JP5433451B2 - Heat source system - Google Patents

Description

  The present invention relates to a heat source system, and more particularly, to a heat source system in which variations in the distribution of processing loads of a refrigerator according to the state of heat load are increased.

  For example, as typified by clean room air conditioning systems in semiconductor-related factories, etc., a system that separates all outside air heat treatment and indoor sensible heat treatment from the viewpoint of energy saving by avoiding dehumidification and reheating operation is adopted. .

  FIG. 6 shows a schematic system diagram of an example of the above-described system. In this system, an intermediate temperature system 180 and a low temperature system 190 are configured independently. The intermediate temperature system 180 connects a dry coil 181 that processes sensible heat and an intermediate temperature refrigerator 110 that manufactures intermediate temperature cold water to be supplied to the dry coil 181 with a pipe, and between the dry coil 181 and the intermediate temperature refrigerator 110. Circulate medium temperature cold water. The low-temperature system 190 connects an external air conditioner 191 that processes total heat and a low-temperature refrigerator 130 that manufactures low-temperature cold water to be supplied to the external air conditioner 191 with pipes, and the external air conditioner 191 and the low-temperature refrigerator 130 Circulate cold water at low temperature between. The medium-temperature cold water supplied to the dry coil 181 need only be at a relatively high temperature (for example, about 13 ° C.) because the dry coil 181 does not perform the latent heat treatment and thus the processing air does not have to be lowered to the dew point temperature. On the other hand, the low-temperature cold water supplied to the external air conditioner 191 is cooled to a relatively low temperature (for example, 7 ° C.) because the treated air is lowered below the dew point temperature for dehumidification. In this system, since the temperature of the cold water produced by the intermediate temperature refrigerator in the intermediate temperature system 180 may be relatively high, the COP (coefficient of performance) of the intermediate temperature refrigerator can be improved, which contributes to energy saving.

  However, in the above-described system, the middle temperature system and the low temperature system are configured independently, and each is operated independently, so when performing an appropriate partial load operation according to the variation of the heat load to be processed, Only the optimum operation can be performed in each of the medium temperature system and the low temperature system, and variations of the optimum operation are limited.

  The above situation applies not only to cooling operation but also to heating operation. In recent years, a radiant cooling and heating system has attracted attention as a cooling and heating system that achieves both energy saving and comfort. However, the temperature of hot water (heat medium) that heats the radiant panel used in the radiant cooling and heating system has been generally used in the past. The temperature is lower than the temperature of the hot air in the convection method. That is, the difference between the temperature of the heat medium supplied to the radiant panel and the temperature of the air conditioning target room is relatively small. Also in the case of heating operation, the COP of the small temperature difference heat source machine can be improved by replacing the medium temperature refrigerator 110 in FIG. 6 with a small temperature difference heat source machine and the low temperature refrigerator 130 with a large temperature difference heat source machine. The optimum operation can be performed only in each of the small temperature difference heat source system and the large temperature difference heat source system, and variations of the optimum operation are limited.

  In view of the above-described problems, an object of the present invention is to provide a heat source system in which variations in the distribution of the processing load of a heat source machine (including a refrigerator) according to the state of the heat load are increased.

  In order to achieve the above object, the heat source system according to the first aspect of the present invention, for example, as shown in FIG. 1, the temperature of the heat medium C so that the difference from the reference temperature becomes a first predetermined value. A small temperature difference heat source device 10 capable of adjusting the temperature; and a small temperature difference heat medium CMS, which is the heat medium C adjusted in temperature by the small temperature difference heat source device 10, is supplied to the first load side device 81 that processes the heat load. A small temperature difference return unit 21 to be passed before the temperature difference is collected; and the small temperature difference heat medium CM in which heat is used in the first load side device 81 is collected before returning to the small temperature difference heat source unit 10. A collecting portion 22; a small temperature difference introducing pipe 12 that guides the heat medium C in the small temperature difference collecting portion 22 to the small temperature difference heat source device 10; a small temperature difference collecting portion 21 and a small temperature difference collecting portion 22; A small temperature difference communication pipe 25 that communicates without passing through the small temperature difference heat source device 10; and a difference from the reference temperature is a first predetermined value A large temperature difference heat source device 30 capable of adjusting the temperature of the heat medium C so as to be a second predetermined value larger than the above; a large temperature difference heat which is the heat medium C whose temperature is adjusted by the large temperature difference heat source device 30 The large temperature difference heat medium CL derived from the second load side device 91 different from the first load side device 81 that processes the heat load using the heat of the medium CLS flows into the small temperature difference communication pipe 25. A large temperature difference heat medium return pipe 44 to be caused; and a large temperature difference introduction pipe 32 for guiding the heat medium C in the small temperature difference forward gathering portion 21 to the large temperature difference heat source unit 30.

  When the heat source system according to the first aspect of the present invention is used for cooling, for example, as shown in FIG. 1, an intermediate temperature refrigerator 10 capable of cooling the heat medium C to a predetermined intermediate temperature; An intermediate temperature collecting unit 21 that passes the medium temperature heat medium CMS that is the heat medium C cooled by the machine 10 before supplying the medium temperature heat medium CMS to the first load side device 81 that processes the heat load; and the first load side device 81 The intermediate temperature collecting medium 22 that collects the medium temperature heating medium CM in which the cold energy is used before returning it to the medium temperature refrigerator 10; and the medium temperature introduction pipe 12 that guides the heat medium C in the medium temperature recovery group 22 to the medium temperature refrigerator 10. An intermediate temperature communication pipe 25 that connects the intermediate temperature collecting section 21 and the intermediate temperature return collecting section 22 without going through the intermediate temperature refrigerator 10, and a low-temperature refrigerator that can cool the heat medium C to a lower temperature than the intermediate temperature. 30; a low temperature heating medium which is the heating medium C cooled by the low temperature refrigerator 30 Return of the low-temperature heat medium that causes the low-temperature heat medium CL derived from the second load-side device 91 different from the first load-side device 81 that processes the heat load using the cold heat of the CLS to flow into the intermediate temperature communication pipe 25 A pipe 44; and a low-temperature introduction pipe 32 that guides the heat medium C in the medium temperature collecting section 21 to the low-temperature refrigerator 30.

  With this configuration, the small temperature difference heat source device and the large temperature difference heat source device are arranged in series, and the large temperature difference heat medium derived from the second load side device is converted into the large temperature difference heat source device and the small temperature. Since it can be distributed and returned to the differential heat source unit, a part or all of the thermal load of the second load side device can be processed by the small temperature differential heat source unit, and the large temperature differential heat source unit and The apportionment of the heat load of the second load side device to be processed by the small temperature difference heat source apparatus can also be determined as an appropriate value from the variations.

  Moreover, when the heat source system according to the second aspect of the present invention is shown with reference to FIG. 1, for example, in the heat source system according to the first aspect of the present invention, the small temperature difference heat source device 10 generates The temperature setting of the temperature difference heat medium CMS can be changed.

  If comprised in this way, the load of a large temperature difference heat source apparatus will be reduced by making the difference with the reference temperature the setting temperature of a small temperature difference heat source apparatus large in the range which does not affect the 1st load side apparatus. For example, it may be possible to stop the large temperature difference heat source unit at a time when the load of the large temperature difference heat source unit is low (for example, an intermediate period).

  In addition, the heat source system according to the third aspect of the present invention is, for example, as shown in FIG. 1, in the heat source system 1 according to the first aspect or the second aspect of the present invention described above. A small temperature difference deriving pipe 11 for guiding the generated small temperature difference heat medium CMS to the small temperature difference collecting section 21; and a heat medium supplied from the small temperature difference collecting section 21 to the first load side device 81 A small temperature difference supply pipe 23 that guides C to the outside of the small temperature difference collecting section 21; a state in which the small temperature difference communication pipe 25 and the large temperature difference introduction pipe 32 are adjacent to each other; The small temperature difference supply pipe 23 is connected to the small temperature difference collecting unit 21 in a state where the small temperature difference supply pipe 23 is adjacent to the small temperature difference supply pipe 23. Here, “the state in which the small temperature difference communication pipe and the large temperature difference introduction pipe are adjacent” typically means that there is no small temperature difference derivation pipe or small temperature difference supply pipe between them. The state in which the temperature difference derivation pipe and the small temperature difference supply pipe are adjacent to each other typically means that a small temperature difference communication pipe or a large temperature difference introduction pipe is not interposed therebetween.

  If comprised in this way, a small temperature difference heat medium will be circulated exclusively in the system | strain of a 1st load side apparatus, and the large temperature difference heat medium which flows through a large temperature difference heat medium return pipe will be given priority to a large temperature difference heat source machine. It is possible to introduce a surplus portion of the large temperature difference heat medium flowing through the large temperature difference heat medium return pipe into the small temperature difference heat source unit, and the first load side device and the second load side device. It is possible to optimally operate the large temperature difference heat source machine and the small temperature difference heat source machine without disturbing the requirements.

  Moreover, as shown in FIG. 3, for example, in the heat source system according to the fourth aspect of the present invention, the heat source system according to the fourth aspect of the present invention has a difference from the reference temperature equal to the first predetermined value. A backup heat source device 50 capable of generating a heat medium C in which the difference between the heat medium C and the reference temperature becomes a second predetermined value; and the heat medium C in the small temperature difference collecting unit 22 as the backup heat source device 50 A backup introduction pipe 52 for guiding the heat medium C, the temperature of which has been adjusted by the backup heat source device 50, between the connection part of the large temperature difference introduction pipe 32 and the connection part of the small temperature difference derivation pipe 11. And a backup lead-out pipe 51 to be introduced into the pipe 21.

  With this configuration, a backup heat source machine can be used for backup without providing a switching valve for switching supply to both systems in the system of the first load side device and the system of the second load side device. It becomes possible to do.

  In addition, the heat source system according to the fifth aspect of the present invention is, for example, referring to FIG. 1, in the heat source system 1 according to any one of the first to fourth aspects of the present invention. The amount of heat corresponding to a part of the maximum heat load processed by the second load side device 91 is applied with the amount of heat held by the small temperature difference heat medium CM adjusted in temperature by the small temperature difference heat source unit 10. In addition, the rated capacities of the small temperature difference heat source device 10 and the large temperature difference heat source device 30 are determined.

  If comprised in this way, the freedom degree at the time of selecting the capacity | capacitance of a small temperature difference heat source machine and a large temperature difference heat source machine can be enlarged.

  In addition, the heat source system according to the sixth aspect of the present invention is a heat source system according to any one of the first to fifth aspects of the present invention, as shown in FIG. There is provided an on-off valve 325v capable of blocking the flow of the heat medium CH in the small temperature difference communication pipe 25 between the connection part to the differential heat medium return pipe 44 and the small temperature return collecting part 22.

  If comprised in this way, the system of a small temperature difference heat source machine and a large temperature difference heat source machine system can be operated independently as needed, a heat carrier is cooled with a small temperature difference heat source machine, and a large temperature difference The heat medium can be heated by the heat source device, and the cold load and the warm load can be satisfied at the same time.

  According to the present invention, the small temperature difference heat source device and the large temperature difference heat source device are arranged in series, and the large temperature difference heat source derived from the second load side device is converted into the large temperature difference heat source device and the small temperature difference. Since it can be distributed and returned to the differential heat source unit, part or all of the thermal load of the second load side equipment can be processed by the small temperature differential heat source unit. The apportionment of the heat load of the second load side device to be processed by the temperature difference heat source apparatus can also be determined as an appropriate value from the variations.

1 is a schematic system diagram of a heat source system according to a first embodiment of the present invention. It is a figure of the table which shows the apportioning example of the rated output of a medium temperature refrigerator and a low-temperature refrigerator. It is a typical systematic diagram of the heat source system which concerns on the 2nd Embodiment of this invention. It is a typical systematic diagram of the heat source system which concerns on the 3rd Embodiment of this invention. It is a partial top view of the small temperature difference gathering part which comprises the heat-source system which concerns on the 3rd Embodiment of this invention. It is a typical systematic diagram of the conventional heat source system.

  Embodiments of the present invention will be described below with reference to the drawings. In the drawings, the same or similar members are denoted by the same or similar reference numerals, and redundant description is omitted.

  First, a heat source system 1 according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a schematic system diagram of the heat source system 1. In the present embodiment, it is assumed that both the small temperature difference heat source machine and the large temperature difference heat source machine are refrigerators. The heat source system 1 includes an intermediate temperature refrigerator 10 and a low temperature refrigerator 30 that cool cold water C as a heat medium, an intermediate temperature header 21 as an intermediate temperature assembly portion, an intermediate temperature header 22 as an intermediate temperature recovery portion, cold water Piping (which will be described in detail later) for effectively flowing C. The intermediate temperature refrigerator 10, the low temperature refrigerator 30, the intermediate temperature return unit, and the intermediate temperature return unit correspond to a small temperature difference heat source unit, a large temperature difference heat source unit, a small temperature difference set unit, and a small temperature return set unit, respectively. .

  In the following description, the cold water C may be distinguished as follows for convenience. The cold water C produced by the intermediate temperature refrigerator 10 is referred to as “medium temperature cold water CMS”, the cold water C introduced into the intermediate temperature refrigerator 10 is referred to as “medium temperature return cold water CMR”, and both are collectively referred to as “medium temperature cold water CM”. The cold water C produced by the low temperature refrigerator 30 is collectively referred to as “low temperature cold water CLS”, the cold water C introduced into the low temperature refrigerator 30 is referred to as “low temperature cold water CLR”, and both are collectively referred to as “low temperature cold water CL”. In addition, when distinguishing the cold water C for convenience of explanation, another name may be used as appropriate, and in this case, a code beginning with “C” is also attached. The medium temperature cold water CM corresponds to a small temperature difference heat medium, and the low temperature cold water CL corresponds to a large temperature difference heat medium. When both the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 are operated, the temperature of the low temperature cooling water CLS is typically lower than the temperature of the medium temperature cooling water CMS.

  The first load side device to which the medium temperature cool water CMS is supplied is typically a sensible heat treatment device for processing sensible heat, and the second load side device to which the low temperature cool water CLS is supplied is typically Is a total heat treatment device that processes total heat, but the first load side device may be a device that processes total heat, and the second load side device may be a device that processes sensible heat. . In the present embodiment, the cold water C produced by the heat source system 1 is used to perform precision air conditioning such as cooling in a clean room, and the dry coil 81 and the second load side device as the first load side device. It will be described as being supplied to the external air conditioner 91. In the precision air conditioning according to the present embodiment, in order to precisely adjust the temperature and humidity, the external air conditioner 91 performs the latent heat treatment (dehumidification) of the air for precision air conditioning, and the dry coil 81 has sensible heat (for example, production equipment). Only heat generation) is performed. For this reason, cold air C having a low temperature (for example, 7 ° C.) similar to that used for general air conditioning for dehumidification is supplied to the external air conditioner 91. On the other hand, the dry coil 81 is supplied with cold water C having a medium temperature (for example, 13 ° C.) higher than the low temperature so that dehumidification is not performed. The predetermined medium temperature is appropriately determined within a range in which sensible heat can be processed, which is higher than the dew point temperature of the processing air. The configuration of the heat source system 1 that manufactures the cold water C supplied to the load side devices 81 and 91 will be described below. In addition, since the load side devices 81 and 91 consume energy to cool the air, in order to distinguish the heat load processed by the load side devices 81 and 91 from the heat load processed by the refrigerators 10 and 30, Sometimes referred to as “air load”. In addition, since the refrigerators 10 and 30 consume energy to cool the cold water C, the heat load processed by the refrigerators 10 and 30 may be referred to as “cold water load”. The “medium temperature” is a temperature at which the difference from the reference temperature becomes the first predetermined value, and the “low temperature” is the temperature at which the difference from the reference temperature becomes the second predetermined value. The second predetermined value is greater than the first predetermined value. Here, the “reference temperature” is an arbitrary temperature at which the difference from the low temperature is greater than the difference from the intermediate temperature, and can be, for example, an outside air temperature in the middle period or 20 ° C.

  The intermediate temperature refrigerator 10 is, for example, a water-cooled or air-cooled heat source device used for air conditioning. Typically, a turbo refrigerator, an absorption refrigerator, a chilling unit, or the like is used. In the intermediate temperature refrigerator 10, a refrigerant (not shown) performs a refrigeration cycle (evaporation and condensation are alternately performed), and when the refrigerant evaporates, heat is taken from the intermediate temperature cold water CM passing through the intermediate temperature refrigerator 10 (cooling). ) To produce medium temperature cold water CMS. The medium-temperature refrigerator 10 is a device that exclusively brings the medium-temperature cold water CMS to a medium temperature, but is preferably configured so that the temperature setting can be changed as appropriate, and further has the ability to reduce the temperature. More preferably. By being configured so that the temperature setting can be changed as appropriate, the distribution of the chilled water load according to the load fluctuation (the share of the cold heat source for processing the air load of the dry coil 81 and the external air conditioner 91) Variations can be further increased. For example, the chilled water load of the low-temperature refrigerator 30 can be reduced by lowering the set temperature of the intermediate temperature refrigerator 10 within a range that does not affect the dry coil 81 (a range where the temperature is not too low). The low-temperature refrigerator 30 whose operation COP (coefficient of performance) has been reduced due to low-load operation in the season or the like can be stopped, and the intermediate-temperature refrigerator 10 can process the air load of the dry coil 81 and the external air conditioner 91. 1 energy saving can be achieved. Furthermore, when the intermediate temperature refrigerator 10 has the ability to reduce the intermediate temperature cold water CMS, the intermediate temperature refrigerator 10 can be used as a backup device when the low temperature refrigerator 30 fails.

  Connected to the intermediate temperature refrigerator 10 are an intermediate temperature cold water outlet tube 11 as an intermediate temperature outlet tube for extracting the produced intermediate temperature cold water CMS and an intermediate temperature cold water return tube 12 as an intermediate temperature inlet tube for introducing the intermediate temperature return cold water CMR. Yes. The intermediate temperature outlet tube corresponds to a small temperature difference inlet tube, and the intermediate temperature inlet tube corresponds to a small temperature difference inlet tube. The other end of the intermediate temperature cold water outgoing pipe 11 is connected to the intermediate temperature outgoing header 21. The other end of the intermediate temperature cold water return pipe 12 is connected to the intermediate temperature return header 22. An intermediate-temperature cold water pump 13 that pumps the intermediate-temperature cold water CM is inserted into the intermediate-temperature cold water return pipe 12. The configuration around the intermediate temperature refrigerator 10 can change the flow rate of the intermediate temperature cold water CMS flowing into the intermediate temperature header 21. As a configuration for making the flow rate of the medium-temperature cold water CMS flowing into the medium-temperature cold header 21 variable, an inverter is provided in the medium-temperature cold water pump 13 so that the discharge flow rate (and thus the flow rate of the cold water C passing through the medium-temperature refrigerator 10) is variable. (In this case, typically, the intermediate temperature refrigerator 10 is a so-called variable flow rate type), or the intermediate temperature in which a part of the intermediate warm water CMS discharged from the intermediate temperature refrigerator 10 is returned to the intermediate temperature cold water return pipe 12. A refrigerator bypass pipe (not shown) may be provided (in this case, typically, the intermediate temperature refrigerator 10 is a so-called constant flow type), or the intermediate temperature refrigerator 10 is divided into a plurality of units (in other words, For example, a group of medium-temperature refrigerators in which a plurality of medium-temperature refrigerators 10 are arranged in parallel is provided), and a medium-temperature cold water return pipe 12 in which a medium-temperature cold water outgoing pipe 11 and an intermediate-temperature cold water pump 13 are arranged is provided for each. Like Well (in this case, typically the medium temperature refrigerator 10 and a so-called constant flow type.) Also, or it may be a combination of two or more of these. In the present embodiment, for the sake of convenience, the description will be made on the assumption that the flow rate of the intermediate temperature cold water CMS flowing into the intermediate temperature header 21 is made variable by performing inverter control of the intermediate temperature cold water pump 13.

  A medium temperature supply pipe 23 is connected to the medium temperature header 21 as a small temperature difference supply pipe for leading the medium temperature cold water CM toward the dry coil 81. The other end of the intermediate temperature supply pipe 23 and the dry coil 81 are connected by a pipe 83 provided with an intermediate temperature secondary pump 82 that pumps the intermediate temperature cold water CM to the dry coil 81. The intermediate temperature secondary pump 82 has an inverter so that the discharge flow rate of the cold water C can be changed and / or is divided into a plurality of units so as to change the discharge flow rate of the cold water C as a whole. It may be configured to be able to. The pipe 83 is provided with an intermediate temperature thermometer 88 that detects the temperature of the cold water C flowing inside. A medium temperature return pipe 24 is connected to the medium temperature return header 22 as a medium temperature heat medium return pipe (small temperature difference heat medium return pipe) for introducing the medium temperature cold water CM derived from the dry coil 81. The other end of the intermediate temperature return pipe 24 and the dry coil 81 are connected by a pipe 84. The intermediate temperature return pipe 24 is provided with an intermediate temperature return thermometer 18 for detecting the temperature of the cold water C flowing inside and an intermediate temperature flow meter 19 for detecting the flow rate. The intermediate temperature return header 21 and the intermediate temperature return header 22 are connected by a medium temperature communication pipe 25 as a small temperature difference communication pipe that communicates the headers 21 and 22 without going through the intermediate temperature refrigerator 10. The medium temperature header 21 and / or medium temperature return header 22 is typically configured to have a frame and be installed on the floor, but may be configured as a pipe header that does not exhibit the appearance of a so-called header. Good. Furthermore, the intermediate temperature return header 21, the intermediate temperature return header 22, and the intermediate temperature communication pipe 25 may be configured so as to be integral with each other in appearance.

  The low-temperature refrigerator 30 is a water-cooled or air-cooled heat source device similar to the medium-temperature refrigerator 10, and typically a turbo refrigerator, an absorption refrigerator, a chilling unit, or the like is used. In the low-temperature refrigerator 30, a refrigerant (not shown) performs a refrigeration cycle (evaporation and condensation are alternately performed), and when the refrigerant evaporates, heat is extracted from the low-temperature cold water CL passing through the low-temperature refrigerator 30 (cools). ) To produce low-temperature cold water CLS. The low-temperature refrigerator 30 is a device that lowers the temperature of the cold cooling water CLS exclusively. However, if the low-temperature refrigerator 30 is configured to be able to change the temperature setting as appropriate, the low-temperature freezing water CLS is brought to a medium temperature in the intermediate period where the cold water load of the low-temperature refrigerator 30 is low, for example, to lower the temperature. The operation COP of the refrigerator 30 can be improved, and energy saving of the heat source system 1 can be achieved, which is preferable.

  Connected to the low-temperature refrigerator 30 are a low-temperature cold water forward pipe 31 as a low-temperature outlet pipe for deriving the produced low-temperature cold-cooled water CLS and a low-temperature cold water return pipe 32 as a low-temperature inlet pipe for introducing the low-temperature return cold water CLR. Yes. The low temperature lead pipe corresponds to a large temperature difference lead pipe, and the low temperature lead pipe corresponds to a large temperature difference lead pipe. The other end of the low-temperature cold water forward pipe 31 is connected to a low-temperature forward header 41. The other end of the low-temperature cold water return pipe 32 is connected to the intermediate temperature header 21. A low-temperature cold water pump 33 for pumping the low-temperature cold water CL is inserted into the low-temperature cold water return pipe 32. The configuration around the low-temperature refrigerator 30 is preferably configured such that the flow rate of the low-temperature cold water CLS flowing into the low-temperature header 41 can be changed from the viewpoint of energy saving. For example, an inverter may be provided in the low-temperature chilled water pump 33 so that the discharge flow rate (and thus the flow rate of the chilled water C passing through the low-temperature refrigerator 30) may be variable (in this case, the low-temperature refrigerator 30 is typically adapted to a so-called variable flow rate). Or by dividing the low-temperature refrigerator 30 into a plurality of units (in other words, forming a group of low-temperature refrigerators in which a plurality of low-temperature refrigerators 30 are arranged in parallel). The number control may be performed by providing a low temperature cold water return pipe 32 provided with a low temperature cold water pump 33 (in this case, the low temperature refrigerator 30 is typically a so-called constant flow type), or these. May be combined. In the present embodiment, for the sake of convenience, description will be made assuming that the flow rate of the low-temperature cold water CLS flowing into the low-temperature cold header 41 is made variable by inverter-controlling the low-temperature cold water pump 33.

  A low-temperature supply pipe 43 that leads low-temperature cold water CL toward the external air conditioner 91 is connected to the low-temperature forward header 41. The other end of the low temperature supply pipe 43 and the external air conditioner 91 are connected to each other by a pipe 93 provided with a low temperature secondary pump 92 that pumps the low temperature cold water CL to the external air conditioner 91. The low-temperature secondary pump 92 has an inverter so that the discharge flow rate of the cold water C can be changed and / or the discharge flow rate of the cold water C is changed as a whole by being divided into a plurality of units and performing unit control. It may be configured to be able to. The pipe 93 is provided with a low temperature thermometer 98 that detects the temperature of the cold water C flowing inside. The external air conditioner 91 is also connected with a pipe 94 for deriving the low-temperature cold water CL whose temperature has increased by using cold heat. The other end of the pipe 94 is connected to a low temperature return pipe 44 as a large temperature difference heat medium return pipe. The other end of the low temperature return pipe 44 is connected to the medium temperature communication pipe 25. Thus, the intermediate temperature communication pipe 25 is a member having a function of communicating the intermediate temperature return header 21 and the intermediate temperature return header 22 and a function of receiving the cold water C from the low temperature return pipe 44. In view of such a purpose, for example, when the low-temperature return pipe 44 is connected to a member having a header appearance, at least the low-temperature return pipe 44 of the member having the header appearance is connected. The portion up to this point is included in the concept of the intermediate temperature communication pipe 25. The low temperature return pipe 44 is provided with a low temperature return thermometer 38 for detecting the temperature of the cold water C flowing inside and a low temperature flow meter 39 for detecting the flow rate. In the intermediate temperature communication pipe 25, a communication flow meter 29 is disposed between the connection portion of the low temperature return pipe 44 and the intermediate temperature return header 22. The communication flow meter 29 may be disposed in the intermediate temperature communication pipe 25 between the connection portion of the low temperature return pipe 44 and the intermediate temperature header 21. Alternatively, it may be disposed both between the connection portion of the low temperature return pipe 44 and the intermediate temperature return header 22 and between the connection portion of the low temperature return pipe 44 and the intermediate temperature return header 21, and in this case, the low temperature flow meter 39 is not necessary. The intermediate temperature header 21 and the low temperature header 41 are connected by a low temperature bypass pipe 26 that communicates the headers 21 and 41 without passing through the low temperature refrigerator 30.

  In the present embodiment, the pipes connected to the intermediate temperature header 21 are, along the longitudinal direction of the intermediate temperature header 21, the intermediate temperature communication pipe 25, the low temperature cold water return pipe 32, the intermediate temperature cold water forward pipe 11, and the intermediate temperature supply pipe 23. However, the connection order is not limited as long as the intermediate temperature communication pipe 25 and the low temperature cold water return pipe 32 are adjacent to each other, and the intermediate temperature cold water outgoing pipe 11 and the intermediate temperature supply pipe 23 are adjacent to each other. In the present embodiment, the low temperature bypass pipe 26 is connected to the intermediate temperature header 21 on the intermediate temperature communication pipe 25 side of the connecting portion with the low temperature cold water return pipe 32. What is necessary is just to be connected in the position close | similar to the low temperature cold water return pipe 32 rather than both the pipes 23. By connecting each pipe to the intermediate temperature header 21 in such a manner, the system of the intermediate temperature refrigerator 10 and the dry coil 81 and the system of the low temperature refrigerator 30 and the external air conditioner 91 are independent (separated). Even if they are integrated without being configured, it is possible to prevent the low-temperature cold water CL flowing from the intermediate-temperature communication pipe 25 and the low-temperature bypass pipe 26 from flowing into the intermediate-temperature feed header 21 from flowing into the intermediate-temperature supply pipe 23, and supplying water to the dry coil 81. It is possible to maintain the chilled water C at an appropriate temperature. Further, the cold water C supplied to the dry coil 81 is connected in series in the order of the intermediate temperature refrigerator 10, the intermediate temperature header 21, and the low temperature refrigerator 30 from the upstream to the downstream as viewed from the overall flow direction of the cold water C. Therefore, the possibility that the low-temperature cold water C is erroneously introduced into the dry coil 81 can be further reduced. In the present embodiment, each pipe connected to the intermediate temperature return header 22 is connected in the order of the intermediate temperature communication pipe 25, the intermediate temperature return pipe 24, and the intermediate temperature cold water return pipe 12 along the longitudinal direction of the intermediate temperature return header 22. However, the order of connection is not limited.

  In the heat source system 1 connected in series in the order of the intermediate temperature refrigerator 10, the intermediate temperature header 21, and the low temperature refrigerator 30, the rated outputs (also referred to as rated refrigeration capacity or rated refrigeration capacity) of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 are obtained. It is possible to determine from a plurality of variations. For example, when the total maximum air load of the dry coil 81 is a heat amount per unit time corresponding to 800 kW, and the total maximum air load of the external air conditioner 91 is a heat amount per unit time corresponding to 1200 kW, the medium temperature refrigeration If the system of the machine 10 and the dry coil 81 and the system of the low temperature refrigerator 30 and the external air conditioner 91 are configured independently (separated), the rated refrigeration capacity of the intermediate temperature refrigerator 10 is set to 800 kW, and the rating of the low temperature refrigerator 30 Although the refrigeration capacity must be 1200 kW, in the heat source system 1 in which the dry coil 81 system and the external air conditioner 91 system are integrated, the rated refrigeration capacity of the intermediate temperature refrigerator 10 corresponds to the maximum air load of the dry coil 81. Refrigeration capacity (800 kW in this example) or more, and the total rated refrigeration capacity of the medium temperature refrigerator 10 and the low temperature refrigerator 30 is 2000 kW. In its apportioning can be determined from a plurality of variations.

  Referring now also to FIG. 2, FIG. 2 shows an example of apportionment of the rated output (rated refrigeration capacity) of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 under the above conditions. In Example 1, the rated output of the intermediate temperature refrigerator 10 is matched with the air load of the dry coil 81, and the rated output of the low temperature refrigerator 30 is matched with the air load of the external air conditioner 91. As in Example 2, both the rated output of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 may be 1000 kW, and the rated output of the intermediate temperature refrigerator 10 is larger than the rated output of the low temperature refrigerator 30 as in Example 3. May be. Alternatively, as shown in Example 4 and Example 5, the intermediate temperature refrigerator 10 and / or the low temperature refrigerator 30 is divided into a plurality of units, the rated output of the intermediate temperature refrigerator 10 is 800 kW or more, and the intermediate temperature refrigerator 10 and the low temperature refrigerator. The apportionment of the rated output of each of the refrigerators 10 and 30 may be appropriately determined so that the total rated output of the refrigerator 30 is 2000 kW. Thus, the economical combination is determined in consideration of the initial cost and the running cost around each of the refrigerators 10 and 30 from various variations of the rated output of the medium temperature refrigerator 10 and the low temperature refrigerator 30. (Economic design)

  The output at the time of operation of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 (the amount of cold heat available for the chilled water C produced by each refrigerator 10, 30) is adjusted by receiving a signal from the control device 60. It is configured. The control device 60 is a device that controls the operation of the heat source system 1, and transmits signals to the medium temperature chilled water pump 13 and the low temperature chilled water pump 33 in addition to operation control and temperature setting of the medium temperature refrigerator 10 and the low temperature refrigerator 30. Each rotational speed (and hence the discharge flow rate) can be adjusted. The control device 60 receives temperature signals from the intermediate temperature return thermometer 18, the low temperature return thermometer 38, the intermediate temperature return thermometer 88, and the low temperature return thermometer 98, and the intermediate temperature flow meter 19, the communication flow meter 29, and the low temperature flow meter. The flow rate signal is received from 39 and can be reflected in the control of both refrigerators 10, 30 and both pumps 13, 33. For example, the operation load of the dry coil 81 is calculated from the measured values of the intermediate temperature return thermometer 18, the intermediate temperature return thermometer 88 and the intermediate temperature flow meter 19, and the low temperature return thermometer 38, the low temperature return thermometer 98 and the low temperature flow meter 39 The operating load of the external air conditioner 91 is calculated from the measured value, and the cold water load in the medium temperature refrigerator 10 and the low temperature refrigerator 30 is taken into consideration, and the proportion of the air load of the external air conditioner 91 that is handled by both the refrigerators 10 and 30 is taken into consideration. Based on this setting, the flow rate and temperature of the cold water C produced by the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 or the flow rate of the cold water C passing through the communication flow meter 29 is calculated. In addition to controlling the operation of the medium-temperature refrigerator 10 and the low-temperature refrigerator 30 so that the calculated flow rate and temperature of the cold water C produced by the medium-temperature refrigerator 10 and the low-temperature refrigerator 30 are obtained, it passes through the communication flow meter 29. The rotational speed of the medium temperature chilled water pump 13 is adjusted so that the flow rate of the chilled water C to be the calculated value. Further, the control device 60 controls other flow sources such as variable flow rate control of the intermediate temperature secondary pump 82 and the low temperature secondary pump 92 and variable flow rate control of the cooling water pumps (not shown) of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30. An operation control system may also be used.

  With continued reference to FIG. 1, the operation of the heat source system 1 will be described. In the following description, the intermediate temperature refrigerator 10, the intermediate temperature cold water pump 13, the intermediate temperature secondary pump 82, the low temperature refrigerator 30, the low temperature cold water pump 33, and the low temperature secondary pump 92 have variable flow specifications, and each pump 13, 33, 82 92, the variable flow rate method is inverter control. Further, the rated output of the intermediate temperature refrigerator 10 and the maximum air load of the dry coil 81, and the rated output of the low temperature refrigerator 30 and the maximum air load of the external air conditioner 91 are assumed to have the same amount of heat. First, as a basic operation situation, intermediate temperature cold water CMS corresponding to the flow rate of cold water C supplied to the dry coil 81 is manufactured by the intermediate temperature refrigerator 10, and corresponds to the flow rate of cold water C supplied to the external air conditioner 91. The case where the low-temperature cold-cooled water CLS is manufactured by the low-temperature refrigerator 30 will be described. In this case, the intermediate temperature refrigerator 10 produces intermediate temperature cold water CMS at an intermediate temperature (eg, 13 ° C. in the present embodiment), and the low temperature refrigerator 30 generates low temperature cold water at a low temperature (eg, 7 ° C. in the present embodiment). CLS is manufactured. The cold water C flowing through the dry coil 81 and the external air conditioner 91 has a variable flow rate in which the flow rate is controlled according to the fluctuation of the air load to be processed. Further, the rotational speed of the intermediate temperature cold water pump 13 is adjusted so that the flow rate of the intermediate temperature cold water CMS flowing into the intermediate temperature header 21 and the flow rate of the cold water C flowing into the dry coil 81 are equal. Further, at least the flow rate of the low-temperature cold water CLS flowing into the low-temperature forward header 41 so that the flow rate of the low-temperature cold-cooled water CLS flowing into the low-temperature forward header 41 and the flow rate of the cold water C flowing into the external controller 91 are preferably equal. The rotational speed of the low-temperature chilled water pump 33 is adjusted so as to be larger than the flow rate of the chilled water C flowing into the external air conditioner 91. When the flow rate of the low-temperature cold water CLS flowing into the low-temperature forward header 41 is larger than the flow rate of the cold water C flowing into the external air conditioner 91, the surplus is led to the low-temperature cold water return pipe 32 via the low-temperature bypass pipe 26.

  As described above, when the rotation speeds of the medium temperature cold water pump 13 and the low temperature cold water pump 33 are adjusted, the medium temperature medium temperature cold water CMS produced by the medium temperature refrigerator 10 is transferred from the medium temperature cold water forward pipe 11 to the medium temperature cold header 21. Into the intermediate temperature supply pipe 23, boosted by the intermediate temperature secondary pump 82, and flows into the dry coil 81 through the pipe 83. The intermediate temperature cold water CMS that has flowed into the dry coil 81 deprives the sensible heat of the air to be treated (not shown) and rises in temperature (for example, 18 ° C. in the present embodiment), and then the pipe 84 and the intermediate temperature return pipe 24. Then, it flows into the intermediate temperature refrigerator 10 as intermediate temperature return cold water CMR via the intermediate temperature return header 22 and the intermediate temperature cold water return pipe 12. The medium-temperature return cold water CMR that has flowed into the medium-temperature refrigerator 10 is cooled and becomes medium-temperature medium-temperature cold water CMS, and is derived from the medium-temperature refrigerator 10 again.

  On the other hand, the low-temperature low-temperature cold water CLS produced by the low-temperature refrigerator 30 flows into the low-temperature supply pipe 43 from the low-temperature cold water forward pipe 31 through the low-temperature forward header 41, and is pressurized by the low-temperature secondary pump 92 to be piped. It flows into the external air conditioner 91 through 93. The low-temperature cold-cooled water CLS that has flowed into the external air conditioner 91 takes the total heat of the air to be treated (not shown) and rises in temperature (in this embodiment, for example, 17 ° C.), and then the pipe 94 and the low-temperature return pipe It flows into the intermediate temperature communication pipe 25 through 44. The low-temperature chilled water CL that has flowed into the intermediate temperature communication pipe 25 flows toward the intermediate-temperature header 21 due to the flow distribution, and the low-temperature refrigerator as the low-temperature return chilled water CLR via the intermediate-temperature header 21 and the low-temperature chilled water return pipe 32. 30. The low-temperature return cold water CLR that has flowed into the low-temperature refrigerator 30 is cooled to become low-temperature low-temperature cold-cooled water CLS, and is derived from the low-temperature refrigerator 30 again.

  As described above, the heat source system 1 is configured so that the flow rate of the medium-temperature cold water CMS flowing into the medium-temperature cold header 21 is equal to the flow rate of the cold water C flowing into the dry coil 81, and preferably in the low-temperature cold header 41. Supplied to the dry coil 81 by adjusting the rotational speeds of the medium temperature chilled water pump 13 and the low temperature chilled water pump 33 so that the flow rate of the flowing cold water CLS and the flow rate of the chilled water C flowing into the air conditioner 91 are equal. The system of the medium temperature cold water CM to be performed and the system of the low temperature cold water CL supplied to the external air conditioner 91 can be operated as separated from each other while being connected and integrated by piping. Based on such operation, the heat source system 1 optimizes the operation of each of the refrigerators 10 and 30 (for example, the viewpoint of the lowest energy consumption (COP becomes higher) or the lowest operation cost). In order to achieve an optimal operating capacity (distribution of treated chilled water load) when viewed from the above, it is possible to operate as follows.

  For example, when the air load of each of the dry coil 81 and the external air conditioner 91 is smaller than the rating (100%) and the medium temperature refrigerator 10 and the low temperature refrigerator 30 are operated with a cold water load smaller than the rating, the medium temperature By increasing the rotation speed of the cold water pump 13, the flow rate of the medium temperature cold water CM cooled by the medium temperature refrigerator 10 is increased. Then, while the system of the medium-temperature cold water CM supplied to the dry coil 81 flows as in the above-described basic operation situation, an increase in the medium-temperature cold water CMS produced by the medium-temperature refrigerator 10 (manufactured by the medium-temperature refrigerator 10). A flow rate obtained by subtracting the flow rate of the medium-temperature cold water CMS flowing into the medium-temperature supply pipe 23 from the flow rate of the medium-temperature cold-cooled water CMS) flows toward the low-temperature cold water return pipe 32. On the other hand, in the system of the low-temperature cold water CL supplied to the external air conditioner 91, a part of the low-temperature cold water CL that flows into the intermediate-temperature communication pipe 25 from the low-temperature return pipe 44 flows toward the intermediate-temperature return header 22. The low-temperature cold water CL that has flowed into the medium-temperature return header 22 from the medium-temperature communication pipe 25 is mixed with the medium-temperature cold water CM that has flowed into the medium-temperature return header 22 from the medium-temperature return pipe 24 and flows into the medium-temperature refrigerator 10 as medium-temperature return cold water CMR. It becomes medium temperature cold water CMS of temperature. And, the intermediate temperature cold water CMS manufactured by the intermediate temperature refrigerator 10 and flowing into the intermediate temperature header 21 from the intermediate temperature cold water outer pipe 11 flows from the intermediate temperature communication pipe 25 except for the amount supplied to the dry coil 81. It mixes with the low temperature cold water CL and flows into the low temperature refrigerator 30 as the low temperature return cold water CLR. At this time, the medium temperature cold water CMS (13 ° C. in the present embodiment) mixed in the medium temperature header 21 has a temperature lower than the low temperature cold water CL (17 ° C. in the present embodiment) flowing in from the medium temperature communication pipe 25. . For this reason, the temperature of the low-temperature return chilled water CLR flowing through the low-temperature chilled water return pipe 32 is lower than that when the entire amount flows from the intermediate temperature communication pipe 25, and the chilled water load to be processed by the low-temperature refrigerator 30 is reduced. As a result of such an operation, the system of the intermediate temperature cold water CM supplied to the dry coil 81 and the system of the low temperature cold water CL supplied to the external air conditioner 91 are separated, and the optimization operation is performed independently of each other. In a situation where each of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 is operated with a cold water load smaller than the rating, a part of the cold water load to be processed by the low temperature refrigerator 30 is distributed to the intermediate temperature refrigerator 10. As a result, the operation efficiency of the entire heat source system 1 can be increased. For example, when an inverter type turbo chiller having a remarkably high operation COP is employed as the intermediate temperature chiller 10 when the cooling water is operated at a low temperature such as in an intermediate period, the energy is further saved. The heat source system 1 changes the flow rate of the low temperature cold water CL flowing into the intermediate temperature communication pipe 25 from the low temperature return pipe 44 to the intermediate temperature return header 21 and the intermediate temperature return header 22 by changing the flow rate of the intermediate temperature cold water pump 13 as described above. The size of each pipe and the head of each pump are designed so that the apportionment with the going flow rate can be changed. Note that such control is performed so that the rated refrigeration capacity of the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 bears a part of the air load processed by the external air conditioner 91 during full load operation. Even if it is determined (for example, in the case of the relationship of Examples 2, 3, and 5 in FIG. 2), it can be similarly applied. That is, the chilled water C flowing into the intermediate temperature communication pipe 25 from the low temperature return pipe 44 is distributed to the flow toward the intermediate temperature return header 21 and the flow toward the intermediate temperature return header 22 even during full load operation, and each header during partial load operation. It is also possible to perform control such that the flow rate distribution of the cold water C toward 21 and 22 changes.

In addition, the control device 60 cools the air load processed by the external air conditioner 91 with the amount of cold heat held by the medium temperature cold water CMS cooled by the medium temperature refrigerator 10 and the low temperature refrigerator 30. A plurality of distribution patterns (for example, a pattern for preferentially operating the intermediate temperature refrigerator 10 in the intermediate period and an operation load factor of the low temperature refrigerator 30). A pattern that is maintained as high as possible) is stored in advance as a plurality of modes for each predetermined selection condition in accordance with a predetermined external condition, and a mode to be adopted in light of the predetermined selection condition is selected from the plurality of modes. The intermediate temperature refrigerator 10 and the low temperature refrigerator 30 may be operated according to the selected mode. Predetermined external conditions include seasons, outside air conditions, operation time, refrigerator cold water load, and the like. Predetermined selection conditions include energy saving, low running cost, low CO ₂ emission, and the like. If comprised in this way, the comparison table of the combination of a predetermined | prescribed external condition and an operation mode, a judgment figure, etc. will be memorize | stored beforehand for every predetermined | prescribed selection condition, and the intermediate temperature refrigerator 10 and low temperature freezing from the memorize | stored several mode will be carried out. The mode for operating the machine 30 can be selected, and the heat source system 1 can be appropriately operated with a relatively simple configuration. At this time, the control device 60 has a driving simulator (not shown) as a calculation unit that calculates a value serving as an index in light of the above-described predetermined selection condition for each of the plurality of modes. The index value obtained by the calculation in (2) may be compared to select a mode that best suits the above-described predetermined selection condition. If comprised in this way, the precision which adapts to a predetermined selection condition can be raised, and more suitable driving | operation can be performed. Further, the control device 60 has a database (not shown) that detects the degree of conformity of the above-described predetermined selection condition in the operation in the selected mode, and converts the detected degree of conformity into data and accumulates it. Also good. If comprised in this way, the adaptation degree of the predetermined | prescribed selection conditions in an actual driving | operation can be accumulated in a database, and it can feed back in order to perform more highly accurate control. The database (not shown) may be configured integrally with the control device 60 or may be configured separately. In addition, the control device 60 directly searches for an optimum value of the cold water load distribution between the intermediate temperature refrigerator 10 and the low temperature refrigerator 30 by an operation simulator (not shown), and adopts the search result as a target value for optimization control. It may be configured as follows. In this case, the search for the optimum value may be executed by combining a local search and an overall search. For example, a comparison between a predetermined increase / decrease value and the current value is performed as a local search with respect to the current set value, and the result of the local search is adopted as a set target value for optimization control. Perform an overall search that picks up the virtual setting values in a range that does not become appropriate, and if the virtual setting values tend to be locally optimized compared to the results of local search periodically, the current setting values are automatically or manually In this control, the local search is performed again for the updated value. If it does in this way, about control of the optimization operation which handles multivariable with respect to heat source system 1, improvement of optimization accuracy, stability of operation control, and simplification of control in system construction and actual operation are secured. Can do. In addition, the control device 60 may select an operation mode or search for an optimum value for the setting of the chilled water temperature and the chilled water amount of each of the refrigerators 10 and 30.

  Next, with reference to FIG. 3, the heat source system 2 which concerns on the 2nd Embodiment of this invention is demonstrated. FIG. 3 is a schematic system diagram of the heat source system 2. The heat source system 2 is different from the heat source system 1 (see FIG. 1) in that an auxiliary refrigerator 50 as a backup refrigerator (backup heat source machine) serving as a backup machine when the intermediate temperature refrigerator 10 or the low temperature refrigerator 30 fails. It is a point equipped with. That is, the configuration of the heat source system 2 further includes an auxiliary refrigerator 50 and an accessory attached thereto in addition to the configuration of the heat source system 1 (see FIG. 1).

  The auxiliary refrigerator 50 is a water-cooled or air-cooled heat source device similar to the medium temperature refrigerator 10 and the low temperature refrigerator 30, and typically a turbo refrigerator, an absorption refrigerator, a chilling unit, or the like is used. In the auxiliary refrigerator 50, a refrigerant (not shown) performs a refrigeration cycle (evaporation and condensation are alternately performed), and when the refrigerant evaporates, it takes heat from the cold water C passing through the auxiliary refrigerator 50 (cools). This is a device for cooling the cold water C. The auxiliary refrigerator 50 is configured to be able to appropriately change the temperature setting of the chilled water C (cooled chilled water C) after manufacture in accordance with the control signal received from the control device 60. Accordingly, it is configured so that cold water C having a medium temperature or cold water C having a low temperature can be produced.

  An auxiliary chiller 50 is connected to an auxiliary chilled water outgoing pipe 51 serving as a backup derivation pipe for extracting cooled chilled water C, and an auxiliary chilled water return pipe 52 serving as a backup introduction pipe for introducing the chilled water C to be cooled. Yes. In the present embodiment, the other end of the auxiliary cold water outgoing pipe 51 is connected to the intermediate temperature outgoing header 21 between the connection position of the intermediate temperature cold water outgoing pipe 11 and the connection position of the low temperature cold water return pipe 32. In the present embodiment, the other end of the auxiliary cold water return pipe 52 is connected to the intermediate temperature return header 22 between the connection position of the intermediate temperature return pipe 24 and the connection position of the intermediate temperature communication pipe 25. An auxiliary cold water pump 53 for pumping the cold water C is inserted into the auxiliary cold water return pipe 52. The auxiliary chilled water pump 53 may be configured to be variable in the discharge flow rate by providing an inverter. In the present embodiment, the connection position of the low temperature bypass pipe 26 to the medium temperature header 21 is opposite to the connection position of the auxiliary cold water return pipe 51 with respect to the low temperature cold water return pipe 32 (in other words, auxiliary cold water). The low temperature cold water return pipe 32 is connected to the intermediate temperature forward header 21 between the outgoing pipe 51 and the low temperature bypass pipe 26.) is positioned closer to the low temperature cold water return pipe 32 than the connecting portion with the intermediate temperature cold water outgoing pipe 11. If you do. In the heat source system 2, the low-temperature bypass pipe 26 has a function of absorbing the difference between the flow rate of the cold water C flowing into the low-temperature forward header 41 and the flow rate of the cold water C flowing into the external air conditioner 91 during steady operation. When the machine 30 breaks down, it functions as a bypass pipe that sends the cold water C produced by the auxiliary refrigerator 50 to the external air conditioner 91 side.

  In the heat source system 2 configured as described above, for example, when the intermediate temperature refrigerator 10 fails, the intermediate temperature cold water pump 13 is stopped and the auxiliary cold water pump 53 is started, and the set temperature is set to the intermediate temperature. Start up. By doing in this way, it becomes possible to perform the operation | movement demonstrated as an effect | action of the heat source system 1 (refer FIG. 1) by using the auxiliary refrigerator 50 as an alternative apparatus of the intermediate temperature refrigerator 10. FIG. Further, when the low-temperature refrigerator 30 breaks down, the low-temperature cold water pump 33 is stopped and the auxiliary cold water pump 53 is started, and the auxiliary refrigerator 50 is started with the set temperature being low. Thus, the auxiliary refrigerator 50 can be operated as an alternative device for the low-temperature refrigerator 30. The heat source system 2 is provided with a common backup machine for a system in which the system of the intermediate temperature refrigerator 10 and the dry coil 81 and the system of the low temperature refrigerator 30 and the external conditioner 91 are configured independently (FIG. 6). The configuration of control valves and pipes for switching the flow path is less than that of a broken line as compared with the example shown in FIG. In addition, the auxiliary refrigerator 50 may be provided for backup purposes, and a part (typically one) when a plurality of medium temperature refrigerators 10 are installed in parallel may be used. In this case, typically, the intermediate temperature refrigerator 10 that leads the cold water C to the intermediate temperature cold water outlet pipe 11 connected to the intermediate temperature header 21 near the coldest cold water return pipe 32 functions as the auxiliary refrigerator 50, and The auxiliary refrigerator 50 and the intermediate temperature refrigerator 10 are subjected to steady operation as the intermediate temperature refrigerator 10 except in an emergency.

  In the above description, for convenience of explanation, it is assumed that the medium temperature refrigerator 10 and the low temperature refrigerator 30 are each constituted by one unit. However, as mentioned in the above description, a plurality of units are arranged in parallel or They may be arranged in series. In this case, typically, a chilled water outgoing pipe and a chilled water return pipe provided with a chilled water pump are installed around the refrigerators connected in parallel. In addition, when the refrigerator is arrange | positioned in series, it is good to consider the whole refrigerator arrange | positioned in series as one refrigerator.

  In the above description, the heat source systems 1 and 2 have been described as producing the cold water C supplied to the load side devices 81 and 91 that perform precision air conditioning. However, for example, an air conditioning device for performing convection air conditioning (for example, Manufacturing medium-temperature chilled water CM supplied to equipment for radiant cooling that only requires introduction of cold water at a higher temperature than air handling units and fan coil units, and low-temperature chilled water CL supplied to air-conditioning equipment such as air handling units It is good to do. That is, the heat source systems 1 and 2 can be applied not only when the load side device is a device that performs precision air conditioning.

  Next, with reference to FIG. 4, the heat source system 3 which concerns on the 3rd Embodiment of this invention is demonstrated. FIG. 4 is a schematic system diagram of the heat source system 3. The heat source system 3 is configured such that the flowing heat medium becomes cold water and / or hot water depending on the situation. The heat source system 3 is different from the heat source system 1 (see FIG. 1) in that the small temperature difference heat source device is configured by the small temperature difference cooling / heating water device 310 and the large temperature difference heat source device is configured by the large temperature difference cooling / heating water device 330. A small temperature difference bypass pipe 328 that connects the small temperature difference collecting portion 21 and the small temperature difference collecting portion 22 without passing through the small temperature difference chiller / heater 310 is provided. The difference communication pipe 25 is provided with a small temperature difference communication cutoff valve 325v as an on-off valve for blocking the flow of the heat medium. Hereinafter, regarding a device that uses the heat of the heat medium supplied from the heat source system 3, the first load side device is the radiation panel 381, and the second load side device is the air conditioner (air handling unit) 391. explain. In addition, regarding the heat medium flowing through the heat source system 3, in the following description, a symbol beginning with “CH” is attached. The other configuration of the heat source system 3 is the same as that of the heat source system 1 (see FIG. 1). Below, description is added about the structure peculiar to the heat-source system 3. FIG. In the following description of the heat source system 3, the same reference numerals as those used in the heat source system 1 (see FIG. 1) but different names are used because the heat source system 1 (see FIG. 1) is cold. It is a system specialized for handling, while considering that the heat source system 3 handles both cold and hot, the physical configuration of equipment and piping with the same reference numerals is This is the same as the heat source system 1 (see FIG. 1).

  The small temperature difference chiller / heater 310 and the large temperature difference chiller / heater 330 are devices that can manufacture cold water or hot water according to the situation, in other words, devices that can manufacture both cold water and hot water. A cold / hot water generator or a heat pump chiller is used. In the present embodiment, the heat medium CH whose temperature is adjusted by the small temperature difference chiller / heater 310 is called a small temperature difference heat medium CHM, and the heat medium CH whose temperature is adjusted by the large temperature difference chiller / heater 330 is large. It is called temperature difference heat medium CHL. The small temperature difference chiller / heater 310 is a device that exclusively adjusts the temperature of the small temperature difference heat medium CHM to a predetermined medium temperature, but is preferably configured so that the temperature setting can be changed as appropriate. It is preferable to have the ability to achieve a high temperature (during heating) and / or a high temperature (during heating). The large temperature difference chiller / heater 330 is a device that adjusts the temperature of the large temperature difference heat medium CHL exclusively to a low temperature (during cooling) or a high temperature (during heating), but the temperature setting can be changed as appropriate. Since it is possible to save energy of the heat source system 3, it is preferable. Here, the “medium temperature” is a temperature at which the difference from the reference temperature is the first predetermined value. “Low temperature” and “high temperature” are temperatures at which the difference from the reference temperature is a second predetermined value. The second predetermined value is greater than the first predetermined value. The “reference temperature” is an arbitrary temperature at which the difference between the low temperature (during cooling) and the high temperature (during heating) becomes larger than the difference from the medium temperature. It can be set to 20 ° C. or the like.

  The small temperature difference bypass pipe 328 is a separate pipe from the small temperature difference communication pipe 25, and cold water is mainly produced by the small temperature difference cold / hot water machine 310, and hot water is produced by the large temperature difference cold / hot water machine 330. This tube is used when The small temperature difference bypass pipe 328 is connected to the small temperature difference forward collecting section 21 at a position closer to the small temperature difference derivation pipe 11 and the small temperature difference supply pipe 23 than the small temperature difference communication pipe 25 and the large temperature difference introduction pipe 32. The small temperature difference communicating pipe 25 is connected to the small temperature difference collecting portion 22 at a position closer to the small temperature difference introducing pipe 12 than the small temperature difference communicating pipe 25. In other words, in the small temperature difference forward collecting portion 21, the small temperature difference communicating tube 25 and the large temperature difference bypass tube 26 are provided between the connecting portion of the small temperature difference bypass tube 328 and the connecting portion of the small temperature difference deriving tube 11. In the small temperature difference return collecting portion 22, a small temperature difference introducing pipe 32 is connected between the connecting portion of the small temperature difference bypass pipe 328 and the connecting portion of the small temperature difference introducing pipe 12. The connecting portion of the temperature difference communication pipe 25 is configured not to intervene. The small temperature difference bypass pipe 328 is provided with a small temperature difference bypass cutoff valve 328v that blocks the flow of the heat medium CHM. The small temperature difference bypass shut-off valve 328v is connected to the control device 60 via a signal cable, and is configured to receive a signal from the control device 60 and perform an opening / closing operation.

  The small temperature difference communication cut-off valve 325v makes it possible to block the inflow of the heat medium CHL that has flowed into the small temperature difference communication pipe 25 from the large temperature difference heat medium return pipe 44 into the small temperature difference return collecting section 22. It is a valve and is provided between the connecting portion of the large temperature difference heat medium return pipe 44 and the small temperature difference collecting portion 22. The small temperature difference communication cut-off valve 325v is connected to the control device 60 through a signal cable, and is configured to receive a signal from the control device 60 and to perform an opening / closing operation.

  In the heat source system 3 configured as described above, the small temperature difference communication shut-off valve 325v is opened by the control device 60 when both the small temperature difference chiller water heater 310 and the large temperature difference chiller water heater 330 perform the cooling operation. The small temperature difference bypass cutoff valve 328v is closed, and the same operation as that of the heat source system 1 (see FIG. 1) is performed.

  Even when both the small temperature difference chiller / heater 310 and the large temperature difference chiller / heater 330 of the heat source system 3 perform heating operation, the small temperature difference communication cutoff valve 325v is opened by the control device 60, and the small temperature difference bypass cutoff valve is opened. 328v is closed. Then, the small temperature difference heat medium CHM is changed to medium temperature hot water by the small temperature difference chiller / heater 310, and the large temperature difference heat medium CHL is changed to high temperature hot water by the large temperature difference chiller / heater 330. Although the direction in which the difference is taken is different from that during cooling, the flow of the heat medium (hot water) CH, the flow rate distribution, and the like are the same as those during cooling. An example of the temperature condition at the time of heating is as follows. The small temperature difference heat medium CHM is heated to 35 ° C. by the small temperature difference chiller / heater 310, dissipates heat by the radiating panel 381, and the temperature is lowered to 30 ° C. It is introduced into the small temperature difference cold / hot water machine 310 and heated. On the other hand, the large temperature difference heat medium CHL is heated to 40 ° C. by the large temperature difference chiller / heater 330, heat-exchanged with air to be treated (not shown) by the air conditioner 391, and then the temperature is decreased to 30 ° C. It flows into the differential communication pipe 25 and is introduced into the small temperature difference collecting portion 21 or is appropriately distributed to the small temperature difference collecting portion 21 and the small temperature difference collecting portion 22.

  The heat source system 3 can also perform a cooling operation with the small temperature difference chiller / heater 310 and can perform a heating operation with the large temperature difference chiller / heater 330. Such an operation is performed, for example, when a cooling load is applied even in winter in a recent office building or the like in which a large number of devices that generate heat such as OA devices are installed indoors. In addition, for example, when the outside air is heated by the system of the air conditioner 391 to a temperature at which a predetermined absolute humidity can be achieved, and the office room that needs to be cooled is cooled by the system of the radiation panel 381, such an operation is performed. May be performed. When such a cold / warm simultaneous operation is performed, in the heat source system 3, the control device 60 closes the small temperature difference communication shut-off valve 325v and opens the small temperature difference bypass shut-off valve 328v. When the small temperature difference communication shut-off valve 325v is closed, the large temperature difference heat medium CHL that has flowed into the small temperature difference communication pipe 25 from the large temperature difference heat medium return pipe 44 flows into the small temperature difference return collecting section 22. All of them will flow into the small temperature difference gathering part 21 without doing so. Further, when the small temperature difference bypass shut-off valve 328v is opened, the flow rate of the small temperature difference heat medium CHM flowing into the small temperature difference collecting portion 21 flows into the radiation panel 381 (first load side device). When the flow rate exceeds the flow rate, the surplus is led to the small temperature difference collection unit 22 via the small temperature difference bypass pipe 328. When such a cold / warm simultaneous operation is performed, the small temperature difference heat medium CHM circulates between the small temperature difference chiller / heater 310 and the first load side device 381, and the large temperature difference heat medium CHL. Circulates between the large temperature difference chiller / heater 330 and the second load side device 391. That is, the small temperature difference system and the large temperature difference system are operated independently. As described above, when the cold / warm simultaneous operation is performed, the optimum operation can be performed in each of the small temperature difference system and the large temperature difference system. However, when performing the cooling operation or the heating operation, the heat source system 3 enables the integrated operation in which the variation of the optimum operation increases like the heat source system 1 (see FIG. 1), and also enables the simultaneous cooling / heating operation. This is a system with expanded applications.

  In addition, as shown in FIG. 5, when constructing the heat source system 3 that may perform the cold / warm simultaneous operation, the independent operation of the small temperature difference system and the large temperature difference system is more reliably performed. In other words, in order to prevent the small temperature difference heat medium CHM from entering the large temperature difference system and the large temperature difference heat medium CHL from entering the small temperature difference system, the small temperature difference transfer unit 21 is obstructed. A plate 21b may be provided. The baffle plate 21b includes a portion where the small temperature difference derivation pipe 11, the small temperature difference supply pipe 23, and the small temperature difference bypass pipe 328 (see FIG. 4) are connected, a large temperature difference introduction pipe 32, and a small temperature difference communication pipe. 25 and the large temperature difference bypass pipe 26 (see FIG. 4) are provided in the small temperature difference collecting portion 21 so as to be partially cut off. The baffle plate 21b may be a permanent plate-like member, or may be partially or fully closed during simultaneous cooling / heating operation as a valve that can be opened and closed, and fully opened during cooling operation or heating operation.

  In the description of the heat source system 3 described above, the small temperature difference heat source device and the large temperature difference heat source device are devices that can produce cold water or hot water depending on the situation, but only a heating operation is performed. In the case, it is good also as an apparatus which can manufacture only warm water. Moreover, although the small temperature difference communication cutoff valve 325v and the small temperature difference bypass cutoff valve 328v have been described as being automatic valves, they may be manual valves.

  Needless to say, the heat source system 3 can also be provided with a backup heat source device similarly to the heat source system 2 (see FIG. 3). In this case, the backup heat source device is preferably a heat source device similar to the small temperature difference heat source device and the large temperature difference heat source device. That is, when the small temperature difference heat source machine and the large temperature difference heat source machine are cold / hot water generators that can produce both cold water and hot water, the backup heat source machine is preferably a cold / hot water generator, etc. If the differential heat source machine and the large temperature difference heat source machine are refrigerators, the backup heat source machine may be a refrigerator. If the small temperature difference heat source machine and the large temperature difference heat source machine are heating heat source machines, the backup heat source machine is also a heating heat source machine. Is enough.

1, 2, 3 Heat source system 10 Medium temperature refrigerator (small temperature difference heat source machine)
11 Medium temperature cold water outlet pipe (small temperature difference derivation pipe)
12 Medium temperature cold water return pipe (small temperature difference introduction pipe)
21 Medium temperature header (small temperature difference collecting part)
22 Medium temperature return header (small temperature return assembly)
23 Medium temperature supply pipe (small temperature difference supply pipe)
25 Medium temperature communication pipe (small temperature difference communication pipe)
30 Low temperature refrigerator (large temperature difference heat source machine)
32 Low temperature cold water return pipe (large temperature difference introduction pipe)
44 Low temperature return pipe (large temperature difference heat medium return pipe)
50 Auxiliary refrigerator (backup heat source machine)
51 Auxiliary cold water outgoing pipe (backup outlet pipe)
52 Auxiliary cold water return pipe (backup introduction pipe)
81 Dry coil (first load side device)
91 External air conditioner (second load side equipment)
325v small temperature difference communication shut-off valve (open / close valve)
C Cold water CLS Low temperature cold water (large temperature difference heat medium)
CMS medium temperature cold water (small temperature difference heat medium)

Claims (6)

A small temperature difference heat source device capable of adjusting the temperature of the heat medium so that the difference from the reference temperature becomes a first predetermined value;
A first heat medium pump for flowing the heat medium passing through the small temperature difference heat source machine;
A small temperature difference gathering unit that passes the small temperature difference heat medium, which is a heat medium whose temperature has been adjusted by the small temperature difference heat source apparatus, before supplying it to the first load side device that processes the heat load;
Small temperature difference heat medium flow rate varying means for varying the flow rate of the small temperature difference heat medium flowing into the small temperature difference forward and backward collecting portion;
A small temperature difference collecting unit that collects the small temperature difference heat medium in which heat is used in the first load side device before returning to the small temperature difference heat source unit;
A small temperature difference introducing pipe for guiding the heat medium in the small temperature difference collecting portion to the small temperature difference heat source unit;
A small temperature difference communicating pipe that communicates the small temperature difference collecting portion and the small temperature difference collecting portion without going through the small temperature difference heat source unit;
A large temperature difference heat source device capable of adjusting the temperature of the heat medium such that a difference from the reference temperature becomes a second predetermined value larger than the first predetermined value;
A second heat medium pump for flowing the heat medium passing through the large temperature difference heat source machine;
Derived from a second load-side device different from the first load-side device that processes the heat load using the heat of the large-temperature-difference heat-medium, which is a heat medium whose temperature is adjusted by the large-temperature-difference heat-source device. A large temperature difference heat medium return pipe for flowing the large temperature difference heat medium into the small temperature difference communication pipe;
Bei example a large temperature difference inlet tube for guiding the heat medium of the small temperature Sa往in the set section to the large temperature difference heat source device;
The small temperature difference heat medium flow rate variable means has a configuration in which an inverter is provided in the first heat medium pump to vary the discharge flow rate, and the small temperature difference heat source device is divided into a plurality of units and corresponds to each of them. A first heat medium pump is provided to control the number of units;
Heat source system. The small temperature difference heat source device is configured to change a temperature setting of the small temperature difference heat medium to be generated;
The heat source system according to claim 1. A small temperature difference deriving tube for guiding the small temperature difference heat medium generated by the small temperature difference heat source device to the small temperature difference forward assembly portion;
A small temperature difference supply pipe that guides a heat medium supplied from the small temperature difference gathering portion toward the first load side device to the outside of the small temperature difference gathering portion;
The small temperature difference communication pipe and the large temperature difference introduction pipe are adjacent to each other, and the small temperature difference derivation pipe and the small temperature difference supply pipe are adjacent to each other, and are connected to the small temperature difference forward collecting portion. ;
The heat source system according to claim 1 or 2. A backup heat source machine capable of generating a heat medium whose difference from the reference temperature is the first predetermined value and a heat medium whose difference from the reference temperature is the second predetermined value;
A third heat medium pump for flowing the heat medium passing through the backup heat source unit;
A backup introduction pipe for guiding the heat medium in the small temperature return collecting section to the backup heat source unit;
A backup lead-out pipe that causes the heat medium adjusted in temperature by the backup heat source unit to flow into the small temperature difference collecting section between the connection part of the large temperature difference introduction pipe and the connection part of the small temperature difference lead-out pipe; Comprising:
The heat source system according to claim 3. The amount of heat corresponding to a part of the maximum heat load processed by the second load side device is applied with the amount of heat held by the small temperature difference heat medium adjusted in temperature by the small temperature difference heat source unit. The rated capacities of the small temperature difference heat source machine and the large temperature difference heat source machine were determined;
The heat source system according to any one of claims 1 to 4. An on-off valve capable of blocking the flow of the heat medium in the small temperature difference communication pipe between the connection portion with the large temperature difference heat medium return pipe and the small temperature difference return collecting section;
The heat source system according to any one of claims 1 to 5.

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