JP2006189228A - Air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the quality in air conditioning by allowing a temperature of heat carrying liquid supplied to an air conditioner to be changed to a target temperature early, in additionally starting a heat source device. <P>SOLUTION: A primary header 3 and a tertiary header 6 are connected with a turbo-type refrigerating machine 1 and an absorption-type refrigerating machine 7, and first, second and third indoor air conditioners 14, 15, 16 are connected with the primary header 3. The primary header 3 and the tertiary header 6 are connected through a bypass circuit 21 for conditioning the air. A part at an indoor air conditioner side and the absorption refrigerating machine 7 are connected by the tertiary header 6 through a three-way valve 26, and the three-way valve 26 is switched in additionally starting the turbo-type refrigerating machine 1 because of the increase of air conditioning load, to supply the cold water of high temperature from the first, second and third indoor air conditioners 14, 15, 16 with priority to reduce the load applied to the turbo-type refrigerating machine 1, thus a time for supplying the cold water of a target temperature to the primary header 3 from the turbo-type refrigerating machine 1 can be shortened. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air conditioning system configured to supply cold water or the like from a plurality of heat source devices such as refrigerators to a use side heat exchanger such as an air conditioner via a header.

In this type of air conditioning system, conventionally, a plurality of refrigerators and a plurality of air conditioners are connected via a pipe having a forward header and a pipe having a two-way valve, a return header, and a pump. And connecting both headers via a pipe with a header bypass valve.
As a result, when the air conditioning load on the air conditioner is low, one chiller is operated, and the number of chiller units increases as the air conditioning load increases. It is comprised so that it can do (refer patent document 1).
Japanese Patent Laid-Open No. 11-83126

  However, when the number of operating refrigerators increases with an increase in the air conditioning load, such as an increase in the number of operating air conditioners or an increase in the overall load, the newly started refrigerator enters a stable operation state. It takes time. In such a situation, the cold header water having a temperature close to the target temperature from the refrigerator in the stable operation state and the cold water having a temperature difference larger than the target temperature from the newly started refrigerator is the forward header. In this case, cold / hot water having a temperature difference from the target temperature is supplied to the air conditioner, and the capacity of the air conditioner is reduced to deteriorate the quality of the air conditioner.

The above point will be described in detail by taking as an example a case where air conditioning is performed with cold water from a refrigerator.
As a condition, two refrigerators were used, and the other refrigerator was additionally activated while one refrigerator was being operated in a stable operation state at 80% load.

  The other refrigerator has its output characteristics increasing with the additional activation [see the graph of FIG. 8 (a) showing the time-dependent change in the output characteristics of the refrigerator to be additionally activated]. The temperature of the chilled water supplied to the header from the chiller of the refrigerator decreases from 11 ° C. to 7 ° C. [See the graph of FIG. 8 (b) showing the change over time in the temperature of the chilled water from the additional chiller. ].

  Although the temperature of the cold water supplied to the header from the refrigerator in the stable operation state is almost unchanged at 7 ° C. [See the graph showing the change in the temperature of the cold water from the refrigerator in the stable operation state in FIG. ] In the header, the cold water supplied to the header from the additional start-up refrigerator and the cold water supplied to the header from the stable operation refrigerator are mixed, and the temperature of the cold water supplied from the header to the air conditioner is 9 ° C However, the time T1 until the chilled water temperature from the header reaches 7 ° C. is longer. [Refer to the graph of FIG. 8 (d) showing the time-dependent change in the chilled water temperature from the header] As a result, the capacity of each air conditioner is reduced and the quality of the air conditioning is reduced.

  The present invention has been made in view of such circumstances, and the inventions according to claims 1 and 2 promptly set the temperature of the heat transfer liquid supplied to the air conditioner or the like when the heat source device is additionally started. The invention according to claim 3 aims to improve the air conditioning quality by shifting to the target temperature, and the invention according to claim 3 supplies a heat carrier liquid having a small temperature difference from the target temperature to the additionally activated heat source unit. The purpose of the invention according to claim 4 is to reduce the load on the heat source machine and improve the quality of the air conditioning. When the characteristics of the heat source machine are different, the quality of the air conditioning is adjusted in accordance with these characteristics. The purpose of the invention according to claim 5 is to improve the quality of the air conditioning by automatically adjusting the supply state of the heat transfer liquid when the heat source machine is additionally started. The purpose of this is to claim The invention automatically adjusts the supply state of the heat transfer liquid when the heat source unit is additionally activated in accordance with the predetermined increase in the number of operating heat exchangers in use, so that the quality of air conditioning can be improved better. With the goal.

In order to achieve the above-described object, the invention according to claim 1
A plurality of heat source devices for controlling the temperature of the heat transfer liquid;
A use side heat exchanger for exchanging heat with the heat transfer liquid;
A header that is interposed between the heat source unit and the user side heat exchanger and mixes a heat transfer liquid from the heat source unit;
In the air conditioning system with
A piping mechanism for supplying the heat source liquid from the use side heat exchanger to the heat source unit;
The piping mechanism is adjusted so that the supply destination for directly supplying the heat carrier liquid returned from the use side heat exchanger to the heat source device can be selectively switched.

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 1, the piping mechanism is adjusted, for example, by switching the on-off valve when the heat source device is added and started in accordance with an increase in load on the use side heat exchanger side. By supplying the heat carrier liquid returned from the use side heat exchanger to the heat source machine that is operating in the stable operation state, increasing the supply amount of the heat carrier liquid returned from the use side heat exchanger, etc. It is possible to reduce the load applied to the heat source device that is additionally activated, to bring the temperature of the heat transfer liquid taken out from the heat source device that is additionally activated closer to the target temperature and to quickly shift to the target temperature. On the other hand, although the temperature of the heat transfer liquid taken out from the heat source unit that is operating in the stable operation state temporarily deviates from the target temperature, the target temperature is reached earlier than when a load is applied to the additionally activated heat source unit. The heat transfer liquids from these heat source units are mixed in the header to prevent the temperature difference from the target temperature of the heat transfer liquid supplied to the use side heat exchanger from becoming large, and to the target temperature at an early stage. Can be migrated.
Therefore, at the time of additional activation of the heat source unit, the temperature of the heat transfer liquid supplied to the use side heat exchanger such as an air conditioner is shifted to the target temperature at an early stage. Can improve the quality of air conditioning.
Also, for example, when the air conditioning load on the use side heat exchanger is suddenly reduced, such as when the number of operating heat exchangers on the use side is decreased after work or the target temperature is relaxed, the use side heat is adjusted by adjusting the piping mechanism. By supplying the heat transfer liquid from the exchanger to the heat source apparatus in a stable operation state, the heat transfer liquid taken out from the heat source apparatus is reduced due to the load reduction at the heat source apparatus due to the rapid decrease in the air conditioning load. The temperature exceeds the target temperature more than necessary, for example, it is possible to suppress a temperature decrease such as excessive cooling in the case of cooling, and the quality of air conditioning when the air conditioning load is rapidly reduced can be improved.

In order to achieve the above-described object, the invention according to claim 2
The air conditioning system according to claim 1,
A second header interposed between the use side heat exchanger and the heat source unit and capable of supplying a heat transfer liquid from the use side heat exchanger;
A first bypass pipe connected to the header and the second header to supply a heat transfer liquid from the header to the second header;
A second bypass pipe connected in parallel with the second header to the use side heat exchanger and the heat source unit, and for supplying a heat transfer liquid from the use side heat exchanger directly to the heat source unit; ,
A valve mechanism that switches proportionally or alternatively between a state in which the heat transfer liquid from the use side heat exchanger is supplied to the second header and a state in which the liquid is supplied to the second bypass pipe;
A piping mechanism is constituted by the second header, the second bypass piping, and the valve mechanism.
As the valve mechanism, a configuration by a combination of a three-way valve, a plurality of on-off valves, a three-way valve capable of adjusting a distribution flow rate ratio, a configuration by a combination of a plurality of flow rate adjustment valves, or the like can be applied.
Here, “connecting to the use side heat exchanger and the heat source device in parallel with the second header” means a part of the use side heat exchanger rather than the second header so as to bypass the second header. (Including the case of direct connection to the use side heat exchanger) and the part on the heat source unit side (including the case of direct connection to the heat source unit).

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 2, when the heat source device is additionally started in accordance with an increase in load on the use side heat exchanger side, the stable operation state is obtained by switching the valve mechanism. In the heat source machine in operation, the entire amount of the heat transfer liquid returned from the use side heat exchanger is directly supplied through the second bypass pipe, or directly from the use side heat exchanger to the heat source machine. Reduce the load on the heat source machine that is additionally started up, such as increasing the supply amount of the heat transfer liquid that is returned to, and bring the temperature of the heat carrier liquid taken out from the heat source machine that is additionally started up closer to the target temperature and quickly It is possible to shift to the target temperature. On the other hand, although the temperature of the heat transfer liquid taken out from the heat source unit that is operating in the stable operation state temporarily deviates from the target temperature, the target temperature is reached earlier than when a load is applied to the additionally activated heat source unit. The heat transfer liquids from these heat source units are mixed in the header to prevent the temperature difference from the target temperature of the heat transfer liquid supplied to the use side heat exchanger from becoming large, and to the target temperature at an early stage. Can be migrated.
Therefore, at the time of additional activation of the heat source unit, the temperature of the heat transfer liquid supplied to the use side heat exchanger such as an air conditioner is shifted to the target temperature at an early stage. Can improve the quality of air conditioning.
Also, for example, when the air conditioning load on the use side heat exchanger side is suddenly reduced, such as reducing the number of operating use side heat exchangers after operation or reducing the target temperature, the user side can be switched by switching the valve mechanism. By supplying the heat transfer liquid from the heat exchanger to the heat source unit in a stable operation state, the heat transfer liquid taken out from the heat source unit due to the load reduction at the heat source unit accompanying a rapid decrease in the air conditioning load Therefore, it is possible to suppress a temperature decrease such as excessive cooling in the case of cooling, and to improve the quality of air conditioning when the air conditioning load is suddenly reduced.

In order to achieve the above-described object, the invention according to claim 3
The air conditioning system according to claim 1 or 2,
A heat carrier liquid with a temperature difference larger than the target temperature is preferentially supplied to the heat source machine in the stable operation state, and a heat carrier liquid with a temperature difference smaller than the target temperature is supplied to the heat source machine in the activated state or the scheduled start-up state. To be configured.

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 3, it is possible to reduce the load on the heat source device by supplying a heat carrier liquid having a small temperature difference from the target temperature to the additionally activated heat source device. At the time of additional activation, since the temperature of the heat transfer liquid supplied to the use side heat exchanger is shifted to the target temperature at an early stage, it is possible to reduce the decrease in capacity in the use side heat exchanger and improve the quality of air conditioning.

That is, it is as follows if it explains in full detail taking the case where the cold water from a refrigerator is supplied to an air conditioner, and is air-conditioned as an example.
As a condition, two refrigerators are used, and one of the refrigerators is operated in a stable operation state at 80% load, while the other refrigerator is additionally started up. The high-temperature cold water returned from the air conditioner is supplied to the freezer, while the cold water returned from the air-conditioner and the cold water from the header are supplied to the additional start-up refrigerator.
In the additionally activated refrigerator, the output characteristics increase with the additional activation [see the graph of FIG. 7 (a) showing the change over time in the output characteristics of the additionally activated refrigerator]. Since the chilled water mixed with the chilled water from the header is supplied, the temperature of the chilled water supplied to the header from the additional start-up refrigerator decreases from 9 ° C. to 7 ° C. [(b) of FIG. [See the graph showing the change over time in the temperature of the chilled water from the additional starting refrigerator].

  The temperature of the cold water supplied to the header from the refrigerator in the stable operation state decreases from 9 ° C. to 7 ° C. [Change of the temperature of the cold water from the refrigerator in the stable operation state in FIG. In the header, the cold water supplied to the header from the newly activated refrigerator and the cold water supplied to the header from the chiller in the stable operation state are mixed, and the cold water supplied from the header to the air conditioner is mixed. Although the temperature also decreases from 9 ° C. to 7 ° C. (see the graph showing the change in the temperature of the chilled water from the header in FIG. 7D), the temperature of the chilled water from the header reaches 7 ° C. Time T2 becomes short, the capability of each air conditioner can be improved, and the quality of air conditioning can be improved.

In order to achieve the above-described object, the invention according to claim 4
In the air conditioning system according to any one of claims 1, 2, and 3,
The multiple heat source machines have different characteristics from each other,
And it is comprised so that the supply amount of the heat transfer liquid to each said heat source apparatus may be adjusted so that the characteristic of the said heat source apparatus may be suited.
Here, “different characteristics” means that the operating characteristics and models of turbo chillers and absorption chillers are different, the same model but different capacity, and even the same model and capacity. Various cases are included, such as the case where the flow rate of the heat transfer liquid supplied to the heat source device is varied in advance.

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 4, for example, in the case of using a heat source device having a quick start-up characteristic in a heat source device to be additionally activated, the burden on the heat source device is slightly increased, and stable operation is performed. The temperature of the heat transfer liquid supplied from the header to the use side heat exchanger can be shifted to the target temperature at an early stage in accordance with the characteristics of the heat source device, such as reducing the load on the heat source device in the state.
Therefore, when the characteristics of the heat source device are different, it is possible to eliminate the deterioration of the capacity of the use side heat exchanger at an early stage according to those characteristics and to improve the quality of the air conditioning well.

In order to achieve the above-described object, the invention according to claim 5
In the air-conditioning system in any one of Claims 1, 2, 3, and 4,
A temperature sensor for detecting the temperature of the heat transfer liquid returning to the heat source machine in a stable operation state;
Start-up sensing means for sensing the start-up of a heat source machine that is not in a stable operation state and outputting a start signal;
In response to the activation signal, temperature control means for adjusting the supply state of the heat transfer liquid to each heat source unit so that the temperature difference between the temperature of the heat transfer liquid sensed by the temperature sensor and the target temperature is increased. , Comprising.

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 5, as the additional activation of the heat source device is sensed by the activation sensing means, the heat carrier liquid having a large temperature difference from the target temperature is applied to the heat source device in the stable operation state. The load applied to the heat source devices in a stable operation state can be increased more than the heat source devices that are additionally started up, and the load applied to the heat source devices that are additionally started up can be reduced to quickly reach the target temperature. It is possible to prevent the temperature difference from the target temperature of the heat transfer liquid to be mixed with the header and to be supplied to the use-side heat exchanger from increasing, and to shift to the target temperature at an early stage.
Therefore, when the heat source unit is additionally started, the supply state of the heat transfer liquid is automatically adjusted and the temperature of the heat transfer liquid supplied to the use side heat exchanger is shifted to the target temperature at an early stage. It is possible to reduce the decrease in the capacity of the air conditioner and improve the air conditioning quality better.

In order to achieve the above object, the invention according to claim 6 provides:
In the air-conditioning system in any one of Claims 1, 2, 3, and 4,
A plurality of user-side heat exchangers;
An operation number sensing means for sensing a predetermined increase in the number of operating heat exchangers on the use side and outputting a start command signal to a heat source machine that is not in a stable operation state;
A temperature sensor for detecting the temperature of the heat transfer liquid returning to the heat source machine in a stable operation state;
Activation sensing means for sensing the activation of the heat source machine activated in response to the activation command signal from the operating number sensing means and outputting an activation signal;
In response to the activation signal, temperature control means for adjusting the supply state of the heat transfer liquid to each heat source unit so that the temperature difference between the temperature of the heat transfer liquid sensed by the temperature sensor and the target temperature is increased. And comprising.

(Action / Effect)
According to the configuration of the air conditioning system of the invention according to claim 6, the heat source in the stable operation state is detected by the operation number sensing means that senses the additional activation of the heat source device that accompanies the predetermined increase in the operation number of the use side heat exchanger. The heat transfer liquid with a large temperature difference from the target temperature is supplied to the machine, and the load on the heat source machine in the stable operation state is increased from that of the heat source machine that is additionally started, and the load on the heat source machine that is additionally started is increased. It can be reduced and transferred to the target temperature at an early stage, and the heat transfer liquid from those heat source devices is mixed in the header to suppress the temperature difference from the target temperature of the heat transfer liquid supplied to the use side heat exchanger from becoming large. At the same time, the target temperature can be shifted to an early stage.
Therefore, upon additional activation of the heat source device with a predetermined increase in the number of operating use side heat exchangers, the temperature of the heat transfer liquid supplied to the use side heat exchanger is automatically adjusted by automatically adjusting the supply state of the heat transfer liquid. Since the temperature is shifted to the target temperature at an early stage, it is possible to reduce the decrease in capacity in the use side heat exchanger and to improve the quality of the air conditioning more favorably.

According to the configuration of the air conditioning system of the invention according to claim 1, when the heat source device is added and started in accordance with an increase in load on the use side heat exchanger side, the heat source device that is operating in a stable operation state For example, by adjusting the piping mechanism such as switching on / off valves, the heat transfer liquid returned from the use side heat exchanger is supplied or the supply amount of the heat transfer liquid returned from the use side heat exchanger is increased. Further, it is possible to reduce the load applied to the additionally activated heat source unit, and to bring the temperature of the heat transfer liquid taken out from the additionally activated heat source unit closer to the target temperature and quickly shift to the target temperature. On the other hand, although the temperature of the heat transfer liquid taken out from the heat source unit that is operating in the stable operation state temporarily deviates from the target temperature, the target temperature is reached earlier than when a load is applied to the additionally activated heat source unit. The heat transfer liquids from these heat source units are mixed in the header to prevent the temperature difference from the target temperature of the heat transfer liquid supplied to the use side heat exchanger from becoming large, and to the target temperature at an early stage. Since it can be made to transfer, at the time of additional activation of the heat source device, it is possible to reduce the decrease in capacity in the use side heat exchanger and improve the quality of air conditioning.
Also, for example, when the air conditioning load on the use side heat exchanger is suddenly reduced, such as when the number of operating heat exchangers on the use side is decreased after work or the target temperature is relaxed, the use side heat is adjusted by adjusting the piping mechanism. By supplying the heat transfer liquid from the exchanger to the heat source apparatus in a stable operation state, the heat transfer liquid taken out from the heat source apparatus is reduced due to the load reduction at the heat source apparatus due to the rapid decrease in the air conditioning load. The temperature exceeds the target temperature more than necessary, for example, it is possible to suppress a temperature decrease such as excessive cooling in the case of cooling, and the quality of air conditioning when the air conditioning load is rapidly reduced can be improved.

  Next, embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1 is an overall schematic configuration diagram showing an embodiment 1 of an air conditioning system according to the present invention, and a primary header 3 as a header is connected to a turbo refrigerator 1 as a heat source device via a first pipe 2. At the same time, a tertiary header 6 as a second header is connected via a second pipe 5 having a first pump 4 interposed therebetween.
The primary header 3 is connected to an absorption refrigerator 7 as a heat source device via a third pipe 8, and the tertiary header 6 is connected via a fourth pipe 10 provided with a second pump 9. Is connected.

  The primary header 3 is connected to first, second and third indoor air conditioners 14, 15 and 16 as user-side heat exchangers via fifth, sixth and seventh pipes 11, 12 and 13. The secondary header 20 is connected to the first, second and third indoor air conditioners 14, 15 and 16 through the eighth, ninth and tenth pipes 17, 18 and 19.

  The primary header 3 and the tertiary header 6 are connected via a temperature adjusting bypass circuit 21. The temperature adjusting bypass circuit 21 is configured by interposing a flow rate adjusting valve 23 on an eleventh pipe 22 serving as a first bypass pipe, and as a heat transfer liquid from the turbo refrigerator 1 or the absorption refrigerator 7. A part of the cold water is not supplied to the first, second and third indoor air conditioners 14, 15, 16 and is returned to the turbo refrigerator 1 and the absorption refrigerator 7.

  The secondary header 20 and the tertiary header 6 are connected to each other through the twelfth pipe 24, and the intermediate portion of the twelfth pipe 24, the tertiary header 6 of the fourth pipe 10, and the second pump 9 are connected. An intermediate portion is connected via a thirteenth pipe 25 as a second bypass pipe and a three-way valve 26 so as to be in parallel with the tertiary header 6. The tertiary header 6 and the eighth, ninth, and ninth headers for supplying cold water from the first, second, and third indoor air conditioners 14, 15, and 16 to the turbo refrigerator 1 and the absorption refrigerator 7. 10 pipes 17, 18, 19, secondary header 20, twelfth and thirteenth pipes 24, 25, and three-way valve 26, which are manually switched, Called.

  With the above configuration, for example, the air conditioning load in the first, second and third indoor air conditioners 14, 15 and 16 increases in a state where only the absorption refrigerator 7 is stably operated, or the first When the operation of the third indoor air conditioner 16 is started while the second indoor air conditioners 14 and 15 are being operated, the air conditioning load increases, and the turbo refrigerator 1 is additionally activated. Can be operated as follows.

  The turbo refrigerator 1 and the first pump 4 are started, and the three-way valve 26 is switched so that cold water is supplied to the absorption refrigerator 7 only through the thirteenth pipe 25. As a result, the absorption refrigerator 7 is supplied with high-temperature cold water from the first, second, and third indoor air conditioners 14, 15, 16. On the other hand, the turbo refrigerator 1 includes a part of high-temperature cold water from the first, second, and third indoor air conditioners 14, 15, and 16 and low-temperature cold water from the temperature adjusting bypass circuit 21. Mixed at the tertiary header 6, cold water is supplied at a lower temperature than that for the absorption refrigerator 7.

  As a result, the load on the turbo refrigerator 1 can be reduced, the time for supplying the target temperature of cold water from the turbo refrigerator 1 to the primary header 3 can be shortened, and the first, second and second from the primary header 3 can be shortened. It is possible to shorten the time until the cold water having the target temperature is supplied to the three indoor air conditioners 14, 15, and 16.

Next, the results of a comparative experiment performed using the air conditioning system of Example 1 will be described.
As a procedure according to the first embodiment, at time 16: 34: 0, the turbo refrigerator 1 is additionally activated, and the three-way valve 26 is connected to the absorption refrigerator 1 only through the thirteenth pipe 25 with cold water. And the temperature of the cold water taken out from each of the turbo refrigerator 1, the primary header 3, and the absorption refrigerator 7 was measured. As a result, the result shown in the graph of the change with time of the cold water temperature in FIG. 2 was obtained.

That is, the load applied to the turbo refrigerator 1 was smaller than that in the absorption refrigerator 7, and it took about 5 minutes until the start-up time was shortened to a predetermined temperature (6.5 ° C.).
The temperature of the cold water from the primary header 3 rose only from 6.5 ° C. to 10 ° C., and the temperature rise was 3.5 ° C.
The time until the temperature of the cold water from the primary header 3 recovered to 6.5 ° C. was 5 minutes and 0 seconds.

  As a procedure according to the comparative example, with the three-way valve 26 switched so that the cold water is not supplied through the thirteenth pipe 25, the turbo refrigerator 1 is additionally started at 15:23:30. The temperature of the cold water taken out from each of the turbo refrigerator 1, the primary header 3, and the absorption refrigerator 7 was measured. As a result, the result shown in the graph of the change with time of the cold water temperature in FIG. 9 was obtained.

That is, the turbo refrigerator 1 was loaded with the same amount as the absorption refrigerator 7, took time to start up, and took about 6 minutes to decrease to a predetermined temperature (6.5 ° C.).
The temperature of the cold water from the primary header 3 rose from 6.5 ° C. to 10.5 ° C., and the temperature rise range was 4.0 ° C.
The time until the temperature of the cold water from the primary header 3 recovered to 6.5 ° C. was 5 minutes 30 seconds.

From the above results, in the case of Example 1, the time shortening effect of 16.7% (≈1 / 6) was recognized when the temperature of the cold water from the turbo refrigerator 1 reached a predetermined temperature.
Further, in terms of the temperature rise width of the temperature of the cold water from the primary header 3, an improvement effect of 12.5% (= 0.5 / 4.0) is recognized, and the temperature of the cold water from the primary header 3 is 6. In terms of the time until recovery to 5 ° C., a time shortening effect of 9.1% (≈30 / 330) was recognized.
In the experiment described above, the turbo chiller 1 was newly activated with no change in the air conditioning load on the first, second, and third indoor air conditioners 14, 15, 16 side. Therefore, the temperature of the chilled water from the absorption refrigeration machine 7 is reduced due to the start of the turbo chiller 1, but even if the turbo chiller 1 is additionally started up due to an increase in the air conditioning load, the change in the chilled water temperature over time The same tendency is observed in, and it is judged that this experiment can prove the effect.

  FIG. 3 is an overall schematic configuration diagram showing an air conditioning system according to a second embodiment of the present invention. The first, second and third refrigerators 31, 32 and 33 serving as heat source units are connected to a fourteenth pipe 34. Is connected to the primary header 35, and the third, fourth, and fifth pumps 36, 37, and 38 are interposed through the fifteenth, sixteenth, and seventeenth pipes 39, 40, and 41, respectively. A header 42 is connected. As each of the first, second, and third refrigerators 31, 32, and 33, various refrigerators such as an absorption refrigerator, an electric turbo refrigerator, and a screw refrigerator can be applied.

  The primary header 35 is provided with first, second and third indoor air conditioners 45, 46 and 47 as use side heat exchangers via an eighteenth pipe 44 having a sixth pump 43 interposed therebetween. A secondary header 49 is connected to each of the first, second, and third indoor air conditioners 45, 46, 47 through a nineteenth pipe 48.

  The primary header 35 and the tertiary header 42 are connected via a temperature adjusting bypass circuit 50. The temperature adjusting bypass circuit 50 is configured by inserting a flow rate adjusting valve 52 in a twentieth pipe 51 serving as a first bypass pipe, and from the first, second and third refrigerators 31, 32, 33. The first, second, and third refrigerators 31, 32, and 33 are not supplied to the first, second, and third indoor air conditioners 45, 46, and 47 without supplying a part of the cold water as the heat transfer liquid. It is configured to return.

  The secondary header 49 and the tertiary header 42 are connected via the 21st piping 53, and the middle portion of the 21st piping 53 and each of the 15th, 16th and 17th piping 39, 40, 41 are connected. The 22nd, 23rd, and 23rd as second bypass pipes are arranged so that the locations between the tertiary header 42 and the third, fourth, and fifth pumps 36, 37, 38 are in parallel with the tertiary header 42. The twenty-fourth pipes 54, 55, and 56 are connected to the first, second, and third three-way valves 57, 58, and 59. Third, fourth and fourth for supplying cold water from the first, second and third indoor air conditioners 45, 46 and 47 to the first, second and third refrigerators 31, 32 and 33, respectively. Fifth pumps 36, 37, 38, fifteenth, sixteenth and seventeenth pipes 39, 40, 41, tertiary header 42, nineteenth pipe 48, secondary header 49, twenty-first, twenty-second. The 23 and 24th pipes 53, 54, 55 and 56 and the first, second and third three-way valves 57, 58 and 59 are configured to be manually switched. This is called a piping mechanism.

  With the above configuration, for example, the air conditioning load in the first, second, and third indoor air conditioners 45, 46, and 47 increases while the first and second refrigerators 31 and 32 are stably operated. In the case where the third refrigerator 33 is additionally started as the operation of the third indoor air conditioner 47 is started while the first and second indoor air conditioners 45 and 46 are being operated. In addition, it can be operated as follows.

  The third refrigerator 33 and the fifth pump 38 are started, and the first and second three-way valves 57 and 58 are connected to the first and second refrigerators only through the 22nd and 23rd pipes 54 and 55. Further, the third three-way valve 59 is switched from the tertiary header 42 to the third refrigerator 33 through the seventeenth pipe 41 so as to be supplied with the cold water. Thus, the first and second refrigerators 31 and 32 are supplied with high-temperature cold water from the first, second and third indoor air conditioners 45, 46 and 47. On the other hand, the third refrigerator 33 includes a part of the high-temperature cold water from the first, second, and third indoor air conditioners 45, 46, and 47, and the low-temperature cold water from the temperature adjusting bypass circuit 50. Are mixed in the tertiary header 42, and cold water having a temperature lower than that for the first and second refrigerators 31 and 32 is supplied.

  As a result, the load on the third refrigerator 33 can be reduced, the time for supplying cold water at the target temperature from the third refrigerator 33 to the primary header 35 can be shortened, and the first and second from the primary header 35 can be reduced. In addition, it is possible to shorten the time until the cold water having the target temperature is supplied to the third indoor air conditioners 45, 46, and 47.

FIG. 4 is an overall schematic configuration diagram showing Embodiment 3 of the air conditioning system according to the present invention, and the differences from Embodiment 2 are as follows.
That is, a location between each of the first, second and third indoor air conditioners 45, 46 and 47 of the nineteenth pipe 48 and the secondary header 49, and the fifteenth, sixteenth and seventeenth pipes 39, 40, 41 and the third header 42 and the portions between the third, fourth and fifth pumps 36, 37, 38 are arranged in parallel with the tertiary header 42, respectively. , Via a pipe 69 as a second bypass pipe provided with the sixth, seventh, eighth and ninth three-way valves 61, 62, 63, 64, 65, 66 (parts in the middle are shared with each other) Connected. Other configurations are the same as those of the second embodiment, and the same reference numerals are given and description thereof is omitted. Third, fourth and fourth for supplying cold water from the first, second and third indoor air conditioners 45, 46 and 47 to the first, second and third refrigerators 31, 32 and 33, respectively. Fifth pump 36, 37, 38, fifteenth, sixteenth and seventeenth pipes 39, 40, 41, tertiary header 42, nineteenth pipe 48, secondary header 49, fourth, fifth The sixth, seventh, eighth and ninth three-way valves 61, 62, 63, 64, 65, 66 and the pipe 69 are configured to be manually switched, and the piping mechanism Called.

  According to the third embodiment, the total amount of cold water from each of the first, second, and third indoor air conditioners 45, 46, 47 is supplied to the first, second, and third refrigerators 31, 32, 33. It can be returned to the desired one, and colder cold water can be supplied to the additionally activated refrigerator.

FIG. 5 is an overall schematic configuration diagram showing Embodiment 4 of the air conditioning system according to the present invention. The differences from Embodiment 2 are as follows.
In other words, the first, second, and third refrigerators 31, 32, and 33 are provided with first, second, and third activation sensors 71, 72, and 73 that sense the activation, respectively. Moreover, the temperature of the cold water returned to each refrigerator is set downstream from the third, fourth, and fifth pumps 36, 37, and 38 of the first, second, and third refrigerators 31, 32, and 33, respectively. First, second and third temperature sensors 74, 75 and 76 for detection are provided. Further, fourth, fifth and sixth temperature sensors for detecting the temperature of the cold water taken out from each refrigerator on the cold water take-out side of each of the first, second and third refrigerators 31, 32 and 33. 74a, 75a, 76a are provided.

  First, second and third activation sensors 71, 72, 73, first, second and third temperature sensors 74, 75, 76, and fourth, fifth and sixth temperature sensors 74a, 75a , 76a are connected to a controller 77 as temperature control means as shown in the block diagram of the temperature control system of FIG. 6, and the controller 77 is connected to first, second and third three-way valves 57, 58. , 59 are connected.

The controller 77 includes an activation sensing means 78, first and second temperature sensor selection means 79 and 79a, first and second cold water temperature detection means 80 and 81, and first and second comparison means 82. , 83 are provided.
The activation sensing means 78 detects a new activation state while sensing at least one activation state based on signals from the first, second and third activation sensors 71, 72, 73. The detected refrigerator is detected as an additional startup refrigerator that is not in a stable operation state, and an activation signal is output.

  In response to the activation signal from the activation sensing unit 78, the first temperature sensor selection unit 79 selects a temperature sensor provided in the refrigerator in a stable operation state, and inputs an input signal from the temperature sensor to the first temperature sensor. This is sent to the cold water temperature detecting means 80. The second temperature sensor selecting means 79a selects a temperature sensor provided on the cold water take-out side of the additional start refrigerator in response to the start signal from the start sensing means 78, and outputs from the temperature sensor. An input signal is sent to the second cold water temperature detecting means 81.

  The first cold water temperature detection means 80 detects the temperature of the cold water supplied to the refrigerator in the stable operation state by a temperature sensor provided on the first cold water temperature detection means 80, while the second cold water temperature detection means 81 performs additional activation. The temperature of the cold water taken out from the refrigerator is detected by a temperature sensor provided there.

  In the first comparison means 82, the temperature of the cold water supplied to the refrigerator in the stable operation state detected by the first cold water temperature detection means 80 is inputted, and the temperature difference between the temperature and the set temperature higher than the target temperature. When the detected temperature is lower than the high temperature set value, an open signal is output to the three-way valve corresponding to the refrigerator, and the tertiary header 42 is not passed. In addition, high-temperature cold water from the first, second, and third indoor air conditioners 45, 46, and 47 is preferentially supplied to the refrigerator.

  In the second comparison unit 83, the temperature of the cold water taken out from the additional start-up refrigerator detected by the second cold water temperature detection unit 81 is input, and the temperature and a low temperature set value close to the target temperature (for example, 7.3 ℃ etc.), if the detected temperature is lower than the low temperature set value, it is judged that the additional start-up refrigerator has also shifted to the stable operation state, and the open signal was output first A close signal is output to the valve so that the chilled water from the first, second and third indoor air conditioners 45, 46 and 47 is supplied to the refrigerator in the stable operation state through the tertiary header 42. It has become.

  With the above configuration, when any one of the refrigerators is additionally activated, the high-temperature cold water from the first, second, and third indoor air conditioners 45, 46, and 47 is automatically operated stably until then. It is possible to preferentially supply the refrigerator in the state, and to reduce the load on the additionally activated refrigerator.

  In the above embodiment, the three-way valve is switched between a state in which cold water from the indoor air conditioner (14, etc.) is supplied to the tertiary header (6, etc.) and a state in which it is supplied to the second bypass pipe (25, etc.). It is configured to selectively switch using, but a configuration using a plurality of on-off valves instead of the three-way valve, or a three-way valve capable of adjusting the distribution flow rate ratio, or a plurality of flow rate adjusting valves It is possible to apply a configuration using the above and collectively refer to the valve mechanism.

Moreover, in the said Example, the tertiary header (6 etc.) which mixes the low temperature cold water which does not pass the indoor air conditioner (14 etc.) from the 1st bypass piping 22 and 51, and the cold water from an indoor air conditioner (14 etc.). ) Is provided to configure the piping mechanism, but the piping mechanism may be configured not to provide a tertiary header (6 or the like). Further, the piping mechanism may be configured as follows.
(1) Connect an indoor air conditioner (14, etc.) and a freezer (1 etc.) in the scheduled start-up state through a pipe with a flow rate adjustment valve. Is configured to increase
(2) An indoor air conditioner (such as 14) and a refrigerator that is scheduled to be activated (such as 1) are connected via a large-diameter pipe and a small-diameter pipe, and cold water is supplied through the small-diameter pipe during startup. When a steady operation state is reached, cold water is supplied through a large-diameter pipe.

The present invention may be implemented with the following configuration.
(1) In the fourth embodiment, the first, second and third indoor air conditioners 45, 46, 47 are sensed that the number of operating units has increased from two to three, so that the refrigerator is not in a stable operating state. An operation number sensing means for outputting a start command signal is added, and the refrigerator is configured to start in response to the start command signal. With the additional start, the first, second and second The high-temperature cold water from the indoor air conditioners 45, 46, 47 side of No. 3 can be preferentially supplied to the refrigerators in the stable operation state so far, and the load on the additional start-up refrigerator can be reduced. Constitute.
(2) As a refrigerator, use a combination of refrigerators having different characteristics. For example, in a refrigerator that is additionally started up, when using a refrigerator with fast startup characteristics, the burden on the refrigerator is slightly increased. The supply state of cold water to the refrigerator is adjusted according to the characteristics of the refrigerator, such as reducing the load on the refrigerator in the stable operation state. In this case, the temperature of the chilled water supplied from the primary headers 3 and 35 to the indoor air conditioner can be shifted to the target temperature at an early stage, and the deterioration of the capacity of the indoor air conditioner can be eliminated at an early stage to improve the air conditioning quality. There is.
(3) When using an absorption refrigerator that operates using exhaust heat from a cogeneration system as a refrigerator, considering the effective use of exhaust heat, the absorption refrigerator is preferentially in a stable operation state. It is configured to operate as a freezer.

  As the present invention, as in the above-described embodiment, when applied to cooling with cold water, cold water at a desired temperature can be supplied to the indoor air conditioner at an early stage, and the quality of air conditioning can be suitably improved from the dehumidifying surface. It can also be applied to the case where a heat exchanger or a heater that obtains hot water by exchanging heat with the exhaust heat from the cogeneration system is used as a heat source unit, and the hot water is supplied as heat transfer liquid to the indoor air conditioner for heating. .

  Moreover, as a use side heat exchanger, the cooling device of a production facility of a factory, the water tank for cooling of a printing factory, etc. can be applied, Furthermore, it can apply also when an indoor air conditioner is one.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole schematic block diagram which shows Example 1 of the air conditioning system which concerns on this invention. 3 is a graph showing a change over time in the cold water temperature of an experiment for Example 1. FIG. It is a whole schematic block diagram which shows Example 2 of the air conditioning system which concerns on this invention. It is a whole schematic block diagram which shows Example 3 of the air conditioning system which concerns on this invention. It is a whole schematic block diagram which shows Example 4 of the air conditioning system which concerns on this invention. It is a block diagram of the temperature control system of Example 4. It is a graph with which it uses for description of this invention, (a) is a graph which shows the time-dependent change of the output characteristic of the refrigerator which starts additionally, (b) is the time-dependent change of the cold water temperature from the refrigerator which starts additionally. The graph which shows, (c) is a graph which shows the time-dependent change of the chilled water temperature from the refrigerator of a stable operation state, (d) is a graph which shows the time-dependent change of the chilled water temperature from a header. It is a graph with which it uses for description of a prior art example, (a) is a graph which shows the time-dependent change of the output characteristic of the refrigerator which starts additionally, (b) is the time-dependent change of the cold water temperature from the refrigerator which starts additionally. The graph which shows, (c) is a graph which shows the time-dependent change of the chilled water temperature from the refrigerator of a stable operation state, (d) is a graph which shows the time-dependent change of the chilled water temperature from a header. It is a graph which shows the time-dependent change of the cold water temperature of the experiment about a comparative example.

Explanation of symbols

1 ... Turbo refrigerator (heat source)
3 ... Primary header (header)
4 ... 1st pump (piping mechanism)
5 ... Second piping (piping mechanism)
6 ... Tertiary header (second header, piping mechanism)
7 ... Absorption refrigerator (heat source)
9 ... Second pump (pipe mechanism)
10 ... Fourth piping (pipe mechanism)
14 ... 1st indoor air conditioner (use side heat exchanger)
15 ... 2nd indoor air conditioner (use side heat exchanger)
16 ... Third indoor air conditioner (use side heat exchanger)
17 ... Eighth pipe (pipe mechanism)
18 ... ninth pipe (pipe mechanism)
19: Tenth pipe (pipe mechanism)
20 ... Secondary header (Piping mechanism)
22 ... Eleventh piping (first bypass piping)
24 ... Twelfth pipe (pipe mechanism)
25 ... 13th piping (2nd bypass piping, piping mechanism)
26. Three-way valve (valve mechanism, piping mechanism)
31 ... 1st refrigerator (heat source machine)
32 ... Second refrigerator (heat source machine)
33 ... Third refrigerator (heat source machine)
35 ... Primary header (header)
36 ... Third pump (piping mechanism)
37 ... Fourth pump (pipe mechanism)
38 ... Fifth pump (pipe mechanism)
39 ... 15th piping (piping mechanism)
40. Sixteenth piping (piping mechanism)
41. Seventeenth piping (piping mechanism)
42 ... Tertiary header (second header, piping mechanism)
45 ... 1st indoor air conditioner (use side heat exchanger)
46. Second indoor air conditioner (use side heat exchanger)
47 ... Third indoor air conditioner (use side heat exchanger)
48 ... 19th piping (piping mechanism)
49 ... Secondary header (Piping mechanism)
51 .. 20th pipe (first bypass pipe)
53 ... 21st piping (piping mechanism)
54 ... 22nd piping (2nd bypass piping, piping mechanism)
55. 23rd piping (second bypass piping, piping mechanism)
56: 24th piping (second bypass piping, piping mechanism)
57. First three-way valve (valve mechanism, piping mechanism)
58. Second three-way valve (valve mechanism, piping mechanism)
59 ... Third three-way valve (valve mechanism, piping mechanism)
61 ... Fourth three-way valve (valve mechanism, piping mechanism)
62 ... Fifth three-way valve (valve mechanism, piping mechanism)
63 ... Sixth three-way valve (valve mechanism, piping mechanism)
64: Seventh three-way valve (valve mechanism, piping mechanism)
65 ... Eighth three-way valve (valve mechanism, piping mechanism)
66 ... Ninth three-way valve (valve mechanism, piping mechanism)
69 ... Piping (second bypass piping, piping mechanism)
77 ... Controller (temperature control means)
78. Activation detection means

Claims (6)

A plurality of heat source devices for controlling the temperature of the heat transfer liquid;
A use side heat exchanger for exchanging heat with the heat transfer liquid;
A header that is interposed between the heat source unit and the user side heat exchanger and mixes a heat transfer liquid from the heat source unit;
In the air conditioning system with
A piping mechanism for supplying the heat source liquid from the use side heat exchanger to the heat source unit;
An air conditioning system characterized in that the piping mechanism is adjusted to selectively switch the supply destination for directly supplying the heat transfer liquid returned from the use side heat exchanger to the heat source unit. The air conditioning system according to claim 1,
A second header interposed between the use side heat exchanger and the heat source unit and capable of supplying a heat transfer liquid from the use side heat exchanger;
A first bypass pipe connected to the header and the second header to supply a heat transfer liquid from the header to the second header;
A second bypass pipe connected in parallel with the second header to the use side heat exchanger and the heat source unit, and for supplying a heat transfer liquid from the use side heat exchanger directly to the heat source unit; ,
A valve mechanism that switches proportionally or alternatively between a state in which the heat transfer liquid from the use side heat exchanger is supplied to the second header and a state in which the liquid is supplied to the second bypass pipe;
An air conditioning system in which a piping mechanism is constituted by the second header, the second bypass piping, and the valve mechanism. The air conditioning system according to claim 1 or 2,
A heat carrier liquid with a temperature difference larger than the target temperature is preferentially supplied to the heat source machine in the stable operation state, and a heat carrier liquid with a temperature difference smaller than the target temperature is supplied to the heat source machine in the activated state or the scheduled start-up state. The air conditioning system that is. In the air conditioning system according to any one of claims 1, 2, and 3,
The multiple heat source machines have different characteristics from each other,
And the air-conditioning system which adjusts supply_amount | feed_rate of the heat transfer liquid to each said heat-source equipment so that the characteristic of the said heat-source equipment may be suited. In the air-conditioning system in any one of Claims 1, 2, 3, and 4,
A temperature sensor for detecting the temperature of the heat transfer liquid returning to the heat source machine in a stable operation state;
Start-up sensing means for sensing the start-up of a heat source machine that is not in a stable operation state and outputting a start-up signal,
In response to the activation signal, temperature control means for adjusting the supply state of the heat transfer liquid to each heat source unit so that the temperature difference between the temperature of the heat transfer liquid sensed by the temperature sensor and the target temperature is increased. An air conditioning system that is equipped with In the air-conditioning system in any one of Claims 1, 2, 3, and 4,
A plurality of user-side heat exchangers;
An operation number sensing means for sensing a predetermined increase in the number of operating heat exchangers on the use side and outputting a start command signal to a heat source machine that is not in a stable operation state;
A temperature sensor for detecting the temperature of the heat transfer liquid returning to the heat source machine in a stable operation state;
Activation sensing means for sensing the activation of the heat source machine activated in response to the activation command signal from the operating number sensing means and outputting an activation signal;
In response to the activation signal, temperature control means for adjusting the supply state of the heat transfer liquid to each heat source unit so that the temperature difference between the temperature of the heat transfer liquid sensed by the temperature sensor and the target temperature is increased. , Which is an air conditioning system.

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