Classifications

• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D16/00—Control of fluid pressure
  • G05D16/20—Control of fluid pressure characterised by the use of electric means
  • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
  • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
  • G05D16/2024—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means the throttling means being a multiple-way valve
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/2496—Self-proportioning or correlating systems
  • Y10T137/2559—Self-controlled branched flow systems
  • Y10T137/2574—Bypass or relief controlled by main line fluid condition
  • Y10T137/2605—Pressure responsive
  • Y10T137/2607—With pressure reducing inlet valve
  • Y10T137/261—Relief port through common sensing means
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/8593—Systems
  • Y10T137/86919—Sequentially closing and opening alternately seating flow controllers

Definitions

• the present invention relates to a pressure regulator which is subjected to the action of a proportional force, for example to that of a proportional magnet, and which comprises a valve cage which comprises a primary connection, a secondary connection and a deaerator connection. and two valve elements which are arranged coaxially with respect to each other, are guided so as to be able to move in the valve cage and can be subjected to the action of the adjusting stuffing, the first of which being controlled a bowl-shaped valve seat formed in the valve cage and connecting the primary side to the secondary side and closes it in the rest and deaeration position and, on the other hand, opens it for passage into the working position while the second valve element is applied, in the rest position, as in the working position, on a seat surface of the first valve element and, in the area of this seat surface, prevents any deaeration by an element valve to the deaeration connection but, on the other hand, in the deaeration and separation position with the first valve element, clears the passage between this valve element and the
• a pressure regulator of this type is known in which the first valve element is constituted by a head mounted at the lower end of a relatively long tubular rod which, at its upper end, has a seat surface for the second element valve which also has the shape of a valve head and which is subjected from the top to the proportional adjusting force.
• the second valve element is located in the deaeration zone which, in this pressure regulator, must be made upwards, towards the correcting member.
• the connection for the secondary pressure is located at the lower end of the valve cage and is arranged coaxially with respect to the two valve elements.
• the connection for the primary pressure is located along the axial length between the connections for the secondary pressure and the deaerator and leads to a torcoidal chamber.
• the object of the invention is to produce a pressure regulator of the type initially defined which makes it possible to use only reduced adjusting forces for high pressures and high flow rates of pressure medium and is suitable in all cases for large nominal passage sections, up to 20 mm for example.
• the pressure regulator according to the invention makes it possible to deal with high pressures and high flow rates while requiring only slight adjustment forces.
• the proportional adjustment force is obtained by means of proportional magnets
• these can, thanks to the invention, be extraordinarily small, light, inexpensive and compact and the device also has the advantage that in this pressure regulator according to the invention, the adjustment force necessary in each case is completely independent of the nominal passage section provided for the valve.
• the adjusting force only depends on the differential pressure surface of the second valve element. This can be changed and chosen without difficulty to be adapted to the circumstances.
• Another advantage is that the pressure regulator also allows deaeration in a direction opposite to that of the correcting member, for example proportional magnets.
• Figure 1 is a schematic section of a pressure regulator constituting a first embodiment and shown in the rest position after obtaining the prescribed secondary pressure.
• Figure 2 is a section on a smaller scale corresponding to Figure 1 and showing the pressure regulator in a working position during adjustment.
• Figure 3 is a schematic section similar to that of Figure 2 showing the pressure regulator during the adjustment operation.
• Figure 4 is a schematic section corresponding substantially to that of Figure 1 and showing a pressure regulator constituting a second embodiment, in the rest position.
• the pressure regulator which constitutes the first embodiment shown in FIGS. 1 to 3 is a 3/2 way seat valve. It can be operated using a proportional adjustment stuffing F to make the adjustment.
• the proportional adjusting force F of any magnitude is for example a magnetic force, an elastic force, a pneumatic, and / or hydraulic or mechanical force and acts in the direction of the arrow F. It is particularly advantageous that this adjusting force F is provided by a proportional magnet 10 which, together with the pressure regulator, constitutes the adjustment device.
• the regulator is subjected to the action of the electric force, of the proportional magnet 10 which acts in the direction of the arrow F.
• the pressure regulator comprises a valve cage 11 which comprises three connections, namely a connection 12 for the primary pressure P1, a connection 13 for the secondary pressure P2 and a connection 14 for deaeration P3.
• a valve cage 11 which comprises three connections, namely a connection 12 for the primary pressure P1, a connection 13 for the secondary pressure P2 and a connection 14 for deaeration P3.
• two valve elements 15 and 35 guided and held so as to be able to move, are arranged coaxially with respect to each other and placed one behind the other on the same axis .
• the two valve elements 15, 35 can be subjected to the action of the adjusting force F.
• the first valve element 15 controls a valve seat 16 constituted by a bowl 17 formed in the valve cage 11.
• the bowl 17 separates a lower toroidal chamber 18 connected to the connector 12 for the primary pressure P1, from a tariff chamber upper 19 connected to connection 13 for secondary pressure P2.
• the valve seat 16 When the valve seat 16 is moved away from the first valve element 15 (FIG. 2) the valve seat 16 connects the toroidal chamber 13 situated on the primary side to the toroidal chamber 19 situated on the secondary side.
• this passage in the region of the valve seat 16 is, on the other hand, closed.
• the second valve member 35 In the rest position shown in Figure 1 and in the working position shown in Figure 2, the second valve member 35 is supported axially on a seat surface 20 of the first valve member 15 and, in the area of this seat surface 20 prevents any deaeration of the interior in the direction of the toroidal chamber 21 which is connected to the connector 14 intended for deaeration.
• This seat surface 20 of the first valve element 15 for this second suopape element 35 which is situated above, and on which the latter can bear, is placed in the axial zone of the seat surface 22 of the first valve element.
• valve 15 which cooperates with the bowl 17 of the valve cage 11.
• the seat surface 20 and the seat surface 22 of the first valve element 15 lie in a common diametrical plane.
• the second surface element 3o comprises, at its lower end shown in FIGS. 1 to 3 and facing the seat surface 20 of the first valve element 15, a bowl 35 constituting the valve seat corresponding to the seat surface 20. This bowl 36 allows the second valve element 35 to bear essentially in linear contact on the seat surface 20 of the first valve element 15.
• the second valve element 35 comprises a cylindrical casing 37 comprising an interior chamber 38 open at its two ends.
• the interior chamber 33 is open in the axial direction.
• the cylindrical envelope 37 has radial ribs or similar centering devices which delimit between them passages 39 allowing the connection between the interior chamber 38 and the toroidal chamber 21.
• This arrangement allows, by the inner chamber 36 and formed in the valve element 35, open at its two ends, to ensure, in the ventilation position indicated in FIG. 3, deaeration of the toroidal chamber 19 on the secondary side P2, in the direction of the toroidal chamber 21 and the deaeration connection 14.
• the first valve element 15 comprises a cylindrical casing 23 which is coaxial with the cylindrical casing 37 and also has an interior chamber 24 open at its two ends.
• the aeration is carried out by the second valve element 35, in the manner already indicated. It is however also possible to provide deaeration by the first valve element 15, deaeration can then be carried out from the end of the interior chamber 24, where the seat surface 20 and the seat surface are located. of valve 22, towards the opposite lower end, the valve cage 11 having to comprise in this case the connector 14 intended for deaeration, located below the first valve element 15.
• the end of the cylindrical casing 23 which is turned towards second valve element 35 and which is located at the top in FIGS.
• the first valve element 15 comprises a ring 25 which, on its upper side, has a seal 26 applied to the insert, the ring 25, and above all the seal 26 which it carries, comprise on the axial side facing the second valve element 35, the seat surface 20 intended for the second valve element 35 and, in addition, the seat surface 22 corresponding to the bowl 17 of the valve cage 11.
• the first valve element 15 is made so as not to be subjected to pressure.
• the axial surface acting in the axial direction which is subjected to the primary pressure P1 and which, in the axial direction, is in the valve cage 11 opposite the valve seat 16 is at the same time large and even slightly larger than the axial surface which is also subjected to the primary pressure P1 and which, in the axial direction, is turned towards the valve seat 16.
• This dimensioning gives a differential surface, which, under the action of the pressure primary P1, gives a closing force directed in the opposite direction to the adjusting force F.
• the valve element 15 can be provided with a spring which acts on it in the closing direction.
• the first embodiment does not have a spring.
• the first valve element 15 is isolated from the valve cage 11 by a bellows 27 which, being metallic, constitutes at the same time a spring exerting a closing force opposite to the force F.
• the bellows 27 is fixed to one of its ends 28 to the first surface element 15 and at its other end 29 to the valve cage 11, in a solid and pressure-tight manner.
• the outside diameter of the bowl 36 is equal to the inside diameter of the bowl 17 formed in the valve seat 16 of the valve cage 11.
• the second valve element 35 has two axial surfaces which can be subjected to the action of secondary pressure and which, when pressure is applied, give opposite forces in the axial direction. These two surfaces constitute a pressure surface differential which, under the action of the secondary pressure, gives a force of direction opposite to the adjustment force F for the adjustment of the secondary pressure P2.
• One of these surfaces is constituted by the upper side 40 of the bowl 35 which, in FIGS. 1 to 3, is shown at the upper part.
• the second surface, of larger diameter, is produced in the following manner: The second valve element 35 is separated by a seal from the valve cage 11 by means of a bellows 41.
• This bellows 41 is firmly connected and sealed on the lower end 42 in the valve cage 41, while the other upper end acts in a solid and sealed manner on the second valve member 35.
• the two diameters at the ends 42 and 43 of the bellows 41 are of the same dimension. They correspond to the median diameters of the bellows.
• the bellows 41 hermetically closes this interior space 44 and at the same time isolates the toroidal chamber 19 located on the secondary side of the toroidal chamber 21 and the connector 14 intended for deaeration.
• the differential surface of the second valve element which intervenes in the adjustment of the secondary pressure F2 and which is designated by the reference 35 results from the fact that the median diameter of the bellows 41 at the end 42 where the connection with the cage takes place valve 11, is larger than the inside diameter of the bowl 17 formed in the valve cage 11. Because the inside diameter of the end 42 of the bellows is larger than the outside diameter of the bowl 36 which has the upper part 40, there is an axial differential surface which, under the influence of the secondary pressure P2, gives a force of direction opposite to the adjustment force F.
• the operating mode of the pressure regulator described in the context of the exemplary embodiment corresponding to FIGS. 1 to 3 is indicated above.
• the operating principle of this pressure regulator is based on a force comparison.
• the other valve seat comprised between the secondary side comprising the toroidal chamber 19 and the toroidal chamber 21 of the deaeration device 14 is closed because the second valve element 35, with its bowl 36, is applied in the axial direction on the seat surface 20 of the first valve element 15.
• the secondary pressure P2 is isolated from the primary pressure P1 and from the deaeration.
• the first valve member 15, which comprises the valve seat surface 22 lifts as shown in Figure 2 in the axial direction fear deviate downward from the bowl 17 of the valve seat 16 located on the side of the cage.
• the effect of this movement is to put the toroidal chamber 18 located on the primary side into communication with the toroidal chamber 19 located on the secondary side. Therefore, the medium can flow, under the action of the primary pressure P1, from the toroidal chamber 18 located on the primary side into the toroidal chamber 19 located on the secondary side until the secondary pressure P2 determined by the proportional magnet 10 and its adjustment force F is reached.
• the second valve element 35 is pushed up in the axial direction under the action of the force of the secondary pressure P2 which cooperates with the differential pressure surface and moves in the direction of the arrow F in the figure. 2 until the fillings are balanced again. Then. the valve element 35 returns to the rest position indicated in FIG. 1.
• the first valve element 15 follows the movement of the second valve element 35 in the axial direction in the direction opposite to the arrow F so that the secondary pressure P2 is isolated from ventilation P3.
• the magnetic force of the proportional magnet 10 must be reduced. Due to the balance of forces obtained, the second valve element 35, due to the presence of the differential pressure surface and under the action of the secondary pressure P2, moves upward in the opposite direction to the arrow F of Figure 3.
• the first valve member 15 cannot follow this upward movement of the second valve member 35 of Figure 3 because the first valve member 15 and its valve seat surface 22 are pushed against the bowl 17 formed in the valve seat on the side of the cage and remain there.
• the only part which is raised is therefore the second valve element 35 of FIG. 3 which deviates upwards from the first valve element 15, so that the bowl 36 deviates upwards from the seat surface 20 of the first valve member 15.
• the inner chamber 38 of the second valve member 35 opens, at its open lower end, in the toroidal chamber 19 located on the secondary side.
• the secondary pressure P2 which prevails in the toroidal chamber 19 can escape through the interior chamber 33 of the second valve element 35 passing through the openings 39 and arrive at the toroidal chamber 21 until the balance sheet forces be balanced again.
• the pressure regulator returns to its rest position indicated in Figure 1. It is understood that it is possible to obtain in this way a complete deaeration of the operating device which can be connected to fitting 13.
• the pressure regulator in question makes it possible, with very low adjustment forces F, to regulate large pressures with large flow rates.
• Another essential advantage of the device consists in that the adjustment force of the corrector member, for example of the proportional magnet 10, is completely independent of the nominal passage section for which the pressure regulator is designed. Pressure regulators of this type can therefore be produced, which can be used for nominal passage sections of 20 mm by using adjustment forces as small as those which occur for nominal passage passage sections. Consequently, the adjustment devices, in particular the proportional magnets 10, can be small, light, therefore inexpensive and space-saving, so that the assembly of the pressure regulator is inexpensive light, small and compact. Another advantage is that the deaeration can be carried out either upwards in the direction of the proportional magnet 10 or downwards through the valve cage 11.
• the second valve element 35 can be constituted by a full piston completely closed to the outside and the deaeration takes place downwards through the first hollow valve element. Since the two valve elements 15 and 35 are isolated by means of a bellows 27 or 31, there is no more frictional force resulting from the tight closure of the valve elements. The valve elements 15, 35 are therefore easy to move, which has the effect of further reducing the necessary adjusting force and, consequently, the dimensions of the proportional magnet 10.
• the pressure regulator according to the invention can, by departing from the first embodiment, be constituted by a simple opening / closing valve. This is achieved by making the differential pressure area of the second valve member 35 equal to zero.
• Another advantage of the pressure regulator according to the invention is that it suffices to give the differential pressure surface of the second valve element 35 of determined dimensions to obtain the desired characteristics for the pressure regulator.
• the other components of the pressure regulator should not be changed.
• the parts which correspond to the first exemplary embodiment are designated by reference numbers which differ from 100 of the preceding figures, which avoids repetitions with respect to the description of the first example of achievement.
• the cylindrical casing 123 of the first valve element 115 is closed in a sealed manner in the valve cage 111 by means of an O-ring 130.
• the outside diameter of the cylindrical casing 123 of the first valve member 115 corresponds at least approximately to the inside diameter of the bowl 117 of the valve seat on the side of the cage, so that the first valve member 115 is at least substantially at a balanced pressure.
• the outside diameter of the cylindrical casing 123 is slightly smaller, which gives, in the region of the ring 125 which carries the seal 126, a greater axial surface 131 on the lower side than on the other axial side where, the surface subjected to the action of the primary pressure P1 results from the difference between the outside diameter d £, the ring 125 and the inside diameter of the bowl 117 in the rage of, valve 16.
• the first valve element 115 has a differential pressure surface which, under the action of the secondary pressure P1, gives a closing force oriented in the axial direction upwards and which is further supported by the force of a spring 132 acting in the same direction. This device ensures the closure of the first valve element 115.
• the second valve element 135 is also sealed in the valve cage 111 by means of an O-ring 14c. Under these conditions, the end of the second valve element 135 which carries the bowl 136 can, as for example in the case of the first example of embodiment, protrude in the radial direction, the external peripheral surface of the external cylindrical envelope, which gives, as in the first embodiment, an upper side 140 of the toroidal chamber 119 subjected to the secondary pressure P2.
• the second valve element 35 which is located at a certain axial distance, for example at its opposite end located at the top in FIG. 4, can have an axial surface 147 also subjected to the action of pressure.
• the secondary pressure P2 of the toroidal chamber 119 also acts in the region of the axial surface 147.
• the second valve element is subjected to the action of a spring 148 which, in Figure 4, is directed upwards.
• the second valve member 135 includes an annular groove 149 having axial surfaces equal constituting its side walls.
• the annular groove 149 communicates with the toroidal chamber 119.
• the outside diameter of the cylindrical casing 137 in this case corresponds to the ns substantially to the inside diameter of the bowl 117 of the valve seat 116.
• connection 114 which serves for deaeration is in this case provided coaxially to the two valve elements 115, 135. In FIG. 4, it is located at the lower end of the valve cage 111.
• the second valve element 135 lifts in the opposite direction to the arrow F in FIG. 4 under the action of the first valve element which is located at 115 below it, the deaeration of the secondary pressure P2 is effected by the internal chamber 124 of the first element valve 115 down towards the connector 114.
• the second valve member 135 can be completely closed in the upper area and also inside.

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• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• General Physics & Mathematics (AREA)
• Engineering & Computer Science (AREA)
• Automation & Control Theory (AREA)
• Control Of Fluid Pressure (AREA)
• Safety Valves (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=6331009

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• 1987
  • 1987-07-07 DE DE19873722315 patent/DE3722315A1/de active Granted
• 1988
  • 1988-07-01 WO PCT/FR1988/000352 patent/WO1989000308A1/fr not_active Application Discontinuation
  • 1988-07-01 JP JP63505882A patent/JPH02500394A/ja active Pending
  • 1988-07-01 EP EP88905896A patent/EP0328573A1/de not_active Withdrawn
  • 1988-07-01 US US07/342,514 patent/US4979537A/en not_active Expired - Fee Related

Non-Patent Citations (1)

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