SE525917C2 - Heat transferring device for generating heat and/or hot water in buildings - Google Patents

Abstract

Intelligent connection block (42) has main connections for connecting external primary fluid source to consumer, and sub-connections for connecting heat exchangers inlet and outlet. Inner channels connect main connections and subconnections. The connection block and heat exchanger are connected by soldering. Soldered plate heat exchanger (43) has inlets and outlets for primary fluids and secondary fluid's inflow and outflow respectively.

Description

25 30 525 2 for example Alfa Laval Industri AB's fully soldered plate heat exchanger CB 51, which is usually compiled and assembled via a pipe system with sensors for temperature, fl fate and pressure and fl fate valves all connected to a control unit to control the parallel thermal processes.

In addition, a circulation pump is usually included for the property's heating system, expansion vessel, vent and refill and drain valves, respectively. The control panel may comprise two separate heat exchangers or a built-in heat exchanger, all of which as a heating medium have hot water from the scarred heat network. Preferably fl the warming district heating water wastes upstream of the domestic hot water and the hot water for heating. These relatively compact combined plate heat exchangers for simultaneous production of domestic hot water and hot water for heating are arranged with a pipe system with pipes and pipe connections for connections for the water systems on two opposite sides. These pipe connections are thus largely based on the space requirements of the heat exchangers. Furthermore, functions for control, monitoring and measurement, etc., of the thermal processes are arranged in the pipe systems without possible integrations with the heat exchanger connection connections having been taken advantage of. The same applies to other means such as circulation pumps, fillers, valves, etc. These means necessary for controlling, monitoring and measuring the thermal processes are usually standard components which are arranged in a difficult-to-understand way in the pipe system constructed for connecting the heat exchanger. Due to this construction, extensive work is required when connecting, disconnecting or replacing such a heat exchanger. This extensive work naturally increases the need for space as the installer must have space to be able to work. Defective components are usually rectified by replacement directly on site at the property. This also applies to tuning of replaced or unadjusted components to the other components included in the control panel. Due to the relatively large need for space that is thus required and the requirement for a good working environment around the unit, they are often installed in basements or in storage rooms adjacent to the property. However, these units should be constantly accessible to the heating supplier or another service provider.

It is also advantageous if they are covered by a more developed functional and system thinking and include for the unit adapted control equipment, measuring equipment and other equipment necessary for optimization and determination of the property's energy consumption, as well as other peripherals such as circulation pumps, filters, temperature sensors. etc. The unit should also have coordinated connection connections to the primary and secondary circuits adapted to quickly connect / disconnect such a unit as the unit must quickly be able to ski on site outside the property. Such a quickly replaceable unit would also enable advanced service work and tuning to be transferred to a workshop with access to control equipment and simulation equipment.

In order to simplify the connection of a single heat exchanger, it is known, for example by means of a heat exchanger described in the Japanese patent specification JP-A-1-247992, to use a coupling block with internal channels for connecting supply and output fittings to such a plate heat exchanger. .

The coupling block is arranged with connections for a primary and a secondary medium and simplifies the connection of the heat exchanger and reduces the need for space. Furthermore, it is known from International Patent Specification WO96 / 38699 to use a coupling block which is built up of a few plates when connecting a single oil cooler for an internal combustion engine.

These plates have recesses and bushings which in the assembled block form internal channels to lead fl the fate of the two flowing media to and fi 'from the heat exchanger. Such a construction simplifies the production of the internal channels in the coupling block. These known coupling blocks both use, where appropriate, conventional peripheral equipment which is mounted in a conventional pipe system which for this purpose is built up in connection with the coupling block and the heat exchanger, whereby most of the space gain and manufacturing rationality is lost. None of these known connection blocks shows any higher degree of avseende flexibility regarding capacity adjustment or integration of peripheral equipment, whereby the conditions for service and / or maintenance are not improved. Nor are these known devices covered by a more developed functional and system thinking where the coupling blocks have some high degree of integrated functions for connecting heating and heated media and for controlling the thermal process in the device. Thus, with these heat transfer devices, it is difficult to meet the requirements for a rational manufacture of compact units with a functional thinking with a high degree of integrated functions and a more rational system thinking, with the possibility of quick and easy disassembly / assembly of the unit during service, maintenance and similar. Nor is it easy with these known coupling blocks to obtain a large fl flexibility for adapting the hydraulic capacity by means of rational production technology. 10 15 20 525 4 This functional thinking and system thinking, with a high degree of functional integration in the unit and quick and easy connection is a prerequisite for providing better conditions for increasing the plant's reliability when complicated and sensitive work steps such as changing, assembling and / or trimming peripherals can fl be moved to premises with good access to equipment, aids and with good working conditions. In addition, time pressure and the associated risk of mistakes and the like are avoided during these work steps.

More specifically, in the area of heating plants for simultaneous production of domestic hot water and hot water for a water-borne heating system in smaller properties, there is a pronounced need for rationally manufactured compact units with integrated system thinking regarding functional peripherals. the various components and thus the risks of leakage can be reduced. In addition, such a compact unit with a high degree of integrated functions provides opportunities for manufacturing, service, upgrading, etc. in a factory environment, whereby modem technology in the field can be fully utilized to produce more cost-effective and for capacity adaptation highly flexible equipment. Experience gained in the industry indicates that the individual homeowner can normally not contribute anything by owning the district heating plant and being responsible for its care, as this requires special skills. It may even be the case that the homeowner prefers not to own the facility if that alternative is offered. There is therefore a need for a district heating plant for a detached house that constitutes a cost-effective compact and fully integrated function unit, which is not maintained with any unnecessary assembly joints for details. This in turn reduces the risk of leakage to a minimum. The district heating plant must be so compact that it can be accommodated in a moderately minimal and thereby sufficiently discreet cabinet that it does not meet any aesthetic obstacles for installation against a house facade.

Such a center opens up opportunities for the energy company to own and manage the external power plant, as it is possible to obtain permanent access to the equipment. This means that you do not have to depend on the property owner's participation for unlocking and admitting the house when inspecting and servicing the district heating plant and when replacing, inspecting and reading measuring equipment. The compactness also opens up the possibility of handling the scar heating plant as a whole as a single service unit that can be quickly and easily skied out in 10 20 25 30 fields in the event of disturbances or in need of maintenance. The heart in the control panel, containing all essential technology, must be able to be cleaned by knowledgeable service personnel within a maximum of 5 minutes, after which the replaced unit must be able to be maintained in a rational workshop environment to become an available spare module for the organization or service. retaget.

THE INVENTION An object of the present invention is to provide a compact heat transfer device comprising a heat exchanger and a coupling means for connecting the inlet and outlet of the heat exchanger to a primary and a secondary system where the coupling means in addition to being space-efficient and highly integrated. to connect heating and heated media and control the thermal process in the heat exchanger. A more specific object of the present invention is to provide a compact and for capacity adaptation fl visible heat transfer device with high thermal efficiency for simultaneous production of heat to waterborne system for heating premises and of domestic hot water by means of hot water 'from an external hot water source , such as a tar heating network. A device according to the invention must have a high degree of integrated functions and connections of the heat-transmitting media, control functions and power supply so that the device as a whole can be quickly or with simple handles and tools replaced or repaired at the installation site, for service, maintenance or upgrade. It is a great advantage for the heating consumer if such a device can be replaced quickly and easily and the replaced unit can be taken to a workshop for service, repair, maintenance or upgrade and after work performed, if necessary, trimming the unit before reassembly as it is reduced. his inconveniences at the same time as an increased quality assurance of the work performed is obtained.

To offer this, the present invention provides a heat transfer device comprising a heat exchanger and a coupling block with internal channels according to the preamble of claim 1, which is characterized by the features stated in the characterizing part of claim 1.

Further developments of the device are characterized by the features according to claims 2 to 34. 5 Q 5 9 1 7 2.- 6 A heat transfer device according to the present invention, which is arranged to transfer heat between a primary fl uid and at least a secondary fl uid, comprises a heat exchanger and a coupling block with internal channels, the coupling block for fulfilling the previously stated purposes comprising fl fate-distributing means for distributing at least one incoming fl fate and / or fl fate-merging means for merging at least two outgoing flows.

Henceforth, in these applications, these agents are often referred to collectively or separately as destructive agents. In addition, a coupling block in a device according to the present invention comprises controlling and / or monitoring means for monitoring and controlling the thermal process in the heat exchanger. The heat exchanger has inlets and outlets for the primary sekund uidens and the secondary fl uidens to fl outputs and outputs och respectively. and the secondary fl uidens to fl fates and out fl fates to and from the device, respectively, whereby the heat exchanger is connected to the primary fl uid source and the consumer system. The main connections are associated with the external primary source and the consumer, which may be a closed circuit or a system comprising one or more taps. The sub-connections are associated with the inlet and outlet of the heat exchanger, for the fl uids to fl fates and out fl fates to and from the heat exchanger, respectively. The primary liquid which may be a cooling or heating medium obtained from an external source such as a heating plant, a heating plant, a boiler, a heat pump, a cooling system or the like. It can also consist of so-called waste heat from an industrial process. The secondary fl uid is tempered before being fed to a dryer, which may comprise one or fl your circulation circuits for tempering an ambient medium and / or one or fl your circuits having one or fl your tapping points for a tempered fl uid. The heat transfer device may comprise, in addition to the heat exchanger, further heat transfer circuits of any kind, such as a shunt circuit or additional heat exchangers. Means for removing particles and other undesired components from the fl uids can advantageously be arranged in connection with the connections and / or channels of the coupling block.

Such means preferably comprise filters and degassing equipment and are, according to a preferred embodiment, integrated in the coupling block. In the event of a need for other treatment, equipment for such treatment can similarly be arranged integrated or close to the association in a similar manner; row with the coupling block.

According to one embodiment, the device according to the present invention comprises only a heat exchanger which is preferably arranged as a water heater for tap water which is heated by heat exchange with hot water from a boiler or the like. The coupling block thereby comprises of the primary water circuit, the boiler water circuit, with cold water taken out of the secondary water circuit, such as cold water to the water heater. But of course the flow of boiler water into or through the heat exchanger can also be controlled.The coupling block can also contain one or fl era of the compensation units for controlling the fate of hot boiler water which are described in more detail in the following.

The control means preferably comprises at least one adjusting means such as a control valve, a pump or the like for controlling the fate of the primary genom uiden genom through the heat exchanger. According to a preferred embodiment, the controlling means also comprise at least one fl fate sensor associated with at least one adjusting means. Wherein the fate sensor is arranged to sense an input of a secondary output and that the actuating means is arranged to manipulate the output of the primary output through the heat exchanger through the sensed output and thereby control the internal process in the heat exchanger. Preferably, such a fate sensor is arranged in the channel of the switching block for the input of the secondary liquid in the heat exchanger. The flow sensor is mechanically, hydraulically and / or electronically, associated, with the adjusting means for controlling from the sensed input the primary input in, through and / or out of the heat exchanger, for example by changing the setting of the adjusting means, preferably the degree of opening of the control valve.

According to an embodiment of the present invention, the fate sensor comprises a network piston associated with a sensor cylinder and a sensor piston axially movable in the sensor cylinder which is associated, preferably mechanically connected, with the measuring piston. The measuring piston is arranged in a fl fate channel, a running tube, for the secondary fl uiden and changes, in the event of a change in the fate of the secondary fl uiden fl, its position in the running tube. This change of position of the measuring piston is transmitted to the movable sensor piston which changes its axial position in the sensor cylinder. The fate of the primary genom uiden genom through the heat exchanger is then controlled based on the axial position of the movable sensor piston in the sensor cylinder by Q 5 1 7 E "than: .ÜJ: o .0v:.:.. 10 15 20 ... n .. _, .QQCI l '2' ".. nv gg '525 917 s it affects the setting of an adjusting means arranged in the channel for the discharge of the primary fluid from the heat exchanger such as a control valve and / or a pump or the like, preferably a hydraulic cylinder with associated hydraulic piston is used as sensor cylinder and sensor piston respectively.

According to a preferred embodiment, a controlled valve with a cone and seat is used, wherein the opening between the cone and the seat is controlled on the basis of the axial position of the sensor's movable sensor piston in the sensor cylinder. The cone and the movable sensor piston of the sensor can then be hydraulically, mechanically and / or electronically associated with each other. The sensor may be provided by any means for determining the axial position of the movable transducer piston in the transducer cylinder, such as mechanical, inductive or similar position sensing means. Furthermore, the sensors may include limit switches for e.g. stop / start of a pump, which is used for starting and stopping the boiler water pump integrated in the water heater in the coupling block. Alternatively or simultaneously, the sensor comprises an own medium which indicates or transmits the axial position of the movable sensor piston to the adjusting member. Preferably, a hydraulic cylinder with a movable hydraulic piston is used, the axial position of the movable hydraulic piston being hydraulically transmitted to influence the setting of the adjusting member, which then comprises a hydraulic slave cylinder with a movable piston.

According to a preferred embodiment, the control unit comprises at least one compensating unit, which by mechanical, hydraulic and / or electronic means is associated with the actuator's slave cylinder and its movable piston to control the primary fl uiden fl fate through the heat exchanger in cooperation with the fl fate sensor. The compensation unit comprises a sensor for preferably determining a process variable for the thermal process, preferably a temperature sensor for determining the temperature of the primary fl uid flowing into the heat exchanger and / or the secondary fl uid flowing out of the heat exchanger. In this application, the sensor refers to a variable-sensing body which, by suitable means, senses a variable or a change in a variable. Furthermore, the compensating unit comprises mechanical, electrical, hydraulic, electronic or other suitable means for converting and / or transmitting the sensed variable or variable change to the slave cylinder of the actuator and its movable piston, whereby the sensed variable will act on the movable piston through its compensating unit. axial position in the slave cylinder of the actuator. As a result, the setting of the actuator, for example the degree of opening of a valve, is changed and the fate is manipulated. For example, such a compensating unit comprises a hydraulic cylinder which by means of a hydraulic line is associated with the hydraulic cylinder of the actuator. In the event of a change in the variable sensed by the sensor, hydraulics are transferred between the hydraulic cylinder of the compensation unit and the hydraulic cylinder of the actuator, whereby the position of the piston in the hydraulic cylinder of the actuator is affected and the fate is manipulated. Of course, a number of compensating units can be used at the same time to simultaneously compensate for your variables. Through the compensating unit, the adjusting member receives a setting which is compensated for one or more of the measured variables or variable changes. If necessary, compensating units with safety function, such as temperature sensors for determining the temperature of the outgoing secondary fl uid, can be arranged. In the event of deviations outside a desired temperature range of the temperature of the outgoing secondary fl uid, the fl fate of the primary fl uid is adjusted so that the desired temperature is obtained at the outgoing secondary fl uid. This adjustment is preferably achieved in that the deviation in temperature of the outgoing secondary fl uid affects the displacement or position of the movable piston in the slave cylinder of the actuator. If necessary, a compensation unit can be arranged, which in the event of large deviations that can cause damage, is allowed to directly affect the adjusting member. This type of safety action is, for example, a scald protection in a system for domestic hot water, which takes effect if the temperature of the domestic hot water from the hot water heater is so high that personal injury can occur. In some embodiments, the compensation unit is also provided with means for correlating measured fl fate and possibly measured temperatures to a setting of primary fl uidens in fl fate in the heat exchanger which gives the desired temperature of outgoing secondary fl uid. These means of course include tuning functions whereby they are adapted to the conditions prevailing for the device. By correlating the measured fl fate and temperature variables with the measured fl fate and temperature variables to the primary fl uidens out fl desolation, in fl desolation into and / or through fl desolation through the heat exchanger by means of the control unit described above with fl fate sensor, compensation means and essentially from the ider uids flowing into the heat exchanger. Compensation based on deviations in the desired temperature is used preferably in cases where deviations can cause damage. If necessary, an additional fl fate sensor can of course be arranged in the coupling block, for example to indicate whether the actuator gives a fl fate in the primary fl circuit which deviates from the desired or as a giv sensor included in an energy measuring equipment. According to an alternative embodiment, the adjusting means is arranged in front of a controlled valve comprising a cone and a seat where the cone is hydraulically actuated to adjust the gap opening between the cone and the seat. The cone is associated, preferably mechanically connected, with a hydraulically movable hydraulic piston which is arranged in the slave cylinder, where the position of the movable hydraulic piston is affected by the fi desensor and any compensation units and transmitted to affect the opening between the cone and the seat.

The control means may also comprise at least one differential pressure valve which, in the event of variations in the pressure difference between the primary flow at the inlet of the device and at the outlet of the device, stabilizes the pressure difference between the inlet and the outlet. Preferably, the differential pressure regulator is arranged to open at a pressure difference of less than a certain value and to close at a pressure difference of more than a certain value. Preferably, the device according to the invention comprises a differential pressure regulator arranged in the coupling block with a thereby uniquely simple and reliable design. This simple design is made possible i.a. by arranging the cone of the valve pressure-relieved for the static pressure of the primary fl uiden and thereby that large diaphragms and strong fi spring arrangements can be avoided. The differential pressure regulator is preferably arranged at least in part integrated in the channels of the coupling block, whereby the pressure relief of the valve cone and the pressure reduction function is effected in a very advantageous, inherently new, manner. The opening tap from the primary inlet pressure, which is applied to the valve cone, is balanced via the pressure relief function on the valve stem and thus the closing cone valve acting in the opposite direction. The closing force is also created by the inlet pressure and is as large as the opening force but in the opposite direction. An additional closing force is created by the reduced inlet pressure of the primary fluid after the cone and the outlet pressure of the primary fluid are channeled out of the device, both internally in the device, to load each side of a piston, which is fixed to the spindle. The pressure difference between them thereby causes an effort to close the valve. It is further preferred that the latter closing force is counteracted by a created spring force, which is produced by a special spring arrangement arranged in the differential pressure regulator.

According to a preferred embodiment which provides a large fl flexibility in the capacity adjustment by Configuration, design and dimensioning of the internal channels can be easily adapted and if necessary adjusted for between units ski fi different or changed capacity needs and which provides good conditions for easy and reliable integration those in the governing bodies 10 15 20 25 30 ._ 5.11; 917 11 comprising sensors, compensation units and valves or other adjusting means, the coupling block is built up of a selectable number of channel-forming discs, channel plates and at least two ends. The duct plates are in turn according to a preferred embodiment built up of a number and from case to case selectable number of disc-shaped elements with recesses or partitions. These recesses and / or partitions form in the composite connection block partly a duct system with internal channels for the inlets and outlets of the heat transfer device and for the distribution of the heat pipes between these circuits and / or the joining of two or more outlets from these circuits, creates cavities for equipment integrated in the coupling block such as sensors, actuators, differential pressure regulators, etc .. The end plates preferably comprise connection sockets which connect these channels to external circuits, such as connectors and external hot water sources. A channel plate comprising a number of thinner disc-shaped elements is preferably arranged so that the dimensioning and configuration of the channels is determined by a combination of the design and location of the holes and recesses and the stacking frequency, thickness and number of the disc-shaped elements. Preferably, the end plates are arranged with bounces and the channel plates as well as the thinner disc-shaped elements in the composite coupling plate are joined together by soldering. A coupling block comprises two ends with connecting bounces, an arbitrary number of channel plates, each of which comprises an arbitrary number of thinner disc-shaped elements and possibly one or fl your intermediate discs. When these components in a composite coupling plate are combined into a stack, the recesses and / or the partitions form internal channels for the fl uids, which through the bounces of the ends are connected to external and internal circuits and cavities to accommodate said components. A further advantage obtained by the ibil flexibility offered with a channel block built up of channel plates according to this embodiment is that the inner channels can easily be arranged to change plate or level if necessary to bypass an obstacle such as another channel a fixed device, peripherals or similar. Such switching or displacement of ducts between plates or levels in coupling blocks may also be justified by the need to change the direction of the duct to obtain an optimal orientation of filters, pumps, valves regulators, sensors and the like, especially to optimally orient seats, parapets and similar for such equipment. With this coupling block comprising inner channels which are formed and dimensioned by stacking the recessed duct plates in the desired order on each other and to the desired height of the duct plates, good conditions are obtained for easily producing a coupling plate with ø Q no Q on 10 15 20 25 30 12 a high degree of function integration and capacity adjustment. For example, heterlter units differential pressure regulator, pumps, control valves, flow sensors, temperature sensors and similar equipment can be installed integrated in the coupling block and with connections on a suitable outer surface of the coupling block. The connection block can be arranged with a channel part comprising the inner channels and the sub-connections and with all the main connections coordinated to a connection block as described in more detail in the following. The duct plates, ends, bounces and thinner disc-shaped elements of the coupling block are preferably joined by soldering to a separate unit which can be disassembled or fixed by, for example, soldering to the heat exchanger connections Keller which is fully integrated with the heat exchanger as its one end. For maximum manufacturing rationality and fl feasibility for hydraulic capacity adjustment, it is preferable to punch all the constituent elements or layers in the coupling block from thinner sheet material. However, the duct plates and / or the thin disc-shaped elements can be manufactured according to possible methods such as: extruded, pre-sprayed or pressed in sheet metal or close to the preferred embodiment which is foamed or punched from material of selectable thickness, which gives some flexibility for capacity adjustment despite fixed programming of cutting machines or given punching tools. The duct plates can also be manufactured according to an inverted approach so that only the required partitions or partitions are built up in the duct plates so that when the plates, gables and any intermediate plates are brought together in a stack form walls between the ducts. The duct block can also be manufactured from a more complete piece of material in which the required ducts are drilled or milled out.

According to a preferred embodiment, the device comprises a connection block with coordinated main connections which are connected to a connection block. On a flat coupling block, a coupling plate, the main connections are preferably arranged on one of the storyteller of the coupling plate and connected to a connection block. Preferably, the bounces of the main connections and the connection block are arranged so that the connection block can be quickly connected to / disconnected from the connection connections of the coupling block. The connection block comprises connections for the connection of the external systems to the friend transmitting device and which is described in more detail in the following connection valves for closing / opening to the fl of fl uid from / to these systems.

The main connections may advantageously be arranged on the one of the coupler plates facing away from the heat transfer circuits, while the sub-connections are preferably arranged on the other of the coupler plates, which is facing the heat transfer circuits. A very compact device can be obtained if both main and sub-connections are arranged on the one of the coupler plate storytors, which faces the heat transfer circuits. Even in this case, as is clear from the following, it is advantageous to coordinate the main connections to be connected to a connection block.

In order to facilitate disconnection and connection of the heat transfer device according to the present invention, the main connections of the coupling block are coordinated to connect to a connection block which is partly arranged so that the coupling block can be detached from the connection block easily and quickly. close and open the main connections, at least two of the connection valves being coordinated for a simultaneous opening and closing of the coordinated valves, respectively.

According to one embodiment, the connection valves for the primary fl uiden are coordinated for a simultaneous opening and closing of the primary fl uiden inlet and outlet, respectively. Likewise, the connection valves for at least one secondary fl uid can be coordinated to coordinate a simultaneous opening and closing of the inlet and outlet of the secondary fl uid, respectively. It is advantageous that e.g. two control groups coordinate all connection valves for simultaneous opening and closing of the affected outlets and inlets. In this way, in a plant for two parallel thermal processes, the three connection valves for the inlet of the three fl uids can be coordinated for simultaneous opening and closing of the inlet of the three id uides and / or that the three connection valves for the outlet of the three fl uides are coordinated. for a simultaneous opening and closing of the outlets, respectively.

According to one embodiment of the heat transfer device according to the invention, it comprises means for two simultaneous parallel thermal processes, wherein heat is transferred between a primary fl uid and two secondary fl uids obtained from an external source. The fluids are each supplied to consumers. Such a device has a connection block and a connection block with a plurality of main connections associated with the external primary fluid source and two consumer circuits, for the primary två uidens and two secondary fl uiders to fl fates and out fl fates to respectively from the device and a fl number of sub-connections and associated ra heat transfer circuit inlets and outlets, for fl uidemas to fl fates and out fl fates to resp. 5 0 coca c no. o n 0: 0; . o. .

I non g no. ..,. . ..:: ao I I g I o o g I 000 nu o: n: oo oc; annas; o o n o o 525 917 14 tive from the two heat transfer circuits. Furthermore, in the internal channels significant fl fate fi determining means are arranged to distribute the primary fluid to fl fate between the inlet of the two heat transfer circuits for the primary fl uiden and / or merge and control the primary fl uiden output från from the two parallel heat exits of the two parallel fl uiden, whereby the number of main connections is less than the number of sub-connections. In addition, in the same manner as previously described for the general case, the coupling block comprises fl fate-distributing / fl fate-carrying means for distributing an incoming fl fate and / or combining two outgoing flows and controlling means for controlling at least the thermal process in the heat exchanger. Of course, the coupling block may also include controlling means for controlling the process in the second heat transfer circuit. Preferably, the heat exchanger and the second heat transfer circuit are connected in parallel. According to this particular embodiment, the coupling block comprises six main connections, two being associated with the external primary source and two each with the respective consumer circuit, and at least seven sub-connections associated with the inlet and outlet of the heat exchanger and the other heat transfer circuit.

According to one embodiment of the invention, the second heat transfer circuit comprises a shunt circuit with a shunt line for supplying the primary retur uiden return from the consumer to the primary fl uiden inlet to the consumer. Such a heat transfer device intended as a heating plant for the production of domestic hot water and hot water for a heating system preferably comprises a heat exchanger for the production of domestic hot water and a shunt circuit for the production of hot water for a heating system, where the hot water return after the heating system is shunted into hot water. is supplied to the heating system to reduce the temperature of the hot water supplied to the heating system. The primary source of water is in a preferred embodiment a district heating network but can be any hot water source as described above.

According to a preferred embodiment, the second heat transfer circuit also comprises a heat exchanger, preferably, in order to improve the possibilities of obtaining a compact modular device, both heat exchangers are plate heat exchangers. According to an embodiment of a compact heat transfer device according to the invention, the device comprises two plate heat exchangers, both of which are arranged with all inlets and outlets on the same end, the plate heat exchangers has a connection end and a rear end. In this case, a first plate heat exchanger is arranged to abut against the second plate heat exchanger in such a way that the first plate heat exchanger abuts with its rear end against the connection end of the second plate heat exchanger. Preferably, the first plate heat exchanger has a continuous channel inside the inlets and outlets, the inlet and outlet of the second plate heat exchanger being coordinated with the inlet and outlet of the first plate heat exchanger in such a way that the inlet and outlet of the second plate heat exchanger are the inlet and outlet of the plate heat exchanger arranged through channels. The through-going channels which are arranged in the inlet and outlet of the first heat exchanger form an integral part of the inlet and outlet of the second heat exchanger, respectively. In this case, the inlet and outlet of the plate heat exchangers will be coordinated in such a way that; the channel for the primary heat exchanger inlet in the second heat exchanger is common to or arranged inside the first heat exchanger inlet for the primary heat exchanger, - the channel for the primary heat exchanger outlet from the second heat exchanger is arranged inside the first heat exchanger heat exchanger. primary fl uiden, - the inlet of the second secondary fl uiden in the second heat exchanger is arranged inside the inlet of the first heat exchanger for the first secondary fl uiden, and - the outlet of the second secondary fl uiden outlet from the second heat exchanger is arranged inside the front heat exchanger. the heat exchanger outlet for the first selcimdära fl uiden.

Usually, a coupling block according to the present invention comprises means for depressurizing a circuit and draining the device from the device, the connecting block usually comprising means for depressurizing at least the primary circuit and draining the fluid from the device. .

As usual, at least one working unit usually comprises a closed heat transfer circuit for tempering an ambient medium by means of the secondary fluid flowing in the circulation circuit, wherein one of the heat transfer or shunted circuits of the device is included. This circulation circuit is preferably a heating system with so-called water-borne heat for a property, but can also be a cooling system such as an air-conditioning or air-conditioning system. A heat transfer device according to the invention may also comprise consumers in the form of circulation circuits arranged as heating or cooling systems in machines and the like. In devices which comprise a dryer in the form of a heat-transmitting circulation circuit, it is advantageous to arrange a circulation pump in order to maintain a primary and / or secondary circulation in the circulation circuit. In devices according to the invention, it is preferred to arrange such a pump integrated in or at least closely associated with the coupling block. Preferably, it is arranged so that it applies its pumping action in one of the internal channels of the coupling block for the current secondary current and / or for the current primary current. It has in many cases also proved advantageous to include in the coupling block integrated valves for filling and draining the primary circuit or the consumer circuit, safety valves, non-return valve and the like for such a circuit as well as primary and secondary lamps and deaerators for such a circuit.

Another type of common consumer of a heat transfer device according to the present invention is a circuit which comprises at least one tapping point for a tempered secondary outlet, such as a hot water circuit or system. According to a preferred embodiment, the heat exchanger of the heat transfer device is connected to a system comprising at least one tap point, such as a hot water system, while the other heat transfer device of the device, which may be a heat exchanger but also a shunt circuit or the like, is connected to a circulation circuit for tempering a surrounding medium, such as a heating system in a property or the like.

The primary liquid may be a cooling medium, such as cooling water, but is preferably a heating medium. The primary fl uid is obtained from an external source such as a heating plant, a heating plant, a boiler, a heat pump, a cooling system or the like. It can also consist of so-called waste heat from an industrial process. According to a preferred embodiment, the external primary source is a district heating network which delivers a primary form of hot water to a heating plant in a smaller property for the production of domestic hot water and hot water for the property's heating system. Such a heating plant includes; 0 QI ~ Q o »10 20 C71 .Y -3 (n xß ._. \ \ 'L 17 - a first heat transfer circuit in the form of a plate heat exchanger arranged for the production of domestic hot water, cold water being heated with hot water from a tar heating network - a second heat transfer circuit in the form of a plate heat exchanger or a shunt circuit for the production of hot water to a circulating circuit for water-borne heating and - a coupling block in the form of a coupling plate comprising internal channels with control means for the thermal processes, respectively from the heat transfer circuits, distributing means for filling a heat-exchanged circulation circuit and that the main connections for the central heating are coordinated to a connection block on one of the coupler plate storytellers. closing of the heating plant from the external connecting k retsarna. Furthermore, preferably such a heating plant according to the present invention also comprises integrated temperature sensors and means for draining one or more of the surfaces, at least the primary surface. Preferably, the means for controlling the thermal processes in the heat exchanger such as valves, circulation pumps, and the like as well as valves for filling the circuits and safety valves, expansion vessels or similar means for ensuring the circulation and desired pressure in the circuits are arranged integrated in the coupling block or at least associated with a modular unit with the connector block. This results in a compact modular heating plant comprising one or two plate heat exchangers and a coupling plate with a high degree of function integration and system thinking. The compact friend center can be quickly and easily detached from the connecting external circuits by means of the connection block and thus easily replaceable for service, repair, tuning, upgrading and similar work. The highly integrated modular unit can advantageously also comprise coordinated connections for electricity and signals to and from the control means so that they are also arranged on the storyteller of the coupling plate which comprises the connection block.

Such a modular heating plant comprising a heat transfer device according to the present invention can advantageously be accommodated in a discrete control cabinet which is installed so that it is always available to the operator of the district heating network independently of the property owner. The appliance cabinet should include sufficient insulation so that under conditions prevailing at the installation site during the winter, a frost-free environment can be maintained in the cabinet even during a longer drift fi saw break, for example a drift fi saw break of up to 24 hours. The cabinet can be installed so that the air in the cabinet communicates with the property, whereby an air exchange between cabinet and property is achieved. Such an air exchange reduces the risks that the temperature in the cabinet will be too low or too high. The cabinet containing the central heating can be facade-mounted in the property, in an outbuilding such as a storage room or a garage or freestanding. The advantage of façade installation in a building or outbuilding is that the risk and sensitivity to cooling in the event of a power outage in winter is significantly reduced. The bottom of the cabinet is at least partially open and connects with a base or similar to the ledning scarring network's service line which runs in a so-called fi scar heating wedge. Obvious advantages of a compact, easily accessible, scar heating plant containing a heat transfer device according to the present invention and with coordinated connections are; Cheaper and simpler culvert connection of the district heating network's service line; - More rational management construction; - No costly sealing problems around the pipe in the wall penetration of the ground; - Always accessible "service valves"; - Reduced risk of damage in and to the building caused by leakage; - No building volume needs to be used; Cheaper, simpler and more rational installation and connection; - Rational and high-function integrated fi scarring plant composed and tuned for commissioning; - Can be delivered to the factory with meters and control equipment; - Can also accommodate cold water meters; - Always accessible meter for service, replacement and reading; - Always accessible fi scarring center for service, upgrade, replacement, etc.

- Compact unit with a high degree of integrated functions; - Easily and quickly detachable; - Can be serviced and tested in a good environment, e.g. in workshop; - Low weight, preferably under 20 kg that can, and from a work environment point of view, be handled by one person; and - Simpler management. 10 l5 20 oo »ooo O o Overall, many of the benefits lead to new opportunities for heat suppliers to develop a new system thinking around connection and management of district heating in smaller properties. Not least, it is about developing a clearer interface and responsibility for each customer's and supplier's facility.

In addition, the compact flat coupling block used in some embodiments, which is made up of a number of channel plates, offers a large degree of flexibility in terms of choice of manufacturing methods and dimensioning. The channel plates and the thinner disc-shaped elements can be punched, milled or cut out. Depending on the choice of material, welding cutting, laser cutting or water jet cutting can be used. Of course, duct tiles with inlaid duct walls can also be used. These duct plates with recesses or inlaid partitions are then stacked on top of each other to form a duct block with the desired dimensioning and design of the inner ducts and with gable plates comprising connections for the various water systems, peripheral equipment and the like.

By stacking duct plates of selectable thickness and with variable and selectable design of the recesses in a selectable number, during the actual manufacturing a flexibility is obtained in the choice of duct area which gives great ability for hydraulic capacity adjustment and also for integration of components such as sensors, regulators etc.

FIGURES The invention will be explained in more detail below and exemplified by a preferred embodiment with reference to the accompanying figures.

Figure 1 shows a basic circuit diagram for a heat transfer device according to an embodiment of the invention comprising a heat exchanger, preferably a water heater.

Figure 2 shows a basic circuit diagram for a heat transfer device according to an alternative embodiment of the invention comprising a heat weaver and a shunt circuit.

Figure 3 shows a basic circuit diagram for a heat transfer device according to a preferred embodiment of the invention comprising two heat shields. a o o o o o .. oo o o oooo ooo oo ooo o. . _ I _,,. Figure 4a shows a heat transfer device comprising a connecting member, two ends, a number of disc-shaped channel plates with recesses which are arranged to be fitted to a coupling plate with internal channel system for connection of the heat transfer device according to an embodiment of the invention comprising a heat exchanger in the form of a water heater.

Figure 4b shows a heat transfer device comprising a connecting member, two ends, a number of disc-shaped channel plates with recesses which are arranged to be assembled to a coupling plate with internal channel system for connection of the heat transfer device according to an embodiment of the device comprising a heat exchanger and a heat exchanger.

Figure 4c shows a heat transfer device comprising a connecting member, two ends, a number of disc-shaped channel plates with recesses which are arranged to be assembled into a coupling plate with internal channel system for connection of the heat transfer device according to an embodiment of the invention comprising two heat exchangers.

Figure 5 shows a differential pressure regulator intended to be integrated in a coupling plate for a heat transfer device according to some embodiment of the invention.

Figure 6a shows a fate meter suitable for being integrated in the coupling block for sensing the flow in a channel in a heat transfer device according to an embodiment of the present invention.

Figure 6b shows in detail the upper part of the same type of master's master or sensor cylinder in a variant with a piston with a shorter extension in the axial direction and alternative sealing between piston and cylinder.

Figure 6c shows in detail the upper part of the same type of master's master or sensor cylinder in an embodiment of the present invention with a switch in the upper end position.

Figure 7 shows a valve suitable for being integrated in the coupling block for manipulating the flow in a duct in a heat transfer device according to an embodiment of the present invention.

The valve is suitably associated with a fate meter according to any of the variants of Figures 6a-6f 10 15 20 25 15 917 into '"\ ¿. 21 or combinations of these constituent parts but can also be controlled from another suitable control means which affects the position of the movable piston in the valve cylinder.

Figure 8a shows a variant of a compensating unit of the scalding protection type, suitable for being associated with a fate meter according to Figures 6a-6c and a valve according to Figure 7 or 9 included in a system of sensors and adjusting means for regulating the fate of a channel. in a heat transfer device according to the present invention, Figure 8b shows an alternative compensation unit, of a type which, in addition to scalding protection, can offer a basic heat retention function for the water heater and thus an indirect heat retention of incoming primary fl uid via a circulation passage.

Figure 9 shows a controlled valve comprising a partially integrated compensation unit, of a type which can offer adjustment for the temperature of incoming primary fl uid and via circulation passage a direct heat holding furilction for incoming primary fl uid, suitable for, associated with a fl fate meter according to any of the variants i fi gur 6a-6f and possibly an additional compensation unit according to fi gur Sa are part of a system of sensors and adjusting means for regulating the flow in a duct in a heat transfer device according to the present invention.

DESCRIPTION OF THE DRAWINGS The description of preferred embodiments will largely be concentrated on the use of a heat transfer device according to the present invention as a heating plant in a smaller property. However, the use is not limited to this, but a number of areas of use will appear to those skilled in the art as equally interesting and obvious in this description in its entirety and the forthcoming description of preferred embodiments in particular. In the schematic figures 1-3, as far as possible, accepted or generally accepted symbols in the field have been used for the constituent components. For this reason, and in order not to unnecessarily burden the ur gures and fi gure description and thereby risk obscuring the description of the invention, not all components shown have been assigned a reference numeral. The schematic circuit diagram shown in Figure 1 comprises a connection block 1, a heat exchanger 3, a coupling plate 2, a consumer 5, for example a domestic hot water system and an external hot water source 6, for example a hot water boiler. The heat exchanger 3 in Figure 1 is, for example, a water heater 3 which is supplied with cold water, which is heated with hot water from the boiler 6 which passes the heat exchanger 3 against the cold water. The heat exchanger includes inlets for cold water and outlets for the heated domestic hot water as well as inlets for incoming hot water and outlets for hot water return. The coupling plate 2 comprises main connections for the inflow and outflow of the two outlets from the device from and / or to the boiler and the domestic hot water system, sub-connections for connection to the inlet and outlet of the heat exchanger 3 and internal channels 2a, 2b, 2c, 2d which connect to a corresponding sub-connection , which is described below. In some embodiments, it is advantageous to coordinate all the main connections to connect to a connection block 1 on one story surface of the coupling plate 2.

Depending on the external connecting system, such a connection block can be arranged on the story surface facing away from the heat exchanger as shown in Figure 1 or on the opposite story surface. It is also advantageous to arrange the connection block 1 with connection valves and to coordinate the opening and closing of two or more of these valves. Furthermore, from the point of view of production and visibility, it is advantageous according to the embodiment of the invention shown in Figure 4a to use a coupling plate which comprises a number of stacked and connected channel plates, two ends and an intermediate plate, where the channel plates have recesses or with intermediate separations provided by lane walls which in the jointed coupling plate cooperate and form the inner channels and other inner cavities as required. In many cases, it is preferred in order to obtain a great deal of flexibility for the adaptation of hydraulic production and an optimized rational production that one or more of the channel plates is in turn built up of a number of thin disc-shaped elements which are bonded together. Preferably, solder is used to bond the channel plates, the ends, the intermediate discs and / or the disc-shaped elements together.

The cold water enters the heat transfer device through a first main connection and is led to the inlet of the water heater 3 via a first internal channel 2c arranged in the plate 2 and a first sub-connection to the inlet of the water heater 3 for tap water, secondary fl uid, and into and through the water heater 3 where it is heated by parm hot water which passes the water heater 3 in countercurrent to the tap water. The heated tap water, the tap hot water, leaves the water heater 3 and is led into the coupling plate 2, and further via a second inner channel 2d to a second main connection, which connects to a system Sb with one or fl your tap hot water points.

The first internal channel 2c for supplying cold water to the water heater 3 also has a fate-distributing means, illustrated in Figure 1 as a branch 7a.

This branch 7a enables the filling of water to the extreme primary fl circuit 6, which in the embodiment according to fi gur 1 consists of a hot water circuit 6, for example a boiler water circuit. The hot boiler water 6a is supplied to the device via a third main connection and is led via a third inner channel 2a to a third sub-connection which connects to the water heater 3 inlet for boiler water, primary fl uid, through the water heater 3 and out to a lower water connection. is led via a fourth internal channel 2b to a fourth main connection and returns as boiler water return 6b to the boiler. The fourth inner channel 2b for the boiler water return comprises a second branch 7b which is connected to the branch 7a in the first inner channel 2c, whereby if necessary new water in the form of cold water can be supplied to the boiler water return 6b, e.g. . for filling an expansion vessel connected to the circuit, not shown. The third inner channel 2a for supplying hot water to the water heater comprises a valve 8a which regulates the flow of boiler water through the water heater 3 from the flow of tap water in the water heater 3, in Figure 1 the valve 8a is placed in channel 2b to regulate the flow of heat based on the cold water fl fate. This input is sensed by means of a flow meter 8b arranged in the channel 2c, for supplying cold water to the water heater, which is associated with the valve 8a. The flow meter 8b can also be electrically associated with a circulation pump 9 for the boiler water, which is preferably arranged to start at a signal generated by the fate meter 8b at a predetermined fate and conversely stopped at another fate. The pump 9 generates its pumping action directly in or in immediate connection with the coupling plate. The valve 8a may, if necessary, be associated with a number of compensation units 8c, 8d which compensate the opening of the control valve on the basis of further variables such as the temperature of the boiler water supplied to the water heater 8c or the temperature of the domestic hot water leaving the water heater 8d. This last compensation is often regarded as a safety measure to avoid personal injury and can therefore, if necessary, be associated with a means which can quickly restrict the boiler water supply in order to quickly reduce the hot water temperature. The third inner channel 2a may also comprise a differential pressure valve 4 for keeping the differential pressure constant between the incoming primary flow after valve 4 and the primary return flow before the pump 9. Of course, this construction of a heat transfer device according to device - can be used for other purposes including the production of heating as well as cooling media.

The consumer in Figure 1 comprises a cold water source Sa, a tap system Sb for the hot water produced in the heat transfer device, a tap system Sc for cold water.

The device shown in Figure 2 is, for example, a heating plant for the production of domestic hot water 15b and hot water for a heating system 15d intended for use in a smaller property 15. The heating plant comprises a connection block 11, a coupling block or plate 12, a heat exchanger 13 for the production of domestic hot water, and a shunt circuit comprising a shunt line 14 for the production of hot water for the property's heating system l5d. The coupling plate 12 comprises internal channels 12a-12f, fate-distributing means 17a, 17b, fate-connecting means 17c, 17d, main connections, sub-connections and control means 15f, 18a, 18b, 18c, 18d for the thermal processes. The connection block 11 comprises means for connecting the heat transfer device according to the present arrangement to an external hot water source 16, for example a district heating network, a consumer 15 with one or more circuits 15b, ldd connected to the friend transferring device, for example a heat system lpv and a tap water system 15b. The district heating network 16 connects to the connection block 11 with an inlet for district heating water 16a and an outlet for district heating 166. The consumer is, for example, a smaller property 15 with a cold water source 15a, a tap circuit with one or more hot water taps 15b, a tap circuit with one or three cold water taps 15c and a heating system 15d. The heating system 15d may be associated with a control unit 15e with a sensor 15g for sensing the outdoor temperature and a sensor 15h for sensing the temperature of the water supplied to the heating system 15d. The sensors 15g, 15h and the control unit 15e may be associated with the heat transfer device for controlling the production of the hot water in the heating system, for example the control unit 15e controls the dilution of new hot primary hot water in the heating system 15d. This dilution is controlled indirectly by a valve 15f which affects the return from the heating system to the district heating return. The control unit 15e can also be associated with sensors for sensing inside the property. 917 10 l5 20 52.3 25 The heat exchanger 13 is for instance arranged for the production of domestic hot water and cold water is supplied which is heated with hot water, for example teal heat water, which passes the heat exchanger countercurrent to the cold water. The heat exchanger 13 includes inlets for cold water and outlets for domestic hot water as well as inlets for incoming scar water 16a and outlets for district heat return 16b.

The coupling plate 12 comprises; - main connections for additional fi scar heat, district heating return, additional cold water, domestic hot water, incoming return from the heating system and outgoing heated water to the heating system, - sub-connections for connection to the heat exchanger inlet and outlet and for connection to shunt circuit l2, 2c, l2e, 12f, which connect a main connection to the corresponding sub-connection, which is described in more detail in the following, 14 and the channel 12b for the return of the district heating water, the destructive means l7d for interconnecting the return from the heat exchanger 13 and the shunt circuit, the fate connecting means 17c for connecting via the shunt circuit, the district heating water via the shunt circuit 14 , - governing or l5f, l8a, l8b, 18c, l8d to control and monitor the thermal processes, - means for purification, degassing, pressure drop, fl direction of control, temperature monitoring, etc., - circulation pump 19 for the return of the heating system, - differential pressure valve 10 for constant maintenance of the pressure value 12a after the valve 10 and the scar return 12b.

In addition, in some embodiments it is advantageous to coordinate all the main connections connected to a connection block 11 on one story surface of the coupling plate 12. Depending on the external closing system, such a connection block 11 can be arranged on the story surface facing away from the heat exchanger 13 or on the opposite story surface. It is also advantageous to arrange the connection block with connection valves for the external circuits inlet and outlet to the respective 917. : ÅÄÉ- ä '- = ZÉ 525 917 .. .. 26 from the heat transfer device and to coordinate the opening and closing of two or fl er of these valves. Furthermore, from the point of view of production and flexibility, it is advantageous according to the embodiment of the invention shown in Figure 4b to use a coupling plate which comprises ends, intermediate plate and a number of stacked and connected channel plates, where the channel plates have recesses or with partitions made separations which in the composite coupling plate interact and form the inner channels and other inner cavities as needed. In many cases, it is preferred in order to obtain a great deal of flexibility for the adaptation of hydraulic production and an optimized rational production that one or more of the channel plates is in turn built up of a number of thin disc-shaped elements which are connected together. Solder is preferably used to bond the channel plates, the ends, the intermediate discs and / or the disc-shaped elements together.

Incoming external water, which typically for the application of the device has a substantially constant temperature of about 65 ° C, is supplied to the device with an inlet 16a via the connection block 11 to a first main connection arranged on the coupling plate 12 and is passed through an inner channel 12a in which it is distributed in a distribution point 17a between the heat exchanger 13 for the production of domestic hot water to the domestic hot water circuit 15b and the shunted heat return 12e, 12f the shunt line 14 and the heating system 15d. The distribution point 17a can, as indicated in Figure 2, be a duct branch in which a duct for supplying fi scar heat to the shunt circuit connects to the duct. The channel branch can also be designed as the starting point for two pipes, one arranged in the other, where one channel is constituted by the outer space between the pipe walls and the other channel by the interior of the inner pipe. The duct 12a connects downstream of the branch 17a to the sub-connection for additional scar water water to the heat exchanger 13 and the duct 12e connects to the shunt circuit with the shunt line 14 and the heating system 15d associated therewith.

A part of the scar water heats leaves the coupling plate 12 and is then led to the inlet of the heat exchanger 13 for incoming heat scar water through the heat exchanger 13 in countercurrent with the domestic hot water heated in the heat exchanger 13. The district heating water leaves the heat exchanger 13 in an outlet which connects to the sub-connection of the coupling plate 12 and further into the duct 12b where it, at the distribution point 17d, is connected with the return from the heating circuit 15d and the shunt circuit Un (II xD ... à \ 'l 27 via the duct 12f and the channel 14b, before leaving the coupling plate 12 and the device through the main connection for fi scar return 16b.

Another part of the district heating water continues in the coupling plate 12 and is led to the shunt circuit, which is associated with the heating system and comprises a shunt line 14 with non-return valve and a distribution point 17a and a connection point 17c. The shunt line 14 is arranged to supply return from the heating system 15d to the district heating water at the connection point 17c before the mixed water is supplied to the heating system 15d. The heating system return supplied through the shunt line 14 has been taken out at the distribution point 17b, downstream of the heating system 15d, and has a lower temperature than incoming thermal water, whereby the temperature of the water supplied to the heating system can be regulated. The district heating water leaves the shunt circuit in the coupling plate 12 via the duct 14b and the control means l5f and continues into the duct 12b where it, at the joining point 17d, is connected to the remnant return from the heat exchanger 13, before leaving the coupling plate 12 and the device through the main connection 16.

The inner channel 12a may be provided with a differential pressure valve 10 according to 5 gur 5 for keeping the pressure difference between incoming fi scar water in channel 12a after the valve 10 and fi the scar heat return in channel 12b at the valve 10. The inner channel 12b comprises a controlled valve 18a, preferably of the type described in more detail with reference to Figures 6 and 7 and Figure 8 or 9. The valve 18a which is located in channel 12b for heat return from the heat exchanger 13 controls the heat water. through the heat exchanger 13 from the flow of incoming tap water in the channel 12c, which is sensed by means of a flow meter 18b associated with the control valve 18a. If necessary, the setting of the valve 18a is adjusted and, in order to influence the incoming 'scar heat', by means of grain cleaning units. associated with valve l8a. Of course, a lik-; ' '°; A conventional valve or a conventional valve 15ff is provided for the shunt circuit to control the withdrawal of: z z scar water in this circuit. Cold water for the production of domestic hot water is supplied to the heating plant through a main connection arranged on the coupling plate 12 and is then led through an internal channel 12c, in which the flow meter 18b is arranged, to the inlet of the heat exchanger 13 for cold water. The water is then heated during the passage through the heat exchanger 13 by the countercurrently destructive scar heat water. The heated domestic hot water drains the heat exchanger 13, is supplied to the coupling plate 12 and is led through the channel 12d to the main connection, which connects to a system 15d comprising at least one tap hot water. If necessary, a temperature sensor 18d can be arranged in the channel 12d to sense the temperature of domestic hot water and at too high a temperature affect the output of the scarred water from the heat exchanger and thus the thermal process in the heat exchanger 13 through the control valve 18a. In this way a scalding protection is obtained.

Return water from the property's heating system ldd is supplied to the heating plant through a main connection arranged on the coupling plate 12 and is then led through an internal duct l2e further into the shunt circuit 14 described above, including duct 14b, control valve 15f and heating system 15d. The water tempered with the shunt circuit for heating system l5d is supplied, downstream of the shunt circuit, further in the coupling plate 12 and via the channel 12a to the main connection, from where it is led out in the heating system l5d to the circulation pump 19, which generates its pumping action directly in or immediately adjacent to the coupling plate 12 .

Figure 3 shows a preferred embodiment of a heating plant for the production of hot water for a tap circuit 25b and hot water for a heating system 25d intended for use in a smaller property comprising a combined heat exchanger for simultaneous production of hot water and hot water for heating. The heating plant comprises a connection block 21, a coupling block or plate 22, a combined heat exchanger with a first heat exchanger 23a, which is arranged for the production of hot water for the heating system 25d of the property, and a second heat exchanger 23b for the production of domestic hot water 25b. The coupling plate 22 includes internal channels 22a-22f, fate distribution means 27a, 27b, fate sampling means 27c, 27d main connections, sub-connections and control means 25fl28a, 28b, 28c, 28d for the thermal processes. The connection block 21 comprises means for connecting the heat transfer device according to the present invention to an external hot water source 26, for example a single heating network, a consumer 25 with one or more circuits 25b, 25d connected to the heat ac 00 ouo 91 7 5 12 5 9 The transmitting device, for example a heating system 25d and a domestic hot water system 25b.

The district heating network 26 connects to the connection block 21 with an inlet 26a for district heating water and an outlet 26b for district heating. The consumer is, for example, a smaller property 25 with a cold water source 25a, a tapping circuit with one or more tapping points for hot water 25h, a tapping circuit with one or three tapping points for cold water 25c, a heating system 25d. The heating system 25d may be associated with a control unit 25e with a sensor 25g for sensing the outdoor temperature and a sensor 25h for sensing the temperature of the water supplied to the heating system 25d, which may be associated with the heat transfer device for controlling the tempering. of the hot water in the heating system, for example, the control unit 25e directs the supply of external water to the heat exchanger 23a for the heating system 25d. This fate is controlled indirectly by a valve 25f which affects the scar heat return from the heat exchanger 23 a. The control unit 25e can also be associated with sensors for sensing the temperature inside the property.

The two plate heat exchangers 23a, 23b of the heat exchanger have all inlets and outlets arranged on the end of the heat plate arranged against the coupling plate 22. The first heat exchanger 23a then abuts the second heat exchanger 23b in such a way that the first heat exchanger 23a lies with its rear end against the connection end of the second heat exchanger 23b. The first heat exchanger 23a has a through-channel arranged inside the inlets and the outlets, respectively, wherein the second heat exchanger 23b comprises inlets and outlets of which at least three are arranged with extended bounces which are inserted into or through the first heat exchanger 23a. channel. The through-channels and the bounces are preferably arranged to form integral parts of the inlet and outlet of the heat exchanger, respectively. The inlet and outlet of the plate heat exchangers 23a, 23b are preferably coordinated in such a way that; the channel for the inertial heat exchanger 23b in the second heat exchanger 23b is common to or arranged inside the inlet of the first heat exchanger 23a for the scarred water, the cold water inlet in the second heat exchanger 23b is arranged inside the inlet of the first heat exchanger 23a for the heating system, and the channel for the outlet of the hot water from the second heat exchanger 23b is arranged inside the outlet of the first heat exchanger 23a system. 10 15 20 25 .30 01 t J C11 mf) * <1 30 The coupling plate 22 comprises; - main connections for additional district heating, fl scar heat return, additional cold water, domestic hot water, incoming return from the heating system and outgoing heated water to the heating system, - sub-connections for connection to the heat exchanger inlet and outlet and for connection to the shunt circuit 22, 22 internal channels, ", 22c, 22d, 22e, 22f, which connect a main connection to the corresponding sub-connection, which is described in more detail in the following, to the heating system 25d for filling, fl fateful means 27c for connecting return 22b 'and 22b "from the heaters 23a and 23b and fl fate connecting means 27d for connecting cold water and heating system water for filling the heating system 25d, and its expansion vessel, - control means 25fl28 a, 28b, 28c, 28d for control and over monitor the thermal processes, - means for purification, degassing, pressure lowering, flow direction control, temperature monitoring, etc., - circulation pump 29 for the heating system 25d water, - differential pressure valve 24 for keeping the pressure difference constant between the district heating water inlet 22a and the return 22.

Like the heating plant in Figure 2, it is also advantageous in certain embodiments of this heating plant shown in Figure 3 to coordinate all the main connections of the coupling plate to be connected to connection blocks 21 on one story surface of the coupling plate 22. Depending on external connecting circuits 25a, 25b, 25d, 26, such a connection block can be arranged on the story surface facing the heat exchanger or on the opposite story surface. It is also advantageous to arrange the connection block with connection valves and to coordinate the opening and closing of two or more of these valves. Furthermore, from the point of view of production and accessibility, it is advantageous according to the embodiment of the invention shown in Figure 4c to use a coupling plate 22 which comprises a number of stacked and interconnected duct plates, two ends and one or more intermediate plates where the duct plates have recesses or partitions provided. 3 1 separations which in the composite coupling plate cooperate and form the inner channels and other inner cavities as required. In many cases, in order to obtain a large flexibility for the adaptation of hydraulic production and an optimized rational production, it is preferred that one or more of the channel plates in turn are built up of a plurality of thin disc-shaped elements which are bonded together. Preferably, solder is used to bond the channel plates, the ends, the intermediate disks and / or the disk-shaped elements together.

Incoming district heating water is led via a district heating inlet 26a and supplied to the device via a connection plate to a first main connection arranged on the coupling plate 22 and is passed further through an inner channel 22a in which it is distributed at a distribution point 27a between a first heat exchanger 23a for production hot water for the property's heating system 25d and a second heat exchanger 23b for the production of domestic hot water for the property's domestic hot water system 25b. The distribution point 27a may be a duct branch or, as shown in the clock, consist of a common inlet duct for the two plate heat exchangers 23a and 23b for supplying scar heat water to the plate heat tissues 23 a, 23b. In the illustrated case, in practice the distribution point 27a consists of a plurality of individual distribution points extending through the inlet duct 23a of the entire plate heat sink 23a, the number of which is equal to the number of plate channels for tar heat water in the plate heat exchanger 23 a. and the common inlet duct for the heat exchanger described above, in which a part is distributed to the inlet of the heat exchanger 23a arranged for the production of hot water for the heat system 25d for incoming scar water and is passed through the heat exchanger 23a in countercurrent to the heat in the heat exchanger. the heating system 25d. The district heating water leaves the heat exchanger 23a in the outlet which connects to the lower connection of the coupling plate 22 and further into the channel 22b 'where it, at the joining point 27c, is connected to the return from the second plate heat exchanger 23b, E. . before leaving the coupling plate 22 and the device through the main connection for district heating return 26b. 5 9 fl 7 E "2": '.' n '' u .- n 32 Another part of the scar water which leaves the coupling plate 22 and is led into the heat exchanger is led to the plate heat exchanger 23b for the production of hot water to the hot water circuit 26b. The district heating water is led countercurrent to the tap water through the plate heat exchanger 23b and leaves the plate heat exchanger 23b and returned to the coupling plate 22 and further through the duct 22 "to the connection point 27c, where it is connected with the return from the heat exchanger 23a, before leaving the coupling plate 22. fi ärrvärdneretiir 26b.

The inner duct 22a preferably includes a diner pressure valve 24, according to Figure 5, for maintaining the pressure difference between incoming district heating water in the inlet duct 22a after the valve 24 and the return in the outlet duct 22b at the valve 24.

The inner channel 22b "comprises a valve 28a, preferably of the type described in more detail with reference to fi gures 6 and 7 and ur gur 8 or 9. The valve 28a, which is arranged in the channel 22b" for return fi from the domestic hot water heat exchanger 23b controls the flow of the scar water water through the heat exchanger 23b based on the flow of incoming tap water in the channel 22d, which is sensed by means of a flow meter 28b associated with the valve 28a. If necessary, the setting of the valve 28a is adjusted and in order to influence the incoming district heating by means of compensation units 28c, 28d which sense the temperature of the incoming hot water in the duct 22a and the temperature of the outgoing hot water in duct 22c by means of temperature sensors 28c, 28d arranged in these ducts. which are associated with the control valve 28a. Of course, a similar valve or a conventional valve 25f can be provided to control the process in the second heat exchanger 23a.

Cold water for the production of domestic hot water is supplied to the heating plant through a main connection arranged on the connection plate 22 and is then led through an internal channel 22d, in which the flow meter 28b is arranged, to the inlet of the domestic hot water heat exchanger 23b for cold water.

The water is then heated during the passage through the heat exchanger 23b by the countercurrently destructive tar heat water. The heated domestic hot water leaves the heat exchanger 23b in the outlet and is supplied to the coupling plate 22 and is led through the channel 22c to the main connection, which connects to a system 25b comprising at least one domestic hot tap. If necessary, a temperature sensor 28d can be arranged in the duct 22c to sense the temperature of the domestic hot water and at too high a temperature affect the inlet of the tar heat water in the heat exchanger 23b. by actuation of the valve 28a. In this way a scalding protection is obtained.

Return water from the property's heating system 25d is supplied to the heating plant through a main connection arranged on the coupling plate 22 and then led through an inner channel 22f to and further into the first heat exchanger 23a of the heat exchanger described above. The water tempered in the heat exchanger 23a for heating system 25d, the coupling plate 22 is again supplied through the sub-connection and passed on in the plate 22 to the circulating pump 29 of the heating system circuit, which generates its pumping action directly in or in immediate connection with the coupling plate 22 and continues via the channel 22e to the main connection.

Figures 4a, 4b and 4c show partially divided heat transfer devices according to preferred embodiments of the heating corresponding to those schematically shown in Figures 1-3. The devices, which are very compact, comprise heat exchangers 43, 43a, 43b, coupling blocks 42 and connection blocks 41. The heat exchanger 43 or the heat exchangers 43a, 43b are so-called plate turning exchangers which all have their inlets and outlets arranged on the same story surface, gable.

The heat transfer device according to Figure 4a is preferably intended to be used as a water heater and comprises a connection block, a coupling block 42 with two ends 42a, 42b, an intermediate plate 42c and a number of thinner disk-shaped elements composed of channel plates 42d, 42e and a plate heat exchanger 43. The ends, the partition plate and the channel plates 42a-42e have holes and sockets 422a-422e, etc., which when the ends, the partition plate and the channel plates the plates 42a-42e are assembled into a coupling plate 42 or a coupling block form inner channels for: - incoming primary 422a, preferably hot water, such as boiler hot water; - primary fl uid return 422b, boiler return; incoming secondary 42 uid 422c, preferably cold water; and - outgoing secondary fl uid 422d, domestic hot water; and other internal cavities 422e m. fl. suitable for accommodating in and on the coupling plate integrated functional equipment such as thermometers, control valves, filters, sensors, pumps, filling 512 5 9 1 7 f; 34, drain, clearing and safety valves, differential pressure regulator and similar components. The ends further include connection pads 423a-423d for the four connections to the two external systems and may include connection pads 424a-424d for the heat exchanger.

The ends also include the required bounces for attachment and mounting of the aforementioned integrated equipment, the composite channel and its parts also include holes for bushings of a lockable fastener 429 against the connection block 41. It is in many cases preferred to obtain a large fl flexibility for hydraulic production adaptation and an optimized rational production that one or more of the channel plates are built up of a plurality of thin disc-shaped elements which are connected together. Solder is preferably used to connect the channel plates, the ends, the intermediate discs and / or the disc-shaped elements.

The heat transfer device according to Figure 4b is preferably intended to be used as a heating plant in a smaller property for the preparation of domestic hot water and hot water for a heating system for heating the property. The heating plant comprises a connection block 41, a coupling block 42 with two ends 42a, 42b, an intermediate plate 42c and a number of thinner disk-shaped elements assembled into channel plates 42d, 42e and a shunt circuit, comprising an external heating circuit and a shunt conduit arranged in the coupling plate. The channel plates 42d, 42e, the intermediate plate 42c and the end caps 42a, 42b have holes and recesses 422f-422n, etc., which when the ends 42a, 42b, the intermediate plate 42c and the channel plates 42d, 42e are assembled into a coupling plate or a coupling block form inner channels for : - incoming primary fl uid 422f, preferably hot water, such as fi scar heat water; - primary fl uid return 422g, heater return; incoming first secondary 42 uid 422h, preferably cold water; - outgoing first secondary fl uid 422k, domestic hot water; incoming second secondary fl uid 4221, preferably return from the heating system ;, and - outgoing second secondary fl uid 422m, hot water to the heating system, and other internal cavities 422n m. fl. suitable for accommodating in and on the coupling plate integrated functional equipment such as thermometers, control valves, sensors, filters, pumps, drain, discharge, non-return and safety valves, differential pressure regulators and similar components. The ends further comprise connection pads 423 a-423f for the six connections to the three external systems and may also, as shown in the figure, comprise studs 424a-424d for an-: note OIIO I Il 0 Qcca oøcø 0 O 00 n 0 0 0 0 0 I 0 0 000 00 0 10 20 25 lT-'ïf 0.40 35 closing of the heat exchanger. The ends also include the required bounces for attachment and mounting of the aforementioned integrated equipment, the composite channel and its parts also include holes for penetrations of a lockable fastener 429 against the connection block 41. It is in many cases preferred to obtain a large fl feasibility for the adaptation of hydraulic production and an optimized rational production that one or fl era of the channel plates are built up of a fl number of thin disc-shaped elements which are bonded together. Solder is preferably used to connect the channel plates, the ends, the intermediate discs and / or the disc-shaped elements.

The heat transfer device according to Figure 4c is preferably intended to be used as a heating plant in a smaller property for the preparation of domestic hot water and hot water for a heating system for heating the property. The heating plant comprises a connection block 41, a coupling block 42 with two ends 42a, 42b, an intermediate plate 42c and a number of duct plates 42d, 42e and two plate heat exchangers 43a, 43b and an intermediate end 43c, which are alternatively replaced by four intermediate exchanges arranged between heat exchangers 43 a, 43b. The intermediate end 43c, which is soldered between the plate heat exchangers 43a and 43b, is arranged with three bounces through the connection channels of the plate heat exchangers 43a, 43b, 431a, 43 lb, 43lc which connect into the corresponding connections of the intermediate plate 42c. Alternatively, when the intermediate end 43c is replaced by intermediate spouts, the intermediate plate 424e, 424f, 424g are extended so that they reach into the intermediate spouts.

The ends 42a, 42b, the intermediate plate 42c and the channel plates 42d, 42e have holes and recesses 422f-422n, etc., which when assembled into a coupling plate 42 or a coupling block form internal channels 422f-422n for: preferably hot water, such as district heating water; - primary fl uid return 422g, fi scarred heat; incoming first secondary fl uid 422h, preferably cold water; - outgoing first secondary fl uid 422k, domestic hot water; incoming second secondary fl uid 4221, preferably return fi from the heating system ;, and - outgoing second secondary fl uid 422m, hot water to the heating system, and other internal cavities 422n m. fl. suitable for accommodating functional equipment integrated in and on the coupling plate, such as thermometers, control valves, sensors, filters, pumps, filling, draining, heating; non-return valves and safety valves, differential pressure regulator and similar components 15 15 36 25 01 Few 36 l components. The ends also include the required bounces for attachment and mounting of the above-mentioned integrated equipment, the composite duct and its parts also include holes for penetrations of a lockable fastening device 429 against the connection block 41. The is in many cases preferred in order to obtain a large fl flexibility for hydraulic production adaptation and an optimized rational production that one or fl era of the channel plates are built up of fl several thin disc-shaped elements which are bonded together. , the ends, the intermediate discs and / or the disc-shaped elements.

These compact devices built up of specially designed plate heat exchangers 43, 43a, 43b and with coupling blocks or preferably coupling plates have a large flexibility for design and dimensioning of the internal channels 422a-422d, 422f-422m as well as good conditions for easily and reliably integrating them. control means with sensors, compensation units and valves or other adjusting means in other cavities and recesses 422e, 422n in the coupling block. The ends 42a, 42b, the intermediate plate 42c and the channel plates 42d, 42e are brought together into a stack, whereby the holes and the recesses 422a-422e and 422f-422m etc. will form internal channels for the cavities and cavities to accommodate said components.

An advantage obtained by the flexibility offered by a channel block 42 constructed of channel plates is that the inner channels formed by the recesses 422a-422e and 422f-422m can be easily arranged to change plate or level if necessary to circumvent an obstacle such as a other duct a fastening device, peripheral equipment or the like. Such switching or displacement of ducts between plates or levels in coupling blocks may also be justified by the need to change the direction of the duct to obtain an optimal orientation of filters, pumps, valves regulators, sensors and the like, especially to optimally orient seats, parapets and similar for such equipment. In preferred embodiments where each channel plate 42d, 42e is constructed of a number of thinner disc-shaped elements, not shown, the channels 422a-e, 422f-m. dimensions and configuration are determined by the configuration, thickness, number and stacking sequence of the disc-shaped elements. With this coupling block comprising inner channels which are formed by the recesses 422a-422e and 422f-422m etc. when the thinner disc-shaped elements included in the channel plates 10d, 42e, 42e, 42e are stacked together with the ends 42a, 42b and the intermediate plate 42c in the desired order on each other, good conditions are obtained for easily producing a coupling plate with a high degree. of tions injection integration. For example, filter units, differential pressure regulators, pumps, control valves, fate sensors, temperature sensors and similar equipment can be installed integrated in the recesses in the coupling block and with connections on a suitable outer surface of the coupling block. The coupling block is arranged to be connected to a connection block 41, the coupling block being arranged with all the connection connections of all the main connections coordinated on a gable. The coupling block can be fully integrated with the adjacent heat exchanger 43, 43a as its one end. The channel plates 42d, 42e, the intermediate plate 42c and the ends 42a, 42b can be manufactured according to fl your possible methods such as: foaming or punching from materials of varying thickness, which gives great fl flexibility for capacity adjustment. The channel plates 42d, 42e can also be manufactured according to an inverted approach so that only the required partitions are built up in the plates which in a stack form internal channels in the same way as recesses. Of course, channel plates with recesses can be arranged alternately with channel plates A connection block 41 with coordinated main connections 41a-41f provided with connection valves for closing and opening the primary connections is usually provided with at least two of the connection valves coordinated for a simultaneous opening and closing, respectively. According to one embodiment, the connection valves for the primary fl uiden are coordinated for a simultaneous opening and closing of the primary fl uiden inlet and outlet, respectively. Likewise, the connection valves for at least one secondary fl uid can be coordinated to coordinate a simultaneous opening or closing of the inlet or outlet of the secondary fl uid. It is advantageous to coordinate at least three connection valves for simultaneous opening and closing of the affected outlets and inlets. Alternatively, in a plant for two parallel thermal processes, the three connection valves for the three fl uidem inlets may be coordinated for simultaneous opening and closing of the three fl uiderm inlets and / or the three connection valves for the three fl uidema outlets are coordinated for a simultaneous opening. respective closing of the outlets. Such a connection block 41 may, depending on the prevailing conditions, be as shown in Figs. 4a, 4b, 4c be arranged on the end face 42a facing away from the heat exchanger 43,43a, 43b or on the end face 42b facing the heat exchanger 43,43a, 43b. 00 00 00 0 0000 0000 IOI 0 0 0 00 0 u 000 0 0 c 0 g 5 0 0 0 0 0 0 0 0 0 00 00 00 000 00 0 10 15 20 30 38 Normally, the need for capacity varies very much between larger fi scarring centers. . For this reason, they are often more or less subject to an exact dimensioning, both of heat exchangers and control valves, where consideration is also given to where they are in the network and the prevailing differential pressure. For smaller facilities, and then especially for smaller properties such as villas, there is no room for such a dimensioning effort, but here you are more in need of large standardized series with, e.g. layout in capacity steps, the same equipment from station to station. If these smaller systems are to be able to fi operate well and be able to perform well in comfort, despite the fact that there are large differences between them in differential pressure exposure conditions, equipment is required that can keep the differential pressure constant to a certain specific level. This is described in the Swedish District Heating Association's Advice and Instructions, FVF 1997: 13, pages 9, 14 and 15, Comments on pages 6 and 18 in the article Din Fjärrvärme Central page 4.

A heat transfer device according to the present invention comprising a coupling block with internal channels offers uniquely simple conditions for integrating in the coupling block an even in itself simple and at the same time both easily produced and inexpensive ditference pressure regulator, which in one embodiment is shown in Figure 5.

The regulator in Fig. 5 comprises a spindle 50 which passes through the inner channels 51 for the scarring water inlet, FV against a inlet duct 5 in the main heating water connection 5 I a arranged seat 54. Furthermore, the regulator comprises a partition 55 in the partition wall between the ducts for the FV and FVNM 51.52. The differential pressure regulator shown in Figure 5 comprises a bounce 58a arranged on the coupling block with a valve cover 58b with a first upper pressure core arm 59, arranged to apply to the actuating piston 57 coordinated with the spindle 50 which acts against the upper surface of the actuating piston 57 and creates a closure through the actuating piston 57 and the spindle 50 acts on the cone 53 and seat 54. To influence the movements of the actuating piston 57 and In the operation of the valve there is also a second, lower, pressure chamber 60 and valve springs 61a, 6lb in series which act against the lower surface of the control piston and create an opening crane fi. The upper pressure chamber 59 of the control piston, which in this embodiment is arranged in a valve cover as associated with the coupling block, may in other embodiments be arranged in recesses inside the duct block, as well as the rest of the valve cover. In order to reduce the dimensions of the valve and avoid a large diaphragm and thus a strong spring, the regulator comprises a so-called pressure-relieved valve cone.

The pressure relief is effected by directing the reduced supply pressure on the channel 51a for FV, which loads the active area of the valve cone 53, in a channel 62 inserted in the center of the spindle 50 up into a third pressure chamber 63. The pressure chamber 63 is in the embodiment shown in Figure 5. valve cover 58b. The spindle 50 terminates at its upper end, which abuts the pressure chamber 63, with a piston 64, which abuts sealingly against the inner surfaces of the pressure chamber. In Figure 5, the seal is shown as an O-ring, but other sealing designs, such as self-sealing surfaces, can be used. The piston 64 connecting the spindle is built together with the actuating piston 57 and has a cross-sectional area which corresponds to the active area of the cone. The valve thereby becomes balanced and insensitive to the static pressure. The pressure relief duct 62 is provided with a nozzle 65, which partly forms a screw for the valve cone 53 and partly, because the duct 62b in the nozzle has a smaller diameter than the duct 62 in the spindle, constitutes a choke in the pressure relief duct 62. This choke in the liquid solder in and out from the pressure chamber 63, in the event of pressure changes which the valve compensates, the cone 53 and thus the entire movement of the spindle 50 dampens to an adapted and calm process. If the scar water is expected to contain particles which interfere with the action of the valve, the nozzle 65 can be provided with an inlet filter 65b, e.g. a sintered porous ceramic or metallic filter. The pressure from the inlet pressure reduced through the slit opening of the cone 53 towards the seat 54 is led up to the pressure chamber 59 of the control piston. and a casing 68. This slit channel 67 is then terminated with a number of small holes 69 in the upper end of the actuating piston 57 which open into the upper active chamber 59 of the actuating piston.This varying pressure loads the upper active area of the actuating piston 57 strives to close the valve. This closing crane fi is balanced for a desired differential pressure by a combined opening crane fi which is created and influenced by, - the return pressure which creates an opening crane directed from the valve seat fi by the pressure prevailing in the channel 52 for FVW acting on the lower active surface of the actuating piston 57. 20 25 30 BUY Yes .. 917 40 52, as shown in Figure 5, openly communicates with the pressure chamber 60 for the lower active surface of the control piston, which is substantially integrated in the channel 52 for the FVm, and - an opening groove created by the valves 6la, 6lb which likewise is directed from the valve seat 54 and selected and adapted from the outside for the differential pressure desired for the device. In order to be simple, functional and robust in the environment in which it is intended to be used, the valve is given a differential pressure determined in advance and at the time of manufacture, given by a certain ratio between the actuating piston 57 active areas in the upper and lower pressure vessels and the spring vessel. This determined differential pressure is then automatically maintained across the controlled circuits. In order to obtain a low proportionality deviation in the control ratio of the valve even in the event of a large variation in the degree of opening, the spring arrangement has been given a low fi spring constant despite installation in a low fi spring carriage height. That is, they have been designed so that a sufficient spring crane with a simultaneously low capercaillie constant is obtained despite a relatively short fi spring length. For example, this can be achieved with a spring arrangement comprising two springs 61a, 61b with different diameters but with equal spring force and spring constant associated with each other via a connecting sleeve 6lc and brought together in series and in circumference within the same spring frame height. In the embodiment shown in Figure 5, the valve seat 54 is connected to the intermediate bushing 55 and placed in the part of the channel 51 which constitutes the channel block inlet connection 70 for scarring and is sealed thereto, in the figure indicated by an o-ring seal.

It can be stated that, at least for smaller properties, the capacity needs to meet the domestic hot water preparation are essentially similar for the very most houses. This relationship creates both a need for and space for a simple, easy-to-manufacture and thus cheap hot water regulator. The equipment that is commercially available is either both unnecessarily large and expensive or lacks any essential function. They must therefore be supplemented with additional equipment. In a heat transfer device according to the present invention, it is based on this preference to use a regulator comprising at least one flow meter and a valve controlled by the flow meter, which are integrated in the coupling plate and arranged to control the primary value of the micro-heat water through the thermal water heater. The controller is based on a flow sensor which is illustrated by the switches 6a-6f and is preferably arranged to sense the flow in the secondary circuit whose flow, the hot water, is to be tempered by the primary flow in the heat exchanger. Figures 6a-6f show a fate meter and Figure 7 shows a valve, these components 10 as well as the compensation units shown in Figures 8a and 8b and the alternative valve in Figure 9 are integrated in the internal cavities of the coupling block and ducts, but they can of course also be arranged in their own adapted valve housings, which according to the present invention are then directly associated and functionally integrated with the coupling block. Of course, the components shown for other applications or the like can be used and installed in own valve housings which are adapted to the current duct or pipe system. The variants of components suitable for inclusion in such a regulator which are illustrated by Figures 6a-6c, 7, 5a, 8b and 9 are intended to be used to control a heat exchange process for hot water preparation and can be performed and combined in olika your different variants. depending on the external conditions it is to be able to handle but where the common "denominator" is always the donor according to Figures 6a-6c with a master cylinder, a piston movable in the master cylinder and a measuring piston. During production, the flow sensor can be given the desired characteristics for its function and for its interaction with the actuating member with which it cooperates. In its simplest variant, the controller includes a fate sensor combined with only one valve.

The flow meter illustrated by fi clocks 6a-6c comprises a measuring piston 82a, which by means of a spindle 82b is associated with a hydraulic master or sensor cylinder 81 filled with oil and a piston 82c axially movable in the sensor cylinder 81. Measuring piston 82a, spindle 82b and sensor movable piston 82c of the cylinder which are preferably mechanically connected to a unit together with other components arranged in connection with these parts are sometimes referred to in this application as sensor piston 82. The measuring piston 82a is according to the embodiment shown in Figure 6a arranged with a good fit, but not completely without gap 83, in a impeller 80 in a fl fate channel, for example the inlet channel for the cold water to a water heater. The measuring piston 82a comprises along its jacket a number of holes 82d or slots, whereby the measuring piston 82a is given a characteristic adapted to the expected fate and change of fate, as well as the character of the equipment and components otherwise connected. The measuring piston 82a has, in order to make the fate meter almost insensitive to the static pressure of the tap water, either a spindle arrangement balanced against the pressure or an extremely folded spindle 82b in relation to the active piston-cross-sectional area which connects the piston 82a to the outside the parapet hydraulic piston 82c. When a fate arises or changes, the measuring piston 82a is forced by the resulting dilation pressure in the cold water over the measuring piston 82a to be displaced in the impeller 80. In the event of an increased fate towards the open end of the impeller 80 into e.g. the water heater and with a reduced fl fate in the opposite direction. This is achieved by the net piston 82a striving to keep a hole area corresponding to the gap open through the holes 82d, 84a through the gap of the water or to create a corresponding opening area via slots. The pressure loss in the cold water channel which occurs over the piston 82a will vary with the open hole area set with the piston 82a according to a predetermined relation to a counterforce. Demia countercurrent is obtained by means of a spring arrangement arranged in an associated valve according to figur 7 or figur 9. The pressure drop is selected within such a low range, e.g. approx. 0.2 bar, that while it can be converted into a sufficient actuating force for the piston 82c of the sensor cylinder, it still does not create a troublesome pressure difference between hot and cold tap water in the tap water system.

To eliminate the risk of coatings on the spindle 82b from contaminants and particles in the water and thus a risk of malfunctions, the spindle 82b is in its entire active length in the water enclosed by a tube 82e with a small gap 82f against the spindle 82b. In this way, the water around the spindle 82b is not converted. The master or sensor cylinder 81 can be designed in two ways as shown in Figures 6a and 6b, either with the sensor cylinder 81 or its movable piston 82c, 82c 'as a machined sealing surface against a sealing o-ring. The top of the movable piston 82c, 82c 'is designed so that it simultaneously contains the function for attaching the spindle 82b and the function for adjusting the working area of the sensor piston 82. The top of the sensor cylinder 81 is designed to contain the function of adjusting a required stop of movement of the movable hydraulic piston 82c, 82c '. As shown in Figure 6c, the top of the sensor cylinder 81 can be designed and supplemented so that it contains an electric shutter / switch function 8 ld for starting and stopping e.g. a circulation pump. The protective tube 82e for the spindle 82b is attached to the lining used for the flow meter, for example in a screw which is inserted into the lattice. The end of the screw is designed as a seat for the o-ring seal of the spindle 82b in the parapet. Correspondingly, the spindle seal of the hydraulic cylinder 81 has been performed. The space between the o-rings is designed as a pressure relief with a leakage indication channel. The flow sensor is fixed in a groove ring on the cylinder shell via an overflow nut with an 8-edge wrench to a threaded bobbin soldered in the duct block over the cold water inlet to the heat exchanger. The valve is sealed to the inner jacket of the bounce via an o-ring seal.

The main cylinder 81 of the flow sensor transfers oil via a hydraulic line 81a to the slave cylinder of an associated valve, such as the valve shown in Figure 7 or 9. When changing the flow in the impeller 80, the movement of the transducer piston 82 generated by the sensor piston 82a and the oil thereby expelled / returned through the hydraulic line 8la from the respective into the main cylinder 81 is changed to change the position of a slave cylinder arranged in the valve slave cylinder. . in a ratio of 1:10 to the transducer of the transducer 82.

It is generally required that a control unit, comprising sensor piston 82, master cylinder 81, and a control unit in a valve or other actuator such as a slave cylinder with a movable piston associated with the valve cone, for example an actuator according to the valves shown in Figures 7 and 9, give rise to a proportional deflection of the setting of the actuator. This can preferably be obtained by transferring the position of the sensor piston by means of a hydraulic system to a hydraulic cylinder included in the actuator and affects the position of a movable piston arranged in this slave cylinder which is associated with, preferably mechanically connected to a valve cone or other in an actuator comprising actuator, whereby the setting of the actuator is affected.

These changes in the setting of the actuator can be based on a compensated value which includes a weighting of signals to the actuator from the output sensor and one or more compensation units. Such compensation is described in more detail in the following.

For heat transfer devices, there is a need for a simple, easy-to-manufacture and thus cheap hot water regulator. The controllers that are commercially available are either both unnecessarily large and expensive or lack any significant function. They must therefore be supplemented with 20 additional equipment. In a controller comprising a fate meter according to any of the variants in Figures 6a-6c and a controlled valve according to the embodiment shown in Figure 7, it is based on this to arrange the controller and its components integrated in a coupling plate included in a heat transfer device according to present invention for manipulating the fate of the district heating water or other equivalent of hot water through the heating boiler. The controller: 25 is based on a fate meter as described in connection with Figures 6a-6c, which in a preferred embodiment of the heat transfer device according to the present invention is - arranged to sense the inflow of cold water in the hot water circuit, and a valve according to fi gur É 'f 7, arranged to control the flow of hot water to the heat exchanger for the production of domestic hot water. Figures 8a and Sh show compensation units to be arranged integrated with the controlled valve and the fate sensor shown in Figure 7 as illustrated by Figures 6a-6c. Alternatively, one or more compensation units according to Figure 8a and a fate sensor according to Figures 6a-6c may be associated with a valve according to Figure 9 which comprises a partially built-in compensation unit.

Of course, the valve according to Figure 9 can be used together with a fate sensor without additional compensation units. The compensation units shown in Figures 8a, 8b and 9 are integrally arranged in a duct block arranged for a heat exchanger with internal cavities and ducts, but it can of course also be arranged in its own adapted valve housing, which according to the present invention is directly associated and functionally integrated with the coupling block. . Of course, this valve can be used and installed in other valve housings for other applications, which are adapted to the current duct or pipe system. The variants of the regulator illustrated with Figures 6a-6c, 7, 8a, 8b and 9 are intended to be used to control a heat exchange process for hot water preparation and can be performed and combined in fl your different variants depending on the external conditions it must be able to handle but where the common proximity is always the fate meter or the sensor according to Figures 6a-6c with its sensor cylinder 81 and sensor piston 82. The flow sensor can be given the desired characteristics during its manufacture to regulate RE. Preferably, the valve regulates the outgoing flow of fi scar heat return or hot water return from this heat exchanger from the outside sensed in fl flow of cold water in the domestic hot water circuit. In its simplest variant, the controller comprises a flow meter and a valve controlled by the fate meter, a suitable embodiment of which is shown in Figure 7 where the sensor cylinder 81 of the fate sensor is associated with a valve slave cylinder 85. This is provided that the following values and criteria are met: on incoming cold water is relatively constant, which in practice is also normal, about 10 ° C - the temperature of outgoing hot water must be kept at a predetermined level, e.g. 50 ° C, not too much deviating from the selectable temperature - the temperature of incoming heat water is relatively constant over time, e.g. 65 ° C - the differential pressure of the district heating water is relatively constant over time, e.g. 0.1 MPa - The scar heating service contains a limited amount of water - the distribution line (trunk) is always kept warm.

According to the embodiment shown in Figure 7, the slave cylinder 85 for the controlled valve is associated with the master cylinder 81 of the fate sensor via a hydraulic line 81a. Furthermore, the spring-loaded piston 86a of the slave cylinder is now attached to the spindle 86b of the controlled valve, which at its other end is fixed to the valve cone 86c. When tapping, the movement of oil generated by the sensor piston 82 is caused to be transferred via the hydraulic line 81a to the Slave cylinder 85 of the valve, whereby the slave piston 86a and the valve cone 86c connected to it by means of the spindle 86b are lyne, e.g. in a ratio of 1:10 to the transducer of the sensor piston 82k, whereby the valve gap between the valve cone 86c and the seat 87a is opened. When tapping decreases or ceases, a leather crank sin with its action on the slave piston 86a causes to lower or close the valve gap by lowering the valve cone 86c towards the seat 87a, and partly to return oil to the sensor cylinder 81 which in turn brings the sensor piston 82, including the to reduce its rash or return to its original position completely if the bottling ceases. A certain minimum amount of oil of atmospheric pressure remains in the slave cylinder 85 when the valve cone 86c is completely closed. The valve preferably has a pressure-relieved cone 86c, and a spring arrangement as described below. The valve cover 85a with pressure chamber 85b is suspended in the slave cylinder 85 and locked with locking screws. The upper jacket part of the slave cylinder 85 is slotted with 2-4 grooves for the adjustable fi spring retainer arrangement required to compensate for tolerances for the springs and to change and be able to set the desired hot water temperature to some extent. The end cap 85d of the valve is mounted on the jacket of the slave cylinder 85 and at the same time constitutes a support for the spring retainer arrangement and a knob for adjusting the spring force and thus also the hot water temperature. The capercaillie-loaded piston 86a forms the seat of the inner spring 86d and has an extended neck 86'a for assembly. The piston neck 86'a is connected to the spindle via 2-4 slotted screws. The spindle bushing of the breast is provided with double o-ring seals with intermediate pressure relief and drainage channel. The valve seat 87 a is connected to the bushing via threaded connections and immersed in the outlet pipe 87 of the duct block for the fi scarring water fi- from the water heater and sealed against the pipe 87 with an o-ring seal.

The valve is attached to a groove ring on the cylinder shell via an overhang nut with an S-edge wrench to a threaded bobbin soldered to the duct block over the iron heat outlet from the heat exchanger. The valve is sealed against the inner jacket of the bounce via an o-ring seal. The slave valve has i.a. to reduce the dimensions, preferably a pressure-relieved cone and a special fi spring arrangement. The pressure relief is provided by a channel 86m arranged in the center of the spindle 86b which connects the discharge channel 87 to a pressure chamber 85b arranged in the upper end of the spindle 86b, the spindle 86b being arranged at this other end with a piston 860 which abuts the inner surface of the pressure chamber 86. This piston 860 has substantially the same cross-sectional area as the active surface of the cone 86c. The valve is thus balanced and substantially insensitive to the static pressure in the fate channel 87. The pressure relief channel 86m can be provided in the jaw end with a choke, Lex. in the form of a nozzle. Such a throttle traps the fluid flow in and out of the pressure chamber. If necessary, such a nozzle can be supplemented with a filter which prevents the following particles from penetrating into the pressure chamber with the scar heat return water. The oil hydraulic circuit is always completely depressurized at atmospheric pressure / at atmospheric pressure. The regulator consists of at least one domestic hot water fl fate-indicating fl fate-giving piston 82, with a measuring piston 82a arranged in a running pipe 80 for cold water to the water heater, connected via a small spindle 82b to a folded piston 82c, which is movable in a hydraulic cylinder 81, converted to a sufficiently large pressure to overcome a der spring fi in at least one slave cylinder 85 with piston 86a which in turn acts on a valve cone 86c in the district heating line 87 from the water heater to open or close or stand still in direct proportion to the need for fi scarred water fl deserted to meet the correct temperature of the domestic hot water. The valve preferably has a pressure-relieved cone 86c, and in particular a spring arrangement, with an inner spring 86d acting between the movable piston 86a and a sleeve 86e and an outer spring 86f acting between the same sleeve 86e and an abutment arranged on and in the jacket of the slave cylinder 85. 85a. The valve end cap 85a is a knob for adjusting the fi spring crane in this arrangement by affecting the position of this abutment 85c.

In plants where the temperature and / or the dilferencing pressure of the scarred water over time shows moderate variations upwards, but where e.g. If the above values are not more than briefly or marginally exceeded, but the above criteria are otherwise valid, the fl fate sensor and control valve according to fi gur 7 are supplemented with a compensation unit of the type shown in fi gur 8a. The compensation unit according to Figure 8a will then prevent too high a hot water temperature from occurring due to the short-term high fi scarring water temperatures and differential pressures. The compensation unit shown in Figure 8a comprises a compensation cylinder 88a, a self-acting sensor body 89a for the temperature in the heat exchanger outlet of the hot water, connected to a spring-loaded hydraulic piston 89b in the compensation cylinder 88a. The compensation cylinder 88a is in turn hydraulically connected to the valve slave cylinder 85 shown in Figure 7 or Figure 9, by means of the hydraulic line 88b. With this compensation unit, overtemperatures can be substantially avoided by withdrawing the required amount of oil from the slave cylinder 85 by means of the compensation unit cylinder 0000 so that the district heating valve reduces its degree of opening and its firothermal water flow, all in order to avoid the risk of overheating. . The compensation cylinder 88a in Fig. 8a, which is arranged to sense the temperature of domestic hot water leaving the heat exchanger, is connected to the slave cylinder 85 via a slender hydraulic line 88b and the spring-loaded hydraulic piston 86a of the slave cylinder, including a tube which includes a tube in the compensating cylinder 88a is affected by a thermal sensing body 89a fixed in the other end of the spindle 89c. This sensing body 89a is arranged in a channel or arm space for the fl uid whose temperature is to be sensed. For example, the pulpit body 89a may be arranged in the space for the outlet of the hot water from the heat transfer channel elements of the water heater. The temperature range, stroke and required fi spring force ens of the sensor body 89a can be selected in relation to the desired temperature compensation capacity and working range of the compensation cylinder 88a. At the same time, these become dimensioning factors for the choice of cylinder diarns and spring. The hydraulic piston 89b of the compensation unit has on its upper side been designed as a seat and guide for a piston spring 89e and on its underside has been designed with a shoulder 89d as a downward movement stop. In the variant shown in Figure 8a, the breast is provided with double o-ring fittings with intermediate pressure relief and a drainage channel which also acts as a leakage indication channel. The holder for the tactile body is in the variant shown in Fig. 5a made in the form of a tube lying on the outside of the spindle, facing the tactile body 89a and the breast. The pipe is threaded into the parapet via a threaded connection during manufacture. The sensor body is attached to the pipe via track fl or track ring. Of course, attachment of the compensation cylinder and sensing body can be arranged in a number of alternative ways without changing the function of the compensation unit and special advantages in a heat transfer device according to the present invention. According to the variant shown in Figure 8a, the compensation cylinder 88a has at its top a threaded lid with a key holder for an Allen key. The lid simultaneously forms the upper seat and guide for a piston spring 89e arranged between the upper surface of the piston 89b and the compensation cylinder rice 88a lid. According to the variant shown in Figure 8a, the compensation cylinder 88a is fixed in a groove ring on the cylinder shell via an overflow nut with an 8-edge wrench to a threaded bobbin soldered in the duct block over the hot water outlet from the heat exchanger. The valve is sealed to the inner jacket of the bounce via an o-ring seal. 0 0000 00 0 0000 0 0 0 000 0 00 00 00 0 0000 0000 0 0 0 0 0 0 0 00 0 0 000 0 0 0 0 g 0 0 0 0 0 0 0 0 0 0 00 00 0 000 00 0 10 15 20 In a heat transfer device with a scar tissue and / or a distribution line, which contains a larger amount of water and which is not kept warm by through-circulation, it is desirable to supplement the control valve with a compensation unit for keeping the lines warm to prevent the water from cooling periodically. Such indirect water holding is obtained with a control valve according to fi gur 7 associated with a compensation unit according to fi gur 8b or 8c. The heat retention compensation unit shown in Figure 8b comprises a temperature sensor body of the same type and construction as that shown in Figure 8a, for which reason only the upper part of the compensation unit, the compensation cylinder, and components associated with it are shown in Figure 8b. The compensation unit in Figure 8b shows a compensation cylinder 88'a and a compensation piston 89'b arranged in the compensation cylinder. The compensating piston 89'b is provided with an internal "keeping piston" 89'd and lugs for downward movement of stops. sleeve 89'g, which, when the temperature of the sensing body has dropped to a level predetermined in the manufacture of the compensation unit, eg 40 ° C, causes the holding piston 89'd to press oil from the compensation cylinder 88'a to the slave cylinder 85 shown in Figure 7. which then opens the valve for the passage of cooled tar heat water which, when its temperature rises, can transfer heat via the heat exchanger to the hot water and thus the sensing body. the process can be closed, and the process is gradually developed into a conventional control process for keeping the temperature constant. the temperature around the sensing body, all in order not to create unnecessarily long waiting times for hot tap water when the tap starts. The spring-loaded sleeve 89'g is loaded with a spring 89'f which, like the piston spring 89e for the movable piston 89'b of the compensating cylinder 88, is arranged between the respective piston 89'b and the sleeve 89'g and so on. arranged in the cover of the compensation cylinder 88a.

A compensation unit similar in principle as in Figure 8a, but with a simpler and probably cheaper, heat maintenance function than that in Figure 8b is obtained with the compensation unit according to Figure 8c for applications where the heating temperature can be accepted, or desired, at the same temperature level as the hot water should normally maintain. ex. 50 ° C. The heat retention compensation unit shown in Figure 8b includes a temperature sensing body of the same type and construction as that shown in Figure 8a for which only the upper part of the compensation unit, the compensation cylinder, and associated components are shown in Figure 8c. The compensating piston 89 "c included in the compensation unit according to Figure 8c does not show a downward movement of movement, which in itself can directly actuate the valve slave cylinder 85 shown in Figure 7 to keep the piston 86a and cone 86c in accordance with the description in Figs. With a design as in fi gur 8c it follows that the compensation piston can also to some extent compensate for the temperature of the hot water at lower temperatures on incoming district heating water than that for which the valve is dimensioned, eg lower than the above-mentioned 65 ° C .

The same, of course, also applies to lower differential pressures or both of these deviations at the same time.

If the motives for keeping warm are present but where an indirect keeping function for the tar heating service cannot be accepted and where a compensation function for lower tar protected temperatures is desired and also a compensation function for higher and large variations in the temperature of incoming hot water is desired, the valve and the slave cylinder 85 'are made with built-in fi scarring temperature compensation and warning fi inlction via a self-acting thermal sensor body 91 mounted in the district heating supply which through a hydraulic transfer device transfers its position to a slave 92 mounted in the top of the slave cylinder 85'. device for adjusting the height fi of the scarred heat valve at all existing drains fl fates in relation to what is required for the correct hot water temperature based on the current temperature of incoming heating water which during draining may vary highly significantly, e.g. from 60 ° C to 120 ° C without changing the hot water temperature and which when kept warm e.g. at 40 ° C. The temperature-compensated slave cylinder 85 'is, according to the variant shown in Figure 9, a valve with an integrated compensation unit, which is partly arranged for compensation outside a varying temperature of incoming hot water and offers a warning function, connected to the master cylinder 8 via a sluice cylinder. and the spring-loaded hydraulic piston 93a of the slave cylinder fi is attached to the valve stem 93b via a link arm system 94 which includes at least 2 opposing link arm pairs. The outer guide points of the link jug systems 94 run in guide rails 94a. The inclination of the longitudinal axis of the guide rails 94a in relation to the longitudinal axis of the spindle 93b is variable and can be influenced by e.g. a device which in turn e.g. can be affected by a temperature thermal body for temperature, e.g. fi scarring water inlet temperature.

The geometry of the link arm system 94 and the guide rails 94a and the device for tilting the guide rails can be selected so that the desired characteristic of the movement of the spindle in relation to the hydraulic piston 93a is obtained in such a way that the movement can be weakened and varied along the movement. The suspension of the guide rails 94a and the device for tilting the guide rails are furthermore designed so that the device for tilting the guide rails can cause the guide rails 94a to, without signal to the slave hydraulic piston 93a from the sensor piston 82, hide the spindle 93b and its cone 93c for passing hot water. Upon tapping, the movement generated by the sensor piston 82 described with reference to Figs. 6a-6c and the oil thereby expelled from the master cylinder via transport through the soft hydraulic line 8a connected between the cylinders 81, 85 'are caused to be carried by the hydraulic piston 93a of the slave cylinder, e.g. in a ratio of 1:10 to the transducer of the transducer 82. The movement of the slave piston 93a is transmitted via the link arm system 94 to the spindle 93b depending on the inclination of the guide rails 94a, e.g. depending on the inlet temperature of the district heating water, so that the correct degree of opening is obtained between the valve cone 93c and the seat 95a for the passage of district heating water so that the desired domestic hot water temperature is obtained from the water heater. When the tapping decreases or ceases, an deredder fi slave piston 93a causes the valve cone 93c to close via the link arm system 94 and to return oil to the master cylinder 81 which in turn causes its sensor piston 82 including the measuring piston 82a to reduce its deflection or return to the initial position. A certain minimum amount of oil of atmospheric pressure remains in the slave cylinder 85 'when the valve cone 93 c is completely closed.

The valve has a pressure-relieved cone 93c, and in particular a spring arrangement, similar to that already described for the general case. The cover 96a with the pressure chamber 96b is formed in its upper part as a guide for the device for the inclination of the guide rails 94a and its springs 94b, 94c.

The cover 96a with the pressure chamber 96b is in its lower part slotted with at least 2 opposite grooves, not shown, which accommodate the arrangement for link arm system 94, guide rails 94a and the device for the inclination of the guide rails and are connected via threads to a spacer 94d which in turn via threaded band is threaded over the slave cylinder 85 'and where both parts are locked with locking screws. The articulation point of the link arm systems 94 in the guide rail 94a is provided with stored rollers which run in the guide rail path with a good fit. The guide rails 94a are suspended in their lower part, via a groove sloping towards the longitudinal axis of the guide rail, in a pin in the slotted lower part of the lid 96a.

The guide rails 94a are in their upper part, which run in the device for the inclination of the guide rails, designed as galls which are provided with a coarser roller pair stored and a weaker roller mounted on the same shaft. The weaker roller runs towards a center part 94e formed as a cylinder with wings at least 2 to opposite paths, upper spring-loaded path 94f which has been given a slope which constantly strives to bring the hinge end outwards. The coarser rollers run towards a lower part 94h, which is designed as a cylinder with at least 2 wings unfolded to opposite paths, a lower path 94h which can be moved in height, e.g. controlled by a temperature, and which strives to bring the hinge end inward. If the web is controlled by a temperature, e.g. at rising temperature the web is moved downwards and conversely at falling temperature the web is moved upwards. The cylindrical center part 94g is connected at its upper end via threaded connections to a capillary-loaded transition piece 96d, supported in the cover 96a, which receives and transmits e.g. the movement controlled by a temperature. The lower web can also, e.g. controlled by a temperature, after at falling temperature it has brought the rollers and guide rail spirit to its innermost position, in case of continued temperature drop, lifts the guide rail, which then in its lower attachment runs in its groove towards the attachment pin and forces the link arms 94 into the guide rail 94a outer joint , whereby the spindle 93b, after the slave piston 93a has been brought down and forced out so much oil to the sensor cylinder 81 that the sensor piston 82 has reached its upper stop, the light and the valve cone 93c are opened. The upper jacket part of the slave cylinder 85 'is slotted with at least 2 opposite grooves for the adjustable spring retainer arrangement 94i which is required to compensate for tolerances for the springs and for e.g. to some extent change and be able to set the desired hot water temperature. The end cap 97 of the valve is designed as an external support for the device for the inclination of the guide rails and in its top is provided with a slotted attachment and adjusting nut for the slave cylinder 92b of the thermal sensing body. The end cap 97 is connected via threaded connections to the lower part of the lid 96a and locked with locking screws therein. A rotary ring for adjusting the spring collar fi and thus also the hot water temperature is applied to the sheath of the slave cylinder 85 'and at the same time constitutes an abutment for the fi spring holder arrangement 94i. The piston 93a forms the seat of the inner lid 93d and has an elongated neck for assembly.

The piston neck is connected to the spindle 93b via at least 2 opposite link arm systems 94 which are fixed in grooves on the piston neck and spindle 93b. The spindle bushing of the breast is provided with double o-ring seals with intermediate pressure relief and drainage channel which also constitutes a leakage indication channel. The valve seat 95a is connected to the bushing via threaded joints and immersed in the outlet pipe 95 of the duct block for the scar water from the water heater and sealed against the pipe with an o-ring seal. The valve is attached to a groove ring on the cylinder 10 15 20 25 5: 5 917. .- 52 the jacket via a union nut with an S-edge wrench to a threaded bobbin soldered to the duct block over the fi scar heat outlet from the heat exchanger. The valve is sealed against the inner jacket of the bounce via an O-rig seal. The sensing body 91 for temperature can e.g. be a temperature sensor for the flow temperature of the scarred water and then placed in a sensor also in the screw connection for the scarred heat filter. The sensor fi ckan is made in its outermost part as a key fob for an Allen key and in its continued part with a dimension and a tolerance that provides a good fit and thereby a good abutment against the mantle of the sensor body. The need for fitting does not need to be exaggerated as the temperature variation over time will be very slow. The compensation cylinder with the temperature sensor 91 in Figure 9 is arranged to compensate for incoming fi scar water fl based on the temperature of incoming fi scar water and is connected to the slave cylinder via a narrow hydraulic line 90a.

The basic difference between the design of the regulator in the variants of the components illustrated by means of the sub-components shown fi gures 6a-6c, 7, 8a, 8b, 8c and 9 and a traditional device for regulating domestic hot water production in a heat exchanger is that the traditional regulation is based on the fact that there is always created either a secondary situation or a surplus in the pararnet to be regulated and which the regulator then strives to compensate for your best ability. This procedure is normally repeated for each disturbance to which the equipment is exposed, Lex. a fatal change in the domestic hot water outlet. In other words, since solution with a control valve according to the embodiments of the invention described above always gives a proportionally correct ör fate ratio between the supply of the heating and cooling water in the heat exchange process, it can be assumed that central heating according to the present invention with domestic hot water production controlled by a regulator components according to Figures 6a-6c, 7, Sa, 8b, 8c and 9 provide a significantly improved comfort and that the torment of the exercise showers can become a thing of the past.

Claims (21)

10 15 20 25 30 525 91% PATENT REQUIREMENTS Heat transfer device for use in heating at least one fl uid and / or producing hot water in buildings, for transferring heat between a primary fl uid obtained from an external source and at least one secondary fl uid, the secondary fl uid being tempered before being supplied a consumer, the device comprising a heat exchanger (3, 13, 23) and a coupling block (2, 12, 22) with internal channels connected to the heat exchanger, where n the heat exchanger has inlets and outlets for the primary id uidens and the secondary “_ fl uidens to fl fates and out fl fates and where the connection block has a number of main connections for connecting the external primary source and the consumer, for the primary source and the secondary distance to the fates and out fates to and from the device, respectively, and a number of outlets and outlets for outlets, inflows and outflows to and from the heat exchanger, respectively, the internal channels connect the main and sub-connections, characterized in that the heat exchanger is a plate heat exchanger, that the coupling block is connected to the plate heat exchanger, that the coupling block comprises des fate-distributing means for distributing at least one incoming fl fate and / or ut interconnecting d interconnecting means is composed of at least two ends (42a, 42b), required partitions, and - one or more intermediate channel plates (42a-42e), the intermediate channel plates having recesses and / or partitions (422a-422e), which in the composite coupling block form a duct system with internal ducts for the distribution and / or distribution of the pipes inside the device and inlets and outlets in and out of the device, and that the recesses and / or partitions create the necessary cavities (422e) for control and monitoring equipment integrated in the coupling block, etc. the thematic processes ongoing in the device, and that plates included in the coupling block are joined together by soldering. Device according to claim 1, characterized in that the coupling block is integrated as part of the plate heat exchanger. Device according to Claim 2, characterized in that the coupling block abuts directly against and is connected to one end of the heat exchanger. 10 lS 20 25 30 Device according to one of the preceding claims, characterized in that the connection of the coupling block to the heat exchanger takes place by means of soldering and that the soldering of the coupling block and the heat exchanger takes place in the same soldering torque. Device according to one of the preceding claims, characterized in that at least one channel plate is composed of a number of thinner disc-shaped elements with recesses and / or partitions, where the disc-shaped elements, in the composite coupling block, are stacked on each other in such a way that the channels dimensions and configuration are determined partly by the configuration of the recesses and partly by the thickness, number and stacking sequence of the disc-shaped elements, which disc-shaped elements are joined together by soldering. Device according to claim 5, characterized in that the end plates comprise connection connections (423 a-423d) which connect the external systems and the internal circuits to the channel system of the coupling block. Device according to any one of the preceding claims, characterized in that the coupling block comprises a number of main connections associated with the external primary fluid source and at least one consumer, for the primary and at least one secondary iluids to and from the device, to and from the device. ut fl the connections of the fates are coordinated to a connection block (41) and that the main connections are adapted and coordinated on the connection block so that it can be quickly and easily connected to or disconnected from the connection block. Device according to claim 7, characterized in that the connection block comprises a draining device for at least the primary outlet, space for a number of temperature sensors, lockable fasteners and connection valves arranged to close and open the main connections, wherein at least two connection valves are coordinated into a control group for a simultaneous opening. respectively closing of the coordinated valves. o .. .- 10 15 20 25 (31 i ”3 01 \ -í> .__ \ \ '1 ss -: g' _, _ Device according to claim 8, characterized in that the connection valves of all the main connections are coordinated into two operating groups for simultaneous opening and closing of the coordinated valves, respectively. Device according to claim 1, characterized in that the coupling block comprises fl fate-distributing means for distributing an incoming fl fate and / or flow-joining means for merging at least two outgoing flows and means for controlling and monitoring the thermal process. Device according to claim 7, characterized in that the controlling and monitoring means comprise at least one control valve for manipulating a fl uids fl fate through, to and / or out of the coupling block. Device according to claim 1 arranged for two thermal processes, characterized in that the coupling block comprises - a number of main connections associated with the external primary source and two consumers, for the primary and two secondary numbers to the fates and out of the device, respectively. sub-connections associated with the heat exchanger and a second heat transfer circuit inlet and outlet, for fl uidemas to fl fates and out fl fates to and from the two heat transfer circuits, respectively, and internal ducts, where the ducts are arranged with des fate-distributing means to distribute and control the the inlet of the circuits for the primary fl uid and / or merge and control the outputs of the primary från uid from the outlets of the two parallel heat transfer circuits for the primary fl uid, the number of main connections being less than the number of sub-connections. 13. Device according to claim 12, characterized in that the heat exchanger and the second heat transfer circuit are connected in parallel. 10 15 20 25 30 5:25 917 Device according to claim 12 or 13, characterized in that the second heat transfer circuit comprises a shunt circuit with a shunt line for supplying the return of the primary current from the consumer to the primary current upstream of the consumer. Device according to claim 12 or 13, characterized in that the second heat transfer circuit comprises a heat exchanger. Device according to claim 12, characterized in that the first heat transfer circuit comprises a first plate heat exchanger, that the second heat transfer circuit comprises a second plate heat exchanger, that the first and the second plate heat exchanger are both arranged with all inlets and outlets on the same end so that the plate heat exchangers each have a connection end and a rear end, and that the first plate heat exchanger is arranged to abut against the second plate heat exchanger in such a way that the first plate heat exchanger abuts with its rear end against the connection end of the second plate heat exchanger. 17. Device according to claim 16, characterized in that the inlet of the first and second heat exchangers for the primary fluide is arranged as a common channel and that the first plate heat exchanger comprises a continuous channel arranged inside the other inlets and outlets, that the inlet and the second plate heat exchanger outlets are coordinated with the inlet and outlet of the first plate heat exchanger and that the inlet and outlet of the second plate heat exchanger are connected to continuous passages arranged in the inlet and outlet of the first plate heat exchanger. Device according to one of the preceding claims, characterized in that the external primary fl uid source is a district heating network with a primary fl uid in the form of hot water. Device according to one of Claims 12 to 18, characterized in that a first plate heat exchanger is arranged for the production of domestic hot water, in that a second heat transfer circuit is arranged for the production of hot water into a circulation circuit for 2, 2, 2, 2, 2, 2, 2, 2 '. In and. , 56 ooonpo o. G. ' 0 Ioo g,. oooono o ',: z .o o g,. lo o o o 10 5: 5 917 57 water-borne heating and that the connecting block is arranged in the form of a block with internal channels where the main connections are coordinated on one of the storytors of the block. Device according to claim 19, characterized in that two plate heat exchangers and a flat coupling block are integrally arranged in a compact, fast and easily detachable and replaceable module unit. 21. Device according to any one of the preceding claims, characterized in that the device is arranged in a space arranged on the outside of a property for facilitating access to the device.