VALVE FOR A SYSTEM HAVING A HEAT-CARRYING MEDIUM

Abstract: Heat exchanger valve (8) with thermostat valve (12), a housing (9) with inlet (20) and outlet (21), a thermostat bellows displaceable spindle (30) with seal (42) which, by the expansion/contraction of the thermostat bellows and against the pressure of a surrounding spring (31), can close/open an opening (27) with a seating (27a) in a transverse wall (24) between the inlet (20) and the outlet (21), and a piston (13) controlled by differential pressure for the control of a medium's differential pressure across a pre-setting (11) and a thermostat valve (12) consisting of the seating (27a) and the seal (42) between the inlet (20) and the piston (13), the thermostat valve (12) being able to cut off the flow between the inlet and the outlet independently of the pre-setting (11). With the valve (8), only a predetermined maximum amount of the heat-carrying medium flows through the heat exchangers (5). If the differential pressure is increased when the valves on a pipe length are closed, the flow in the individual heat exchangers (5) is not increased.

Description: VALVE FOR A SYSTEM HAVING A HEAT CARRYING MEDIUM This invention concerns a valve for a system having a heat- carrying medium which flows through a number of heat ex- changers in the system, said valve having a thermostat valve with a housing comprising an inlet and an outlet, a spindle with a seal which can be displaced by a thermostat bellows and which, depending on the expansion/contraction of the thermostat bellows and against the force of a spring which surrounds the spindle, can respectively close and open an opening with a seating in a transverse wall in the housing between the inlet and the outlet. A central heating plant with a similar valve is known from U.S. Patent No. 5,178,324, said plant being configured in such a manner that it is possible to control the flow in the entire plant, a single part of the plant or in several zone-divided sections of the plant. This plant comprises several heat exchangers each provided with its own valve, said heat exchangers being intended to be placed in a number of at least one in each room in a building, and where the valves are disposed in the piping of the plant. In central heating plants it is important that the water is distributed through the plant in a pre-calculated propor¬ tion so that the dimensioned heat requirements of the indi¬ vidual " heat exchangers are taken into consideration. It is also important that the heat-carrying liquid remains in the heat exchangers for a period of time which is long enough to allow a reasonable amount of heat to be dissi¬ pated in the rooms of the building which are to be heated by the heat exchangers, which can be ensured by means of a differential pressure valve placed in the individual branches of the plant, in that this valve can regulate th flow of the heat-carrying fluid. Furthermore, it is important that the differential pressur across the individual heat exchangers is so low that nois does not arise in the valves, in that such noise can caus inconvenience, either directly or by transmission throug the piping system. In the individual rooms, the flow of heat-carrying liqui through the heat exchanger or each of the heat exchanger can be controlled by means of thermostatic valves which, depending on the temperature in the room, can open more o less to allow flow through the heat exchanger(s) so tha the emission of heat to the rooms can be held within thos limits which are determined by the accuracy of the thermo static valves, and by the temperature which the user of th room desires to maintain by the adjustment of the thermo¬ static valve or valves. When ordinary thermostatic valves are mounted in a lengt of piping which leads the heat-carrying medium from a hea exchanger to the subsequent heat exchangers, each of thes thermostatic valves will be dependent on the others. Thu if ten thermostatic valves are mounted in a length o piping, and nine of these are closed, the differential pressure across the open valve will be increased. Thi results in an increase in the flow through the associate heat exchanger, and the increased flow can also give ris to disturbing noise. This situation can arise, for example, at times of the yea when the incidence of sunlight makes heating unnecessary. If there is also opened a window in that room in which th open thermostatic valve is mounted, the associated heat exchanger will receive a considerably greater flow than would otherwise be the case. It is also difficult to achieve a mutual balance between the individual pipes in the building, the reason being that the flow will change depending on the differential pressure. Today, this drawback is overcome by providing each length of piping with an extra valve which is care¬ fully adjusted to ensure the balance between the individual pipes. The object of the present invention is therefore to improve a valve of the kind described so that the above-mentioned drawbacks of a heating plant can be avoided. This object is achieved by means of a valve of the above- mentioned kind, said valve according to the invention being characteristic in that the valve is further provided with a piston which is controlled by a differential pressure for the regulation of the differential pressure of the heat- carrying medium across an adjustable pre-setting, and the thermostatic valve consisting of the seating and the seal between the inlet and the piston, and that the thermostatic valve is arranged to be able to cut off the flow between the inlet and the outlet independently of the adjustable pre-setting. The piston in the valve according to the invention thus maintains a constant differential pressure across the adjustable pre-setting and across the seating and the seal together. It is hereby achieved that the valve according to the invention can be adjusted to allow only a predetermined maximum amount of the heat-carrying medium to flow through the valve independently of the remaining heat exchangers and pressure conditions in the plant. If the differential pressure is increased, for example because one or more o the remaining valves on a length of piping are closed, thi will not result in an increase in the flow through th individual heat exchanger. Moreover, in certain cases a reduction in noise can b achieved, in that the pressure/flow is reduced in thre steps, whereas in the ordinary thermostatic valves this i effected in one or two steps. Furthermore, it will not be necessary to mount an extr valve in order to mutually balance the individual pip lengths. The dependent claims disclose expedient arrangements of th valve according to the invention. In the following, the valve according to the invention wil be described in more detail with reference to the drawing where Fig. 1 schematically shows a commonly known, double pip heating plant, and Fig. 2 shows a section through an embodiment of the valv according to the invention. In fig. 1 is shown a double-pipe heating plant, one pip of which is the main pipe 1 which leads the heat-carryin medium, such as water, from a source of heat, which i not illustrated, in the heating plant, and the second pip is a return pipe 2 which leads the medium back to th boiler. From a branch point 3 there extends a first side pipe which leads the medium forward to a number of hea exchangers 5, each of which is connected to the first side pipe 4 at connection points 6 and to the second side pipe 7 which leads the medium back to the return pipe 2. Each heat exchanger 5 is provided with a valve 8 according to the invention, which is arranged to control the flow of the heat-carrying medium through the respective heat ex¬ changers 5. In fig. 2 is shown an embodiment of the valve according to the invention, said embodiment comprising a housing 9 which contains a combination of a differential pressure valve 10, an adjustable pre-setting 11 and a thermostat valve 12. The differential pressure valve 10 comprises a first, cup- shaped bush 14 which is placed in a bore 16 which is co¬ axial with the axis 15 of the housing 9. The first cup- shaped bush is connected with a second cup-shaped bush 14a which is arranged in such a manner that the bottoms in the two bushes face away from each other. The bottom in the second cup-shaped bush 14a forms a transverse wall 24 in the valve 8. In the space between the bottoms in the two cup-shaped bushes 14, 14a, there is housed a piston 13 which is stepped in diameter, of which the part with the smallest diameter lies inside the first cup-shaped bush 14, and the part with the largest diameter is inside the second cup- shaped bush 14a. The step between the two diameters hereby forms a first area 13a on the piston 13 in an annular space at the transition between the two cup-shaped bushes 14, 14a. That part of the piston 13 which is enclosed within the first cup-shaped bush 14 demarcates a space 26, where the area of the end surface of the piston 13 is indicated with the reference figure 13b in the drawing. Furthermore, a helical spring 25 is inserted between the bottom or the transverse wall 24 in the second cup-shaped bush 14a and the front of the piston 13. The spring 25 is secured in a centred manner on the front of the piston 13 by means of an annular recess or stepping-down, whereby radially outside the spring 25 said spring 25 demarcates a circular area indicated by the reference figure 13c, and also a circle with the area 13d inside the spring. From the front radially outside the spring 25, i.e. from the area 13c to the above-mentioned end surface 13b, the piston 13 also has a through-going bore 22. Transversely to the bore 16, the housing 9 has an inlet 20 and an outlet 21 for the medium, and along the circum- ference the second cup-shaped bush 14a is provided with a longitudinal channel 28 which extends from the inlet 20 to the above-mentioned circular space with the area 13a on the piston 13. From fig. 2 it will be clear that a medium which is led in through the inlet 20 will be able to flow through the bore 22 and exercise a pressure against the end surface 13b of the piston 13 in the space 26, so that the piston 13 com¬ presses the spring 25. The medium can also flow from the inlet 20 through an opening 27 with a seating 27a, which is configured in the bottom or the transverse wall 24 of the second cup-shaped bush 14a, and flow further into the space 29 enclosed with- in the windings of the spring 25. The area of the space 19 between the windings of the spring 25 changes in size depending on the length of the spring 25, in that the area is increased when the spring is extended and reduced when the spring 25 is compressed by the piston 13. If the spring is compressed completely together, so that the windings lie up against one another, the area can even be completely closed so that through-flow is prevented. From the space 19, the medium can flow out of the second cup-shaped bush 14a through an opening 23 which opens out in the outlet 21. By a suitable dimensioning of the areas 13a, 13b, 13c and 13d of the piston 13 in relation to the pressure of the spring 25, with a displacement of the piston and the con¬ sequent changing of the area of the space 19 between the windings of the spring 25, there can be generated a desired differential pressure across the inlet 20 and the thermo- stat seating 27a with an associated seal 42. The adjustable pre-setting 11 can be set to a desired through-flow opening by being turned around the axis 15, and can thereafter be locked in its setting. It can, for example, be configured as follows: In one end of the housing 9 there is screwed a threaded bush 33 in which a cylindrical plug 34 is secured in a manner in which it cannot be displaced in the direction of the axis 15 of the housing 9, but can be turned around said axis. At the free end of the threaded bush 33, there is also provided a ijush-shaped setting element 35. In a radial plane, the threaded bush 33 and the setting element 35 have cooperating teeth 36 which extend for a short distance axially. In a locking position for the setting element 35, the teeth 36 prevent a relative turning of the parts 33, 35, whereby the plug 34 is also prevented from turning. On the other hand, in a second position in which the setting element 35, against the pressure of a conical spring 37 which is compressed between a flange on the plug 34 and a contact surface in the setting element 35, is drawn out axially in relation to the threaded bush 33, the engagemen between the teeth 36 is terminated. In a second radial plane there are cooperating teeth 38 on the setting elemen 35 and the plug 34, whereby the setting element 35 can tur the plug in the threaded bush 33 when the setting elemen 35 is drawn axially out from the threaded bush 33, in that the teeth 38 on the plug 34 have adequate axial extensio for this purpose. That end of the cylindrical plug 34 which faces inwards i the housing 9, lies up against the outer side of the botto or the transverse wall 24 in the second cup-shaped bus 14a. The plug 34 is configured with an inclined surface 39 which extends from the said end, in that the intersection between the end and the inclined surface 39 extends along a chord 40 on one side of the axis 15 of the plug, extends at an angle through the axis 15 of the plug and ends in a surface 41 which is at right angles to the axis 15. The inlet 20 has a predetermined area, and in the position of the plug 34 shown in fig. 2 there is unhindered flow through the inlet 20 and the opening 27 in the bottom or the transverse wall 24 of the second cup-shaped bush 14a. By turning the plug 34 at an angle of 180° around its axis in the threaded bush 33, and herewith in relation to the housing 9 and the inlet 20, the inlet 20 will be blocked. It will be clear that the turning of the plug 34 at angles of less than 180° from the shown position will block smaller or greater parts of the inlet 20, hereby making it possible to select a desired area of flow through the in¬ let 20 and to the opening 27. The thermostat valve 12 is of commonly known construction. Its arrangement comprises a spindle 30 which is surrounded by a helical spring 31 which with its one end abuts against a locking element 32 in the housing 9, and with its other end against the bottom of the first cup-shaped bush 14 in the housing. Outside the housing 9, the spindle 30 is connected to a not-shown thermostat bellows which can dis¬ place the spindle 30 in its longitudinal direction depend- ing on the surrounding temperature and against the pressure from the spring 31. The spindle 30 also has the above- mentioned seal 42 which can close the opening 27 with the seating 27a in the bottom or the transverse wall 24 of the second cup-shaped bush 14a, regardless of the setting of the differential pressure valve 10 and the adjustable pre¬ setting 11.

Claims: C L A I M S 1. Valve for a system having a heat-carrying medium whic flows through a number of heat exchangers (5) in th system, said valve (8) having a thermostat valve (12) wit a housing (9) comprising an inlet (20) and an outlet (21) a spindle (30) which can be displaced by a thermosta bellows and having a seal (42), and which depending on th expansion/contraction of the thermostat bellows and agains the pressure of a spring (31) which surrounds the spindl (30) can respectively close and open an opening (27) with seating (27a) in a transverse wall (24) in the housing (9 between the inlet (20) and the outlet (21), characterize in that the valve (8) also has a differential pressur controlled piston (13) for the regulation of the differen tial pressure of the heat-carrying medium across an ad justable pre-setting (11) and the thermostat valve (12 consisting of the seating (27a) and the seal (42) betwee the inlet (20) and the piston (13), and that the thermosta valve (12) is arranged to be able to cut off the flo between the inlet (20) and the outlet (27) independently o the adjustable pre-setting (11). 2. Valve according to claim 1, characterized in that th piston (13) of the differential pressure valve (10) i surrounded by a first cup-shaped bush (14) and is herewit connected to a second cup-shaped bush (14a), the bottoms o which face in opposite directions and are disposed in bore (16) which is coaxial with the axis (15) of th housing (9), that the piston (13) is stepped in diameter, whereby the part with the smallest diameter lies in th first cup-shaped bush (14), and in that a channel (22) leads from the front of the piston (13) to the rear of sai piston (13). Valve according to claim 2, characterized in that spring (25) is provided between the piston (13) and the bottom or the transverse wall (24) of the second cup-shaped bush (14a) in such a manner that the area of the space (19) between the windings of the spring (25) can be varied depending on the movement of the piston (13), said bottom or transverse wall (24) having the said opening (27) which is limited by the seating (27a). 4. Valve according to claim 3, characterized in that the second cup-shaped bush (14a) has on its outer side at least one longitudinal channel (28) which, from the inlet (20), leads to an annular space between the two bushes (14, 14a), in which space at the stepping of the piston (13) there is formed an area (13a), that inside the first cup-shaped bush (14) the rear of the piston has an area (13b), and in that the spring (25), at its abutment against the piston (13) inside the second cup-shaped bush (14a), on its outer side demarcates an area (13c) and on its inner side an area (13d). 5. Valve according to claim 1, characterized in that the adjustable pre-setting (11) comprises a cylindrical plug (34) which, by a threaded bush (33), is secured in a rotatable manner but lockable in the housing (9), that the plug (34) with the end inside the housing (9) lies up against the bottom or the transverse wall (24) of the second cup-shaped bush (14a), and is configured with an inclined surface (39) which runs from a chord (40) on one side of the axis (15) of the plug (34), extends at an angle through the axis (15) beyond the inlet (20) and ends in a surface (41) which is at right angles to the axis (15). 6. Valve according to claim 5, characterized in that the threaded bush (33) is surrounded by a setting element (35), that in a radial plane on the threaded bush (33) and the setting element (35) there are cooperating teeth (36) with a slight axial extension, which in a locking position fo the setting element (35) prevent mutual rotation betwee the threaded bush (33) and the setting element (35), and i that the plug (34) and the setting element (35) in a secon radial plane have cooperating teeth (38), where the teet (38) on the plug (33) have a predetermined axial length, s that the setting element (35) in a second position draw out of the locking position can turn the plug (33) in th housing (9). 7. Valve according to claim 6, characterized in that th setting element is held in the locked position by a sprin (37) which is inserted between a flange on the plug (33) and a contact surface on the setting element (35). 8. Valve according to claim 1, characterized in that th thermostat valve (12) comprises a spindle (30) whic extends through the first cup-shaped bush (14) and th piston (13), that the spindle is surrounded by a sprin (31) which is compressed between a locking element (32) an the bottom of the first cup-shaped bush (14), and in tha the spindle (30), on that end which projects into the spac which is surrounded by the spring (25), has the said sea (42) which is arranged to lie up against the seating (27a) and close the opening (27).

Inventors: GYLOV HANS HENRIK, JOERGENSEN OLE, MOELLER CARSTEN, GYLOV, HANS, HENRIK, JOERGENSEN, OLE, MOELLER, CARSTEN
Applicants: FRESE ARMATUR, GYLOV HANS HENRIK, JOERGENSEN OLE, MOELLER CARSTEN, FRESE ARMATUR A/S, GYLOV, HANS, HENRIK, JOERGENSEN, OLE, MOELLER, CARSTEN
Application year: 1995
Main classification: F16K31
IPC codes: F24D19, G05D23