JP4266780B2 - Thermal storage heat source equipment - Google Patents

Description

The present invention relates to a heat storage type heat source facility used for air conditioning and the like, and in detail (see FIG. 2), in the heat exchanger 2 for heat radiation, the heat storage tank 1 is subjected to heat exchange with the primary heat medium A stored and cooled or heated. The secondary side heat medium B is supplied to the forward side merging section 5 by the heat radiation pump P1 through the heat radiation path 6 and the secondary side heat medium B cooled or heated by the heat source machine 4 is used for the heat source machine in parallel with this. The heat source machine pump P2 supplies the forward side junction 5 through the forward path 7,
The secondary heat medium B supplied from the heat-dissipating heat exchanger 2 and the heat source device 4 to the forward junction 5 is supplied to the load heat exchanger 9 by the load-side pump P3 through the load-side forward path 8, and this heat In parallel with the supply of the medium, the secondary heat medium B sent from the load heat exchanger 9 to the load side return path 10 is divided into a heat return return path 20 'and a heat source machine return path 21' to radiate heat. It is configured to return in parallel to the exchanger 2 and the heat source unit 4,
In this configuration, the flow rate of the secondary side heat medium B supplied to the forward side junction unit 5 by the heat dissipation pump P1, the flow rate of the secondary side heat medium B supplied to the forward side junction unit 5 by the heat source machine pump P2, and The flow control means 19 for adjusting the flow rate of the secondary side heat medium B supplied to the load heat exchanger 9 by the load side pump P3 according to the load in the load heat exchanger 9,
The present invention relates to a heat storage type heat source facility provided with a bypass path 25 ′ that short-circuits the forward-side merging section 5 to the return side heat medium path from the load heat exchanger 9.

  In this type of heat storage type heat source equipment, the secondary side heat medium B sent from the heat exchanger 2 for heat dissipation and the heat source unit 4 to the forward junction 5 for some reason such as a control error in the flow rate control by the flow rate control means 19. When the flow rate of the secondary side becomes larger than the flow rate of the secondary side heat medium B sent from the forward junction 5 to the load heat exchanger 9, the difference secondary side heat medium B is passed through the bypass 25 'to the load heat exchanger. 9 is made to flow in a short-circuited manner to the return side heat medium path from 9 so that the output (cold power output or heat output) on the side of the heat exchanger 2 for heat radiation and the heat source 4 and the load on the side of the load heat exchanger 9 ( Stable facility operation is maintained while achieving a smooth balance with the cooling load or heating load.

Conventionally, in this type of heat storage type heat source equipment, a return side heat medium path from the load heat exchanger 9 is formed, and as shown in FIG. 2, the load heat exchanger 9 passes through the load side return path 10. The returning secondary side heat medium B is received by the return side header 23 ′, and the secondary side heat medium B is radiated from the return side header 23 ′ through the heat release return path 20 ′ and the heat source unit return path 21 ′. It is configured to return in parallel to the exchanger 2 and the heat source unit 4, and the bypass path 25 ′ is connected to the return side heat medium path from the load heat exchanger 9 as a connection of the return side header 23 ′. The structure connected to the load side return path 10 in the vicinity of the upstream side or connected to the return side header 23 'has been adopted (see Patent Document 1).
JP 2002-89935 A

  However, in the case of the cold source equipment corresponding to the cooling load in the load heat exchanger 9 by cooling the secondary heat medium B by the heat exchanger 2 for heat dissipation and the heat source unit 4 respectively, When the heat medium flow toward the return-side heat medium path from the load heat exchanger 9 occurs in the bypass path 25 ′, one of the secondary-side heat medium B cooled by the heat dissipation heat exchanger 2 and the heat source unit 4. Is mixed into the return side secondary heat medium B in the load side return path 10 through the bypass path 25 '(that is, the secondary side heat medium heated by the cold heat consumption in the load heat exchanger 9). The secondary side heat medium B returned from the return side header 23 ′ to the heat radiating heat exchanger 2 is lowered in temperature, so that the secondary side heat medium B and the primary side heat medium A in the heat radiating heat exchanger 2 are The amount of heat exchange (in other words, the amount of cold heat extracted from the heat storage tank 1) is limited to a small amount, and in the load heat exchanger 9 at that time The consumption of the stored cold heat in the heat storage tank 1 does not progress for the rejection load, and this causes, for example, a state in which a large amount of cold heat remains in the heat storage tank 1 at the end of the operation of the equipment in one day. There is a problem that the advantages of the heat storage method cannot be fully utilized.

  In particular, the delay in the consumption of the heat stored in the heat storage tank due to the mixing of the low-temperature heat medium from the bypass 25 'occurs when the cooling load in the load heat exchanger 9 is extremely small (that is, load heat exchange by the load-side pump P3). In the situation where the flow rate of the secondary side heat medium B supplied to the vessel 9 is largely adjusted to the decrease side by the flow rate control means 19).

  This problem also applies to the case of the heat source equipment corresponding to the heating load in the load heat exchanger 9 by heating the secondary heat medium B in each of the heat dissipation heat exchanger 2 and the heat source unit 4. The temperature of the secondary heat medium B that is returned to the heat radiating heat exchanger 2 due to mixing of the high temperature heat medium from the bypass passage 25 ′ is increased, and the consumption of the stored heat in the heat storage tank 1 does not proceed. At the end of the operation, a large amount of heat remained in the heat storage tank 1.

  In view of this situation, the main problem of the present invention is to effectively solve the above problem by rational improvement.

The first characteristic configuration of the present invention is that a secondary heat medium cooled or heated by exchanging heat with a primary heat medium stored in a heat storage tank in a heat radiating heat exchanger is forwarded by a heat radiating pump through a heat radiating forward path. In parallel with this, the secondary side heat medium cooled or heated by the heat source unit is supplied to the forward side junction by the heat source unit pump through the forward path for the heat source unit.
While supplying the secondary side heat medium supplied from the heat-dissipating heat exchanger and the heat source unit to the forward side junction to the load heat exchanger by the load side pump through the load side forward path, in parallel with the supply of the heat medium The secondary side heat medium sent from the load heat exchanger to the load side return path is divided into a heat release return path and a heat source machine return path, and is parallel to the heat release heat exchanger and the heat source machine. To the configuration
In this configuration, the flow rate of the secondary heat medium supplied to the forward merging portion by the heat dissipation pump, the flow rate of the secondary heat medium supplied to the forward merging portion by the heat source machine pump, and the While providing a flow rate control means for adjusting the flow rate of the secondary side heat medium supplied to the load heat exchanger by the load side pump according to the load in the load heat exchanger,
For a heat storage heat source facility that provides a bypass path that short-circuits the return side heat transfer path from the load heat exchanger to the forward side merge section,
Connecting the bypass path to the return path for the heat source machine as a connection of the bypass path to the return side heat medium path from the load heat exchanger,
In the return path for the heat source unit, the heat medium that flows toward the side of the heat source unit by blocking the flow of the heat medium toward the branch point with the return path for heat dissipation at a location upstream of the connection point of the bypass path. In addition to providing a check means that allows only flow ,
Whereas a plurality of the heat source devices are installed in parallel, a return header for receiving a secondary side heat medium returning from the load side return passage through the return passage for the heat source device downstream from the connection point of the bypass passage. There is a configuration in which the secondary side heat medium is returned from the return side header to a plurality of the heat source units through the separate return paths for the heat source units .

  That is, according to the first characteristic configuration (see FIG. 1), when there is no heat medium flow toward the heat source unit return path 21 side from the forward-side merging section 5 in the bypass path 25 (the forward-side merging in the bypass path 25). (Including a state in which the flow of the heat medium toward the portion 5 is forcibly blocked by a check valve or the like, or a state in which there is a heat medium flow toward the forward junction 5 in the bypass passage 25) In the machine return path 21, the check means 27 allows the flow of the heat medium toward the heat source machine 4 at a location upstream of the connection point of the bypass path 25, whereby the load heat exchanger is passed through the load side return path 10. The secondary-side heat medium B returning from 9 is divided into the heat dissipation return path 20 and the heat source machine return path 21, and is almost loaded heat exchanger 9 with respect to each of the heat dissipation heat exchanger 2 and the heat source apparatus 4. Are returned in parallel with the temperature at the time of delivery from.

  On the other hand, when the heat medium flow toward the heat source machine return path 21 side from the forward junction 5 in the bypass path 25 occurs in the heat source machine return path 21 upstream of the connection point of the bypass path 25. The non-return means 27 flows in the heat source unit return path 21 through the bypass path 25 by blocking the reverse flow of the heat transfer medium 27 toward the branching point side with the heat return return path 20 at the location. The entire amount of B is returned to the heat source unit 4, and the inflow heat medium to the heat return return path 20 of the secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 20 is a bypass path. Without being mixed with the heat medium from 25, the temperature is returned to the heat-dissipating heat exchanger 2 almost at the temperature at the time of delivery from the load heat exchanger 9.

  That is, due to this, delay in consumption of the heat storage tank storage cold heat and heat storage tank storage heat caused by mixing of the heat medium from the bypass passage which has occurred in the conventional equipment configuration described above, that is, (see FIG. 2), the cold heat source equipment In this case, the consumption of the stored cold heat in the heat storage tank 1 does not proceed because the temperature of the secondary side heat medium B returned to the heat radiating heat exchanger 2 is lowered by mixing of the low temperature heat medium from the bypass passage 25 ′. In the case of the source equipment, a situation in which the consumption of the stored heat in the heat storage tank 1 does not proceed due to the high temperature of the secondary heat medium B that is returned to the heat exchanger 2 for heat radiation due to mixing of the high temperature heat medium from the bypass 25 '. ) Can be effectively avoided, and as a result, compared to conventional equipment, the cold and warm heat stored in the heat storage tank can be used more accurately and effectively for load processing in the load heat exchanger. The advantages of the method It can be made more advantageous in energy saving face in a state of utilizing the.

In carrying out this first characteristic configuration, as the second characteristic configuration of the present invention, the load side return path is divided into the heat dissipation return path and the heat source machine return path by a T-shaped or Y-shaped branch pipe structure. It may branch off.

  That is, in the conventional equipment configuration (see FIG. 2), the secondary side heat medium B sent from the load heat exchanger 2 to the load side return path 10 is diverted into the heat dissipation heat exchanger 2 and the heat source unit 4. On the other hand, in order to return in parallel, as described above, the secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 10 is received by the return side header 23 ′, and the return side header 23 ′ returns for heat dissipation. The secondary side heat medium B is returned in parallel to the heat dissipation heat exchanger 2 and the heat source unit 4 through the path 20 'and the heat source unit return path 21'. The first characteristic configuration (FIG. 1) is adopted. As shown in FIG. 5), there is no mixing of the heat medium from the bypass 25 on the upstream side of the branch point between the heat dissipation return path 20 and the heat source machine return path 21, and the load heat exchanger 9 passes through the load side return path 10. When the returning secondary heat medium B is simply shunted into the return path 20 for heat dissipation and the return path 21 for the heat source machine, the header is used. Medium shunt will having no appreciable sense when viewed from the header of the equalizing Yutakaka function (the heat medium to uniform Yutakaka by mixing).

  Focusing on this, as described above (see FIG. 1), the load-side return path 10 is branched into a heat radiation return path 20 and a heat source machine return path 21 by a T-shaped or Y-shaped branch pipe structure 22. By adopting such a structure and omitting the header for the heat medium distribution to the return path 20 for heat dissipation and the return path 21 for the heat source machine, the equipment cost can be reduced correspondingly, and the piping as the whole equipment The resistance can be reduced as much as possible, and the required pump power can also be reduced.

  In the implementation of the second characteristic configuration, when a plurality of load heat exchangers are provided in parallel (see FIG. 1), the secondary heat medium B sent from the plurality of load heat exchangers 9 is merged. In the load-side return path 10 (that is, the return-side main pipe) to be made, between the joining portion of the delivery heat medium B from each load heat exchanger 9 and the branch portion by the T-shaped or Y-shaped branch pipe structure 22 The length of the pipe is made as long as possible, so that the mixing of the secondary heat medium B sent from each load heat exchanger 9 after the merging is sufficient, and the temperature equalization of the heat medium B after the merging is promoted. It is desirable to do.

In the first characteristic configuration of the present invention, a plurality of the heat source devices are provided in parallel, whereas a secondary side heat medium returning from the load side return passage through the return passage for the heat source device is supplied to the bypass passage. Since a return side header that is received downstream from the connection point is provided and the secondary side heat medium is returned from the return side header to the plurality of heat source units through the separate return paths for the heat source units , the following functions are provided. Can also be obtained.

  That is, according to this structure (refer FIG. 1), compared with taking the structure which connects the bypass path 25 with respect to the said return side header 23, for example, in the bypass path 25, the return path 21 of the heat source machine return path 21 from the outgoing side junction part 5 is provided. When the heat medium flow toward the side occurs, heat medium mixing in the flow process in the pipe from the connection point of the bypass path 25 to the return side header 23 in the return path 21 for the heat source machine, and then in the return side header 23 Mixing the secondary side heat medium B flowing from the bypass path 25 and the secondary side heat medium B flowing from the load side return path 10 to the heat source machine return path 21 side more sufficiently. Then, the mixed heat medium B can be returned to each of the plurality of heat source units 4 through the branch return path 24 for the heat source unit in a temperature-equalized state.

  And by this, in the parallel operation of the plurality of heat source units 4, the temperature of the secondary side heat medium B sent out from these heat source units 4 can be more effectively and stably uniformed. The heat loss of the secondary side heat transfer medium B sent from each of the heat source machines 4 can be made more advantageous in terms of energy saving by suppressing the mixed heat loss in the outgoing side merging section 5 due to the difference in temperature, and the load heat exchange The temperature of the secondary heat medium B supplied to the vessel 9 can be further stabilized, and the load processing function in the load heat exchanger 9 can be further enhanced in terms of stability and temperature accuracy.

In addition, in this structure , since the return side header 23 is equipped in the return path 21 for heat source machines after branching from the load side return path 10, even if this return side header 23 is provided, it is parallel to the second characteristic configuration. In implementation, the effect of the second characteristic configuration, that is, the header that diverts the secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 10 into the heat dissipation return path 20 and the heat source machine return path 21. The effect (especially the effect that can reduce the piping resistance of the entire equipment) as much as possible can be fully utilized.

The third feature configuration of the present invention is the implementation of either the first or second feature configuration,
A short-circuit for temperature adjustment is provided to supply a part of the secondary side heat medium sent from the heat-dissipating heat exchanger to the heat-dissipating return path, and supplied to the heat-dissipating return path through the short-circuiting path. By adjusting the flow rate of the secondary heat medium to be performed, the temperature of the secondary heat medium returned from the heat dissipation return path to the heat dissipation heat exchanger is automatically adjusted to the set return temperature.

  That is, in the first characteristic configuration (see FIG. 1), it is possible to prevent the temperature of the return secondary heat medium B from returning to the heat-dissipating heat exchanger 2 due to mixing of the heat medium from the bypass path from being lowered or raised. Caused by temperature fluctuations of the secondary side heat medium B itself sent from the load heat exchanger 9 or variations in temperature of the secondary side heat medium B sent from a plurality of load heat exchangers 9 arranged in parallel. The temperature fluctuation of the secondary side heat medium B returned to the heat radiating heat exchanger 2 cannot be prevented. For this reason, the supply flow rate of the secondary side heat medium B by the heat radiating pump P1 (that is, for heat radiation) Even under a condition where the flow rate of the secondary side heat medium B in the heat exchanger 2 is constant, the heat exchange amount in the heat radiating heat exchanger 2 (that is, the amount of cold and warm heat extracted from the heat storage tank 1) is The phenomenon that still fluctuates remains.

On the other hand, according to the third characteristic configuration (see FIG. 1), the flow rate of the secondary side heating medium B supplied to the heat dissipation return path 20 through the temperature adjusting short circuit 28 is adjusted from the heat dissipation return path 20. Since the temperature of the secondary side heat medium B returned to the heat dissipation heat exchanger 2 is automatically adjusted to the set return temperature, the secondary side heat medium B by the heat dissipation pump P1 according to the increase or decrease of the load in the load heat exchanger 9. Naturally, the amount of heat exchange in the heat-dissipating heat exchanger 2 changes accordingly, but the amount of the secondary-side heat medium B supplied by the heat-dissipating pump P1 is constant ( In general, the heat source unit 4 is stopped with respect to the decrease in the load in the load heat exchanger 9 and the heat source unit is operated in parallel until the load is accommodated only by the stored cold heat or stored heat in the heat storage tank 1). Then, the temperature change of the secondary side heat medium B itself sent from the load heat exchanger 9 is changed. Regardless of variations in the temperature of the secondary side heat transfer medium B sent from the plurality of load heat exchangers 9 arranged in parallel, the heat exchange amount in the heat exchanger 2 for heat radiation is kept constant, and the heat storage tank The consumption per unit time of the stored cold heat and stored hot heat in 1 can be kept constant.

  And by this, combined with the effect of the first characteristic configuration (that is, the effect of preventing the delay in the consumption of the heat storage tank storage cold heat and the heat storage tank storage temperature caused by mixing of the heat medium from the bypass passage), The actual operation can be effectively brought close to the ideal operation for energy saving where the stored cold heat and stored heat in the heat storage tank 1 are almost used up at the end of the operation, and this can be made more advantageous in terms of energy saving. .

  FIG. 1 shows a heat storage type cold heat source facility, 1 is a static type ice heat storage tank for storing a primary heat medium A (water in this example), 2 is a primary side circulation path 3 between the ice heat storage tank 1 The heat exchanger for heat radiation that cools the secondary side heat medium B by exchanging heat between the primary side heat medium A and the secondary side heat medium B (water in this example) circulated through the secondary side heat medium B A plurality of refrigerators (that is, a cold heat generating heat source machine) 5 for cooling the outer side header 5 as an outgoing side merging portion, and the secondary side heat medium B cooled by the heat radiating heat exchanger 2 is used as the outgoing route 6 for radiating heat. In parallel with this, the secondary side heat medium B cooled by each refrigerator 4 is sent to each other heat source machine pump P2 through the parallel heat source machine forward path 7. It is sent to the outgoing header 5.

  The low-temperature secondary heat medium B supplied from the heat-dissipating heat exchanger 2 and each refrigerator 4 to the outward header 5 is mixed in the outward header 5 and then mixed in the flow process in the pipe. Is supplied in parallel to the plurality of load heat exchangers 9 through the load-side outward path 8 and the plurality of load-side branch outward paths 8a branched from the load-side pump P3. The secondary side heat medium B sent out (that is, the secondary side heat medium heated by the cold heat consumption in the load heat exchanger 9) is joined to the load side return path 10 through the parallel load side branch return path 10a. Thus, the heat radiation heat exchanger 2 and each refrigerator 4 are returned through the load side return path 10.

  A plurality of load-side pumps P3 are provided in a parallel arrangement in a portion upstream of the branch portion of the load-side branch forward passage 8a (specifically, the heat medium extraction portion from the forward-side header 5) in the load-side forward passage 8. Further, a plurality of heat radiation pumps P1 are provided in parallel with the heat radiation outward path 6.

  Among the plurality of load heat exchangers 9, the farthest load heat exchanger 9A having the longest pipe length from the forward header 5 is provided with a bypass 11 and sent from the farthest load heat exchanger 9A. The secondary side heat medium that bypasses the farthest load heat exchanger 9A through the secondary side heat medium B that passes through the farthest load heat exchanger 9A and the bypass circuit 11 based on the detected temperature of the secondary side heat medium B An automatic three-way valve 12 that automatically adjusts the temperature of the secondary heat medium B sent from the farthest load heat exchanger 9A to the set return temperature trm by adjusting the flow rate ratio with B is provided.

  Moreover, about the load heat exchangers 9B other than the farthest load heat exchanger 9A, the secondary passed through the load heat exchanger 9B based on the detected temperature of the secondary heat medium B sent from the load heat exchanger 9B. By adjusting the flow rate of the side heat medium B, an automatic two-way valve 13 that automatically adjusts the temperature of the secondary side heat medium B delivered from the load heat exchanger 9B to the set return temperature trm is provided.

  That is, by adjusting the flow rate for each load heat exchanger 9 by the automatic three-way valve 12 and the automatic two-way valve 13, the cooling output of each load heat exchanger 9 is changed to the cooling load q of each load heat exchanger 9. In response to this individual flow rate adjustment, the heat medium supply pressure in the load-side forward path 8 and the load-side branch forward path 8a is secured with a flow path secured by the detour 11 provided in the farthest load heat exchanger 9A. Prevent abnormal rise.

  For the farthest load heat exchanger 9A, in place of the automatic three-way valve 12 as described above, a method in which the bypass circuit 11 provided with a fixed resistance such as an orifice and the automatic two-way valve 13 is provided. Alternatively, the load heat exchanger 9B other than the farthest load heat exchanger 9A may be replaced with the automatic two-way valve 13 as described above, and the secondary side heat passed through the load heat exchanger 9B. A system equipped with a manual two-way valve for adjusting the flow rate of the medium B in an initial setting may be adopted.

  Each refrigerator 4 adjusts the output of the refrigerator by inverter control or the like based on the detected temperature of the secondary heat medium B to be sent to the heat source machine forward path 7, thereby sending the secondary side to the heat source machine forward path 7. A function of automatically adjusting the temperature of the heat medium B (that is, the refrigerator outlet temperature) to the set feed temperature tsm is provided, and the heat dissipation heat exchanger 2 is connected with the heat dissipation heat exchanger 2 to the heat dissipation path 6. The temperature sensor 14 for detecting the temperature to of the secondary side heat medium B delivered to the primary side, and the primary side that is passed through the heat dissipation heat exchanger 2 in the primary side circulation path 3 based on the detected temperature to of the temperature sensor 14 By adjusting the flow rate ratio between the heat medium A and the primary side heat medium A that bypasses the heat dissipation heat exchanger 2 through the bypass circuit 3a, the secondary side sent from the heat dissipation heat exchanger 2 to the heat dissipation outbound path 6 Automatic adjustment of the temperature to of the heating medium B to the set feed temperature tsm A three-way valve 15 is provided so that the secondary heat medium B cooled to the same temperature (set feed temperature tsm) is supplied to the forward header 5 from both the heat exchanger 2 for heat dissipation and each refrigerator 4. I have to do it.

  Reference numeral 16 denotes an outward temperature sensor for detecting the temperature ts (ideally a temperature equal to the set feed temperature tsm) of the secondary side heat medium B supplied to the load heat exchanger 9 in the load side outward path 8, and 17 denotes the load side. A return-side temperature sensor 18 for detecting a temperature tr (ideally equal to the set return temperature trm) of the secondary-side heat medium B returning from each load heat exchanger 9 in the return path 10, 18 is also the load side A flow rate sensor for detecting a flow rate G after the joining of the secondary side heat medium B returning from each load heat exchanger 9 in the return path 10 (in other words, a flow rate of the heat medium sent from the forward header 5 to the load side forward path 8). 19 is a controller for controlling the refrigerator 4 and the pumps P1 to P3 based on the detected temperatures ts and tr and the detected flow rate G of the temperature sensors 16 and 17 and the flow rate sensor 18.

  The controller 19 multiplies the temperature difference Δt (= tr−ts) between the temperature detected by the return temperature sensor 17 and the temperature detected by the forward temperature sensor 16 by the detected flow rate Q by the flow rate sensor 18. The cooling load Q (= Σq) as a whole of the load heat exchanger 9 group at each time point is calculated, and when the calculated cooling load Q is equal to or greater than a predetermined threshold load Qs (Q ≧ Qs), the controller 19 4 and the cooling of the secondary heat medium B by the heat-dissipating heat exchanger 2 (in other words, the generated cold heat in the refrigerator 4 and the cold heat extracted from the heat storage tank 1). Both) carry out a cooling heat supply operation in parallel with a refrigerator that processes the cooling load Q of the group 9 of load heat exchangers.

  When the calculated cooling load Q (= Σq) is less than the predetermined threshold load Qs (Q <Qs), the controller 19 cools the secondary heat medium B by the heat exchanger 2 for heat dissipation (in other words, The cooling heat supply operation of the heat storage tank alone that processes the cooling load Q of the load heat exchanger 9 group is carried out only with the cold heat extracted from the heat storage tank 1, and as a specific operation control, the controller 19 supplies the cold heat in parallel with the refrigerator The following controls (a) to (c) are executed at the time of operation, and the following controls (d) and (e) are executed at the time of the cold storage operation of the heat storage tank alone.

(Cooling supply operation in parallel with refrigerator)
(B) Operate all the heat radiation pumps P1 at the rated output, and keep the flow rate of the secondary side heat medium B supplied from the heat radiation heat exchanger 2 to the forward header 5 at a substantially maximum planned flow rate. The number of operating refrigerators 4 is changed according to the calculated cooling load Q.

  (B) In the form of operating the heat source unit pump P2 of the refrigerator 4 in the operating state, the operating unit number of the heat source unit pump P2 is changed in accordance with the change in the operating unit number of the refrigerator 4, and the heat source unit in the operating state The output of the pump P2 is adjusted by inverter control or the like in accordance with the calculated cooling load Q, whereby the flow rate of the secondary heat medium B supplied from the operating refrigerator 4 to the forward header 5 is changed to the calculated cooling load Q. Adjust accordingly.

  (C) The number of operating load side pumps P3 is changed according to the calculated cooling load Q, and the output of the load side pump P3 in the operating state is also adjusted by inverter control or the like according to the calculated cooling load Q. The flow rate G of the secondary side heat medium B supplied from the side header 5 to the load heat exchange device 9 is adjusted according to the calculation cooling load Q.

  That is, in the cold supply operation in parallel with the refrigerator, the number of operating units of the refrigerator 4 and the heat source unit pump P2 is changed, the output of the heat source unit pump P2 is adjusted, and the temperature of the secondary heat medium B to be sent is set as the set feed temperature. By adjusting the cooling amount of the secondary side heat medium B as the whole refrigerator group 4 by adjusting the output of each refrigerator 4 adjusted to tsm, the cooling of the secondary side heat medium B as the whole refrigerator group 4 Sum of the amount and the cooling amount of the secondary heat medium B in the heat exchanger 2 for heat dissipation (that is, the amount of cold generated per unit time as a whole of the refrigerator 4 group and the cold heat per unit time from the heat storage tank 1) The sum of the amount taken out) is balanced with the cooling load Q of the entire load heat exchanger 9 group.

  In addition, the supply flow rate of the secondary side heat medium B to the forward header 5 changes due to the change in the number of operating heat pumps P2 and the output adjustment, while the change in the number of operating load pumps P3 and the output adjustment result in the output flow adjustment. The flow rate G of the secondary side heat medium B sent from the side header 5 to the load side outward path 8 is balanced with the flow rate of the secondary side heat medium B supplied to the forward side header 5 from the refrigerator 4 and the heat exchanger 2 for heat radiation. .

(Cooling supply operation of single heat storage tank)
(D) With all the refrigeration machines 4 and all the heat source machine pumps P2 stopped, the number of operating heat radiation pumps P1 is changed according to the calculation cooling load Q, and the output of the heat radiation pump P1 in the operating state Is also adjusted by inverter control or the like in accordance with the calculated cooling load Q, whereby the flow rate of the secondary side heat medium B supplied from the heat exchanger 2 for heat radiation to the forward header 5 is adjusted in accordance with the calculated cooling load Q. .

  (E) The number of load-side pumps P3 to be operated is changed according to the calculated cooling load Q, and the output of the load-side pump P3 in the operating state is also adjusted by inverter control or the like according to the calculated cooling load Q. The flow rate G of the secondary side heat medium B supplied from the side header 5 to the load heat exchanger 9 is adjusted according to the calculation cooling load Q.

  That is, in the cold supply operation of the heat storage tank alone, the flow rate of the primary heat medium A in the heat dissipation heat exchanger 2 is adjusted and the temperature to the secondary heat medium B sent from the heat dissipation heat exchanger 2 is adjusted. Under the action of the automatic three-way valve 15 that adjusts to the set feed temperature tsm, by adjusting the flow rate of the secondary side heat medium B in the heat dissipation heat exchanger 2 by changing the number of operating heat pumps P1 and adjusting the output, The amount of cooling of the secondary side heat medium B in the heat dissipation heat exchanger 2 is adjusted, and the amount of cooling of the secondary side heat medium B in the heat dissipation heat exchanger 2 (that is, the unit time from the heat storage tank 1) The amount of cold heat extracted) is balanced with the cooling load Q of the entire load heat exchanger 9 group.

  In addition, the supply flow rate of the secondary side heat medium B to the forward header 5 changes due to the change in the number of operating heat pumps P1 and the output adjustment, while the change in the number of operation of the load side pumps P3 and the output adjustment The flow rate G of the secondary side heat medium B sent out from the header 5 to the load side outward path 8 is balanced with the flow rate of the secondary side heat medium B supplied from the heat dissipation heat exchanger 2 to the forward side header 5.

  Regarding the piping structure for returning the secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 10 to the heat dissipation heat exchanger 2 and the refrigerator 4, respectively, through the return side temperature sensor 17 and the flow rate sensor 18. Heat source unit for returning the secondary side heat medium B to the refrigeration unit 4 and the heat return unit 20 for returning the secondary side heat medium B to the heat exchanger 2 for heat dissipation, and the heat return unit 20 for refrigeration 4 For branching to the return path 21 by a T-shaped (or Y-shaped) branch tube structure 22 and connecting the heat dissipation return path 20 to the secondary side heat medium inlet of the heat dissipation heat exchanger 2 On the other hand, the return path 21 for the heat source unit is provided with a return side header 23 that receives the secondary side heat medium B returning through the return path 21 for the heat source unit, and the secondary side heat of the return side header 23 and each refrigerator 4 is provided. The inlet of the medium is connected by a separate branch return path 24 for the heat source machine.

  Further, in this piping structure, a bypass path 25 that short-circuits the outgoing header 5 and a midpoint of the return path 21 for the heat source machine, and a heat medium flow toward the outgoing header 5 side in the bypass path 25 And a bypass check valve 26 that allows only the flow of the heat medium toward the heat source machine return path 21 side is provided, and the heat source machine return path 21 is located upstream of the connection point of the bypass path 25. Return side check that allows only the heat medium flow toward the refrigerator 4 side (that is, the return side header 23 side) by preventing the heat medium flow toward the branch point side with the heat return return path 20 at the location. A valve 27 is provided.

  That is, in this cold heat source facility, the flow rate of the secondary side heat medium B supplied to the forward side header 5 by the heat radiation pump P1, and the flow rate of the secondary side heat medium B supplied to the forward side header 5 by the heat source machine pump P2. In addition, in the flow rate control in which the flow rate of the secondary side heat medium B supplied to the load heat exchanger 9 group by the load side pump P3 is adjusted by the controller 19 as the flow rate control means according to the calculation cooling load Q. The flow rate of the secondary heat medium B sent from the heat-dissipating heat exchanger 2 and the refrigerator 4 to the outward header 5 due to some reason such as a control error in the flow rate control is changed from the outward header 5 to the load heat exchanger 9 group. When the flow rate of the secondary side heat medium B to be sent to the heat source machine becomes larger than the flow rate of the secondary side heat medium B, the return side heat medium B that is the return side heat medium path from the load heat exchanger 9 through the bypass path 25 through the secondary side heat medium B 21 is caused to flow in a short-circuited manner, thereby dissipating heat exchanger 2 And to keep stable equipment operation while achieving a smooth equilibrium with cold output side of the refrigerator 4 and the cooling load Q on the side of the load heat exchanger 9.

  In addition, the bypass path 25 is connected to the heat source machine return path 21, and the return side check valve 27 is provided upstream of the connection point of the bypass path 25 in the heat source machine return path 21. When there is no heat medium flow toward the heat source machine return path 21 in the path 25 (including a state where the heat medium flow toward the forward header 5 in the bypass path 25 is blocked by the bypass check valve 26). The secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 10 is divided into the heat return return path 20 and the heat source machine return path 21 so that the heat release heat exchanger 2 and the refrigerator 4 For each of the above, the temperature is returned in parallel with the temperature at the time of delivery from the load heat exchanger 9, and in contrast, the flow of the heat medium toward the heat source unit return path 21 side in the bypass path 25 When it occurs, a heat source machine through the bypass 25 The entire amount of the secondary side heat medium B flowing into the return path 21 is returned to the refrigerator 4 side, and the secondary side heat medium B returning from the load heat exchanger 9 through the load side return path 10 is for heat dissipation. The heat medium flowing into the return path 20 is returned to the heat-dissipating heat exchanger 2 with the temperature at the time of delivery from the load heat exchanger 9 almost unchanged without being mixed with the low-temperature heat medium from the bypass path 25. It is.

  In other words, this prevents the temperature of the return secondary heat medium B from returning to the heat-dissipating heat exchanger 2 due to mixing of the low-temperature heat medium from the bypass passage 25 from being lowered, and the stored cold heat in the heat storage tank 1 is used as load heat. It can be effectively used for load processing in the exchanger 9.

  As for the heat exchanger 2 for heat dissipation, a temperature adjusting short circuit that supplies a part of the secondary side heat medium B sent from the heat exchanger 2 for heat dissipation to the heat dissipation outward path 6 to the heat dissipation return path 20 in a short circuit. A temperature sensor 29 that detects the temperature tr ′ of the secondary side heat medium B that is returned from the heat dissipation return path 20 to the heat dissipation heat exchanger 2 and a detection temperature tr ′ of the temperature sensor 29 is provided. By adjusting the flow rate of the secondary side heat medium B supplied to the heat dissipation return path 20 through the temperature adjusting short-circuit path 28, the secondary side heat medium returned from the heat dissipation return path 20 to the heat dissipation heat exchanger 2 is obtained. An automatic three-way valve 30 for automatically adjusting the temperature tr ′ of B to the set return temperature trm is provided, whereby the flow rate of the secondary side heat medium B supplied from the heat exchanger 2 for heat radiation to the forward header 5 When the cooling heat supply operation is performed in parallel with the refrigerator, the load heat exchanger 9 Heat exchange in the heat-dissipating heat exchanger 2 regardless of temperature fluctuations of the secondary-side heat medium B itself sent from the heat exchanger or variations in the temperature of the secondary-side heat medium B sent from each load heat exchanger 9 The amount (that is, the amount of cold heat taken out per unit time from the heat storage tank 1) is made as constant as possible.

  In the figure, P4 is a primary side circulation pump that circulates the primary side heat transfer medium A between the ice heat storage tank 1 and the heat dissipation heat exchanger 2 in the primary side circulation path 3, and 31 is in the tank of the ice heat storage tank 1. This is an ice making refrigerator that generates ice in the arranged ice making heat exchanger 32 (that is, stores cold heat in the ice heat storage tank 1).

[Another embodiment]
Next, other embodiments of the present invention will be listed.

  In the above-described embodiment, the cooling heat source equipment corresponding to the cooling load in the load heat exchanger 9 by cooling the secondary heat medium B in each of the heat exchanger 2 for heat dissipation and the heat source machine 4 (refrigerator) is shown. However, the present invention is also applied to the heat source equipment corresponding to the heating load in the load heat exchanger 9 by heating the secondary heat medium B in each of the heat dissipation heat exchanger 2 and the heat source unit 4. Can do.

  In the above-described embodiment, the forward header 5 is provided as the forward merging portion, and a piping structure is shown in which the forward header 5 is connected to the heat radiating forward path 6, the heat source machine forward path 7, and the load side forward path 8. However, the outgoing side merging portion is not necessarily limited to the header. In some cases, a structure is adopted in which the three of the heat radiating forward path 6, the heat source unit forward path 7, and the load side forward path 8 are connected to each other by pipes. May be.

  The flow rate of the secondary side heat medium B supplied to the forward side junction unit 5 by the heat radiation pump P1, the flow rate of the secondary side heat medium B supplied to the forward side junction unit 5 by the heat source unit pump P2, and the load side pump In order to automatically adjust the flow rate of the secondary side heat medium B supplied to the load heat exchanger 9 by P3 according to the load Q in the load heat exchanger 9, the specific adjustment form is the above-described embodiment. Various modifications are possible, for example, as the number of operating pumps of the load-side pump P3 is changed or the output is adjusted in accordance with the load Q in the load heat exchanger 9. The number of operating heat pumps P1 and the heat source unit pump P2 may be changed or the output may be adjusted based on the operating number of P3 and the output adjustment state.

  In the above-described embodiment, as a check means for preventing the heat medium flow toward the branching point side with the heat radiation return path 20 at a location upstream of the connection point of the bypass path 25 in the heat source machine return path 21, The example in which the check valve 27 is interposed in the return path 21 for the heat source machine has been shown. It may be configured with such as.

  In the above-described embodiment, an example in which the bypass check valve 26 that prevents the flow of the heat medium from the heat source return path 21 toward the outbound side merging portion 5 (outbound header) is provided in the bypass path 25 is described. In some cases, the bypass check valve 26 may be omitted to allow the flow of the heat medium in any direction in the bypass path 25, and each pump according to the heat medium flow state in the bypass path 25. You may employ | adopt the structure which adjusts the heat medium delivery flow rate of P1-P3 correctively.

  The heat storage tank 1 is not limited to a latent heat storage tank such as an ice heat storage tank, and may be a sensible heat storage tank such as a water heat storage tank that simply stores cold water or hot water.

  The heat storage type heat source equipment according to the present invention can be used for various applications that require cooling or heating, such as air conditioning such as cooling or heating, or cooling or heating of articles.

Facility configuration diagram showing the embodiment Equipment configuration diagram showing a conventional example

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat storage tank 2 Heat exchanger for heat dissipation 4 Heat source machine 5 Outbound side junction part 6 Outbound path for heat dissipation 7 Outbound path for heat source 8 Load side outbound path 9 Load heat exchanger 10 Load side return path 19 Flow rate control means 20 Heat dissipation return path 21 Return path for heat source machine 22 Branch pipe structure 23 Return side header 24 Branch return path for heat source machine 25 Bypass path 27 Checking means 28 Short circuit A Primary side heat medium B Secondary side heat medium P1 Heat dissipation pump P2 Heat source machine pump P3 Load side pump Q Load

Claims (3)

In the heat exchanger for radiating heat, the secondary side heat medium cooled and heated by exchanging heat with the primary side heat medium stored in the heat storage tank is supplied to the forward side merging section by the heat radiating pump through the radiating forward path. In parallel, the secondary heat medium cooled or heated by the heat source machine is supplied to the forward junction by the heat source machine pump through the heat source machine forward path,
While supplying the secondary side heat medium supplied from the heat-dissipating heat exchanger and the heat source unit to the forward side junction to the load heat exchanger by the load side pump through the load side forward path, in parallel with the supply of the heat medium The secondary side heat medium sent from the load heat exchanger to the load side return path is divided into a heat release return path and a heat source machine return path, and is parallel to the heat release heat exchanger and the heat source machine. To the configuration
In this configuration, the flow rate of the secondary heat medium supplied to the forward merging portion by the heat dissipation pump, the flow rate of the secondary heat medium supplied to the forward merging portion by the heat source machine pump, and the While providing a flow rate control means for adjusting the flow rate of the secondary side heat medium supplied to the load heat exchanger by the load side pump according to the load in the load heat exchanger,
A heat storage type heat source facility that provides a bypass path that short-circuits the return side heat transfer path from the load heat exchanger to the return side junction,
Connecting the bypass path to the return path for the heat source machine as a connection of the bypass path to the return side heat medium path from the load heat exchanger,
In the return path for the heat source unit, the heat medium that flows toward the side of the heat source unit by blocking the flow of the heat medium toward the branch point with the return path for heat dissipation at a location upstream of the connection point of the bypass path. In addition to providing a check means that allows only flow ,
Whereas a plurality of the heat source devices are installed in parallel, a return header for receiving a secondary side heat medium returning from the load side return passage through the return passage for the heat source device downstream from the connection point of the bypass passage. A heat storage type heat source facility that is configured to return the secondary side heat medium from the return side header to the plurality of heat source units through separate return paths for heat source units .   The heat storage type heat source facility according to claim 1, wherein the load side return path is branched into the heat dissipation return path and the heat source machine return path by a T-shaped or Y-shaped branch pipe structure. A short-circuit for temperature adjustment is provided to supply a part of the secondary side heat medium sent from the heat-dissipating heat exchanger to the heat-dissipating return path, and supplied to the heat-dissipating return path through the short-circuiting path. The temperature of the secondary side heat medium returned to the heat dissipation heat exchanger from the heat dissipation return path is automatically adjusted to the set return temperature by adjusting the flow rate of the secondary side heat medium. regenerative heat source equipment.

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