhaust port 70 in housing cover 24 is provided.

Static O-ring 72 prevents loss of fluid between housing 22 and housing cover 24.

Figure 3 is a perspective of the rotor used in the embodiment shown in figure 2. Two transverse passages 46 are shown. The transverse passages 46 permit fluid to flow transversely through the rotor, and equalize pressures around the circumference of the rotor.

Supply port 49 shown in this figure, is also shown in figure 2. When this valve is in the supply position, as shown in Figure 2, supply port 49 is lined up with discharge passage 60. Additionally, exhaust ports 100 and 102 are shown in the rotor. These are connected by an internal passageway (not shown) in the rotor. When the valve is in the exhaust position, these ports are lined up with the discharge port 60 and exhaust port 70.

Torsion spring 36, which cooperates with rotary electromagnetic means 32 to establish angular position is shown in this figure.

Figure 4 shows the housing cover, the view being taken from the left side in figure 2. The delivery port is denoted 60 and the exhaust port is denoted 70. Torsional spring 36 is shown, as are the rotary stops 110 and 120, which limit the angular motion.

This embodiment of the invention works as follows. When no current is supplied to the rotary electromagnetic means, it generates zero torque. The rotary spring 36 then positions the rotor in the delivery position, which is the position shown in figure 2. When a large current is supplied to the rotary electromagnetic means, the rotor moves until it is stopped by rotary stops 110 and 120. In this position, the delivery port 60 and exhaust port 70 in the cover communicate with ports 100 and 102 on the rotor. In this position, fluid is exhausted from the volume (not shown) which is supplied by the delivery port 60.

When a current of intermediate magnitude is supplied to the rotary electromagnetic means, the rotor is moved to a position in which the torque due to torsion spring 36 balances the torque from the electromagnetic means. In this position, none of the ports are lined up. This is the lap position.

The rotary electromagnetic means may be a DC motor, an AC-DC motor, or a rotary solenoid. The electromagnetic means are selected to demand very little power in the stalled condition.

In a variation of this embodiment, a step motor is used in place of the type of electromagnetic means suggested above. The step motor changes its angle in accordance with the number of pulses supplied to it. In this case, the torsional spring 36 would not be required.

Figure 5 shows an embodiment of this invention which is a valve assembly employing three seals of the type shown in figure 1. This valve has three positions. In one position, it admits fluid from supply port 140 and passes it to discharge port 160. In another position, the discharge port 160 is exhausted through exhaust port 170. The third position is a lap position in which the passages are blocked off.

This embodiment of the invention has a housing 122 and a housing cover 124. A rotor 128, having axis 101, is placed inside the housing. Clearance, with allowance for manufacturing tolerances, is provided by the gap 123 between the housing 122 and the rotor 128. Rotor 128 is turned by rotary electromagnetic means 132 through an optional flexible coupling 130 and bearing 134, which is kept in place by retaining ring 135. Bearing 134 and retaining ring 135 serve in part as a rotary bearing means for connecting rotor 128 and housing 122. Control of its angular position is facilitated by a torsion spring 136. The housing 122 is closed off at its right end by a bearing mount 137 and coil cover, 126.

Fluid from the fluid supply (not shown) is admitted to the housing through port 140. It passes through filter 142 and port 144 into gap 145 between housing 122 and rotor 128. A seal, generally shown as 192 is provided to the right of gap 145, pressing against machined face 190 on the inside of the housing 122. Seal 192 is a version of the seal shown in figure 1. This seal passes entirely around the axis of the valve, 101.

Transverse passage 146 serves to equalize pressures on opposite sides of the rotor 128 in gap 145.

In the relative angular position shown in figure 5, the axial supply passage 149 in the rotor 128 is lined up with the discharge port 160.

A seal consisting of conformable member 162 with O-ring 166 and pressed by spring 164 surrounds the discharge port 160 in the housing cover 124. This seals against the machined surface of the rotor, 129. This seal prevents flow of fluid from gap 123 to the discharge port 160.

An exhaust port 170 in housing cover 124 is also provided. This port has seal consisting of conformable sealing member 172 with O-ring 176 and spring 174. This seals against the machined surface of the rotor, 129. This seal prevents flow of fluid from gap 123 to the exhaust port.

Static O-ring 112 prevents loss of fluid between housing 122 and housing cover 124.

Figure 6 is an exploded perspective of the rotor used in the embodiment shown in figure 5. Housing 122 has supply port 140. Rotor 128 is disposed inside housing 122. A seal between rotor 128 and an inner surface of housing 122 is indicated generally as 192. This prevents flow to the right in the figure, in the space between the rotor and the housing. The end of passage 149 through the rotor is shown in this figure. The rotor is mounted by bearing 134 which is retained by retaining ring 135 and located in bearing mount 137. The rotor is driven by rotary electromagnetic means 132, which is in the coil cover 126.

The housing cover 124 has delivery port 160. This port is sealed against the face of the rotor by conformable sealing member 162 which is sealed on its outside diameter by O-ring 166, and pressed against the rotor by spring 164.

The housing cover 124 also has exhaust port 170. This port is sealed against the face of the rotor by conformable sealing member 172 which is sealed on its outside diameter by O-ring 176 and pressed against the rotor by spring 174.

When this valve is in the supply position, as shown in Figure 5, supply passage 149 is lined up with discharge port 160. Additionally, exhaust ports 200 and 202 are shown in the rotor. These are connected by an internal passageway in the rotor.

This passageway may be provided by drilling diametrically through the rotor, an end of this passageway being shown as 203. This passageway would be completed by drilling axially from port 200 and 202 to meet this passageway, and by plugging the ends of this passageway; one end of this passageway being shown at 203.

When the valve is in the exhaust position, port 200 is lined up with the delivery port 160, and port 202 is lined up with exhaust port 170. Since port 200 and 202 are joined by a passageway through the rotor, this causes the pressure in the delivery port 160 to be exhausted out the exhaust port 170.

This embodiment of the invention works as follows. When no current is supplied to the rotary electromagnetic means, it generates zero torque. The rotary spring 136 then positions the rotor in the delivery position, which is the position shown in figure 5. When a large current is supplied to the rotary electromagnetic means, the rotor moves until it is stopped by rotary stops (not shown). In this position, the delivery port 160 and exhaust port 170 in the cover communicate with ports 200 and 202 on the rotor. In this position, fluid is exhausted from the volume (not shown) which is supplied by the delivery port 160.

When a current of intermediate magnitude is supplied to the rotary electromagnetic means, the rotor is moved to a position in which the torque due to torsion spring 136 balances the torque from the electromagnetic means. In this position, none of the ports are lined up. This is the lap position.

The rotary electromagnetic means may be a DC motor, an AC-DC motor, or a rotary solenoid. The electromagnetic means are selected to demand very little power in the stalled condition.

In a variation of this embodiment, a step motor is used in place of the type of electromagnetic means suggested above. The step motor changes its angle in accordance with the number of pulses supplied to it. In this case, the torsional spring 136 would not be required.

The embodiment of the invention shown in figures 5 and 6 is the presently most preferred embodiment.

Now, discussing the invention more generally, in a first aspect, this invention provides a valve for controlling flow of air or other fluid from a supply to a destination. A first and a second component are required, each having an internal space for containing the fluid. Fluid from the supply is admitted to the internal space in the first component, and the internal space in the second component is connected to the destination. Each component has a surface for sealing with a port in it communicating with its internal space. The sealing surfaces are adjacent each other, and the two components move relative to each other with a shearing motion.

A seal is provided on one of the components. The seal has an annular recess surrounding the port in the surface. A conformable sealing member having an annular form is placed in the annular recess. A spring is placed underneath it to press it against the surface of the other component. The spring may be a coil spring, a spring washer, or any other spring which can exert an axial force on the annular conformable sealing member. An O-ring is placed between the outer diameter of the conformable sealing member and the inside of the annular recess. This prevents leakage outside of the conformable sealing member. It also permits pressure of the fluid to be exerted on the conformable sealing member, so the pressure available for sealing increases with the pressure of the fluid. The force due to the fluid pressure is added to the force due to the spring.

It should be noted that the O-ring is subjected to very little wear, because relative motion does not occur with every cycle of the valve. The conformable sealing member moves relative to the O-ring only as the conformable sealing member is worn away.

The relative shearing motion of this valve may be provided by a relative rotation of the two components. In that case, the sealing surface on the component not having the conformable sealing member is an axisymmetric surface. A simple example of such a surface is a flat, planar surface, which is perpendicular to the axis of relative rotation of the two members. It is desirable for this surface to be a smooth, machined surface, which may be polished. The conformable sealing member should be made of a low-friction material which is softer than the surface on which it seals.

The two relatively-moving components of this valve may be positioned relative to each other through a rotary bearing. electromagnetic means may be used to provide the motion.

In an additional aspect, this invention provides a valve for controlling flow of a fluid from a supply to a volume wherein pressure is to be controlled, and for exhausting fluid from the volume to an exhaust port. A housing (which may have a plurality of components, such as a main body and a cover) has three ports: a supply port, a delivery port, and an exhaust port. A rotor is placed inside the housing, and means are provided for controlling its angular position. In a first position, a flowpath is provided through the rotor to join the supply port and the delivery port. In a second angular position, a flowpath is provided through the rotor to join the delivery port to the exhaust port. The rotor may also be positioned in a third angular position, which is a lap position in which no flowpaths are provided between ports.

A seal is provided which prevents loss of fluid from the supply port, a seal is provided which prevents loss of fluid from the delivery port, and a seal is provided which prevents loss of fluid to the exhaust port.

The seal which prevents loss of fluid from the supply port can be located on either the rotor or the housing, and it may pass completely around the axis of the rotor.

The seal which prevents loss of fluid from the supply port may consist of an annular recess in either the rotor or the housing, and a conformable sealing member in the recess. A spring pushes the conformable sealing member toward the sealing surface, and an O-ring on the outside of the conformable sealing member prevents loss of fluid through the recess outside of the conformable sealing member.

In like manner, the seal which prevents loss of fluid from the delivery port may consist of an annular recess passing around the delivery port. A conformable sealing member is placed in the recess. A spring pushes the conformable sealing member toward the sealing surface on the rotor, and an O-ring on the outside of the conformable sealing member prevents loss of fluid through the recess outside of the conformable sealing member.

In like manner, the seal which prevents loss of fluid to the exhaust port may consist of an annular recess passing around the exhaust port. A conformable sealing member is placed in the recess. A spring pushes the conformable sealing member toward the sealing surface on the rotor, and an O-ring on the outside of the conformable sealing member prevents loss of fluid through the recess outside of the conformable sealing member.

The sealing surface on the rotor may be a planar surface perpendicular to the axis of the rotor.

The positioning of the rotor relative to the housing may be accomplished by a rotary bearing means, and rotation of the rotor may be accomplished by a rotary electromagnetic means.

To define the angle of the exhaust position, a stop to limit the rotary motion may be provided. To define a range of angles for the lap position, a torsion spring may be used, and the current supplied to the rotary electromagnetic means may be adjusted to balance the spring torque at the desired lap position.

In a further aspect, this invention provides a valve for controlling flow of a fluid between a supply and a volume in which pressure is to be controlled, and between the volume and an exhaust port. In a first position, the valve provides connection between the supply and the volume where pressure is to be controlled. In a second position, the valve provides connection between the volume where pressure is to be controlled an exhaust. In a third position, which is a lap position, no flowpaths are established through the valve.

The valve has a housing (which may have a plurality of components, such as a main body and a cover). A rotor is placed inside the housing. Inside the housing there are two axisymmetric surfaces, at two different axial positions. These may be planar surfaces perpendicular to the axis of the rotor. Seals are provided on the rotor pressing against these axisymmetric surfaces to prevent flow of fluid past either of the two axial positions. Fluid from the supply is introduced into the inside of the housing at an axial position between that of the two seals. A gap is provided between the housing and the rotor in the space between the two seals, so that fluid can flow around the rotor inside the housing. From this gap, the fluid flows into an internal space in the rotor.

The rotor has an axisymmetric surface (which may be a planar surface perpendicular to its axis). A port is provided on this surface which communicates with the internal space inside the rotor. Two additional ports are provided in this surface, and these are connected to each other through a second passageway inside the rotor.

The housing has an additional axisymmetric surface (which may be a planar surface perpendicular to the axis of the rotor). Two ports are provided on this surface, one is a delivery port connected to the volume in which pressure is to be controlled, and the other is for exhaust.

Annular seals are provided surrounding each of the three ports on the axisymmetric surface of the rotor, and these seal against the axisymmetric surface of the housing. An annular seal is also provided surrounding the delivery port on the housing, and this seals against the axisymmetric surface on the rotor.

Means are provided for positioning the rotor in three different positions. In one position, fluid from the first internal space in the rotor, which is the fluid being supplied, flows into the delivery port on the housing. In a second position, the supply space in the rotor is sealed off, and the delivery port is connected through the second passageway in the rotor to the exhaust port. In a third position, which is a lap position, each of the ports on these surfaces is sealed off, so that no flow to or from the delivery port occurs.

Equalization of pressures around the circumference of the rotor may be provided by ports which pass transversely across the rotor.

While the presently preferred embodiment, and various additional alternative embodiments for carrying out the instant invention has been set forth in detail in accordance with the Patent Act, those persons skilled in the electric valve art to which this invention pertains will recognize various alternative ways of practicing the invention without departing from the spirit and scope of the appended claims.

Accordingly, to promote the progress of science and useful arts, I secure for myself by Letters Patent for a limited time exclusive rights to all subject matter embraced by the following claims.


Anspruch[de]
  1. Eigenverschleiß kompensierendes Ventil zum Steuern des Fluidflusses von einer Quelle zu einem Ziel, wobei das Ventil umfaßt:
    • (i) ein erstes Element (2, 28) mit wenigstens einem darin ausgebildeten ersten Innenraum (4, 48);
    • (ii) eine erste Oberfläche (13, 29) auf dem ersten Element (2, 28), wobei die erste Oberfläche (13, 29) wenigstens eine erste Öffnung (3, 49) enthält, welche mit dem wenigstens einem ersten Innenraum (4, 48) in Verbindung steht, der in dem ersten Element (2, 28) ausgebildet ist;
    • (iii) ein zweites Element (201, 24) mit wenigstens einem darin ausgebildeten zweiten Innenraum (203);
    • (iv) eine zweite Oberfläche (202, 25) auf dem zweiten Element, wobei die zweite Oberfläche wenigstens eine zweite Öffnung (205) enthält, welche mit dem wenigstens einen zweiten Innenraum in Verbindung steht, der in dem zweiten Element ausgebildet ist, wobei die erste Oberfläche (13, 29) auf dem ersten Element (2, 28) und die zweite Oberfläche (202, 25) auf dem zweiten Element (201, 24) in einem von unmittelbarer Nähe und Kontakt stehen, wobei die erste Oberfläche und die zweite Oberfläche so geformt sind, daß sie eine relative Scherungsbewegung dazwischen zulassen, während die erste Oberfläche und die zweite Oberfläche in einem von unmittelbarer Nähe und Kontakt stehen;
    • (v) eine Versorgungsöffnung (40) mit einer Verbindung zu dem ersten Innenraum und zur Verbindung zu der Quelle eines derartigen Fluids;
    • (vi) eine Ausgabeöffnung (60) mit einer Verbindung zu dem zweiten Innenraum und zur Verbindung mit dem Ziel eines derartigen Fluids; wobei das Ventil
    gekennzeichnet ist, durch
    • (a) eine Einrichtung (32) zum Drehen des ersten Elementes (28) so, daß eine relative Scherungsbewegung zwischen dem ersten Element (28) und dem zweiten Element (24) erzeugt wird;
    • (b) eine ringförmige Aussparung (10), welche in dem ersten Element (2, 28) ausgebildet ist, wobei die ringförmige Aussparung die erste Öffnung (3, 49) umgibt, während die ringförmige Aussparung ein Außendurchmesser (11) und Innendurchmesser (9) aufweist;
    • (c) eine ringförmige Dichtungseinrichtung (8, 50), welche in der ringförmigen Aussparung (10) angeordnet ist, wobei die ringförmige Dichtungseinrichtung einen Außendurchmesser (7) und einen Innendurchmesser (5) aufweist, und das ringförmige Dichtungselement aus einem Material mit niedriger Reibung besteht, das weicher als wenigstens ein Abschnitt der zweiten Oberfläche (202, 25) ist, wobei der Innendurchmesser (5) der ringförmigen Dichtungseinrichtung (8, 50) und der Innendurchmesser (9) der Aussparung (10) eine Übertragung des Fluiddrucks dazwischen erlauben;
    • (d) eine federnde Einrichtung (6, 52), welche in der ringförmigen Aussparung angeordnet ist, wobei die federnde Einrichtung die ringförmige Dichtungseinrichtung (8, 50) vorspannt, um sie gegen die zweite Oberfläche auf dem zweiten Element (201, 24) zu drücken;
    • (e) einen O-Ring (18, 54), welcher zwischen dem Außendurchmesser (7) der ringförmigen Dichtungseinrichtung (8, 50) und dem Außendurchmesser (11) der ringförmigen Aussparung (10) angeordnet ist, wobei der O-Ring dazu dient, einen Fluidfluß zwischen dem Außendurchmesser des ringförmigen Dichtungselementes und dem Außendurchmesser der ringförmigen Aussparung zu verhindern;
    wobei die zweite Öffnung (205) einen Durchmesser kleiner als der Außendurchmesser (7) der ringförmigen Dichtungseinrichtung (8, 50) besitzt;

    wobei die Einrichtung (32) für die Erzeugung der relativen Scherungsbewegung zwischen dem ersten Element (2, 28) und dem zweiten Element (201, 24) wenigstens eine erste Stellung bereitstellt, in welchem die erste Öffnung (3) mit der zweiten Öffnung (205) in Verbindung steht, und eine zweite Stellung, in welcher die erste Öffnung durch die zweite Oberfläche auf dem zweiten Element verschlossen ist, wobei die ringförmige Dichtungseinrichtung (8, 50) einen Fluidfluß zwischen der ersten Oberfläche (13, 29) und der zweiten Oberfläche (202, 25) verhindert;

    wobei ein Druck eines derartigen Fluids mit der federnden Einrichtung (6, 52) zusammenwirkt, um die ringförmige Abdichtungseinrichtung (8, 50) auf die zweite Oberfläche (202, 25) mit einer Kraft zu drücken, welche mit zunehmendem Wert eines derartigen Druckes zunimmt.
  2. Ventil nach Anspruch 1, wobei die zweite Oberfläche (202, 25) des zweiten Elementes (201, 24) wenigstens als ein Teilabschnitt einer Umdrehungsoberfläche ausgebildet ist.
  3. Ventil nach Anspruch 3, wobei die zweite Oberfläche (202, 25) des zweiten Elementes (201, 24) als eine ebene Oberfläche ausgebildet ist.
  4. Ventil nach Anspruch 2, wobei die zweite Oberfläche (202, 25) des zweiten Elementes (201, 24) glatt ist.
  5. Ventil nach Anspruch 2, wobei die Einrichtung (32) für die Erzeugung der Scherungsbewegung zwischen dem ersten Element (2, 28) und dem zweiten Element (201, 24) wenigstens eine Rotationslagerungseinrichtung enthält, wobei die Rotationslagerungseinrichtung das erste Element mit dem zweiten Element verbindet.
  6. Ventil nach Anspruch 2, wobei die Einrichtung (32) für die Erzeugung der Scherungsbewegung zwischen dem ersten Element (2, 28) und dem zweiten Element (201, 24) eine elektromagnetische Rotationseinrichtung ist.
  7. Ventil nach Anspruch 1, wobei die federnde Einrichtung (16, 52) eine von einer Spiralfeder und einem Federring ist.
Anspruch[en]
  1. A self wear compensating valve for controlling flow of a fluid from a source to a destination, said valve comprising:
    • (i) a first member (2,28) having at least one first internal space (4,48) formed therein;
    • (ii) a first surface (13,29) on said first member, (2, 28), said first surface (13,29) having at least one first port (3,49) communicating with said at least one first internal space (4,48) formed in said first member (2,28);
    • (iii) a second member (201,24) having at least one second internal space (203) formed therein;
    • (iv) a second surface (202,25) on said second member, said second surface having at least one second port (205) communicating with said at least one second internal space formed in said second member, said first surface (13,29) on said first member (2,28) and said second surface (202,25) on said second member (201,24) being disposed in one of close proximity and contact, said first surface and said second surface being formed so as to permit a relative shearing motion therebetween, while maintaining said first surface and said second surface in one of close proximity and contact;
    • (v) a supply port (40) having connection to said first internal space and for connection to said source of such fluid;
    • (vi) a discharge port (60) having connection to said second internal space and for connection to said destination of such fluid; said valve
       characterized by
    • (a) means (32) for rotating said first member (28) so as to provide said relative shearing motion between said first member (28) and said second member (24),
    • (b) an annular recess (10) formed in said first member (2,28), said annular recess surrounding said first port (3,49), said annular recess having an outer diameter (11) and an inner diameter (9);
    • (c) an annular sealing means (8,50) disposed in said annular recess (10), said annular sealing means having an outer diameter (7) and an inner diameter (5), said annular sealing means being made of a low-friction material softer than at least a portion of said second surface (202,25) said inner diameter (5) of said annular sealing means (8,50) and said inner diameter (9) of said recess (10) permitting fluid pressure communication therebetween;
    • (d) resilient means (6,52) disposed in said annular recess, said resilient means biasing said annular sealing means (8,50) to press against said second surface on said second member (201,24);
    • (e) an O-ring (18,54) disposed between said outer diameter (7) of said annular sealing means (8,50) and said outer diameter (11) of said annular recess (10), said O-ring serving to prevent fluid flow between said outer diameter of said annular sealing means and said outer diameter of said annular recess;
       said second port (205) having a diameter smaller than said outer diameter (7) of said annular sealing means (8,50);

       said means (32) for providing said relative shearing motion between said first member (2,28) and said second member (201,24) providing at least a first position wherein said first port (3) communicates with said second port (205), and a second position wherein said first port is closed off by said second surface on said second member, said annular sealing means (8,50) preventing fluid flow between said first surface (13,29) and said second surface (202,25);

       a pressure of such fluid cooperating with said resilient means (6,52) to bias said annular sealing means (8,50) towards said second surface (202,25) with a force that increases with increasing value of such pressure.
  2. A valve according to claim 1 wherein said second surface (202,25) of said second member (201,24) is formed as at least a portion of a surface of revolution.
  3. A valve according to claim 2 wherein said second surface (202,25) of said second member (201,24) is formed as a planar surface.
  4. A valve according to claim 2 wherein said second surface (202,25) of said second member (201,24) is smooth.
  5. A valve according to claim 2 wherein said means (32) for providing said shearing motion between said first member (2,28) and said second member (201,24) includes at least one rotary bearing means, said rotary bearing means connecting said first member to said second member.
  6. A valve according to claim 2 wherein said means (32) for providing said shearing motion between said first member (2,28) and said second member (201,24) is a rotary electromagnetic means.
  7. A valve according to claim 1 wherein said resilient means (16,52) is one of a coil spring and a spring washer.
Anspruch[fr]
  1. Robinet à compensation automatique d'usure destiné au réglage de la circulation d'un fluide d'une source et une destination, le robinet comprenant :
    • (i) un premier organe (2, 28) ayant au moins un premier espace (4, 48) formé à l'intérieur,
    • (ii) une première surface (13, 29) placée sur le premier organe (2, 28), la première surface (13, 29) ayant au moins un premier orifice (3, 49) qui communique avec le premier espace interne au moins (4, 48) formé dans le premier organe (2, 28),
    • (iii) un second organe (201, 24) ayant au moins un second espace interne (203) formé à l'intérieur,
    • (iv) une seconde surface (202, 25) placée sur le second organe, la seconde surface ayant au moins un second orifice (205) qui communique avec le second espace interne au moins formé dans le second organe, la première surface (13, 29) du premier organe (2, 28) et la seconde surface (202, 25) du second organe (201, 24) étant très proches ou en contact, la première surface du premier organe et la seconde surface du second organe étant formées afin qu'elles permettent un mouvement de cisaillement entre elles, avec maintien de la première surface et de la seconde surface afin qu'elles soient très proches ou en contact,
    • (v) un orifice d'alimentation (40) connecté au premier espace interne et destiné à être connecté à la source de fluide,
    • (vi) un orifice de décharge (60) connecté au second espace interne et destiné à être connecté à la destination du fluide, le robinet étant caractérisé par
      • (a) un dispositif (32) destiné à faire tourner le premier organe (28) afin qu'il crée le mouvement relatif de cisaillement entre le premier organe (28) et le second organe (24),
      • (b) une cavité annulaire (10) formée dans le premier organe (2, 28), la cavité annulaire entourant le premier orifice (3, 49), la cavité annulaire ayant un diamètre externe (11) et un diamètre interne (9),
      • (c) un dispositif annulaire d'étanchéité (8, 50) disposé dans la cavité annulaire (10), le dispositif annulaire d'étanchéité ayant un diamètre externe (7) et un diamètre interne (5), le dispositif annulaire d'étanchéité étant formé d'un matériau à faible coefficient de frottement plus tendre qu'une partie au moins de la seconde surface (202, 25), le diamètre interne (5) du dispositif annulaire d'étanchéité (8, 50) et le diamètre interne (9) de la cavité (10) permettant la communication de la pression du fluide,
      • (d) un dispositif élastique (6, 52) disposé dans la cavité annulaire, le dispositif élastique rappelant le dispositif annulaire d'étanchéité (8, 50) afin qu'il exerce une pression contre la seconde surface sur le second organe (201, 24),
      • (e) un joint torique (18, 54) disposé entre le diamètre externe (7) du dispositif annulaire d'étanchéité (8, 50) et le diamètre externe (11) de la cavité annulaire (10), le joint torique étant utilisé pour empêcher la circulation du fluide entre le diamètre externe du dispositif annulaire d'étanchéité et le diamètre externe de la cavité annulaire,
       le second orifice (205) ayant un diamètre inférieur au diamètre externe (7) du dispositif annulaire d'étanchéité (8, 50),

       le dispositif (32) destiné à créer le mouvement relatif de cisaillement entre le premier organe (2, 28) et le second organe (201, 24) donnant au moins une première position dans laquelle le premier orifice (3) communique avec le second orifice (205), et une seconde position dans laquelle le premier orifice est fermé par la seconde surface disposée sur le second organe, le dispositif annulaire d'étanchéité (8, 50) empêchant la circulation du fluide entre la première surface (13, 29) et la seconde surface (202, 25), et

       la pression du fluide coopérant avec le dispositif élastique (6, 52) pour rappeler le dispositif annulaire d'étanchéité (8, 50) vers la seconde surface (202, 25) avec une force qui augmente lorsque la valeur de la pression augmente.
  2. Robinet selon la revendication 1, dans lequel la seconde surface (202, 25) du second organe (201, 24) est formée par une partie au moins d'une surface de révolution.
  3. Robinet selon la revendication 2, dans lequel la seconde surface (202, 25) du second organe (201, 24) est formée par une surface plane.
  4. Robinet selon la revendication 2, dans lequel la seconde surface (202, 25) du second organe (201, 24) est lisse.
  5. Robinet selon la revendication 2, dans lequel le dispositif (32) destiné à assurer le mouvement de cisaillement entre le premier organe (2, 28) et le second organe (201, 24) comprend au moins un dispositif à palier rotatif, le dispositif à palier rotatif raccordant le premier organe au second.
  6. Robinet selon la revendication 2, dans lequel le dispositif (32) destiné à donner le mouvement de cisaillement entre le premier organe (2, 28) et le second organe (201, 24) est un dispositif électromagnétique de rotation.
  7. Robinet selon la revendication 1, dans lequel le dispositif élastique (16, 52) est un dispositif choisi parmi un ressort hélicoïdal et une rondelle élastique.






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