EP2014992A1 - Tempering facility distributor - Google Patents

Abstract

The device has several, especially 3 to 5, stages (10,20), each with a definable desired outflow temperature of the liquid and each with a feed line connection and a return line connection and a direct overflow connection (5) between adjacent stages, especially with a non-return valve. Each stage is defined as an elongated tubular container with the heat carrier liquid flow direction along its longitudinal axis and divided axially into an input flow part (11,21), a mixer part (13,23) and an outflow part (12,22). An independent claim is also included for a method of collecting and distributing a heat carrier liquid for a tempering system.

Description

The invention relates to a Temperieranlagenverteiler according to the preamble of claim 1 and a method for collecting and distributing heat transfer fluid according to the preamble of claim 12.

In modern heating systems are increasingly used various energy sources that raise heat transfer fluids to different temperature levels, and various energy delivery devices that are fed with different temperature controlled heat transfer fluids used. For example, radiator heaters are fed with warmer liquids than underfloor heating or the tempering liquids heated by condensing boiler higher than by heat exchangers of solar systems. From the scriptures DE 197 29 747 A1 . US 5 617 994 A . DE 196 42 721 A1 . DE 92 14 762 U1 . DE 196 37 575 A1 and AT 399 770 B are Temperieranlagenverteiler known for connecting system circuits with flow and return lines for Temperierflüssigkeiten with different temperature levels. From these documents it is apparent to build the distributor for this purpose from different temperature chambers. Thus, system circuits can each be supplied with appropriately tempered heat transfer fluids and the returning heat transfer fluids are collected in appropriately tempered chambers, so that little heat energy is wasted unused.

In the context of the invention are to be understood as temperature control both heating systems and cooling systems or combined heating and cooling systems. The system circuits are consumer circuits and source circuits, where Consumer groups such as radiator heaters, underfloor heating or water heaters and source circuits condensing boilers, heat pumps or refrigerators may include.

The AT 411 190 B describes a heating system with a cylinder-shaped container as a distributor with several superimposed chambers. The individual chambers are each tempered differently and have in the radial direction inlet and outlet connections for return or flow lines of the system circuits. Depending on the heat exchange device of a system circuit, it can be fed with heat transfer fluid of a certain temperature level and the liquid return flow can be returned to a corresponding chamber. The chambers are each interconnected by overcurrent connections with check valves. Due to the structure with different temperatures chambers results already discussed in terms of the prior art and known advantages.

As a disadvantage of in the AT 411 190 B described heating system, however, proves a high space requirement of the integrally formed, barrel-shaped distributor, since often such a distributor installed in basements and thus should be transported through narrow, steep basement stairs and through narrow cellar doors. Due to the radial alignment of the distributor connections, the laying of the system circuit lines connected to the distributor also proves to be very complicated. Furthermore, there are no defined flow directions of the heat transfer fluids in the individual flat cylindrical chambers, so that they mixed poorly or directly and unmixed by a Return return connection into a flow connection. Thus, undesirable temperature differences of the heat transfer fluid can arise in the headers of the system circuits.

An object of the invention is thus to provide a manifold having multiple temperature levels for temperature control systems with a smaller footprint and easy-to-install connecting lines for system circuits.

Another object of the invention is to improve a predictability of the temperature of the heat transfer fluid, so that undesirable temperature differences between the tempering liquids flowing into the system circuits are reduced.

These objects are achieved by the realization of the characterizing features of the independent claims. Features which further develop the invention in an alternative or advantageous manner can be found in the dependent claims.

An inventive Temperieranlagenverteiler is composed of a plurality of elongated, tubular containers, which are referred to as stages and provide different temperature levels of the heat transfer medium, constructed. The steps each have three areas along their longitudinal axes. At an inflow part, which is designed to collect heat transfer fluids from the return lines of the system circuits, at least one, preferably a plurality of return line connections are arranged. The inflow part is followed by a mixer part for the mixing of heat transfer fluids flowing from the inflow part into a discharge part, in particular temperature differences. The discharge part following the mixer part has at least one, preferably a plurality of supply line connections and is therefore designed to distribute heat transfer fluid at a defined predefinable mixing temperature into the system circuits.

Due to the successive structure of the three areas results for the heat transfer fluid a predetermined and defined flow direction through the respective stages. The heat transfer fluids collected in the inflow section are forcibly guided through the mixer before they can reach the supply lines of the system circuits via the outflow section. This ensures an improved mixing of the heat transfer fluids and thus an improved, more accurate predictability of the discharge target temperature.

For example, the Temperieranlagenverteiler of three, four or five stages is constructed, which are arranged one above the other with spaced parallel longitudinal axes, wherein the three regions of adjacent stages are each arranged along the longitudinal axis in opposite order. This allows a straightforward arrangement of overcurrent connections between the stages, i. from the inflow parts to the outflow parts of adjacent stages, respectively. In general, the stages are ordered by their respective target discharge temperature so that overcurrent flows are directed to the adjacent stages with the least temperature differential.

The steps may be formed as an elongated tube of, for example, circular, oval or rectangular cross-section, the longitudinal axes preferably being horizontally aligned. For example, in the two first fifths of the tube, measured along the longitudinal axis, a plurality of pipe sockets arranged as connections for return lines of system circuits sequentially sequentially along the longitudinal axis. In particular, the pipe sockets designed as return line connections can protrude slightly into the interior of the step tube. This area of the step forms the inflow part. Approximately the third fifth of the stage is designed, for example, as a mixer and for this purpose has an arrangement of flow line plates in the interior of the step tube, as is known to those skilled in the art, whereby the mixing of liquid flowing from the inlet part into the drain part is supported and thus the temperature is evened out. For example, about the last two-fifths of the tube have pipe sockets as connections for flow lines of system circuits, which are sequentially arranged sequentially along the longitudinal axis. In particular, the pipe sockets designed as feed line connections are flush with the step tube wall. This part of the step thus forms the drainage part. The individual pipe sockets are generally arranged at right angles to the longitudinal axis of the step, wherein the cross sections of the pipe sockets are preferably formed to match the cross sections of the corresponding system circuit lines.

The overcurrent connections, which are respectively disposed between the discharge parts and the supply parts of adjacent stages, may be tubular. In the event of a short circuit - no heat dissipation by consumer circuits - the entire mass flow of the source circuits must be dissipated by means of the overflow connections. In this case, the distributor works as a hydraulic switch. In normal operation, the overflow connections cause a Compensation of the mass flows, since the mass flows in the inflows of a stage do not correspond to the mass flows of the outflows. Due to the presence of the overflow connections, each system circuit has a closed circuit in itself, the flow resistance of which is caused only by the pipelines and various installations. The pumps installed in the system circuits only have to overcome this flow resistance.

In particular, the overcurrent connections have check valves or pressure compensation valves. As pressure equalizing valves, for example, conventional spring-loaded pressure compensation valves can be used. But it is also possible to use pressure compensation valves, which are electronically controlled via pressure sensors. These pressure compensation valves have a passage direction in which they open above a certain, optionally adjustable, pressure difference. In the opposite direction these valves close in the manner of a check valve.

As heat transfer fluids, all known in the art, suitable liquids, especially water, can be used. Due to the spaced and spatially separated arrangement of the individual stages, these can each be lined with insulating material, which compared to a one-piece, barrel-shaped design of the distributor with chamber partitions a lower energy loss can be realized.

In particular, the sum of the cross-sectional areas of the inflows approximately corresponds to the cross-sectional area of the tubular step, the skilled person corresponding to the dimensions and the number of stages and the pipe socket can adjust the flow rates and the number of system circuits. The cross-sectional areas of the overflow connections are also designed by the person skilled in the art, so that a sufficient size for a short circuit is present. Even at high flow rates, the diameter of the tube-like steps can be kept small, so that the steps can be easily inserted through common door openings and through narrow aisles. Due to the parallel arrangement of the individual stages to one another and by arranging the system circuit line connections sequentially one behind the other along the longitudinal axes of the stages, the system circuit flow and return lines can be laid with little effort and space.

In a concrete Temperieranlagenverteiler inventive moreover conventional and conventional valves, lines and sensors may be present, which are used for control or for proper operation in practice.

Fig. 1

einen erfindungsgemässen Temperieranlagenverteiler mit drei Stufen in einer 3-D-Ansicht;

Fig. 2

eine Schnittdarstellung einer Stufe eines erfindungsgemässen Temperieranlagenverteilers;

Fig. 3

einen erfindungsgemässen Temperieranlagenverteiler mit zwei Stufen in einer 3-D-Ansicht; und

Fig. 4

eine schematische Darstellung einer Temperieranlage mit einem erfindungsgemässen Temperieranlagenverteiler mit drei Stufen und daran angeschlossenen Systemkreisen.

The device according to the invention is described in more detail below purely by way of example with reference to concrete exemplary embodiments shown schematically in the drawings, with further advantages of the invention also being discussed. In detail show:

Fig. 1

an inventive Temperieranlagenverteiler with three stages in a 3-D view;

Fig. 2

a sectional view of a stage of an inventive Temperieranlagenverteilers;

Fig. 3

an inventive Temperieranlagenverteiler with two stages in a 3-D view; and

Fig. 4

a schematic representation of a temperature control with a novel Temperieranlagenverteiler with three stages and system circuits connected thereto.

The in FIG. 1 illustrated Temperieranlagenverteiler 1 for collecting, mixing and distributing a heat transfer fluid has three stages 10,20,30 with predetermined discharge target temperatures of the heat transfer fluid. The three stages are each formed as elongated, tubular containers with a longitudinal axis and - arranged in order of their respective outflow target temperature - arranged successively spaced, wherein the longitudinal axes of the steps 10,20,30 are parallel to each other. Each of the stages 10, 20, 30 has an inflow part 11, 21, 31, a mixer part 13, 23, 33 and a discharge part 12, 22, 32, which follow one another along the longitudinal axis.

At the inflow parts 11, 21, 31, three return line connections 15 are arranged sequentially one after the other along the longitudinal axis, so that the heat transfer fluid flowing back from the return lines is respectively collected in the inflow parts 11, 21, 31. By a successively arranged return of the heat transfer fluids in the supply parts 11,21,31 the heat transfer fluids are already mixed there among themselves. In addition, according to the invention, the mixer parts 13, 23, 33 of the stages 10, 20, 30 follow, in each case, the inflow parts 11, 21, 31, the mixer parts 13, 23, 33 being forced by the heat transfer fluid flows through in a predetermined direction. In particular, the mixer parts 13,23,33 Strömungsleitbleche, so that the heat transfer fluid actively mixed when flowing through the mixer parts 13,23,33 and their temperature is made uniform to the discharge target temperature. At the discharge parts 12, 22, 32, three supply line connections 17 for connecting supply lines of the system circuits are arranged one after the other. The feed and return line connections designed as pipe sockets are all oriented perpendicular to the longitudinal axes of the steps, which simplifies the laying of system circuit lines to be connected.

Due to the spatial separation of inflow part, mixer part and outflow part within the stages, fixed flow directions, namely from the inflow parts via the mixer parts into the outflow parts and essentially in the direction of the stepped longitudinal axes, are provided for the heat transfer fluids. All collected liquids inevitably flow through the mixer parts, whereby the target discharge temperature can be specified more precisely, since only well-mixed liquids with a uniform temperature distribution reach via the discharge parts in the supply lines of the system circuits.

Between each adjacent stages 10, 20, 30 there are direct overflow connections 5. The overflow connections 5 connect the outflow part 12 of the first stage 10 with the inflow part 21 of the second stage 20, the outflow part 22 of the second stage 20 with the inflow parts 11, 31 of the first and third stages 10,30 and the discharge part 32 of the third stage 30 with the inflow part 21 of the second stage 20. Therefore, it is advantageous to successive stages each to arrange in a mirror-inverted manner, so that in each case below an inflow part of a stage, a drainage part of the adjacent stage follows and vice versa. The overflow connections 5 each have a check valve or a non-return valve with a passage direction from the discharge parts 12, 22, 32 to the supply parts 11, 21, 31. Equally possible is a design of the overcurrent connections 5 with ball valves or motor valves for controlling overflow flow rates of the heat transfer fluid.

The steps 10, 20, 30 are in each case essentially the same size and functionally identical and have in the in FIG. 1 shown embodiment on a square cross-section.

The illustrated mixer sublimiting lines are shown purely for the purpose of illustration, for example, the steps can each be formed in one piece. However, it is also possible to form the parts of the steps separately and to arrange them further apart, wherein the heat transfer fluid is collected in an inflow part, passed through a mixer part and distributed via a discharge part into the system circuit lines.

Due to the elongated and space-saving design of the steps, they can also be easily transported through narrow doors and steep stairs into basements and can be installed in small rooms.

FIG. 2 shows a sectional view of a formed as an elongated tubular container stage 10. The stage 10 is divided into an inflow part 11, a mixer part 13 and a drain part 12. At the inflow part 11 of the stage 10, which is used to collect refluxes from the System circuits is used, three pipe sockets 15 are arranged for connection of system circuit return lines, wherein the pipe socket 15 each protrude slightly into the interior of the stage. The arrows shown in the figure are intended to illustrate the flow directions of the heat transfer fluid. At the discharge part 12, which is designed to distribute the heat transfer liquid mixed to the outflow target temperature, three pipe stubs 17 are arranged for the connection of system circuit supply lines. The pipe sockets 17, which are in the form of flow line connections, close in particular flush with the stepped container wall. Furthermore, the inflow part 11 and the outflow part 12 each have an overflow connection connection 5 with a check valve 6, via which they can be connected to outflow or inflow parts of adjacent stages.

By the inventive construction of the stage 10, in which the collecting of the refluxes locally separated from the distribution of the heat transfer fluid in the flow lines of the system circuits, a defined flow direction results for the heat transfer fluids. This allows an improved mixing of the heat transfer fluids, so that a target discharge temperature can be specified more accurately.

In FIG. 3 shows an embodiment of a Temperieranlagenverteilers 1 according to the invention with two stages 10,20 shown in a 3-D view. At the inflow parts 11, 21 of the two stages 10, 20, seven return pipe connections 15, 25, designed as pipe sockets, are arranged for collecting the heat transfer fluids flowing back into the distributor from the system circuits. At the other end of the steps, the are formed as elongated, round tubes, are the discharge parts 12,22, each with seven flow line connections. Between the feed parts 11,21 and the discharge parts 12,22 are the mixer parts, which are flowed through by the heat transfer fluids prior to distribution in the system circuits. In each case from the two discharge parts 12,22 to the supply parts 11,21 of the other stage 10,20 overcurrent connections 5 are arranged to compensate for the mass flows.

As already mentioned above, the number and the cross-sectional area of the stages can be adapted by a person skilled in the art in accordance with the number and type of system circuits present.

FIG. 4 shows a schematic representation of a temperature control system with an inventive distributor and connected consumer circuits 65,66 and source circuits 61,62,63,64. The stages are arranged one below the other according to their target discharge temperature, with the highest outflow setpoint temperature being mixed in the uppermost stage.

The source circuit 61 has, for example, a condensing boiler for oil, gas or biomass, wherein the heat transfer fluid is usually heated to a temperature of more than 75 ° C. The return line of the system circuit 61 is thus connected to the upper stage 10 with the highest target discharge temperature. Since a condensing boiler is most efficient when there is a large difference in temperature between supply and return, which also applies to district heating, the supply line of this system circuit to the drain part 31 of the lowest stage 30 with the lowest run-off target temperature connected. The source circuit 62 has, for example, a heat pump or a heat exchanger of a solar system. The headers, which are fed from the discharge part 32 of the lowest stage 30 are heated by the heat pump or the heat exchanger of the solar system to temperatures of about 25-40 ° C. The refluxes are thus directed into the inflow part of the middle stage 20. As a further producer in the source circuit 63, for example, a log wood boiler with thermal return increase is shown. In this case, the flow temperature may be about 35 ° C, which is why the flow line is connected to a flow line connection of the discharge part 21 of the middle stage 20. By heat dissipation of the log wood boiler, the heat transfer fluid is heated to about 60 ° C. The return is thus connected to the inflow part 11 of the upper stage 10. The source circuit 64 has, for example, a buffer storage, which is fed with heat transfer fluid having a temperature of about 60-70 ° C, which is why the supply line to the discharge part 12 of the upper stage 10 is connected to the highest target discharge temperature. A return line of the buffer memory is connected to the inflow part 11 of the stage 10, via which line the heat transfer fluid from the buffer store, which has the highest temperature, is returned to the distributor. Another return line is connected to the inflow part 31 of the lower stage 30, whereby the already most cooled heat transfer liquid can be returned to the manifold via this line.

As consumer circuits 65,66 a system circuit 65 with a radiator heater and a system circuit 66 are shown with a floor heating example. The Radiator heating supply line is connected to the discharge part 12 of the upper stage 10, since the radiator heater is fed with heat transfer fluid having a temperature of up to about 70 ° C. The refluxes cooled by the heat release are returned to the inflow part 21 of the middle stage 20. The underfloor heating is fed with heat transfer fluid from the discharge section 21 of the middle stage 20 at a temperature of up to 38 ° C. The cooled refluxes are returned to the inflow part 31 of the lowest stage 30.

By virtue of the construction of the stages according to the invention, the inflows, which inevitably all flow through the mixer part, can be mixed exactly to a predefinable temperature. The heat transfer fluids mixed to the respective outflow target temperature are then distributed via the respective outflow parts into the supply lines of the system circuits.

The arrows shown in the figure show the flow directions of the heat transfer fluids.

In concrete temperature control and Temperieranlagenverteilern beyond conventional and conventional valves, lines and sensors are available, which are used for control and proper operation in practice. In particular, the system circuits are only simplified and shown schematically.

It is understood that these illustrated figures represent only examples of possible embodiments.

Claims (12)

Temperinganlagenverteiler (1) for collecting and distributing a heat transfer fluid (2) having a plurality, in particular three to five, stages (10; 20) each having a predetermined discharge target temperature of the heat transfer fluid (2),
in which • the steps (10; 20) at least each □ a flow line connection (17; 27) and □ a return line connection (15; 25) have, and A direct overcurrent connection (5) for the heat transfer fluid (2), in particular with a check valve (6), exists between respectively adjacent stages (10; 20),
characterized in that
the steps (10; 20) respectively • are formed as elongated, tubular containers with a longitudinal axis, so that in each case a flow direction for the heat transfer fluid (2) is defined substantially in the direction of the respective longitudinal axis, and • are divided one after the other in flow direction □ an inflow part (11; 21) for collecting heat transfer fluid (2), the at least one return line connection (15; 25) being arranged at the inflow part (11; 21), □ a mixer part (13; 23) for mixing flow from the inflow part (11; 21) into a drain part (12; 22), Temperature differences exhibiting heat transfer fluid (2), and □ the discharge part (12; 22) for distributing the heat transfer fluid (2), wherein the at least one supply line connection (17; 27) is arranged on the discharge part. Temperature control distributor (1) according to claim 1,
characterized in that • the inflow parts (11; 21) each have at least two return line connections (15; 16; 25; 26), which are in each case arranged sequentially one after the other along the longitudinal axes (19; 29) of the inflow parts, and • the discharge parts (12; 22) each have at least two supply line connections (17; 18; 27; 28), which are in each case arranged sequentially one after the other along the longitudinal axes (19; 29) of the discharge parts. Temperature control distributor (1) according to claim 1 or 2,
characterized in that
the steps (10, 20) are arranged in a succession spaced manner according to their respective discharge target temperature, in particular wherein the longitudinal axes of the steps (10, 20) are parallel to each other. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the steps (10; 20) are in each case of essentially the same size and functionally identical. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the steps (10; 20) each have a circular or square cross-section. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
The mixer parts (13, 23) each have flow baffles, so that heat transfer fluid (2) actively flows through the mixer parts (13, 23) and their temperature is made uniform to the discharge target temperature. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the overcurrent connections connect the discharge parts (12; 22) to the supply parts (11; 21) of respective adjacent stages (10; 20) and one non-return valve or one non-return valve (6) from the discharge parts (12; 22) to the supply parts (11, 21). Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the steps are each formed in one piece. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the return line connections (15; 16; 25; 26) and the supply line connections (17; 18; 27; 28) are each designed as pipe sockets whose longitudinal axes are aligned perpendicular to the respective longitudinal axes of the steps. Temperature control distributor (1) according to one of the preceding claims,
characterized in that
each of the return line connections (15; 16; 25; 26) protrude into the interior of the feed parts (11; 21) and terminate the feed line connections (17; 18; 27; 28) substantially flush with a container wall of the discharge parts (12; , Temperature control distributor (1) according to one of the preceding claims,
characterized in that
the sum of the cross-sectional areas of the return line connections (15; 25) corresponds in each case to one step (10; 20) of the cross-sectional area of this step (10; 20) substantially. Method for collecting and distributing heat transfer fluid for a temperature control system having a temperature control manifold with a plurality of stages (10; 20), each of which has a predetermined, predetermined outflow target temperature that is different from one another,
with the steps Collecting heat transfer fluids from system circuits in each of the stages (10, 20), Mixing the heat transfer fluids in each of the stages (10, 20), • Distributing the heat transfer fluids respectively from the stages (10, 20) into the system circuits, wherein the steps are each carried out successively in spatially separated areas of the stages and thus the heat transfer fluid has a defined flow direction.

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