DIFFERENTIAL PRESSURE REGULATOR

Abstract: The present invention relates to a differential pressure regulator (1) having a lower part (2) and an upper part (3), the upper part being connected to the lower part. The lower part has an inlet (4) and an outlet (5). Between the inlet and the outlet there is a partition (6) with a valve seat (7), against which a valve body (8) acts at one end of a valve spindle (9), mounted in the upper part and actuatable in an axial direction by means of a biased compression spring (33) and surrounded by a membrane (30), which is fastened by means of a bead (27) all around between the upper part (3) and the lower part (2) and seals these parts against each other. According to the invention the coupling end (21) of the upper part (3) beyond a stop flange (20) in a direction towards the lower part is designed as an axially directed, annual projection (24), which at its free end forms a radially outwardly directed holding flange (25), enclosing a groove (26) all around, in which the membrane bead (27) is inserted. The fastening area of the membrane (28) is axially directed, i.e. mainly parallel to the insertion direction. A sealing is accomplished through a radial compression of the bead area (27) between an axial inner wall (18) of the coupling end (55) of the lower part and the bottom of the groove (26). The stop flange (20) acts against a step (19) in the coupling end of the lower part and a locking ring (23) rotatably retains the upper part on the lower part.

Description: DIFFERENTIAL PRESSURE REGULATOR The present invention relates to a differential pressure regulator of the type set forth in the preamble of claim 1. Such regulators are used e.g. to regulate the pressure drop over the contents in a heating or cooling system and are usually built into a water return conduit. The already known regulators in this field have various deficiencies. E.g. for various relatively limi- ted uses valves dimensioned in various ways are required, and consequently such valves need more production and storage capacity. Also, it is necessary regarding these regulators to pay attention to the presence of a relatively large friction between the moveable parts and the friction variations and the received signals with a not satisfactory accuracy caused thereby. The installation requirements are problematic in several respects. Thus, the building height is often substantial. The attachment of e.g. measuring and signal circuit cables is often fixed and may prove to be unfavorable in certain mounting situations. The exchange and the change of the position of certain parts, particularly during operation, often are difficult or impossible to carry out. Thus, the regulator must be disassembled, a plurality of individual loose parts being obtained, and such loose parts are not always the parts, which are subjected to e.g. wear and tear to a great extent. Consequently, the subsequent mounting will be more lengthy and time-consuming. During an assembly and disassembly it is often necessary to initially remove all the attachments, since these in their attached condition are likely to be subjected to improper stresses. Various measuring and discharge possibilities often do not exist. The adjustment requirement of a required function of the regulator often is less expedient. A change a preadjusted values often is carried out by non-authorized persons. A deairation of the regulators, particularly a complete one, can be a difficult problem and furthermore, special tools may be required for this purpose and also a certain precise mounting position may be required. A cut-off function is lacking sometimes or it is not easily accessible or it is complicated, e.g. requiring special tools. Finally, because of errors the adjustment of the regulator and consequently its performance can be changed, e.g. in such a way, that the stroke/flow volume of the valve is restricted. The reliability and the life of the regulators can be unsatisfactory. The problem may be, that it is difficult to quickly, simply and reliably measure a functional failure and then in a suitable way take care of it. Problems with generated noise may arise. A well balanced reaction capacity often does not exist. Also, the material consumption and too large dimensions and proportions respectively sometimes can be troublesome factors. Examples of already known regulators, which are impaired by at least some of the deficiencies mentioned above, are described in EP-A-0451 326, EP-A-0 689 652 and DE-A-3 708 166. The object of the present invention is to counteract and as far as possible eliminate the above- mentioned drawbacks and to develop a differential pressure regulator , which is improved as regards separate details as well as particularly combined details. These objects are attained according to the present invention by designing a differential pressure regulator of the type described in the introduction mainly in such a way, as is set forth in the characterizing clause of claim 1. Additional characterizing features and advantages of the invention are set forth in the following description, reference being made to the enclosed drawings, which depict a preferred but not limiting embodiment. The drawings show in detail in: Fig. 1 a diametrical, longitudinal cross-section along line I-I in Fig. 3 of a differential pressure regulator according to the invention in a manually closed position and an open position respectively ; Fig. 2 and 3 a lateral view and a view from above respectively of the regulator according to Fig. 1 ; Fig. 4 a perspective view from above of a spring holder according to the invention; and Fig. 5 a diametrical cross-section through the bottom part of the upper part of the regulator. In the drawings the differential pressure regulator 1 is shown in its entirety. It comprises two main parts, namely a lower part 2 and an upper part 3. The lower part comprises an inlet 4 and an outlet 5. However, the flow direction may in particular cases be reverse, the inlet being an outlet and the outlet being an inlet. They are separated from each other by means of a partition 6, which accommodates a seat 7, against which a valve body 8 is designed to act, which constitutes or is connected to the lower end of valve spindle 9. The lower part comprises also discharge and/or measuring connection means 11 of a type known per se, which houses an circumferential flange 10, which projects into the inlet. These means are suitably protected by a cover 12, made of rubber or a plastic material, which by means of an in a suitable way shaped first holder 13 is fastened to said lower part and which by means of a second holder 14 secures a cap 15. The end of the valve body and the spindle respectively close to the partition is concentrically surrounded by a cup 16, which preferably has a plane bottom 17 with a relatively large diameter and a shorter circular cylindrical wall 18, which surrounds said bottom and has an extension, designed as a step 19 all around, which is connected to the free end and is used as stop means for a flange 20 at coupling end 21 of upper part 3. In the axial wall of step 19 there is a groove 22 all around, designed for a lock ring 23. Below flange 20 a shorter axial, annular projection 24 projects axially into cup 16 at a distance from wall 18, the lower end of the projection being designed as a radially outwardly directed holding flange 25. Flanges 20and 25 include between themselves and wall 24 a groove 26 all around, designed to house an annular bead 27, which constitutes the outer end of a membrane 28, which is extended somewhat and abuts wall 18 towards bottom 17 and then via a soft rounded fold 29, while retreating from wall 18 and bottom 17, becomes a plane, central part 30 at a level roughly between bead 27 and bottom 17 in a closed regulating position. The outer diameter of holding flange 25 is somewhat smaller than the inner diameter of the cup, at least regarding this level, the membrane being fastened between wall 18 and flange 25. Upper part 3 comprises a house 31, which e.g. is die-cast and can be connected to the lower part by means of said coupling end 21, and in the coupling movement per se there is no relative torsion between the lower part and the upper part despite the fact, that the upper part and the lower part can be rotated limitlessly in relation to each other. In this way the advantage is obtained, that the upper part quickly and without problems steplessly can occupy an arbitrary rotated position in relation to the lower part in order to meet any requirements as to positional alignment between the lower part and the upper part, and that possibly existing connections do not have to be removed , when the upper part and the lower part are joined to each other and disassembled from each other respectively. Also, the connections are not subjected to inappropriate stresses. House 31 suitably has a rotational symmetrical cross-section and preferably comprises a central portion 32, designed as a truncated cover in an axial direction, the lower part of which coincides with or is adjacent coupling end 21. This cone-shaped portion houses spindle 9 as well as a cone- shaped compression spring 33, which surrounds the spindle and the upper narrow end of which is retained by a support 34, which with a central hole 35 having an inner thread is threaded on the spindle, which is provided with an outer thread, and which with two projections 36 on mutually diametrically opposite sides is guided in axial guiding channels 37 in house 31. These grooves are made in parts 38 of the house, which are designed in a corresponding way. In this manner a torsion of the spindle will result in, that support 34, which is not rotatable , will move in an axial direction in house 31 and thereby compress spring 33 and let it expand respectively. One of house parts 38 is e.g. provided with an upper connection 39 and a lower connection 40, which are designed for partly signaling circuit connection and partly deairation. The connection, which depending on the assembly position of the regulator ends up in an upper position, is used for deairation, whereas "the other connection is used for signaling circuit connection. The connection or connections, which possibly are not used, can be provided with a plug 85. Spindle 9 extends with its outer end into the area within the free end of house 31, which end recei- ves a bushing 42, the end of which, which projects out of the house, is surrounded by a hand wheel 41. The hand wheel is rotatably mounted on the bushing and is, with an inner thread 43, threaded on an outer thread 44 on house 31. However, bushing 42 is not rotable but axially moveable in a relative way on the outer spindle end, which is not rotation symmetrical, but e.g. hexagonal, and is inserted into an in a corresponding way designed blind hole 80 in the bushing, which is rotated by means of an opening 45, made in the free bushing end, e.g. for a hexagon spanner. Bushing 42 is inserted from within into a circumferential flange 46 in the house, a flange 47 all around and mounted on the remote bushing end projecting into a groove 48, which surrounds the inner end of the opening of the circumferential flange, in house 31 and thus being used as an insertion stop. The bushing is surrounded by an O-ring 50, which is inserted into a groove 49 all around and seals against the opening of the circumferential flange , and keeps , close to its free outer end by means of a locking ring 51, the hand wheel 41 in place. Close to the bushing but at a small distance from it and the outer gable of house 31 respectively the spindle is surrounded by a groove 52 and a locking ring 53, inserted in the groove, which is desig- ned to prevent, that support 36, already at a minor prestressing of spring 33, abuts said gable and in this way limits or eliminates the movement path of the valve body. Where appropriate locking ring 53 enters into an extension 54 all around in the support adjacent to its inner thread, the locking ring in this way being efficiently locked along about 300° of the cross-section area of the locking ring and it will be practically impossible for the locking ring to leave its position, when the rotation of the spindle is continued. Said groove 52 must be deeper than the depth of the outer thread in a radial direction in order to avoid a deformation of the thread and a loosening of the locking ring. Naive body 8 is at its end , which is exposed to seat 7, provided with a groove 56 all around, which suitably is roughly semicircular in its cross-section and has an engaging lip 57. Subsequent to an insertion of an O-ring 58 into the groove the radially projecting lip is pressed downwards into an axial direction, the O-ring being squeezed and projecting with only a portion of its axial extension through groove 56, which in the same direction roughly is reduced by halves. In this way the O-ring is efficiently kept in place and is extended at the same time in a radial direction in order to optimally seal against seat 7 in a closing position. Further away from seat 7 the valve body is surrounded by a groove 59, in which however the groove wall, which faces the seat, suitably is somewhat withdrawn in order to pass a stop 60 in bore 61 of lower part 2 for the valve body and to more readily fill up the more narrow part 62 of this bore close to the seat. The groove wall, which is turned away from the seat, fills on the other hand with a slip fit up the upper bore part, which has a large diameter. In a closed position (the left portion in Fig. 1) an O-ring 63, which is inserted in groove 59, abuts step 60 and accomplishes in this way a satisfactory sealing between the inlet and the outlet. Said O-ring 63 has such small dimensions in relation to the rest of said bore part, that the least possible friction is obtained between these parts. A sealing effect is aimed at and is obtained only, when O-ring 63 abuts said step with a certain elastic deformation, which results in the sealing function. Further away from the seat the end side of the valve body is provided with a groove all around, which is open in an axial direction and used to form a thinner annular wall 65 on the inner side, which wall is pressed into a groove 66 around the spindle end, which is fastened to the valve body. In this way the valve body and the spindle constitute a homogenous unit. Membrane 28 is supported with its plane portion 30 by a membrane plate 67, also plane, and suitably, with its intermediate part 68, provided with holes, with which it is slipped onto the spindle, is forced onto and around the center, with its holes, of the plate in order to make it abut the lower side of the plate having a lower, annular termination 69, which softly is allowed to abut the side of the valve body close to the cup. The membrane and the plate suitably are vulcanized together in order to obtain an easily mountable unit, which preferably is slidably mounted on the spindle. Spring 33 is supported with its wide lower end by a spring holder 70, which suitably comprises a stamped and bent metal plate having a central hole 71 with a diameter, which is much larger than the diameter of the spindle, which projects through said hole, and has holes 72 for a mounting fixture. Center 73 of the holder suitably is elevated in order to obtain a lower edge section 74 all around, against which the spring abuts in a self-centering way. In two mutually diametrically opposite places the edge section is extended outwards in a radial direction in order to form bayonet pro- jections 75, designed to be inserted into house 31 through corresponding recesses 76, circumferen- tially seen outside and in an axial direction above which the house is provided with a locking groove 77 all around, in which projections 75 are designed to be inserted. Thus, the locking groove is limited downwards by flange sections 78, which are terminated symmetrically by guiding channels 37, i.e. each guiding channel being centrally arranged in relation to the corresponding flange section. Each one of the projections is centrally provided with a downwardly stamped locking lug 79, which snaps into the guiding channel, when the spring holder is turned 90° into its mounting position. Thus, the extension of the locking groove in the axial direction is sufficiently large in order to initially house the total extension in an axial direction of the projections and the locking lugs, which are somewhat pressed downwards. A differential pressure regulator designed in this way functions in the following manner: The mounting of the parts of the differential pressure regulator is to begin with simple and reliable. The lower part comprises, with the exception of measuring connecting means 11, no movable parts. Its coupling end 55 suitably has an angle of inclination of 15° in relation to the axis of flow passage 4,5, whereas circular edge 10 can have an angle of 45° in relation to said axis. This means, that the mol- ding and the tooling , the accessibility and the adaptability are facilitated. Other arbitrary angular positions of said parts are of course possible. In the upper part bushing 42, provided with O-ring 50 is initially inserted from within through circumferential edge 46, until flange 47 abuts step 48. Then hand wheel 41 is screwed onto thread 44 of edge 46, until, with an inner flange 81, it abuts an outer bushing flange 82, in which position the hand wheel is secured on the bushing by mounting locking ring 51 on the latter. As regards the rest of the "guts" of the upper part, it can be assembled separately into an integral unit, which it is easy to insert into house 31 and to remove there from respectively. The valve body can initially be provided with the two O-rings and be mounted on the spindle in the described manner. Then the membrane plate with its membrane is mounted on the spindle and will be supported by the valve body, subsequent to which spring holder 70 and spring 33 are mounted on the spindle and are secured by screwing support 34 onto the spindle. Support 34 is fastened in its turn by means of locking ring 53. The unit, which is obtained in this way, is inserted into house 31 and projections 36 are inserted into guiding channels 37 and the free spindle end is pressed into the bushing, whereas bayonet projections 75 are guided through recesses 76, until they end up at the same level as locking groove 77, at which level they are stopped by means of a step 83 in house 31. Now the required axial position has been reached and the unit is rotated 90° in relation to the house, projections 75 being forced into the portion of groove 77, which is limited downwards by flange section 78. In the final phase of this rotational movement each one of lugs 79 ends up in a position in front of a guiding channel 37 and is pressed into a lower indent 84, formed therein. The pressure of spring 33 will guarantee , that the lugs are retained in their respective indents. In the final phase of the insertion of the described unit into house 31 the membrane is pushed forwards on axial projection 24, bead 27 being positioned in groove 26. The bead is then still not actuated and its cross-sectional shape is depicted by the central encirclement in Fig. 1, namely with a slight radial bulging in a direction away from groove 26 and a pronounced radial bulging towards the groove bottom. The atter bulging preferably is roughly semicircular, whereas the groove cross-section can be U-shaped. These cross-sectional shapes, which differ from each other, guarantee, that space will be available for a constriction room and that a substantial, permanently acting radial sealing force can be developed , when the bead is compressed, when the complete upper part in the next phase with its coupling end 21 is inserted into coupling end 55 of the lower part. In addition to the valve body, by means of bore 61, bead fold 29 and particularly its in an radial direction outer part will act as a soft guiding notch. In the final phase of said insertion movement the in a radial direction outer side of the bead runs along the upper/outer portion of inner wall 18 of the cup, until this portion fully or mainly will be positioned in front of groove 26, and then will fasten and elastically deform the bead, which is depicted in the lower encirclement in Fig. 1. Holding flange 25 is also important to some extent in this context, because it will force the membrane area to a position inside/below the bead between itself and wall 18, an additional sealing as well as an additional stabilizing of the coupling bond being obtained in this way, which latter is made permanent by mounting locking ring 23 in groove 22. A slight pressure against the free axial end of the bead can be generated in this way, which end thus is compressed and , when it springs back, elastically retains flange 20 against locking ring 23. The differential pressure regulator , completely assembled in this manner, can now be mounted in a medium conduit, and a signal circuit and measuring equipment respectively can then be connected. In case it is later necessary to disassemble the upper part, it is possible to do this with or without the attachments connected to the regulator, and it is only necessary to remove locking ring 23, and then lift up the complete upper part from the lower part. Two extreme regulating positions are shown in Fig. 1, in which the left part shows a manually obtained closing position. The hand wheel has then been completely screwed onto thread 44 and the bushing has thereby been moved as far as possible into house 31. The bushing then abuts with its inlet to blind hole 80 against a bevel 86 all around, which terminates the thread on the spindle within this area, and moves the spindle, until the valve body abuts seat 7, lower O-ring accomplishing the sealing against the seat, whereas the upper O-ring abuts against step 60 in order to seal the inlet against the outlet also via bore 61. In the open position (shown in the right part of Fig. 1) forces acting on the valve body, which have been transferred from the membrane and the membrane plate, can be balanced via spring 33. The pressure above and below the membrane, the so called differential pressure, will be held constant within a certain pressure and flow area. By means of the spring the differential pressure can be changed, i.e. 'by changing the position of spring support 34, which will be done by inserting a tool in opening 45 and rotating the bushing, support 34 being moved upwards and downwards respectively along the spindle. It is of course possible to select a certain differential pressure area by the selection of a spring. However, the spring according to the invention often makes such a selection superfluous or expands said area, because it is designed to be partly linear and partly progressive, which can be obtained by means of a non-uniform pitch and/or a non-uniform spring wire diameter design. In this way curve-shaped force characteristics are obtained and the length of the spring can be made substantially smaller than the length of a spring with an even pitch and an constant wire diameter. Tests with a regulator with a spring designed in this way have shown, that only 75 % of the total Δp-tolerance depends on the spring and that the rest of the percentage, 25 %, includes the mechanical inertias of the regulator construction and this is independent of the Δp- value, which has been selected within the operational area of the product. When the differential pressure has been adjusted by means of a tool inserted into the bushing, which pressure by the way can be read during the operation of the regulator, this preadjustment position can be fixed by turning the hand wheel e.g. anti-clockwise, until a distinct stop has been reached. In this position the bushing cannot be rotated using normal forces and consequently the preadjustment has been secured. The fixing is obtained by tightening flange 47 against the bottom of groove 48, the friction between these two parts generating the locking force. The present invention is not limited to the above described embodiments, but it can be modified and supplemented in an arbitrary manner within the scope of the inventive idea and the following claims. Thus, the various locking rings e.g. can be replaced by other stop and locking means, known per se.

Claims: CLAIMS 9 1. A differential pressure regulator (1) which comprises a lower part (2) and an upper part (3), which can be connected to said lower part by means of an end (21) having a stop flange (20), the lo- wer part being provided with an inlet (4) and an outlet (5) as well as a partition (6), mounted between the inlet and the outlet and having a valve seat (7), against which a valve body (8) is designed to act, which is mounted at one end of a valve spindle (9), mounted in said upper part (3) and actuated in one direction of a biased compression spring (33) and surrounded by a membrane (30), which is affixed by means of a bead (27) all around between said upper part (3) and said lower part (2) and which seals these parts against each other, c h a r a c t e r i z e d in that the coupling end (21) of the upper part (3) beyond the stop flange (20) towards the lower part is designed as an axially directed, annual projection (24), which with its free end forms a radially outwardly directed holder flange (25) and surrounds a groove (26) all around, in which the membrane bead (27) is inserted, in that the fixation area of the membrane (28) mainly is axially directed, i.e. mainly parallel to the insertion direction, in that a sealing is designed to be done and reinforced respectively by radially compressing the bead area (27) between an axial inner wall (18) of the coupling end (55) of the lower part and the bottom of the groove (26), in that the stop flange (20) acts on a step (19) in the coupling end of the step (19), and in that a locking ring (23) is designed to rotatably and fixedly hold the upper part against the lower part. 2. A differential pressure regulator according to claim 1, c h a r a c t e r i z e d in that the valve body and the end of the spindle close to the valve body respectively are concentrically surrounded by a cup (16), which preferably has a plane bottom (17) with a relatively large diameter, which bottom is surrounded by said inner wall (18) , which is shorter and circular cylindric and functions as a support for the area of the membrane close to the bead , which area develops into a soft rounded fold (29) all around away from the wall (18) and the bottom (17), which fold develops into a plane central membrane part (30). 3. Adifferential pressure regulator according to claim 2, c h a r a c t e r i z e d in that the outer diameter of the holding flange (25) is somewhat smaller than the inner diameter of the cup in order to fasten the membrane between the inner wall (18) and the holding flange (25). 4. A differential pressure regulator according to claim 1-3, c h a r a c t e r i z e d in that the upper part (3) comprises an eg die-cast house (31), which can be coupled to the lower part by means of said coupling end (21), in that the house (31) suitably is non-rotation symmetrical in its cross-section and preferably has an in an, axial direction as a truncated cone designed central part (32), the base of which coincides with or is adjacent the coupling end (21), in that said cone-shaped part houses partly the spindle (9) and partly said compression spring (33), which surrounds the spindle and has a conical shape, the upper, narrow spring end being retained by a support (34), which with a central hole (35) having an inner thread is threaded on a spindle provided with an outer thread and which with two projections (36) on mutually diametrically opposite sides is guided in axial guiding channels (37) in the house (31), which channels are made of the parts (38) of the house, which are designed in a corresponding way, a rotation of the spindle and a not rotatable axial movement of the support (34) in the house (31) causing a compression and an expansion of the spring (33) respectively. 5. A differential pressure regulator according to claim 4, c h a r a c t e r i z e d in that at least one house portion (38) is provided with an upper connection (39) and a lower connection (40), which in an artibtrary order are designed for partly a signal circuit connection and partly a deairation. 6. A differential pressure regulator according to any of claims 1-5, c h a r a c t e r i z e d in that the spindle (9) extends with its outer end into the area within the free end of the house (31), which holds a bushing (42), the end of which , which projects out of the house , is surrounded by a hand wheel (41), and in that the hand wheel is rotatably mounted on the bushing and with an inner thread (43) is threaded on an outer thread (44) on the house (31), whereas the bushing (42) is not rotatably mounted but mounted axially with a relative displacement on the outer spindle end, which is non- rotationally symmetrical , eg hexagonal and is inserted into a blind hole (80), designed in a corresponding way, in the bushing, which is designed to be rotated by means of an opening (45), in the free bushing end for e.g. a hexagon spanner. 7. A differential pressure regulator according to claim 6, c h a r a c t e r i z e d in that the bushing (42) is designed to be inserted from within into a circumferential flange (46) in the house, a flange (47) all around mounted at the far end of the bushing projecting into a groove (48), which surrounds the inner end of the circumferential flange in the house (31) and consequently functions as an insertion stop, and in that the bushing is surrounded by an O-ring (50), which is inserted into a groove (49) all around and seals against the opening of the circumferential flange, and holds the hand wheel (41) in place by means of a locking ring (51) adjacent its free outer end. 8. A differential pressure regulator according to claims 6 or 7, c h a r a c t e r i z e d in that adjacent the bushing but at a small distance from it and the outer gable of the house (31) the spindle is surrounded by a groove (52) and a locking ring (53) inserted into it, the function of which consists of preventing, that the support (36), already when the spring (33) is slightly biased, abuts said gable and in this way restricts or eliminates the movement path of the valve body, in that the locking ring (53) is designed to be pressed into an extension (54) all around in the support adjacent its inner thread in order to efficiently lock the locking ring along about 300° of the cross-sectional area of the locking ring, and in that said groove (52) is deeper than the depth of the outer thread in a radial direction in order to prevent, that the thread will be deformed and the locking ring will come loose. 9. A differential pressure regulator according to any of claims 1-8, c h a r a c t e r i z e d in that the valve body (8) at its end, exposed to seat (7), is provided with a groove (56) all around, which suitably has a mainly semicircular cross-section with an embracing, mainly radially projecting lip (57), which subsequent to an insertion of an O-ring (58) into the groove is designed to be pressed downwards in an axial direction and fasten the O-ring, with the exception of only a portion of its axial extension through the groove (56), which in the same direction is reduced mainly by halves. 10. Differential pressure regulator according to any of claims 1-9, c h a r a c t e r i z e d in that the valve body at a distance away from the seat (7) is surrounded by a groove (59), the wall of which, which faces the seat, is somewhat withdrawn in order to pass a step (60) in the bore (61) of the lower part (2) for the valve body and with slip fit fill up the narrow part (62) of this bore adjacent the seat, whereas the groove wall, which is turned away from the seat, with slip fit fills up the upper bore part with a large diameter, in that in a closed position an O-ring (63), which is inserted into the groove (59), which is turned away from the seat, is designed, with an elastic deformation, to abut the step (60), and in that the last-mentioned O-ring (63) has such small dimensions compared to said other bore part, that solely a negligible friction exists between said parts. 11. Differential pressure regulator according to any of claims 1-10, c h a r a c t e r i z e d in that the membrane (28) with its plane portion (30) is supported by an also plane membrane plate (67) and, suitably with its intermediate part (68), provided with holes, with which part it surrounds the spindle, applied over and around the center, with holes, of the plate in order to abut the lower side of the plate with a lower annual termination (69), which is designed as an elastic stop against the side of the valve adjacent the cup, and in that the membrane and the plate suitably are vulcanized together in order to obtain an easily mountable unit, which preferably is slidably mounted on the spindle. 12. A differential pressure regulator according to any of claims 4-11, c h a r a c t e r i z e d in that the spring (33) is supported with its wide lower end by a spring holder (70), which suitably comprises a stamped and bent metal plate having a central opening (71) with a diameter, which is substantially larger than the diameter of the spindle, which extends through the opening, and possi- bly with hole's (72) for a mounting fixture, in that the center (73) of the holder, suitably is elevated in order to form a lower edge section (74) all around, against which the spring is self-centering, in that in e.g. two mutually diametrically opposite positions the edge section is extended outwards in a radial direction in order to form bayonet projections (75), designed to be inserted into the house (31) through corresponding recesses (76), circumferentially outside which in an axial direction above which the house is provided with a locking groove (77) all around, into which the projections (75) are designed to be inserted, in that the locking groove downwards is restricted by flange sections (78), which are interrupted, symmetrically by guiding channels (37), ie with a guiding channel arranged centrally in relation to a corresponding flange section, and in that the projection prefer- ably each on is designed with its downwardly stamped locking lug (79), which will be inserted into the corresponding guiding channel, when the spring holder is rotated 90° into its mounting position. 13. A differential pressure regulator according to any of claims 1-12, c h a r a c t e r i z e d in that the bead has a cross-section with a slight radial bulge in a direction away from the groove (26) of the projection (24) and a pronounced bulge turned towards the bottom of the groove, in that the last-mentioned bulge mainly is semi-circular, whereas the cross-section of the groove mainly is U- shaped in order to guarantee, that space is available for a constriction area, and in that a substantial permanently acting radial sealing force will be developed , when the bead is compressed, when the coupling end (21) of the upper part is inserted into the coupling end (55) of the lower part and/or in that the holding flange (25) presses the membrane area into a position inside/between the bead between itself and the cup wall (18) in order to obtain an additional sealing as well as an additional stabilizing of the coupling bond, preferably a slight pressure by the stop flange (20) against the free axial end of the bead being generated in order to compress it and with spring force retain the flange (20) in an elastic abutment against the locking ring (23). 14. A differential pressure regulator according to any of claims 1-13, c h a r a c t e r i z e d in that the spring has a partly linear and a partly progressive section by means of a non-uniform pitch and/or a non-uniform spring wire diameter design. 15. A differential pressure regulator according to any of claims 1-14, c h a r a c t e r i z e d in that the preadjustment position of the bushing is designed to be fixed by rotating the hand wheel, until a distinct stop has been reached, and in that the fixation is obtained , when the flange (47) is pressed against the groove (48), the friction between these two parts resulting in the locking force.

Inventors: ENGELBREKTSSON ANDERS, TORSTENSSON ALVAR, ENGELBREKTSSON, ANDERS, TORSTENSSON, ALVAR
Applicants: ENGELBREKTSSON ANDERS, TORSTENSSON ALVAR, TOUR & ANDERSSON HYDRONICS AB, ENGELBREKTSSON, ANDERS, TORSTENSSON, ALVAR
Application year: 2001
Main classification: F16K17
IPC codes: G05D16