JP3733371B2 - Temperature control system - Google Patents

Description

  The present invention relates to a liquid piping facility and temperature control system used for heat utilization, and more particularly to a liquid piping facility and temperature control system used for heat utilization using a liquid as a heat medium.

  It is publicly known that hot / cold heat is conveyed to a predetermined heat load using a fluid such as water as a heat medium. For example, in the field of air conditioning, a method of independently air-conditioning each area (hereinafter referred to as “zone”) obtained by dividing a building into several areas is called a zone control system. One of the piping systems used to air-condition each zone is the reverse return water method (reverse return method).

  As shown in FIG. 5, the liquid piping equipment used for heat utilization by this reverse return water method includes, for each zone 73, a control valve 61, a fan coil unit (heat exchanger) 7 that is a heat utilization device, and a branch pipe 9. A temperature control system 63 is provided.

  These temperature control systems 63 are connected in parallel to a heat source device 13 provided with a refrigerator or the like via a main pipe 15, and the main pipe 15 is connected to the downstream pipe 65 connected to the downstream side of the heat source device 13 and the heat source device. 13 of return pipes 67 connected to the upstream side.

  A pump 69 for sending out the heat medium adjusted by the heat source device 13 is connected to the upstream end of the outgoing pipe 65, and an upstream end of the branch pipe 9 is connected to the downstream side of the outgoing pipe 65. Yes.

  An upstream end of the branch pipe 9 is connected to the upstream side of the return pipe 67, and the upstream side of the return pipe 67 to which the downstream end of the branch pipe 9 is connected is once in the same direction as the forward pipe 65. At the final end Q that is returned, the heat medium exchanged with the room air by the fan coil unit 7 is collectively returned to the heat source device 13. Further, in the return water method, the pressure loss of the temperature control system 63 including the piping system is made equal, and the flow rate of the heat medium flowing into each temperature control system 63 is made the same. The control valve 61 is provided for temperature control of each zone 73.

  A return pipe for returning the heat medium flowing out from the temperature control system 63 in the same direction as the forward pipe 65 is hereinafter referred to as a “saddle pipe 71”. According to this reverse water return method, the length of the flow path from the pump 69 to the downstream end Q of the soot pipe 71 can be made equal even when passing through any zone 73, so that heat is exchanged by the heat source device 13. Thus, there is an advantage that a flow rate adjusting means such as a constant flow valve can be omitted in each fan coil unit 7.

  However, in the reverse water return method, since the heat medium that has flowed out of the temperature control system 63 has the soot pipe 71 for returning in the same direction as the forward pipe 65, the heat medium that has flowed out of each temperature control system 63 is removed. Compared with the so-called direct return water method in which the pipe 65 is returned in the opposite direction, the length of the pipe is increased. For this reason, there has been a problem that a large amount of piping material is consumed and the construction cost is increased.

  Further, the control valve 61 provided in the temperature control system 63 is selected so that the pressure loss of the control valve 61 occupies several tens of percent of the entire temperature control system 63 in order to improve the flow rate controllability. For this reason, the pump 69 has a problem that it requires a large required power and causes an increase in power consumption.

  Furthermore, in the conventional liquid piping equipment used for heat utilization by the reverse water return method, the piping system having the largest pressure loss (piping system including the temperature control system 63) among the piping systems reaching the plurality of temperature control systems 63, that is, Based on the pressure loss value of the piping system farthest from the pump 69, the pressure loss value of the piping system reaching the other temperature control system 63 is adjusted to be substantially the same. Therefore, there is a problem that extra energy is required and power consumption is further increased.

  The object of the present invention has been made in view of the problems of the prior art described above, and is intended to conserve resources of piping materials, reduce the construction cost, and reduce the required power of the pump 69. This is to reduce power consumption.

  The present invention employs the following means in order to solve the above problems. The present invention has two or more temperature control systems including two or more heat exchangers connected in parallel to each other, and these temperature control systems are connected in parallel to the heat source device via the main pipe. In a liquid piping facility that sends a heat medium having a desired temperature to each temperature control system via the main pipe, performs heat exchange in the temperature control system, and returns to the heat source device, the temperature control system An exchanger, a pump capable of controlling the capacity to supply the heat medium to the heat exchanger, and a back flow prevention connected to the upstream side or the downstream side of the pump to prevent the back flow of the heat medium and to keep the flow direction constant. And a branch pipe connecting the heat exchanger, the pump, and the backflow prevention means.

  The heat medium exchanged by the heat source device is pumped by a pump for each zone, passes through the main pipe, and is supplied to each heat exchanger via the backflow prevention means. The operation capacity of the pump provided in each temperature control system is adjusted according to the temperature (for example, room temperature) of each temperature control system and the set temperature.

  The heat medium exchanges heat with the air in the temperature control system by the heat exchanger, and the heat load corresponding to each temperature control system becomes a desired temperature. The heat exchange medium subjected to the heat exchange is returned to the heat source device through the branch pipe and the main pipe. Thereafter, the same operation as described above is repeated.

  The heat source device may be configured in any system as long as it has a function of supplying heat to the heat medium and removing heat from the heat medium. Examples of the heat source device include a heat source device such as a boiler, a cold heat source device including a refrigerator, and a heat pump.

  The heat source device may include a heat storage device. Examples of the heat storage device include a water heat storage tank and an ice heat storage tank. The structure of the pump is not limited as long as it has a capability of maintaining a high water supply pressure even when the flow rate of water is increased. Examples of the pump include a line pump and a centrifugal pump.

  The structure of the backflow prevention means is not limited as long as it has a function of preventing the backflow of the heat medium and keeping the flow direction constant. As the backflow prevention means, for example, a swing type and a lift type can be exemplified by the structure of the valve seat.

  The structure of the heat exchanger is not limited as long as it has a function of supplying heat to the heat medium and taking heat from the heat medium. As a heat exchanger, a fan coil unit can be illustrated, for example.

The heat medium is preferably water. This is because water has a large specific heat and is easy to handle. The main pipe is connected to a bypass pipe that bypasses all temperature control systems and connects the upstream side and the downstream side of the main pipe, and this bypass pipe is connected to a heat medium sent from the heat source device. Controllable circulation pump that bypasses the part and returns it to the upstream side of the heat source device, and backflow prevention means connected to the upstream side or downstream side of this circulation pump to prevent the backflow of the heat medium and keep the flow direction constant , And are preferably provided.

  When the temperature difference between the temperature of the heat load corresponding to the current temperature control system and the set temperature of the load is small, or there is a demand for heat consumption of the heat load in some of the temperature control systems. If not, the circulation pump is started and a part of the heat medium sent out from the heat source device is returned to the main pipe via the bypass pipe and the backflow prevention means. In this way, it is not necessary to reduce the flow rate of the heat medium flowing into the heat source device, and as a result, the heat exchange efficiency of the heat source device can be maintained in a high state. Among heat source devices, for example, some refrigerators are equipped with a security circuit that stops equipment when the flow rate of the introduced heat medium is below a certain level, preventing frequent stoppage of these equipment. it can.

  In addition, instead of providing a circulation pump and a backflow prevention means in the bypass pipe described above, the bypass pipe connecting the upstream side and the downstream side of the main pipe by bypassing all temperature control systems to the main pipe connected to the heat source device Is connected between the upstream end of the bypass pipe line and the heat source apparatus, and a heat pump capable of controlling the ability to send out the heat medium from the heat source apparatus is provided, and the heat medium flowing in the bypass pipe line is provided in the bypass pipe line. It is also possible to provide a flow rate adjusting valve for adjusting the flow rate. In this case, the same effect as described above is obtained.

  As described above, according to the liquid piping facility for heat utilization of the present invention, there are a plurality of temperature control systems including two or more heat exchangers connected in parallel to each other, and these temperature control systems are heat sources. The heat source connected to the apparatus in parallel via the main pipe and sent to each temperature control system via the main pipe by the heat source device having a desired temperature by the heat source apparatus, and after heat exchange in this temperature control system, the heat source apparatus In the liquid piping equipment to be returned to, the temperature control system includes a heat exchanger, a pump capable of controlling the capacity of supplying the heat medium to the heat exchanger, and a back flow of the heat medium connected to the upstream side or the downstream side of the pump. And a branch pipe connecting the heat exchanger, the pump and the check valve to prevent the heat medium flowing out of the temperature control system from flowing upstream. There is no need for piping to return in the same direction as piping. It is possible to shorten the length. For this reason, it is possible to save resources of the piping material and reduce the construction cost.

  Moreover, since the pressure loss of the whole temperature control system can be reduced, the required power of the pump can be reduced. For this reason, power consumption can be reduced.

  Furthermore, the pump can be operated independently for each temperature control system, and the operation capability of the pump can be controlled, so that the power consumption can be further reduced.

  The main pipe is connected to a bypass pipe that bypasses all temperature control systems and connects the upstream side and the downstream side of the main pipe, and the bypass pipe is connected to the heat medium flowing out from the heat source device. A circulation pump capable of bypassing a part of it and returning it to the upstream side of the heat source device, and a reverse pump connected to the upstream side or downstream side of this circulation pump to prevent the back flow of the heat medium and keep the flow direction constant If a stop valve is provided, the flow rate of the heat medium flowing into the heat source device even when the temperature control level of the temperature control system is small or the number of temperature control systems that require temperature control decreases. It is possible to maintain the heat exchange efficiency of the heat source device in a high state without drastically reducing (or the flow velocity) and to supply the heat medium that has flowed into a desired temperature to each temperature control system. Therefore, the equipment efficiency (for example, the refrigerator performance coefficient) of the heat source device can be improved and the power consumption can be reduced.

Also, when a flow rate adjusting valve is provided in the bypass line and a delivery pump capable of controlling the ability to send out the heat medium from the heat source unit is provided between the upstream end of the bypass line and the heat source unit, the heat source The apparatus efficiency (for example, the performance coefficient of the refrigerator) of the apparatus can be improved and the power consumption can be reduced, and the pump provided in the temperature control system can be downsized.

  In addition, when the heat source device includes a heat storage device, it is possible to reduce the other equipment capacity in the heat source device, and to diversify the heat utilization mode. Therefore, power consumption can be reduced.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a liquid piping facility used for heat utilization according to the present invention will be described with reference to the drawings of FIGS.

  [First Embodiment] First, liquid piping equipment used for heat utilization according to the first embodiment will be described with reference to FIG. Liquid piping equipment used for heat utilization according to the present invention will be described with reference to an example of an air conditioning system using a zone control system. This air conditioning system divides a building or the like into several areas, and air-conditions the zones that are the divided areas independently.

  For example, if a building faces east, west, south, and north, and there are windows on each side, if the area around the window inside the building is divided into the east zone, west zone, south zone, and north zone, Since the temperature of each zone changes, it is necessary to perform air conditioning by dividing into zones with windows. Further, since the conference room needs air conditioning only when used by a person, it is necessary to make this conference room an independent zone.

  The liquid piping facility 1 used for heat utilization is divided into three zones. As shown in FIG. 1, a check valve (backflow prevention means) 3 and pumps 5 and 3 are provided for each zone for temperature adjustment. Temperature control systems 11 a, 11 b, and 11 c including a fan coil unit (heat exchanger) 7 and a branch pipe 9, and these temperature control systems 11 a, 11 b, and 11 c are connected to the heat source device 13 and the main pipe 15. Are connected in parallel, and a water (heat medium) circulation path is formed around the heat source device 13. Hereinafter, the heat loads (air conditioning zones) 12 corresponding to the three temperature control systems 11a, 11b, and 11c are designated as the first air conditioning zone 12a, the second air conditioning zone 12b, and the third air conditioning zone 12c from the upper air conditioning zone 12 in FIG. explain.

  The outlet water temperature from the heat source device 13 is controlled to a constant temperature, and the heat source device 13 is composed of a cold heat source device including a refrigerator and a cooling tower, a steam boiler and a steam / water heat exchanger, and the like. A heat source device can be exemplified.

  The temperature control system 11 has a check valve 3 on the upstream side thereof, and a pump 5 capable of capacity control is connected to the downstream side of the check valve 3 via a branch pipe 9. Three fan coil units 7 are connected in parallel via branch pipes 9. The check valve 3 can also be provided downstream of the pump 5 and upstream of the fan coil unit 7. The check valve 3 and the pump 5 may be provided on the downstream side of the fan coil unit 7. In this case, the check valve 3 may be provided on the upstream side or the downstream side of the pump 5.

  The temperature control system 11 is provided with a temperature sensor 16 for detecting the temperature of the air conditioning zone 12 corresponding to the temperature control system 11. The pump 5 changes the flow rate (or flow velocity) of the water flowing through the branch pipe 9 by changing the rotation speed of the impeller of the pump 5 based on the detection signal of the temperature sensor 16, and is supplied to the fan coil unit 7. The flow rate of the water to be adjusted can be adjusted to set the air conditioning zone 12 to a set temperature. As the pump 5, for example, a line pump or a centrifugal pump can be used.

  Next, an example of controlling the air-conditioning zone 12 corresponding to each temperature control system 11 to the set temperature, when controlling the temperature of all three air-conditioning zones 12a, 12b, 12c, and one or two air-conditioning zones 12 This will be described separately for temperature control.

  (1) When temperature control is performed on all three air-conditioning zones 12a, 12b, and 12c First, the heat source device 13 is operated, and the temperatures corresponding to the first air-conditioning zone 12a, the second air-conditioning zone 12b, and the third air-conditioning zone 12c. The pumps 5 and the fan coil units 7 of the control systems 11a, 11b, and 11c are operated. The heat source device 13 controls the operation capacity according to the degree of temperature control of each air-conditioning zone 12a, 12b, 12c, and brings water to a predetermined constant temperature.

  Next, the water adjusted to a constant temperature by the heat source device 13 is pumped by the pumps 5 of the temperature control systems 11 a, 11 b, 11 c and flows into the branch pipes 9 through the main pipes 15.

  The water flowing into the branch pipe 9 is supplied to the three fan coil units 7 via the check valve 3. Since the three fan coil units 7 are connected in parallel, the pressure loss of each fan coil unit 7 and branch pipe 9 is the same, and the pipe length of the branch pipe 9 is also the same. Since they are connected, the flow rate of water supplied to each fan coil unit 7 is the same. Therefore, all three air-conditioning zones 12a, 12b, and 12c can be set to a uniform set temperature.

  Next, the heat-exchanged water flows out of the fan coil unit 7, flows through the branch pipe 9, flows into the main pipe 15, and returns to the heat source device 13 through the main pipe 15. Then, for each air conditioning zone 12a, 12b, 12c, the detection signal of the temperature sensor (room temperature sensor) 16 is compared with the set temperature of each air conditioning zone 12a, 12b, 12c, and the blades of the pump 5 based on these temperature differences. The number of rotations of the vehicle is controlled to adjust the flow rate of water flowing into the fan coil unit 7, and the air conditioning zones 12a, 12b, and 12c corresponding to the temperature control systems 11a, 11b, and 11c are set to the set temperatures. Then, the temperature of the water is adjusted again by the heat source device 13, and thereafter the same action as described above is repeated.

  (2) When controlling the temperature of one or two air-conditioning zones 12 When controlling the temperature of the first air-conditioning zone 12a and the second air-conditioning zone 12b, the heat source device 13 is operated and the first air-conditioning zone 12a and the second air-conditioning zone 12b are operated. The pump 5 and the fan coil unit 7 of the temperature control systems 11a and 11b corresponding to the air conditioning zone 12b are operated. And the pump 5 and the fan coil unit 7 of the temperature control system 11c corresponding to the 3rd air conditioning zone 12c do not drive | operate.

  The heat source device 13 controls the operation capacity according to the number of the air-conditioning zones 12 to be temperature-controlled to bring the water to a predetermined constant temperature. Since the flow of water flowing out from the heat source device 13 and heat exchange are in accordance with the above (1), the description thereof is omitted. However, the heat medium of the temperature control system 11c and the heat medium downstream from this system are not sucked into the other temperature control systems 11a and 11b by the action of the check valve 3.

  In addition, the combination of the air-conditioning zone 12 which controls temperature is not restricted to what was mentioned above, It is also possible to temperature-control only the 1st air-conditioning zone 12a. In the conventional liquid piping equipment used for heat utilization by the reverse water return method, a dredger pipe 71 for once returning water flowing out of the temperature control system 11 in the same direction as the upstream main pipe 15 connected to the heat source device 13 is provided. Although it is necessary, the liquid piping facility 1 used for heat utilization in the first embodiment does not require the soot pipe 71, so that the length of the pipe can be shortened and the resource of the piping material can be saved. Can be realized.

In addition, by using the pump 5 capable of capacity control instead of the control valve 61 that has been conventionally required for the temperature control system 11, the pressure loss of each temperature control system 11 as a whole is reduced and the required power of the pump 5 is reduced. Can be made. For this reason, power consumption can be reduced.

  Furthermore, since the pump 5 can be operated independently for each temperature control system 11 and the operation capacity of the pump 5 can be controlled, the power consumption can be further reduced.

  [Second Embodiment] The number of air-conditioning zones 12 corresponding to the temperature control system 11 for temperature control in the liquid piping facility 1 used for heat utilization in the first embodiment is reduced, or the temperature control system 11 When the difference between the current value and the set value of the room temperature sensor 16 installed in the air conditioning zone 12 corresponding to is small (hereinafter referred to as “low load”), the flow rate of water flowing into the heat source device 13 is small. As a result, the heat transfer performance of the heat transfer surface in the heat source device 13 also decreases.

  Therefore, in the liquid piping equipment used for heat utilization in the second embodiment, the heat transfer performance heat on the heat transfer surface in the heat source device 13 is high without reducing the flow rate of water flowing into the heat source device 13. In this way, water that has been maintained and adjusted to a constant temperature can be supplied to the temperature control system 11.

  Hereinafter, the liquid piping equipment used for heat utilization in the second embodiment will be described with reference to FIG. In the liquid piping facility 17 used for heat utilization in the second embodiment, the main piping 15 connected to the heat source device 13 bypasses all the temperature control systems 11a, 11b, and 11c, and the upstream side of the main piping 15 A bypass line 19 connecting the downstream side is connected.

  On the upstream side of the bypass pipe 19, a check valve 23 that prevents a back flow of water and keeps the flow direction constant, and a part of the water that is connected to the downstream side of the check valve 23 and is sent from the heat source device 13. And a circulation pump 21 capable of controlling the capability of supplying water as a heat medium to the upstream side of the heat source device 13. Since other configurations are the same as those of the liquid piping facility 1 used for heat utilization in the first embodiment, the same reference numerals are given to the same mode portions, and the description thereof is omitted.

  The circulation pump 21 can change the rotational speed of the impeller of the circulation pump 21 in accordance with the degree of heat exchange in the temperature control system 11 and the number of air conditioning zones 12 that require air conditioning. And a centrifugal pump.

  Next, of the three air conditioning zones 12a, 12b, and 12c, the first air conditioning zone 12a does not require heat consumption (no air conditioning), and the second air conditioning zone 12b and the third air conditioning zone 12c are temperature controlled. The operation of one embodiment will be described.

  First, the heat source device 13 is operated, and the pumps 5 and the fan coil units 7 of the temperature control systems 11b and 11c corresponding to the second air conditioning zone 12b and the third air conditioning zone 12c are operated. And the pump 5 and the fan coil unit 7 of the temperature control system 11a corresponding to the 1st air conditioning zone 12a do not drive | operate.

  The water temperature-controlled by the heat source device 13 is sent out from the heat source device 13 and branches through the main pipe 15 at a portion where the bypass pipe line 19 is connected. A part of the water flows into the bypass pipe line 19 and remains. The water flows through the main pipe 15 into the temperature control systems 11b and 11c corresponding to the second air conditioning zone 11b and the third air conditioning zone 11c. The flow of water flowing into the temperature control systems 11b, 11c, heat exchange, and the like are the same as those in the first embodiment described above, and thus the description thereof is omitted.

Since the pump 5 of the temperature control system 11a corresponding to the first air conditioning zone 11a is not operated and the check valve 3 is closed, water does not flow into the fan coil unit 7 provided in the temperature control system 11a.

  Therefore, in the downstream main pipe 15 connected to the heat source device 13, the flow rate of water flowing into the upstream side of the main pipe 15 is the temperature control system 11b corresponding to the second air conditioning zone 12b and the third air conditioning zone 12c, Compared with the case where the temperature control is required for the three air-conditioning zones 12, the flow rate of the water decreases to about 2/3.

  The water flowing into the main pipe 15 on the downstream side flows toward the heat source device 13 through the main pipe 15. On the other hand, the water sent from the heat source device 13 and circulated around the heat source device 13 by the circulation pump 21 flows through the bypass pipe 19 and joins the water flowing through the main pipe 15 via the check valve 23. Accordingly, the flow rate of water flowing into the heat source device 13 is maintained.

  By the way, when it comes to the operation capability of the heat source device 13, the operation capability is reduced in the case of two air-conditioning zones 12 requiring temperature control than in the case of three. However, as described above, the water that is the heat source is supplied to the heat source device 13 through the bypass pipe 19, so that the water supplied to the heat source device 13 is reduced even if the number of air-conditioning zones 12 that require temperature control is reduced. The flow rate is maintained. Therefore, since the heat transfer surface of the heat source device 13 can be operated while maintaining high heat transfer performance, the heat exchange efficiency can be maintained high. In addition, it is possible to prevent the operation of a refrigerator or the like from being stopped due to a low flow rate.

  The flow rate of the water flowing through the bypass line 19 is adjusted by changing the rotational speed of the impeller of the circulation pump 21 in accordance with, for example, the differential pressure between the inlet / outlet side and the inlet side of the heat source device 13.

  The combination of the air-conditioning zones 12 for temperature control is not limited to that described above, and the temperature control of the three air-conditioning zones 12 may be simultaneously performed and the degree of the temperature control may be reduced.

  According to the liquid piping equipment 17 used for heat utilization of the second embodiment, the heat exchange efficiency can be improved without extremely reducing the flow rate (or flow velocity) of the water flowing into the heat source device 13 even in the case of a low load. It can be maintained in a high state, and the inflowing water can be set to a desired temperature and supplied to each temperature control system 11. Accordingly, it is possible to improve the air conditioning efficiency of the liquid piping facility 17 used for heat utilization and to reduce power consumption.

  [Third Embodiment] An example in which a booster pump is provided in the liquid piping equipment used for heat utilization in the third embodiment is shown. In the liquid piping facility used for this heat utilization, water is allowed to flow into the bypass pipe 19 at a low load so as not to decrease the flow rate of the water flowing into the heat source device 13 so that the heat exchange efficiency is maintained at a high level. Thus, water adjusted to a constant temperature can be supplied to the temperature control system 11.

  Hereinafter, liquid piping equipment used for heat utilization in the third embodiment will be described with reference to FIG. In the liquid piping facility 25 used for heat utilization in the third embodiment, a booster pump (feeding pump) capable of controlling the ability to send water from the heat source device 13 between the upstream end of the bypass pipe line 19 and the heat source device 13. ) 29, and the bypass pipe 19 is provided with a flow rate adjusting valve 27 for adjusting the flow rate of water flowing through the bypass pipe 19. Since other configurations are the same as those of the liquid piping equipment 17 used for heat utilization in the second embodiment, the same reference numerals are given to the same mode portions and the description thereof is omitted.

  The booster pump 29 is always operated as long as the temperature control system 11 for temperature control is operating. As the booster pump 29, for example, a centrifugal pump can be used.

  The flow rate adjusting valve 27 changes the degree of temperature adjustment of the air-conditioning zone 12 corresponding to the temperature control system 11 and the number of air-conditioning zones 12 requiring temperature control, and the water flowing through the bypass line 19 by changing the opening of the valve. Adjust the flow rate. As the flow rate adjustment valve 27, for example, a two-way valve can be used.

  Next, the operation of one embodiment when the air conditioning of the first air conditioning zone 12a among the three air conditioning zones 12 is stopped and the temperature of the second air conditioning zone 12b and the third air conditioning zone 12c is controlled will be described.

  First, the heat source device 13 is operated, and the pumps 5 and the fan coil units 7 of the temperature control systems 11b and 11c corresponding to the delivery pump 29, the second air conditioning zone 12b, and the third air conditioning zone 12c are operated. The pump 5 and the fan coil unit 7 of the temperature control system 11a corresponding to the first air conditioning zone 12a are not operated.

  The water adjusted in temperature by the heat source device 13 is pumped from the heat source device 13 by the booster pump 29, and a part of the water flows into the bypass line 19 due to the frictional resistance of the main pipe 15 and is constant via the flow rate adjustment valve 27. The water flows through the main pipe 15 and flows. Therefore, the water flowing into the heat source device 13 reaches a predetermined temperature by the heat source device 13 without being extremely reduced.

  The heat source device 13 is operated with a reduced operating capacity compared to the case where all the air-conditioning zones 12 are temperature-controlled even at a low load, but the heat exchange efficiency of water can be maintained at a high level. .

  On the other hand, the remaining water branched on the downstream side of the booster pump 29 flows through the main pipe 15 into the temperature control systems 11b and 11c corresponding to the second air conditioning zone 12b and the third air conditioning zone 12c. Since the flow of water flowing into the temperature control systems 11b and 11c and the heat exchange and the flow of water to the temperature control system 11a corresponding to the first air conditioning zone 12a are in accordance with the second embodiment, the description thereof is omitted. To do.

  The combination of the air-conditioning zones 12 for temperature control is not limited to that described above, and the temperature control of the three air-conditioning zones 12 may be simultaneously performed and the degree of the temperature control may be reduced.

  According to the liquid piping facility 25 used for heat utilization of the third embodiment, heat exchange of the heat source device 13 without extremely reducing the flow rate (or flow velocity) of water flowing into the heat source device 13 at the time of low load. Efficiency can be maintained in a high state. Therefore, the air conditioning efficiency of the liquid piping facility 25 used for heat utilization can be improved and the power consumption can be reduced.

  Further, by providing the booster pump 29 on the upstream side of the main pipe 15, the pump 5 provided in the temperature control system 11 can be downsized.

  [Fourth Embodiment] Next, a liquid piping facility used for heat utilization according to a fourth embodiment will be described with reference to FIG. The liquid piping facility 31 used for heat utilization in the fourth embodiment is different from the liquid piping facility 1 used for heat utilization in the first embodiment in that a heat storage tank (heat storage device) 33 is provided in the heat source device 13. To do.

  Since the basic configuration of the liquid piping facility 31 used for heat utilization is the same as that of the liquid piping facility 1 used for heat utilization in the first embodiment, the same reference numerals are given to the same mode portions and the description thereof is omitted.

  The heat source device 32 of the liquid piping facility 31 used for heat utilization is composed of a water-water heat exchanger 35, an air heat source heat pump 37 for producing heat source water, two pumps 39a and 39b, and a heat storage tank 33.

  The water-water heat exchanger 35 exchanges heat between the water that has passed through the temperature control system 11 and the heat source water (cold / warm water) of the heat storage tank 33, and the secondary side of the water-water heat exchanger 35. The main pipe 15 is connected to the flow path 45, and the heat source water circulation pipe 41 of the heat storage tank 33 is connected to the primary side flow path 47.

  The heat source water in the heat storage tank 33 is pumped by the pump 39b, passes through the circulation line 41 and the primary flow path 47 of the water-water heat exchanger 35, and returns to the heat storage tank 33 again. Further, the heat source water in the heat storage tank 33 is stored at a constant temperature by the air heat source heat pump 37.

  The heat storage tank 33 is configured so that the heat source water released from the discharge port of the circulation line 43 is not connected to the intake port of the circulation line 43 so that the heat source water released from the discharge port of the circulation line 41 is short-circuited. In the heat storage tank 33, the heat source water discharged from the circulation pipe 41 to the heat storage tank 33 and the discharge pipe of the circulation pipe 43 are discharged to the heat storage tank 33 so as not to short-circuit to the water intake of the path 41. Heat source water is not mixed.

  For example, a plate-type heat exchanger can be used as the water-water heat exchanger 35, and a heat production device having a heat transfer surface such as power generation exhaust heat of a cogeneration system can be used instead of the air heat source heat pump 37. Can do. The form of heat storage may be ice or a latent heat storage material, and the primary liquid in the water-water heat exchange may be brine or ice water slurry.

  According to the liquid piping facility 31 used for heat utilization in the fourth embodiment, the heat source device 32 includes the heat storage tank 33, thereby reducing the facility capacity of the first heat exchanger 35 of the heat source device 32. At the same time, the heat exchange efficiency can be improved. Therefore, it is possible to reduce power consumption in the liquid piping facility 31 used for heat utilization.

  (Other Examples) In the first to fourth embodiments, the detection signal of the temperature sensor 16 in the air conditioning zone 12 corresponding to the temperature control system 11 and the constant outlet water temperature flowing out from the heat source devices 13 and 32 are used. Based on this, the operation capacity of the pump 5 is changed to control the flow rate of water. However, the present invention is not limited to this, and it corresponds to the temperature change of the water flowing out from the heat source devices 13 and 32 and the detection signal of the temperature sensor 16. It is also possible to control the flow rate of water by changing the operation capacity of the pumps 5, 21, and 29.

  Moreover, it is good also considering the acceptance heat source from DHC (district cooling / heating) as a heat source apparatus. Furthermore, the heat exchanger is not limited to the fan coil unit 7 but can be constituted by a water heat source heat pump unit, a cooling / refrigeration unit for a refrigerator using brine, a panel heater, a fan convector, and other devices that perform individual heat dissipation / heat absorption functions.

  As the backflow prevention means, an on / off valve (two-way valve / electromagnetic valve) can be used in addition to the check valve. Since the on / off valve does not reduce the pipe diameter around the valve, the pressure loss does not increase as in the case of using the control valve.

It is a block diagram which shows the liquid piping equipment with which it uses for the heat | fever in the 1st Embodiment of this invention. It is a block diagram which shows the liquid piping equipment with which it uses for the heat in the 2nd Embodiment of this invention. It is a block diagram which shows the liquid piping equipment with which it uses for the heat in the 3rd Embodiment of this invention. It is a block diagram which shows the liquid piping equipment with which it uses for the heat | fever in the 4th Embodiment of this invention. It is a block diagram which shows the liquid piping installation used for the conventional heat utilization.

Explanation of symbols

1, 17, 25, 31 Liquid piping equipment for heat utilization 3 Check valve (back flow prevention means)
5 Pump 7 Fan coil unit (heat exchanger)
9 Branch piping 11, 11a, 11b, 11c Temperature control system 13, 32 Heat source device 15 Main piping 19 Bypass piping 21 Circulating pump 23 Check valve 27 Flow rate adjusting valve 29 Booster pump (feeding pump)
33 Heat storage tank (heat storage device)

Claims (3)

A temperature control system for independently air-conditioning multiple zones,
While connected in parallel to the heat source device via the main pipe,
Each with a heat exchanger,
A capacity-controllable pump that variably controls the heat medium supply amount to the heat exchanger according to the temperature state of the zone;
Back flow prevention means connected to the upstream side or downstream side of the pump to prevent the back flow of the heat medium and to keep the flow direction constant;
A branch pipe connecting the heat exchanger, the pump and the backflow prevention means;
With
The backflow prevention means opens when the capacity-controllable pump is in operation and allows the flow of the heat medium, and closes when the capacity-controllable pump stops operating to prevent the backflow of the heat medium. A temperature control system characterized by being a valve. The temperature control system according to claim 1, wherein the temperature control system does not include a control valve for reducing a pipe diameter in the system. The temperature control system according to claim 1, wherein the pump controls the rotational speed of the pump according to a temperature condition of the zone.

Images